CN107514764A - Air conditioner and its efficiency computational methods - Google Patents

Air conditioner and its efficiency computational methods Download PDF

Info

Publication number
CN107514764A
CN107514764A CN201710772633.8A CN201710772633A CN107514764A CN 107514764 A CN107514764 A CN 107514764A CN 201710772633 A CN201710772633 A CN 201710772633A CN 107514764 A CN107514764 A CN 107514764A
Authority
CN
China
Prior art keywords
heat exchanger
msub
air conditioner
temperature
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201710772633.8A
Other languages
Chinese (zh)
Inventor
张�浩
戚文端
杨亚新
刘燕飞
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GD Midea Air Conditioning Equipment Co Ltd
Original Assignee
Guangdong Midea Refrigeration Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guangdong Midea Refrigeration Equipment Co Ltd filed Critical Guangdong Midea Refrigeration Equipment Co Ltd
Priority to CN201710772633.8A priority Critical patent/CN107514764A/en
Publication of CN107514764A publication Critical patent/CN107514764A/en
Pending legal-status Critical Current

Links

Abstract

The invention discloses a kind of air conditioner and its efficiency computational methods, the efficiency computational methods comprise the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain the housing heat dissipation capacity Q of compressorloss；Obtain the temperature t in the middle part of exhaust outlet, outdoor heat exchanger first end and indoor heat exchanger in compressor2、t4And t6And indoor environment temperature t9；According to t9And t4Generate the gas returning port temperature t of gas returning port in compressor1, and according to t9And t6Generate indoor heat exchanger first end temperature t7；When the current working of air conditioner is cooling condition, respectively according to t1、t2、t4And t7The refrigerant enthalpy h of corresponding generation gas returning port1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4With the refrigerant enthalpy h of indoor heat exchanger first end7；According to the power of compressor, Qloss、h1、h2、h4And h7Generate the refrigerating capacity of air conditioner；And the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Description

