CN107328058A - Air conditioner and its efficiency computational methods - Google Patents
Air conditioner and its efficiency computational methods Download PDFInfo
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- CN107328058A CN107328058A CN201710776010.8A CN201710776010A CN107328058A CN 107328058 A CN107328058 A CN 107328058A CN 201710776010 A CN201710776010 A CN 201710776010A CN 107328058 A CN107328058 A CN 107328058A
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Abstract
The invention discloses a kind of air conditioner and its efficiency computational methods, it the described method comprises the following steps：Obtain the current working and power consumption, the current frequency housing heat dissipation capacity Q of compressor of air conditionerloss；Obtain compressor return air mouthful temperature t1, exhaust port temperatures t2, outdoor heat exchanger first end temperature t4, indoor heat exchanger first end temperature t7With compressor tonifying Qi temperature t8；When current working is cooling condition, according to t1、t2、t4、t7And t8The refrigerant enthalpy h of gas returning port is generated respectively1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；The power of compressor is obtained according to current frequency and preset compressor performance curve；According to power, Qloss、h1、h2、h4、h7、h8’And h8”Generate the refrigerating capacity of air conditioner；The efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Description
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
First 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, bag
Include following steps：Obtain current working, the current frequency of compressor and the air conditioner power consumption of air conditioner；Obtain compressor
Housing 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, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4, indoor heat exchanger first end indoor heat exchanger first end
Temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8；When the current working of the air conditioner is cooling condition, according to described
The gas returning port temperature t of gas returning port in compressor1Generate the refrigerant enthalpy h of gas returning port1, according to exhaust outlet in the compressor
Exhaust port temperatures t2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the outdoor heat exchanger of the outdoor heat exchanger first end
One end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4, changed according to the interior of the indoor heat exchanger first end
Hot device first end temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7With the benefit according to the compressor tonifying Qi entrance
Temperature degree t8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the pressure
The current frequency and preset compressor performance curve of contracting machine obtain the power of the compressor；According to the power of the compressor,
The housing heat dissipation capacity Q for obtaining compressorloss, the gas returning port refrigerant enthalpy h1, the exhaust outlet refrigerant enthalpy
Value h2, the outdoor heat exchanger first end refrigerant enthalpy h4, the indoor heat exchanger first end refrigerant enthalpy h7, institute
State the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the refrigeration of air conditioner
Amount；And 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 of the current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature of outdoor heat exchanger first end, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When the current working for adjusting device is cooling condition, each above-mentioned temperature detecting point is generated according to the temperature of each above-mentioned temperature detecting point
Refrigerant enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the refrigerant enthalpy of each above-mentioned temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The real-time energy efficiency of device optimizes the running status of air conditioner, reaches energy-conservation and improves the purpose of 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 compressor1Generation is described to return
The refrigerant enthalpy h of gas port1Specifically 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 the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；In the middle part of the indoor heat exchanger
Temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the suction superheat Δ t1With the indoor heat exchange
Device middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the modifying factor of the gas returning port refrigerant enthalpy
Sub- D1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h1。
Further, the enthalpy h of saturation refrigerant under the 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 the 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.
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end
t7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specifically 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 the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to the indoor heat exchanger first end
The modifying factor D of refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the row
The enthalpy h of the refrigerant of gas port2Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to described
Outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；It is vented according in the compressor
The exhaust port temperatures t of mouth2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to the discharge superheat
Spend Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to the amendment
Factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the enthalpy h of the refrigerant of the exhaust outlet2。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
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：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
According to one embodiment of present invention, the refrigerating capacity of the air conditioner is generated according to below equation：
Wherein, QRefrigerating capacityFor the air conditioner
Refrigerating capacity, PcomFor compressor horsepower.
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, consequently facilitating according to reality
Shi Nengxiao is optimized to running status, is reached energy-conservation and is improved the purpose of refrigeration.
