CN107504648A - Air conditioner and its efficiency computational methods - Google Patents
Air conditioner and its efficiency computational methods Download PDFInfo
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- CN107504648A CN107504648A CN201710772640.8A CN201710772640A CN107504648A CN 107504648 A CN107504648 A CN 107504648A CN 201710772640 A CN201710772640 A CN 201710772640A CN 107504648 A CN107504648 A CN 107504648A
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Abstract
The invention discloses a kind of air conditioner and its efficiency computational methods, the described method comprises the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain the housing heat dissipation capacity Q of compressorloss；Obtain gas returning port in compressor, exhaust outlet, indoor heat exchanger middle part, the temperature t of indoor heat exchanger first end1、t2、t6、t7With indoor environment temperature t9；According to t6And t9Generate the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5；When the current working of air conditioner is heating condition, respectively according to t1、t2、t5And t7It is corresponding to generate the refrigerant enthalpy and lubricating oil enthalpy of gas returning port, exhaust outlet, the end of indoor heat exchanger second and indoor heat exchanger first end, and further generate the mixture enthalpy h of above-mentioned each temperature detecting point1、h2、h5And h7；According to the power of compressor, h1、h2、h5And h7Generate the heating capacity of air conditioner；And the efficiency of air conditioner is generated according to air conditioner power consumption and heating 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 preferable fortune 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 solves one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention
One purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
To reach above-mentioned purpose, a kind of efficiency computational methods for air conditioner that first aspect present invention embodiment proposes include
Following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain return-air in compressor
The gas returning port temperature t of mouth1, in the compressor exhaust outlet exhaust port temperatures t2, indoor heat exchanger in the middle part of indoor heat exchanger
Middle portion temperature t6, indoor heat exchanger first end indoor heat exchanger first end temperature t7With indoor environment temperature t9；According to described
Indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With the indoor environment temperature t9Generate the end of indoor heat exchanger second
The second end of indoor heat exchanger temperature t5；When the current working of the air conditioner is heating condition, according in the compressor
The gas returning port temperature t of gas returning port1Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the compression
The exhaust port temperatures t of exhaust outlet in machine2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to described
The second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants
With lubricating oil enthalpy h5 lubricating oilWith the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generation interior is changed
The refrigerant enthalpy h of hot device first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerant
With lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsAnd profit
Lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to the refrigerant enthalpy at the end of indoor heat exchanger second
h5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixture enthalpy h at the end of indoor heat exchanger second5With according to the indoor heat exchanger
The refrigerant enthalpy h of first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；Root
According to the power of the compressor, the mixture enthalpy h of the gas returning port1, exhaust outlet mixture enthalpy h2, indoor heat exchanger
The mixture enthalpy h at two ends5With the mixture enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner；And according to
The air conditioner power consumption and the heating capacity generate the efficiency of the air conditioner.
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 power and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet, indoor heat exchanger middle part, indoor heat exchange
The temperature and indoor environment temperature of device first end, and when air conditioner is in heating condition according to above-mentioned each temperature detection
The temperature of point generates the refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points, and further generates multiple temperature detections
The mixture enthalpy of point, the mixture enthalpy and air conditioner power consumption work(of power, multiple temperature detecting points then in conjunction with compressor
Rate 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 conditioner
Real-time energy efficiency optimization air conditioner running status, reach energy-conservation and improve heating effect purpose.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add
Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1Generate back
The refrigerant enthalpy h of gas port1 refrigerantSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to institute
State gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat
Δt1With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；Changed according to the outdoor
Hot device middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the gas returning port refrigerant enthalpy
Modifying factor D1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy of the gas returning port
h1 refrigerant。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the evaporator inlet temperature t is generated by below equation5：
t5=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
Further, the exhaust port temperatures t according to exhaust outlet in the compressor2Generate the refrigeration of the exhaust outlet
Agent enthalpy h2 refrigerantsSpecifically include：According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the compressor
The exhaust port temperatures t of middle exhaust outlet2Generate discharge superheat Δ t2；According to the discharge superheat Δ t2With the indoor heat exchange
Device middle portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；Indoor heat exchange in the middle part of the indoor heat exchanger
Device middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to repairing for the exhaust outlet refrigerant enthalpy
Positive divisor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein,
d1-d6For overheated zone coefficient corresponding to refrigerant.
