CN107514776A - Air conditioner and its efficiency computational methods - Google Patents
Air conditioner and its efficiency computational methods Download PDFInfo
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- CN107514776A CN107514776A CN201710775493.XA CN201710775493A CN107514776A CN 107514776 A CN107514776 A CN 107514776A CN 201710775493 A CN201710775493 A CN 201710775493A CN 107514776 A CN107514776 A CN 107514776A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/46—Improving electric energy efficiency or saving
- F24F11/47—Responding to energy costs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/60—Energy consumption
Abstract
The invention discloses a kind of air conditioner and its efficiency computational methods, the described method comprises the following steps：Obtain current working and power consumption, the current frequency of the compressor and housing heat dissipation capacity Q of air conditionerloss；Obtain compressor return air mouth temperature t1, exhaust port temperatures t2, outdoor heat exchanger first end temperature t4, indoor heat exchanger first end temperature t7With compressor tonifying Qi temperature t8；When current working is cooling condition, according to t1、t2、t4、t7And t8The mixture enthalpy h of gas returning port is generated respectively1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger first end mixture enthalpy h4, indoor heat exchanger first end mixture enthalpy h7, fill into compressor mixture enthalpy h8’With the mixture enthalpy h of flash vessel8”；The power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve；According to power, Qloss、h1、h2、h4、h7、h8’And h8”Generate the refrigerating capacity of air conditioner；According to the efficiency of air conditioner power consumption and refrigerating capacity generation air conditioner.
Description
Technical field
The present invention relates to air conditioner technical field, the efficiency computational methods of more particularly to a kind of air conditioner, a kind of air conditioner
With a kind of non-transitorycomputer readable storage medium.
Background technology
It is comfortably the problem of user more pays close attention to that whether air conditioner, which saves,.
Current air conditioner is difficult to maintain preferable fortune operationally due to that can not know the situation of change of efficiency
Row state, cooling or heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention
First 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, bag
Include following steps：Obtain current working, the current frequency and air conditioner power consumption of compressor of air conditioner；Obtain compressor
Housing heat dissipation capacity Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures
t2, outdoor heat exchanger first end outdoor heat exchanger first end temperature t4, 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 cooling condition, according to described
The gas returning port temperature t of gas returning port in compressor1Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to
The exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil,
According to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generate the refrigerant of outdoor heat exchanger first end
Enthalpy h4 refrigerantsWith lubricating oil enthalpy h4 lubricating oil, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7It is raw
Into the refrigerant enthalpy t of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilWith according to the compressor tonifying Qi entrance
Tonifying Qi temperature t8Generation fills into the gaseous refrigerant enthalpy h of compressor8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid system
Cryogen enthalpy h8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy
h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil
Generate the mixture enthalpy h of exhaust outlet2, according to the refrigerant enthalpy h of the outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy
h4 lubricating oilGenerate the mixture enthalpy h of outdoor heat exchanger first end4, according to the refrigerant enthalpy of the indoor heat exchanger first end
t7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7, according to the compressor of filling into
Gaseous refrigerant enthalpy h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oilGeneration fills into compressor mixture enthalpy h8’, according to the flash distillation
The liquid refrigerant enthalpy h of device8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oilGenerate the mixture enthalpy h of flash vessel8”；According to the pressure
The current frequency and preset compressor performance curve of contracting machine obtain the power of the compressor；According to the power of the compressor,
The housing heat dissipation capacity Q of the compressorloss, the gas returning port mixture enthalpy h1, the exhaust outlet mixture enthalpy h2、
The mixture enthalpy h of the outdoor heat exchanger first end4, the indoor heat exchanger first end mixture enthalpy h7, described fill into
Compressor mixture enthalpy h8’With the mixture enthalpy h of the 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 housing heat dissipation capacity of the current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature of outdoor heat exchanger first end, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When adjusting the current working of device to be cooling condition, above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point
Mixture enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the mixture enthalpy of above-mentioned each temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The running status of the real-time energy efficiency optimization air conditioner of device, reaches energy-conservation and improves the purpose of refrigeration.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add
Technical characteristic：
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor1Generation is described to return
The refrigerant enthalpy h of gas port1 refrigerantSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to institute
State gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to the indoor heat exchanger
Middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the suction superheat Δ t1With indoor heat exchange
Device middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the modifying factor of the gas returning port refrigerant enthalpy
Sub- D1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h1 refrigerant。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of the 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.