Air conditioner and its efficiency computational methods
Technical field
The present invention relates to air conditioner technical field, the efficiency computational methods of more particularly to a kind of air conditioner, a kind of air conditioner With a kind of non-transitorycomputer readable storage medium.
Background technology
It is comfortably the problem of user more pays close attention to that whether air conditioner, which saves,.
Current air conditioner is difficult to maintain preferable fortune operationally due to that can not know the situation of change of efficiency Row state, cooling or heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention One purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
Fourth object of the present invention is the efficiency computational methods for proposing another air conditioner.
The 5th purpose of the present invention is to propose another air conditioner.
The 6th purpose of the present invention is to propose another non-transitorycomputer readable storage medium.
To reach above-mentioned purpose, a kind of efficiency computational methods for air conditioner that first aspect present invention embodiment proposes include Following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；The housing for obtaining compressor dissipates Heat Qloss；Obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger first end temperature Spend t4, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With indoor environment temperature t9；According to indoor environment temperature t9With Outdoor heat exchanger first end temperature t4Generate the gas returning port temperature t of gas returning port in compressor1, and according to the indoor environment temperature t9With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7；When the current working of the air conditioner is system During cold operating mode, according to the gas returning port temperature t of gas returning port in the compressor1Generate the refrigerant enthalpy h of gas returning port1, according to described The exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant enthalpy h of exhaust outlet2, according to the outdoor heat exchanger first end Outdoor heat exchanger first end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4With according to the indoor heat exchanger The indoor heat exchanger first end temperature t of first end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7；According to the compression The housing heat dissipation capacity Q of the power of machine, the compressorloss, the gas returning port refrigerant enthalpy h1, exhaust outlet refrigerant enthalpy Value h2, outdoor heat exchanger first end refrigerant enthalpy h4With the refrigerant enthalpy h of indoor heat exchanger first end7Generate air conditioner Refrigerating capacity；And the efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet, outdoor The temperature of heat exchanger first end and indoor heat exchanger first end, and when air conditioner is in cooling condition according to above-mentioned each position The refrigerant enthalpy for the above-mentioned each position of temperature generation put, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, The refrigerant enthalpy and air conditioner power consumption of above-mentioned each position obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving refrigeration.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor1Generate gas returning port Refrigerant enthalpy h1Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to the gas returning port Temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to the suction superheat Δ t1Changed with interior Hot device middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the indoor heat exchanger middle portion temperature t6It is raw The enthalpy h of saturation refrigerant under into suction temperatureAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, it is described full With the enthalpy h of refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h1.Further, generated according to below equation and satisfied under suction temperature With the enthalpy h of refrigerantAir-breathing saturation：hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region corresponding to refrigerant Coefficient.
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to below equationAir-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to below equation1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Further, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchange The refrigerant enthalpy h of device first end7Specifically include：According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger Middle portion temperature t6Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generation is indoor The modifying factor D of heat exchanger first end refrigerant enthalpy7；According to the modifying factor of the indoor heat exchanger first end refrigerant enthalpy Sub- D7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6 For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation institute State the refrigerant enthalpy h of exhaust outlet2Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to institute State the exhaust port temperatures t of exhaust outlet in compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；Root According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor of exhaust outlet refrigerant enthalpy D2：According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the row The modifying factor D of gas port refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the exhaust outlet Refrigerant enthalpy h2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation Value h4：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the refrigerating capacity of air conditioner is generated according to below equation：Wherein, QRefrigerating capacityFor the Air conditioner refrigerating capacity, PCompressorFor the power of compressor.
According to one embodiment of present invention, the housing heat dissipation capacity Q of compressor is generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8), wherein, ACompressorFor the surface area of compressor housing, t8 is the temperature at outdoor heat exchanger fin.
According to one embodiment of present invention, the gas returning port temperature t is generated according to below equation1With the indoor heat exchange Device first end temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c is fitting coefficient.
To reach above-mentioned purpose, a kind of air conditioner that second aspect of the present invention embodiment proposes includes memory, processor And the computer program that can be run on the memory and on the processor is stored in, calculating described in the computing device During machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
To reach above-mentioned purpose, a kind of non-transitory computer-readable storage medium that third aspect present invention embodiment proposes Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor The efficiency computational methods of the air conditioner of proposition.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
To reach above-mentioned purpose, the efficiency computational methods bag for another air conditioner that fourth aspect present invention embodiment proposes Include following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain the housing of compressor Heat dissipation capacity Qloss；Obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger first end Temperature t4, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, in the middle part of indoor heat exchanger in the middle part of indoor heat exchanger Temperature t6With indoor environment temperature t9；According to indoor environment temperature t9With outdoor heat exchanger first end temperature t4Generate in compressor The gas returning port temperature t of gas returning port1, and according to the indoor environment temperature t9With indoor heat exchanger middle portion temperature t6Generation interior is changed Hot device first end temperature t7；When the current working of the air conditioner is heating condition, according to gas returning port in the compressor Gas returning port temperature t1Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generation The refrigerant enthalpy h of exhaust outlet2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generation is indoor The refrigerant enthalpy h at the end of heat exchanger second5With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7It is raw Into the refrigerant enthalpy h of indoor heat exchanger first end7；According to the housing heat dissipation capacity of the power of the compressor, the compressor Qloss, the gas returning port refrigerant enthalpy h1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy Value h5With the refrigerant enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner；And according to the air conditioner power consumption Power and the heating capacity generate the efficiency of the air conditioner.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet, interior The end of heat exchanger second and the temperature of indoor heat exchanger first end, and when air conditioner is in heating condition according to above-mentioned each position The refrigerant enthalpy for the above-mentioned each position of temperature generation put, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, The refrigerant enthalpy and air conditioner power consumption of above-mentioned each position obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving heating effect.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1Generate back The refrigerant enthalpy h of gas port1Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to described time Gas port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat Δ t1 With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the outdoor heat exchanger Middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the amendment of the gas returning port refrigerant enthalpy Factor D1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For Overheated zone coefficient corresponding to refrigerant.
Further, the exhaust port temperatures t according to exhaust outlet in the compressor2Generate the refrigeration of the exhaust outlet Agent enthalpy h2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According in the indoor heat exchanger The indoor heat exchanger middle portion temperature t in portion6With the exhaust port temperatures t of exhaust outlet in the compressor2Generate discharge superheat Δ t2； According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the modifying factor of exhaust outlet refrigerant enthalpy D2；According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate the enthalpy of saturation refrigerant under delivery temperature hIt is vented saturation；According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Further, the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generate respectively The refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：According to the indoor heat exchanger in the middle part of the indoor heat exchanger Middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With it is described Indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；Changed according to the interior The modifying factor D of hot device first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationDescribed in generation The refrigerant enthalpy h of indoor heat exchanger first end7。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6 For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation Value h5：
