CN107328055A - Air conditioner and its efficiency computational methods - Google Patents

Air conditioner and its efficiency computational methods Download PDF

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Publication number
CN107328055A
CN107328055A CN201710775562.7A CN201710775562A CN107328055A CN 107328055 A CN107328055 A CN 107328055A CN 201710775562 A CN201710775562 A CN 201710775562A CN 107328055 A CN107328055 A CN 107328055A
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enthalpy
heat exchanger
refrigerant
msub
temperature
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刘燕飞
李金波
张�浩
戚文端
杨亚新
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GD Midea Air Conditioning Equipment Co Ltd
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Guangdong Midea Refrigeration Equipment Co Ltd
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Abstract

The invention discloses a kind of air conditioner and its efficiency computational methods, this method comprises the following steps：Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；Obtain the housing heat dissipation capacity Q of compressorloss；Obtain the temperature t of gas returning port in compressor1, in compressor exhaust outlet temperature t2, outdoor heat exchanger first end temperature t4, indoor heat exchanger first end temperature t7With indoor environment temperature t9；When the current working of air conditioner is cooling condition, respectively according to t1、t2、t4、t7And t9Correspondence generates the refrigerant enthalpy and lubricating oil enthalpy of gas returning port, exhaust outlet, outdoor heat exchanger first end and indoor heat exchanger first end；Respectively according to the mixture enthalpy h of refrigerant enthalpy each temperature detecting point of generation corresponding with lubricating oil enthalpy of above-mentioned each temperature detecting point1、h2、h4And h7；According to the power of compressor, Qloss、h1、h2、h4And h7Generate the refrigerating capacity of air conditioner；The efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Description

Air conditioner and its efficiency computational methods
Technical field
The present invention relates to air conditioner technical field, the efficiency computational methods of more particularly to a kind of air conditioner, a kind of air conditioner With a kind of non-transitorycomputer readable storage medium.
Background technology
It is comfortably the problem of user more pays close attention to that whether air conditioner, which saves,.
Current air conditioner is difficult to maintain and preferably transported operationally due to that can not know the situation of change of efficiency Row state, cooling or heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solving one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention One purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
Fourth object of the present invention is the efficiency computational methods for proposing another air conditioner.
The 5th purpose of the present invention is to propose another air conditioner.
The 6th purpose of the present invention is to propose another non-transitorycomputer readable storage medium.
To reach above-mentioned purpose, a kind of efficiency computational methods for air conditioner that first aspect present invention embodiment is proposed include Following steps：Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；The housing for obtaining compressor dissipates Heat Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, room The outdoor heat exchanger first end temperature t of external heat exchanger first end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7With indoor environment temperature t9；When the current working of the air conditioner is cooling condition, according to gas returning port in the compressor Gas returning port temperature t1Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, it is vented according in the compressor The exhaust port temperatures t of mouth2With the indoor environment temperature t9Generate the refrigerant enthalpy h of exhaust outlet2 refrigerants, according to the compressor The exhaust port temperatures t of middle exhaust outlet2Generate the lubricating oil enthalpy h of exhaust outlet2 lubricating oil, according to the room of the outdoor heat exchanger first end External heat exchanger first end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilAnd root According to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end Value h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGeneration The mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGeneration exhaust The mixture enthalpy h of mouth2, according to the refrigerant enthalpy h of the outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilIt is raw Into the mixture enthalpy h of outdoor heat exchanger first end4With the refrigerant enthalpy h according to the indoor heat exchanger first end7 refrigerantsWith Lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；According to the power of the compressor, the pressure The housing heat dissipation capacity Q of contracting machineloss, the gas returning port mixture enthalpy h1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger The mixture enthalpy h of first end4With the mixture enthalpy h of indoor heat exchanger first end7Generate the refrigerating capacity of air conditioner；And root The efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity Q of the power of machine, air conditioner power consumption and compressorloss, and obtain gas returning port in compressor, exhaust outlet, Outdoor heat exchanger first end, the temperature of indoor heat exchanger first end and indoor environment temperature, and it is in refrigeration work in air conditioner The refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points are generated during condition according to the temperature of each above-mentioned temperature detecting point, and The mixture enthalpy of multiple temperature detecting points is further generated, the housing heat dissipation capacity of power, compressor then in conjunction with compressor Qloss, multiple temperature detecting points mixture enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time The efficiency of air conditioner is accurately detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, is reached To the purpose for saving and improving refrigeration.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor1Generate gas returning port Refrigerant enthalpy h1 refrigerantSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to described time Gas port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to the suction superheat Δ t1And room Interior heat exchanger middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, institute State the enthalpy h of saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h1 refrigerant.Further, air-breathing is generated according to below equation At a temperature of saturation refrigerant enthalpy hAir-breathing saturation：hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For refrigerant correspondence Saturation region coefficient.
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to below equationAir-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to below equation1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Further, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7The indoor heat exchange of generation The refrigerant enthalpy h of device first end7 refrigerantsSpecifically include：According to the indoor heat exchanger first end temperature t7With the indoor heat exchange Device middle portion temperature t6Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate room The modifying factor D of interior heat exchanger first end refrigerant enthalpy7；According to the amendment of the indoor heat exchanger first end refrigerant enthalpy Factor D7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7 refrigerants。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6 For the corresponding overheated zone coefficient of refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2And interior Environment temperature t9Generate the refrigerant enthalpy h of the exhaust outlet2 refrigerantsSpecifically include：According to the indoor environment temperature t9, it is described Outdoor heat exchanger first end temperature t4Generate outdoor heat exchanger middle portion temperature t3；According to the exhaust outlet of exhaust outlet in the compressor Temperature t2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to the discharge superheat Δ t2And institute State outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2：In the middle part of the outdoor heat exchanger Temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the modifying factor of the exhaust outlet refrigerant enthalpy D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3, wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Further, the outdoor heat exchanger middle portion temperature t is generated by below equation3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation Value h4 refrigerants：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
According to one embodiment of present invention, the refrigerating capacity of air conditioner is generated according to below equation：Wherein, QRefrigerating capacityFor the Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation hI lubricating oil, wherein, i is positive integer,
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i, wherein, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each temperature detecting point is calculated according to below equationi, Wherein, i is positive integer,
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104, wherein, CgFor mixture oil content, f is the running frequency of the compressor.
According to one embodiment of present invention, the housing heat dissipation capacity Q of compressor is generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8), wherein, ACompressorFor the surface area of compressor housing, t8For the temperature at outdoor heat exchanger fin.
To reach above-mentioned purpose, a kind of air conditioner that second aspect of the present invention embodiment is proposed includes memory, processor And it is stored in the computer program that can be run on the memory and on the processor, calculating described in the computing device During machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment is proposed are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately can be detected to efficiency.
To reach above-mentioned purpose, a kind of non-transitory computer-readable storage medium that third aspect present invention embodiment is proposed Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor The efficiency computational methods of the air conditioner of proposition.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by performing its computer journey stored Sequence, can real-time and accurately detect the efficiency of air conditioner, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reaches energy-conservation and improves the purpose of refrigeration.