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end
t7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerantsSpecifically include：According to the indoor heat exchanger first end temperature
Spend 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 exchange
Device middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to the indoor heat exchanger first
Hold the modifying factor D of refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7 refrigerants。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the row
The enthalpy h of the refrigerant of gas port2 refrigerantsSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to
The outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According in the compressor
The exhaust port temperatures t of exhaust outlet2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to the exhaust
Degree of superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2：According to described
Modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the enthalpy of the refrigerant of the exhaust outlet
h2 refrigerants。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation
Value h4 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the refrigerating capacity of the air conditioner is generated according to below equation：
Wherein, QRefrigerating capacityFor the air conditioner
Refrigerating capacity, PcomFor compressor horsepower.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation
hI lubricating oil, wherein, i is positive integer,
hI, lubricating oil=-0.0808+1.7032ti+0.0025ti 2
Wherein, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each point is calculated according to below equationi, wherein, i is
Positive integer,
hi=(1-Cg)hI, refrigerant+CghI, lubricating oil
Cg=f/104
Wherein, Cg is mixture oil content, and f is the running frequency of the 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 for another air conditioner that fourth aspect present invention embodiment proposes,
Comprise the following steps：Obtain current working, the current frequency and air conditioner power consumption of compressor of air conditioner；Obtain compressor
Housing heat dissipation capacity Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust outlet temperature
Spend 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
Hold 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 institute
State the gas returning port temperature t of gas returning port in compressor1Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, root
According to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the enthalpy h of the refrigerant of exhaust outlet2 refrigerantsWith lubricating oil enthalpy
h2 lubricating oil, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the system at the end of indoor heat exchanger second
Cryogen enthalpy h5 refrigerantsWith lubricating oil enthalpy h5 lubricating oil, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end
t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilEnter with according to the compressor tonifying Qi
The tonifying Qi temperature t of mouth8Generation fills into the gaseous refrigerant enthalpy h of compressor8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid
State refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oil；According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy
Value h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1, according to the enthalpy h of the refrigerant of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy
h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsAnd lubrication
Oily enthalpy h5 lubricating oilGenerate the mixture enthalpy h at the end of indoor heat exchanger second5, according to the refrigeration of the indoor heat exchanger first end
Agent enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate the mixture enthalpy h of indoor heat exchanger first end7, pressure is filled into according to described
The gaseous refrigerant enthalpy h of contracting machine8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oilGeneration fills into compressor mixture enthalpy h8’, according to institute
State the liquid refrigerant enthalpy h of flash vessel8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oilGenerate the mixture enthalpy h of flash vessel8”；According to
The current frequency and preset compressor performance curve of the compressor obtain the power of the compressor；According to the compressor
The housing heat dissipation capacity Q of power, the compressorloss, the gas returning port mixture enthalpy h1, the exhaust outlet mixture enthalpy
Value h2, the end of indoor heat exchanger second mixture enthalpy h5, the indoor heat exchanger first end mixture enthalpy h7, institute
State and fill into compressor mixture enthalpy h8’With the mixture enthalpy h of the flash vessel8”Generate the heating capacity of air conditioner；And root
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner
The housing heat dissipation capacity of the current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature at the end of indoor heat exchanger second, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When adjusting the current working of device to be heating condition, above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point
Mixture enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the mixture enthalpy of above-mentioned each temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The running status of the real-time energy efficiency optimization air conditioner of device, reaches energy-conservation and improves the purpose of refrigeration.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add
Technical characteristic：
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor1Generation is described to return
The refrigerant enthalpy h of gas port1 refrigerantSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to institute
State gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat
Δt1With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；Changed according to the outdoor
Hot device middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the gas returning port refrigerant enthalpy
Modifying factor D1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1 refrigerant。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the row
The enthalpy h of the refrigerant of gas port2 refrigerantsSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to
Indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust port temperatures t of exhaust outlet in the compressor2Generation
Discharge superheat Δ t2；According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigeration
The modifying factor D of agent enthalpy2；According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy of saturation refrigerant under delivery temperature
hIt is vented saturation；According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy
hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2 refrigerants。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end
t7The refrigerant enthalpy h of the indoor heat exchanger first end is generated respectively7 refrigerantsSpecifically include：In the middle part of the indoor heat exchanger
Indoor heat exchanger middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the overheat
Spend Δ t7With the indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；Root
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy
hIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerants。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation
Value h5 refrigerants：
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
Heating capacity, PcomFor compressor horsepower.
According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation
hI lubricating oil, wherein, i is positive integer,
hI, lubricating oil=-0.0808+1.7032ti+0.0025ti 2
Wherein, tiFor the temperature of temperature detecting point.