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 for another air conditioner that fourth aspect present invention embodiment is proposed,
Comprise the following steps：Obtain current working, the current frequency of compressor and the air conditioner power consumption of air conditioner；The shell of compressor
Body 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 end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, indoor heat exchanger first end indoor heat exchanger first end
Temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8；When the current working of the air conditioner is heating condition, according to described
The gas returning port temperature t of gas returning port in compressor1Generate the refrigerant enthalpy h of gas returning port1, according to exhaust outlet in the compressor
Exhaust port temperatures t2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the indoor heat exchanger at the end of indoor heat exchanger second
Two end temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5, changed according to the interior of the indoor heat exchanger first end
Hot device first end temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7With the benefit according to the compressor tonifying Qi entrance
Temperature degree t8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the pressure
The current frequency and preset compressor performance curve of contracting machine obtain the power of the compressor；According to the power of the compressor,
The housing heat dissipation capacity Q of the compressorloss, the gas returning port refrigerant enthalpy h1, the exhaust outlet refrigerant enthalpy
h2, the end of indoor heat exchanger second refrigerant enthalpy h5, the indoor heat exchanger first end refrigerant enthalpy h7, it is described
Fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate heating for air conditioner
Amount；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 of the current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature at the end of indoor heat exchanger second, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When the current working for adjusting device is heating condition, each above-mentioned temperature detecting point is generated according to the temperature of each above-mentioned temperature detecting point
Refrigerant enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the refrigerant enthalpy of each above-mentioned temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The real-time energy efficiency of device optimizes the running status of air conditioner, reaches energy-conservation and improves the purpose of 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 compressor1Generation is described to return
The refrigerant enthalpy h of gas port1Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to described time
Gas port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat Δ t1
With 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 the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the amendment of the gas returning port refrigerant enthalpy
Factor D1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
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 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.
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the row
The enthalpy h of the refrigerant of gas port2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to described
Indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With the exhaust port temperatures t of exhaust outlet in the compressor2Generation exhaust
Degree of superheat Δ t2；According to the suction and discharge degree of superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigerant
The modifying factor D of enthalpy2；According to the indoor heat exchanger middle portion temperature t6Generate 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 saturationGenerate the refrigerant enthalpy h of the exhaust outlet2。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end
t7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：According to the interior in the middle part of the indoor heat exchanger
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 t7
With the indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to described
The modifying factor D of indoor heat exchanger first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw
Into the refrigerant enthalpy h of the outlet7。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6For 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：
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 air conditioner
Heating capacity, PcomFor compressor horsepower.
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, consequently facilitating according to reality
Shi Nengxiao is optimized to running status, is reached energy-conservation and is improved the purpose of refrigeration.
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 structural representation of the air conditioner according to one embodiment of the invention；
Fig. 2 is a kind of flow chart of the efficiency computational methods of air conditioner according to the embodiment of the present invention；
Fig. 3 is the flow chart of the efficiency computational methods 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.
In an embodiment of the present invention, air conditioner can be twin-stage steam compressing air conditioner device.
As shown in figure 1, the air conditioner of the embodiment of the present invention may include compressor 100, four-way valve 200, outdoor heat exchanger
300th, restricting element 400, indoor heat exchanger 500, restricting element 600 and flash vessel 700.Wherein, the exhaust outlet of compressor 100 leads to
Four-way valve 200 is crossed with the second end of outdoor heat exchanger 300 to be connected, the first end of outdoor heat exchanger 300 by restricting element 600 with
The first end of flash vessel 700 is connected, and the second end of flash vessel 700 passes through the second end of restricting element 400 and indoor heat exchanger 500
It is connected, the first end of indoor heat exchanger 500 is connected by four-way valve 200 with the gas returning port of compressor 100, the of flash vessel 700
Three ends are connected with the tonifying Qi entrance of compressor 100.
When the current working of air conditioner is cooling condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and
A2 ends are directly connected with outdoor heat exchanger 300, and refrigerant is flowed to as shown in the solid arrow in Fig. 1；When the current working of air conditioner
During for heating condition, the exhaust outlet of compressor 100 is directly connected by the A1 ends and A4 ends of four-way valve 200 with indoor heat exchanger 500
Logical, refrigerant is flowed to as shown in the dotted arrow in Fig. 1, is specifically not detailed here.