To reach above-mentioned purpose, the efficiency computational methods bag for another air conditioner that fourth aspect present invention embodiment is proposed Include following steps：Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；Obtain the housing of compressor Heat dissipation capacity Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2、 The second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5, indoor heat exchanger first end indoor heat exchanger first end temperature Spend t7With indoor environment temperature t9；When the current working of the air conditioner is heating condition, according to gas returning port in the compressor Gas returning port temperature t1With the indoor environment temperature t9Generate the refrigerant enthalpy h of gas returning port1 refrigerant, according in the compressor The gas returning port temperature t of gas returning port1Generate the lubricating oil enthalpy h of gas returning port1 lubricating oil, according to the exhaust outlet of exhaust outlet in the compressor Temperature t2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the end of indoor heat exchanger second The second end of indoor heat exchanger temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith According to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate the refrigerant of indoor heat exchanger first end Enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilIt is raw Into the mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGeneration row The mixture enthalpy h of gas port2, according to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oil Generate the mixture enthalpy h at the end of indoor heat exchanger second5With the refrigerant enthalpy h according to the indoor heat exchanger first end7 refrigerants With lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；According to the power of the compressor, described The housing heat dissipation capacity Q of compressorloss, the gas returning port mixture enthalpy h1, exhaust outlet mixture enthalpy h2, indoor heat exchange The mixture enthalpy h at the end of device second5With the mixture enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner；And The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity Q of the power of machine, air conditioner power consumption and compressorloss, and obtain gas returning port in compressor, exhaust outlet, The end of indoor heat exchanger second, the temperature of indoor heat exchanger first end and indoor environment temperature, and air conditioner be in heat work The refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points are generated during condition according to the temperature of each above-mentioned temperature detecting point, and The mixture enthalpy of multiple temperature detecting points is further generated, the housing heat dissipation capacity of power, compressor then in conjunction with compressor Qloss, multiple temperature detecting points mixture enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time The efficiency of air conditioner is accurately detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, is reached To the purpose for saving and improving heating effect.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1And interior Environment temperature t9Generate the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：According to the indoor environment temperature t9, the outdoor Heat exchanger first end temperature t4Generate outdoor heat exchanger middle portion temperature t3；According to the gas returning port temperature t1With the outdoor heat exchange Device middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the outdoor heat exchanger middle portion temperature t3Generate under suction temperature The enthalpy h of saturation refrigerantAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, saturation under the suction temperature The enthalpy h of refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1 refrigerant。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
Wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
Further, the outdoor heat exchanger middle portion temperature t is generated by below equation3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For The corresponding overheated zone coefficient of refrigerant.
Further, the exhaust port temperatures t according to exhaust outlet in the compressor2Generate the refrigeration of the exhaust outlet Agent enthalpy h2 refrigerantsSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to the indoor heat exchange Indoor heat exchanger middle portion temperature t in the middle part of device6With the exhaust port temperatures t of exhaust outlet in the compressor2Generate discharge superheat Δ t2；According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate saturation refrigerant under delivery temperature Enthalpy hIt is vented saturation；According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Further, the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generation is described The refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：According to the indoor heat exchanger in the middle part of the indoor heat exchanger Middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With it is described Indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；Changed according to the interior The modifying factor D of hot device first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGeneration is described The refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6 For the corresponding overheated zone coefficient of refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation Value h5 refrigerants：
h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor compressor horsepower.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation hI lubricating oil, wherein, i is positive integer,
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i, wherein, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each temperature detecting point is calculated according to below equationi, Wherein, i is positive integer,
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104, wherein, CgFor mixture oil content, f is the running frequency of the compressor.
According to one embodiment of present invention, the housing heat dissipation capacity Q of compressor is generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8), wherein, ACompressorFor the surface area of compressor housing, t8For the temperature at outdoor heat exchanger fin.
To reach above-mentioned purpose, another air conditioner that fifth aspect present invention embodiment is proposed includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, is counted described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that fourth aspect present invention embodiment is proposed are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately can be detected to efficiency.
To reach above-mentioned purpose, the computer-readable storage of another non-transitory that sixth aspect present invention embodiment is proposed Medium, is stored thereon with computer program, and the computer program realizes that fourth aspect present invention is implemented when being executed by processor The efficiency computational methods for the air conditioner that example is proposed.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by performing its computer journey stored Sequence, can real-time and accurately detect the efficiency of air conditioner, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reaches energy-conservation and improves the purpose of heating effect.
Brief description of the drawings
Fig. 1 is the flow chart of the efficiency computational methods of the air conditioner according to the embodiment of the present invention；
Fig. 2 is the structural representation of the air conditioner according to one embodiment of the invention；
Fig. 3 is the block diagram of the efficiency computing system of the air conditioner according to the embodiment of the present invention；
Fig. 4 is the flow chart of the efficiency computational methods of another air conditioner according to the embodiment of the present invention；
Fig. 5 is the block diagram of the efficiency computing system of another air conditioner according to the embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and be not considered as limiting the invention.
The air conditioner and its efficiency computational methods of the embodiment of the present invention described below in conjunction with the accompanying drawings.
Fig. 1 is the flow chart of the efficiency computational methods of the air conditioner according to the embodiment of the present invention.
As shown in figure 1, the efficiency computational methods of the air conditioner of the embodiment of the present invention, comprise the following steps：
S101, obtains current working, the power of compressor and the air conditioner power consumption of air conditioner.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionerCompressorAnd air-conditioning Device power consumption PPower consumption。
S102, obtains the housing heat dissipation capacity Q of compressorloss。
S103, obtains the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room The outdoor heat exchanger first end temperature t of external heat exchanger first end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7With indoor environment temperature t9。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor, four-way valve, outdoor heat exchanger, restricting element and indoor heat exchanger.
In one embodiment of the invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss, The housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin Outer temperature sensor detection is obtained.
In one embodiment of the invention, can be by setting temperature sensor to detect respectively in corresponding temperature test point The temperature of the temperature detecting point.Specifically, as shown in Fig. 2 can be by setting gas returning port temperature to pass at gas returning port within the compressor Sensor is to detect gas returning port temperature t1, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t2, at outdoor heat exchanger first end outdoor heat exchanger first end temperature sensor is set to detect outdoor heat exchanger first end temperature Spend t4, indoors set indoor heat exchanger first end temperature sensor at heat exchanger first end to detect indoor heat exchanger first end Temperature t7And at heat exchanger fin indoor temperature transmitter is set to detect indoor environment temperature t indoors9。
Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially sets the position of temperature sensor to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
S104, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1 Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in compressor2 With indoor environment temperature t9Generate the refrigerant enthalpy h of exhaust outlet2 refrigerants, according to the exhaust port temperatures t of exhaust outlet in compressor2It is raw Into the lubricating oil enthalpy h of exhaust outlet2 lubricating oil, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4Generation is outdoor The refrigerant enthalpy h of heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilWith the indoor heat exchange according to indoor heat exchanger first end Device first end temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil。
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
Because the refrigerant of different temperatures test point is different with the state of the mixture of lubricating oil, therefore different temperatures is detected The refrigerant enthalpy and lubricating oil enthalpy of point are different.In one embodiment of the invention, rule of thumb formula it can calculate To refrigerant enthalpy and lubricating oil enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、 The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end refrigerant enthalpy h4 refrigerantsAnd profit Lubricating oil enthalpy h4 lubricating oil, indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilDetailed process.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the gas returning port of contracting machine, can combine the refrigerant enthalpy h that suction superheat calculates gas returning port1 refrigerant。
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger can be obtained6, wherein, as shown in Fig. 2 indoor Indoor heat exchanger middle portion temperature t in the middle part of heat exchanger6Can be warm by the indoor heat exchanger middle part set in the middle part of heat exchanger indoors Degree sensor detection is obtained.
