CN107576008A - Air conditioner and its efficiency computational methods - Google Patents
Air conditioner and its efficiency computational methods Download PDFInfo
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- CN107576008A CN107576008A CN201710775733.6A CN201710775733A CN107576008A CN 107576008 A CN107576008 A CN 107576008A CN 201710775733 A CN201710775733 A CN 201710775733A CN 107576008 A CN107576008 A CN 107576008A
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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 the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption；Obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end temperature t4, indoor heat exchanger middle portion temperature t6, compressor tonifying Qi temperature t8With indoor environment temperature t10；According to t6With the gas returning port temperature t of gas returning port in the running frequency generation compressor of compressor1, according to t10And t6Generate indoor heat exchanger first end temperature t7；When the current working of air conditioner is cooling condition, according to the temperature t of above-mentioned each temperature detecting point1、t2、t4、t7And t8Generate the refrigerant enthalpy of above-mentioned each temperature detecting point；The refrigerating capacity of air conditioner is generated according to the refrigerant enthalpy of the power of compressor, above-mentioned each temperature detecting point；And 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
As country increasingly payes attention to energy-conservation, consumer comfortably requires also more and more higher to the energy-conservation of air conditioner.Mesh
Before, during air conditioner is run, due to that can not detect the situation of change of energy efficiency of air conditioner in real time, thus air conditioner is difficult to tie up
Hold in preferable running status, so that refrigeration, 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, first purpose of the present invention is the efficiency computational methods for proposing a kind of air conditioner, can be accurate in real time
Ground detects 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, first aspect present invention embodiment proposes a kind of efficiency computational methods of air conditioner, bag
Include following steps：Obtain the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption work(
Rate；Obtain the exhaust port temperatures t of exhaust outlet in the compressor2, outdoor heat exchanger first end outdoor heat exchanger first end temperature
Spend t4, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6, compressor tonifying Qi entrance tonifying Qi temperature t8And indoor environment
Temperature t10；According to the indoor heat exchanger middle portion temperature t6With gas returning port in the running frequency generation compressor of the compressor
Gas returning port temperature t1, according to the indoor environment temperature t10With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger the
One end temperature t7；When the current working of the air conditioner is cooling condition, according to the gas returning port of gas returning port in the compressor
Temperature t1Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate exhaust outlet
Refrigerant enthalpy h2, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generate outdoor heat exchange
The refrigerant enthalpy h of device first end4, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate room
The refrigerant enthalpy h of interior heat exchanger first end7, and the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation is mended respectively
Enter the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the power of the compressor, institute
State the refrigerant enthalpy h of gas returning port1, the exhaust outlet refrigerant enthalpy h2, the outdoor heat exchanger first end refrigerant
Enthalpy h4, the indoor heat exchanger first end refrigerant enthalpy h7, the gaseous refrigerant enthalpy h for filling into compressor8’With
The liquid refrigerant enthalpy h of the flash vessel8”Generate the refrigerating capacity of air conditioner；And according to the air conditioner power consumption and institute
State the efficiency that refrigerating capacity generates the air conditioner.
The efficiency computational methods of air conditioner according to embodiments of the present invention, current working, the compression of air conditioner are obtained first
The power of machine, the running frequency of compressor and air conditioner power consumption, and obtain the exhaust port temperatures t of exhaust outlet in compressor2、
The outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6、
The tonifying Qi temperature t of compressor tonifying Qi entrance8With indoor environment temperature t10, and according to t6Pressure is generated with the running frequency of compressor
The gas returning port temperature t of gas returning port in contracting machine1, and according to t10And t6Generate indoor heat exchanger first end temperature t7, when working as air conditioner
When preceding operating mode is cooling condition, according to the temperature t of above-mentioned each temperature detecting point1、t2、t4、t7And t8Generate above-mentioned each temperature
The refrigerant enthalpy of test point, the refrigerant enthalpy and air-conditioning of power, above-mentioned each temperature detecting point then in conjunction with compressor
Device power consumption 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
The running status of the real-time energy efficiency optimization air conditioner 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, the gas returning port temperature t according to gas returning port in the compressor1Generation institute
State the refrigerant enthalpy h of gas returning port1Specifically include：According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6
Generate suction superheat Δ t1；According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy of saturation refrigerant under suction temperature
hAir-breathing saturation；According to the suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor of gas returning port refrigerant enthalpy
Sub- D1；According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the system
Cryogen enthalpy h1。
According to one embodiment of present invention, the enthalpy of saturation refrigerant under the suction temperature is generated according to below equation
hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
According to one embodiment of present invention, the modifying factor of the gas returning port refrigerant enthalpy is generated according to below equation
D1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end
Temperature 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 t7Changed with the interior
Hot device middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to the indoor heat exchanger
The modifying factor D of one end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7。
According to one embodiment of present invention, the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation
Modifying factor D7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation institute
State the enthalpy h of the refrigerant of 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 in the compressor
The exhaust port temperatures t of exhaust outlet2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to the exhaust
Degree of superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to described
Modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the enthalpy h of the refrigerant of the exhaust outlet2。
According to one embodiment of present invention, the modifying factor of the exhaust outlet refrigerant enthalpy is generated according to below equation
D2：
Wherein, d1-d6For overheated zone coefficient corresponding to 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 fauna number is subcooled corresponding to 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, PCompressorFor compressor horsepower.
