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CN114396710A - Air conditioner and energy efficiency calculation method thereof - Google Patents

Air conditioner and energy efficiency calculation method thereof Download PDF

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Publication number
CN114396710A
CN114396710A CN202210006323.6A CN202210006323A CN114396710A CN 114396710 A CN114396710 A CN 114396710A CN 202210006323 A CN202210006323 A CN 202210006323A CN 114396710 A CN114396710 A CN 114396710A
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refrigerant
heat exchanger
temperature
air conditioner
enthalpy value
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Chinese (zh)
Inventor
刘燕飞
李金波
戚文端
杨亚新
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GD Midea Air Conditioning Equipment Co Ltd
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GD Midea Air Conditioning Equipment Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/50—Load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/60—Energy consumption

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Signal Processing (AREA)
  • Physics & Mathematics (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The invention discloses an air conditioner and an energy efficiency calculation method thereof, wherein the method comprises the following steps: acquiring the current working condition of the air conditioner, the power of a compressor and the power consumption of the air conditioner; obtaining the shell heat dissipation Q of the compressorloss(ii) a Obtaining the temperature t of the exhaust port of the compressor, the first end of the outdoor heat exchanger and the middle part of the indoor heat exchanger2、t4、t6And indoor ambient temperature t9(ii) a According to t9And t4Generating return port temperature of return port in compressorDegree t1And according to t9And t6Generating a first end temperature t of the indoor heat exchanger7(ii) a When the current working condition is a refrigeration working condition, according to t1、t2、t4And t7Correspondingly generating the enthalpy values of the refrigerant and the lubricating oil of the return air port, the exhaust port, the first end of the outdoor heat exchanger and the first end of the indoor heat exchanger; generating a mixture enthalpy value of each position according to the enthalpy value of the refrigerant and the enthalpy value of the lubricating oil; according to compressor power, QlossGenerating the refrigerating capacity of the air conditioner by the enthalpy value of each mixture; and generating the energy efficiency of the air conditioner according to the consumed power and the refrigerating capacity of the air conditioner.

Description

Air conditioner and energy efficiency calculation method thereof
The application is a divisional application of patent applications with application dates of 2017, 8 and 31, application number of 201710772917.7 and invented name of "air conditioner and energy efficiency calculation method thereof".
Technical Field
The invention relates to the technical field of air conditioners, in particular to an energy efficiency calculation method of an air conditioner, the air conditioner and a non-transitory computer readable storage medium.
Background
Whether the air conditioner is energy-saving and comfortable is a concern of users.
The current air conditioner is difficult to maintain in a better running state because the change condition of energy efficiency can not be known during running, and the refrigerating and heating effect and the energy-saving performance are not ideal enough.
Disclosure of Invention
The present invention is directed to solving, at least to some extent, one of the technical problems in the art described above. Therefore, an object of the present invention is to provide an energy efficiency calculation method for an air conditioner, which can accurately detect the energy efficiency of the air conditioner in real time.
The second purpose of the invention is to provide an air conditioner.
A third object of the invention is to propose a non-transitory computer-readable storage medium.
A fourth object of the present invention is to provide another energy efficiency calculation method for an air conditioner.
A fifth object of the present invention is to provide another air conditioner.
A sixth object of the invention is to propose another non-transitory computer-readable storage medium.
In order to achieve the above object, an energy efficiency calculation method for an air conditioner according to an embodiment of a first aspect of the present invention includes the following steps: acquiring the current working condition of the air conditioner, the power of a compressor and the power consumption of the air conditioner; obtaining the shell heat dissipation Q of the compressorloss(ii) a Obtaining a discharge port temperature t of a discharge port in a compressor2The temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4And the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And indoor ambient temperature t9(ii) a According to the indoor ambient temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1And according to the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7(ii) a When the current working condition of the air conditioner is a refrigeration working condition, according to the return air port temperature t of the return air port in the compressor1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4Generating a refrigerant enthalpy h at a first end of an outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oil(ii) a According to the enthalpy value h of the refrigerant at the air return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGeneratingMixture enthalpy h of exhaust port2According to the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilGenerating the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7(ii) a According to the power of the compressor and the shell heat dissipation Q of the compressorlossThe enthalpy value h of the mixture of the air return port1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the refrigerating capacity of the air conditioner; and generating the energy efficiency of the air conditioner according to the consumed power of the air conditioner and the refrigerating capacity.
According to the energy efficiency calculation method of the air conditioner, the current working condition of the air conditioner, the power of the compressor, the power consumption of the air conditioner and the shell heat dissipation Q of the compressor are obtainedlossAnd obtaining the temperatures of the return air port, the exhaust port, the first end of the outdoor heat exchanger and the first end of the indoor heat exchanger in the compressor, generating the enthalpy value of the refrigerant and the enthalpy value of the lubricating oil at each position according to the temperatures at each position when the air conditioner is in a refrigeration working condition, further generating the enthalpy value of a mixture at each position, and then combining the power of the compressor and the heat dissipation capacity Q of the shell of the compressorlossThe energy efficiency of the air conditioner is obtained through the enthalpy value of the mixture at each position and the power consumption of the air conditioner, so that the energy efficiency of the air conditioner can be accurately detected in real time, the running state of the air conditioner is conveniently optimized according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the refrigeration effect are achieved.
In addition, the energy efficiency calculation method for the air conditioner according to the above embodiment of the present invention may further have the following additional technical features:
according to one embodiment of the invention, the return port temperature t of the return port in the compressor is determined according to the temperature of the return port1Generating the enthalpy h of the refrigerant at the return port1 refrigerantThe method specifically comprises the following steps: obtainingTemperature t of middle part of indoor heat exchanger in middle part of indoor heat exchanger6(ii) a According to the temperature t of the return air port1And the temperature t of the middle part of the indoor heat exchanger6Generating degree of superheat Δ t of intake air1(ii) a According to the degree of superheat delta t of the suction gas1And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of return air port refrigerant1(ii) a According to the middle temperature t of the indoor heat exchanger6Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration(ii) a Correction factor D according to enthalpy value of return air port refrigerant1An enthalpy value h of the saturated refrigerantSaturation of inspirationGenerating an enthalpy h of said refrigerant1 refrigerant. Further, the enthalpy value h of the saturated refrigerant at the suction temperature is generated according to the following formulaSaturation of inspiration：hSaturation of inspiration＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Further, the enthalpy value h of the saturated refrigerant at the suction temperature is generated according to the following formulaSaturation of inspiration：
hSaturation of inspiration＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Further, a correction factor D of the enthalpy value of the return air port refrigerant is generated according to the following formula1：
D1＝1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Further, the refrigerant enthalpy value h is generated according to the following formula1 refrigerant：h1 refrigerant＝D1·hSaturation of inspiration+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
Further, the temperature t of the first end of the indoor heat exchanger at the first end of the indoor heat exchanger is determined according to the temperature t of the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantThe method specifically comprises the following steps: according to the temperature t of the first end of the indoor heat exchanger7And the temperature t of the middle part of the indoor heat exchanger6To generate a degree of superheat Deltat7(ii) a According to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7(ii) a Correction factor D according to enthalpy value of refrigerant at first end of indoor heat exchanger7And the enthalpy value h of the saturated refrigerantSaturation of inspirationGenerating an enthalpy h of said refrigerant7 refrigerant。
Further, a correction factor D of the enthalpy value of the refrigerant at the first end of the indoor heat exchanger is generated according to the following formula7：
Figure BDA0003456932000000021
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Further, the refrigerant enthalpy value h is generated according to the following formula7 refrigerant：h7 refrigerant＝D7·hSaturation of inspiration+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
According to an embodiment of the present invention, the temperature t of the discharge port is determined according to the discharge port temperature t of the discharge port in the compressor2Generating an enthalpy h of the refrigerant at the exhaust port2 refrigerantThe method specifically comprises the following steps: acquiring the middle temperature t of the outdoor heat exchanger at the middle part of the outdoor heat exchanger3(ii) a According to the exhaust port temperature t of the exhaust port in the compressor2And the temperature t of the middle part of the outdoor heat exchanger3Generating exhaust superheat degree Deltat2(ii) a According to the superheat degree delta t of the exhaust gas2And the temperature t of the middle part of the outdoor heat exchanger3Generate rowsCorrection factor D of air port refrigerant enthalpy value2: according to the middle temperature t of the outdoor heat exchanger3Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation(ii) a Correction factor D based on enthalpy of refrigerant at said exhaust port2An enthalpy value h of the saturated refrigerant at the discharge temperatureExhaust gas saturationGenerating an enthalpy h of the refrigerant at the exhaust port2 refrigerant。
Further, a correction factor D for the enthalpy of the outlet refrigerant is generated according to the following formula2：
D2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Further, the refrigerant enthalpy value h is generated according to the following formula2 refrigerant：h2 refrigerant＝D2·hExhaust gas saturation+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
According to one embodiment of the invention, the refrigerant enthalpy h at the first end of the outdoor heat exchanger is generated according to the following formula4 refrigerant：
Figure BDA0003456932000000022
Wherein, c1-c4Is the corresponding supercooling coefficient of the refrigerant.
According to one embodiment of the present invention, the cooling capacity of the air conditioner is generated according to the following formula:
Figure BDA0003456932000000023
wherein Q isRefrigerating capacityFor the cooling capacity of the air conditioner, PCompressorIs the compressor power.
According to one embodiment of the invention, according to the following disclosureCalculating the enthalpy value h of the lubricating oil at each temperature detection point by the formulai lubricating oilWherein i is a positive integer,
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 iWherein, tiIs the temperature at the temperature detection point.
According to one embodiment of the invention, the enthalpy value h of the mixture at each temperature detection point is calculated according to the following formulaiWherein i is a positive integer, hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor.
According to one embodiment of the present invention, the shell heat dissipation Q of the compressor is generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8) Wherein A isCompressorT8 is the temperature at the outdoor heat exchanger fins, which is the surface area of the compressor shell.
According to one embodiment of the invention, the return air port temperature t is generated according to the following formula1And the temperature t of the first end of the indoor heat exchanger7：
Figure BDA0003456932000000031
Wherein f is the operating frequency of the compressor, and a, b and c are fitting coefficients.
In order to achieve the above object, an air conditioner according to an embodiment of a second aspect of the present invention includes a memory, a processor, and a computer program stored in the memory and executable on the processor, where the processor executes the computer program to implement the method for calculating the energy efficiency of the air conditioner according to the embodiment of the first aspect of the present invention.
According to the air conditioner provided by the embodiment of the invention, the energy efficiency can be accurately detected in real time.
To achieve the above object, a non-transitory computer-readable storage medium according to an embodiment of a third aspect of the present invention stores thereon a computer program, and the computer program, when executed by a processor, implements the energy efficiency calculation method for an air conditioner according to an embodiment of the first aspect of the present invention.
According to the non-transitory computer readable storage medium of the embodiment of the invention, the stored computer program is executed, so that the energy efficiency of the air conditioner can be accurately detected in real time, the running state of the air conditioner can be conveniently optimized according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the refrigeration effect are achieved.
