CN107514778A - Air conditioner and its efficiency computational methods - Google Patents

Air conditioner and its efficiency computational methods Download PDF

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Publication number
CN107514778A
CN107514778A CN201710775524.1A CN201710775524A CN107514778A CN 107514778 A CN107514778 A CN 107514778A CN 201710775524 A CN201710775524 A CN 201710775524A CN 107514778 A CN107514778 A CN 107514778A
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msub
enthalpy
heat exchanger
refrigerant
mrow
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Inventor
刘燕飞
李金波
戚文端
杨亚新
汪亚涛
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GD Midea Air Conditioning Equipment Co Ltd
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Guangdong Midea Refrigeration Equipment Co Ltd
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Abstract

The invention discloses a kind of air conditioner and its efficiency computational methods and system, methods described to include：Obtain the current working and power consumption, the power of compressor, the high side pressure of exhaust outlet and exhaust port temperatures t of air conditioner2, gas returning port low-pressure lateral pressure and gas returning port temperature t1, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4With the indoor heat exchanger first end temperature t of indoor heat exchanger first end7；When the current working of air conditioner is cooling condition, according to t1、t2, high side pressure, low-pressure lateral pressure, t4And t7The refrigerant enthalpy and lubricating oil enthalpy of gas returning port, exhaust outlet, outdoor heat exchanger first end and indoor heat exchanger first end are generated respectively；According to above-mentioned refrigerant enthalpy and lubricating oil enthalpy generation mixture enthalpy h1、h2、h4And h7；According to power, h1、h2、h4And h7Generate the refrigerating capacity of air conditioner；According to the efficiency of power consumption and refrigerating capacity generation air conditioner, so as to realize the real-time accurate detection to energy efficiency of air conditioner.

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 and a kind of air-conditioning Device.
Background technology
As country increasingly payes attention to energy-conservation, consumer comfortably requires also more and more higher to the energy-conservation of air conditioner.Mesh Before, during air conditioner is run, due to that can not detect the situation of change of energy efficiency of air conditioner in real time, thus air conditioner is difficult to tie up Hold in preferable running status, so that refrigeration, heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.
Therefore, first purpose of the present invention is the efficiency computational methods for proposing a kind of air conditioner, can be accurate in real time Ground detects the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
Fourth object of the present invention is the efficiency computational methods for proposing another air conditioner.
The 5th purpose of the present invention is to propose another air conditioner.
The 6th purpose of the present invention is to propose another non-transitorycomputer readable storage medium.
To reach above-mentioned purpose, first aspect present invention embodiment proposes a kind of efficiency computational methods of air conditioner, bag Include following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain exhaust outlet of compressor High side pressure；Obtain the low-pressure lateral pressure of compressor return air mouth；Obtain the gas returning port temperature t of gas returning port in compressor1, institute State the exhaust port temperatures t of exhaust outlet in compressor2, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4And interior The indoor heat exchanger first end temperature t of heat exchanger first end7；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 compressor1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantWith Lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate and arrange with the high side pressure The refrigerant enthalpy h of gas port2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the outdoor heat exchanger of the outdoor heat exchanger first end One end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilWith according to the interior The indoor heat exchanger first end temperature t of heat exchanger first end7With the system of low-pressure lateral pressure generation indoor heat exchanger first end Cryogen enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil Generate the mixture enthalpy h of exhaust outlet2, according to the refrigerant enthalpy h of the outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixture enthalpy h of outdoor heat exchanger first end4, according to the refrigerant enthalpy of the indoor heat exchanger first end h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；According to the power of the compressor, The mixture enthalpy h of the gas returning port1, the exhaust outlet mixture enthalpy h2, the outdoor heat exchanger first end mixture Enthalpy h4With the mixture enthalpy h of the indoor heat exchanger first end7Generate the refrigerating capacity of air conditioner；And according to the air-conditioning Device power consumption and the refrigerating capacity generate the efficiency of the air conditioner.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The power and air conditioner power consumption of machine, and obtain the high side pressure of exhaust outlet of compressor, the low-pressure side of compressor return air mouth Exhaust port temperatures of exhaust outlet in the gas returning port temperature of gas returning port, compressor in pressure, compressor, outdoor heat exchanger first end The indoor heat exchanger first end temperature of outdoor heat exchanger first end temperature and indoor heat exchanger first end, and when air conditioner is in During cooling condition, above-mentioned each temperature is generated according to the temperature of above-mentioned each temperature detecting point, high side pressure and low-pressure lateral pressure The refrigerant enthalpy and lubricating oil enthalpy of test point are spent, and further generates the mixture enthalpy of each temperature detecting point, then According to the refrigerating capacity of the power of compressor and the mixture enthalpy of multiple temperature detecting points generation air conditioner, finally according to air conditioner The efficiency of power consumption and refrigerating capacity generation air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, so as to just In the running status for optimizing air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the purpose of refrigeration.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1With it is described Low-pressure lateral pressure generates the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：Obtain the indoor heat exchanger in the middle part of indoor heat exchanger Middle portion temperature t6；According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；Root The enthalpy h of saturation refrigerant under suction temperature is generated according to the low-pressure lateral pressureAir-breathing saturation；According to the suction superheat Δ t1With The indoor heat exchanger middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the gas returning port refrigerant The modifying factor D of enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h1 refrigerant。
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For Overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end Temperature t7With the refrigerant enthalpy h of low-pressure lateral pressure generation indoor heat exchanger first end7 refrigerantsSpecifically include：According to the room Interior heat exchanger first end temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to institute State the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the system Cryogen enthalpy h7 refrigerants。
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 exhaust port temperatures t according to exhaust outlet in the compressor2With it is described The enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsSpecifically include：Obtain the outdoor heat exchange in the middle part of outdoor heat exchanger Device middle portion temperature t3；The enthalpy h of saturation refrigerant under delivery temperature is generated according to the high side pressureIt is vented saturation；According to the pressure The exhaust port temperatures t of exhaust outlet in contracting machine2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to institute State discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；Root According to the modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant of the exhaust outlet Enthalpy h2 refrigerants。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
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 refrigerants：
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 refrigerating capacity of the air conditioner, PCompressorFor the compressor Power.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation hI lubricating oil：
hI lubricating oil=-0.0808+1.7032ti+0.0025ti 2, wherein, i is positive integer, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each point is calculated according to below equationi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil,
Cg=f/104, wherein, i is positive integer, CgFor oil content, f is the running frequency of the compressor.