To reach above-mentioned purpose, second aspect of the present invention embodiment proposes a kind of air conditioner, and it includes memory, processing
Device and the computer program that can be run on the memory and on the processor is stored in, meter described in the computing device
During calculation machine 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, third aspect present invention embodiment proposes a kind of non-transitory computer-readable storage medium
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 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 refrigeration.
To reach above-mentioned purpose, fourth aspect present invention embodiment proposes the efficiency computational methods of another air conditioner,
Comprise the following steps：Obtain the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption work(
Rate；Obtain the exhaust port temperatures t of exhaust outlet in the compressor2, outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3、
The second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6、
The tonifying Qi temperature t of compressor tonifying Qi entrance8With indoor environment temperature t10；According to the outdoor heat exchanger middle portion temperature t3With it is described
The gas returning port temperature t of gas returning port in the running frequency generation compressor of compressor1, according to the indoor environment temperature t10With it is described
Indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7；When the current working of the air conditioner is heating work
During condition, according to the gas returning port temperature t of gas returning port in the compressor1Generate the refrigerant enthalpy h of gas returning port1, according to the compression
The exhaust port temperatures t of exhaust outlet in machine2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the end of indoor heat exchanger second
The second end of indoor heat exchanger temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5, according to the indoor heat exchanger
The indoor heat exchanger first end temperature t of one end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7, and according to the pressure
The tonifying Qi temperature t of contracting machine tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor respectively8’With the liquid system of flash vessel
Cryogen enthalpy h8”；According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, 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、
The gaseous refrigerant enthalpy h for filling into compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the system of air conditioner
Heat；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, current working, the compression of air conditioner are obtained first
The power of machine, the running frequency of compressor and air conditioner power consumption, and obtain the exhaust port temperatures t of exhaust outlet in compressor2、
Outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5、
Indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6And indoor environment temperature t10, and according to t3With the fortune of compressor
The gas returning port temperature t of gas returning port in line frequency generation compressor1, according to t10And t6Generate indoor heat exchanger first end temperature t7, when
When the current working of air conditioner is heating condition, according to the temperature t of above-mentioned each temperature detecting point1、t2、t5、t7And t8In generation
The refrigerant enthalpy of each temperature detecting point is stated, power, the refrigerant of above-mentioned each temperature detecting point then in conjunction with compressor
Enthalpy and air conditioner power consumption obtain the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, from
And it is easy to optimize according to the real-time energy efficiency of air conditioner the running status of air conditioner, reach energy-conservation and improve the purpose of heating effect.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add
Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1Generation institute
State the refrigerant enthalpy h of gas returning port1Specifically include：According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3
Generate suction superheat Δ t1；According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate gas returning port
The modifying factor D of refrigerant enthalpy1；According to the outdoor heat exchanger middle portion temperature t3Generate saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy
hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
According to one embodiment of present invention, the enthalpy of saturation refrigerant under the suction temperature is generated according to below equation
hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
According to one embodiment of present invention, the modifying factor of the gas returning port refrigerant enthalpy is generated according to below equation
D1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation institute
State the enthalpy h of the refrigerant of exhaust outlet2Specifically include：According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6
With the exhaust port temperatures t of exhaust outlet in the compressor2Generate discharge superheat Δ t2；According to the discharge superheat Δ t2With
The indoor heat exchanger middle portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According in the outdoor heat exchanger
Portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the modifying factor of the exhaust outlet refrigerant enthalpy
Sub- D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2。
According to one embodiment of present invention, the modifying factor of the exhaust outlet refrigerant enthalpy is generated according to below equation
D2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end
Temperature t7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：In the middle part of the indoor heat exchanger
Indoor heat exchanger middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat
Δt7With the indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to
The modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy
hIt is vented saturationGenerate the refrigerant enthalpy h7。
According to one embodiment of present invention, the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation
Modifying factor D7：
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：
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.