In order to achieve the above object, another energy efficiency calculation method for an air conditioner according to a fourth aspect of the present invention includes the following steps: acquiring the current working condition of the air conditioner, the power of a compressor and the power consumption of the air conditioner; obtaining the shell heat dissipation Q of the compressorloss(ii) a Obtaining a discharge port temperature t of a discharge port in a compressor2And the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5And the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And indoor ambient temperature t9(ii) a According to the indoor ambient temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1And according to the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7(ii) a When the current working condition of the air conditioner is a heating working condition, the temperature t of the return air port in the compressor is determined according to the temperature t of the return air port1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5Generating a refrigerant enthalpy h at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubrication ofOilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oil(ii) a According to the enthalpy value h of the refrigerant at the air return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilGenerating the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7(ii) a According to the power of the compressor and the shell heat dissipation Q of the compressorlossThe enthalpy value h of the mixture of the air return port1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the heating capacity of the air conditioner; and generating the energy efficiency of the air conditioner according to the consumed electric power of the air conditioner and the heating quantity.
According to the energy efficiency calculation method of the air conditioner, the current working condition of the air conditioner, the power of the compressor, the power consumption of the air conditioner and the shell heat dissipation Q of the compressor are obtainedlossAnd obtaining the temperatures of the return air port, the exhaust port, the second end of the indoor heat exchanger and the first end of the indoor heat exchanger in the compressor, generating the enthalpy value of the refrigerant and the enthalpy value of the lubricating oil at each position according to the temperatures at each position when the air conditioner is in a heating working condition, further generating the enthalpy value of a mixture at each position, and then combining the power of the compressor and the heat dissipation capacity Q of the shell of the compressorlossThe energy efficiency of the air conditioner is obtained according to the enthalpy value of the mixture at each position and the power consumption of the air conditioner, so that the energy efficiency of the air conditioner can be accurately detected in real time, and convenience is brought to the air conditionerThe running state of the air conditioner is optimized in real time and energy efficiency, and the purposes of saving energy and improving heating effect are achieved.
In addition, the energy efficiency calculation method for the air conditioner according to the above embodiment of the present invention may further have the following additional technical features:
according to one embodiment of the invention, said temperature t of the return port in said compressor is dependent on the return port temperature t1Generating the enthalpy h of the refrigerant at the return port1 refrigerantThe method specifically comprises the following steps: acquiring the middle temperature t of the outdoor heat exchanger at the middle part of the outdoor heat exchanger3(ii) a According to the temperature t of the return air port1And the temperature t of the middle part of the outdoor heat exchanger3Generating degree of superheat Δ t of intake air1(ii) a According to the degree of superheat delta t of the suction gas1And the temperature t of the middle part of the outdoor heat exchanger3Correction factor D for generating enthalpy value of return air port refrigerant1(ii) a According to the middle temperature t of the outdoor heat exchanger3Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration(ii) a Correction factor D according to enthalpy value of return air port refrigerant1The enthalpy value h of the saturated refrigerant at the suction temperatureSaturation of inspirationGenerating the enthalpy value h of the refrigerant at the air return port1 refrigerant。
Further, the enthalpy value h of the saturated refrigerant at the suction temperature is generated according to the following formulaSaturation of inspiration：
Figure BDA0003456932000000041
Wherein, a1-a5Is the saturation area coefficient corresponding to the refrigerant.
Further, a correction factor D of the enthalpy value of the return air port refrigerant is generated according to the following formula1：
Figure BDA0003456932000000042
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Further, the refrigerant enthalpy value h is generated according to the following formula1 refrigerant：h1 refrigerant＝D1·hSaturation of inspiration+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
Further, the temperature t of the exhaust port in the compressor is determined2Generating an enthalpy h of the refrigerant at the exhaust port2 refrigerantThe method specifically comprises the following steps: acquiring middle temperature t of indoor heat exchanger in middle of indoor heat exchanger6(ii) a According to the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And a discharge port temperature t of a discharge port in the compressor2Generating exhaust superheat degree Deltat2(ii) a According to the superheat degree delta t of the exhaust gas2And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy of exhaust port refrigerant2(ii) a According to the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation(ii) a Correction factor D based on enthalpy of refrigerant at said exhaust port2An enthalpy value h of the saturated refrigerant at the discharge temperatureExhaust gas saturationGenerating an enthalpy h of the refrigerant at the exhaust port2 refrigerant。
Further, a correction factor D for the enthalpy of the outlet port refrigerant is generated according to the following formula2：
D2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Further, the refrigerant enthalpy value h is generated according to the following formula2 refrigerant：h2 refrigerant＝D2·hExhaust gas saturation+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
Further, the temperature t of the first end of the indoor heat exchanger is determined according to the temperature t of the first end of the indoor heat exchanger7Respectively generateThe enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantThe method specifically comprises the following steps: according to the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And the temperature t of the first end of the indoor heat exchanger7To generate a degree of superheat Deltat7(ii) a According to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7(ii) a Correction factor D according to enthalpy value of refrigerant at first end of indoor heat exchanger7An enthalpy value h of the saturated refrigerant at the discharge temperatureExhaust gas saturationGenerating a refrigerant enthalpy h for the first end of the indoor heat exchanger7 refrigerant。
Further, a correction factor D of the enthalpy value of the refrigerant at the first end of the indoor heat exchanger is generated according to the following formula7：
Figure BDA0003456932000000043
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Further, the refrigerant enthalpy value h is generated according to the following formula7 refrigerant：h7 refrigerant＝D7·hExhaust gas saturation+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
According to one embodiment of the invention, the enthalpy h of the refrigerant at the second end of the indoor heat exchanger is calculated according to the following formula5 refrigerant：
h5 refrigerant＝c1+c2t5+c3t2 5+c4t3 5Wherein c is1-c4Is the corresponding supercooling coefficient of the refrigerant.
According to one embodiment of the present invention, the heating capacity of the air conditioner is generated according to the following formula:
Figure BDA0003456932000000044
wherein Q isHeating capacityFor heating capacity of said air conditioner, PCompressorIs the compressor power.
According to one embodiment of the present invention, the enthalpy value h of the lubricating oil at each temperature detection point is calculated according to the following formulai lubricating oilWherein i is a positive integer,
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 iWherein, tiIs the temperature at the temperature detection point.
According to one embodiment of the invention, the enthalpy value h of the mixture at each temperature detection point is calculated according to the following formulaiWherein i is a positive integer, hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor.
According to one embodiment of the present invention, the shell heat dissipation Q of the compressor is generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8) Wherein A isCompressorT8 is the temperature at the outdoor heat exchanger fins, which is the surface area of the compressor shell.
According to one embodiment of the invention, the return air port temperature t is generated according to the following formula1And the temperature t of the first end of the indoor heat exchanger7：
Figure BDA0003456932000000045
Wherein f is the compressor operating frequency, and a, b and c are fitting coefficients.
In order to achieve the above object, another air conditioner according to an embodiment of the fifth aspect of the present invention includes a memory, a processor, and a computer program stored in the memory and executable on the processor, where the processor executes the computer program to implement the method for calculating the energy efficiency of the air conditioner according to the fourth aspect of the present invention.
According to the air conditioner provided by the embodiment of the invention, the energy efficiency can be accurately detected in real time.
To achieve the above object, another non-transitory computer-readable storage medium according to a sixth aspect of the present invention stores thereon a computer program, which when executed by a processor, implements the energy efficiency calculation method of an air conditioner according to the fourth aspect of the present invention.
According to the non-transitory computer readable storage medium of the embodiment of the invention, the stored computer program is executed, so that the energy efficiency of the air conditioner can be accurately detected in real time, the running state of the air conditioner can be conveniently optimized according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the heating effect are achieved.
Drawings
Fig. 1 is a flowchart of an energy efficiency calculation method of an air conditioner according to an embodiment of the present invention;
fig. 2 is a schematic structural view of an air conditioner according to an embodiment of the present invention;
FIG. 3 is a block diagram illustrating an energy efficiency calculation system of an air conditioner according to an embodiment of the present invention;
fig. 4 is a flowchart illustrating an energy efficiency calculation method of an air conditioner according to an embodiment of the present invention;
fig. 5 is a block diagram illustrating an energy efficiency calculating system of an air conditioner according to an embodiment of the present invention.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
An air conditioner and an energy efficiency calculation method thereof according to an embodiment of the present invention will be described with reference to the accompanying drawings.
Fig. 1 is a flowchart of an energy efficiency calculation method of an air conditioner according to an embodiment of the present invention.
As shown in fig. 1, the energy efficiency calculation method of an air conditioner according to an embodiment of the present invention includes the following steps:
s101, obtaining the current working condition of the air conditioner, the power of the compressor and the power consumed by the air conditioner.
The current working condition of the air conditioner and the power P of the compressor can be monitored in real time through an electric control system of the air conditionerCompressorAnd the power consumption P of the air conditionerPower consumption。
S102, obtaining the shell heat dissipation Q of the compressorloss。
S103, acquiring the exhaust port temperature t of the exhaust port in the compressor2The temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4And the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And indoor ambient temperature t9。
S104, according to the indoor environment temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1And according to the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7。
The air conditioner according to the embodiment of the present invention may be a single-stage vapor compression type air conditioner, and as shown in fig. 2, the air conditioner according to the embodiment of the present invention may include a compressor, a four-way valve, an outdoor heat exchanger, a throttling element, and an indoor heat exchanger.
In one embodiment of the invention, the shell heat dissipation Q of the compressor can be calculated by a convection and radiation formulalossSpecifically, the shell heat dissipation Q of the compressor can be generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8)，
Wherein A isCompressorFor compressor casingsThe surface area of (a), which can be obtained by looking up the compressor model number, etc.; t is t8Which is the temperature at the outdoor heat exchanger fins, i.e., the outdoor ambient temperature, as shown in fig. 2, can be detected by the outdoor temperature sensors provided at the outdoor heat exchanger fins.
In one embodiment of the present invention, the temperature of the temperature detection point can be detected by disposing a temperature sensor at the corresponding temperature detection point. Specifically, as shown in fig. 2, the discharge port temperature t may be detected by providing a discharge port temperature sensor at the discharge port in the compressor2The first end of the outdoor heat exchanger is provided with a first end temperature sensor for detecting the first end temperature t of the outdoor heat exchanger4The middle part of the indoor heat exchanger is provided with an indoor heat exchanger middle part temperature sensor for detecting the middle part temperature t of the indoor heat exchanger6And arranging an indoor temperature sensor at the fins of the indoor heat exchanger to detect the indoor environment temperature t9。
Each temperature sensor is in effective contact with the refrigerant pipe wall corresponding to the temperature detection point, and heat preservation measures are taken for the refrigerant pipe wall, particularly for the position where the temperature sensor is arranged. For example, the temperature sensor can be arranged close to the copper pipe, and the copper pipe is wound and sealed through the heat-insulating adhesive tape. Therefore, the reliability and the accuracy of temperature detection can be improved.
In one embodiment of the present invention, the return air port temperature t may be generated according to the following equation1And the first end temperature t of the indoor heat exchanger7：
Figure BDA0003456932000000051
Wherein f is the compressor operating frequency, and a, b and c are fitting coefficients.
S105, when the current working condition of the air conditioner is a refrigeration working condition, according to the return air port temperature t of the return air port in the compressor1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd lubricating oilEnthalpy value h2 lubricating oilAccording to the temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4Generating a refrigerant enthalpy h at a first end of an outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oil。
It should be noted that, when the current working condition of the air conditioner is a cooling working condition, the outdoor heat exchanger serves as a condenser, the first end of the outdoor heat exchanger serves as a condenser outlet, the indoor heat exchanger serves as an evaporator, the first end of the indoor heat exchanger serves as an evaporator outlet, and the second end of the indoor heat exchanger serves as an evaporator inlet.