Fig. 2 is the flow chart of the efficiency computational methods of the air conditioner according to the embodiment of the present invention.As shown in Fig. 2 of the invention
The efficiency computational methods of the air conditioner of embodiment comprise the following steps：
S101, obtains current working, the current frequency of compressor and the air conditioner power consumption of air conditioner, and obtains compression
The housing heat dissipation capacity Q of machineloss。
Specifically, the current working of air conditioner, the current frequency of compressor can be monitored in real time by the electric-control system of air conditioner
Rate and air conditioner power consumption PPower consumption。
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-(t9+273.15)4+(9.4+0.052×(t2-t9))×
ACompressor×(t2-t9),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition, t by looking into pressure contracting type number9For outdoor ring
Border temperature, can be obtained, t by being disposed in the outdoor the temperature sensor at heat exchanger fin2For the exhaust of exhaust outlet in compressor
Mouth temperature.
S102, 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 the tonifying Qi temperature t of compressor tonifying Qi entrance8。
Specifically, the temperature of the temperature detecting point can be detected by setting temperature sensor respectively in corresponding temperature test point
Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature
t1；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t2；By setting
The temperature sensor (as shown in Figure 1 04) put in outdoor heat exchanger first end obtains outdoor heat exchanger first end temperature t4；It is logical
Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end
t7；Compressor tonifying Qi entrance is obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi porch
Tonifying Qi temperature t8。
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.
S103, 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, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant of exhaust outlet
Enthalpy h2, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4Generate the refrigeration of outdoor heat exchanger first end
Agent enthalpy h4, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the system of indoor heat exchanger first end
Cryogen enthalpy h7With the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With
The liquid refrigerant enthalpy h of flash vessel8”。
Specifically, during air conditioner works, because the state of the refrigerant of different temperatures test point is different, therefore
The enthalpy of the refrigerant of different temperatures test point is different.In one embodiment of the invention, rule of thumb formula it can calculate
To the enthalpy of refrigerant.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h of outdoor heat exchanger first end4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous state of compressor
Refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is cooling condition,
The refrigerant superheat of the gas returning port of compressor, can combine the refrigerant enthalpy h that suction superheat calculates gas returning port1。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Generate the system of gas returning port
Cryogen enthalpy h1Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to gas returning port temperature t1With
Indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to indoor heat exchanger middle portion temperature t6Generate under suction temperature
The enthalpy h of saturation refrigerantAir-breathing saturation；According to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate gas returning port refrigerant
The modifying factor D of enthalpy1；According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration system
Cryogen enthalpy h1。
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (1)Air-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5 (1)
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 following formula (2)1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6 (2)
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger
Interior heat exchanger middle portion temperature t6, then according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ
t1=t1-t6, and according to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the amendment of gas returning port refrigerant enthalpy
Factor D1, such as shown in above-mentioned formula (2).Meanwhile, according to indoor heat exchanger middle portion temperature t6Generate saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturation, such as shown in above-mentioned formula (1).Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigeration
The enthalpy h of agentAir-breathing saturationGenerate refrigerant enthalpy h1, h1=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, when the current working of air conditioner is refrigeration work
During condition, the refrigerant superheat of indoor heat exchanger first end can combine the position refrigerant superheat degree and calculate indoor heat exchanger first
The refrigerant enthalpy h at end7。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7It is raw
Into the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：According to indoor heat exchanger first end temperature t7With indoor heat exchange
Device middle portion temperature t6Generate degree of superheat Δ t7；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；According to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7And saturation
The enthalpy h of refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (3)7：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Specifically, can be first according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generation overheat
Spend Δ t7=t7-t6, then 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, such as shown in above-mentioned formula (3), meanwhile, according to indoor heat exchanger middle portion temperature t6Generate suction temperature
