CN107490143A - Air conditioner and its efficiency computational methods - Google Patents

Air conditioner and its efficiency computational methods Download PDF

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Publication number
CN107490143A
CN107490143A CN201710774255.7A CN201710774255A CN107490143A CN 107490143 A CN107490143 A CN 107490143A CN 201710774255 A CN201710774255 A CN 201710774255A CN 107490143 A CN107490143 A CN 107490143A
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China
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msub
heat exchanger
mrow
air conditioner
refrigerant
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刘燕飞
张�浩
戚文端
陈新
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, the described method comprises the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain low-pressure lateral pressure；Obtain compressor return air mouth temperature t1, exhaust port temperatures t2, low-pressure lateral pressure, the temperature t of outdoor heat exchanger first end4, indoor heat exchanger first end temperature t7With compressor tonifying Qi temperature t8；When current working is cooling condition, according to low-pressure lateral pressure, t1、t2、t4、t7And t8Gas returning port refrigerant enthalpy h is generated respectively1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the power of compressor, h1、h2、h4、h7、h8’And h8”Generate refrigerating capacity；According to the efficiency of air conditioner power consumption and refrigerating capacity generation air conditioner.The present invention can detect energy efficiency of air conditioner exactly.

Description

Air conditioner and its efficiency computational methods
Technical field
The present invention relates to air conditioner technical field, the efficiency computational methods of more particularly to a kind of air conditioner, a kind of air conditioner With a kind of non-transitorycomputer readable storage medium.
Background technology
It is comfortably the problem of user more pays close attention to that whether air conditioner, which saves,.
Air conditioner in correlation technique operationally due to the situation of change of efficiency can not be known, thus be difficult to maintain compared with Good running status, cooling or heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention One purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
Fourth object of the present invention is the efficiency computational methods for proposing another air conditioner.
The 5th purpose of the present invention is to propose another air conditioner.
The 6th purpose of the present invention is to propose another non-transitorycomputer readable storage medium.
To reach above-mentioned purpose, a kind of efficiency computational methods for air conditioner that first aspect present invention embodiment proposes include Following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain compressor return air mouth Low-pressure lateral pressure；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2、 The outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4, indoor heat exchanger first end indoor heat exchanger first end temperature Spend t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8；When the current working of the air conditioner is cooling condition, according to the pressure The gas returning port temperature t of gas returning port in contracting machine1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1, according to the pressure The exhaust port temperatures t of exhaust outlet in contracting machine2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the outdoor heat exchanger first end Outdoor heat exchanger first end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4, according to indoor heat exchanger first The indoor heat exchanger first end temperature t at end7With the refrigerant enthalpy h of low-pressure lateral pressure generation indoor heat exchanger first end7, According to the tonifying Qi temperature t of compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With the liquid of flash vessel Refrigerant enthalpy h8”；According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, exhaust outlet refrigerant enthalpy Value h2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into compressor Gaseous refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the refrigerating capacity of air conditioner；And according to described Air conditioner 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 low-pressure lateral pressure of compressor return air mouth, and obtain gas returning port in compressor, The tonifying Qi temperature of exhaust outlet, the temperature of outdoor heat exchanger first end and indoor heat exchanger first end and compressor tonifying Qi entrance, And when air conditioner is in cooling condition according to the pressing creation of the temperature and pressure test point of above-mentioned each temperature detecting point The refrigerant enthalpy of above-mentioned each temperature detecting point, power, the refrigeration of above-mentioned each temperature detecting point then in conjunction with compressor Agent enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, Consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the mesh of refrigeration 's.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor1Generate gas returning port Refrigerant enthalpy h1Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to the gas returning port Temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to the suction superheat Δ t1Changed with interior Hot device middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；Suction temperature is generated according to the low-pressure lateral pressure The enthalpy h of lower saturation refrigerantAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant Enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h1。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to below equation1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Further, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchange The refrigerant enthalpy h of device first end7Specifically include：According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger Middle portion temperature t6Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generation is indoor The modifying factor D of heat exchanger first end refrigerant enthalpy7；According to the modifying factor of the indoor heat exchanger first end refrigerant enthalpy Sub- D7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6 For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation institute State the refrigerant enthalpy h of exhaust outlet2Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to institute State the exhaust port temperatures t of exhaust outlet in compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；Root According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor of exhaust outlet refrigerant enthalpy D2：According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the row The modifying factor D of gas port refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the exhaust outlet Refrigerant enthalpy h2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6For Overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation Value h4：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the refrigerating capacity of air conditioner is generated according to below equation：
Wherein, QRefrigerating capacityFor the system of the air conditioner Cold, PcomFor the power of compressor.
To reach above-mentioned purpose, a kind of air conditioner that second aspect of the present invention embodiment proposes includes memory, processor And the computer program that can be run on the memory and on the processor is stored in, calculating described in the computing device During machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, consequently facilitating according to reality Shi Nengxiao optimizes to running status, reaches energy-conservation and improves the purpose of refrigeration.