Because the mixture state of the refrigerant and the lubricating oil at different temperature detection points is different, the enthalpy values of the refrigerant and the lubricating oil at different temperature detection points are different. In one embodiment of the invention, the refrigerant enthalpy and the lubricant oil enthalpy may be calculated according to empirical formulas.
The following description will be made of the enthalpy value h of the refrigerant at the return port obtained by an empirical formula1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilRefrigerant enthalpy value h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAnd the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilRefrigerant enthalpy value h at first end of indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilThe specific process of (1).
Enthalpy h of refrigerant to return port in compressor1 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the return port of the compressor is overheated, and the enthalpy value h of the refrigerant at the return port can be calculated by combining the suction superheat degree1 refrigerant。
Specifically, the temperature t of the return air port can be determined according to1And the temperature t of the middle part of the indoor heat exchanger6Generating degree of superheat Δ t of intake air1And according to the degree of superheat Deltat of the suction gas1And the temperature t of the middle part of the indoor heat exchanger6Gas return port generation systemCorrection factor D of refrigerant enthalpy value1And according to the temperature t of the middle part of the indoor heat exchanger6Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration. Wherein the degree of superheat Δ t of the intake air1Is the temperature t of the return air port1And the temperature t of the middle part of the indoor heat exchanger6The difference, i.e. Δ t1＝t1-t6. Correction factor D of enthalpy value of return air port refrigerant1＝1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant. Enthalpy value h of saturated refrigerant at suction temperatureSaturation of inspiration＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Correction factor D in generating enthalpy value of return air port refrigerant1Enthalpy value h of saturated refrigerantSaturation of inspirationThen, the correction factor D can be further based on the enthalpy value of the return air port refrigerant1Enthalpy value h of saturated refrigerantSaturation of inspirationGenerating enthalpy value h of refrigerant1 refrigerant，h1 refrigerant＝D1·hSaturation of inspiration+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Similarly, the enthalpy h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the first end of the indoor heat exchanger is overheated, and the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger can be calculated by combining the superheat degree of the refrigerant at the position7 refrigerant。
Specifically, the temperature t of the first end of the indoor heat exchanger can be determined7And the temperature t of the middle part of the indoor heat exchanger6To generate a degree of superheat Deltat7And according to the degree of superheat Deltat7And indoorsTemperature t in the middle of the heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7And a correction factor D according to the enthalpy value of the refrigerant at the first end of the indoor heat exchanger7And enthalpy h of saturated refrigerantSaturation of inspirationGenerating enthalpy value h of refrigerant7 refrigerant. Wherein, Δ t7＝t7-t6，
Figure BDA0003456932000000061
h7 refrigerant＝D7·hSaturation of inspiration+d7Wherein d is1-d7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy h of refrigerant at discharge port in compressor2 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the exhaust port of the compressor is overheated, and the enthalpy value h of the refrigerant at the exhaust port can be calculated by combining the exhaust superheat degree2 refrigerant。
Specifically, the outdoor heat exchanger middle temperature t at the middle of the outdoor heat exchanger can be acquired3Wherein, as shown in fig. 2, the outdoor heat exchanger middle temperature t of the outdoor heat exchanger middle part3The temperature sensor can be used for detecting the temperature of the middle part of the outdoor heat exchanger.
Then, the temperature t of the exhaust port in the compressor can be determined2And the temperature t of the middle part of the outdoor heat exchanger3Generating exhaust superheat degree Deltat2And according to the degree of superheat Deltat of the exhaust gas2And the temperature t of the middle part of the outdoor heat exchanger3Correction factor D for generating enthalpy of exhaust port refrigerant2And according to the outdoor heat exchanger middle temperature t3Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation. Wherein, the degree of superheat delta t of the exhaust gas2Is the discharge outlet temperature t of the discharge outlet in the compressor2And the temperature t of the middle part of the outdoor heat exchanger3The difference, i.e. Δ t2＝t2-t3. Correction factor D of enthalpy value of exhaust port refrigerant2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant. Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation＝a1+a2t3+a3t2 3+a4t3 3+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Correction factor D in generating enthalpy value of refrigerant at exhaust port2Enthalpy value h of saturated refrigerant at exhaust temperatureExhaust gas saturationThen, the correction factor D can be further based on the enthalpy value of the refrigerant at the exhaust port2Enthalpy value h of saturated refrigerant at exhaust temperatureExhaust gas saturationGenerating refrigerant enthalpy h of exhaust port2 refrigerant，h2 refrigerant＝D2·hExhaust gas saturation+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy value h of refrigerant at first end of outdoor heat exchanger4 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the first end of the outdoor heat exchanger is overcooled, and the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger can be directly calculated4 refrigerant：
Figure BDA0003456932000000062
Wherein, c1-c4Is the corresponding supercooling coefficient of the refrigerant.
The saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the refrigerant are related to the type of the refrigerant, and the saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the R410A refrigerant and the R32 refrigerant are shown in table 1:
Figure BDA0003456932000000071
TABLE 1
Thus, the values of the coefficients are obtained according to the type of the refrigerant and the correspondence relationship shown in Table 1, and the enthalpy value of the refrigerant at each temperature detection point is calculated.
In other embodiments of the present invention, the calculation result of the software can be directly called, or the enthalpy value of the refrigerant at each temperature detection point can be obtained by other ways. For example, when the current working condition of the air conditioner is a cooling working condition, the current working condition can also be according to the low-pressure in the air conditioner and the temperature t of the return air port1First end temperature t of indoor heat exchanger7Respectively obtaining the enthalpy value h of the refrigerant at the air return port1And the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7And according to the high-pressure in the air conditioner and the temperature t of the exhaust port2The temperature t of the first end of the outdoor heat exchanger4Respectively obtaining the enthalpy values h of the refrigerants at the exhaust ports2And the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4。
Enthalpy value h of lubricating oil for each temperature detection pointi lubricating oilThe calculation can be made according to the following formula:
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 i，
Wherein i is a positive integer, tiIs the temperature at the temperature detection point. Therefore, the enthalpy value h of the lubricating oil at the air return port can be calculated1 lubricating oilEnthalpy value h of lubricating oil at exhaust port2 lubricating oilAnd the enthalpy value h of the lubricating oil at the first end of the outdoor heat exchanger4 lubricating oilAnd the enthalpy value h of the lubricating oil at the first end of the indoor heat exchanger7 lubricating oil。
S106, according to the enthalpy value h of the refrigerant at the air return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilGenerating the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerationAgent for treating cancerAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7。
Specifically, the enthalpy value h of the mixture at each temperature detection point can be calculated according to the following formulai：
hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104，
Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor. Therefore, the enthalpy value h of the mixture of the return air port can be calculated1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7。
S107, according to the power of the compressor and the shell heat dissipation Q of the compressorlossAnd enthalpy value h of mixture of air return port1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7The cooling capacity of the air conditioner is generated.
Specifically, the cooling capacity of the air conditioner may be generated according to the following formula:
Figure BDA0003456932000000072
wherein Q isRefrigerating capacityFor air conditioner cooling capacity, PCompressorIs the compressor power.
And S108, generating the energy efficiency of the air conditioner according to the power consumption and the refrigerating capacity of the air conditioner.
The current working condition of the air conditioner is a refrigeration working condition, so the refrigeration energy efficiency of the air conditioner can be generated according to the power consumption and the refrigeration capacity of the air conditioner, specifically, the refrigeration energy efficiency of the air conditioner is the ratio of the refrigeration capacity and the power consumption of the air conditioner, namely EER QRefrigerating capacity/PPower consumption。
After the refrigeration energy efficiency of the air conditioner is generated, the current operation state of the air conditioner can be adjusted according to the refrigeration energy efficiency of the air conditioner. For example, when the refrigeration energy efficiency of the air conditioner is low, the power of the compressor can be increased to improve the refrigeration capacity of the air conditioner, and the energy consumption of the air conditioner is relatively reduced, so that not only can energy be saved, but also the comfort of a user can be improved.
According to the energy efficiency calculation method of the air conditioner, by acquiring the current working condition of the air conditioner, the power of the compressor, the power consumption of the air conditioner and the heat dissipation capacity of the shell of the compressor, and obtaining the temperatures of the return air port, the exhaust port, the first end of the outdoor heat exchanger and the first end of the indoor heat exchanger in the compressor, and when the air conditioner is in a refrigerating working condition, the enthalpy values of the refrigerant and the lubricating oil at all the positions are generated according to the temperature at all the positions, and further the enthalpy value of the mixture at all the positions is generated, then the energy efficiency of the air conditioner is obtained by combining the power of the compressor, the heat dissipation capacity of the shell of the compressor, the enthalpy value of the mixture at each position and the power consumption of the air conditioner, so that the energy efficiency of the air conditioner can be accurately detected in real time, therefore, the running state of the air conditioner can be optimized conveniently according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the refrigeration effect are achieved.
The invention further provides an air conditioner corresponding to the embodiment.
The air conditioner provided by the embodiment of the invention comprises a memory, a processor and a computer program which is stored on the memory and can run on the processor, and when the processor executes the computer program, the energy efficiency calculation method of the air conditioner provided by the embodiment of the invention can be realized.
According to the air conditioner provided by the embodiment of the invention, the energy efficiency can be accurately detected in real time.
The invention also provides a non-transitory computer readable storage medium corresponding to the above embodiment.
A non-transitory computer-readable storage medium of an embodiment of the present invention stores thereon a computer program, which, when executed by a processor, can implement the energy efficiency calculation method of an air conditioner proposed in the above-described embodiment of the present invention.
According to the non-transitory computer readable storage medium of the embodiment of the invention, the stored computer program is executed, so that the energy efficiency of the air conditioner can be accurately detected in real time, the running state of the air conditioner can be conveniently optimized according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the refrigeration effect are achieved.
Corresponding to the embodiment, the invention further provides an energy efficiency calculation system of the air conditioner.
As shown in fig. 3, the energy efficiency calculation system of the air conditioner according to the embodiment of the present invention includes an exhaust port temperature sensor 02, an outdoor heat exchanger first end temperature sensor 04, an indoor heat exchanger middle temperature sensor 06, a return air port temperature generation module 60, an indoor heat exchanger first end temperature generation module 70, an acquisition module 10, a mixture enthalpy value generation module 20, a refrigerating capacity generation module 30, and an energy efficiency generation module 40.
Wherein the discharge port temperature sensor 02 is used for acquiring the discharge port temperature t of the discharge port in the compressor2(ii) a The first end temperature sensor 04 of the outdoor heat exchanger is used for acquiring the first end temperature t of the outdoor heat exchanger at the first end of the outdoor heat exchanger4(ii) a The indoor heat exchanger middle temperature sensor 06 is used for acquiring the indoor heat exchanger middle temperature t at the middle part of the indoor heat exchanger6。
The air conditioner according to an embodiment of the present invention may be a single-stage vapor compression type air conditioner, and as shown in fig. 2, the air conditioner according to an embodiment of the present invention may include a compressor 100, a four-way valve 200, an outdoor heat exchanger 300, a throttling element 400, and an indoor heat exchanger 500.