Then can be according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1, and according to Suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1, and according to Indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Wherein, suction superheat Δ t1For Gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t1=t1-t6.The modifying factor of gas returning port refrigerant enthalpy D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For system The corresponding overheated zone coefficient of cryogen.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, its In, a1-a5For the corresponding saturation region coefficient of refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1 refrigerant, h1 refrigerant =D1·hAir-breathing saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is refrigeration During operating mode, the refrigerant superheat of indoor heat exchanger first end can combine position refrigerant superheat degree and calculate indoor heat exchanger the The refrigerant enthalpy h of one end7 refrigerants。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generated Temperature Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigeration The modifying factor D of agent enthalpy7, and the indoor heat exchanger first end refrigerant enthalpy according to generation modifying factor D7With The enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7 refrigerants.Wherein, Δ t7=t7-t6,h7 refrigerants=D7·hAir-breathing saturation+d7, Wherein, d1-d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet2 refrigerants。
Specifically, can be according to indoor environment temperature t9, outdoor heat exchanger first end temperature t4Generate temperature in the middle part of outdoor heat exchanger Spend t3.In one embodiment of the invention, outdoor heat exchanger middle portion temperature t can be generated by below equation3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient, and each fitting coefficient can Obtained by testing.
Then, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3Generation exhaust Degree of superheat Δ t2, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generate repairing for exhaust outlet refrigerant enthalpy Positive divisor D2, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation.Wherein, Discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t2 =t2-t3.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5 (Δt2)t2 3+d6(Δt2)2t2 3, wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.Saturation refrigerant under delivery temperature Enthalpy hIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGeneration The refrigerant enthalpy h of exhaust outlet2 refrigerants, h2 refrigerants=D2·hIt is vented saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants, when the current working of air conditioner is cooling condition, The refrigerant supercooling of outdoor heat exchanger first end, can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants：Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
The species of the corresponding saturation region coefficient of above-mentioned refrigerant, overheated zone coefficient and supercooling fauna number and refrigerant has Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and cold-zone is crossed Coefficient：
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate the inspection of each temperature The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is cooling condition Adjust low pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be in air conditioner high-pressure, exhaust port temperatures t2, room External heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy of outdoor heat exchanger first end h4。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, can be calculated according to below equation：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy for obtaining out gas returning port can be calculated Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end lubricating oil enthalpy h4 lubricating oilAnd indoor heat exchanger The lubricating oil enthalpy h of first end7 lubricating oil。
S105, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port Value h1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to The refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixture of outdoor heat exchanger first end Enthalpy h4With the refrigerant enthalpy h according to indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate indoor heat exchanger the The mixture enthalpy h of one end7。
Specifically, the mixture enthalpy h of each temperature detecting point can be calculated according to below equationi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, it can calculate and obtain out the mixed of gas returning port Compound enthalpy h1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger first end mixture enthalpy h4With indoor heat exchanger first The mixture enthalpy h at end7。
S106, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port mixture enthalpy h1, exhaust The mixture enthalpy h of mouth2, outdoor heat exchanger first end mixture enthalpy h4With the mixture enthalpy of indoor heat exchanger first end h7Generate the refrigerating capacity of air conditioner.
Specifically, the refrigerating capacity of air conditioner can be generated according to below equation：Wherein, QRefrigerating capacityFor Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
S107, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Because the current working of air conditioner is cooling condition, thus it can be generated according to air conditioner power consumption and refrigerating capacity empty The refrigeration efficiency of device is adjusted, specifically, the refrigeration efficiency of air conditioner is the ratio between refrigerating capacity and power consumption of air conditioner, i.e. EER= QRefrigerating capacity/PPower consumption。
, can also be according to the operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to can not only save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet, outdoor Heat exchanger first end, the temperature of indoor heat exchanger first end and indoor environment temperature, and when air conditioner is in cooling condition The refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points are generated according to the temperature of each above-mentioned temperature detecting point, one is gone forward side by side The mixture enthalpy of the multiple temperature detecting points of step generation, it is the housing heat dissipation capacity of power, compressor then in conjunction with compressor, multiple The mixture enthalpy and air conditioner power consumption of temperature detecting point obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately examine Measure the efficiency of air conditioner, consequently facilitating according to the real-time energy efficiency of air conditioner optimize air conditioner running status, reach energy-conservation and Improve the purpose of refrigeration.
Correspondence above-described embodiment, the present invention also proposes a kind of air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and store on a memory and can be on a processor The computer program of operation, during computing device computer program, can be achieved the air conditioner that the above embodiment of the present invention is proposed Efficiency computational methods.
Air conditioner according to embodiments of the present invention, real-time and accurately can be detected to efficiency.
Correspondence above-described embodiment, the present invention also proposes a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for the air conditioner that the above embodiment of the present invention is proposed can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by performing its computer journey stored Sequence, can real-time and accurately detect the efficiency of air conditioner, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reaches energy-conservation and improves the purpose of refrigeration.
Correspondence above-described embodiment, the present invention also proposes a kind of efficiency computing system of air conditioner.
As shown in figure 3, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port temperature sensor 01, Exhaust port temperatures sensor 02, outdoor heat exchanger first end temperature sensor 04, indoor heat exchanger first end temperature sensor 07, Indoor temperature transmitter 09 and acquisition module 10, mixture enthalpy generation module 20, refrigerating capacity generation module 30, efficiency generation Module 40.
Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1；Exhaust outlet temperature Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Outdoor heat exchanger first end temperature sensor 04 is used In the outdoor heat exchanger first end temperature t for obtaining outdoor heat exchanger first end4；Indoor heat exchanger first end temperature sensor 07 is used In the indoor heat exchanger first end temperature t for obtaining indoor heat exchanger first end7；Indoor temperature transmitter 09 is used to obtain indoor ring Border temperature t9。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element 400 and indoor heat exchanger 500.
As shown in Fig. 2 at the settable gas returning port within the compressor of gas returning port temperature sensor 01, exhaust port temperatures sensor 02 settable exhaust ports within the compressor, outdoor heat exchanger first end temperature sensor 04 may be provided at outdoor heat exchanger first Indoor heat exchanger first end can be set in end, indoor heat exchanger first end temperature sensor 07, and indoor temperature transmitter 09 can be set Indoors at heat exchanger fin.Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, And to refrigerant tube wall, especially set the position of temperature sensor to take Insulation.For example, temperature sensor can be close to Copper pipe is set, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability of temperature detection and accurate Property.