To reach above-mentioned purpose, a kind of non-transitory computer-readable storage medium that third aspect present invention embodiment proposes Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor The efficiency computational methods of the air conditioner of proposition.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
To reach above-mentioned purpose, the efficiency computational methods bag for another air conditioner that fourth aspect present invention embodiment proposes Include following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain compressor return air mouth Low-pressure lateral pressure；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, indoor heat exchanger first end indoor heat exchanger first end Temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8；When the current working of the air conditioner is heating condition, according to described The gas returning port temperature t of gas returning port in compressor1With the refrigerant enthalpy h of low-pressure lateral pressure generation gas returning port1, according to described The exhaust port temperatures t of exhaust outlet in compressor2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the indoor heat exchanger second The second end of indoor heat exchanger temperature t at end5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5, according to indoor heat exchanger The indoor heat exchanger first end temperature t of one end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7, according to compressor tonifying Qi The tonifying Qi temperature t of entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；Root According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, exhaust outlet refrigerant enthalpy h2, indoor heat exchanger The refrigerant enthalpy h at the second end5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy of compressor h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner；And according to the air conditioner power consumption and The heating capacity generates 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 low-pressure lateral pressure of compressor return air mouth, and obtain gas returning port in compressor, Exhaust outlet, the temperature at the end of indoor heat exchanger second and indoor heat exchanger first end, the tonifying Qi temperature of compressor tonifying Qi entrance, and Pressing creation when air conditioner is in heating condition according to the temperature and pressure test point of above-mentioned each temperature detecting point is above-mentioned The refrigerant enthalpy of each temperature detecting point, power, the refrigerant enthalpy of above-mentioned each temperature detecting point then in conjunction with compressor Value and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, so as to It is easy to optimize according to the real-time energy efficiency of air conditioner the running status of air conditioner, reaches 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 compressor1Generate back The refrigerant enthalpy h of gas port1Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to described time Gas port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat Δ t1 With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the low-pressure lateral pressure Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, it is described The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For Overheated zone coefficient corresponding to refrigerant.
Further, the exhaust port temperatures t according to exhaust outlet in the compressor2Generate the refrigeration of the exhaust outlet Agent enthalpy h2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According in the indoor heat exchanger The indoor heat exchanger middle portion temperature t in portion6With the exhaust port temperatures t of exhaust outlet in the compressor2Generate discharge superheat Δ t2； According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the modifying factor of exhaust outlet refrigerant enthalpy D2；According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the row The modifying factor D of gas port refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the exhaust outlet Refrigerant enthalpy h2。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Further, the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generate respectively The refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：According to the indoor heat exchanger in the middle part of the indoor heat exchanger Middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With it is described Indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；Changed according to the interior The modifying factor D of hot device first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationDescribed in generation The refrigerant enthalpy h of indoor heat exchanger first end7。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6 For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation Value h5：
h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：
Wherein, QHeating capacityFor the air conditioner system Heat, PcomFor the power of compressor.
To reach above-mentioned purpose, another air conditioner that fifth aspect present invention embodiment proposes includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, meter described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that fifth aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, consequently facilitating according to reality Shi Nengxiao optimizes to running status, reaches energy-conservation and improves the purpose of refrigeration.
To reach above-mentioned purpose, the computer-readable storage of another non-transitory that sixth aspect present invention embodiment proposes Medium, is stored thereon with computer program, and the computer program realizes that fifth aspect present invention is implemented when being executed by processor The efficiency computational methods for the air conditioner that example proposes.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
Brief description of the drawings
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention；
Fig. 2 is the structural representation according to the air conditioner of one embodiment of the invention；
Fig. 3 is the block diagram according to the efficiency computing system of the air conditioner of the embodiment of the present invention；
Fig. 4 is the flow chart according to the efficiency computational methods of another air conditioner of the embodiment of the present invention；
Fig. 5 is the block diagram according to the efficiency computing system of another air conditioner of the embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
The air conditioner of the embodiment of the present invention and its efficiency computational methods and system described below in conjunction with the accompanying drawings.
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention.
As shown in figure 1, the efficiency computational methods of the air conditioner of the embodiment of the present invention, comprise the following steps：
S101, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionercomAnd air-conditioning Device power consumption PPower consumption。
S102, obtain the low-pressure lateral pressure of compressor return air mouth.
S103, 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 end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8。
The air conditioner of the embodiment of the present invention can be twin-stage steam compressing air conditioner device, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor, four-way valve, outdoor heat exchanger, restricting element, flash vessel and indoor heat exchanger.
In one embodiment of the invention, can be by setting pressure sensor to be examined to detect the pressure in pressure detecting point The pressure of measuring point.Specifically, low pressure side pressure can be set by the optional position in restricting element into compressor between gas returning port Force snesor, to detect low-pressure lateral pressure.More specifically, as shown in Fig. 2 low-pressure lateral pressure sensor can be disposed in the interior changes In the middle part of hot device.
In one embodiment of the invention, can be by setting temperature sensor to detect respectively in corresponding temperature test point The temperature of the temperature detecting point.Specifically, as shown in Fig. 2 by within the compressor at gas returning port gas returning port temperature can be set to pass Sensor is to detect gas returning port temperature t1, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t2, at outdoor heat exchanger first end outdoor heat exchanger first end temperature sensor is set to detect outdoor heat exchanger first end temperature Spend t4And at heat exchanger first end indoor heat exchanger first end temperature sensor is set to detect indoor heat exchanger the indoors One end temperature t7, in compressor tonifying Qi porch tonifying Qi inlet temperature sensor is set to detect the tonifying Qi of compressor tonifying Qi entrance Temperature t8.Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant pipe Wall, especially the position of temperature sensor is set to take Insulation.For example, temperature sensor can be close to copper pipe setting, and Sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
S104, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1、 The exhaust port temperatures t of exhaust outlet in compressor2, low-pressure lateral pressure, the outdoor heat exchanger first end temperature of outdoor heat exchanger first end Spend t4, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8Respectively Generate the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4、 The refrigerant enthalpy h of indoor heat exchanger first end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigeration of flash vessel Agent enthalpy h8”。
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
Because different test points include temperature detecting point and the state difference of the refrigerant of pressure detecting point, therefore different inspections The enthalpy of the refrigerant of measuring point is different.In one embodiment of the invention, rule of thumb refrigerant can be calculated by formula Enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、 The refrigerant enthalpy h of outdoor heat exchanger first end4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous state of compressor Refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the gas returning port of machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger can be obtained6, wherein, as shown in Fig. 2 indoor Indoor heat exchanger middle portion temperature t in the middle part of heat exchanger6Can be warm by the indoor heat exchanger middle part set in the middle part of heat exchanger indoors Degree sensor detects to obtain.