According to one embodiment of present invention, the mixture enthalpy h of each point is calculated according to below equationi, wherein, i is
Positive integer,
hi=(1-Cg)hI, refrigerant+CghI, lubricating oil
Cg=f/104
Wherein, Cg is mixture oil content, and f is the running frequency of the 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 fourth aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, 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 fourth aspect present invention is implemented when being executed by processor
The efficiency computational methods for the air conditioner that example proposes.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage
Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner
Running status, reach energy-conservation and improve the purpose of heating effect.
Brief description of the drawings
Fig. 1 is the structural representation according to the air conditioner of one embodiment of the invention；
Fig. 2 is the flow chart according to a kind of efficiency computational methods of air conditioner of the embodiment of the present invention；
Fig. 3 is the flow chart according to the efficiency computational methods of another air conditioner of the embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end
Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached
The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
The air conditioner of the embodiment of the present invention and its efficiency computational methods are described below in conjunction with the accompanying drawings.
In an embodiment of the present invention, air conditioner can be twin-stage steam compressing air conditioner device.
As shown in figure 1, the air conditioner of the embodiment of the present invention may include compressor 100, four-way valve 200, outdoor heat exchanger
300th, restricting element 400, indoor heat exchanger 500, restricting element 600 and flash vessel 700.Wherein, the exhaust outlet of compressor 100 leads to
Four-way valve 200 is crossed with the second end of outdoor heat exchanger 300 to be connected, the first end of outdoor heat exchanger 300 by restricting element 600 with
The first end of flash vessel 700 is connected, and the second end of flash vessel 700 passes through the second end of restricting element 400 and indoor heat exchanger 500
It is connected, the first end of indoor heat exchanger 500 is connected by four-way valve 200 with the gas returning port of compressor 100, and the of flash vessel 700
Three ends are connected with the tonifying Qi entrance of compressor 100.
When the current working of air conditioner is cooling condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and
A2 ends are directly connected with outdoor heat exchanger 300, and refrigerant is flowed to as shown in the solid arrow in Fig. 1；When the current working of air conditioner
For heating condition when, the exhaust outlet of compressor 100 is directly connected by the A1 ends of four-way valve 200 and A4 ends with indoor heat exchanger 500
Logical, refrigerant is flowed to as shown in the dotted arrow in Fig. 1, is specifically not detailed here.
Fig. 2 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention.It is as shown in Fig. 2 of the invention
The efficiency computational methods of the air conditioner of embodiment comprise the following steps：
S101, the current working of air conditioner, the current frequency of compressor and air conditioner power consumption are obtained, and obtain compression
The housing heat dissipation capacity Q of machineloss。
Specifically, the current working of air conditioner, the current frequency of compressor can be monitored in real time by the electric-control system of air conditioner
Rate and air conditioner power consumption PPower consumption。
In one embodiment of the invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss,
The housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t9+273.15)4+(9.4+0.052×(t2-t9))×
ACompressor×(t2-t9),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition, t by looking into pressure contracting type number9For outdoor ring
Border temperature, it can be obtained by being disposed in the outdoor the temperature sensor at heat exchanger fin, t2For the exhaust of exhaust outlet in compressor
Mouth temperature.
S102, 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。
Specifically, can be by setting temperature sensor respectively in corresponding temperature test point to detect the temperature of the temperature detecting point
Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature
t1；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t2；By setting
The temperature sensor (as shown in Figure 1 04) put in outdoor heat exchanger first end obtains outdoor heat exchanger first end temperature t4；It is logical
Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end
t7；Compressor tonifying Qi entrance is obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi porch
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.