To reach above-mentioned purpose, fifth aspect present invention embodiment proposes another air conditioner, and it includes memory, place
Manage device and be stored in the computer program that can be run on the memory and on the processor, described in the computing device
During computer program, the efficiency computational methods for the air conditioner that fifth 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, sixth aspect present invention embodiment proposes the computer-readable storage of another non-transitory
Medium, is stored thereon with computer program, and the computer program realizes that fifth aspect present invention is implemented when being executed by processor
The efficiency computational methods for the air conditioner that example proposes.
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 structural representation of air conditioner according to an embodiment of the invention；
Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention；And
Fig. 3 is the flow chart of the efficiency computational methods of air conditioner in accordance with another 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 is not considered as limiting the invention.
Efficiency computational methods, air conditioner, the non-transitory of the air conditioner of the embodiment of the present invention described below in conjunction with the accompanying drawings
The efficiency computing system of computer-readable recording medium and air conditioner.
In an embodiment of the present invention, air conditioner can be single-stage vapor compression formula air conditioner.
As shown in figure 1, the air conditioner of the embodiment of the present invention, it may include compressor 100, four-way valve 200, outdoor heat exchanger
300th, first throttle element 400, the second restricting element 700, flash vessel 600 and indoor heat exchanger 500.
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.Specifically, from compressor 100
Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A2 ends flow into outdoor heat exchanger 300 (now
As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after outdoor heat exchanger 300 condenses heat release
Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of second restricting element 700, low-temp low-pressure liquid refrigerants passes through flash vessel 600
First port flows into flash vessel 600, and a part of liquid refrigerants quickly becomes gaseous coolant in flash vessel 600, and from flash vessel
600 second port enters compressor 100 and carries out tonifying Qi to compressor 100, so as to improve air conditioner operating efficiency, remaining liquid
State refrigerant flows out from the 3rd port of flash vessel 600, and is getting in heat exchange after the reducing pressure by regulating flow of first throttle element 400
Device 500 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gas after the evaporation endothermic of indoor heat exchanger 500
A4 end of the state refrigerant through four-way valve 200 and A3 ends flow into the gas returning port of compressor 100, pass through the low of the gas returning port of compressor 100
Warm low-pressure gaseous refrigerant enters compressor 100, so far completes refrigerative circle system.
When the current working of air conditioner is heating condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and
A4 ends are directly connected with indoor heat exchanger 500, and refrigerant is flowed to as shown in the dotted arrow in Fig. 1.Specifically, from compressor 100
Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A4 ends flow into indoor heat exchanger 500 (now
As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after indoor heat exchanger 500 condenses heat release
Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of first throttle element 400, low-temp low-pressure liquid refrigerants passes through flash vessel 600
3rd port flows into flash vessel 600, and a part of liquid refrigerants quickly becomes gaseous coolant in flash vessel 600, and from flash vessel
600 second port enters compressor 100 and carries out tonifying Qi to compressor 100, so as to improve air conditioner operating efficiency, remaining liquid
State refrigerant flows out from the first port of flash vessel 600, and is entering outdoor heat exchange after the reducing pressure by regulating flow of the second restricting element 700
Device 300 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gas after the evaporation endothermic of outdoor heat exchanger 300
A2 end of the state refrigerant through four-way valve 200 and A3 ends flow into the gas returning port of compressor 100, pass through the low of the gas returning port of compressor 100
Warm low-pressure gaseous refrigerant enters compressor 100, so far completes heating cyclic process.
Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention.As shown in Fig. 2 this
The efficiency computational methods of the air conditioner of inventive embodiments, it may include following steps：
S101, obtain the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption work(
Rate.
Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner
PCompressor, compressor running frequency f and air conditioner power consumption PPower consumption。
S102, obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger
One end temperature t4, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6, compressor tonifying Qi entrance tonifying Qi temperature t8And room
Interior environment temperature t10。
In an embodiment of the present invention, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature
Spend the temperature of test point.