Then can be according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1, and according to Suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1.Wherein, air-breathing Degree of superheat Δ t1For gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t1=t1-t6.Gas returning port refrigerant enthalpy The modifying factor D of value1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6, Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Also, the enthalpy h of saturation refrigerant under suction temperature can be also generated according to low-pressure lateral pressureAir-breathing saturation.Wherein, can be first According to low-pressure lateral pressure PLow pressureGenerate air-breathing saturation temperature Tl, such asFurther according to air-breathing saturation temperature Tl Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation, for example, hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4T+ 3+a5, wherein, a1-a5 For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1· hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end, the degree of superheat that can combine the position calculates indoor heat exchanger first end Refrigerant enthalpy h7。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the amendment of indoor heat exchanger first end refrigerant enthalpy Factor D7, and the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy according to generation7With the enthalpy of saturation refrigerant hAir-breathing saturationGenerate refrigerant enthalpy h7。
Wherein, Δ t7=t7-t6, h7=D7·hAir-breathing saturation+d7, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained3, wherein, as shown in Fig. 2 outdoor Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger3Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through Degree sensor detects to obtain.
Then, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3Generation exhaust Degree of superheat Δ t2, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generation exhaust outlet refrigerant enthalpy is repaiied Positive divisor D2, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation。
Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t2=t2-t3.The modifying factor of exhaust outlet refrigerant enthalpyWherein, d1-d6For refrigerant Corresponding overheated zone coefficient.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1- a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGeneration The refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of outdoor heat exchanger first end4, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4：Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Also, when the current working of air conditioner is cooling condition, the liquid refrigerant enthalpy h of flash vessel8”Can according to Lower formula calculates：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Fill into the gaseous refrigerant enthalpy h of compressor8’It can be calculated according to below equation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close.For example, R410A refrigerants and saturation region coefficient, overheat fauna corresponding to R32 refrigerants are respectively illustrated in table 1 Number and supercooling fauna number：
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is cooling condition Adjust the indoor heat exchanger middle portion temperature t in device6, gas returning port temperature t1, indoor heat exchanger first end temperature t7Respectively obtain gas returning port Refrigerant enthalpy h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high side pressure in air conditioner, row Gas port temperature t2, outdoor heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2With outdoor heat exchanger first The refrigerant enthalpy h at end4, and saturated gas enthalpy and saturated liquid under the state can be obtained according to temperature or pressure Enthalpy.
S105, according to the power of compressor, the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, outdoor changes The refrigerant enthalpy h of hot device first end4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant of compressor Enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the refrigerating capacity of air conditioner.
Specifically, the refrigerating capacity of air conditioner can be generated according to below equation：
Wherein, QRefrigerating capacityFor the system of the air conditioner Cold, PcomFor the power of compressor.
S106, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Because the current working of air conditioner is cooling condition, thus can be generated according to air conditioner power consumption and refrigerating capacity empty The refrigeration efficiency of device is adjusted, specifically, the refrigeration efficiency EER of air conditioner is the refrigerating capacity Q of air conditionerRefrigerating capacityWith power consumption PPower consumptionIt Than i.e. EER=QRefrigerating capacity/PPower consumption。
, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The power and air conditioner power consumption of machine, and obtain the low-pressure lateral pressure of compressor return air mouth, and obtain gas returning port in compressor, The tonifying Qi temperature of exhaust outlet, the temperature of outdoor heat exchanger first end and indoor heat exchanger first end and compressor tonifying Qi entrance, And when air conditioner is in cooling condition according to the pressing creation of the temperature and pressure test point of above-mentioned each temperature detecting point The refrigerant enthalpy of above-mentioned each temperature detecting point, power, the refrigeration of above-mentioned each temperature detecting point then in conjunction with compressor Agent enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, Consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the mesh of refrigeration 's.
Corresponding above-described embodiment, the present invention also propose a kind of air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor The computer program of operation, during computing device computer program, the air conditioner that the above embodiment of the present invention proposes can be achieved Efficiency computational methods.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, consequently facilitating according to reality Shi Nengxiao optimizes to running status, reaches energy-conservation and improves the purpose of refrigeration.
Corresponding above-described embodiment, the present invention also propose a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for the air conditioner that the above embodiment of the present invention proposes can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
Corresponding above-described embodiment, the present invention also propose a kind of efficiency computing system of air conditioner.
As shown in Figures 2 and 3, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port TEMP Device 01, exhaust port temperatures sensor 02, outdoor heat exchanger first end temperature sensor 04, indoor heat exchanger first end TEMP Device 07, tonifying Qi inlet temperature sensor 08, low-pressure lateral pressure sensor 16 and acquisition module 10, refrigerant enthalpy generation module 20th, refrigerating capacity generation module 30, efficiency generation module 40.
Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1；Exhaust outlet temperature Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Tonifying Qi inlet temperature sensor 08, which is used to obtain, presses The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；Outdoor heat exchanger first end temperature sensor 04 is used to obtain outdoor heat exchanger first end Outdoor heat exchanger first end temperature t4；Indoor heat exchanger first end temperature sensor 07 is used to obtain indoor heat exchanger first end Indoor heat exchanger first end temperature t7；Low-pressure lateral pressure sensor 16 is used for the low-pressure lateral pressure for obtaining compressor return air mouth.
The air conditioner of the embodiment of the present invention can be twin-stage steam compressing air conditioner device, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element such as choke valve 400 and choke valve 600th, flash vessel 700 and indoor heat exchanger 500.
As shown in Fig. 2 gas returning port temperature sensor 01 can be set within the compressor at gas returning port, exhaust port temperatures sensor 02 settable exhaust ports, outdoor heat exchanger first end temperature sensor 04 may be provided at outdoor heat exchanger first within the compressor End, indoor heat exchanger first end temperature sensor 07 may be provided at indoor heat exchanger first end, tonifying Qi inlet temperature sensor 08 It is arranged on compressor tonifying Qi porch.Wherein, each temperature sensor is effective with the refrigerant tube wall of corresponding temperature test point Contact, and to refrigerant tube wall, especially set the position of temperature sensor to take Insulation.For example, can be by TEMP Device is close to copper pipe setting, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability of temperature detection And accuracy.