h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor compressor horsepower.
According to one embodiment of present invention, the housing heat dissipation capacity Q of compressor is generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8), wherein, ACompressorFor the surface area of compressor housing, t8 is the temperature at outdoor heat exchanger fin.
According to one embodiment of present invention, the gas returning port temperature t is generated according to below equation1With the indoor heat exchange Device first end temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is the running frequency of compressor, and a, b, c is fitting coefficient.
To reach above-mentioned purpose, another air conditioner that fifth aspect present invention embodiment proposes includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, meter described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that fourth aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
To reach above-mentioned purpose, the computer-readable storage of another non-transitory that sixth aspect present invention embodiment proposes Medium, is stored thereon with computer program, and the computer program realizes that fourth aspect present invention is implemented when being executed by processor The efficiency computational methods for the air conditioner that example proposes.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
Brief description of the drawings
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention；
Fig. 2 is the structural representation according to the air conditioner of one embodiment of the invention；
Fig. 3 is the block diagram according to the efficiency computing system of the air conditioner of the embodiment of the present invention；
Fig. 4 is the flow chart according to the efficiency computational methods of another air conditioner of the embodiment of the present invention；
Fig. 5 is the block diagram according to the efficiency computing system of another air conditioner of the embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
The air conditioner of the embodiment of the present invention and its efficiency computational methods are described below in conjunction with the accompanying drawings.
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention.
As shown in figure 1, the efficiency computational methods of the air conditioner of the embodiment of the present invention, comprise the following steps：
S101, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionerCompressorAnd air-conditioning Device power consumption PPower consumption。
S102, obtain the housing heat dissipation capacity Q of compressorloss。
S103, obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger One end temperature t4, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With indoor environment temperature t9。
S104, according to indoor environment temperature t9With outdoor heat exchanger first end temperature t4Generate time of gas returning port in compressor Gas port temperature t1, and according to indoor environment temperature t9With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor, four-way valve, outdoor heat exchanger, restricting element and indoor heat exchanger.
In one embodiment of the invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss, The housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin Outer temperature sensor detects to obtain.
In one embodiment of the invention, can be by setting temperature sensor to detect respectively in corresponding temperature test point The temperature of the temperature detecting point.Specifically, as shown in Fig. 2 by exhaust ports within the compressor exhaust port temperatures can be set to pass Sensor is to detect exhaust port temperatures t2, at outdoor heat exchanger first end outdoor heat exchanger first end temperature sensor is set to examine Survey outdoor heat exchanger first end temperature t4, indoors indoor heat exchanger middle portion temperature sensor is set with sensing chamber in the middle part of heat exchanger Interior heat exchanger middle portion temperature t6And at heat exchanger fin indoor temperature transmitter is set to detect indoor environment temperature indoors t9。
Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially the position of temperature sensor is set to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
In one embodiment of the invention, gas returning port temperature t can be generated according to below equation1With indoor heat exchanger first Hold temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c is fitting coefficient.
S105, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1 Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant enthalpy of exhaust outlet Value h2, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4Generate the refrigerant of outdoor heat exchanger first end Enthalpy h4With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generate the refrigeration of indoor heat exchanger first end Agent enthalpy h7。
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point It is different.In one embodiment of the invention, rule of thumb the enthalpy of refrigerant can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、 The refrigerant enthalpy h of outdoor heat exchanger first end4With the refrigerant enthalpy h of indoor heat exchanger first end7Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the gas returning port of machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
Specifically, can be according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1, and root According to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1, Yi Jigen According to indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Wherein, suction superheat Δ t1 For gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t1=t1-t6.The modifying factor of gas returning port refrigerant enthalpy Sub- D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For Overheated zone coefficient corresponding to refrigerant.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1· hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end, the position refrigerant superheat degree can be combined and calculate indoor heat exchanger first The refrigerant enthalpy h at end7。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7, and According to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7, and According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy of generation7With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy Value h7.Wherein, Δ t7=t7-t6, h7=D7·hAir-breathing saturation+d7, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained3, wherein, as shown in Fig. 2 outdoor Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger3Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through Degree sensor detects to obtain.
Then, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3Generation exhaust Degree of superheat Δ t2, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generation exhaust outlet refrigerant enthalpy is repaiied Positive divisor D2, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation.Wherein, Discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t2 =t2-t3.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5 (Δt2)t2 3+d6(Δt2)2t2 3, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.Saturation refrigerant under delivery temperature Enthalpy hIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGeneration The refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of outdoor heat exchanger first end4, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4：Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone Coefficient：
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is cooling condition Adjust low pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room External heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy of outdoor heat exchanger first end h4。
S106, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port refrigerant enthalpy h1, exhaust The refrigerant enthalpy h of mouth2, outdoor heat exchanger first end refrigerant enthalpy h4With the refrigerant enthalpy of indoor heat exchanger first end h7Generate the refrigerating capacity of air conditioner.
Specifically, the refrigerating capacity of air conditioner can be generated according to below equation：Wherein, QRefrigerating capacityFor Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
S107, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Because the current working of air conditioner is cooling condition, thus can be generated according to air conditioner power consumption and refrigerating capacity empty The refrigeration efficiency of device is adjusted, specifically, the refrigeration efficiency of air conditioner is the ratio between the refrigerating capacity of air conditioner and power consumption, i.e. EER= QRefrigerating capacity/PPower consumption。
, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet, outdoor The temperature of heat exchanger first end and indoor heat exchanger first end, and when air conditioner is in cooling condition according to above-mentioned each position The refrigerant enthalpy for the above-mentioned each position of temperature generation put, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, The refrigerant enthalpy and air conditioner power consumption of above-mentioned each position obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving refrigeration.
Corresponding above-described embodiment, the present invention also propose a kind of air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor The computer program of operation, during computing device computer program, the air conditioner that the above embodiment of the present invention proposes can be achieved Efficiency computational methods.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
Corresponding above-described embodiment, the present invention also propose a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for the air conditioner that the above embodiment of the present invention proposes can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
Corresponding above-described embodiment, the present invention also propose a kind of efficiency computing system of air conditioner.
As shown in figure 3, the efficiency computing system of the air conditioner of the embodiment of the present invention, including exhaust port temperatures sensor 02, Outdoor heat exchanger first end temperature sensor 04, indoor heat exchanger middle portion temperature sensor 06 and gas returning port temperature generation module 60th, indoor heat exchanger first end temperature generation module 70, acquisition module 10, refrigerant enthalpy generation module 20, refrigerating capacity generation Module 30, efficiency generation module 40.