Further, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchange
The refrigerant enthalpy h of device first end7 refrigerantsSpecifically include：According to the indoor heat exchanger middle portion temperature in the middle part of the indoor heat exchanger
t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With the indoor heat exchange
Device middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to the indoor heat exchanger first
Hold the modifying factor D of refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the indoor heat exchange
The refrigerant enthalpy h of device first end7 refrigerants。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation
Value h5 refrigerants：
h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor compressor horsepower.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation
hI lubricating oil, wherein, i is positive integer,
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i, wherein, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each temperature detecting point is calculated according to below equationi,
Wherein, i is positive integer,
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104, wherein, CgFor mixture oil content, f is the running frequency of the compressor.
To reach above-mentioned purpose, the air conditioner that second aspect of the present invention embodiment proposes includes memory, processor and deposited
Store up the computer program that can be run on the memory and on the processor, computer described in the computing device
During program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
To reach above-mentioned purpose, non-transitorycomputer readable storage medium that third aspect present invention embodiment proposes,
Computer program is stored thereon with, the computer program realizes that first aspect present invention embodiment carries when being executed by processor
The efficiency computational methods of the air conditioner gone out.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage
Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner
Running status, reach energy-conservation and improve the purpose of heating effect.
Brief description of the drawings
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention；
Fig. 2 is the structural representation according to the air conditioner of one embodiment of the invention；
Fig. 3 is the block diagram according to the efficiency computing system of the air conditioner of 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
The embodiment of accompanying drawing description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
The air conditioner of the embodiment of the present invention and its efficiency computational methods are described below in conjunction with the accompanying drawings.
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention.
As shown in figure 1, the efficiency computational methods of the air conditioner of the embodiment of the present invention, comprise the following steps：
S101, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionerCompressorAnd air-conditioning
Device power consumption PPower consumption。
S102, obtain the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room
Indoor heat exchanger middle portion temperature t in the middle part of interior heat exchanger6, indoor heat exchanger first end indoor heat exchanger first end temperature t7With
Indoor environment temperature t9。
As shown in Fig. 2 can be by setting gas returning port temperature sensor at gas returning port within the compressor to detect gas returning port temperature
Spend t1, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t2, indoors in heat exchanger
Portion sets indoor heat exchanger middle portion temperature sensor to detect indoor heat exchanger middle portion temperature t6, heat exchanger first end indoors
Place sets indoor heat exchanger first end temperature sensor to detect indoor heat exchanger first end temperature t7And heat exchanger indoors
Indoor temperature transmitter is set to detect indoor environment temperature t at fin9。
Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant
Tube wall, especially the position of temperature sensor is set 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, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With indoor environment temperature t9Generation is indoor
The second end of indoor heat exchanger temperature t at the end of heat exchanger second5。
In one embodiment of the invention, indoor heat exchanger the second end temperature t can be generated by below equation5：
t5=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
S104, 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 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in compressor2
Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the indoor heat exchanger at the end of indoor heat exchanger second
Second end temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith according to interior
The indoor heat exchanger first end temperature t of heat exchanger first end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsAnd profit
Lubricating oil enthalpy h7 lubricating oil。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room
Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, is in the middle part of condenser in the middle part of indoor heat exchanger.
Because the refrigerant of different temperatures test point and the state of the mixture of lubricating oil are different, therefore different temperatures detects
The refrigerant enthalpy and lubricating oil enthalpy of point are different.In one embodiment of the invention, rule of thumb formula can calculate
To refrigerant enthalpy and lubricating oil enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、
The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second refrigerant enthalpy h5 refrigerantsWith
Lubricating oil enthalpy h5 lubricating oilWith the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilSpecific mistake
Journey.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is heating condition, pressure
The refrigerant superheat of the gas returning port of contracting machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1 refrigerant。
Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained3, wherein, as shown in Fig. 2 outdoor
Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger3Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through
Degree sensor detects to obtain.