Wherein, low-pressure lateral pressure sensor 16 may be provided at any position of the restricting element into compressor between gas returning port Put.More specifically, as shown in Fig. 2 low-pressure lateral pressure sensor can be disposed in the interior in the middle part of heat exchanger.
Acquisition module 10 is used to obtain the current working of air conditioner, the power of compressor and air conditioner power consumption；Refrigeration Agent enthalpy generation module 20 is used for when the current working of air conditioner is cooling condition, according to the gas returning port of gas returning port in compressor Temperature t1, in compressor exhaust outlet exhaust port temperatures t2, low-pressure lateral pressure, the outdoor heat exchanger of outdoor heat exchanger first end One end temperature t4, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature of compressor tonifying Qi entrance t8The refrigerant enthalpy h of gas returning port is generated respectively1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy Value h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid of flash vessel State refrigerant enthalpy h8”；Refrigerating capacity generation module 30 is used for power, the refrigerant enthalpy h of gas returning port according to compressor1, exhaust The refrigerant enthalpy h of mouth2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the refrigerating capacity of air conditioner； Efficiency generation module 40 is used for the efficiency that air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Wherein, acquisition module 10, refrigerant enthalpy generation module 20, refrigerating capacity generation module 30 and efficiency generation module 40 It may be disposed in the electric-control system of air conditioner.Acquisition module 10 can monitor the current working of air conditioner, the power of compressor in real time PcomWith air conditioner power consumption PPower consumption。
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
Because different test points include temperature detecting point and the state difference of the refrigerant of pressure detecting point, therefore different inspections The enthalpy of the refrigerant of measuring point is different.In one embodiment of the invention, refrigerant enthalpy generation module 20 can be rule of thumb The enthalpy of refrigerant is calculated in formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below1、 The refrigerant enthalpy h of exhaust outlet2, outdoor heat exchanger first end refrigerant enthalpy h4With the refrigerant of indoor heat exchanger first end Enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port Enthalpy h1。
Specifically, the indoor heat exchanger in the middle part of indoor heat exchanger can be obtained by indoor heat exchanger middle portion temperature sensor 06 Middle portion temperature t6, wherein, as shown in Fig. 2 indoor heat exchanger middle portion temperature sensor 06 may be provided in the middle part of indoor heat exchanger.
Then refrigerant enthalpy generation module 20 can be according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generation is inhaled Gas degree of superheat Δ t1, and according to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate gas returning port refrigerant enthalpy Modifying factor D1.Wherein, suction superheat Δ t1For gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t1= t1-t6.The modifying factor D of gas returning port refrigerant enthalpy1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5 (Δt1)t2 6+d6(Δt1)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Also, the enthalpy h of saturation refrigerant under suction temperature can be also generated according to low-pressure lateral pressureAir-breathing saturation.Wherein, can be first According to low-pressure lateral pressure PLow pressureGenerate air-breathing saturation temperature Tl, such asFurther according to air-breathing saturation temperature Tl Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation, for example, hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4Tl 3+a5, wherein, a1-a5 For saturation region coefficient corresponding to refrigerant.In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, refrigerant enthalpy generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigeration The enthalpy h of agentAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end, refrigerant enthalpy generation module 20 can combine the degree of superheat meter of the position Calculate the refrigerant enthalpy h of indoor heat exchanger first end7。
Specifically, refrigerant enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7With indoor heat exchange Device middle portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate room The modifying factor D of interior heat exchanger first end refrigerant enthalpy7, and the indoor heat exchanger first end refrigerant according to generation The modifying factor D of enthalpy7With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7.Wherein, Δ t7=t7-t6,h7=D7·hAir-breathing saturation+d7, its In, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet Enthalpy h2。
Specifically, the outdoor heat exchanger in the middle part of outdoor heat exchanger can be obtained by outdoor heat exchanger middle portion temperature sensor 03 Middle portion temperature t3, wherein, as shown in Fig. 2 outdoor heat exchanger middle portion temperature sensor 03 may be provided in the middle part of outdoor heat exchanger.
Then, refrigerant enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2Changed with outdoor Hot device middle portion temperature t3Generate discharge superheat Δ t2, and according to discharge superheat Δ t2With temperature in the middle part of outdoor heat exchanger Spend t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2, and according to outdoor heat exchanger middle portion temperature t3Generation The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation.Wherein, discharge superheat Δ t2For the exhaust of exhaust outlet in compressor Mouth temperature t2With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t2=t2-t3.The modifying factor of exhaust outlet refrigerant enthalpyWherein, d1-d6For refrigerant Corresponding overheated zone coefficient.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1- a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Refrigerant enthalpy generation module 20 can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For corresponding to refrigerant Overheated zone coefficient.
For the refrigerant enthalpy h of outdoor heat exchanger first end4, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, refrigerant enthalpy generation module 20 can directly calculate the system of outdoor heat exchanger first end Cryogen enthalpy h4：Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Also, when the current working of air conditioner is cooling condition, refrigerant enthalpy generation module 20 can be according to following public affairs Formula calculates the liquid refrigerant enthalpy h of flash vessel8”：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Refrigerant enthalpy generation module 20 can calculate the gaseous refrigerant enthalpy h for filling into compressor according to below equation8’：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close.For example, R410A refrigerants and saturation region coefficient, overheat fauna corresponding to R32 refrigerants are respectively illustrated in table 1 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, it is each to calculate The refrigerant enthalpy of individual temperature detecting point.
In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software Fruit, or the refrigerant enthalpy by each temperature detecting point of other approach acquisition.For example, when the current working of air conditioner is During cooling condition, refrigerant enthalpy generation module 20 can also be according to the indoor heat exchanger middle portion temperature t in air conditioner6, gas returning port Temperature t1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With indoor heat exchanger first end Refrigerant enthalpy h7, and can be according to the high side pressure in air conditioner, exhaust port temperatures t2, outdoor heat exchanger first end temperature t4 Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy h of outdoor heat exchanger first end4, and according to temperature or Pressure can obtain saturated gas enthalpy and saturated liquid enthalpy under the state.