Wherein, exhaust port temperatures sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Outdoor heat exchange Device first end temperature sensor 04 is used for the outdoor heat exchanger first end temperature t for obtaining outdoor heat exchanger first end4；Indoor heat exchange Device middle portion temperature sensor 06 is used to obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element 400 and indoor heat exchanger 500.
As shown in Fig. 2 the settable exhaust ports within the compressor of exhaust port temperatures sensor 02, outdoor heat exchanger first end Temperature sensor 04 may be provided at outdoor heat exchanger first end, and indoor heat exchanger middle portion temperature sensor 06 may be provided at interior and change In the middle part of hot device.Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially the position of temperature sensor is set to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
Gas returning port temperature generation module 60 is used for according to indoor environment temperature t9With outdoor heat exchanger first end temperature t4Generation The gas returning port temperature t of gas returning port in compressor1；Indoor heat exchanger first end temperature generation module 70 is used for according to indoor environment temperature Spend t9With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7；Acquisition module 10 is used to obtain air conditioner Current working, the power of compressor, the housing heat dissipation capacity Q of air conditioner power consumption and compressorloss；Refrigerant enthalpy is given birth to It is used for into module 20 when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1It is raw Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant enthalpy of exhaust outlet h2, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4Generate the refrigerant enthalpy of outdoor heat exchanger first end Value h4With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generate the refrigerant of indoor heat exchanger first end Enthalpy h7；Refrigerating capacity generation module 30 is used for power, the housing heat dissipation capacity Q of compressor according to compressorloss, gas returning port system Cryogen enthalpy h1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4With indoor heat exchanger first The refrigerant enthalpy h at end7Generate the refrigerating capacity of air conditioner；Efficiency generation module 40 is used for according to air conditioner power consumption and refrigeration The efficiency of amount generation air conditioner.
Wherein, gas returning port temperature generation module 60, indoor heat exchanger first end temperature generation module 70, acquisition module 10, Refrigerant enthalpy generation module 20, refrigerating capacity generation module 30 and efficiency generation module 40 may be disposed at the electric-control system of air conditioner In.Acquisition module 10 can monitor the current working of air conditioner, the power P of compressor in real timeCompressorWith air conditioner power consumption PPower consumption。 In one embodiment of the invention, acquisition module 10 can calculate the housing heat dissipation capacity of compressor by convection current, radiation formula Qloss, specifically can be according to the housing heat dissipation capacity Q of below equation generation compressorloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin The outer detection of temperature sensor 08 obtains.
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
In one embodiment of the invention, as shown in Fig. 2 at heat exchanger fin indoor environment can be set to sense indoors Device 09 is to detect indoor environment temperature t9, further, gas returning port temperature generation module 60 and indoor heat exchanger first end temperature Generation module 70 can generate gas returning port temperature t according to below equation respectively1With indoor heat exchanger first end temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c is fitting coefficient.
Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point It is different.In one embodiment of the invention, rule of thumb refrigerant can be calculated by formula in refrigerant enthalpy generation module 20 Enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below1、 The refrigerant enthalpy h of exhaust outlet2, outdoor heat exchanger first end refrigerant enthalpy h4With the refrigerant of indoor heat exchanger first end Enthalpy h7Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port Enthalpy h1。
Specifically, refrigerant enthalpy generation module 20 can be according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6It is raw Into suction superheat Δ t1, and according to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate gas returning port refrigerant enthalpy The modifying factor D of value1, and according to indoor heat exchanger middle portion temperature t6Generate the enthalpy of saturation refrigerant under suction temperature hAir-breathing saturation.Wherein, suction superheat Δ t1 is gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t1=t1- t6.The modifying factor D of gas returning port refrigerant enthalpy1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δ t1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.The enthalpy of saturation refrigerant under suction temperature Value hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, refrigerant enthalpy Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration Refrigerant enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end, refrigerant enthalpy generation module 20 can combine the position refrigerant superheat Degree calculates the refrigerant enthalpy h of indoor heat exchanger first end7。
Specifically, refrigerant enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7In indoor heat exchanger Portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger the The modifying factor D of one end refrigerant enthalpy7, and the modifying factor of the indoor heat exchanger first end refrigerant enthalpy according to generation D7With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7.Wherein, Δ t7=t7-t6,h7=D7·hAir-breathing saturation+d7, its In, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet Enthalpy h2。
Specifically, the outdoor heat exchanger in the middle part of outdoor heat exchanger can be obtained by outdoor heat exchanger middle portion temperature sensor 03 Middle portion temperature t3, wherein, as shown in Fig. 2 outdoor heat exchanger middle portion temperature sensor 03 may be provided in the middle part of outdoor heat exchanger.
Then, refrigerant enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2And outdoor heat exchange Device middle portion temperature t3Generate discharge superheat Δ t2, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generation The modifying factor D of exhaust outlet refrigerant enthalpy2, and according to outdoor heat exchanger middle portion temperature t3Generate saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturation.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2And outdoor heat exchanger Middle portion temperature t3Difference, i.e. Δ t2=t2-t3.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δt2)2+d3 (Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.Row The enthalpy h of saturation refrigerant at a temperature of gasIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5To satisfy corresponding to refrigerant With fauna number.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Refrigerant enthalpy generation module 20 can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For corresponding to refrigerant Overheated zone coefficient.
For the refrigerant enthalpy h of outdoor heat exchanger first end4, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, refrigerant enthalpy generation module 20 can directly calculate the system of outdoor heat exchanger first end Cryogen enthalpy h4：Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.
In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software Fruit, or the refrigerant enthalpy by each temperature detecting point of other approach acquisition.For example, when the current working of air conditioner is During cooling condition, refrigerant enthalpy generation module 20 can also be according to the low pressure in air conditioner, gas returning port temperature t1, interior changes Hot device first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With the refrigerant enthalpy h of indoor heat exchanger first end7, And can be according to the high-pressure in air conditioner, exhaust port temperatures t2, outdoor heat exchanger first end temperature t4Respectively obtain exhaust outlet Refrigerant enthalpy h2With the refrigerant enthalpy h of outdoor heat exchanger first end4。
In an embodiment of the present invention, refrigerating capacity generation module 30 can generate the refrigerating capacity of air conditioner according to below equation：Wherein, QRefrigerating capacityFor Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
Because the current working of air conditioner is cooling condition, thus efficiency generation module 40 can be according to air conditioner power consumption With the refrigeration efficiency of refrigerating capacity generation air conditioner, specifically, the refrigeration efficiency of air conditioner is the refrigerating capacity and power consumption work(of air conditioner The ratio between rate, i.e. EER=QRefrigerating capacity/PPower consumption。
, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor, the housing heat dissipation capacity of air conditioner power consumption and compressor, and obtained by corresponding temperature sensor Gas returning port in compressor, exhaust outlet, the temperature of outdoor heat exchanger first end and indoor heat exchanger first end, and at air conditioner By refrigerant enthalpy generation module, refrigerating capacity generation module and efficiency generation module according to above-mentioned each position when cooling condition The refrigerant enthalpy for the above-mentioned each position of temperature generation put, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, The refrigerant enthalpy and air conditioner power consumption of above-mentioned each position obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving refrigeration.
The air conditioner and its efficiency computational methods and system of above-described embodiment can detect the refrigeration efficiency of air conditioner, for inspection The heat efficiency of air conditioner is surveyed, the present invention also proposes the efficiency computational methods of another air conditioner.
As shown in figure 4, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：
S401, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionerCompressorAnd air-conditioning Device power consumption PPower consumption。
S402, obtain the housing heat dissipation capacity Q of compressorloss。
S403, obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger One end temperature t4, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, indoor heat exchanger in the middle part of indoor heat exchanger Middle portion temperature t6With indoor environment temperature t9。