To reach above-mentioned purpose, second aspect of the present invention embodiment proposes a kind of air conditioner, and it includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, meter described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
To reach above-mentioned purpose, third aspect present invention embodiment proposes a kind of non-transitory computer-readable storage medium Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor The efficiency computational methods of the air conditioner of proposition.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
To reach above-mentioned purpose, fourth aspect present invention embodiment proposes the efficiency computational methods of another air conditioner, Comprise the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain compressor air-discharging The high side pressure of mouth；Obtain the low-pressure lateral pressure of compressor return air mouth；Obtain the gas returning port temperature t of gas returning port in compressor1、 The exhaust port temperatures t of exhaust outlet in the compressor2, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5And room The indoor heat exchanger first end temperature t of interior heat exchanger first end7；When the current working of the air conditioner is heating condition, root According to the gas returning port temperature t of gas returning port in the compressor1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerant With lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate and be vented with the high side pressure The enthalpy h of the refrigerant of mouth2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the indoor heat exchanger at the end of indoor heat exchanger second Two end temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith according to the interior The indoor heat exchanger first end temperature t of heat exchanger first end7With the system of high side pressure generation indoor heat exchanger first end Cryogen enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the enthalpy h of the refrigerant of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsAnd lubrication Oily enthalpy h5 lubricating oilGenerate the mixture enthalpy h at the end of indoor heat exchanger second5, according to the refrigeration of the indoor heat exchanger first end Agent enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7；According to the compressor Power, the mixture enthalpy h of the gas returning port1, the exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second Mixture enthalpy h5With the mixture enthalpy h of the indoor heat exchanger first end7Generate the heating capacity of air conditioner；And according to The air conditioner power consumption and the heating capacity generate the efficiency of the air conditioner.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The power and air conditioner power consumption of machine, and obtain the high side pressure of exhaust outlet of compressor, the low-pressure side of compressor return air mouth Exhaust port temperatures of exhaust outlet in the gas returning port temperature of gas returning port, compressor in pressure, compressor, outdoor heat exchanger first end The indoor heat exchanger first end temperature of outdoor heat exchanger first end temperature and indoor heat exchanger first end, and when air conditioner is in During heating condition, above-mentioned each temperature is generated according to the temperature of above-mentioned each temperature detecting point, high side pressure and low-pressure lateral pressure The refrigerant enthalpy and lubricating oil enthalpy of test point are spent, and further generates the mixture enthalpy of each temperature detecting point, then According to the power of compressor and the heating capacity of the mixture enthalpy of multiple temperature detecting points generation air conditioner, finally according to air conditioner The efficiency of power consumption and heating capacity generation air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, so as to just In the running status for optimizing air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the purpose of heating effect.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1With it is described Low-pressure lateral pressure generates the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：Obtain the outdoor heat exchanger in the middle part of outdoor heat exchanger Middle portion temperature t3；According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；Root According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor of gas returning port refrigerant enthalpy D1；The enthalpy h of saturation refrigerant under suction temperature is generated according to the low-pressure lateral pressureAir-breathing saturation；According to the gas returning port refrigerant The modifying factor D of enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy of the gas returning port Value h1 refrigerant。
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For Overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2With it is described The enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsSpecifically include：Obtain the indoor heat exchange in the middle part of indoor heat exchanger Device middle portion temperature t6；According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With exhaust outlet in the compressor Exhaust port temperatures t2Generate discharge superheat Δ t2；According to the discharge superheat Δ t2With temperature in the middle part of the indoor heat exchanger Spend t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；Saturation under delivery temperature is generated according to the high side pressure to freeze The enthalpy h of agentIt is vented saturation；According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, saturation refrigerant under the delivery temperature Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6 For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end Temperature t7With the refrigerant enthalpy h of high side pressure generation indoor heat exchanger first end7 refrigerantsSpecifically include：According to the room Indoor heat exchanger middle portion temperature t in the middle part of interior heat exchanger6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7； According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generation indoor heat exchanger first end refrigerant enthalpy is repaiied Positive divisor D7；According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation is freezed under the delivery temperature The enthalpy h of agentIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerants。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-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 refrigerants：
Wherein, c1-c4 is supercooling fauna number 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 the air conditioner, PCompressorFor the compressor Power.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation hI lubricating oil：
hI lubricating oil=-0.0808+1.7032ti+0.0025ti 2, wherein, i is positive integer, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each point is calculated according to below equationi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil,
Cg=f/104, wherein, i is positive integer, CgFor oil content, f is the running frequency of the compressor.
To reach above-mentioned purpose, fifth aspect present invention embodiment proposes another air conditioner, and it includes memory, place Manage device and be stored in the computer program that can be run on the memory and on the processor, described in the computing device During computer program, the efficiency computational methods for the air conditioner that 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, sixth aspect present invention embodiment proposes the computer-readable storage of another non-transitory Medium, is stored thereon with computer program, and the computer program realizes that 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 structural representation of air conditioner according to an embodiment of the invention；
Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention；
Fig. 3 is the block diagram of the efficiency computing system of air conditioner according to an embodiment of the invention；
Fig. 4 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention；And
Fig. 5 is the block diagram of the efficiency computing system of air conditioner in accordance with another embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
Efficiency computational methods, air conditioner, the non-transitory of the air conditioner of the embodiment of the present invention described below in conjunction with the accompanying drawings The efficiency computing system of computer-readable recording medium and air conditioner.
In an embodiment of the present invention, air conditioner can be single-stage vapor compression formula air conditioner.