The enthalpy h of lower saturation refrigerantAir-breathing saturation, such as shown in above-mentioned formula (1).Finally, freezed according to the indoor heat exchanger first end of generation
The modifying factor D of agent enthalpy7With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7=D7·hAir-breathing saturation+d7, wherein, d7
For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is cooling condition, compression
The refrigerant superheat of the exhaust outlet of machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet2。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the system of exhaust outlet
The enthalpy h of cryogen2Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According in outdoor heat exchanger
Portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the exhaust port temperatures t of exhaust outlet in compressor2With
Outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature
t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to modifying factor D2, under delivery temperature saturation refrigerant enthalpy
hIt is vented saturationGenerate the enthalpy h of the refrigerant of exhaust outlet2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (4)2：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger
External heat exchanger middle portion temperature t3, then according to the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3
Generate discharge superheat Δ t2=t2-t3, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generate exhaust outlet
The modifying factor D of refrigerant enthalpy2, such as shown in above-mentioned formula (4), meanwhile, according to outdoor heat exchanger middle portion temperature t3Generation exhaust
At a temperature of saturation refrigerant enthalpy hIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5For the corresponding saturation of refrigerant
Fauna number.Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturation
Generate the refrigerant enthalpy h of exhaust outlet2, h2=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, when the current working of air conditioner is cooling condition, room
The refrigerant supercooling of external heat exchanger first end, can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4。
According to one embodiment of present invention, the refrigerant enthalpy of outdoor heat exchanger first end is generated according to following formula (5)
Value h4：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
In addition, filling into the gaseous refrigerant enthalpy h of compressor8’It can be calculated according to below equation：
h8’=a1+a2*t8+a3*t8 2+a4*t8 3+a5, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, a1-a5For system
The corresponding saturation region coefficient of cryogen.
The liquid refrigerant enthalpy h of flash vessel8”It can be calculated according to below equation：
h8”=c1+c2*t8+c3*t8 2+c4*t8 3, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, c1-c4For refrigeration
The corresponding supercooling fauna number of agent.
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.
It should be noted that in other embodiments of the invention, can also directly invoke the result of calculation of software, or pass through
Other approach obtain the refrigerant enthalpy of each temperature detecting point.For example, when the current working of air conditioner is cooling condition
When, low pressure that can also be in air conditioner, gas returning port temperature t1, indoor heat exchanger first end temperature t7Respectively obtain return-air
The refrigerant enthalpy h of mouth1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be in air conditioner high-pressure, row
Gas port temperature t2, outdoor heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2With outdoor heat exchanger first
The refrigerant enthalpy h at end4, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure8’And it is full
With liquid enthalpy h8”。
S104, the power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve.
Specifically, (it can be provided by compressor producer according to preset compressor performance curve, and be stored in advance in compressor
In) calculate the flow and compressor consumption power for obtaining compressor under different running frequencies.
S105, according to the power of compressor, the housing heat dissipation capacity Q of acquisition compressorloss, gas returning port refrigerant enthalpy h1、
The enthalpy h of the refrigerant of exhaust outlet2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant
Enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the refrigeration of air conditioner
Amount.
Specifically, the refrigerating capacity of air conditioner can be generated according to below equation：
Wherein, QRefrigerating capacityFreeze for air conditioner
Amount, PcomFor compressor horsepower.
S106, 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 current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature of outdoor heat exchanger first end, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When the current working for adjusting device is cooling condition, each above-mentioned temperature detecting point is generated according to the temperature of each above-mentioned temperature detecting point
Refrigerant enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the refrigerant enthalpy of each above-mentioned temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The real-time energy efficiency of device optimizes the running status of air conditioner, reaches energy-conservation and improves 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, consequently facilitating according to reality
Shi Nengxiao is optimized to running status, is reached energy-conservation and is improved the purpose of refrigeration.
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.
The air conditioner and its efficiency computational methods of above-described embodiment can detect the refrigeration efficiency of air conditioner, for detection air-conditioning
The heat efficiency of device, the present invention also proposes the efficiency computational methods of another air conditioner.