In an embodiment of the present invention, refrigerating capacity generation module 30 can generate the refrigerating capacity of air conditioner according to below equation：Wherein, QRefrigerating capacityFor the refrigerating capacity of air conditioner, Pcom For the power of compressor.
Because the current working of air conditioner is cooling condition, thus efficiency generation module 40 can be according to air conditioner power consumption With the refrigeration efficiency of refrigerating capacity generation air conditioner, specifically, the refrigeration efficiency EER of air conditioner is the refrigerating capacity Q of air conditionerRefrigerating capacityWith Power consumption PPower consumptionThe ratio between, i.e. EER=QRefrigerating capacity/PPower consumption。
, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor and air conditioner power consumption, and pass through the low pressure of correspondingly pressure sensor acquisition compressor return air mouth Lateral pressure, and gas returning port, exhaust outlet, outdoor heat exchanger first end and interior in compressor are obtained by corresponding temperature sensor Temperature, the tonifying Qi temperature of compressor tonifying Qi entrance of heat exchanger first end, and pass through system when air conditioner is in cooling condition Cryogen enthalpy generation module, refrigerating capacity generation module and efficiency generation module are according to the temperature and pressure of above-mentioned each temperature detecting point The refrigerant enthalpy of the above-mentioned each temperature detecting point of pressing creation of power test point, it is power then in conjunction with compressor, above-mentioned each The refrigerant enthalpy and air conditioner power consumption of individual temperature detecting point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving refrigeration.
The air conditioner and its efficiency computational methods and system of above-described embodiment can detect the refrigeration efficiency of air conditioner, for inspection The heat efficiency of air conditioner is surveyed, the present invention also proposes the efficiency computational methods of another air conditioner.
As shown in figure 4, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：
S401, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionercomAnd air-conditioning Device power consumption PPower consumption。
S402, obtain the low-pressure lateral pressure of compressor return air mouth.
S403, 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 second5, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8。
Specifically, by the optional position in restricting element into compressor between gas returning port low-pressure lateral pressure can be set to pass Sensor, to detect low-pressure lateral pressure.More specifically, as shown in Fig. 2 low-pressure lateral pressure sensor can be disposed in the interior heat exchanger Middle part.
As shown in Fig. 2 can be by setting gas returning port temperature sensor at gas returning port within the compressor to detect gas returning port temperature Spend t1, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t2, heat exchanger second indoors Indoor heat exchanger the second end temperature sensor is set to detect the second end of indoor heat exchanger temperature t at end5And exchange heat indoors Indoor heat exchanger first end temperature sensor is set to detect indoor heat exchanger first end temperature t at device first end7, in compressor Tonifying Qi porch sets tonifying Qi inlet temperature sensor to detect tonifying Qi temperature t8。
Wherein, each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially the position of temperature sensor is set to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
S404, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1、 The exhaust port temperatures t of exhaust outlet in compressor2, low-pressure lateral pressure, the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second Spend t5, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8Respectively Generate the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5With The refrigerant enthalpy h of indoor heat exchanger first end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigeration of flash vessel Agent enthalpy h8”。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
Because different test points include temperature detecting point and the state difference of the refrigerant of pressure detecting point, therefore different inspections The enthalpy of the refrigerant of measuring point is different.In one embodiment of the invention, rule of thumb refrigerant can be calculated by formula Enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、 The refrigerant enthalpy h at the end of indoor heat exchanger second5With the refrigerant enthalpy h of indoor heat exchanger first end7, fill into the gas of compressor State refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the gas returning port of machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained3, wherein, as shown in Fig. 2 outdoor Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger3Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through Degree sensor detects to obtain.
Then can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1, and according to Suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1.Wherein, air-breathing Degree of superheat Δ t1For gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.Gas returning port refrigerant enthalpy The modifying factor of valueWherein, d1- d6For overheated zone coefficient corresponding to refrigerant.
Also, the enthalpy h of saturation refrigerant under suction temperature can be also generated according to low-pressure lateral pressureAir-breathing saturation.Wherein, can be first According to low-pressure lateral pressure PLow pressureGenerate air-breathing saturation temperature Tl, such asFurther according to air-breathing saturation temperature Tl Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation, for example, hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4Tl 3+a5, wherein, a1-a5 For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1· hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger can be obtained6, wherein, as shown in Fig. 2 indoor Indoor heat exchanger middle portion temperature t in the middle part of heat exchanger6Can be warm by the indoor heat exchanger middle part set in the middle part of heat exchanger indoors Degree sensor detects to obtain.
Then, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Generation exhaust Degree of superheat Δ t2, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generation exhaust outlet refrigerant enthalpy is repaiied Positive divisor D2, and according to indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation.Wherein, Discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Difference, i.e. Δ t2 =t2-t6.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5 (Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.Saturation refrigerant under delivery temperature Enthalpy hIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGeneration The refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work During condition, the refrigerant superheat of indoor heat exchanger first end, the degree of superheat that can combine the position calculates indoor heat exchanger first end Refrigerant enthalpy h7。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the amendment of indoor heat exchanger first end refrigerant enthalpy Factor D7, and the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy according to generation7With saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturationGenerate the refrigerant enthalpy h of indoor heat exchanger first end7.Wherein, Δ t7=t7-t6,h7=D7·hIt is vented saturation+d7, its In, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5：h5=c1+c2t5 +c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Also, when the current working of air conditioner is cooling condition, the liquid refrigerant enthalpy h of flash vessel8”Can according to Lower formula calculates：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Fill into the gaseous refrigerant enthalpy h of compressor8’It can be calculated according to below equation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close.For example, R410A refrigerants and saturation region coefficient, overheat fauna corresponding to R32 refrigerants are respectively illustrated in table 1 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, it is each to calculate The refrigerant enthalpy of individual 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 example, can also be according to sky when the current working of air conditioner is heating condition Adjust the indoor heat exchanger middle portion temperature t in device6, gas returning port temperature t1, indoor heat exchanger first end temperature t7Respectively obtain gas returning port Refrigerant enthalpy h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high side pressure (example in air conditioner Pressure in the middle part of outdoor heat exchanger), exhaust port temperatures t2, the second end of indoor heat exchanger temperature t5Respectively obtain the system of exhaust outlet Cryogen enthalpy h2With the refrigerant enthalpy h at the end of indoor heat exchanger second5, and the state can be obtained according to temperature or pressure Lower saturated gas enthalpy and saturated liquid enthalpy.