Acquisition module 10 is used for current working, the power of compressor, air conditioner power consumption and the pressure for obtaining air conditioner The housing heat dissipation capacity Q of contracting machineloss；Mixture enthalpy generation module 20 is used for when the current working of air conditioner is cooling condition, According to the gas returning port temperature t of gas returning port in compressor1Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, According to the exhaust port temperatures t of exhaust outlet in compressor2With indoor environment temperature t9Generate the refrigerant enthalpy h of exhaust outlet2 refrigerants, root According to the exhaust port temperatures t of exhaust outlet in compressor2Generate the lubricating oil enthalpy h of exhaust outlet2 lubricating oil, according to outdoor heat exchanger first end Outdoor heat exchanger first end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oil With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end Value h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, and according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGeneration The mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate exhaust outlet Mixture enthalpy h2, according to the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGeneration outdoor is changed The mixture enthalpy h of hot device first end4With the refrigerant enthalpy h according to indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；Refrigerating capacity generation module 30 be used for according to the power of compressor, The housing heat dissipation capacity Q of compressorloss, gas returning port mixture enthalpy h1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger The mixture enthalpy h of one end4With the mixture enthalpy h of indoor heat exchanger first end7Generate the refrigerating capacity of air conditioner；Efficiency is generated Module 40 is used for the efficiency that air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Wherein, acquisition module 10, mixture enthalpy generation module 20, refrigerating capacity generation module 30 and efficiency generation module 40 In the electric-control system that may be disposed at air conditioner.Acquisition module 10 can monitor the current working of air conditioner, the power of compressor in real time PCompressorWith air conditioner power consumption PPower consumption.In one embodiment of the invention, acquisition module 10 can pass through convection current, radiation formula Calculate the housing heat dissipation capacity Q of compressorloss, the housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin The outer detection of temperature sensor 08 is obtained.
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
Because the refrigerant of different temperatures test point is different with the state of the mixture of lubricating oil, therefore different temperatures is detected The refrigerant enthalpy and lubricating oil enthalpy of point are different.In one embodiment of the invention, mixture enthalpy generation module 20 Rule of thumb formula calculating it can obtain refrigerant enthalpy value and lubricating oil enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy of gas returning port to mixture enthalpy generation module 20 separately below h1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, exhaust outlet refrigerant enthalpy h2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first The refrigerant enthalpy h at end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oil, indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsAnd lubricating oil Enthalpy h7 lubricating oilDetailed process.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the gas returning port of contracting machine, mixture enthalpy generation module 20 can combine the refrigeration that suction superheat calculates gas returning port Agent enthalpy h1 refrigerant。
Specifically, the indoor heat exchanger in the middle part of indoor heat exchanger can be obtained by indoor heat exchanger middle portion temperature sensor 06 Middle portion temperature t6, wherein, as shown in Fig. 2 indoor heat exchanger middle portion temperature sensor 06 may be provided in the middle part of indoor heat exchanger.
Then mixture enthalpy generation module 20 can be according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generation is inhaled Gas degree of superheat Δ t1, and according to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate gas returning port refrigerant enthalpy Modifying factor D1, and according to indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Its In, suction superheat Δ t1 is gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t1=t1-t6.Gas returning port The modifying factor D of refrigerant enthalpy1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δ t1)2t2 6, wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+ a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, mixture enthalpy Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration Refrigerant enthalpy h1 refrigerant, h1 refrigerant=D1·hAir-breathing saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is refrigeration During operating mode, the refrigerant superheat of indoor heat exchanger first end, mixture enthalpy generation module 20 can combine the position refrigerant mistake Temperature calculates the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants。
Specifically, mixture enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7In indoor heat exchanger Portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger The modifying factor D of first end refrigerant enthalpy7, and the indoor heat exchanger first end refrigerant enthalpy according to generation amendment Factor D7With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7 refrigerants.Wherein, Δ t7=t7-t6,h7 refrigerants=D7·hAir-breathing saturation+d7, Wherein, d1-d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, mixture enthalpy generation module 20 can combine the refrigeration that discharge superheat calculates exhaust outlet Agent enthalpy h2 refrigerants。
Specifically, mixture enthalpy generation module 20 can be according to indoor environment temperature t9, outdoor heat exchanger first end temperature t4 Generate outdoor heat exchanger middle portion temperature t3.In one embodiment of the invention, mixture enthalpy generation module 20 can by with Lower formula generation outdoor heat exchanger middle portion temperature t3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient, and each fitting coefficient can Obtained by testing.
Then, mixture enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2And outdoor heat exchange Device middle portion temperature t3Generate discharge superheat Δ t2, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generation The modifying factor D of exhaust outlet refrigerant enthalpy2, and according to outdoor heat exchanger middle portion temperature t3Generate saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturation.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2And outdoor heat exchanger Middle portion temperature t3Difference, i.e. Δ t2=t2-t3.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δt2)2+d3 (Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3, wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.Row The enthalpy h of saturation refrigerant at a temperature of gasIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5It is corresponding full for refrigerant With fauna number.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Mixture enthalpy generation module 20 can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants, h2 refrigerants=D2·hIt is vented saturation+d7, wherein, d7For refrigerant Corresponding overheated zone coefficient.
For the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants, when the current working of air conditioner is cooling condition, The refrigerant supercooling of outdoor heat exchanger first end, mixture enthalpy generation module 20 can directly calculate outdoor heat exchanger first end Refrigerant enthalpy h4 refrigerants：Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
The species of the corresponding saturation region coefficient of above-mentioned refrigerant, overheated zone coefficient and supercooling fauna number and refrigerant has Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and cold-zone is crossed Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.
In other embodiments of the invention, mixture enthalpy generation module 20 can also directly invoke the calculating knot of software Really, or by other approach the refrigerant enthalpy of each temperature detecting point is obtained.For example, when the current working of air conditioner is During cooling condition, low pressure that mixture enthalpy generation module 20 can also be in air conditioner, gas returning port temperature t1, interior changes Hot device first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With the refrigerant enthalpy h of indoor heat exchanger first end7, And can be in air conditioner high-pressure, exhaust port temperatures t2, outdoor heat exchanger first end temperature t4Respectively obtain exhaust outlet Refrigerant enthalpy h2With the refrigerant enthalpy h of outdoor heat exchanger first end4。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, mixture enthalpy generation module 20 can be according to following public affairs Formula is calculated and obtained：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy for obtaining out gas returning port can be calculated Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end lubricating oil enthalpy h4 lubricating oilAnd indoor heat exchanger The lubricating oil enthalpy h of first end7 lubricating oil。
Further, mixture enthalpy generation module 20 can calculate the mixture of each temperature detecting point according to below equation Enthalpy hi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, it can calculate and obtain out the mixed of gas returning port Compound enthalpy h1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger first end mixture enthalpy h4With indoor heat exchanger first The mixture enthalpy h at end7。
In an embodiment of the present invention, refrigerating capacity generation module 30 can generate the refrigerating capacity of air conditioner according to below equation：Wherein, QRefrigerating capacityFor Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
Because the current working of air conditioner is cooling condition, thus efficiency generation module 40 can be according to air conditioner power consumption The refrigeration efficiency of air conditioner is generated with refrigerating capacity, specifically, the refrigeration efficiency of air conditioner is the refrigerating capacity and power consumption work(of air conditioner The ratio between rate, i.e. EER=QRefrigerating capacity/PPower consumption。
, can also be according to the operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to can not only save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor, the housing heat dissipation capacity of air conditioner power consumption and compressor, and obtained by corresponding temperature sensor Gas returning port, exhaust outlet, outdoor heat exchanger first end, the temperature of indoor heat exchanger first end and indoor environment temperature in compressor, And pass through mixture enthalpy generation module, refrigerating capacity generation module and efficiency generation module when air conditioner is in cooling condition The refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points are generated according to the temperature of each above-mentioned temperature detecting point, one is gone forward side by side The mixture enthalpy of the multiple temperature detecting points of step generation, it is the housing heat dissipation capacity of power, compressor then in conjunction with compressor, multiple The mixture enthalpy and air conditioner power consumption of temperature detecting point obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately examine Measure the efficiency of air conditioner, consequently facilitating according to the real-time energy efficiency of air conditioner optimize air conditioner running status, reach energy-conservation and Improve the purpose of refrigeration.