S103, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1
Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in compressor2
Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the outdoor heat exchanger of outdoor heat exchanger first end
First end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oil, changed according to interior
The indoor heat exchanger first end temperature t of hot device first end7Generate the refrigerant enthalpy t of indoor heat exchanger first end7 refrigerantsAnd lubrication
Oily enthalpy h7 lubricating oilWith the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor
h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oil。
Specifically, during air conditioner works, due to the mixing of the refrigerant and lubricating oil of different temperatures test point
The state of thing is different, therefore the refrigerant enthalpy of different temperatures test point and lubricating oil enthalpy are different.At one of the present invention
In embodiment, rule of thumb refrigerant enthalpy and lubricating oil enthalpy can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、
The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end refrigerant enthalpy h4 refrigerantsAnd profit
Lubricating oil enthalpy h4 lubricating oil, indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, fill into compressor
Gaseous refrigerant enthalpy h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy
h8 " lubricating oilDetailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is cooling condition
When, the refrigerant superheat of the gas returning port of compressor, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1 refrigerant。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Generate the system of gas returning port
Cryogen enthalpy h1 refrigerantSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to gas returning port temperature
t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to indoor heat exchanger middle portion temperature t6Generate air-breathing temperature
The enthalpy h of the lower saturation refrigerant of degreeAir-breathing saturation；According to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6The gas returning port system of generation
The modifying factor D of cryogen enthalpy1；According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationIt is raw
Into refrigerant enthalpy h1 refrigerant。
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (1)Air-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5 (1)
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (2)1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6 (2)
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger
Interior heat exchanger middle portion temperature t6, then according to gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ
t1=t1-t6, and according to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the amendment of gas returning port refrigerant enthalpy
Factor D1, such as shown in above-mentioned formula (2), while according to indoor heat exchanger middle portion temperature t6Generate saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturation, such as shown in above-mentioned formula (1).Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigeration
The enthalpy h of agentAir-breathing saturationGenerate refrigerant enthalpy h1 refrigerant, h1 refrigerant=D1·hAir-breathing saturation+d7, wherein, d7For overheat corresponding to refrigerant
Fauna number.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is refrigeration
During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the
The refrigerant enthalpy h of one end7 refrigerants。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7It is raw
Into the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsSpecifically include：According to indoor heat exchanger first end temperature t7Changed with interior
Hot device middle portion temperature t6Generate degree of superheat Δ t7；According to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchange
The modifying factor D of device first end refrigerant enthalpy7；According to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7With it is full
With the enthalpy h of refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7 refrigerants。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (3)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, can be first according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate the degree of superheat
Δt7=t7-t6, then according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant
The modifying factor D of enthalpy7, such as shown in above-mentioned formula (3), while according to indoor heat exchanger middle portion temperature t6Generate under suction temperature
The enthalpy h of saturation refrigerantAir-breathing saturation, such as shown in above-mentioned formula (1).Finally, according to the indoor heat exchanger first end refrigerant of generation
The modifying factor D of enthalpy7With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7 refrigerants, h7 refrigerants=D7·hAir-breathing saturation+d7,
Wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is cooling condition, pressure
The refrigerant superheat of the exhaust outlet of contracting machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2 refrigerants。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the system of exhaust outlet
The enthalpy h of cryogen2 refrigerantsSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to outdoor heat exchange
Device middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the exhaust outlet temperature of exhaust outlet in compressor
Spend t2With outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to discharge superheat Δ t2In outdoor heat exchanger
Portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2：According to modifying factor D2, saturation refrigerant under delivery temperature
Enthalpy hIt is vented saturationGenerate the enthalpy h of the refrigerant of exhaust outlet2 refrigerants。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (4)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger
External heat exchanger middle portion temperature t3, then according to the exhaust port temperatures t of exhaust outlet in compressor2With outdoor heat exchanger middle portion temperature t3
Generate discharge superheat Δ t2=t2-t3, and according to discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Generate exhaust outlet
The modifying factor D of refrigerant enthalpy2, such as shown in above-mentioned formula (4), while according to outdoor heat exchanger middle portion temperature t3Generation exhaust
At a temperature of saturation refrigerant enthalpy hIt is vented saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5For saturation corresponding to refrigerant
Fauna number.Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturation
Generate the refrigerant enthalpy h of exhaust outlet2 refrigerants, h2 refrigerants=D2·hIt is vented saturation+d7, wherein, d7To overheat fauna corresponding to refrigerant
Number.
For the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants, when the current working of air conditioner is cooling condition,
The refrigerant supercooling of outdoor heat exchanger first end, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerants。
According to one embodiment of present invention, the refrigerant enthalpy of outdoor heat exchanger first end is generated according to following formula (5)
Value h4 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, fill into the gaseous refrigerant enthalpy h of compressor8 ' refrigerantsIt can be calculated according to below equation：
h8 ' refrigerants=a1+a2*t8+a3*t8 2+a4*t8 3+a5, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, a1-a5
For saturation region coefficient corresponding to refrigerant.
The liquid refrigerant enthalpy h of flash vessel8 " refrigerantsIt can be calculated according to below equation：
h8 " refrigerants=c1+c2*t8+c3*t8 2+c4*t8 3, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, c1-c4For system
Supercooling fauna number corresponding to cryogen.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant
Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone
Coefficient：
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature
The refrigerant enthalpy of measuring point.