Specifically, as shown in figure 1, can be by setting the temperature sensor of exhaust outlet within the compressor (as shown in Figure 1
02) exhaust port temperatures t is obtained2；Obtained by the temperature sensor (as shown in Figure 1 04) for being disposed in the outdoor heat exchanger first end
Outdoor heat exchanger first end temperature t4；Obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger
Take indoor heat exchanger middle portion temperature t6；Obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi entrance
Take the tonifying Qi temperature t of compressor tonifying Qi entrance8With by being disposed in the interior the temperature sensor at heat exchanger fin (such as Fig. 1 institutes
10) that shows obtains indoor environment temperature t10。
Wherein, in above-mentioned each temperature sensor except the temperature sensor being disposed in the interior at heat exchanger fin, with
The refrigerant tube wall of corresponding temperature test point effectively contacts, and when testing the temperature of refrigerant tube wall, refrigerant tube wall can be taken
Insulation, the installation site of temperature sensor is as close to temperature detecting point.For example, temperature sensor can be set
In corresponding temperature detecting point and it is close to copper pipe, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve temperature
Spend the reliability and accuracy of detection.
S103, according to indoor heat exchanger middle portion temperature t6With time of gas returning port in the running frequency generation compressor of compressor
Gas port temperature t1, according to indoor environment temperature t10With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7。
According to one embodiment of present invention, can be according to following formula when the current working of air conditioner is cooling condition
(1) the gas returning port temperature t of gas returning port in compressor is generated1：
t1=a*t6+b*f (1)
Wherein, f is compressor operating frequency, and a, b are fitting coefficient, and a, b can obtain according to lot of experimental data.
According to another embodiment of the invention, indoor heat exchanger first end temperature t can be generated according to following formula (2)7：
t7=x*t10+y*t6+z*f (2)
Wherein, f is compressor operating frequency, and x, y, z is fitting coefficient, and x, y, z can obtain according to lot of experimental data
.
S104, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1
Generate the refrigerant enthalpy h of gas returning port1, 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 h7, and the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor respectively
Value h8’With the liquid refrigerant enthalpy h of flash vessel8”。
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room
External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room
The interior end of heat exchanger second is evaporator inlet.
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 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, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into compressor
Gaseous 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, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
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：According to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1, and
According to indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation, and according to suction superheat
Spend Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1, finally according to gas returning port system
The modifying factor D of cryogen enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (3)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, gas returning port temperature t is being got1With indoor heat exchanger middle portion temperature t6Afterwards, according to following formula (4)
Generate suction superheat Δ t1：
Δt1=t1-t6 (4)
Getting suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Afterwards, return-air is generated according to above-mentioned formula (3)
The modifying factor D of mouth refrigerant enthalpy1, then can be according to the enthalpy of saturation refrigerant under following formula (5) generation suction temperature
hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant
Enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to 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, the position refrigerant superheat degree can be combined 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, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchange
The modifying factor D of device first end refrigerant enthalpy7, and the modifying factor D according to indoor heat exchanger first end refrigerant enthalpy7
With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation (6)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, indoor heat exchanger first end temperature t is being got7With indoor heat exchanger middle portion temperature t6Afterwards, under
State formula (7) generation degree of superheat Δ t7：
Δt7=t7-t6 (7)
Getting degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Afterwards, interior can be generated according to above-mentioned formula (6) to change
The modifying factor D of hot device first end refrigerant enthalpy7, saturation under suction temperature then can be generated according to above-mentioned formula (5) and is freezed
The enthalpy h of agentAir-breathing saturation。
Finally, according to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7With the enthalpy of saturation refrigerant
hAir-breathing saturationGenerate refrigerant enthalpy h7, h7=D7·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
In addition, the refrigerant enthalpy h for exhaust outlet in compressor2, when the current working of air conditioner is cooling condition,
The refrigerant superheat of the exhaust outlet of compressor, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
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, and according to outdoor heat exchanger
Middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation, then according to the exhaust outlet of exhaust outlet in compressor
Temperature t2With outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2, subsequently according to discharge superheat Δ t2And outdoor
Heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2, finally according to modifying factor D2, under delivery temperature
The enthalpy h of saturation refrigerantIt 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 below equation (8)2：
Wherein, d1-d6For overheated zone coefficient corresponding to 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。
The exhaust port temperatures t of exhaust outlet in compressor is got2With outdoor heat exchanger middle portion temperature t3Afterwards, can be under
State formula (9) generation discharge superheat Δ t2：
Δt2=t2-t3 (9)
Getting discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Afterwards, generated and be vented according to above-mentioned formula (8)
The modifying factor D of mouth refrigerant enthalpy2, then according to the enthalpy of saturation refrigerant under following formula (10) generation delivery temperature
hIt is vented saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturation
Generate the enthalpy h of the refrigerant of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to 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, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4, i.e. according to
The refrigerant enthalpy h of lower formula (11) generation outdoor heat exchanger first end4：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, based on same principle, the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid system of flash vessel
Cryogen enthalpy h8”, the gaseous refrigerant enthalpy h of compressor can be calculated by following formula (12)8’, pass through following formula
(13) the liquid refrigerant enthalpy h of flash vessel is calculated8”。
Wherein, a1-a5For the saturation region coefficient corresponding to refrigerant, c1-c4For fauna number is subcooled corresponding to refrigerant.