As shown in figure 1, the air conditioner of the embodiment of the present invention may include compressor 100, four-way valve 200, outdoor heat exchanger 300th, restricting element 400 and indoor heat exchanger 500.Wherein, the exhaust outlet of compressor 100 passes through four-way valve 200 and outdoor heat exchange Second end of device 300 is connected, and the first end of outdoor heat exchanger 300 passes through the second end of restricting element 400 and indoor heat exchanger 500 It is connected, the first end of indoor heat exchanger 500 is connected by four-way valve 200 with the gas returning port of compressor 100.
When the current working of air conditioner is cooling condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A2 ends are directly connected with outdoor heat exchanger 300, and refrigerant is flowed to as shown in the solid arrow in Fig. 1.Specifically, from compressor 100 Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A2 ends flow into outdoor heat exchanger 300 (now As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after outdoor heat exchanger 300 condenses heat release Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of restricting element 400, low-temp low-pressure liquid refrigerant stream enters indoor heat exchanger 500 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gaseous coolant after the evaporation endothermic of indoor heat exchanger 500 A4 ends and A3 ends through four-way valve 200 flow into the gas returning port of compressor 100, pass through the low-temp low-pressure of the gas returning port of compressor 100 Gaseous coolant enters compressor 100, so far completes refrigerative circle system.
When the current working of air conditioner is heating condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A4 ends are directly connected with indoor heat exchanger 500, and refrigerant is flowed to as shown in the dotted arrow in Fig. 1.Specifically, from compressor 100 Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A4 ends flow into indoor heat exchanger 500 (now As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after indoor heat exchanger 500 condenses heat release Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of restricting element 400, low-temp low-pressure liquid refrigerant stream enters outdoor heat exchanger 300 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gaseous coolant after the evaporation endothermic of outdoor heat exchanger 300 A2 ends and A3 ends through four-way valve 200 flow into the gas returning port of compressor 100, pass through the low-temp low-pressure of the gas returning port of compressor 100 Gaseous coolant enters compressor 100, so far completes heating cyclic process.
Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention.As shown in Fig. 2 should The efficiency computational methods of air conditioner may include following steps：
S101, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner PCompressorWith air conditioner power consumption PPower consumption。
S102, obtain the high side pressure of exhaust outlet of compressor.
Specifically, can be by being arranged on the exhaust outlet of compressor to the high side pressure of the optional position between restricting element Sensor obtains the high side pressure P of exhaust outlet of compressorHigh pressure。
S103, obtain the low-pressure lateral pressure of compressor return air mouth.
Specifically, can be passed by being arranged on the low-pressure lateral pressure of optional position between restricting element and the gas returning port of compressor Sensor obtains the low-pressure lateral pressure P of compressor return air mouthLow pressure。
S104, obtain the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room The outdoor heat exchanger first end temperature t of external heat exchanger first end4With the indoor heat exchanger first end temperature of indoor heat exchanger first end Spend t7。
Specifically, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature of the temperature detecting point Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature t1；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t2；By setting The temperature sensor (as shown in Figure 1 04) put in outdoor heat exchanger first end obtains outdoor heat exchanger first end temperature t4；It is logical Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end t7。
Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, freezes in test During the temperature of agent tube wall, refrigerant tube wall can take Insulation, and the installation site of temperature sensor is examined as close to temperature Measuring point.For example, temperature sensor can be arranged on to corresponding temperature detecting point and be close to copper pipe, and by being incubated adhesive tape pair Copper pipe is wound sealing.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
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 With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to exhaust outlet in compressor Exhaust port temperatures t2With the refrigerant enthalpy h of high side pressure generation exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to outdoor The outdoor heat exchanger first end temperature t of heat exchanger first end4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsAnd profit Lubricating oil enthalpy h4 lubricating oilWith the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Room is generated with low-pressure lateral pressure The refrigerant enthalpy h of interior heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil。
Specifically, during air conditioner works, due to the mixing of the refrigerant and lubricating oil of different temperatures test point The state of thing is different, therefore the refrigerant enthalpy of different temperatures test point and lubricating oil enthalpy are different.At one of the present invention In embodiment, rule of thumb refrigerant enthalpy and lubricating oil enthalpy can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、 The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end refrigerant enthalpy h4 refrigerantsAnd profit Lubricating oil enthalpy h4 lubricating oil, indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilDetailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is cooling condition When, the refrigerant superheat of the gas returning port of compressor, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1 refrigerant。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Given birth to low-pressure lateral pressure Into the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；Root According to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；Air-breathing is generated according to low-pressure lateral pressure At a temperature of saturation refrigerant enthalpy hAir-breathing saturation；According to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate gas returning port The modifying factor D of refrigerant enthalpy1；According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturation Generate refrigerant enthalpy h1 refrigerant。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (1)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger Interior heat exchanger middle portion temperature t6.Getting gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Afterwards, according to following formula (2) suction superheat Δ t is generated1：
Δt1=t1-t6 (2)
Getting suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Afterwards, return-air is generated according to above-mentioned formula (1) The modifying factor D of mouth refrigerant enthalpy1.Meanwhile according to low-pressure lateral pressure PLow pressureFirst generate air-breathing saturation temperature Tl：Further according to air-breathing saturation temperature TlGenerate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation： hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4Tl 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, refrigerant enthalpy h is generated according to following formula (3)1 refrigerant：
h1 refrigerant=D1·hAir-breathing saturation+d7 (3)
Wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is refrigeration During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the The refrigerant enthalpy h of one end7 refrigerants。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7With Low-pressure lateral pressure generates the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：According to indoor heat exchanger first end Temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；According to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6 Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to repairing for indoor heat exchanger first end refrigerant enthalpy Positive divisor D7, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h7 refrigerants。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (4)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, indoor heat exchanger first end temperature t is being got7With indoor heat exchanger middle portion temperature t6Afterwards, under State formula (5) generation degree of superheat Δ t7：