As shown in fig. 2, the discharge port temperature sensor 02 may be disposed at the discharge port in the compressor, the outdoor heat exchanger first end temperature sensor 04 may be disposed at the outdoor heat exchanger first end, and the indoor heat exchanger middle temperature sensor 06 may be disposed at the indoor heat exchanger middle. Each temperature sensor is in effective contact with the refrigerant pipe wall corresponding to the temperature detection point, and heat preservation measures are taken for the refrigerant pipe wall, particularly for the position where the temperature sensor is arranged. For example, the temperature sensor can be arranged close to the copper pipe, and the copper pipe is wound and sealed through the heat-insulating adhesive tape. Therefore, the reliability and the accuracy of temperature detection can be improved.
The return air inlet temperature generating module 60 is used for generating the indoor ambient temperature t9Exchange heat with outdoorTemperature t of the first end of the device4Generating a return port temperature t of a return port in a compressor1(ii) a The indoor heat exchanger first end temperature generating module 70 is used for generating the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7(ii) a The obtaining module 10 is used for obtaining the current working condition of the air conditioner, the power of the compressor, the power consumed by the air conditioner and the heat dissipating capacity Q of the shell of the compressorloss(ii) a The mixture enthalpy value generation module 20 is used for generating a return air port temperature t according to a return air port in the compressor when the current working condition of the air conditioner is a refrigeration working condition1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4Generating a refrigerant enthalpy h at a first end of an outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilAnd according to the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilGenerating the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7(ii) a (ii) a The cooling capacity generation module 30 is used for generating the cooling capacity Q according to the power of the compressor and the shell heat dissipation capacity Q of the compressorlossAnd enthalpy value h of mixture of air return port1Enthalpy value h of mixture of exhaust port2First of the outdoor heat exchangerEnd mixture enthalpy value h4And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the refrigerating capacity of the air conditioner; the energy efficiency generating module 40 is configured to generate the energy efficiency of the air conditioner according to the power consumed by the air conditioner and the cooling capacity.
The return air inlet temperature generating module 60, the indoor heat exchanger first end temperature generating module 70, the obtaining module 10, the mixture enthalpy value generating module 20, the refrigerating capacity generating module 30 and the energy efficiency generating module 40 may be disposed in an electric control system of the air conditioner. The acquisition module 10 can monitor the current working condition of the air conditioner and the power P of the compressor in real timeCompressorAnd the power consumption P of the air conditionerPower consumption. In one embodiment of the present invention, the obtaining module 10 may calculate the shell heat dissipation Q of the compressor by a convection and radiation formulalossSpecifically, the shell heat dissipation Q of the compressor can be generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8)，
Wherein A isCompressorThe surface area of the compressor shell is obtained by checking the model number of the compressor and the like; t is t8Which is the temperature at the outdoor heat exchanger fins, i.e., the outdoor ambient temperature, as shown in fig. 2, can be detected by an outdoor temperature sensor 08 provided at the outdoor heat exchanger fins.
It should be noted that, when the current working condition of the air conditioner is a cooling working condition, the outdoor heat exchanger serves as a condenser, the first end of the outdoor heat exchanger serves as a condenser outlet, the indoor heat exchanger serves as an evaporator, the first end of the indoor heat exchanger serves as an evaporator outlet, and the second end of the indoor heat exchanger serves as an evaporator inlet.
In one embodiment of the present invention, as shown in fig. 2, an indoor environment sensor 09 may be provided at the indoor heat exchanger fin to detect an indoor environment temperature t9Further, the return air port temperature generating module 60 and the indoor heat exchanger first end temperature generating module 70 may generate the return air port temperature according to the following formulas, respectivelyDegree t1And the first end temperature t of the indoor heat exchanger7：
Figure BDA0003456932000000091
Wherein f is the compressor operating frequency, and a, b and c are fitting coefficients.
Because the mixture state of the refrigerant and the lubricating oil at different temperature detection points is different, the enthalpy values of the refrigerant and the lubricating oil at different temperature detection points are different. In one embodiment of the present invention, the mixture enthalpy generation module 20 may calculate the refrigerant enthalpy and the lubricant oil enthalpy according to empirical formulas.
The following description will be made of the case where the enthalpy value h of the refrigerant at the return port is obtained by the mixture enthalpy value generation module 20 according to an empirical formula1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilRefrigerant enthalpy value h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAnd the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilRefrigerant enthalpy value h at first end of indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilThe specific process of (1).
Enthalpy h of refrigerant to return port in compressor1 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the return port of the compressor is overheated, and the mixture enthalpy value generation module 20 can calculate the enthalpy value h of the refrigerant at the return port by combining the suction superheat degree1 refrigerant。
Specifically, the enthalpy value generation module 20 may generate enthalpy values according to the return air port temperature t1And the temperature t of the middle part of the indoor heat exchanger6Generating degree of superheat Δ t of intake air1And according to the degree of superheat Deltat of the suction gas1And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of return air port refrigerant1And according to the temperature t of the middle part of the indoor heat exchanger6Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration. Wherein, the degree of superheat delta t1 of the intake air is the temperature t of the return air port1And the temperature t of the middle part of the indoor heat exchanger6The difference, i.e. Δ t1＝t1-t6. Correction factor D of enthalpy value of return air port refrigerant1＝1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant. Enthalpy value h of saturated refrigerant at suction temperatureSaturation of inspiration＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Correction factor D in generating enthalpy value of return air port refrigerant1Enthalpy value h of saturated refrigerantSaturation of inspirationThe mixture enthalpy value generation module 20 can further modify the enthalpy value of the return air port refrigerant according to a modification factor D1Enthalpy value h of saturated refrigerantSaturation of inspirationGenerating enthalpy value h of refrigerant1 refrigerant，h1 refrigerant＝D1·hSaturation of inspiration+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Similarly, the enthalpy h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the first end of the indoor heat exchanger is overheated, and the mixture enthalpy value generation module 20 can calculate the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger by combining the superheat degree of the refrigerant at the position7 refrigerant。
Specifically, the enthalpy value generation module 20 may generate the enthalpy value of the mixture according to the temperature t of the first end of the indoor heat exchanger7And the temperature t of the middle part of the indoor heat exchanger6To generate a degree of superheat Deltat7And according to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7And a correction factor D according to the enthalpy value of the refrigerant at the first end of the indoor heat exchanger7And saturated refrigerantEnthalpy value hSaturation of inspirationGenerating enthalpy value h of refrigerant7 refrigerant. Wherein, Δ t7＝t7-t6，
Figure BDA0003456932000000092
h7 refrigerant＝D7·hSaturation of inspiration+d7Wherein d is1-d7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy h of refrigerant at discharge port in compressor2 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the exhaust port of the compressor is overheated, and the mixture enthalpy value generation module 20 can calculate the enthalpy value h of the refrigerant at the exhaust port by combining the exhaust overheating degree2 refrigerant。
Specifically, the temperature t at the middle part of the outdoor heat exchanger can be acquired by the temperature sensor 03 at the middle part of the outdoor heat exchanger3Wherein, as shown in fig. 2, the outdoor heat exchanger middle temperature sensor 03 may be disposed in the middle of the outdoor heat exchanger.
The mixture enthalpy generation module 20 may then generate a mixture enthalpy based on the discharge port temperature t of the discharge port in the compressor2And the temperature t of the middle part of the outdoor heat exchanger3Generating exhaust superheat degree Deltat2And according to the degree of superheat Deltat of the exhaust gas2And the temperature t of the middle part of the outdoor heat exchanger3Correction factor D for generating enthalpy of exhaust port refrigerant2And according to the outdoor heat exchanger middle temperature t3Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation. Wherein, the degree of superheat delta t of the exhaust gas2Is the discharge outlet temperature t of the discharge outlet in the compressor2And the temperature t of the middle part of the outdoor heat exchanger3The difference, i.e. Δ t2＝t2-t3. Correction factor D of enthalpy value of exhaust port refrigerant2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant. Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation＝a1+a2t3+a3t2 3+a4t3 3+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Correction factor D in generating enthalpy value of refrigerant at exhaust port2Enthalpy value h of saturated refrigerant at exhaust temperatureExhaust gas saturationThereafter, the mixture enthalpy generation module 20 may further modify the enthalpy of the exhaust refrigerant based on a correction factor D2Enthalpy value h of saturated refrigerant at exhaust temperatureExhaust gas saturationGenerating refrigerant enthalpy h of exhaust port2 refrigerant，h2 refrigerant＝D2·hExhaust gas saturation+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy value h of refrigerant at first end of outdoor heat exchanger4 refrigerantWhen the current working condition of the air conditioner is a refrigeration working condition, the refrigerant at the first end of the outdoor heat exchanger is supercooled, and the mixture enthalpy value generation module 20 can directly calculate the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerant：
Figure BDA0003456932000000101
Wherein, c1-c4Is the corresponding supercooling coefficient of the refrigerant.
The saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the refrigerant described above are related to the type of refrigerant, and the saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the R410A refrigerant and the R32 refrigerant, respectively, are shown in table 1. Thus, the values of the coefficients are obtained according to the type of the refrigerant and the correspondence relationship shown in Table 1, and the enthalpy value of the refrigerant at each temperature detection point is calculated.
In other embodiments of the present invention, the enthalpy value generating module 20 may also directly call the calculation result of the software, or obtain the enthalpy value of the refrigerant at each temperature detecting point through other ways. For example, when the current working condition of the air conditioner is the controlIn cold working condition, the enthalpy value generation module 20 can also generate enthalpy value according to low pressure in the air conditioner and temperature t of the return air port1First end temperature t of indoor heat exchanger7Respectively obtaining the enthalpy value h of the refrigerant at the air return port1And the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7And according to the high-pressure in the air conditioner and the temperature t of the exhaust port2The temperature t of the first end of the outdoor heat exchanger4Respectively obtaining the enthalpy values h of the refrigerants at the exhaust ports2And the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4。
Enthalpy value h of lubricating oil for each temperature detection pointi lubricating oilThe enthalpy value generation module 20 may calculate according to the following formula:
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 i，
Wherein i is a positive integer, tiIs the temperature at the temperature detection point. Therefore, the enthalpy value h of the lubricating oil at the air return port can be calculated1 lubricating oilEnthalpy value h of lubricating oil at exhaust port2 lubricating oilAnd the enthalpy value h of the lubricating oil at the first end of the outdoor heat exchanger4 lubricating oilAnd the enthalpy value h of the lubricating oil at the first end of the indoor heat exchanger7 lubricationAnd (3) oil.
Further, the enthalpy value generation module 20 can calculate the enthalpy value h of the mixture at each temperature detection point according to the following formulai：
hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104，
Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor. Therefore, the enthalpy value h of the mixture of the return air port can be calculated1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7。
In an embodiment of the present invention, the cooling capacity generation module 30 may generate the cooling capacity of the air conditioner according to the following formula:
Figure BDA0003456932000000102
wherein Q isRefrigerating capacityFor air conditioner cooling capacity, PCompressorIs the compressor power.