It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system
The species of cryogen is relevant, and R410A refrigerants and saturation region coefficient, overheated zone corresponding to R32 refrigerants are respectively illustrated in table 1
Coefficient and supercooling 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 be according to sky when the current working of air conditioner is cooling condition
Adjust low pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port
h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room
External heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy of outdoor heat exchanger first end
h4, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure8’And saturated liquid enthalpy h8”。
S105, according to the power of compressor, the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, it is outdoor
The refrigerant enthalpy h of heat exchanger first end4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant of compressor
Agent enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the refrigerating capacity of air conditioner.
According to one embodiment of present invention, the refrigerating capacity of air conditioner can be generated according to below equation (14)：
Wherein, QRefrigerating capacityFor Air conditioner refrigerating capacity, PCompressorFor 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 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 the refrigerating capacity of air conditioner and power consumption, i.e. EER=
QRefrigerating capacity/PPower consumption。
, can also be according to 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 save, additionally it is possible to improve the comfortableness of user.
To sum up, the efficiency computational methods of air conditioner according to embodiments of the present invention, the first current working of acquisition air conditioner,
The power of compressor, the running frequency of compressor and air conditioner power consumption, and obtain the exhaust outlet temperature of exhaust outlet in compressor
Spend t2, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4, temperature in the middle part of indoor heat exchanger in the middle part of indoor heat exchanger
Spend t6, compressor tonifying Qi entrance tonifying Qi temperature t8With indoor environment temperature t10, and according to t6Given birth to the running frequency of compressor
The gas returning port temperature t of gas returning port into compressor1, and according to t10And t6Generate indoor heat exchanger first end temperature t7, work as air conditioner
Current working when being cooling condition, according to the temperature t of above-mentioned each temperature detecting point1、t2、t4、t7And t8Generate above-mentioned each
The refrigerant enthalpy of temperature detecting point, the refrigerant enthalpy of power, above-mentioned each temperature detecting point then in conjunction with compressor and
Air conditioner power consumption obtains the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating
Optimize the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the purpose of refrigeration.
In addition, embodiments of the invention also proposed a kind of air conditioner, it includes memory, processor and is stored in storage
On device and the computer program that can run on a processor, during computing device computer program, the above-mentioned implementation of the present invention is realized
The efficiency computational methods for the air conditioner that example proposes.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
In addition, embodiments of the invention also proposed a kind of non-transitorycomputer readable storage medium, it is stored thereon with
Computer program, realize that the efficiency for the air conditioner that the above embodiment of the present invention proposes calculates when computer program is executed by processor
Method.
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 refrigeration.
The air conditioner and its efficiency computational methods of above-described embodiment can detect the refrigeration efficiency of air conditioner, to detect air-conditioning
The heat efficiency of device, the present invention also propose the efficiency computational methods of another air conditioner.
Fig. 3 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention.As shown in figure 3,
The efficiency computational methods of the air conditioner of the embodiment of the present invention may include following steps：
S201, obtain the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption work(
Rate.
Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner
PCompressor, the running frequency f of compressor and air conditioner power consumption PPower consumption。
S202, obtain the exhaust port temperatures t of exhaust outlet in compressor2, in the middle part of outdoor heat exchanger in the middle part of outdoor heat exchanger
Temperature t3, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, in the middle part of indoor heat exchanger in the middle part of indoor heat exchanger
Temperature t6, compressor tonifying Qi entrance tonifying Qi temperature t8With indoor environment temperature t10。
In an embodiment of the present invention, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature
Spend the temperature of test point.