Δt7=t7-t6 (5)
Getting degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Afterwards, indoor heat exchange is generated according to above-mentioned formula (4) The modifying factor D of device first end refrigerant enthalpy7.Meanwhile according to low-pressure lateral pressure PLow pressureFirst generate air-breathing saturation temperature Tl：Further according to air-breathing saturation temperature TlGenerate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation： hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4Tl 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, refrigerant enthalpy h is generated according to following formula (6)7 refrigerants：
h7 refrigerants=D7·hAir-breathing saturation+d7 (6)
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2 refrigerants。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Given birth to high side pressure Into the refrigerant enthalpy h of exhaust outlet2 refrigerantsSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；Root The enthalpy h of saturation refrigerant under delivery temperature is generated according to high side pressureIt is vented saturation；According to the exhaust outlet temperature of exhaust outlet in compressor Spend t2With outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to discharge superheat Δ t2In outdoor heat exchanger Portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to modifying factor D2, saturation refrigerant under delivery temperature Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (7)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t3.Getting exhaust port temperatures t2With outdoor heat exchanger middle portion temperature t3Afterwards, according to following formula (8) discharge superheat Δ t is generated2：
Δt2=t2-t3 (8)
Getting discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Afterwards, exhaust outlet system is generated according to above-mentioned formula (7) The modifying factor D of cryogen enthalpy2.Meanwhile according to high side pressure PHigh pressureMr. into exhaust saturation temperature Th： Further according to exhaust saturation temperature ThGenerate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation：Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, the refrigerant enthalpy h of exhaust outlet is generated according to following formula (9)2 refrigerants：
h2 refrigerants=D2·hIt is vented saturation+d7 (9)
For the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants, when the current working of air conditioner is cooling condition, The refrigerant supercooling of outdoor heat exchanger first end, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants。
According to one embodiment of present invention, the refrigerant enthalpy of outdoor heat exchanger first end is generated according to following formula (10) Value h4 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system The species of cryogen is relevant, and R410A refrigerants and saturation region coefficient, overheated zone corresponding to R32 refrigerants are respectively illustrated in table 1 Coefficient and supercooling fauna number：
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, according to one embodiment of present invention, according to following public affairs Formula (11) calculates the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil：
hI lubricating oil=-0.0808+1.7032ti+0.0025ti 2 (11)
Wherein, tiFor the temperature of temperature detecting point, i is positive integer.Thus, the lubricating oil enthalpy of gas returning port can be calculated out Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end lubricating oil enthalpy h4 lubricating oilAnd indoor heat exchanger The lubricating oil enthalpy h of first end7 lubricating oil。
S106, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port Value h1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to The refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixture of outdoor heat exchanger first end Enthalpy h4, according to the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate indoor heat exchanger the The mixture enthalpy h of one end7。
According to one embodiment of present invention, oil content C can be calculated by following formula (12)g：
Cg=f/104 (12)
Wherein, f is the running frequency of compressor.
Further, the mixture enthalpy h of each point is calculated according to following formula (13)i：
hi=(1-Cg)hI refrigerants+CghI lubricating oil (13)
Wherein, i is positive integer, CgFor oil content.
Thus, the mixture enthalpy h of gas returning port can be calculated out1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger The mixture enthalpy h of first end4With the mixture enthalpy h of indoor heat exchanger first end7。
S107, according to the power of compressor, the mixture enthalpy h of gas returning port1, exhaust outlet mixture enthalpy h2, outdoor changes The mixture enthalpy h of hot device first end4With the mixture enthalpy h of indoor heat exchanger first end7Generate the refrigerating capacity of air conditioner.
According to one embodiment of present invention, the refrigerating capacity of air conditioner is generated according to following formula (14)：
Wherein, QRefrigerating capacityFor the refrigerating capacity of air conditioner, PCompressorFor the power of compressor.
S108, 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, is obtaining air conditioner power consumption PPower consumptionWith refrigerating capacity QRefrigerating capacityAfterwards, can be according to following formula (15) the efficiency EER of air conditioner is generated：
EER=QRefrigerating capacity/PPower consumption (15)
, 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.
In summary, the efficiency computational methods of air conditioner according to embodiments of the present invention, by obtaining the current of air conditioner Operating mode, the power of compressor and air conditioner power consumption, and obtain the high side pressure of exhaust outlet of compressor, compressor return air mouth Low-pressure lateral pressure, in compressor in the gas returning port temperature of gas returning port, compressor exhaust outlet exhaust port temperatures, outdoor heat exchanger The outdoor heat exchanger first end temperature of first end and the indoor heat exchanger first end temperature of indoor heat exchanger first end, and when sky When tune device is in cooling condition, according in the generation of the temperature of above-mentioned each temperature detecting point, high side pressure and low-pressure lateral pressure The refrigerant enthalpy and lubricating oil enthalpy of each temperature detecting point are stated, and further generates the mixture enthalpy of each temperature detecting point Value, the refrigerating capacity of air conditioner, last root are then generated according to the power of compressor and the mixture enthalpy of multiple temperature detecting points According to the efficiency of air conditioner power consumption and refrigerating capacity generation air conditioner.Thereby, it is possible to real-time and accurately detect the energy of air conditioner Effect, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve refrigeration Purpose.
In addition, embodiments of the invention also proposed a kind of air conditioner, it includes memory, processor and is stored in storage On device and the computer program that can run on a processor, during computing device computer program, the above-mentioned implementation of the present invention is realized The efficiency computational methods for the air conditioner that example proposes.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
In addition, embodiments of the invention also proposed a kind of non-transitorycomputer readable storage medium, it is stored thereon with Computer program, realize that the efficiency for the air conditioner that the above embodiment of the present invention proposes calculates when computer program is executed by processor Method.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
Fig. 3 is the block diagram of the efficiency computing system of air conditioner according to an embodiment of the invention.Such as Fig. 3 institutes Show, the efficiency computing system of the air conditioner includes：Acquisition module 10, first pressure sensor 21, second pressure sensor 22, return Gas port temperature sensor 01, exhaust port temperatures sensor 02, outdoor heat exchanger first end temperature sensor 04, indoor heat exchanger One end temperature sensor 07, refrigerant enthalpy generation module 30, refrigerating capacity generation module 40 and efficiency generation module 50.