As shown in figure 3, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：
S201, obtains current working, the current frequency of compressor and the air conditioner power consumption of air conditioner, and obtains compression
The housing heat dissipation capacity Q of machineloss。
Specifically, the current working of air conditioner, the current frequency of compressor can be monitored in real time by the electric-control system of air conditioner
Rate and air conditioner power consumption PPower consumption。
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, t by looking into pressure contracting type number8For compressor
The tonifying Qi temperature of tonifying Qi entrance, can be obtained by being arranged on the temperature sensor (as shown in Figure 1 08) of compressor tonifying Qi entrance,
t2, can be by setting the temperature sensor of exhaust outlet within the compressor (such as Fig. 1 institutes for the exhaust port temperatures of exhaust outlet in compressor
Show 02).
S202, 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 the tonifying Qi temperature t of compressor tonifying Qi entrance8。
Specifically, the temperature of the temperature detecting point can be detected by setting temperature sensor respectively in corresponding temperature test point
Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature
t1；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t2；By setting
The temperature sensor (as shown in Figure 1 05) for putting the end of heat exchanger second indoors obtains indoor heat exchanger the second end temperature t5；It is logical
Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end
t7；Compressor tonifying Qi entrance is obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi porch
Tonifying Qi temperature t8。
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.
S203, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1
Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant of exhaust outlet
Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigeration at the end of indoor heat exchanger second
Agent enthalpy h5, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the system of indoor heat exchanger first end
Cryogen enthalpy h7With the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With
The liquid refrigerant enthalpy h of flash vessel8”。
Specifically, during air conditioner works, because the state of the refrigerant of different temperatures test point is different, therefore
The enthalpy of the refrigerant of different temperatures test point is different.In one embodiment of the invention, rule of thumb formula it can calculate
To the enthalpy of refrigerant.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h at the end of indoor heat exchanger second5With the refrigerant enthalpy h of indoor heat exchanger first end7, fill into the gas of compressor
State refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition,
The refrigerant superheat of the gas returning port of compressor, can combine the refrigerant enthalpy h that suction superheat calculates gas returning port1。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Generate the system of gas returning port
Cryogen enthalpy h1Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to gas returning port temperature t1With
Outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to suction superheat Δ t1With outdoor heat exchanger middle portion temperature
t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to outdoor heat exchanger middle portion temperature t3Generate saturation under suction temperature
The enthalpy h of refrigerantAir-breathing saturation；According to the modifying factor D of gas returning port refrigerant enthalpy1, under suction temperature saturation refrigerant enthalpy
hAir-breathing saturationGenerate the refrigerant enthalpy h of gas returning port1。
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (6)Air-breathing saturation：
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 following formula (7)1：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger
External heat exchanger middle portion temperature t3, then according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ
t1=t1-t3, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy
Factor D1, such as shown in above-mentioned formula (7).Meanwhile, according to outdoor heat exchanger middle portion temperature t3Generate saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturation, such as shown in above-mentioned formula (6).Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigeration
The enthalpy h of agentAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For the corresponding overheated zone coefficient of refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression
The refrigerant superheat of the exhaust outlet of machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet2。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the system of exhaust outlet
The enthalpy h of cryogen2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According in indoor heat exchanger
The indoor heat exchanger middle portion temperature t in portion6With the exhaust port temperatures t of exhaust outlet in compressor2Generate discharge superheat Δ t2；According to
Discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to interior
Heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to repairing for exhaust outlet refrigerant enthalpy
Positive divisor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (8)2：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Specifically, can be first according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6It is raw
Into discharge superheat Δ t2=t2-t6, then according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet
The modifying factor D of refrigerant enthalpy2, such as shown in above-mentioned formula (8), meanwhile, according to indoor heat exchanger middle portion temperature t6Generation exhaust
At a temperature of saturation refrigerant enthalpy hIt is vented saturation,Wherein, a1-a5For refrigerant pair
The saturation region coefficient answered.Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy
Value hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For the corresponding overheat fauna of refrigerant
Number.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is to heat work
During condition, the refrigerant superheat of indoor heat exchanger first end can combine the position refrigerant superheat degree and calculate indoor heat exchanger first
The refrigerant enthalpy h at end7。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7It is raw
Into the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：Temperature in the middle part of indoor heat exchanger in the middle part of indoor heat exchanger
Spend t6With indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6
Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to repairing for indoor heat exchanger first end refrigerant enthalpy
Positive divisor D7, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (9)7：
Wherein, d1-d6For the corresponding overheated zone coefficient of refrigerant.