S405, according to the power of compressor, the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, interior changes The refrigerant enthalpy h at the hot end of device second5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant of compressor Enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to below equation：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PcomFor the power of compressor.
S406, the efficiency of air conditioner is generated according to air conditioner power consumption and heating capacity.
Because the current working of air conditioner is heating condition, thus can be generated according to air conditioner power consumption and heating capacity empty The heat efficiency of device is adjusted, specifically, the heat efficiency COP of air conditioner is the heating capacity Q of air conditionerHeating capacityWith power consumption PPower consumptionIt Than i.e. COP=QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The power and air conditioner power consumption of machine, and obtain the low-pressure lateral pressure of compressor return air mouth, and obtain gas returning port in compressor, Exhaust outlet, the temperature at the end of indoor heat exchanger second and indoor heat exchanger first end, the tonifying Qi temperature of compressor tonifying Qi entrance, and Pressing creation when air conditioner is in heating condition according to the temperature and pressure test point of above-mentioned each temperature detecting point is above-mentioned The refrigerant enthalpy of each temperature detecting point, power, the refrigerant enthalpy of above-mentioned each temperature detecting point then in conjunction with compressor Value and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, so as to It is easy to optimize according to the real-time energy efficiency of air conditioner the running status of air conditioner, reaches energy-conservation and improve the purpose of heating effect.
Corresponding above-described embodiment, the present invention also propose another air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor The computer program of operation, during computing device computer program, it is empty that the another kind that the above embodiment of the present invention proposes can be achieved Adjust the efficiency computational methods of device.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, be easy to according to real-time energy Effect optimization running status, reach energy-conservation and improve the purpose of heating effect.
Corresponding above-described embodiment, the present invention also propose a kind of non-transitorycomputer readable storage medium.
The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for another air conditioner that the above embodiment of the present invention proposes can be achieved.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
Corresponding above-described embodiment, the present invention also propose the efficiency computing system of another air conditioner.
As shown in Figure 2 and Figure 5, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port TEMP Device 01, exhaust port temperatures sensor 02, the second end of indoor heat exchanger temperature sensor 05, indoor heat exchanger first end TEMP Device 07, tonifying Qi inlet temperature sensor 08 and acquisition module 10, refrigerant enthalpy generation module 20, heating capacity generation module 50th, efficiency generation module 40.
Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1；Exhaust outlet temperature Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Tonifying Qi inlet temperature sensor 08, which is used to obtain, presses The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；The second end of indoor heat exchanger temperature sensor 05 is used to obtain the end of indoor heat exchanger second The second end of indoor heat exchanger temperature t5；Indoor heat exchanger first end temperature sensor 07 is used to obtain indoor heat exchanger first end Indoor heat exchanger first end temperature t7；Low-pressure lateral pressure sensor 16 is used for the low-pressure lateral pressure for obtaining compressor return air mouth.
The air conditioner of the embodiment of the present invention can be twin-stage steam compressing air conditioner device, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element such as choke valve 400 and choke valve 600th, flash vessel 700 and indoor heat exchanger 500.
As shown in Fig. 2 gas returning port temperature sensor 01 can be set within the compressor at gas returning port, exhaust port temperatures sensor 02 settable exhaust ports, the second end of indoor heat exchanger temperature sensor 05 may be provided at outdoor heat exchanger second within the compressor End, indoor heat exchanger first end temperature sensor 07 may be provided at indoor heat exchanger first end, tonifying Qi inlet temperature sensor 08 It is arranged on compressor tonifying Qi porch.Wherein, each temperature sensor is effective with the refrigerant tube wall of corresponding temperature test point Contact, and to refrigerant tube wall, especially set the position of temperature sensor to take Insulation.For example, can be by TEMP Device is close to copper pipe setting, and sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability of temperature detection And accuracy.
Wherein, low-pressure lateral pressure sensor 16 may be provided at any position of the restricting element into compressor between gas returning port Put.More specifically, as shown in Fig. 2 low-pressure lateral pressure sensor can be disposed in the interior in the middle part of heat exchanger.
Acquisition module 10 is used to obtain the current working of air conditioner, the power of compressor and air conditioner power consumption；Refrigeration Agent enthalpy generation module 20 is used for when the current working of air conditioner is heating condition, according to the gas returning port of gas returning port in compressor Temperature t1, in compressor exhaust outlet exhaust port temperatures t2, low-pressure lateral pressure, the indoor heat exchanger at the end of indoor heat exchanger second Two end temperature t5, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature of compressor tonifying Qi entrance t8The refrigerant enthalpy h of gas returning port is generated respectively1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy Value h5With the refrigerant enthalpy h of indoor heat exchanger first end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid of flash vessel State refrigerant enthalpy h8”；Heating capacity generation module 50 is used for power, the refrigerant enthalpy h of gas returning port according to compressor1, exhaust The refrigerant enthalpy h of mouth2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner； Efficiency generation module 40 is used for the efficiency that air conditioner is generated according to air conditioner power consumption and heating capacity.