Wherein, acquisition module 10 is used to obtain the current working of air conditioner, the power of compressor and air conditioner power consumption. First pressure sensor 21 is used for the high side pressure for obtaining exhaust outlet of compressor.Second pressure sensor 22, which is used to obtain, to be compressed The low-pressure lateral pressure of machine gas returning port.Gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1。 Exhaust port temperatures sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2.The end sensor of outdoor heat exchanger first The 04 outdoor heat exchanger first end temperature t for obtaining outdoor heat exchanger first end4.The first end sensor of indoor heat exchanger 07 is used In the indoor heat exchanger first end temperature t for obtaining indoor heat exchanger first end7。
Mixture enthalpy generation module 30 is used for when the current working of air conditioner is cooling condition, is returned according in compressor The gas returning port temperature t of gas port1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, root According to the exhaust port temperatures t of exhaust outlet in compressor2With the refrigerant enthalpy h of high side pressure generation exhaust outlet2 refrigerantsAnd lubricating oil Enthalpy h2 lubricating oil, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4Generate the system of outdoor heat exchanger first end Cryogen enthalpy h4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilWith the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7With Low-pressure lateral pressure generates the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, and according to return-air The refrigerant enthalpy h of mouth1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the refrigeration of exhaust outlet Agent enthalpy h2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to the system of outdoor heat exchanger first end Cryogen enthalpy h4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixture enthalpy h of outdoor heat exchanger first end4, according to indoor heat exchange The refrigerant enthalpy h of device first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7。
Refrigerating capacity generation module 40 is used for power, the mixture enthalpy h of gas returning port according to compressor1, exhaust outlet it is mixed Compound enthalpy h2, outdoor heat exchanger first end mixture enthalpy h4With the mixture enthalpy h of indoor heat exchanger first end7Generation The refrigerating capacity of air conditioner.Efficiency generation module 50 is used for the efficiency that air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
It should be noted that the details not disclosed in the efficiency computing system of the air conditioner of the embodiment of the present invention, refer to Details disclosed in the efficiency computational methods of the air conditioner of the embodiment of the present invention, specific I will not elaborate.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor and air conditioner power consumption, the high pressure side pressure of exhaust outlet of compressor is obtained by first pressure sensor Power and second pressure sensor obtain the low-pressure lateral pressure of compressor return air mouth, and are obtained and compressed by corresponding temperature sensor The exhaust port temperatures of exhaust outlet, the outdoor heat exchange of outdoor heat exchanger first end in the gas returning port temperature of gas returning port, compressor in machine The indoor heat exchanger first end temperature of device first end temperature and indoor heat exchanger first end, and when the current working of air conditioner is During cooling condition, by mixture enthalpy generation module according to the temperature of above-mentioned each temperature detecting point, high side pressure and low Lateral pressure is pressed to generate the refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points, and the system according to multiple temperature detecting points Cryogen enthalpy and lubricating oil enthalpy generate the mixture enthalpy of each temperature detecting point, then by refrigerating capacity generation module according to The refrigerating capacity of the power of compressor and the mixture enthalpy of multiple temperature detecting points generation air conditioner, mould is generated finally by efficiency Root tuber generates the efficiency of air conditioner according to air conditioner power consumption and refrigerating capacity.Thereby, it is possible to real-time and accurately detect air conditioner Efficiency, consequently facilitating according to the real-time energy efficiency of air conditioner optimize air conditioner running status, reach energy-conservation and improve refrigeration effect The purpose of fruit.
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.
Fig. 4 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention.As shown in figure 4, The efficiency computational methods of the air conditioner may include following steps：
S201, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner PCompressorWith air conditioner power consumption PPower consumption。
S202, obtain the high side pressure of exhaust outlet of compressor.
Specifically, can be by being arranged on the exhaust outlet of compressor to the high side pressure of the optional position between restricting element Sensor obtains the high side pressure P of exhaust outlet of compressorHigh pressure。
S203, obtain the low-pressure lateral pressure of compressor return air mouth.
Specifically, can be passed by being arranged on the low-pressure lateral pressure of optional position between restricting element and the gas returning port of compressor Sensor obtains the low-pressure lateral pressure P of compressor return air mouthLow pressure。
S204, obtain the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room The second end of indoor heat exchanger temperature t at the interior end of heat exchanger second5With the indoor heat exchanger first end temperature of indoor heat exchanger first end Spend t7。
Specifically, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature of the temperature detecting point Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature t1；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t2；By setting The temperature sensor (as shown in Figure 1 05) for putting the end of heat exchanger second indoors obtains indoor heat exchanger the second end temperature t5；It is logical Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end t7。
Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, freezes in test During the temperature of agent tube wall, refrigerant tube wall can take Insulation, and the installation site of temperature sensor is examined as close to temperature Measuring point.For example, temperature sensor can be arranged on to corresponding temperature detecting point and be close to copper pipe, and by being incubated adhesive tape pair Copper pipe is wound sealing.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
S205, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1 With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to exhaust outlet in compressor Exhaust port temperatures t2With the enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to room The second end of indoor heat exchanger temperature t at the interior end of heat exchanger second5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith Lubricating oil enthalpy h5 lubricating oilWith the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7Generated with high side pressure The refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil。
Specifically, during air conditioner works, due to the mixing of the refrigerant and lubricating oil of different temperatures test point The state of thing is different, therefore the refrigerant enthalpy of different temperatures test point and lubricating oil enthalpy are different.At one of the present invention In embodiment, rule of thumb refrigerant enthalpy and lubricating oil enthalpy can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、 The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end refrigerant enthalpy h4 refrigerantsAnd profit Lubricating oil enthalpy h4 lubricating oil, indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilDetailed process.