The air conditioner and its efficiency computational methods and system of above-described embodiment can detect the refrigeration efficiency of air conditioner, for inspection The heat efficiency of air conditioner is surveyed, the present invention also proposes the efficiency computational methods of another air conditioner.
As shown in figure 4, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：
S401, obtains current working, the power of compressor and the air conditioner power consumption of air conditioner.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionerCompressorAnd air-conditioning Device power consumption PPower consumption。
S402, obtains the housing heat dissipation capacity Q of compressorloss。
S403, obtains the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room The second end of indoor heat exchanger temperature t at the interior end of heat exchanger second5, indoor heat exchanger first end indoor heat exchanger first end temperature t7With indoor environment temperature t9。
In one embodiment of the invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss, The housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin Outer temperature sensor detection is obtained.
As shown in Fig. 2 gas returning port temperature can be detected by setting gas returning port temperature sensor at gas returning port within the compressor Spend t1, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t2, heat exchanger second indoors Indoor heat exchanger the second end temperature sensor is set to detect the second end of indoor heat exchanger temperature t at end5, heat exchanger indoors End sets indoor heat exchanger first end temperature sensor to detect indoor heat exchanger first end temperature t7And change indoors Indoor temperature transmitter is set to detect indoor environment temperature t at hot device fin9。
Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially sets the position of temperature sensor to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
S404, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1 With indoor environment temperature t9Generate the refrigerant enthalpy h of gas returning port1 refrigerant, according to the gas returning port temperature t of gas returning port in compressor1It is raw Into the lubricating oil enthalpy h of gas returning port1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant enthalpy of exhaust outlet Value h2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generation is indoor The refrigerant enthalpy h at the end of heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith the indoor heat exchange according to indoor heat exchanger first end Device first end temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
Because the refrigerant of different temperatures test point is different with the state of the mixture of lubricating oil, therefore different temperatures is detected The refrigerant enthalpy and lubricating oil enthalpy of point are different.In one embodiment of the invention, rule of thumb formula it can calculate To refrigerant enthalpy and lubricating oil enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、 The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second refrigerant enthalpy h5 refrigerantsAnd profit Lubricating oil enthalpy h5 lubricating oilWith the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilDetailed process.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the gas returning port of contracting machine, can combine the refrigerant enthalpy h that suction superheat calculates gas returning port1 refrigerant。
Specifically, can be according to indoor environment temperature t9, outdoor heat exchanger first end temperature t4Generate temperature in the middle part of outdoor heat exchanger Spend t3.In one embodiment of the invention, outdoor heat exchanger middle portion temperature t can be generated by below equation3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient, and each fitting coefficient can Obtained by testing.
Then can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1, and according to Suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1, and according to Outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Wherein, suction superheat Δ t1For Gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.The modifying factor of gas returning port refrigerant enthalpyWherein, d1-d6For refrigerant pair The overheated zone coefficient answered.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5 For the corresponding saturation region coefficient of refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1 refrigerant, h1 refrigerant =D1·hAir-breathing saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet2 refrigerants。
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger can be obtained6, wherein, as shown in Fig. 2 indoor Indoor heat exchanger middle portion temperature t in the middle part of heat exchanger6Can be warm by the indoor heat exchanger middle part set in the middle part of heat exchanger indoors Degree sensor detection is obtained.
Then, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Generation exhaust Degree of superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Generate saturation refrigerant under delivery temperature Enthalpy hIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigerant enthalpy Modifying factor D2.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With temperature in the middle part of indoor heat exchanger Spend t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5, its In, a1-a5For the corresponding saturation region coefficient of refrigerant.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δ t2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For the corresponding overheated zone of refrigerant Coefficient.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, can further repairing according to exhaust outlet refrigerant enthalpy Positive divisor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants, h2 refrigerants= D2·hIt is vented saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is to heat During operating mode, the refrigerant superheat of indoor heat exchanger first end can combine position refrigerant superheat degree and calculate indoor heat exchanger the The refrigerant enthalpy h of one end7 refrigerants。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generation overheat Spend Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7, and the indoor heat exchanger first end refrigerant enthalpy according to generation modifying factor D7With saturation system The enthalpy h of cryogenIt is vented saturationGenerate refrigerant enthalpy h7 refrigerants.Wherein, Δ t7=t7-t6,h7 refrigerants=D7·hIt is vented saturation+ d7, wherein, wherein, d1-d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, when the current working of air conditioner is heating condition, The refrigerant supercooling at the end of indoor heat exchanger second, can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants：h5 refrigerants =c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
The species of the corresponding saturation region coefficient of above-mentioned refrigerant, overheated zone coefficient and supercooling fauna number and refrigerant has Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and cold-zone is crossed Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is heating condition Adjust high-pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be in air conditioner high-pressure, exhaust port temperatures t2, room Interior the second end of heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy at the end of indoor heat exchanger second h5。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, can be calculated according to below equation：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy for obtaining out gas returning port can be calculated Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second lubricating oil enthalpy h5 lubricating oilAnd indoor heat exchanger The lubricating oil enthalpy h of first end7 lubricating oil。
S405, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port Value h1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixture at the end of indoor heat exchanger second Enthalpy h5With the refrigerant enthalpy h according to indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate indoor heat exchanger the The mixture enthalpy h of one end7。
Specifically, the mixture enthalpy h of each temperature detecting point can be calculated according to below equationi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, it can calculate and obtain out the mixed of gas returning port Compound enthalpy h1, exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second mixture enthalpy h5With indoor heat exchanger first The mixture enthalpy h at end7。
S406, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port mixture enthalpy h1, exhaust The mixture enthalpy h of mouth2, the end of indoor heat exchanger second mixture enthalpy h5With the mixture enthalpy of indoor heat exchanger first end h7Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to below equation：Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor compressor horsepower.
S407, the efficiency of air conditioner is generated according to air conditioner power consumption and heating capacity.
Because the current working of air conditioner is heating condition, thus it can be generated according to air conditioner power consumption and heating capacity empty The heat efficiency of device is adjusted, specifically, the heat efficiency of air conditioner is the ratio between heating capacity and power consumption of air conditioner, i.e. COP= QHeating capacity/PPower consumption。
, can also be according to the operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to can not only save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet, interior The end of heat exchanger second, the temperature of indoor heat exchanger first end and indoor environment temperature, and when air conditioner is in heating condition The refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points are generated according to the temperature of each above-mentioned temperature detecting point, one is gone forward side by side The mixture enthalpy of the multiple temperature detecting points of step generation, it is the housing heat dissipation capacity of power, compressor then in conjunction with compressor, multiple The mixture enthalpy and air conditioner power consumption of temperature detecting point obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately examine Measure the efficiency of air conditioner, consequently facilitating according to the real-time energy efficiency of air conditioner optimize air conditioner running status, reach energy-conservation and Improve the purpose of heating effect.
Correspondence above-described embodiment, the present invention also proposes another air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and store on a memory and can be on a processor The computer program of operation, during computing device computer program, can be achieved another sky that the above embodiment of the present invention is proposed Adjust the efficiency computational methods of device.