Specifically, as shown in figure 1, can be by setting the temperature sensor of exhaust outlet within the compressor (as shown in Figure 1
02) exhaust port temperatures t is obtained2；Room is 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；Obtained by the temperature sensor (as shown in Figure 1 05) for being disposed in the interior the end of heat exchanger second
Take the second end of indoor heat exchanger temperature t5；Can be (as shown in Figure 1 by being disposed in the interior temperature sensor in the middle part of heat exchanger
06) indoor heat exchanger middle portion temperature t is obtained6；It is (as shown in Figure 1 by the temperature sensor for being arranged on compressor tonifying Qi entrance
08) the tonifying Qi temperature t of compressor tonifying Qi entrance is obtained8；By being disposed in the interior the temperature sensor at heat exchanger fin (as schemed
Indoor environment temperature t 10) is obtained shown in 110。
Wherein, in above-mentioned each temperature sensor except the temperature sensor being disposed in the interior at heat exchanger fin, with
The refrigerant tube wall of corresponding temperature test point effectively contacts, and when testing the temperature of refrigerant tube wall, refrigerant tube wall can be taken
Insulation, the installation site of temperature sensor is as close to temperature detecting point.For example, temperature sensor can be set
In corresponding temperature detecting point and it is close to copper pipe, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve temperature
Spend the reliability and accuracy of detection.
S203, according to outdoor heat exchanger middle portion temperature t3With time of gas returning port in the running frequency generation compressor of compressor
Gas port temperature t1, according to indoor environment temperature t10With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7。
According to one embodiment of present invention, can be according to following formula when the current working of air conditioner is heating condition
(15) gas returning port temperature t is generated1：
t1=c*t3+d*f (15)
Wherein, f is compressor operating frequency, and c, d are fitting coefficient, and c, d can obtain according to lot of experimental data.
According to another embodiment of the invention, indoor heat exchanger first end temperature can be generated according to above-mentioned formula (2)
t7, i.e. t7=x*t10+y*t6+ z*f, wherein, f is compressor operating frequency, and x, y, z is fitting coefficient, and x, y, z can bases
Lot of experimental data obtains.
S204, 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 h7, and the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor respectively
Value h8’With the liquid refrigerant enthalpy h of flash vessel8”。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room
Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
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 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 end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy h7, fill into compressor
Gaseous 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, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
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：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, finally according to gas returning port system
The modifying factor D of cryogen enthalpy1, under suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of gas returning port1。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to below equation (16)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, gas returning port temperature t is being got1With outdoor heat exchanger middle portion temperature t3Afterwards, according to following formula (17)
Generate suction superheat Δ t1：
Δt1=t1-t3 (17)
Getting suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Afterwards, according to above-mentioned formula (16) gas returning port
The modifying factor D of refrigerant enthalpy1, then can be according to the enthalpy of saturation refrigerant under following formula (18) generation suction temperature
hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, under suction temperature saturation refrigerant enthalpy hAir-breathing saturation
Generate the refrigerant enthalpy h of gas returning port1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to 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, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
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：Indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With exhaust outlet in compressor
Exhaust port temperatures t2Generate discharge superheat Δ t2, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6It is raw
Into the modifying factor D of exhaust outlet refrigerant enthalpy value2, and according to outdoor heat exchanger middle portion temperature t6Generate saturation under delivery temperature
The enthalpy h of refrigerantIt is vented saturation, finally according to the modifying factor D of exhaust outlet refrigerant enthalpy2, saturation refrigerant under delivery temperature
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 below equation (19)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger is being got6With exhaust outlet in compressor
Exhaust port temperatures t2Afterwards, discharge superheat Δ t can be generated according to following formula (20)2：
Δt2=t2-t6 (20)
Getting discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Afterwards, generated and arranged according to above-mentioned formula (19)
The modifying factor D of gas port refrigerant enthalpy2, then can be according to the enthalpy of saturation refrigerant under following formula (21) generation delivery temperature
Value hIt is vented saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
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 overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work
During condition, the refrigerant superheat of indoor heat exchanger first end, the position refrigerant superheat degree can be combined 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 end7Point
Not Sheng Cheng indoor heat exchanger first end refrigerant enthalpy h7Specifically include：In indoor heat exchanger in the middle part of indoor heat exchanger
Portion temperature t6With indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7, and according to degree of superheat Δ t7In indoor heat exchanger
Portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7, and according to indoor heat exchanger first end system
The modifying factor D of cryogen enthalpy7, 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 below equation (22)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger is being got6With indoor heat exchanger first
Hold temperature t7Afterwards, degree of superheat Δ t is generated according to following formula (23)7：
Δt7=t7-t6 (23)
Getting degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Afterwards, can be generated according to above-mentioned formula (22) indoor
The modifying factor D of heat exchanger first end refrigerant enthalpy7, then saturation system under delivery temperature can be generated according to above-mentioned formula (21)
The enthalpy h of cryogenIt is vented saturation。
Finally, according to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7With the enthalpy of saturation refrigerant
hIt is vented saturationGenerate refrigerant enthalpy h7, h7=D7·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
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, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5, i.e. according to