Since the current working condition of the air conditioner is the refrigeration working condition, the energy efficiency generation module 40 can generate the refrigeration energy efficiency of the air conditioner according to the power consumption and the refrigeration capacity of the air conditioner, specifically, the refrigeration energy efficiency of the air conditioner is the ratio of the refrigeration capacity and the power consumption of the air conditioner, that is, EER is QRefrigerating capacity/PPower consumption。
After the refrigeration energy efficiency of the air conditioner is generated, the current operation state of the air conditioner can be adjusted according to the refrigeration energy efficiency of the air conditioner. For example, when the refrigeration energy efficiency of the air conditioner is low, the power of the compressor can be increased to improve the refrigeration capacity of the air conditioner, and the energy consumption of the air conditioner is relatively reduced, so that not only can energy be saved, but also the comfort of a user can be improved.
According to the energy efficiency calculation system of the air conditioner, the current working condition of the air conditioner, the power of the compressor, the power consumption of the air conditioner and the shell heat dissipation capacity of the compressor are obtained through the obtaining module, the temperatures of the return air port, the exhaust port, the first end of the outdoor heat exchanger and the first end of the indoor heat exchanger in the compressor are obtained through the corresponding temperature sensors, the refrigerant enthalpy value and the lubricating oil enthalpy value of each position are generated through the mixture enthalpy value generating module, the refrigerating capacity generating module and the energy efficiency generating module according to the temperatures of each position when the air conditioner is in the refrigerating working condition, the mixture enthalpy value of each position is further generated, then the enthalpy value of the air conditioner is obtained by combining the power of the compressor, the shell heat dissipation capacity of the compressor, the mixture value of each position and the power of the air conditioner, and therefore the energy efficiency of the air conditioner can be accurately detected in real time, therefore, the running state of the air conditioner can be optimized conveniently according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the refrigeration effect are achieved.
The air conditioner and the energy efficiency calculating method and system thereof in the embodiment can detect the refrigeration energy efficiency of the air conditioner, and the invention also provides another energy efficiency calculating method of the air conditioner for detecting the heating energy efficiency of the air conditioner.
As shown in fig. 4, another energy efficiency calculation method for an air conditioner according to an embodiment of the present invention includes the following steps:
s401, obtaining the current working condition of the air conditioner, the power of the compressor and the power consumed by the air conditioner.
The current working condition of the air conditioner and the power P of the compressor can be monitored in real time through an electric control system of the air conditionerCompressorAnd the power consumption P of the air conditionerPower consumption。
S402, obtaining the shell heat dissipation Q of the compressorloss。
S403, acquiring the exhaust port temperature t of the exhaust port in the compressor2The temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4And the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5And the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And indoor ambient temperature t9。
S404, according to the indoor environment temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1And according to the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7。
In one embodiment of the invention, the shell heat dissipation Q of the compressor can be calculated by a convection and radiation formulalossSpecifically, the shell heat dissipation Q of the compressor can be generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8)，
Wherein A isCompressorThe surface area of the compressor shell is obtained by checking the model number of the compressor and the like; t is t8Is the temperature at the outdoor heat exchanger fin, i.e., the outdoor ambient temperature, which can be detected by an outdoor temperature sensor provided at the outdoor heat exchanger fin, as shown in fig. 2And (6) measuring to obtain.
As shown in fig. 2, the discharge port temperature t may be detected by providing a discharge port temperature sensor at the discharge port in the compressor2The first end of the outdoor heat exchanger is provided with a first end temperature sensor for detecting the first end temperature t of the outdoor heat exchanger4A second end temperature sensor of the indoor heat exchanger is arranged at the second end of the indoor heat exchanger to detect the second end temperature t of the indoor heat exchanger5The middle part of the indoor heat exchanger is provided with an indoor heat exchanger middle part temperature sensor for detecting the middle part temperature t of the indoor heat exchanger6And arranging an indoor temperature sensor at the fins of the indoor heat exchanger to detect the indoor environment temperature t9。
Each temperature sensor is in effective contact with the refrigerant pipe wall corresponding to the temperature detection point, and heat preservation measures are taken for the refrigerant pipe wall, particularly for the position where the temperature sensor is arranged. For example, the temperature sensor can be arranged close to the copper pipe, and the copper pipe is wound and sealed through the heat-insulating adhesive tape. Therefore, the reliability and the accuracy of temperature detection can be improved.
In one embodiment of the present invention, the return air port temperature t may be generated according to the following equation1And the first end temperature t of the indoor heat exchanger7：
Figure BDA0003456932000000111
Wherein f is the compressor operating frequency, and a, b and c are fitting coefficients.
S405, when the current working condition of the air conditioner is a heating working condition, according to the return air port temperature t of the return air port in the compressor1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5Generating a refrigerant enthalpy h at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilAnd according to the indoor heat exchangerFirst end temperature t of indoor heat exchanger at first end7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oil。
It should be noted that, when the current working condition of the air conditioner is a heating working condition, the outdoor heat exchanger serves as an evaporator, the indoor heat exchanger serves as a condenser, the first end of the indoor heat exchanger is a condenser inlet, and the second end of the indoor heat exchanger is a condenser outlet.
Because the mixture state of the refrigerant and the lubricating oil at different temperature detection points is different, the enthalpy values of the refrigerant and the lubricating oil at different temperature detection points are different. In one embodiment of the invention, the refrigerant enthalpy and the lubricant oil enthalpy may be calculated according to empirical formulas.
The following description will be made of the enthalpy value h of the refrigerant at the return port obtained by an empirical formula1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilRefrigerant enthalpy value h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilRefrigerant enthalpy value h of second end of indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilAnd the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilThe specific process of (1).
Enthalpy h of refrigerant to return port in compressor1 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the return port of the compressor is overheated, and the enthalpy value h of the refrigerant at the return port can be calculated by combining the suction superheat degree1 refrigerant。
Specifically, the outdoor heat exchanger middle temperature t at the middle of the outdoor heat exchanger can be acquired3Wherein, as shown in fig. 2, the outdoor heat exchanger middle temperature t of the outdoor heat exchanger middle part3The temperature sensor can be used for detecting the temperature of the middle part of the outdoor heat exchanger.
Then according to the temperature t of the return air port1And the temperature t of the middle part of the outdoor heat exchanger3Generating degree of superheat Δ t of intake air1And according to the degree of superheat Deltat of the suction gas1And the temperature t of the middle part of the outdoor heat exchanger3GeneratingCorrection factor D of enthalpy value of return air port refrigerant1And according to the outdoor heat exchanger middle temperature t3Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration. Wherein the degree of superheat Δ t of the intake air1Is the temperature t of the return air port1And the temperature t of the middle part of the outdoor heat exchanger3The difference, i.e. Δ t1＝t1-t3. Correction factor for enthalpy of refrigerant at return air port
Figure BDA0003456932000000112
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant. Enthalpy value h of saturated refrigerant at suction temperatureSaturation of inspiration＝a1+a2t3+a3t2 3+a4t3 3+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Correction factor D in generating enthalpy value of return air port refrigerant1Enthalpy value h of saturated refrigerantSaturation of inspirationThen, the correction factor D can be further based on the enthalpy value of the return air port refrigerant1Enthalpy value h of saturated refrigerantSaturation of inspirationGenerating enthalpy value h of refrigerant1 refrigerant，h1 refrigerant＝D1·hSaturation of inspiration+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy h of refrigerant at discharge port in compressor2 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the exhaust port of the compressor is overheated, and the enthalpy value h of the refrigerant at the exhaust port can be calculated by combining the exhaust superheat degree2 refrigerant。
Specifically, the temperature t of the exhaust port in the compressor can be determined2And the temperature t of the middle part of the indoor heat exchanger6Generating exhaust superheat degree Deltat2And according to the temperature t of the middle part of the indoor heat exchanger6Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturationAnd according to the degree of superheat Δ t of the exhaust gas2And the temperature t of the middle part of the indoor heat exchanger6Generating exhaust gasCorrection factor D of enthalpy value of port refrigerant2. Wherein, the degree of superheat delta t of the exhaust gas2Is the discharge outlet temperature t of the discharge outlet in the compressor2And the temperature t of the middle part of the indoor heat exchanger6The difference, i.e. Δ t2＝t2-t6. Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant. Correction factor D of enthalpy value of exhaust port refrigerant2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Correction factor D in generating enthalpy value of refrigerant at exhaust port2Then, the correction factor D can be further based on the enthalpy value of the refrigerant at the exhaust port2Enthalpy value h of saturated refrigerant at exhaust temperatureExhaust gas saturationGenerating refrigerant enthalpy h of exhaust port2 refrigerant，h2 refrigerant＝D2·hExhaust gas saturation+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Similarly, the enthalpy h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the first end of the indoor heat exchanger is overheated, and the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger can be calculated by combining the superheat degree of the refrigerant at the position7 refrigerant。
Specifically, the temperature t of the first end of the indoor heat exchanger can be determined7And the temperature t of the middle part of the indoor heat exchanger6To generate a degree of superheat Deltat7And according to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7And anCorrection factor D according to enthalpy value of refrigerant at first end of indoor heat exchanger7And enthalpy h of saturated refrigerantExhaust gas saturationGenerating enthalpy value h of refrigerant7 refrigerant. Wherein, Δ t7＝t7-t6，
Figure BDA0003456932000000121
h7 refrigerant＝D7·hExhaust gas saturation+d7Wherein, d is1-d7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy value h of refrigerant at second end of indoor heat exchanger5 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the second end of the indoor heat exchanger is overcooled, and the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger can be directly calculated5 refrigerant：h5 refrigerant＝c1+c2t5+c3t2 5+c4t3 5Wherein c is1-c4Is the corresponding supercooling coefficient of the refrigerant.
The saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the refrigerant described above are related to the type of refrigerant, and the saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the R410A refrigerant and the R32 refrigerant, respectively, are shown in table 1. Thus, the values of the coefficients are obtained according to the type of the refrigerant and the correspondence relationship shown in Table 1, and the enthalpy value of the refrigerant at each temperature detection point is calculated.
In other embodiments of the present invention, the calculation result of the software can be directly called, or the enthalpy value of the refrigerant at each temperature detection point can be obtained by other ways. For example, when the current working condition of the air conditioner is a heating working condition, the current working condition can also be according to the high-pressure in the air conditioner and the temperature t of the return air inlet1First end temperature t of indoor heat exchanger7Respectively obtaining the enthalpy value h of the refrigerant at the air return port1And the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7And according to the high-pressure in the air conditioner and the temperature t of the exhaust port2And the second end temperature t of the indoor heat exchanger5Respectively obtaining exhaust portsEnthalpy value h of refrigerant2And the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5。
Enthalpy value h of lubricating oil for each temperature detection pointi lubricating oilThe calculation can be made according to the following formula:
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 i，
Wherein i is a positive integer, tiIs the temperature at the temperature detection point. Therefore, the enthalpy value h of the lubricating oil at the air return port can be calculated1 lubricating oilEnthalpy value h of lubricating oil at exhaust port2 lubricating oilAnd the enthalpy value h of the lubricating oil at the second end of the indoor heat exchanger5 lubricating oilAnd the enthalpy value h of the lubricating oil at the first end of the indoor heat exchanger7 lubricationAnd (3) oil.
S406, according to the enthalpy value h of the refrigerant at the air return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilGenerating the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7。
Specifically, the enthalpy value h of the mixture at each temperature detection point can be calculated according to the following formulai：
hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104，
Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor. Therefore, the enthalpy value h of the mixture of the return air port can be calculated1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And the first end of the indoor heat exchangerEnthalpy value h7。
S407, according to the power of the compressor and the enthalpy value h of the mixture of the return air ports1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the heating capacity of the air conditioner.