Wherein, acquisition module 10, refrigerant enthalpy generation module 20, heating capacity generation module 50 and efficiency generation module 40 It may be disposed in the electric-control system of air conditioner.Acquisition module 10 can monitor the current working of air conditioner, the power of compressor in real time PcomWith air conditioner power consumption PPower consumption。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
Because different test points include temperature detecting point and the state difference of the refrigerant of pressure detecting point, therefore different inspections The enthalpy of the refrigerant of measuring point is different.In one embodiment of the invention, refrigerant enthalpy generation module 20 can be rule of thumb The enthalpy of refrigerant is calculated in formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below1、 The refrigerant enthalpy h of exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5With the refrigerant of indoor heat exchanger first end Enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port Enthalpy h1。
Specifically, refrigerant enthalpy generation module 20 can obtain the outdoor heat exchanger middle portion temperature in the middle part of outdoor heat exchanger t3, wherein, as shown in Fig. 2 the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3Can be by being set in the middle part of outdoor heat exchanger The detection of outdoor heat exchanger middle portion temperature sensor 03 put obtains.
Then refrigerant enthalpy generation module 20 can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generation is inhaled Gas degree of superheat Δ t1, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generation gas returning port refrigerant enthalpy is repaiied Positive divisor D1.Wherein, suction superheat Δ t1For gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1- t3.The modifying factor of gas returning port refrigerant enthalpy Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Also, the enthalpy h of saturation refrigerant under suction temperature can be also generated according to low-pressure lateral pressureAir-breathing saturation.Wherein, can be first According to low-pressure lateral pressure PLow pressureGenerate air-breathing saturation temperature Tl, such asFurther according to air-breathing saturation temperature Tl Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation, for example, hAir-breathing saturation=a1+a2Tl+a3Tl 2+a4Tl 3+a5, wherein, a1-a5 For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, refrigerant enthalpy Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration Refrigerant enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet Enthalpy h2。
Specifically, refrigerant enthalpy generation module 20 can obtain the indoor heat exchanger middle portion temperature in the middle part of indoor heat exchanger t6, wherein, as shown in Fig. 2 the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Can be by being set in the middle part of heat exchanger indoors The indoor heat exchanger middle portion temperature sensor put detects to obtain.
Then, refrigerant enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchange Device middle portion temperature t6Generate discharge superheat Δ t2, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generation The modifying factor D of exhaust outlet refrigerant enthalpy2, and according to indoor heat exchanger middle portion temperature t6Generate saturation system under delivery temperature The enthalpy h of cryogenIt is vented saturation.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2And indoor heat exchanger Middle portion temperature t6Difference, i.e. Δ t2=t2-t6.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δt2)2+d3 (Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.Row The enthalpy h of saturation refrigerant at a temperature of gasIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5To satisfy corresponding to refrigerant With fauna number.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationAfterwards, Refrigerant enthalpy generation module 20 can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy2, saturation under delivery temperature The enthalpy h of refrigerantIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7It is corresponding for refrigerant Overheated zone coefficient.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work During condition, the refrigerant superheat of indoor heat exchanger first end, refrigerant enthalpy generation module 20 can combine the degree of superheat meter of the position Calculate the refrigerant enthalpy h of indoor heat exchanger first end7。
Specifically, refrigerant enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t7In indoor heat exchanger Portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger the The modifying factor D of one end refrigerant enthalpy7, and the modifying factor of the indoor heat exchanger first end refrigerant enthalpy according to generation D7With the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturationGenerate the refrigerant enthalpy h of indoor heat exchanger first end7.Wherein, Δ t7=t7-t6,h7=D7· hIt is vented saturation+d7, wherein, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, refrigerant enthalpy generation module 20 can directly calculate the system at the end of indoor heat exchanger second Cryogen enthalpy h5：h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Also, when the current working of air conditioner is cooling condition, the liquid refrigerant enthalpy h of flash vessel8”Can according to Lower formula calculates：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Fill into the gaseous refrigerant enthalpy h of compressor8’It can be calculated according to below equation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant Close.For example, R410A refrigerants and saturation region coefficient, overheat fauna corresponding to R32 refrigerants are respectively illustrated in table 1 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, it is each to calculate The refrigerant enthalpy of individual temperature detecting point.
In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software Fruit, or the refrigerant enthalpy by each temperature detecting point of other approach acquisition.For example, when the current working of air conditioner is During heating condition, refrigerant enthalpy generation module 20 can also be according to the indoor heat exchanger middle portion temperature t in air conditioner6, gas returning port Temperature t1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With indoor heat exchanger first end Refrigerant enthalpy h7, and can be according to the high side pressure (such as pressure in the middle part of outdoor heat exchanger) in air conditioner, exhaust outlet temperature Spend t2, the second end of indoor heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the system at the end of indoor heat exchanger second Cryogen enthalpy h5, and saturated gas enthalpy and saturated liquid enthalpy under the state can be obtained according to temperature or pressure.
In an embodiment of the present invention, heating capacity generation module 50 can generate the heating capacity of air conditioner according to below equation：Wherein, QHeating capacityFor the heating capacity of air conditioner, PcomFor The power of compressor.
Because the current working of air conditioner is heating condition, thus efficiency generation module 40 can be according to air conditioner power consumption With the heat efficiency of heating capacity generation air conditioner, specifically, the heat efficiency COP of air conditioner is heating capacity=Q of air conditionerHeating capacity With power consumption PPower consumptionThe ratio between, i.e. COP=QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor and air conditioner power consumption, and pass through the low pressure of corresponding pressure sensor acquisition compressor return air mouth Lateral pressure, and gas returning port, exhaust outlet, the end of indoor heat exchanger second and interior in compressor are obtained by corresponding temperature sensor Temperature, the tonifying Qi temperature of compressor tonifying Qi entrance of heat exchanger first end, and pass through system when air conditioner is in heating condition Cryogen enthalpy generation module, heating capacity generation module and efficiency generation module are according to the temperature and pressure of above-mentioned each temperature detecting point The refrigerant enthalpy of the above-mentioned each temperature detecting point of pressing creation of power test point, it is power then in conjunction with compressor, above-mentioned each The refrigerant enthalpy and air conditioner power consumption of individual temperature detecting point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately The efficiency of air conditioner is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reaches energy-conservation With the purpose for improving heating effect.