Then can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1, and according to
Suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1, and according to
Outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Wherein, suction superheat Δ t1For
Gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.The modifying factor of gas returning port refrigerant enthalpyWherein, d1-d6For refrigerant pair
The overheated zone coefficient answered.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5
For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root
According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1 refrigerant, h1 refrigerant
=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is heating condition, pressure
The refrigerant superheat of the exhaust outlet of contracting machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2 refrigerants。
Specifically, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Generation row
Gas degree of superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Saturation under delivery temperature is generated to freeze
The enthalpy h of agentIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigerant enthalpy
The modifying factor D of value2.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2And indoor heat exchanger
Middle portion temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t6+a3t2 6+
a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1
Δt2+d2(Δ t2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For refrigerant pair
The overheated zone coefficient answered.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, can further repairing according to exhaust outlet refrigerant enthalpy
Positive divisor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants, h2 refrigerants=
D2·h It is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is heating
During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the
The refrigerant enthalpy h of one end7 refrigerants。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ
t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the amendment of indoor heat exchanger first end refrigerant enthalpy
Factor D7, and the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy according to generation7With the enthalpy of saturation refrigerant
hIt is vented saturationGenerate refrigerant enthalpy h7 refrigerants.Wherein, Δ t7=t7-t6,
h7 refrigerants=D7·hIt is vented saturation+d7, wherein, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, when the current working of air conditioner is heating condition,
The refrigerant supercooling at the end of indoor heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants：
h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant
Close, R410A refrigerants and saturation region coefficient, overheated zone coefficient and supercooling corresponding to R32 refrigerants are respectively illustrated in table 1
Fauna number.
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature
The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach
The refrigerant enthalpy of each temperature detecting point.For example, can also basis when the current working of air conditioner is heating condition
High-pressure, gas returning port temperature t in air conditioner1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant of gas returning port
Enthalpy h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures
t2, the second end of indoor heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigeration at the end of indoor heat exchanger second
Agent enthalpy h5。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, can be calculated according to below equation：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy of gas returning port can be calculated out
Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second lubricating oil enthalpy h5 lubricating oilAnd indoor heat exchanger
The lubricating oil enthalpy h of first end7 lubricating oil。
S105, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port
Value h1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, root
According to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixed of the end of indoor heat exchanger second
Compound enthalpy h5With the refrigerant enthalpy h according to indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration interior is changed
The mixture enthalpy h of hot device first end7。
Specifically, the mixture enthalpy h of each temperature detecting point can be calculated according to below equationi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, the mixed of gas returning port can be calculated out
Compound enthalpy h1, exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second mixture enthalpy h5With indoor heat exchanger
The mixture enthalpy h of one end7。
S106, according to the power of compressor, the mixture enthalpy h of gas returning port1, exhaust outlet mixture enthalpy h2, interior changes
The mixture enthalpy h at the hot end of device second5With the mixture enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to below equation：Wherein, QHeating capacity
For heating capacity of air conditioner, PCompressorFor compressor horsepower.
S107, 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 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 the heating capacity of air conditioner and power consumption, i.e. COP=
QHeating capacity/PPower consumption。
, can also be according to 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 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 power and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet, indoor heat exchanger middle part, indoor heat exchange
The temperature and indoor environment temperature of device first end, and when air conditioner is in heating condition according to above-mentioned each temperature detection
The temperature of point generates the refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points, and further generates multiple temperature detections
The mixture enthalpy of point, the mixture enthalpy and air conditioner power consumption work(of power, multiple temperature detecting points then in conjunction with compressor
Rate 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 conditioner
Real-time energy efficiency optimization air conditioner running status, reach energy-conservation and improve heating effect purpose.
Corresponding above-described embodiment, the present invention also propose a kind of air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor
The computer program of operation, during computing device computer program, it is empty that the another kind that the above embodiment of the present invention proposes can be achieved
Adjust the efficiency computational methods of device.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
Corresponding above-described embodiment, the present invention also propose a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating
When machine program is executed by processor, the efficiency computational methods for another air conditioner that the above embodiment of the present invention proposes can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage
Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner
Running status, reach energy-conservation and improve the purpose of heating effect.
Corresponding above-described embodiment, the present invention also propose the efficiency computing system of another air conditioner.
As shown in figure 3, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port temperature sensor 01,
Exhaust port temperatures sensor 02, indoor heat exchanger middle portion temperature sensor 06, indoor heat exchanger first end temperature sensor 07,
Indoor temperature transmitter 09 and acquisition module 10, mixture enthalpy generation module 20, the generation of the second end of indoor heat exchanger temperature
Module 30, heating capacity generation module 50, efficiency generation module 40.
Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1；Exhaust outlet temperature
Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Indoor heat exchanger middle portion temperature sensor 06 is used
Indoor heat exchanger middle portion temperature t in the middle part of acquisition indoor heat exchanger6；Indoor heat exchanger first end temperature sensor 07 is used for
Obtain the indoor heat exchanger first end temperature t of indoor heat exchanger first end7；Indoor temperature transmitter 09 is used to obtain indoor ring
Border temperature t9。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention
Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element 400 and indoor heat exchanger 500.
As shown in Fig. 2 gas returning port temperature sensor 01 can be set within the compressor at gas returning port, exhaust port temperatures sensor
02 settable exhaust ports within the compressor, indoor heat exchanger middle portion temperature sensor 06 may be provided in the middle part of indoor heat exchanger,
Indoor heat exchanger first end can be set in indoor heat exchanger first end temperature sensor 07, and indoor temperature transmitter 09 may be provided at
At indoor heat exchanger fin.Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point,
And to refrigerant tube wall, especially the position of temperature sensor is set to take Insulation.For example, can be tight by temperature sensor
Copper-surfaced pipe is set, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve temperature detection reliability and
Accuracy.
Acquisition module 10 is used to obtain the current working of air conditioner, the power of compressor and air conditioner power consumption；It is indoor
The indoor heat exchanger middle portion temperature t that the second end of heat exchanger temperature generation module 30 is used in the middle part of indoor heat exchanger6And interior
Environment temperature t9Generate the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5；Mixture enthalpy generation module 20 is used
In when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1Generate back
The refrigerant enthalpy h of gas port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in the compressor2It is raw
Into the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the indoor heat exchange at the end of indoor heat exchanger second
The second end of device temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith according to institute
State the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end
h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, and the refrigerant enthalpy h according to the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilIt is raw
Into the mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGeneration row
The mixture enthalpy h of gas port2, according to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oil
Generate the mixture enthalpy h at the end of indoor heat exchanger second5With the refrigerant enthalpy h according to the indoor heat exchanger first end7 refrigerants
With lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；Heating capacity generation module 50 is used for basis
The power of compressor, the mixture enthalpy h of gas returning port1, exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second mixing
Thing enthalpy h5With the mixture enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner；Efficiency generation module 40 is used for
According to the efficiency of air conditioner power consumption and heating capacity generation air conditioner.
Wherein, acquisition module 10, mixture enthalpy generation module 20, the second end of indoor heat exchanger temperature generation module 30,
Heating capacity generation module 50 and efficiency generation module 40 may be disposed in the electric-control system of air conditioner.Acquisition module 10 can be real-time
Monitor current working, the power P of compressor of air conditionerCompressorWith air conditioner power consumption PPower consumption。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room
Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, is in the middle part of condenser in the middle part of indoor heat exchanger.
In one embodiment of the invention, the second end of indoor heat exchanger temperature generation module 30 can be given birth to by below equation
Into the second end of indoor heat exchanger temperature t5：
t5=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
Because the refrigerant of different temperatures test point and the state of the mixture of lubricating oil are different, therefore different temperatures detects
The refrigerant enthalpy and lubricating oil enthalpy of point are different.In one embodiment of the invention, mixture enthalpy generation module 20
Rule of thumb refrigerant enthalpy and lubricating oil enthalpy can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy of gas returning port to mixture enthalpy generation module 20 separately below
h1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, exhaust outlet refrigerant enthalpy h2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, indoor heat exchanger
The refrigerant enthalpy h at two ends5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsAnd profit
Lubricating oil enthalpy h7 lubricating oilDetailed process.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is heating condition, pressure
The refrigerant superheat of the gas returning port of contracting machine, mixture enthalpy generation module 20 can combine the system that suction superheat calculates gas returning port
Cryogen enthalpy h1 refrigerant。
Specifically, mixture enthalpy generation module 20 can obtain the outdoor heat exchanger middle portion temperature in the middle part of outdoor heat exchanger
t3, wherein, as shown in Fig. 2 the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3Can be by the middle part of outdoor heat exchanger
The outdoor heat exchanger middle portion temperature sensor of setting detects to obtain.