Specifically, can be first according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generation overheat
Spend Δ t7=t7-t6, then 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, such as shown in above-mentioned formula (9), meanwhile, according to indoor heat exchanger middle portion temperature t6Generate delivery temperature
The enthalpy h of lower saturation refrigerantIt is vented saturation,Wherein, a1-a5It is corresponding for refrigerant
Saturation region coefficient.Finally, according to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy of generation7Under delivery temperature
The enthalpy h of saturation refrigerantIt is vented saturationGenerate refrigerant enthalpy h7=D7·hIt is vented saturation+d7, wherein, d7For the corresponding overheat of refrigerant
Fauna number.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room
The refrigerant supercooling at the interior end of heat exchanger second, can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5。
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to following formula (10)
Value h5：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
In addition, filling into the gaseous refrigerant enthalpy h of compressor8’It can be calculated according to below equation：
h8’=a1+a2*t8+a3*t8 2+a4*t8 3+a5, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, a1-a5For system
The corresponding saturation region coefficient of cryogen.
The liquid refrigerant enthalpy h of flash vessel8”It can be calculated according to below equation：
h8”=c1+c2*t8+c3*t8 2+c4*t8 3, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, c1-c4For refrigeration
The corresponding supercooling fauna number of agent.
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.
It should be noted that in other embodiments of the invention, can also directly invoke the result of calculation of software, or pass through
Other approach obtain the refrigerant enthalpy of each temperature detecting point.For example, when the current working of air conditioner is heating condition
When, low pressure that can also be in air conditioner, gas returning port temperature t1, the second end of indoor heat exchanger temperature t5Respectively obtain return-air
The refrigerant enthalpy h of mouth1With the refrigerant enthalpy h at the end of indoor heat exchanger second5, and can be in air conditioner high-pressure, row
Gas port temperature t2, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy h of exhaust outlet2With indoor heat exchanger first
The refrigerant enthalpy h at end7, and saturated gas enthalpy h under the state obtained according to tonifying Qi temperature or pressure8’And saturated solution
Body enthalpy h8”。
S204, the power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve.
Specifically, (it can be provided by compressor producer according to preset compressor performance curve, and be stored in advance in compressor
In) calculate the flow and compressor consumption power for obtaining compressor under different running frequencies.
S205, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port refrigerant enthalpy h1, exhaust
The enthalpy h of the refrigerant of mouth2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy
h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to equation below：
Wherein, QHeating capacityFor air conditioner heat-production
Amount, PcomFor compressor horsepower.
S206, 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 current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature at the end of indoor heat exchanger second, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When the current working for adjusting device is heating condition, each above-mentioned temperature detecting point is generated according to the temperature of each above-mentioned temperature detecting point
Refrigerant enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the refrigerant enthalpy of each above-mentioned temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The real-time energy efficiency of device optimizes the running status of air conditioner, reaches energy-conservation and improves 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 a kind of air-conditioning that the above embodiment of the present invention is proposed
The efficiency computational methods of device.
Air conditioner according to embodiments of the present invention, can real-time and accurately detect to efficiency, be easy to according to real-time energy
Effect optimization running status, reaches energy-conservation and improves the purpose of heating effect.
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, a kind of efficiency computational methods for 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.