In summary, the air conditioner of the embodiment of the present invention and its efficiency computational methods and system, by obtaining air conditioner system The physical property of refrigerant in refrigerant cycle system, and the power of air conditioner is calculated according to the physical property of refrigerant, with And the efficiency of air conditioner is further calculated, so as to be able to real-time and accurately detect the refrigeration efficiency of air conditioner and heating energy Effect.
In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom ", " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, it is for only for ease of and describes the present invention and simplify description, rather than indicates or imply that signified device or element must There must be specific orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.
In addition, term " first ", " second " are only used for describing purpose, and it is not intended that instruction or hint relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can be expressed or Implicitly include one or more this feature.In the description of the invention, " multiple " are meant that two or more, Unless otherwise specifically defined.
In the present invention, unless otherwise clearly defined and limited, term " installation ", " connected ", " connection ", " fixation " etc. Term should be interpreted broadly, for example, it may be fixedly connected or be detachably connected, or integrally；Can be that machinery connects Connect or electrically connect；Can be joined directly together, can also be indirectly connected by intermediary, can be in two elements The connection in portion or the interaction relationship of two elements.For the ordinary skill in the art, can be according to specific feelings Condition understands the concrete meaning of above-mentioned term in the present invention.
In the present invention, unless otherwise clearly defined and limited, fisrt feature can be with "above" or "below" second feature It is that the first and second features directly contact, or the first and second features pass through intermediary mediate contact.Moreover, fisrt feature exists Second feature " on ", " top " and " above " but fisrt feature are directly over second feature or oblique upper, or be merely representative of Fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be One feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height and is less than second feature.
In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means specific features, structure, material or the spy for combining the embodiment or example description Point is contained at least one embodiment or example of the present invention.In this manual, to the schematic representation of above-mentioned term not Identical embodiment or example must be directed to.Moreover, specific features, structure, material or the feature of description can be with office Combined in an appropriate manner in one or more embodiments or example.In addition, in the case of not conflicting, the skill of this area Art personnel can be tied the different embodiments or example and the feature of different embodiments or example described in this specification Close and combine.
Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is example Property, it is impossible to limitation of the present invention is interpreted as, one of ordinary skill in the art within the scope of the invention can be to above-mentioned Embodiment is changed, changed, replacing and modification.

Claims (22)

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 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 end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7And pressure The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；
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, according to the exhaust port temperatures t of exhaust outlet in the compressor2It is raw Into the enthalpy h of the refrigerant of exhaust outlet2, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generation The refrigerant enthalpy h of outdoor heat exchanger first end4, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7With The refrigerant enthalpy h of the low-pressure lateral pressure generation indoor heat exchanger first end7, according to the tonifying Qi temperature of compressor tonifying Qi entrance t8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2、 The refrigerant enthalpy h of the outdoor heat exchanger first end4, the indoor heat exchanger first end refrigerant enthalpy h7, described fill into The gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the refrigerating capacity of air conditioner；With And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to gas returning port in the compressor Gas returning port temperature t1Generate the refrigerant enthalpy h of gas returning port1Specifically 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；
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；
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, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigeration Agent enthalpy h1。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that 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 3, it is characterised in that according to the indoor heat exchanger first The indoor heat exchanger first end temperature t at end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：
According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturation Generate the refrigerant enthalpy h7。
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 port2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the exhaust port temperatures t of exhaust outlet in the compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Spend Δ t2；
According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of the exhaust outlet The enthalpy h of agent2。
7. the efficiency computational methods of air conditioner as claimed in claim 6, it is characterised in that exhaust outlet is generated according to below equation The modifying factor D of 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：
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 capacityFreeze for the air conditioner Amount, PcomFor compressor horsepower.
10. 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 appointed in claim 1-9 Method described in one.
11. 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 1-9 is realized when calculation machine program is executed by processor.
12. 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 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 second5, indoor heat exchanger first end indoor heat exchanger first end temperature t7And pressure The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；
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, according to the exhaust port temperatures t of exhaust outlet in the compressor2It is raw Into the enthalpy h of the refrigerant of exhaust outlet2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generation The refrigerant enthalpy h at the end of indoor heat exchanger second5, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7It is raw Into the refrigerant enthalpy h of indoor heat exchanger first end7, according to the tonifying Qi temperature t of compressor tonifying Qi entrance8Generation fills into compressor Gaseous refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2、 The refrigerant enthalpy h at the end of indoor heat exchanger second5, the indoor heat exchanger first end refrigerant enthalpy h7, described fill into The gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the heating capacity of air conditioner；With And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
13. the efficiency computational methods of air conditioner as claimed in claim 12, it is characterised in that described according in the compressor The gas returning port temperature t of gas returning port1Generate the refrigerant enthalpy h of gas returning port1Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
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。
14. the efficiency computational methods of air conditioner as claimed in claim 13, 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> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
15. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that described according in the compressor The exhaust port temperatures t of exhaust outlet2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically include：
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；
According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2。
16. the efficiency computational methods of the air conditioner described in claim 15, 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> </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 to the indoor heat exchange The indoor heat exchanger first end temperature t of device first end7The refrigerant enthalpy h of the indoor heat exchanger first end is generated respectively7Specifically Including：
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。
18. the efficiency computational methods of air conditioner as claimed in claim 17, 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> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
19. the efficiency computational methods of air conditioner as claimed in claim 12, it is characterised in that according to calculating below equation The refrigerant enthalpy h at the end of indoor heat exchanger second5：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
20. the efficiency computational methods of air conditioner as claimed in claim 12, it is characterised in that according to generating equation below The heating capacity of air conditioner：
Wherein, QHeating capacityFor the air conditioner heat-production Amount, PcomFor compressor horsepower.
21. 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 12-20 Any described method.
22. 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 12-20 is realized when calculation machine program is executed by processor.
CN201710774255.7A 2017-08-31 2017-08-31 Air conditioner and its efficiency computational methods Pending CN107490143A (en)

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Application publication date: 20171219