Lower formula meter (24) calculates the refrigerant enthalpy h at the end of indoor heat exchanger second5：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, in one embodiment of the invention, the gaseous refrigerant enthalpy h for filling into compressor8’And flash vessel
Liquid refrigerant enthalpy h8”, the gaseous refrigerant enthalpy h of compressor can be calculated by above-mentioned formula (12)8’, by upper
State the liquid refrigerant enthalpy h that flash vessel is calculated in formula (13)8”, i.e., Wherein, a1-a5For the saturation region coefficient corresponding to refrigerant, c1-c4For mistake corresponding to refrigerant
Cold-zone coefficient.
It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system
The species of cryogen is relevant, respectively illustrated in above-mentioned table 1 R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants,
Overheated zone coefficient and supercooling 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, the result of calculation of software can be also directly invoked, or is obtained by other approach
The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is heating condition
Adjust high-pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port
h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room
Interior the second end of heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy at the end of indoor heat exchanger second
h5, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure8’And saturated liquid enthalpy h8”。
S205, according to the power of compressor, the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, it is indoor
The refrigerant enthalpy h at the end of heat exchanger second5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant of compressor
Agent enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner.
According to one embodiment of present invention, the heating capacity of air conditioner is generated according to equation below (25)：
Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor 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 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.
To sum up, the efficiency computational methods of air conditioner according to embodiments of the present invention, the first current working of acquisition air conditioner,
The power of compressor, the running frequency of compressor and air conditioner power consumption, and obtain the exhaust outlet temperature of exhaust outlet in compressor
Spend t2, outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature
Spend t5, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6And indoor environment temperature t10, and according to t3And compressor
Running frequency generation compressor in gas returning port gas returning port temperature t1, according to t10And t6Generate indoor heat exchanger first end temperature
t7, when the current working of air conditioner is heating condition, according to the temperature t of above-mentioned each temperature detecting point1、t2、t5、t7And t8It is raw
Into the refrigerant enthalpy of above-mentioned each temperature detecting point, power, the system of above-mentioned each temperature detecting point then in conjunction with compressor
Cryogen enthalpy and air conditioner power consumption obtain the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the energy of air conditioner
Effect, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve heating effect
Purpose.
In addition, embodiments of the invention also proposed another air conditioner, it includes memory, processor and is stored in
On reservoir and the computer program that can run on a processor, during computing device computer program, the invention described above reality is realized
Apply the efficiency computational methods of the air conditioner of example proposition.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
In addition, embodiments of the invention also proposed another non-transitorycomputer readable storage medium, store thereon
There is computer program, the efficiency meter for the air conditioner that the above embodiment of the present invention proposes is realized when computer program is executed by processor
Calculation method.
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.
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, it is for only for ease of and describes the present invention and simplify description, rather than indicates or imply that signified device or element 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 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
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 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 directly contact, 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 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, the skill of this area
Art personnel can be tied the different embodiments or example and the feature of different embodiments 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 the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption；
Obtain the exhaust port temperatures t of exhaust outlet in the compressor2, outdoor heat exchanger first end outdoor heat exchanger first end temperature
Spend t4, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6, compressor tonifying Qi entrance tonifying Qi temperature t8And indoor environment
Temperature t10；
According to the indoor heat exchanger middle portion temperature t6With the return-air of gas returning port in the running frequency generation compressor of the compressor
Mouth temperature t1, according to the indoor environment temperature t10With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end
Temperature t7；
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 end7, and the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into compressor respectively
Gaseous refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h of the outdoor heat exchanger first end4, the indoor heat exchanger first end refrigerant enthalpy h7, described fill into
The gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the refrigerating capacity of air conditioner；With
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 described to be returned according in the compressor
The gas returning port temperature t of gas port1Generate the refrigerant enthalpy h of the gas returning port1Specifically include：
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 indoor heat exchanger middle portion temperature t6Generate the modifying factor of gas returning port refrigerant enthalpy
D1；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigeration
Agent enthalpy h1。
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：
<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>6</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>6</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>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>1</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 overheated zone coefficient corresponding to refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 3, it is characterised in that described according to the indoor heat exchanger
The indoor heat exchanger first end temperature t of first 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 the room is generated according to below equation
The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
<mrow>
<msub>
<mi>D</mi>
<mn>7</mn>
</msub>
<mo>=</mo>
<mn>1</mn>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>1</mn>
</msub>
<msub>
<mi>&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 overheated zone coefficient corresponding to refrigerant.