Then mixture enthalpy generation module 20 can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generation is inhaled
Gas degree of superheat Δ t1, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate gas returning port refrigerant enthalpy
Modifying factor D1, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Its
In, suction superheat Δ t1For gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.Gas returning port
The modifying factor of refrigerant enthalpy
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+
a3t2 3+a4t3 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, mixture enthalpy
Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration
Refrigerant enthalpy h1 refrigerant, h1 refrigerant=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is heating condition, pressure
The refrigerant superheat of the exhaust outlet of contracting machine, mixture enthalpy generation module 20 can combine the system that discharge superheat calculates exhaust outlet
Cryogen enthalpy h2 refrigerants。
Specifically, mixture enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2Changed with interior
Hot device middle portion temperature t6Generate discharge superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6It is raw
The enthalpy h of saturation refrigerant under into delivery temperatureIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature
t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2.Wherein, discharge superheat Δ t2For the exhaust of exhaust outlet in compressor
Mouth temperature t2With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy of saturation refrigerant under delivery temperature
hIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.Exhaust outlet refrigerant enthalpy
The modifying factor D of value2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6,
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, mixture enthalpy generation module 20 can further basis
The modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of exhaust outlet
Agent enthalpy h2 refrigerants, h2 refrigerants=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is heating
During operating mode, the refrigerant superheat of indoor heat exchanger first end, mixture enthalpy generation module 20 can combine the position refrigerant mistake
Temperature calculates the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants。
Specifically, mixture enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7In indoor heat exchanger
Portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger the
The modifying factor D of one end refrigerant enthalpy7, and the modifying factor of the indoor heat exchanger first end refrigerant enthalpy according to generation
Sub- D7With the enthalpy h of saturation refrigerantIt is vented saturationGenerate refrigerant enthalpy h7 refrigerants.Wherein, Δ t7=t7-t6,h7 refrigerants=D7·hIt is vented saturation+
d7, wherein, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, when the current working of air conditioner is heating condition,
The refrigerant supercooling at the end of indoor heat exchanger second, mixture enthalpy generation module 20 can directly calculate the end of indoor heat exchanger second
Refrigerant enthalpy h5 refrigerants：h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant
Close, R410A refrigerants and saturation region coefficient, overheated zone coefficient and supercooling corresponding to R32 refrigerants are respectively illustrated in table 1
Fauna number.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature
The refrigerant enthalpy of measuring point.
In other embodiments of the invention, mixture enthalpy generation module 20 can also directly invoke the calculating knot of software
Fruit, or the refrigerant enthalpy by each temperature detecting point of other approach acquisition.For example, when the current working of air conditioner
For heating condition when, mixture enthalpy generation module 20 can also be according to the high-pressure in air conditioner, gas returning port temperature t1, room
Interior heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With the refrigerant enthalpy of indoor heat exchanger first end
Value h7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, the second end of indoor heat exchanger temperature t5The row of respectively obtaining
The refrigerant enthalpy h of gas port2With the refrigerant enthalpy h at the end of indoor heat exchanger second5。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, mixture enthalpy generation module 20 can be according to following public affairs
Formula is calculated：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy of gas returning port can be calculated out
Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second lubricating oil enthalpy h5 lubricating oilAnd indoor heat exchanger
The lubricating oil enthalpy h of first end7 lubricating oil。
Further, mixture enthalpy generation module 20 can calculate the mixture of each temperature detecting point according to below equation
Enthalpy hi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, the mixed of gas returning port can be calculated out
Compound enthalpy h1, exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second mixture enthalpy h5With indoor heat exchanger
The mixture enthalpy h of one end7。
In an embodiment of the present invention, heating capacity generation module 50 can generate the heating capacity of air conditioner according to below equation：Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor compressor horsepower.
Because the current working of air conditioner is heating condition, thus efficiency generation module 40 can be according to air conditioner power consumption
With the heat efficiency of heating capacity generation air conditioner, specifically, the heat efficiency of air conditioner is the heating capacity and power consumption work(of air conditioner
The ratio between rate, i.e. COP=QHeating capacity/PPower consumption。
, can also be according to 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 save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module
Condition, the power of compressor and air conditioner power consumption, and gas returning port in compressor, row are obtained by corresponding temperature sensor
Gas port, indoor heat exchanger middle part, the temperature of indoor heat exchanger first end and indoor environment temperature, and it is in system in air conditioner
During thermal condition by the second end of indoor heat exchanger temperature generation module, mixture enthalpy generation module, heating capacity generation module and
Efficiency generation module generates the refrigerant enthalpy and lubrication of multiple temperature detecting points according to the temperature of above-mentioned each temperature detecting point
Oily enthalpy, and the mixture enthalpy of multiple temperature detecting points is further generated, power, multiple temperature then in conjunction with compressor
The refrigerant enthalpy and air conditioner power consumption of test point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect
The efficiency of air conditioner, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve
The purpose of heating effect.