Specifically, the heating capacity of the air conditioner may be generated according to the following formula:
Figure BDA0003456932000000122
wherein Q isHeating capacityFor heating of air-conditioners, PCompressorIs the compressor power.
And S408, generating the energy efficiency of the air conditioner according to the power consumption and the heating capacity of the air conditioner.
The current working condition of the air conditioner is a heating working condition, so the heating energy efficiency of the air conditioner can be generated according to the power consumption and the heating quantity of the air conditioner, specifically, the heating energy efficiency of the air conditioner is the ratio of the heating quantity and the power consumption of the air conditioner, namely COP (coefficient of performance) QHeating capacity/PPower consumption。
After the heating energy efficiency of the air conditioner is generated, the current operation state of the air conditioner can be adjusted according to the heating energy efficiency of the air conditioner. For example, when the heating energy efficiency of the air conditioner is low, the power of the compressor can be increased to improve the heating capacity of the air conditioner, and the energy consumption of the air conditioner is relatively reduced, so that not only can energy be saved, but also the comfort of a user can be improved.
According to the energy efficiency calculation method of the air conditioner, by acquiring the current working condition of the air conditioner, the power of the compressor, the power consumption of the air conditioner and the heat dissipation capacity of the shell of the compressor, and obtaining the temperatures of the return air port, the exhaust port, the second end of the indoor heat exchanger and the first end of the indoor heat exchanger in the compressor, and when the air conditioner is in heating working condition, the enthalpy value of the refrigerant and the enthalpy value of the lubricating oil at each position are generated according to the temperature at each position, and further the enthalpy value of the mixture at each position is generated, then the energy efficiency of the air conditioner is obtained by combining the power of the compressor, the heat dissipation capacity of the shell of the compressor, the enthalpy value of the mixture at each position and the power consumption of the air conditioner, so that the energy efficiency of the air conditioner can be accurately detected in real time, therefore, the running state of the air conditioner can be optimized conveniently according to the real-time energy efficiency of the air conditioner, and the aims of saving energy and improving the heating effect are fulfilled.
The invention also provides another air conditioner corresponding to the embodiment.
The air conditioner provided by the embodiment of the invention comprises a memory, a processor and a computer program which is stored on the memory and can run on the processor, and when the processor executes the computer program, the energy efficiency calculation method of the air conditioner provided by the embodiment of the invention can be realized.
According to the air conditioner provided by the embodiment of the invention, the energy efficiency can be accurately detected in real time.
The invention also provides a non-transitory computer readable storage medium corresponding to the above embodiment.
A non-transitory computer-readable storage medium of an embodiment of the present invention stores thereon a computer program, which, when executed by a processor, can implement another energy efficiency calculation method for an air conditioner proposed in the above-described embodiment of the present invention.
According to the non-transitory computer readable storage medium of the embodiment of the invention, the stored computer program is executed, so that the energy efficiency of the air conditioner can be accurately detected in real time, the running state of the air conditioner can be conveniently optimized according to the real-time energy efficiency of the air conditioner, and the purposes of saving energy and improving the heating effect are achieved.
The invention further provides another energy efficiency calculation system of the air conditioner corresponding to the embodiment.
As shown in fig. 5, the energy efficiency calculation system of the air conditioner according to the embodiment of the present invention includes an exhaust port temperature sensor 02, an outdoor heat exchanger first end temperature sensor 04, an indoor heat exchanger second end temperature sensor 05, an indoor heat exchanger middle temperature sensor 06, a return air port temperature generation module 60, an indoor heat exchanger first end temperature generation module 70, an acquisition module 10, a mixture enthalpy value generation module 20, a heating capacity generation module 50, and an energy efficiency generation module 40.
Wherein the exhaust gas is dischargedThe port temperature sensor 02 is used to obtain the exhaust port temperature t of the exhaust port in the compressor2(ii) a The first end temperature sensor 04 of the outdoor heat exchanger is used for acquiring the first end temperature t of the outdoor heat exchanger at the first end of the outdoor heat exchanger4(ii) a The indoor heat exchanger second end temperature sensor 05 is used for acquiring the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5(ii) a The indoor heat exchanger middle temperature sensor 06 is used for acquiring the indoor heat exchanger middle temperature t at the middle part of the indoor heat exchanger6。
The air conditioner according to an embodiment of the present invention may be a single-stage vapor compression type air conditioner, and as shown in fig. 2, the air conditioner according to an embodiment of the present invention may include a compressor 100, a four-way valve 200, an outdoor heat exchanger 300, a throttling element 400, and an indoor heat exchanger 500.
As shown in fig. 2, the discharge port temperature sensor 02 may be disposed at the discharge port in the compressor, the outdoor heat exchanger first end temperature sensor 04 may be disposed at the outdoor heat exchanger first end, the indoor heat exchanger second end temperature sensor 05 may be disposed at the indoor heat exchanger second end, and the indoor heat exchanger middle temperature sensor 06 may be disposed at the indoor heat exchanger middle. Each temperature sensor is in effective contact with the refrigerant pipe wall corresponding to the temperature detection point, and heat preservation measures are taken for the refrigerant pipe wall, particularly for the position where the temperature sensor is arranged. For example, the temperature sensor can be arranged close to the copper pipe, and the copper pipe is wound and sealed through the heat-insulating adhesive tape. Therefore, the reliability and the accuracy of temperature detection can be improved.
The return air inlet temperature generating module 60 is used for generating the indoor ambient temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1(ii) a The indoor heat exchanger first end temperature generating module 70 is used for generating the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7(ii) a The obtaining module 10 is used for obtaining the current working condition of the air conditioner, the power of the compressor, the power consumed by the air conditioner and the heat dissipating capacity Q of the shell of the compressorloss(ii) a The mixture enthalpy value generation module 20 is used for generating a mixture enthalpy value according to return air in the compressor when the current working condition of the air conditioner is a heating working conditionTemperature t of return port of port1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5Generating a refrigerant enthalpy h at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilAnd according to the enthalpy value h of the refrigerant at the return air port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilGenerating the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7(ii) a The heating quantity generating module 50 is used for generating the heating quantity Q according to the power of the compressor and the shell heat dissipation quantity Q of the compressorlossAnd enthalpy value h of mixture of air return port1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the heating capacity of the air conditioner; the energy efficiency generating module 40 is used for generating the energy efficiency of the air conditioner according to the power consumed by the air conditioner and the heating capacity.
The return air inlet temperature generating module 60, the indoor heat exchanger first end temperature generating module 70, the obtaining module 10, the mixture enthalpy value generating module 20, the heating capacity generating module 50 and the energy efficiency generating module 40 may be disposed in an electric control system of the air conditioner. Acquisition module 10The current working condition of the air conditioner and the power P of the compressor can be monitored in real timeCompressorAnd the power consumption P of the air conditionerPower consumption. In one embodiment of the present invention, the obtaining module 10 may calculate the shell heat dissipation Q of the compressor by a convection and radiation formulalossSpecifically, the shell heat dissipation Q of the compressor can be generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8)，
Wherein A isCompressorThe surface area of the compressor shell is obtained by checking the model number of the compressor and the like; t is t8Which is the temperature at the outdoor heat exchanger fins, i.e., the outdoor ambient temperature, as shown in fig. 2, can be detected by an outdoor temperature sensor 08 provided at the outdoor heat exchanger fins.
It should be noted that, when the current working condition of the air conditioner is a heating working condition, the outdoor heat exchanger serves as an evaporator, the indoor heat exchanger serves as a condenser, the first end of the indoor heat exchanger is a condenser inlet, and the second end of the indoor heat exchanger is a condenser outlet.
In one embodiment of the present invention, as shown in fig. 2, an indoor environment sensor 09 may be provided at the indoor heat exchanger fin to detect an indoor environment temperature t9Further, the return air inlet temperature generating module 60 and the indoor heat exchanger first end temperature generating module 70 may generate the return air inlet temperature t according to the following formula respectively1And the first end temperature t of the indoor heat exchanger7：
Figure BDA0003456932000000141
Wherein f is the compressor operating frequency, and a, b and c are fitting coefficients.
Because the mixture state of the refrigerant and the lubricating oil at different temperature detection points is different, the enthalpy values of the refrigerant and the lubricating oil at different temperature detection points are different. In one embodiment of the present invention, the mixture enthalpy generation module 20 may calculate the refrigerant enthalpy and the lubricant oil enthalpy according to empirical formulas.
The following description will be made of the case where the enthalpy value h of the refrigerant at the return port is obtained by the mixture enthalpy value generation module 20 according to an empirical formula1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilRefrigerant enthalpy value h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilRefrigerant enthalpy value h of second end of indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilAnd the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilThe specific process of (1).
Enthalpy h of refrigerant to return port in compressor1 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the return port of the compressor is overheated, and the mixture enthalpy value generation module 20 can calculate the enthalpy value h of the refrigerant at the return port by combining the suction superheat degree1 refrigerant。
Specifically, the mixture enthalpy value generation module 20 can obtain the temperature t of the middle part of the outdoor heat exchanger in the middle part of the outdoor heat exchanger3Wherein, as shown in fig. 2, the outdoor heat exchanger middle temperature t of the outdoor heat exchanger middle part3The temperature sensor can be used for detecting the temperature of the middle part of the outdoor heat exchanger.
The enthalpy value generation module 20 may then generate a enthalpy value based on the return air port temperature t1And the temperature t of the middle part of the outdoor heat exchanger3Generating degree of superheat Δ t of intake air1And according to the degree of superheat Deltat of the suction gas1And the temperature t of the middle part of the outdoor heat exchanger3Correction factor D for generating enthalpy value of return air port refrigerant1And according to the outdoor heat exchanger middle temperature t3Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration. Wherein the degree of superheat Δ t of the intake air1Is the temperature t of the return air port1And the temperature t of the middle part of the outdoor heat exchanger3The difference, i.e. Δ t1＝t1-t3. Correction factor for enthalpy of refrigerant at return air port
Figure BDA0003456932000000142
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant. Enthalpy value h of saturated refrigerant at suction temperatureSaturation of inspiration＝a1+a2t3+a3t2 3+a4t3 3+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
Correction factor D in generating enthalpy value of return air port refrigerant1Enthalpy value h of saturated refrigerantSaturation of inspirationThe mixture enthalpy value generation module 20 can further modify the enthalpy value of the return air port refrigerant according to a modification factor D1Enthalpy value h of saturated refrigerantSaturation of inspirationGenerating enthalpy value h of refrigerant1 refrigerant，h1 refrigerant＝D1·hSaturation of inspiration+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy h of refrigerant at discharge port in compressor2 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the exhaust port of the compressor is overheated, and the mixture enthalpy value generation module 20 can calculate the enthalpy value h of the refrigerant at the exhaust port by combining the exhaust overheating degree2 refrigerant。
Specifically, the mixture enthalpy generation module 20 may generate the enthalpy value of the mixture according to the discharge port temperature t of the discharge port in the compressor2And the temperature t of the middle part of the indoor heat exchanger6Generating exhaust superheat degree Deltat2And according to the temperature t of the middle part of the indoor heat exchanger6Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturationAnd according to the degree of superheat Δ t of the exhaust gas2And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy of exhaust port refrigerant2. Wherein, the degree of superheat delta t of the exhaust gas2Is the discharge outlet temperature t of the discharge outlet in the compressor2And the temperature t of the middle part of the indoor heat exchanger6The difference, i.e. Δ t2＝t2-t6. Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant. Correction factor D of enthalpy value of exhaust port refrigerant2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
Correction factor D in generating enthalpy value of refrigerant at exhaust port2Thereafter, the mixture enthalpy generation module 20 may further modify the enthalpy of the exhaust refrigerant based on a correction factor D2Enthalpy value h of saturated refrigerant at exhaust temperatureExhaust gas saturationGenerating refrigerant enthalpy h of exhaust port2 refrigerant，h2 refrigerant＝D2·hExhaust gas saturation+d7Wherein d is7The coefficient of superheat zone corresponding to the refrigerant.