7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be arranged according in the compressor
The exhaust port temperatures t of gas port2Generate 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 overheated zone coefficient corresponding to 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：
<mrow>
<msub>
<mi>h</mi>
<mn>4</mn>
</msub>
<mo>=</mo>
<msub>
<mi>c</mi>
<mn>1</mn>
</msub>
<mo>+</mo>
<msub>
<mi>c</mi>
<mn>2</mn>
</msub>
<msub>
<mi>t</mi>
<mn>4</mn>
</msub>
<mo>+</mo>
<msub>
<mi>c</mi>
<mn>3</mn>
</msub>
<msubsup>
<mi>t</mi>
<mn>4</mn>
<mn>2</mn>
</msubsup>
<mo>+</mo>
<msub>
<mi>c</mi>
<mn>4</mn>
</msub>
<msubsup>
<mi>t</mi>
<mn>4</mn>
<mn>3</mn>
</msubsup>
<mo>,</mo>
</mrow>
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation
The refrigerating capacity of air conditioner：
Wherein, QRefrigerating capacityFor the Air conditioner refrigerating capacity, PCompressorFor 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, realize 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 the current working of air conditioner, the power of compressor, the running frequency of compressor and air conditioner power consumption；
Obtain the exhaust port temperatures t of exhaust outlet in the compressor2, outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3、
The second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6、
The tonifying Qi temperature t of compressor tonifying Qi entrance8With indoor environment temperature t10；
According to the outdoor heat exchanger middle portion temperature t3With the return-air of gas returning port in the running frequency generation compressor of the compressor
Mouth temperature t1, according to the indoor environment temperature t10With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end
Temperature t7；
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 end7, and the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into compressor respectively
Gaseous refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h at the end of indoor heat exchanger second5, the indoor heat exchanger first end refrigerant enthalpy h7, described fill into
The gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the heating capacity of air conditioner；With
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 described according in the compressor
The gas returning port temperature t of gas returning port1Generate the refrigerant enthalpy h of the gas returning port1Specifically include：
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 generating below equation
The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
16. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to generating below equation
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 overheated zone coefficient corresponding to refrigerant.
17. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that described according in the compressor
The exhaust port temperatures t of exhaust outlet2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically 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 outdoor 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 overheated zone coefficient corresponding to refrigerant.
19. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that described according to the indoor heat exchange
The indoor heat exchanger first end temperature t of device first end7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specific bag
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 h7。
20. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that according to generating below equation
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 overheated zone coefficient corresponding to refrigerant.
21. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to calculating below equation
The refrigerant enthalpy h at the end of indoor heat exchanger second5：
<mrow>
<msub>
<mi>h</mi>
<mn>5</mn>
</msub>
<mo>=</mo>
<msub>
<mi>c</mi>
<mn>1</mn>
</msub>
<mo>+</mo>
<msub>
<mi>c</mi>
<mn>2</mn>
</msub>
<msub>
<mi>t</mi>
<mn>5</mn>
</msub>
<mo>+</mo>
<msub>
<mi>c</mi>
<mn>3</mn>
</msub>
<msubsup>
<mi>t</mi>
<mn>5</mn>
<mn>2</mn>
</msubsup>
<mo>+</mo>
<msub>
<mi>c</mi>
<mn>4</mn>
</msub>
<msubsup>
<mi>t</mi>
<mn>5</mn>
<mn>3</mn>
</msubsup>
<mo>,</mo>
</mrow>
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
22. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to generating equation below
The heating capacity of air conditioner：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor 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, realize 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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