In summary, the air conditioner of the embodiment of the present invention and its efficiency computational methods and system, by obtaining air conditioner system
The physical property of refrigerant and the physical property of lubricating oil in refrigerant cycle system, and according to the mixing of refrigerant and lubricating oil
The power of air conditioner is calculated in the physical property of thing, and the efficiency of air conditioner is further calculated, so as to be able in real time
The heat efficiency of air conditioner is detected exactly.
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 " are based on orientation shown in the drawings
Or position relationship, it is for only for ease of the description present invention and simplifies description, rather than instruction or the device or element that imply meaning
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 instruction or hint relative importance
Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can be expressed or
Person implicitly includes one or more this feature.In the description of the invention, " multiple " be meant that two or two with
On, 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 machinery
Connection or electrical connection；Can be joined directly together, can also be indirectly connected by intermediary, can be two elements
Internal connection or the interaction relationship of two elements.For the ordinary skill in the art, can be according to specific
Situation 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 directly contact, or the first and second features pass through intermediary mediate contact.Moreover, fisrt feature
Second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only table
Show that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be
Fisrt feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height and is 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 specific features, structure, material or the spy for combining the embodiment or example description
Point is contained at least one embodiment or example of the present invention.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, this area
Technical staff can be carried out the different embodiments or example and the feature of different embodiments or example described in this specification
With reference to and combination.
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 (15)
1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；
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
Indoor heat exchanger middle portion temperature t in the middle part of device6, indoor heat exchanger first end indoor heat exchanger first end temperature t7With indoor ring
Border temperature t9；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor environment temperature t9Generation interior is changed
The second end of indoor heat exchanger temperature t at the hot end of device second5；
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 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures of exhaust outlet in the compressor
t2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the interior at the end of indoor heat exchanger second
The second end of heat exchanger temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilAnd basis
The indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end
h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1,
According to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to
The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixed of the end of indoor heat exchanger second
Compound enthalpy h5With the refrigerant enthalpy h according to the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration is indoor
The mixture enthalpy h of heat exchanger first end7；
According to the power of the compressor, the mixture enthalpy h of the gas returning port1, the exhaust outlet mixture enthalpy h2, institute
State the mixture enthalpy h at the end of indoor heat exchanger second5With the mixture enthalpy h of the indoor heat exchanger first end7Generate air conditioner
Heating capacity；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to gas returning port in the compressor
Gas returning port temperature t1Generate the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：
Obtain the 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 refrigerant。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that the suction is generated according to below equation
The enthalpy h of saturation refrigerant at a temperature of gasAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to 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：
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Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated by below equation
Interior the second end of heat exchanger temperature t5：
t5=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
6. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that according to exhaust outlet in the compressor
Exhaust port temperatures t2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsSpecifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor
Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy
Factor D2；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate the enthalpy of saturation refrigerant under delivery temperature
hIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw
Into the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
7. the efficiency computational methods of the air conditioner described in claim 6, it is characterised in that the exhaust is generated according to below equation
The modifying factor D of mouth refrigerant enthalpy2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6,
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
8. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that according to the indoor heat exchanger first
The indoor heat exchanger first end temperature t at end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor heat exchanger first end temperature t7It is raw
Into degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy
Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation refrigerant under the delivery temperature
Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerants。
9. the efficiency computational methods of air conditioner as claimed in claim 8, it is characterised in that the room is generated according to below equation
The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
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Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to calculating below equation
The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants：
h5 refrigerants=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating equation below
The heating capacity of air conditioner：
Wherein, QHeating capacityFor the heating capacity of the air conditioner, PCompressorFor the power of the compressor.
12. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each
The lubricating oil enthalpy h of temperature detecting pointI lubricating oil, wherein, i is positive integer,
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, tiFor the temperature of temperature detecting point.
13. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each
The mixture enthalpy h of temperature detecting pointi, wherein, i is positive integer,
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of the compressor.
14. 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, realize as in claim 1-13
Any described method.
15. 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 1-13 is realized when calculation machine program is executed by processor.
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