S404, according to indoor environment temperature t9With outdoor heat exchanger first end temperature t4Generate time of gas returning port in compressor Gas port temperature t1, and according to indoor environment temperature t9With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7。
In one embodiment of the invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss, The housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin Outer temperature sensor detects to obtain.
As shown in Fig. 2 by exhaust ports within the compressor exhaust port temperatures sensor can be set to detect exhaust outlet temperature Spend t2, at outdoor heat exchanger first end outdoor heat exchanger first end temperature sensor is set to detect outdoor heat exchanger first end Temperature t4, indoors indoor heat exchanger the second end temperature sensor is set to detect indoor heat exchanger second at the end of heat exchanger second Hold temperature t5, indoors indoor heat exchanger middle portion temperature sensor is set to detect indoor heat exchanger middle portion temperature in the middle part of heat exchanger t6And at heat exchanger fin indoor temperature transmitter is set to detect indoor environment temperature t indoors9。
Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially the position of temperature sensor is set to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
In one embodiment of the invention, gas returning port temperature t can be generated according to below equation1With indoor heat exchanger first Hold temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c is fitting coefficient.
S405, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1 Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant enthalpy of exhaust outlet Value h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigerant at the end of indoor heat exchanger second Enthalpy h5With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generate the refrigeration of indoor heat exchanger first end Agent enthalpy h7。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point It is different.In one embodiment of the invention, rule of thumb the enthalpy of refrigerant can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、 The refrigerant enthalpy h at the end of indoor heat exchanger second5With the refrigerant enthalpy h of indoor heat exchanger first end7Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the gas returning port of machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained3, wherein, as shown in Fig. 2 outdoor Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger3Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through Degree sensor detects to obtain.
Then can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1, and according to Suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1, and according to Outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Wherein, suction superheat Δ t1For Gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.The modifying factor of gas returning port refrigerant enthalpyWherein, d1-d6For refrigerant pair The overheated zone coefficient answered.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5 For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1· hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
Specifically, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Generation row Gas degree of superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Saturation under delivery temperature is generated to freeze The enthalpy h of agentIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigerant enthalpy Modifying factor D2.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle part Temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5, Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δ t2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone corresponding to refrigerant Coefficient.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, can further repairing according to exhaust outlet refrigerant enthalpy Positive divisor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation +d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work During condition, the refrigerant superheat of indoor heat exchanger first end, the position refrigerant superheat degree can be combined and calculate indoor heat exchanger first The refrigerant enthalpy h at end7。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7, and According to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7, and According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy of generation7With the enthalpy h of saturation refrigerantIt is vented saturationGenerate refrigerant enthalpy Value h7.Wherein, Δ t7=t7-t6, h7=D7·hIt is vented saturation+d7, wherein, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5：h5=c1+c2t5 +c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is heating condition Adjust high-pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room Interior the second end of heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy at the end of indoor heat exchanger second h5。
S406, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port refrigerant enthalpy h1, exhaust The refrigerant enthalpy h of mouth2, the end of indoor heat exchanger second refrigerant enthalpy h5With the refrigerant enthalpy of indoor heat exchanger first end h7Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to below equation：Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor compressor horsepower.
S407, the efficiency of air conditioner is generated according to air conditioner power consumption and heating capacity.
Because the current working of air conditioner is heating condition, thus can be generated according to air conditioner power consumption and heating capacity empty The heat efficiency of device is adjusted, specifically, the heat efficiency of air conditioner is the ratio between the heating capacity of air conditioner and power consumption, i.e. COP= QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet, interior The end of heat exchanger second and the temperature of indoor heat exchanger first end, and when air conditioner is in heating condition according to above-mentioned each position The refrigerant enthalpy for the above-mentioned each position of temperature generation put, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, The refrigerant enthalpy and air conditioner power consumption of above-mentioned each position obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving heating effect.
Corresponding above-described embodiment, the present invention also propose another air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor The computer program of operation, during computing device computer program, it is empty that the another kind that the above embodiment of the present invention proposes can be achieved Adjust the efficiency computational methods of device.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
Corresponding above-described embodiment, the present invention also propose a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for another air conditioner that the above embodiment of the present invention proposes can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
Corresponding above-described embodiment, the present invention also propose the efficiency computing system of another air conditioner.
As shown in figure 5, the efficiency computing system of the air conditioner of the embodiment of the present invention, including exhaust port temperatures sensor 02, Outdoor heat exchanger first end temperature sensor 04, the second end of indoor heat exchanger temperature sensor 05, indoor heat exchanger middle portion temperature Sensor 06 and gas returning port temperature generation module 60, indoor heat exchanger first end temperature generation module 70, acquisition module 10, system Cryogen enthalpy generation module 20, heating capacity generation module 50, efficiency generation module 40.
Wherein, exhaust port temperatures sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Outdoor heat exchange Device first end temperature sensor 04 is used for the outdoor heat exchanger first end temperature t for obtaining outdoor heat exchanger first end4；Indoor heat exchange The second end of device temperature sensor 05 is used for the second end of the indoor heat exchanger temperature t for obtaining the end of indoor heat exchanger second5；Indoor heat exchange Device middle portion temperature sensor 06 is used to obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6。
The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element 400 and indoor heat exchanger 500.
As shown in Fig. 2 the settable exhaust ports within the compressor of exhaust port temperatures sensor 02, outdoor heat exchanger first end Temperature sensor 04 may be provided at outdoor heat exchanger first end, and the second end of indoor heat exchanger temperature sensor 05 may be provided at interior The end of heat exchanger second, indoor heat exchanger middle portion temperature sensor 06 may be provided in the middle part of indoor heat exchanger.Wherein, each temperature passes Sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant tube wall, especially sets TEMP Take Insulation in the position of device.For example, temperature sensor can be close to copper pipe setting, and copper pipe is carried out by being incubated adhesive tape Winding sealing.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
Gas returning port temperature generation module 60 is used for according to indoor environment temperature t9With outdoor heat exchanger first end temperature t4Generation The gas returning port temperature t of gas returning port in compressor1；Indoor heat exchanger first end temperature generation module 70 is used for according to indoor environment temperature Spend t9With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature t7；Acquisition module 10 is used to obtain air conditioner Current working, the power of compressor, the housing heat dissipation capacity Q of air conditioner power consumption and compressorloss；Refrigerant enthalpy is given birth to It is used for into module 20 when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1It is raw Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant enthalpy of exhaust outlet h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigerant enthalpy at the end of indoor heat exchanger second Value h5With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generate the refrigerant of indoor heat exchanger first end Enthalpy h7；Heating capacity generation module 50 is used for power, the housing heat dissipation capacity Q of compressor according to compressorloss, gas returning port system Cryogen enthalpy h1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5With indoor heat exchanger first The refrigerant enthalpy h at end7Generate the heating capacity of air conditioner；Efficiency generation module 40 is used for according to air conditioner power consumption and heating The efficiency of amount generation air conditioner.