For the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the gas returning port of contracting machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1 refrigerant。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Given birth to low-pressure lateral pressure Into the refrigerant enthalpy h of gas returning port1 refrigerantSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；Root According to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to suction superheat Δ t1And room External heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；Suction temperature is generated according to low-pressure lateral pressure The enthalpy h of lower saturation refrigerantAir-breathing saturation；According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant under suction temperature Enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of gas returning port1 refrigerant。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (16)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t3.Getting gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Afterwards, according to following formula (17) suction superheat Δ t is generated1：
Δt1=t1-t3 (17)
Getting suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Afterwards, generated back according to above-mentioned formula (16) The modifying factor D of gas port refrigerant enthalpy1.Meanwhile according to low-pressure lateral pressure PLow pressureFirst generate air-breathing saturation temperature Tl：Further according to air-breathing saturation temperature TlGenerate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation： hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4Tl 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, refrigerant enthalpy h is generated according to following formula (18)1 refrigerant：
h1 refrigerant=D1·hAir-breathing saturation+d7 (18)
Wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2 refrigerants。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Given birth to high side pressure Into the refrigerant enthalpy h of exhaust outlet2 refrigerantsSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；Root According to the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With the exhaust port temperatures t of exhaust outlet in compressor2Generation was vented Temperature Δ t2；According to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate the modifying factor of exhaust outlet refrigerant enthalpy Sub- D2；The enthalpy h of saturation refrigerant under delivery temperature is generated according to high side pressureIt is vented saturation；According to exhaust outlet refrigerant enthalpy Modifying factor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (19)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger Interior heat exchanger middle portion temperature t6.Getting exhaust port temperatures t2With indoor heat exchanger middle portion temperature t6Afterwards, according to following formula (20) discharge superheat Δ t is generated2：
Δt2=t2-t6 (20)
Getting discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Afterwards, generated and arranged according to above-mentioned formula (19) The modifying factor D of gas port refrigerant enthalpy2.Meanwhile according to high side pressure PHigh pressureMr. into exhaust saturation temperature Th：Further according to exhaust saturation temperature ThGenerate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation：Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, the refrigerant enthalpy h of exhaust outlet is generated according to following formula (21)2 refrigerants：
h2 refrigerants=D2·hIt is vented saturation+d7 (21)
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is heating During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the The refrigerant enthalpy h of one end7 refrigerants。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7With High side pressure generates the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：In the middle part of indoor heat exchanger Indoor heat exchanger middle portion temperature t6With indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to degree of superheat Δ t7And room Interior heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to indoor heat exchanger The modifying factor D of one end refrigerant enthalpy7, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate indoor heat exchanger first The refrigerant enthalpy h at end7 refrigerants。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (22)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger is being got6With indoor heat exchanger first end Temperature t7Afterwards, degree of superheat Δ t is generated according to following formula (23)7：
Δt7=t7-t6 (23)
Getting degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Afterwards, interior is generated according to above-mentioned formula (22) to change The modifying factor D of hot device first end refrigerant enthalpy7.Meanwhile according to high side pressure PHigh pressureMr. into exhaust saturation temperature Th：Further according to exhaust saturation temperature ThGenerate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation：Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, refrigerant enthalpy h is generated according to following formula (24)7 refrigerants：
h7 refrigerants=D7·hIt is vented saturation+d7 (24)
For the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, when the current working of air conditioner is heating condition, The refrigerant supercooling at the end of indoor heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants。
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to following formula (25) Value h5 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system The species of cryogen is relevant, and R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheat are respectively illustrated in upper table 1 Fauna number and supercooling fauna number.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, in terms of Calculate the refrigerant enthalpy of each temperature detecting 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 the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil.According to one embodiment of present invention, can be according to following Formula (26) calculates the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil：
hI lubricating oil=-0.0808+1.7032ti+0.0025ti 2 (26)
Wherein, tiFor the temperature of temperature detecting point, i is positive integer.Thus, the lubricating oil enthalpy of gas returning port can be calculated out Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second lubricating oil enthalpy h5 lubricating oilAnd indoor heat exchanger The lubricating oil enthalpy h of first end7 lubricating oil。
S206, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port Value h1, according to the enthalpy h of the refrigerant of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, root According to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixed of the end of indoor heat exchanger second Compound enthalpy h5, according to the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate indoor heat exchange The mixture enthalpy h of device first end7。
According to one embodiment of present invention, oil content C can be calculated by following formula (27)g：
Cg=f/104 (27)
Wherein, f is the running frequency of compressor.
Further, the mixture enthalpy h of each point is calculated according to following formula (28)i：
hi=(1-Cg)hI refrigerants+CghI lubricating oil (28)
Wherein, i is positive integer, CgFor oil content.
Thus, the mixture enthalpy h of gas returning port can be calculated1, exhaust outlet mixture enthalpy h2, indoor heat exchanger The mixture enthalpy h at two ends5With the mixture enthalpy h of indoor heat exchanger first end7。
S207, according to the power of compressor, the mixture enthalpy h of gas returning port1, exhaust outlet mixture enthalpy h2, interior changes The mixture enthalpy h at the hot end of device second5With the mixture enthalpy h of indoor heat exchanger first end7Generate the heating capacity of air conditioner.
According to one embodiment of present invention, the heating capacity of air conditioner is generated according to following formula (29)：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor the power of compressor.
S208, 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, is obtaining air conditioner power consumption PPower consumptionWith heating capacity QHeating capacityAfterwards, can be according to following formula (30) the efficiency COP of air conditioner is generated：
COP=QHeating capacity/PPower consumption (30)
, 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.