Similarly, the enthalpy h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the first end of the indoor heat exchanger is overheated, and the mixture enthalpy value generation module 20 can calculate the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger by combining the superheat degree of the refrigerant at the position7 refrigerant。
Specifically, the enthalpy value generation module 20 may generate the enthalpy value of the mixture according to the temperature t of the first end of the indoor heat exchanger7And the temperature t of the middle part of the indoor heat exchanger6To generate a degree of superheat Deltat7And according to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7And a correction factor D according to the enthalpy value of the refrigerant at the first end of the indoor heat exchanger7And enthalpy h of saturated refrigerantExhaust gas saturationGenerating enthalpy value h of refrigerant7 refrigerant. Wherein, Δ t7＝t7-t6，
Figure BDA0003456932000000151
h7 refrigerant＝D7·hExhaust gas saturation+d7Wherein, d is1-d7The coefficient of superheat zone corresponding to the refrigerant.
Enthalpy value h of refrigerant at second end of indoor heat exchanger5 refrigerantWhen the current working condition of the air conditioner is a heating working condition, the refrigerant at the second end of the indoor heat exchanger is overcooled, and the mixture enthalpy value generation module 20 can directly calculate the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5 refrigerant：h5 refrigerant＝c1+c2t5+c3t2 5+c4t3 5Wherein c is1-c4Is the corresponding supercooling coefficient of the refrigerant.
The saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the refrigerant described above are related to the type of refrigerant, and the saturation area coefficient, the superheat area coefficient, and the subcooling area coefficient corresponding to the R410A refrigerant and the R32 refrigerant, respectively, are shown in table 1. Thus, the values of the coefficients are obtained according to the type of the refrigerant and the correspondence relationship shown in Table 1, and the enthalpy value of the refrigerant at each temperature detection point is calculated.
In other embodiments of the present invention, the enthalpy value generating module 20 may also directly call the calculation result of the software, or obtain the enthalpy value of the refrigerant at each temperature detecting point through other ways. For example, when the current operating condition of the air conditioner is a heating operating condition, the enthalpy value generation module 20 may further generate the enthalpy value according to the high pressure in the air conditioner and the temperature t of the return air inlet1First end temperature t of indoor heat exchanger7Respectively obtaining the enthalpy value h of the refrigerant at the air return port1And the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7And according to the high-pressure in the air conditioner and the temperature t of the exhaust port2And the second end temperature t of the indoor heat exchanger5Respectively obtaining the enthalpy values h of the refrigerants at the exhaust ports2And the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5。
Enthalpy value h of lubricating oil for each temperature detection pointi lubricating oilThe enthalpy value generation module 20 may generate enthalpy values according to the following equationAnd calculating to obtain:
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 i，
Wherein i is a positive integer, tiIs the temperature at the temperature detection point. Therefore, the enthalpy value h of the lubricating oil at the air return port can be calculated1 lubricating oilEnthalpy value h of lubricating oil at exhaust port2 lubricating oilAnd the enthalpy value h of the lubricating oil at the second end of the indoor heat exchanger5 lubricating oilAnd the enthalpy value h of the lubricating oil at the first end of the indoor heat exchanger7 lubricating oil。
Further, the enthalpy value generation module 20 can calculate the enthalpy value h of the mixture at each temperature detection point according to the following formulai：
hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104，
Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor. Therefore, the enthalpy value h of the mixture of the return air port can be calculated1Enthalpy value h of mixture of exhaust port2And the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7。
In an embodiment of the present invention, the heating amount generating module 50 may generate the heating amount of the air conditioner according to the following formula:
Figure BDA0003456932000000152
wherein Q isHeating capacityFor heating of air-conditioners, PCompressorIs the compressor power.
Since the current operating mode of the air conditioner is a heating operating mode, the energy efficiency generating module 40 may generate the heating energy efficiency of the air conditioner according to the power consumed by the air conditioner and the heating amount, and specifically, the heating energy efficiency of the air conditioner is the ratio of the heating amount to the power consumed by the air conditioner, that is, COP QHeating capacity/PPower consumption。
After the heating energy efficiency of the air conditioner is generated, the current operation state of the air conditioner can be adjusted according to the heating energy efficiency of the air conditioner. For example, when the heating energy efficiency of the air conditioner is low, the power of the compressor can be increased to improve the heating capacity of the air conditioner, and the energy consumption of the air conditioner is relatively reduced, so that not only can energy be saved, but also the comfort of a user can be improved.
According to the energy efficiency calculation system of the air conditioner, the current working condition of the air conditioner, the power of the compressor, the power consumption of the air conditioner and the shell heat dissipation capacity of the compressor are obtained through the obtaining module, the temperatures of the air return port, the exhaust port, the second end of the indoor heat exchanger and the first end of the indoor heat exchanger in the compressor are obtained through the corresponding temperature sensors, the refrigerant enthalpy value and the lubricating oil enthalpy value of each position are generated through the mixture enthalpy value generating module, the heating quantity generating module and the energy efficiency generating module according to the temperatures of each position when the air conditioner is in the heating working condition, the mixture enthalpy value of each position is further generated, then the enthalpy value of the air conditioner is obtained by combining the power of the compressor, the shell heat dissipation capacity of the compressor, the refrigerant value of each position and the power of the air conditioner, and therefore the energy efficiency of the air conditioner can be accurately detected in real time, therefore, the running state of the air conditioner can be optimized conveniently according to the real-time energy efficiency of the air conditioner, and the aims of saving energy and improving the heating effect are fulfilled.
In summary, according to the air conditioner and the energy efficiency calculation method and system thereof in the embodiments of the present invention, the physical properties of the refrigerant and the physical properties of the lubricating oil in the refrigerant circulation system of the air conditioner are obtained, the power of the air conditioner is calculated by combining the physical properties of the mixture of the refrigerant and the lubricating oil and the heat leakage condition of the compressor, and the energy efficiency of the air conditioner is further calculated, so that the refrigeration energy efficiency and the heating energy efficiency of the air conditioner can be accurately detected in real time.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims (38)

1. The energy efficiency calculation method of the air conditioner is characterized by comprising the following steps of:
acquiring the current working condition of the air conditioner, the power of a compressor and the power consumption of the air conditioner;
obtaining the shell heat dissipation Q of the compressorloss；
Obtaining a discharge port temperature t of a discharge port in a compressor2The temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4And the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And indoor ambient temperature t9；
According to the indoor ambient temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1And according to the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7；
When the current working condition of the air conditioner is a refrigeration working condition, the air conditioner is controlled according to the return air of the return air port in the compressorMouth temperature t1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4Generating a refrigerant enthalpy h at a first end of an outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oil；
According to the enthalpy value h of the refrigerant at the air return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger4 refrigerantAnd enthalpy value h of lubricating oil4 lubricating oilGenerating the enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7；
According to the power of the compressor and the shell heat dissipation Q of the compressorlossThe enthalpy value h of the mixture of the air return port1The enthalpy value h of the mixture of the exhaust port2The enthalpy value h of the mixture at the first end of the outdoor heat exchanger4And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the refrigerating capacity of the air conditioner; and
and generating the energy efficiency of the air conditioner according to the power consumption of the air conditioner and the refrigerating capacity.
2. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the energy efficiency is calculated according to a return air in the compressorTemperature t of return port of port1Generating the enthalpy h of the refrigerant at the return port1 refrigerantThe method specifically comprises the following steps:
according to the temperature t of the return air port1And the temperature t of the middle part of the indoor heat exchanger6Generating degree of superheat Δ t of intake air1；
According to the degree of superheat delta t of the suction gas1And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of return air port refrigerant1；
According to the middle temperature t of the indoor heat exchanger6Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration；
Correction factor D according to enthalpy value of return air port refrigerant1An enthalpy value h of the saturated refrigerantSaturation of inspirationGenerating an enthalpy h of said refrigerant1 refrigerant。
3. The energy efficiency calculation method of an air conditioner according to claim 2, wherein the enthalpy value h of the saturated refrigerant at the suction temperature is generated according to the following formulaSaturation of inspiration：
hSaturation of inspiration＝a1+a2t6+a3t2 6+a4t3 6+a5Wherein a is1-a5Is the saturation area coefficient corresponding to the refrigerant.
4. The energy efficiency calculation method of an air conditioner according to claim 2, wherein the correction factor D of the enthalpy value of the return air port refrigerant is generated according to the following formula1：
D1＝1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6，
Wherein d is1-d6For the corresponding superheated zone of the refrigerantAnd (4) counting.
5. The energy efficiency calculation method of an air conditioner according to claim 2, wherein the enthalpy value h of the refrigerant is generated according to the following formula1 refrigerant：h1 refrigerant＝D1·hSaturation of inspiration+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
6. The energy efficiency calculation method of an air conditioner according to claim 3, wherein the first end temperature t of the indoor heat exchanger at the first end of the indoor heat exchanger is based on7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantThe method specifically comprises the following steps:
according to the temperature t of the first end of the indoor heat exchanger7And the temperature t of the middle part of the indoor heat exchanger6To generate a degree of superheat Deltat7；
According to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7；
Correction factor D according to enthalpy value of refrigerant at first end of indoor heat exchanger7And the enthalpy value h of the saturated refrigerantSaturation of inspirationGenerating an enthalpy h of said refrigerant7 refrigerant。
7. The energy efficiency calculation method of an air conditioner according to claim 6, wherein the correction factor D for the enthalpy value of the refrigerant at the first end of the indoor heat exchanger is generated according to the following formula7：
Figure FDA0003456931990000021
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
8. The energy efficiency calculation method of an air conditioner according to claim 6, wherein the energy efficiency is calculated according toFormulation of the enthalpy h of the refrigerant7 refrigerant：h7 refrigerant＝D7·hSaturation of inspiration+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
9. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the energy efficiency calculation method is based on a discharge port temperature t of a discharge port in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantThe method specifically comprises the following steps:
acquiring the middle temperature t of the outdoor heat exchanger at the middle part of the outdoor heat exchanger3；
According to the exhaust port temperature t of the exhaust port in the compressor2And the temperature t of the middle part of the outdoor heat exchanger3Generating exhaust superheat degree Deltat2；
According to the superheat degree delta t of the exhaust gas2And the temperature t of the middle part of the outdoor heat exchanger3Correction factor D for generating enthalpy of exhaust port refrigerant2；
According to the middle temperature t of the outdoor heat exchanger3Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation；
Correction factor D based on enthalpy of refrigerant at said exhaust port2An enthalpy value h of the saturated refrigerant at the discharge temperatureExhaust gas saturationGenerating an enthalpy h of the refrigerant at the exhaust port2 refrigerant。
10. The energy efficiency calculation method of an air conditioner according to claim 9, wherein the correction factor D of the enthalpy value of the discharge port refrigerant is generated according to the following formula2：
D2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3，
Wherein d is1-d6For refrigerant correspond toThe coefficient of superheat zone.