Wherein, gas returning port temperature generation module 60, indoor heat exchanger first end temperature generation module 70, acquisition module 10, Refrigerant enthalpy generation module 20, heating capacity generation module 50 and efficiency generation module 40 may be disposed at the electric-control system of air conditioner In.Acquisition module 10 can monitor the current working of air conditioner, the power P of compressor in real timeCompressorWith air conditioner power consumption PPower consumption。 In one embodiment of the invention, acquisition module 10 can calculate the housing heat dissipation capacity of compressor by convection current, radiation formula Qloss, specifically can be according to the housing heat dissipation capacity Q of below equation generation compressorloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t8Changed for outdoor Temperature at hot device fin, i.e. outdoor environment temperature, as shown in Fig. 2 it can be by the room that is disposed in the outdoor at heat exchanger fin The outer detection of temperature sensor 08 obtains.
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
In one embodiment of the invention, as shown in Fig. 2 at heat exchanger fin indoor environment can be set to sense indoors Device 09 is to detect indoor environment temperature t9, further, gas returning port temperature generation module 60 and indoor heat exchanger first end temperature Generation module 70 can generate gas returning port temperature t according to below equation respectively1With indoor heat exchanger first end temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c is fitting coefficient.
Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point It is different.In one embodiment of the invention, rule of thumb refrigerant can be calculated by formula in refrigerant enthalpy generation module 20 Enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below1、 The refrigerant enthalpy h of exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5With the refrigerant of indoor heat exchanger first end Enthalpy h7Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port Enthalpy h1。
Specifically, refrigerant enthalpy generation module 20 can obtain the outdoor heat exchanger middle portion temperature in the middle part of outdoor heat exchanger t3, wherein, as shown in Fig. 2 the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3Can be by being set in the middle part of outdoor heat exchanger The outdoor heat exchanger middle portion temperature sensor put detects to obtain.
Then refrigerant enthalpy generation module 20 can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generation is inhaled Gas degree of superheat Δ t1, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate gas returning port refrigerant enthalpy Modifying factor D1, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Its In, suction superheat Δ t1For gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.Gas returning port The modifying factor of refrigerant enthalpy Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+ a3t2 3+a4t3 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, refrigerant enthalpy Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration Refrigerant enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet Enthalpy h2。
Specifically, refrigerant enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2Changed with interior Hot device middle portion temperature t6Generate discharge superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6It is raw The enthalpy h of saturation refrigerant under into delivery temperatureIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6 Generate the modifying factor D of exhaust outlet refrigerant enthalpy2.Wherein, discharge superheat Δ t2For the exhaust outlet temperature of exhaust outlet in compressor Spend t2With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation= a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.The amendment of exhaust outlet refrigerant enthalpy Factor D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6 For overheated zone coefficient corresponding to refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, refrigerant enthalpy generation module 20 can further basis The modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of exhaust outlet Agent enthalpy h2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work During condition, the refrigerant superheat of indoor heat exchanger first end, refrigerant enthalpy generation module 20 can combine the position refrigerant superheat Degree calculates the refrigerant enthalpy h of indoor heat exchanger first end7。
Specifically, refrigerant enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7In indoor heat exchanger Portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger the The modifying factor D of one end refrigerant enthalpy7, and the modifying factor of the indoor heat exchanger first end refrigerant enthalpy according to generation D7With the enthalpy h of saturation refrigerantIt is vented saturationGenerate refrigerant enthalpy h7.Wherein, Δ t7=t7-t6,h7=D7·hIt is vented saturation+d7, its In, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, refrigerant enthalpy generation module 20 can directly calculate the system at the end of indoor heat exchanger second Cryogen enthalpy h5：h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.
In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software Fruit, or the refrigerant enthalpy by each temperature detecting point of other approach acquisition.For example, when the current working of air conditioner is During heating condition, refrigerant enthalpy generation module 20 can also be according to the high-pressure in air conditioner, gas returning port temperature t1, interior changes Hot device first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With the refrigerant enthalpy h of indoor heat exchanger first end7, And can be according to the high-pressure in air conditioner, exhaust port temperatures t2, the second end of indoor heat exchanger temperature t5Respectively obtain exhaust outlet Refrigerant enthalpy h2With the refrigerant enthalpy h at the end of indoor heat exchanger second5。
In an embodiment of the present invention, heating capacity generation module 50 can generate the heating capacity of air conditioner according to below equation：Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor compressor horsepower.
Because the current working of air conditioner is heating condition, thus efficiency generation module 40 can be according to air conditioner power consumption With the heat efficiency of heating capacity generation air conditioner, specifically, the heat efficiency of air conditioner is the heating capacity and power consumption work(of air conditioner The ratio between rate, i.e. COP=QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor, the housing heat dissipation capacity of air conditioner power consumption and compressor, and obtained by corresponding temperature sensor Gas returning port in compressor, exhaust outlet, the temperature of the end of indoor heat exchanger second and indoor heat exchanger first end, and at air conditioner By refrigerant enthalpy generation module, heating capacity generation module and efficiency generation module according to above-mentioned each position when heating condition The refrigerant enthalpy for the above-mentioned each position of temperature generation put, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, The refrigerant enthalpy and air conditioner power consumption of above-mentioned each position obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving heating effect.
In summary, the air conditioner of the embodiment of the present invention and its efficiency computational methods and system, by obtaining air conditioner system The physical property of refrigerant in refrigerant cycle system, and the physical property of combination refrigerant and the leakage enthusiasm condition of compressor calculate To the power of air conditioner, and the efficiency of air conditioner is further calculated, so as to be able to real-time and accurately detect air conditioner Refrigeration efficiency and heat efficiency.
In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom ", " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, it is for only for ease of and describes the present invention and simplify description, rather than indicates or imply that signified device or element must There must be specific orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.
In addition, term " first ", " second " are only used for describing purpose, and it is not intended that instruction or hint relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can be expressed or Implicitly include one or more this feature.In the description of the invention, " multiple " are meant that two or more, Unless otherwise specifically defined.
In the present invention, unless otherwise clearly defined and limited, term " installation ", " connected ", " connection ", " fixation " etc. Term should be interpreted broadly, for example, it may be fixedly connected or be detachably connected, or integrally；Can be that machinery connects Connect or electrically connect；Can be joined directly together, can also be indirectly connected by intermediary, can be in two elements The connection in portion or the interaction relationship of two elements.For the ordinary skill in the art, can be according to specific feelings Condition understands the concrete meaning of above-mentioned term in the present invention.
In the present invention, unless otherwise clearly defined and limited, fisrt feature can be with "above" or "below" second feature It is that the first and second features directly contact, or the first and second features pass through intermediary mediate contact.Moreover, fisrt feature exists Second feature " on ", " top " and " above " but fisrt feature are directly over second feature or oblique upper, or be merely representative of Fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be One feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height and is less than second feature.
In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means specific features, structure, material or the spy for combining the embodiment or example description Point is contained at least one embodiment or example of the present invention.In this manual, to the schematic representation of above-mentioned term not Identical embodiment or example must be directed to.Moreover, specific features, structure, material or the feature of description can be with office Combined in an appropriate manner in one or more embodiments or example.In addition, in the case of not conflicting, the skill of this area Art personnel can be tied the different embodiments or example and the feature of different embodiments or example described in this specification Close and combine.
Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is example Property, it is impossible to limitation of the present invention is interpreted as, one of ordinary skill in the art within the scope of the invention can be to above-mentioned Embodiment is changed, changed, replacing and modification.