Air conditioner according to embodiments of the present invention, real-time and accurately can be detected to efficiency.
Correspondence above-described embodiment, the present invention also proposes a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for another air conditioner that the above embodiment of the present invention is proposed can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by performing its computer journey stored Sequence, can real-time and accurately detect the efficiency of air conditioner, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reaches energy-conservation and improves the purpose of heating effect.
Correspondence above-described embodiment, the present invention also proposes the efficiency computing system of another air conditioner.
As shown in figure 5, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port temperature sensor 01, Exhaust port temperatures sensor 02, the second end of indoor heat exchanger temperature sensor 05, indoor heat exchanger first end temperature sensor 07, Indoor temperature transmitter 09 and acquisition module 10, mixture enthalpy generation module 20, heating capacity generation module 50, efficiency generation Module 40.
Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1；Exhaust outlet temperature Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；The second end of indoor heat exchanger temperature sensor 05 is used In the second end of the indoor heat exchanger temperature t for obtaining the end of indoor heat exchanger second5；Indoor heat exchanger first end temperature sensor 07 is used In the indoor heat exchanger first end temperature t for obtaining indoor heat exchanger first end7；Indoor temperature transmitter 09 is used to obtain indoor ring Border temperature t9。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element 400 and indoor heat exchanger 500.
As shown in Fig. 2 at the settable gas returning port within the compressor of gas returning port temperature sensor 01, exhaust port temperatures sensor 02 settable exhaust ports within the compressor, the second end of indoor heat exchanger temperature sensor 05 may be provided at indoor heat exchanger second Indoor heat exchanger first end can be set in end, indoor heat exchanger first end temperature sensor 07, and indoor temperature transmitter 09 can be set Indoors at heat exchanger fin.Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, And to refrigerant tube wall, especially set the position of temperature sensor to take Insulation.For example, temperature sensor can be close to Copper pipe is set, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability of temperature detection and accurate Property.
Acquisition module 10 is used for current working, the power of compressor, air conditioner power consumption and the pressure for obtaining air conditioner The housing heat dissipation capacity Q of contracting machineloss；Mixture enthalpy generation module 20 is used for when the current working of air conditioner is heating condition, According to the gas returning port temperature t of gas returning port in compressor1With indoor environment temperature t9Generate the refrigerant enthalpy h of gas returning port1 refrigerant, root According to the gas returning port temperature t of gas returning port in compressor1Generate the lubricating oil enthalpy h of gas returning port1 lubricating oil, according to exhaust outlet in compressor Exhaust port temperatures t2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the end of indoor heat exchanger second The second end of indoor heat exchanger temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oil With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end Value h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, and according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGeneration The mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate exhaust outlet Mixture enthalpy h2, according to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGeneration interior is changed The mixture enthalpy h at the hot end of device second5With the refrigerant enthalpy h according to indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；Heating capacity generation module 50 be used for according to the power of compressor, The housing heat dissipation capacity Q of compressorloss, gas returning port mixture enthalpy h1, exhaust outlet mixture enthalpy h2, indoor heat exchanger The mixture enthalpy h at two ends5With the mixture enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner；Efficiency is generated Module 40 is used for the efficiency that air conditioner is generated according to air conditioner power consumption and heating capacity.
Wherein, acquisition module 10, mixture enthalpy generation module 20, heating capacity generation module 50 and efficiency generation module 40 In the electric-control system that may be disposed at air conditioner.Acquisition module 10 can monitor the current working of air conditioner, the power of compressor in real time PCompressorWith air conditioner power consumption PPower consumption.In one embodiment of the invention, acquisition module 10 can pass through convection current, radiation formula Calculate the housing heat dissipation capacity Q of compressorloss, the housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin The outer detection of temperature sensor 08 is obtained.
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
Because the refrigerant of different temperatures test point is different with the state of the mixture of lubricating oil, therefore different temperatures is detected The refrigerant enthalpy and lubricating oil enthalpy of point are different.In one embodiment of the invention, mixture enthalpy generation module 20 Rule of thumb formula calculating it can obtain refrigerant enthalpy value and lubricating oil enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy of gas returning port to mixture enthalpy generation module 20 separately below h1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, exhaust outlet refrigerant enthalpy h2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, indoor heat exchanger second The refrigerant enthalpy h at end5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsAnd lubrication Oily enthalpy h7 lubricating oilDetailed process.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the gas returning port of contracting machine, mixture enthalpy generation module 20 can combine the refrigeration that suction superheat calculates gas returning port Agent enthalpy h1 refrigerant。
Specifically, mixture enthalpy generation module 20 can be according to indoor environment temperature t9, outdoor heat exchanger first end temperature t4 Generate outdoor heat exchanger middle portion temperature t3.In one embodiment of the invention, refrigerant enthalpy generation module 20 can by with Lower formula generation outdoor heat exchanger middle portion temperature t3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient, and each fitting coefficient can Obtained by testing.
Then mixture enthalpy generation module 20 can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generation is inhaled Gas degree of superheat Δ t1, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate gas returning port refrigerant enthalpy Modifying factor D1, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Its In, suction superheat Δ t1For gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.Gas returning port The modifying factor of refrigerant enthalpy Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+ a3t2 3+a4t3 3+a5, wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, mixture enthalpy Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration Refrigerant enthalpy h1 refrigerant, h1 refrigerant=D1·hAir-breathing saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, mixture enthalpy generation module 20 can combine the refrigeration that discharge superheat calculates exhaust outlet Agent enthalpy h2 refrigerants。
Specifically, mixture enthalpy generation module 20 can obtain the indoor heat exchanger middle portion temperature in the middle part of indoor heat exchanger t6, wherein, as shown in Fig. 2 the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Can be by being set in the middle part of heat exchanger indoors The indoor heat exchanger middle portion temperature sensor detection put is obtained.
Then, mixture enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchange Device middle portion temperature t6Generate discharge superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Generation The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6It is raw Into the modifying factor D of exhaust outlet refrigerant enthalpy value2.Wherein, discharge superheat Δ t2For the exhaust port temperatures of exhaust outlet in compressor t2With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+ a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.The modifying factor of exhaust outlet refrigerant enthalpy D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For system The corresponding overheated zone coefficient of cryogen.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, mixture enthalpy generation module 20 can further basis The modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of exhaust outlet Agent enthalpy h2 refrigerants, h2 refrigerants=D2·hIt is vented saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is to heat During operating mode, the refrigerant superheat of indoor heat exchanger first end, mixture enthalpy generation module 20 can combine the position refrigerant mistake Temperature calculates the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants。
Specifically, mixture enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7In indoor heat exchanger Portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger The modifying factor D of first end refrigerant enthalpy7, and the indoor heat exchanger first end refrigerant enthalpy according to generation amendment Factor D7With the enthalpy h of saturation refrigerantIt is vented saturationGenerate refrigerant enthalpy h7 refrigerants.Wherein, Δ t7=t7-t6,h7 refrigerants=D7·hIt is vented saturation+d7, Wherein, wherein, d1-d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, when the current working of air conditioner is heating condition, The refrigerant supercooling at the end of indoor heat exchanger second, mixture enthalpy generation module 20 can directly calculate the end of indoor heat exchanger second Refrigerant enthalpy h5 refrigerants：h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
The species of the corresponding saturation region coefficient of above-mentioned refrigerant, overheated zone coefficient and supercooling fauna number and refrigerant has Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and cold-zone is crossed Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.