11. The energy efficiency calculation method of an air conditioner according to claim 9, wherein the enthalpy value h of the refrigerant is generated according to the following formula2 refrigerant：h2 refrigerant＝D2·hExhaust gas saturation+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
12. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the enthalpy value h of the refrigerant at the first end of the outdoor heat exchanger is generated according to the following formula4 refrigerant：
Figure FDA0003456931990000022
Wherein, c1-c4Is the corresponding supercooling coefficient of the refrigerant.
13. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the cooling capacity of the air conditioner is generated according to the following formula:
Figure FDA0003456931990000023
wherein Q isRefrigerating capacityFor the cooling capacity of the air conditioner, PCompressorIs the power of the compressor.
14. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the enthalpy value h of the lubricating oil at each temperature detection point is calculated according to the following formulai lubricating oilWherein i is a positive integer,
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 i，
Wherein, tiIs the temperature at the temperature detection point.
15. Energy efficiency of air conditioner according to claim 1The calculation method is characterized in that the enthalpy value h of the mixture at each temperature detection point is calculated according to the following formulaiWherein i is a positive integer,
hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104，
Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor.
16. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the shell heat dissipation Q of the compressor is generated according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8)，
Wherein A isCompressorSurface area of compressor casing, t8Is the temperature at the fins of the outdoor heat exchanger.
17. The energy efficiency calculation method of an air conditioner according to claim 1, wherein the return air port temperature t is generated according to the following formula1And the temperature t of the first end of the indoor heat exchanger7：
t1＝a*t9+b*t4+c*f，
t7＝a*t9+b*t6+ c f, where f is the operating frequency of the compressor and a, b, c are fitting coefficients.
18. An air conditioner, comprising a memory, a processor and a computer program stored on the memory and operable on the processor, wherein the processor executes the computer program to implement the energy efficiency calculation method of the air conditioner according to any one of claims 1 to 17.
19. A non-transitory computer-readable storage medium having a computer program stored thereon, wherein the computer program, when executed by a processor, implements the energy efficiency calculation method of an air conditioner according to any one of claims 1 to 17.
20. The energy efficiency calculation method of the air conditioner is characterized by comprising the following steps of:
acquiring the current working condition of the air conditioner, the power of a compressor and the power consumption of the air conditioner;
obtaining the shell heat dissipation Q of the compressorloss；
Obtaining a discharge port temperature t of a discharge port in a compressor2The temperature t of the first end of the outdoor heat exchanger at the first end of the outdoor heat exchanger4And the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5And the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And indoor ambient temperature t9；
According to the indoor ambient temperature t9And the first end temperature t of the outdoor heat exchanger4Generating a return port temperature t of a return port in a compressor1And according to the indoor ambient temperature t9And the temperature t of the middle part of the indoor heat exchanger6Generating a first end temperature t of the indoor heat exchanger7；
When the current working condition of the air conditioner is a heating working condition, the temperature t of the return air port in the compressor is determined according to the temperature t of the return air port1Generating the enthalpy h of the refrigerant at the return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilAccording to the discharge outlet temperature t of the discharge outlet in the compressor2Generating refrigerant enthalpy h of exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilAccording to the temperature t of the second end of the indoor heat exchanger at the second end of the indoor heat exchanger5Generating a refrigerant enthalpy h at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilAnd the temperature t of the first end of the indoor heat exchanger according to the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oil；
According to the enthalpy value h of the refrigerant at the air return port1 refrigerantAnd enthalpy value h of lubricating oil1 lubricating oilGenerating enthalpy value h of mixture of air return port1According to the enthalpy h of the refrigerant at the exhaust port2 refrigerantAnd enthalpy value h of lubricating oil2 lubricating oilGenerating enthalpy value h of mixture of exhaust port2According to the enthalpy value h of the refrigerant at the second end of the indoor heat exchanger5 refrigerantAnd enthalpy value h of lubricating oil5 lubricating oilGenerating the enthalpy value h of the mixture at the second end of the indoor heat exchanger5And according to the enthalpy value h of the refrigerant at the first end of the indoor heat exchanger7 refrigerantAnd enthalpy value h of lubricating oil7 lubricating oilGenerating a mixture enthalpy value h at a first end of the indoor heat exchanger7；
According to the power of the compressor and the shell heat dissipation Q of the compressorlossThe enthalpy value h of the mixture of the air return port1The enthalpy value h of the mixture of the exhaust port2The enthalpy value h of the mixture at the second end of the indoor heat exchanger5And the enthalpy value h of the mixture at the first end of the indoor heat exchanger7Generating the heating capacity of the air conditioner; and
and generating the energy efficiency of the air conditioner according to the power consumption of the air conditioner and the heating quantity.
21. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the return air port temperature t of the return air port in the compressor is based on1Generating the enthalpy h of the refrigerant at the return port1 refrigerantThe method specifically comprises the following steps:
acquiring the middle temperature t of the outdoor heat exchanger at the middle part of the outdoor heat exchanger3；
According to the temperature t of the return air port1And the temperature t of the middle part of the outdoor heat exchanger3Generating degree of superheat Δ t of intake air1；
According to the degree of superheat delta t of the suction gas1And the temperature t of the middle part of the outdoor heat exchanger3Correction factor D for generating enthalpy value of return air port refrigerant1；
According to the outdoor changeMiddle temperature t of heater3Generating enthalpy h of saturated refrigerant at suction temperatureSaturation of inspiration；
Correction factor D according to enthalpy value of return air port refrigerant1The enthalpy value h of the saturated refrigerant at the suction temperatureSaturation of inspirationGenerating the enthalpy value h of the refrigerant at the air return port1 refrigerant。
22. The energy efficiency calculation method of an air conditioner according to claim 21, wherein the enthalpy value h of the saturated refrigerant at the suction temperature is generated according to the following formulaSaturation of inspiration：
Figure FDA0003456931990000031
Wherein, a1-a5Is the saturation area coefficient corresponding to the refrigerant.
23. The energy efficiency calculation method of an air conditioner according to claim 21, wherein the correction factor D of the enthalpy value of the return air port refrigerant is generated according to the following formula1：
Figure FDA0003456931990000032
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
24. The energy efficiency calculation method of an air conditioner according to claim 21, wherein the enthalpy value h of the refrigerant is generated according to the following formula1 refrigerant：h1 refrigerant＝D1·hSaturation of inspiration+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
25. The energy efficiency calculation method of an air conditioner according to claim 21, wherein the energy efficiency calculation is based on a discharge port temperature t of a discharge port in the compressor2Generating the rowRefrigerant enthalpy h of ports2 refrigerantThe method specifically comprises the following steps:
according to the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And a discharge port temperature t of a discharge port in the compressor2Generating exhaust superheat degree Deltat2；
According to the superheat degree delta t of the exhaust gas2And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy of exhaust port refrigerant2；
According to the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6Enthalpy h of saturated refrigerant at discharge temperatureExhaust gas saturation；
Correction factor D based on enthalpy of refrigerant at said exhaust port2An enthalpy value h of the saturated refrigerant at the discharge temperatureExhaust gas saturationGenerating an enthalpy h of the refrigerant at the exhaust port2 refrigerant。
26. The energy efficiency calculation method of an air conditioner according to claim 25, wherein the correction factor D of the enthalpy value of the discharge port refrigerant is generated according to the following formula2：
D2＝1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6，
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
27. The energy efficiency calculation method of an air conditioner according to claim 25, wherein the enthalpy value h of the refrigerant is generated according to the following formula2 refrigerant：h2 refrigerant＝D2·hExhaust gas saturation+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
28. As claimed inThe energy efficiency calculation method of the air conditioner is characterized in that the energy efficiency calculation method is carried out according to the temperature t of the first end of the indoor heat exchanger at the first end of the indoor heat exchanger7Generating a refrigerant enthalpy h at a first end of an indoor heat exchanger7 refrigerantThe method specifically comprises the following steps:
according to the middle temperature t of the indoor heat exchanger in the middle of the indoor heat exchanger6And the temperature t of the first end of the indoor heat exchanger7To generate a degree of superheat Deltat7；
According to the degree of superheat Deltat7And the temperature t of the middle part of the indoor heat exchanger6Correction factor D for generating enthalpy value of first end refrigerant of indoor heat exchanger7；
Correction factor D according to enthalpy value of refrigerant at first end of indoor heat exchanger7An enthalpy value h of the saturated refrigerant at the discharge temperatureExhaust gas saturationGenerating an enthalpy h of the refrigerant at the outlet7 refrigerant。
29. The energy efficiency calculation method of an air conditioner according to claim 28, wherein the correction factor D for the enthalpy value of the refrigerant at the first end of the indoor heat exchanger is generated according to the following formula7：
Figure FDA0003456931990000041
Wherein d is1-d6The coefficient of superheat zone corresponding to the refrigerant.
30. The energy efficiency calculation method of an air conditioner according to claim 28, wherein the enthalpy value h of the refrigerant is generated according to the following formula7 refrigerant：h7 refrigerant＝D7·hExhaust gas saturation+d7，d7The coefficient of superheat zone corresponding to the refrigerant.
31. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the cooling of the second end of the indoor heat exchanger is calculated according to the following formulaEnthalpy value h of agent5 refrigerant：
h5 refrigerant＝c1+c2t5+c3t2 5+c4t3 5Wherein c is1-c4Is the corresponding supercooling coefficient of the refrigerant.
32. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the heating capacity of the air conditioner is generated according to the following formula:
Figure FDA0003456931990000042
wherein Q isHeating capacityIs the heating capacity of the air conditioner, PCompressorIs the power of the compressor.
33. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the enthalpy value h of the lubricating oil at each temperature detection point is calculated according to the following formulai lubricating oilWherein i is a positive integer,
hi lubricating oil＝-0.0808+1.7032ti+0.0025t2 i，
Wherein, tiIs the temperature at the temperature detection point.
34. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the mixture enthalpy value h at each temperature detection point is calculated according to the following formulaiWherein i is a positive integer,
hi＝(1-Cg)hi refrigerant+Cghi lubricating oil
Cg＝f/104，
Wherein, CgIs the oil content of the mixture and f is the operating frequency of the compressor.
35. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the rootGenerating the shell heat dissipation Q of the compressor according to the following formulaloss：
Qloss＝5.67×10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor×(t2-t8)，
Wherein A isCompressorSurface area of compressor casing, t8Is the temperature at the fins of the outdoor heat exchanger.
36. The energy efficiency calculation method of an air conditioner according to claim 20, wherein the return air port temperature t is generated according to the following formula1And the temperature t of the first end of the indoor heat exchanger7：
t1＝a*t9+b*t4+c*f，
t7＝a*t9+b*t6+ c f, where f is the operating frequency of the compressor and a, b, c are fitting coefficients.
37. An air conditioner comprising a memory, a processor and a computer program stored on the memory and executable on the processor, the processor implementing the method of any one of claims 20-36 when executing the computer program.
38. A non-transitory computer readable storage medium having a computer program stored thereon, wherein the computer program, when executed by a processor, implements the method of any of claims 20-36.
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