Claims (28)

1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
Obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4、 Indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With indoor environment temperature t9；
According to the indoor environment temperature t9With the outdoor heat exchanger first end temperature t4Generate the return-air of gas returning port in compressor Mouth temperature t1, and according to the indoor environment temperature t9With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first Hold temperature t7；
When the current working of the air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in the compressor1It is raw Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet Enthalpy h2, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generate outdoor heat exchanger first end Refrigerant enthalpy h4With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generate indoor heat exchanger the The refrigerant enthalpy h of one end7；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port refrigerant enthalpy h1、 The refrigerant enthalpy h of the exhaust outlet2, the outdoor heat exchanger first end refrigerant enthalpy h4With the indoor heat exchanger The refrigerant enthalpy h of one end7Generate the refrigerating capacity of air conditioner；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to gas returning port in the compressor Gas returning port temperature t1Generate the refrigerant enthalpy h of gas returning port1Specifically include：
According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the indoor heat exchanger middle portion temperature t6Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigeration Agent enthalpy h1。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that the suction is generated according to below equation The enthalpy h of saturation refrigerant at a temperature of gasAir-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
4. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that returned according to below equation generation The modifying factor D of gas port refrigerant enthalpy1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6,
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 3, it is characterised in that according to the indoor heat exchanger first The indoor heat exchanger first end temperature t at end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：
According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturation Generate the refrigerant enthalpy h7。
6. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that the room is generated according to below equation The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to exhaust outlet in the compressor Exhaust port temperatures t2Generate the refrigerant enthalpy h of exhaust outlet2Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the exhaust port temperatures t of exhaust outlet in the compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Spend Δ t2；
According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2。
8. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t3+d4(Δt2)2t3+d5(Δt2)t2 3+d6(Δt2)2t2 3,
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated according to below equation The refrigerant enthalpy h of external heat exchanger first end4：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation The refrigerating capacity of air conditioner：
Wherein, QRefrigerating capacityFor the refrigerating capacity of the air conditioner, PCompressorFor the work(of the compressor Rate.
11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation The housing heat dissipation capacity Q of compressorloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor ×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, t8For the temperature at outdoor heat exchanger fin.
12. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation Gas returning port temperature t1With the indoor heat exchanger first end temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is the running frequency of the compressor, and a, b, c is fitting coefficient.
13. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, realize as in claim 1-12 The efficiency computational methods of any described air conditioner.
14. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The efficiency computational methods of the air conditioner as described in any in claim 1-12 are realized when calculation machine program is executed by processor.
15. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
Obtain the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4、 The second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6 With indoor environment temperature t9；
According to indoor environment temperature t9With the outdoor heat exchanger first end temperature t4Generate the gas returning port temperature of gas returning port in compressor Spend t1, and according to the indoor environment temperature t9With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end temperature Spend t7；
When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1It is raw Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the end of indoor heat exchanger second Refrigerant enthalpy h5With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generate indoor heat exchanger the The refrigerant enthalpy h of one end7；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port refrigerant enthalpy h1、 The refrigerant enthalpy h of the exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5With the indoor heat exchanger The refrigerant enthalpy h of one end7Generate the heating capacity of air conditioner；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
16. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that described according in the compressor The gas returning port temperature t of gas returning port1Generate the refrigerant enthalpy h of gas returning port1Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationIt is raw Into the refrigerant enthalpy h of the gas returning port1。
17. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that according to generating below equation The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
18. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that according to generating below equation The modifying factor D of gas returning port refrigerant enthalpy1：
<mrow> <msub> <mi>D</mi> <mn>1</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
19. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that be vented according in the compressor The exhaust port temperatures t of mouth2Generate the refrigerant enthalpy h of exhaust outlet2Specifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate the enthalpy of saturation refrigerant under delivery temperature hIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2。
20. the efficiency computational methods of the air conditioner described in claim 19, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6,
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
21. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that according to the indoor heat exchanger The indoor heat exchanger first end temperature t of one end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor heat exchanger first end temperature t7It is raw Into degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation refrigerant under the delivery temperature Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7。
22. the efficiency computational methods of air conditioner as claimed in claim 21, it is characterised in that according to generating below equation The modifying factor D of indoor heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
23. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to calculating below equation The refrigerant enthalpy h at the end of indoor heat exchanger second5：
h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
24. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to generating below equation The heating capacity of air conditioner：
Wherein, QHeating capacityFor the heating capacity of the air conditioner, PCompressorFor the compressor Power.
25. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to generating below equation The housing heat dissipation capacity Q of compressorloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×ACompressor ×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, t8For the temperature at outdoor heat exchanger fin.
26. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to generating below equation Gas returning port temperature t1With the indoor heat exchanger first end temperature t7：
t1=a*t9+b*t4+ c*f,
t7=a*t9+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c is fitting coefficient.
27. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, realize as in claim 15-26 Any described method.
28. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 15-26 is realized when calculation machine program is executed by processor.
CN201710772633.8A 2017-08-31 2017-08-31 Air conditioner and its efficiency computational methods Pending CN107514764A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201710772633.8A CN107514764A (en) 2017-08-31 2017-08-31 Air conditioner and its efficiency computational methods