In summary, the efficiency computational methods of air conditioner according to embodiments of the present invention, by obtaining the current of air conditioner Operating mode, the power of compressor and air conditioner power consumption, and obtain the high side pressure of exhaust outlet of compressor, compressor return air mouth Low-pressure lateral pressure, in compressor in the gas returning port temperature of gas returning port, compressor exhaust outlet exhaust port temperatures, outdoor heat exchanger The outdoor heat exchanger first end temperature of first end and the indoor heat exchanger first end temperature of indoor heat exchanger first end, and when sky When tune device is in heating condition, according in the generation of the temperature of above-mentioned each temperature detecting point, high side pressure and low-pressure lateral pressure The refrigerant enthalpy and lubricating oil enthalpy of each temperature detecting point are stated, and further generates the mixture enthalpy of each temperature detecting point Value, the heating capacity of air conditioner, last root are then generated according to the power of compressor and the mixture enthalpy of multiple temperature detecting points According to the efficiency of air conditioner power consumption and heating capacity generation air conditioner.Thereby, it is possible to real-time and accurately detect the energy of air conditioner Effect, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve heating effect Purpose.
In addition, embodiments of the invention also proposed another air conditioner, it includes memory, processor and is stored in On reservoir and the computer program that can run on a processor, during computing device computer program, the invention described above reality is realized Apply the efficiency computational methods of the air conditioner of example proposition.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
In addition, embodiments of the invention also proposed another non-transitorycomputer readable storage medium, store thereon There is computer program, the efficiency meter for the air conditioner that the above embodiment of the present invention proposes is realized when computer program is executed by processor Calculation method.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
Fig. 5 is the block diagram of the efficiency computing system of air conditioner in accordance with another embodiment of the present invention.Such as Fig. 5 institutes Show, the efficiency computing system of the air conditioner includes：Acquisition module 10, first pressure sensor 21, second pressure sensor 22, return Gas port temperature sensor 01, exhaust port temperatures sensor 02, the second end of indoor heat exchanger temperature sensor 05, indoor heat exchanger One end temperature sensor 07, mixture enthalpy generation module 30, heating capacity generation module 60 and efficiency generation module 50.
Wherein, acquisition module 10 is used to obtain the current working of air conditioner, the power of compressor and air conditioner power consumption. First pressure sensor 21 is used for the high side pressure for obtaining exhaust outlet of compressor.Second pressure sensor 22, which is used to obtain, to be compressed The low-pressure lateral pressure of machine gas returning port.Gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1。 Exhaust port temperatures sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2.The second end of indoor heat exchanger temperature passes 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 exchanger first end temperature passes Sensor 07 is used for the indoor heat exchanger first end temperature t for obtaining indoor heat exchanger first end7。
Mixture enthalpy generation module 30 is used for when the current working of air conditioner is heating condition, is returned according in compressor The gas returning port temperature t of gas port1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, root According to the exhaust port temperatures t of exhaust outlet in compressor2With the enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsAnd lubrication Oily enthalpy h2 lubricating oil, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the end of indoor heat exchanger second Refrigerant enthalpy h5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith the indoor heat exchanger first end temperature t according to indoor heat exchanger first end7 With the refrigerant enthalpy h of high side pressure generation indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, and according to return The refrigerant enthalpy h of gas port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the system of exhaust outlet The enthalpy h of cryogen2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to the end of indoor heat exchanger second Refrigerant enthalpy h5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixture enthalpy h at the end of indoor heat exchanger second5, according to room The refrigerant enthalpy h of interior heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy of indoor heat exchanger first end Value h7。
Heating capacity generation module 60 is used for power, the mixture enthalpy h of gas returning port according to compressor1, exhaust outlet it is mixed Compound enthalpy h2, the end of indoor heat exchanger second mixture enthalpy h5With the mixture enthalpy h of indoor heat exchanger first end7Generation The heating capacity of air conditioner.Efficiency generation module 50 is used for the efficiency that air conditioner is generated according to air conditioner power consumption and heating capacity.
It should be noted that the details not disclosed in the efficiency computing system of the air conditioner of the embodiment of the present invention, refer to Details disclosed in the efficiency computational methods of the air conditioner of the embodiment of the present invention, specific I will not elaborate.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor and air conditioner power consumption, the high pressure side pressure of exhaust outlet of compressor is obtained by first pressure sensor Power and second pressure sensor obtain the low-pressure lateral pressure of compressor return air mouth, and are obtained and compressed by corresponding temperature sensor In machine in the gas returning port temperature of gas returning port, compressor the exhaust port temperatures of exhaust outlet, the end of indoor heat exchanger second indoor heat exchange The indoor heat exchanger first end temperature of device the second end temperature and indoor heat exchanger first end, and when the current working of air conditioner is During heating condition, by mixture enthalpy generation module according to the temperature of above-mentioned each temperature detecting point, high side pressure and low Lateral pressure is pressed to generate the refrigerant enthalpy and lubricating oil enthalpy of multiple temperature detecting points, further according to refrigerant enthalpy and lubrication Oily enthalpy generates mixture enthalpy, then by heating capacity generation module according to the power of compressor and multiple temperature detecting points Lubricating oil enthalpy generates the heating capacity of air conditioner, is given birth to finally by efficiency generation module according to air conditioner power consumption and heating capacity Into the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to the real-time of air conditioner Efficiency optimizes the running status of air conditioner, reaches energy-conservation and improves the purpose of heating effect.
It should be appreciated that each several part of the present invention can be realized with hardware, software, firmware or combinations thereof.Above-mentioned In embodiment, software that multiple steps or method can be performed in memory and by suitable instruction execution system with storage Or firmware is realized.If, and in another embodiment, can be with well known in the art for example, realized with hardware Any one of row technology or their combination are realized：With the logic gates for realizing logic function to data-signal Discrete logic, have suitable combinational logic gate circuit application specific integrated circuit, programmable gate array (PGA), scene Programmable gate array (FPGA) etc..