In other embodiments of the invention, mixture enthalpy generation module 20 can also directly invoke the calculating knot of software Really, or by other approach the refrigerant enthalpy of each temperature detecting point is obtained.For example, when the current working of air conditioner is During heating condition, high-pressure that mixture enthalpy generation module 20 can also be in air conditioner, gas returning port temperature t1, interior changes Hot device first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With the refrigerant enthalpy h of indoor heat exchanger first end7, And can be in air conditioner high-pressure, exhaust port temperatures t2, the second end of indoor heat exchanger temperature t5Respectively obtain exhaust outlet Refrigerant enthalpy h2With the refrigerant enthalpy h at the end of indoor heat exchanger second5。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, mixture enthalpy generation module 20 can be according to following public affairs Formula is calculated and obtained：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy for obtaining out gas returning port can be calculated Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second lubricating oil enthalpy h5 lubricating oilAnd indoor heat exchanger The lubricating oil enthalpy h of first end7 lubricating oil。
Further, mixture enthalpy generation module 20 can calculate the mixture of each temperature detecting point according to below equation Enthalpy hi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, it can calculate and obtain out the mixed of gas returning port Compound enthalpy h1, exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second mixture enthalpy h5With indoor heat exchanger first The mixture enthalpy h at end7。
In an embodiment of the present invention, heating capacity generation module 50 can generate the heating capacity of air conditioner according to below equation：Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor compressor horsepower.
Because the current working of air conditioner is heating condition, thus efficiency generation module 40 can be according to air conditioner power consumption The heat efficiency of air conditioner is generated with heating capacity, specifically, the heat efficiency of air conditioner is the heating capacity and power consumption work(of air conditioner The ratio between rate, i.e. COP=QHeating capacity/PPower consumption。
, can also be according to the operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to can not only save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor, the housing heat dissipation capacity of air conditioner power consumption and compressor, and obtained by corresponding temperature sensor Gas returning port, exhaust outlet, the end of indoor heat exchanger second, the temperature of indoor heat exchanger first end and indoor environment temperature in compressor, And pass through mixture enthalpy generation module, heating capacity generation module and efficiency generation module when air conditioner is in heating condition The refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points are generated according to the temperature of each above-mentioned temperature detecting point, one is gone forward side by side The mixture enthalpy of the multiple temperature detecting points of step generation, it is the housing heat dissipation capacity of power, compressor then in conjunction with compressor, multiple The refrigerant enthalpy and air conditioner power consumption of temperature detecting point obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately examine Measure the efficiency of air conditioner, consequently facilitating according to the real-time energy efficiency of air conditioner optimize air conditioner running status, reach energy-conservation and Improve the purpose of heating effect.
In summary, the air conditioner of the embodiment of the present invention and its efficiency computational methods and system, by obtaining air conditioner system The physical property of refrigerant and the physical property of lubricating oil in refrigerant cycle system, and combine the mixture of refrigerant and lubricating oil Physical property and the leakage enthusiasm condition of compressor calculate and obtain the power of air conditioner, and further calculate the energy for obtaining air conditioner Effect, so as to be able to real-time and accurately detect the refrigeration efficiency and heat efficiency of air conditioner.
In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom ", " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, is for only for ease of the description present invention and simplifies description, rather than indicate or imply that the device or element of meaning must There must be specific orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.
In addition, term " first ", " second " are only used for describing purpose, and it is not intended that indicating or implying relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or Implicitly include one or more this feature.In the description of the invention, " multiple " are meant that two or more, Unless otherwise specifically defined.
In the present invention, unless otherwise clearly defined and limited, term " installation ", " connected ", " connection ", " fixation " etc. Term should be interpreted broadly, for example, it may be fixedly connected or be detachably connected, or integrally；Can be that machinery connects Connect or electrically connect；Can be joined directly together, can also be indirectly connected to by intermediary, can be in two elements The connection in portion or the interaction relationship of two elements.For the ordinary skill in the art, can be according to specific feelings Condition understands the concrete meaning of above-mentioned term in the present invention.
In the present invention, unless otherwise clearly defined and limited, fisrt feature can be with "above" or "below" second feature It is that the first and second features are directly contacted, or the first and second features pass through intermediary mediate contact.Moreover, fisrt feature exists Second feature " on ", " top " and " above " but fisrt feature are directly over second feature or oblique upper, or be merely representative of Fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be One feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height less than second feature.
In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means to combine specific features, structure, material or the spy that the embodiment or example are described Point is contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not Identical embodiment or example must be directed to.Moreover, specific features, structure, material or the feature of description can be with office Combined in an appropriate manner in one or more embodiments or example.In addition, in the case of not conflicting, the skill of this area Art personnel can be tied the not be the same as Example or the feature of example and non-be the same as Example or example described in this specification Close and combine.
Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is example Property, it is impossible to limitation of the present invention is interpreted as, one of ordinary skill in the art within the scope of the invention can be to above-mentioned Embodiment is changed, changed, replacing and modification.

Claims (32)

1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, outdoor heat exchange The outdoor heat exchanger first end temperature t of device first end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7And room Interior environment temperature t9；
When the current working of the air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in the compressor1It is raw Into the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures of exhaust outlet in the compressor t2With the indoor environment temperature t9Generate the refrigerant enthalpy h of exhaust outlet2 refrigerants, according to the exhaust of exhaust outlet in the compressor Mouth temperature t2Generate the lubricating oil enthalpy h of exhaust outlet2 lubricating oil, according to the outdoor heat exchanger first end of the outdoor heat exchanger first end Temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilWith according to the indoor heat exchange The indoor heat exchanger first end temperature t of device first end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsAnd lubricating oil Enthalpy h7 lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, According to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to The refrigerant enthalpy h of the outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixed of outdoor heat exchanger first end Compound enthalpy h4With the refrigerant enthalpy h according to the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration is indoor The mixture enthalpy h of heat exchanger first end7；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port mixture enthalpy h1、 The mixture enthalpy h of the exhaust outlet2, the outdoor heat exchanger first end mixture enthalpy h4With the indoor heat exchanger The mixture enthalpy h of one end7Generate the refrigerating capacity of air conditioner；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to gas returning port in the compressor Gas returning port temperature t1Generate the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the indoor heat exchanger middle portion temperature t6Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationThe generation refrigeration Agent enthalpy h1 refrigerant。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that inhaled according to below equation generation is described The enthalpy h of saturation refrigerant at a temperature of gasAir-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
4. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that returned according to below equation generation The modifying factor D of gas port refrigerant enthalpy1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6,
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 3, it is characterised in that according to the indoor heat exchanger first The indoor heat exchanger first end temperature t at end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：
According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturation Generate the refrigerant enthalpy h7 refrigerants。
6. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that give birth to described into room according to below equation The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to exhaust outlet in the compressor Exhaust port temperatures t2With indoor environment temperature t9Generate the refrigerant enthalpy h of the exhaust outlet2 refrigerantsSpecifically include：
According to the indoor environment temperature t9, the outdoor heat exchanger first end temperature t4Generate outdoor heat exchanger middle portion temperature t3；
According to the exhaust port temperatures t of exhaust outlet in the compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Spend Δ t2；
According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2：
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
8. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3,
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
9. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the room is generated by below equation External heat exchanger middle portion temperature t3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to below equation generation The refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to below equation generation The refrigerating capacity of air conditioner：
Wherein, QRefrigerating capacityFor the refrigerating capacity of the air conditioner, PCompressorFor the work(of the compressor Rate.
12. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that each is calculated according to below equation The lubricating oil enthalpy h of temperature detecting pointI lubricating oil, wherein, i is positive integer,
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, tiFor the temperature of temperature detecting point.
13. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that each is calculated according to below equation The mixture enthalpy h of temperature detecting pointi, wherein, i is positive integer,
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of the compressor.
14. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that generated and compressed according to below equation The housing heat dissipation capacity Q of machineloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor ×(t2-t8), wherein, ACompressorFor the surface area of compressor housing, t8For the temperature at outdoor heat exchanger fin.
15. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, is realized as in claim 1-14 The efficiency computational methods of any described air conditioner.
16. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The efficiency computational methods of the air conditioner as described in any in claim 1-14 are realized when calculation machine program is executed by processor.
17. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, indoor heat exchange The second end of indoor heat exchanger temperature t at the end of device second5, indoor heat exchanger first end indoor heat exchanger first end temperature t7And room Interior environment temperature t9；
When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1With The indoor environment temperature t9Generate the refrigerant enthalpy h of gas returning port1 refrigerant, according to the gas returning port temperature of gas returning port in the compressor Spend t1Generate the lubricating oil enthalpy h of gas returning port1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate exhaust outlet Refrigerant enthalpy h2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the end of indoor heat exchanger second at the end of indoor heat exchanger second Temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith according to the indoor heat exchange The indoor heat exchanger first end temperature t of device first end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsAnd lubricating oil Enthalpy h7 lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, According to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixed of the end of indoor heat exchanger second Compound enthalpy h5With the refrigerant enthalpy h according to the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration is indoor The mixture enthalpy h of heat exchanger first end7；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port mixture enthalpy h1、 The mixture enthalpy h of exhaust outlet2, the end of indoor heat exchanger second mixture enthalpy h5With the mixture of indoor heat exchanger first end Enthalpy h7Generate the heating capacity of air conditioner；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
18. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that according to return-air in the compressor The gas returning port temperature t of mouth1With the indoor environment temperature t9Generate the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：
According to the indoor environment temperature t9, the outdoor heat exchanger first end temperature t4Generate outdoor heat exchanger middle portion temperature t3；
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationIt is raw Into the refrigerant enthalpy h of the gas returning port1 refrigerant。
19. the efficiency computational methods of air conditioner as claimed in claim 18, it is characterised in that according to below equation generation The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation：
Wherein, a1-a5For the corresponding saturation region coefficient of refrigerant.
20. the efficiency computational methods of air conditioner as claimed in claim 18, it is characterised in that generated by below equation described Outdoor heat exchanger middle portion temperature t3：
t3=a*t9+b*t4+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
21. the efficiency computational methods of air conditioner as claimed in claim 18, it is characterised in that according to below equation generation The modifying factor D of gas returning port refrigerant enthalpy1：
<mrow> <msub> <mi>D</mi> <mn>1</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
22. the efficiency computational methods of air conditioner as claimed in claim 18, it is characterised in that be vented according in the compressor The exhaust port temperatures t of mouth2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsSpecifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate the enthalpy of saturation refrigerant under delivery temperature hIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
23. the efficiency computational methods of the air conditioner described in claim 22, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6,
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
24. the efficiency computational methods of air conditioner as claimed in claim 22, it is characterised in that according to the indoor heat exchanger The indoor heat exchanger first end temperature t of one end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor heat exchanger first end temperature t7It is raw Into degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation refrigerant under the delivery temperature Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerants。
25. the efficiency computational methods of air conditioner as claimed in claim 24, it is characterised in that according to below equation generation The modifying factor D of indoor heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
26. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that according to being calculated below equation The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants：
h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
27. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that according to equation below generation The heating capacity of air conditioner：
Wherein, QHeating capacityFor the heating capacity of the air conditioner, PCompressorFor the compressor Power.
28. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that each is calculated according to below equation The lubricating oil enthalpy h of temperature detecting pointI lubricating oil, wherein, i is positive integer,
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, tiFor the temperature of temperature detecting point.
29. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that each is calculated according to below equation The mixture enthalpy h of temperature detecting pointi, wherein, i is positive integer,
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of the compressor.
30. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that generated and compressed according to below equation The housing heat dissipation capacity Q of machineloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor ×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, t8For the temperature at outdoor heat exchanger fin.
31. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, is realized as in claim 17-30 Any described method.
32. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 17-30 is realized when calculation machine program is executed by processor.
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0100210A2 (en) * 1982-07-26 1984-02-08 Honeywell Inc. Coefficient of performance measuring device
CN103032996A (en) * 2012-12-12 2013-04-10 宁波奥克斯电气有限公司 Parallel compressor selection and configuration method for preventing compressor from being frequently started up and shut down
CN105091439A (en) * 2014-05-07 2015-11-25 苏州必信空调有限公司 Computing method of refrigerating capacity and refrigerating efficiency of oil-free refrigerating system and refrigerating system
CN106524551A (en) * 2016-11-07 2017-03-22 清华大学 Mass and flow measuring method and device of refrigerant in refrigerating system and measuring instrument
CN106949680A (en) * 2016-01-07 2017-07-14 青岛海尔开利冷冻设备有限公司 A kind of refrigeration system compressor group coefficient of performance detection method and detecting system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0100210A2 (en) * 1982-07-26 1984-02-08 Honeywell Inc. Coefficient of performance measuring device
CN103032996A (en) * 2012-12-12 2013-04-10 宁波奥克斯电气有限公司 Parallel compressor selection and configuration method for preventing compressor from being frequently started up and shut down
CN105091439A (en) * 2014-05-07 2015-11-25 苏州必信空调有限公司 Computing method of refrigerating capacity and refrigerating efficiency of oil-free refrigerating system and refrigerating system
CN106949680A (en) * 2016-01-07 2017-07-14 青岛海尔开利冷冻设备有限公司 A kind of refrigeration system compressor group coefficient of performance detection method and detecting system
CN106524551A (en) * 2016-11-07 2017-03-22 清华大学 Mass and flow measuring method and device of refrigerant in refrigerating system and measuring instrument

Non-Patent Citations (6)

* Cited by examiner, † Cited by third party
Title
EMMA SINGER等: "On-field measurement method of vapor injection heat pump system", 《INTERNATIONAL JOURNAL OF REFRIGERATION》 *
MITSUHIRO FUKUTA等: "Performance of compression/absorption hybrid refrigeration cycle with propane/mineral oil combination", 《INTERNATIONAL JOURNAL OF REFRIGERATION》 *
丁国良等编著: "《制冷空调新工质：热物理性质的计算方法与实用图表》", 31 May 2003, 上海交通大学出版社 *
周光辉等: "制冷剂HCFC-124热力性质计算研究", 《低温与超导》 *
郑兆志等: "《家用空调维修安装技术》", 31 March 2006, 中国科学技术出版社 *
郑旭煦等: "《化工原理》", 31 January 2016, 华中科技大学出版社 *

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Application publication date: 20171107