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201710772633.8A CN107514764A (en) 2017-08-31 2017-08-31 Air conditioner and its efficiency computational methods

Publications (1)

Publication Number Publication Date
CN107514764A true CN107514764A (en) 2017-12-26

Family

ID=60724668

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201710772633.8A Pending CN107514764A (en) 2017-08-31 2017-08-31 Air conditioner and its efficiency computational methods

Country Status (1)

Country Link
CN (1) CN107514764A (en)

Citations (5)

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

Patent Citations (5)

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

Non-Patent Citations (5)

* Cited by examiner, † Cited by third party
Title
（美）辛格（SINGH,R.P.）等著，许学勤译: "《食品工程导论（第三版）》", 31 August 2006, 北京：中国轻工业出版社 *
周光辉等: "制冷剂HCFC-124热力性质计算研究", 《低温与超导》 *
苏晶等: "R410A热力性质的拟合计算", 《制冷与空调》 *
郑兆志等: "《家用空调维修安装技术》", 31 March 2006, 中国科学技术出版社 *
郑旭煦等: "《化工原理》", 31 January 2016, 华中科技大学出版社 *

Similar Documents

Publication Publication Date Title
CN107328041A (en) Air conditioner and its efficiency computational methods
CN107367030A (en) Air conditioner and its efficiency computational methods
CN107514764A (en) Air conditioner and its efficiency computational methods
CN107514782A (en) Air conditioner and its efficiency computational methods
CN107490140A (en) Air conditioner and its efficiency computational methods
CN107514771A (en) Air conditioner and its efficiency computational methods
CN107388515A (en) Air conditioner and its efficiency computational methods
CN107514766A (en) Air conditioner and its efficiency computational methods
CN107504649A (en) Air conditioner and its efficiency computational methods
CN107388520A (en) Air conditioner and its efficiency computational methods
CN107514760A (en) Air conditioner and its efficiency computational methods
CN107328052A (en) Air conditioner and its efficiency computational methods
CN107328045A (en) Air conditioner and its efficiency computational methods
CN107328056A (en) Air conditioner and its efficiency computational methods
CN107388519A (en) Air conditioner and its efficiency computational methods
CN107525240A (en) Air conditioner and its efficiency computational methods
CN107328048A (en) Air conditioner and its efficiency computational methods
CN107490146A (en) Air conditioner and its efficiency computational methods
CN107328055A (en) Air conditioner and its efficiency computational methods
CN107328054A (en) Air conditioner and its efficiency computational methods
CN107514765A (en) Air conditioner and its efficiency computational methods
CN107514762A (en) Air conditioner and its efficiency computational methods
CN107328053A (en) Air conditioner and its efficiency computational methods
CN107514763A (en) Air conditioner and its efficiency computational methods
CN107514769A (en) Air conditioner and its efficiency computational methods

Legal Events

Date Code Title Description
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
RJ01 Rejection of invention patent application after publication
RJ01 Rejection of invention patent application after publication

Application publication date: 20171226