In summary, the air conditioner of the embodiment of the present invention and its efficiency computational methods, are followed by obtaining air conditioner refrigerant
The physical property of refrigerant in loop system, and the power for obtaining air conditioner is calculated according to the physical property of refrigerant, and enter one
Step calculates the efficiency for obtaining air conditioner, 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 (24)
1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the current frequency 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 pressure
The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；
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, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet
Enthalpy h2, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generate outdoor heat exchanger first end
Refrigerant enthalpy h4, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchanger
The refrigerant enthalpy h of first end7With the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gaseous state system of compressor
Cryogen enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
The power of the compressor is obtained according to the current frequency of the compressor and preset compressor performance curve；
According to the power of the compressor, the housing heat dissipation capacity Q of the acquisition compressorloss, the gas returning port refrigerant enthalpy
h1, the exhaust outlet refrigerant enthalpy h2, the outdoor heat exchanger first end refrigerant enthalpy h4, the indoor heat exchange
The refrigerant enthalpy h of device first end7, the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid refrigeration of the flash vessel
Agent enthalpy h8”Generate 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 the gas returning port1Specifically 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 indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
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 modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationThe generation refrigeration
Agent enthalpy h1。
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 the indoor heat exchanger first end7Specifically 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。
6. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that interior is generated according to below equation and changed
The modifying factor D of hot device 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>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&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>&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>&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>&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>&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 t2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
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 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 modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of the exhaust outlet
The enthalpy h of agent2。
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：
<mrow>
<msub>
<mi>D</mi>
<mn>2</mn>
</msub>
<mo>=</mo>
<mn>1</mn>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>1</mn>
</msub>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>3</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</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>&Delta;t</mi>
<mn>2</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>&Delta;t</mi>
<mn>2</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>&Delta;t</mi>
<mn>2</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.
9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated according to below equation
The refrigerant enthalpy h of external heat exchanger first end4：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
10. 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 capacityFreeze for the air conditioner
Amount, PcomFor compressor horsepower.
11. 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 1-10
Any described method.
12. 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 1-10 is realized when calculation machine program is executed by processor.
13. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the current frequency 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 pressure
The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；
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 compressor1It is raw
Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet
Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the end of indoor heat exchanger second
Refrigerant enthalpy h5, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchanger
The refrigerant enthalpy h of first end7With the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gaseous state system of compressor
Cryogen enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
The power of the compressor is obtained according to the current frequency of the compressor and preset compressor performance curve；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port refrigerant enthalpy h1、
The enthalpy h of the refrigerant of the exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5, the indoor heat exchanger
The refrigerant enthalpy h of one end7, the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid refrigerant enthalpy of the flash vessel
Value h8”Generate 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.
14. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to return-air in the compressor
The gas returning port temperature t of mouth1Generate the refrigerant enthalpy h of the gas returning port1Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
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。
15. the efficiency computational methods of air conditioner as claimed in claim 14, 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.
16. the efficiency computational methods of air conditioner as claimed in claim 14, 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>&Delta;t</mi>
<mn>1</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&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>&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>&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>&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>&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.
17. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that be vented according in the compressor
The exhaust port temperatures t of mouth2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically 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 t6Generate 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。
18. the efficiency computational methods of the air conditioner described in claim 17, it is characterised in that the row is generated according to below equation
The modifying factor D of gas port refrigerant enthalpy2：
<mrow>
<msub>
<mi>D</mi>
<mn>2</mn>
</msub>
<mo>=</mo>
<mn>1</mn>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>1</mn>
</msub>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>3</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</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>&Delta;t</mi>
<mn>2</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>&Delta;t</mi>
<mn>2</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>&Delta;t</mi>
<mn>2</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.
19. the efficiency computational methods of air conditioner as claimed in claim 17, 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 the indoor heat exchanger first end7Specifically 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 outlet7。
20. the efficiency computational methods of air conditioner as claimed in claim 19, 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>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&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>&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>&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>&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>&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.
21. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to being calculated below equation
The refrigerant enthalpy h at the end of indoor heat exchanger second5：
Wherein, c1-c4For the corresponding supercooling fauna number of refrigerant.
22. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to equation below generation
The heating capacity of air conditioner：
Wherein, QHeating capacityFor the air conditioner heat-production
Amount, PcomFor compressor horsepower.
23. 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 13-22
Any described method.
24. 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 13-22 is realized when calculation machine program is executed by processor.
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| 陈雨田等: "SD-5型汽车空调用制冷压缩机性能曲线的拟合与修正", 《流体机械》 * |
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