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 (26)

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 high side pressure of exhaust outlet of compressor；
Obtain the low-pressure lateral pressure of compressor return air mouth；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, outdoor heat exchange The outdoor heat exchanger first end temperature t of device first end4With the indoor heat exchanger first end temperature t of indoor heat exchanger first end7；
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 compressor1With The refrigerant enthalpy h of the low-pressure lateral pressure generation gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, arranged according in the compressor The exhaust port temperatures t of gas port2With the refrigerant enthalpy h of high side pressure generation exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generate the system of outdoor heat exchanger first end Cryogen enthalpy h4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilWith the indoor heat exchanger first end temperature according to the indoor heat exchanger first end t7With the refrigerant enthalpy h of low-pressure lateral pressure generation indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, According to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to The refrigerant enthalpy h of the outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixed of outdoor heat exchanger first end Compound enthalpy h4, according to the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration is indoor The mixture enthalpy h of heat exchanger first end7；
According to the power of the compressor, the mixture enthalpy h of the gas returning port1, the exhaust outlet mixture enthalpy h2, institute State the mixture enthalpy h of outdoor heat exchanger first end4With the mixture enthalpy h of the 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.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be returned according in the compressor The gas returning port temperature t of gas port1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantSpecifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；
The enthalpy h of saturation refrigerant under suction temperature is generated according to the low-pressure lateral pressureAir-breathing saturation；
According to the suction superheat Δ t1With the indoor heat exchanger middle portion temperature t6Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigeration Agent enthalpy h1 refrigerant。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that returned according to below equation generation The modifying factor D of gas port refrigerant enthalpy1：
<mrow> <msub> <mi>D</mi> <mn>1</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&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>6</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>6</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>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>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
4. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that described according to the indoor heat exchanger The indoor heat exchanger first end temperature t of first end7With the refrigerant enthalpy of low-pressure lateral pressure generation indoor heat exchanger first end Value h7 refrigerantsSpecifically 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 refrigerants。
5. the efficiency computational methods of air conditioner as claimed in claim 4, 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.
6. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be arranged according in the compressor The exhaust port temperatures t of gas port2With the enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsSpecifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
The enthalpy h of saturation refrigerant under delivery temperature is generated according to the high side pressureIt is vented saturation；
According to the exhaust port temperatures t of exhaust outlet in the compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Spend Δ t2；
According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of the exhaust outlet The enthalpy h of agent2 refrigerants。
7. the efficiency computational methods of air conditioner as claimed in claim 6, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
<mrow> <msub> <mi>D</mi> <mn>2</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
8. 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 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the sky is generated according to below equation Adjust the refrigerating capacity of device：
Wherein, QRefrigerating capacityFor the refrigerating capacity of the air conditioner, PCompressorFor the power of the compressor.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each The lubricating oil enthalpy h of temperature detecting pointI lubricating oil：hI lubricating oil=-0.0808+1.7032ti+0.0025ti 2,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.
11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each The mixture enthalpy h of pointi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil,
Cg=f/104,
Wherein, i is positive integer, CgFor oil content, f is the running frequency of the compressor.
12. 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 1-11 Any described method.
13. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 1-11 is realized when calculation machine program is executed by processor.
14. 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 high side pressure of exhaust outlet of compressor；
Obtain the low-pressure lateral pressure of compressor return air mouth；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, indoor heat exchange The second end of indoor heat exchanger temperature t at the end of device second5With the indoor heat exchanger first end temperature t of indoor heat exchanger first end7；
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 compressor1With The refrigerant enthalpy h of the low-pressure lateral pressure generation gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, arranged according in the compressor The exhaust port temperatures t of gas port2With the enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the system at the end of indoor heat exchanger second Cryogen enthalpy h5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilWith the indoor heat exchanger first end temperature according to the indoor heat exchanger first end t7With the refrigerant enthalpy h of high side pressure generation indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, According to the enthalpy h of the refrigerant of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, root According to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the end of indoor heat exchanger second Mixture enthalpy h5, according to the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration The mixture enthalpy h of indoor heat exchanger first end7；
According to the power of the compressor, the mixture enthalpy h of the gas returning port1, the exhaust outlet mixture enthalpy h2, institute State the mixture enthalpy h at the end of indoor heat exchanger second5With the mixture enthalpy h of the indoor heat exchanger first end7Generate air conditioner Heating capacity；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
15. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that described according in the compressor The gas returning port temperature t of gas returning port1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1 refrigerantSpecifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
The enthalpy h of saturation refrigerant under suction temperature is generated according to the low-pressure lateral pressureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationIt is raw Into the refrigerant enthalpy h of the gas returning port1 refrigerant。
16. the efficiency computational methods of air conditioner as claimed in claim 15, 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.
17. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that described according in the compressor The exhaust port temperatures t of exhaust outlet2With the enthalpy h of the refrigerant of high side pressure generation exhaust outlet2 refrigerantsSpecifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
The enthalpy h of saturation refrigerant under delivery temperature is generated according to the high side pressureIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
18. the efficiency computational methods of the air conditioner described in claim 17, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
<mrow> <msub> <mi>D</mi> <mn>2</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
19. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that described according to the indoor heat exchange The indoor heat exchanger first end temperature t of device first end7With the refrigerant of high side pressure generation indoor heat exchanger first end Enthalpy h7 refrigerantsSpecifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor heat exchanger first end temperature t7It is raw Into degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation refrigerant under the delivery temperature Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerants。
20. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that according to generating below equation The modifying factor D of indoor heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&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.
21. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to calculating below equation The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
22. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to generating equation below The heating capacity of air conditioner：
Wherein, QHeating capacityFor the heating capacity of the air conditioner, PCompressorFor the power of the compressor.
23. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that calculated according to below equation each The lubricating oil enthalpy h of temperature detecting pointI lubricating oil：
hI lubricating oil=-0.0808+1.7032ti+0.0025ti 2,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.
24. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that calculated according to below equation each The mixture enthalpy h of pointi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil,
Cg=f/104,
Wherein, i is positive integer, CgFor oil content, f is the running frequency of the compressor.
25. 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 14-24 Any described method.
26. 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 14-24 is realized when calculation machine program is executed by processor.
CN201710775524.1A 2017-08-31 2017-08-31 Air conditioner and its efficiency computational methods Pending CN107514778A (en)

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