It should be noted that in other embodiments of the invention, can also directly invoke the result of calculation of software, or pass through
Other approach obtain the refrigerant enthalpy of each temperature detecting point.For example, when the current working of air conditioner is cooling condition
When, can also be according to the low pressure in air conditioner, gas returning port temperature t1, indoor heat exchanger first end temperature t7Respectively obtain return-air
The refrigerant enthalpy h of mouth1 refrigerantWith the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, and can be according to the high pressure in air conditioner
Pressure, exhaust port temperatures t2, outdoor heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2 refrigerantsAnd outdoor
The refrigerant enthalpy h of heat exchanger first end4 refrigerants, and saturated air under the state can be obtained according to tonifying Qi temperature or pressure
Body enthalpy h8 ' refrigerantsAnd saturated liquid enthalpy h8 " refrigerants。
In addition, the lubricating oil enthalpy h for each temperature detecting pointI lubricating oil, can be calculated according to below equation：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy of gas returning port can be calculated out
Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, outdoor heat exchanger first end lubricating oil enthalpy h4 lubricating oilAnd indoor heat exchanger
The lubricating oil enthalpy h of first end7 lubricating oil, fill into the lubricating oil enthalpy h of compressor8 ' lubricating oil, flash vessel lubricating oil enthalpy h8 " lubricationsOil.
S104, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port
Value h1, according to the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to
The refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixture of outdoor heat exchanger first end
Enthalpy h4, according to the refrigerant enthalpy t of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate indoor heat exchanger the
The mixture enthalpy h of one end7, according to the gaseous refrigerant enthalpy h for filling into compressor8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oilGeneration is mended
Enter compressor mixture enthalpy h8’, according to the liquid refrigerant enthalpy h of flash vessel8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oilGeneration is dodged
The mixture enthalpy h of steaming device8”。
Specifically, the mixture enthalpy h of each temperature detecting point can be calculated according to below equationi：
hi=(1-Cg)hI refrigerants+CghI lubricating oil
Cg=f/104,
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, the mixed of gas returning port can be calculated out
Compound enthalpy h1, exhaust outlet mixture enthalpy h2, outdoor heat exchanger first end mixture enthalpy h4, indoor heat exchanger first
The mixture enthalpy h at end7, fill into compressor mixture enthalpy h8’With the mixture enthalpy h of flash vessel8”。
S105, the power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve.
Specifically, (it can be provided by compressor producer according to preset compressor performance curve, and be stored in advance in compressor
In) calculate the flow and compressor consumption power for obtaining compressor under different running frequencies.
S106, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port mixture enthalpy h1, exhaust
The mixture enthalpy h of mouth2, outdoor heat exchanger first end mixture enthalpy h4, indoor heat exchanger first end mixture enthalpy
h7, fill into compressor mixture enthalpy h8’With the mixture 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 capacityFreeze for air conditioner
Amount, PcomFor compressor horsepower.
S107, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Because the current working of air conditioner is cooling condition, thus can be generated according to air conditioner power consumption and refrigerating capacity empty
The refrigeration efficiency of device is adjusted, specifically, the refrigeration efficiency of air conditioner is the ratio between the refrigerating capacity of air conditioner and power consumption, i.e. EER=
QRefrigerating capacity/PPower consumption。
, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner
State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner
Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner
The housing heat dissipation capacity of the current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature of outdoor heat exchanger first end, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When adjusting the current working of device to be cooling condition, above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point
Mixture enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the mixture enthalpy of above-mentioned each temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The running status of the real-time energy efficiency optimization air conditioner of device, reaches energy-conservation and improves the purpose of refrigeration.
Corresponding above-described embodiment, the present invention also propose a kind of air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor
The computer program of operation, during computing device computer program, the air conditioner that the above embodiment of the present invention proposes can be achieved
Efficiency computational methods.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, be entered according to real-time energy efficiency
Row running status optimizes, and 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.
The air conditioner and its efficiency computational methods of above-described embodiment can detect the refrigeration efficiency of air conditioner, to detect air-conditioning
The heat efficiency of device, the present invention also propose the efficiency computational methods of another air conditioner.
As shown in figure 3, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：
S201, the current working of air conditioner, the current frequency of compressor and air conditioner power consumption are obtained, and obtain compression
The housing heat dissipation capacity Q of machineloss。
Specifically, the current working of air conditioner, the current frequency of compressor can be monitored in real time by the electric-control system of air conditioner
Rate and air conditioner power consumption PPower consumption。
In one embodiment of the invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss,
The housing heat dissipation capacity Q of compressor can be specifically generated according to below equationloss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))×
ACompressor×(t2-t8),
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition, t by looking into pressure contracting type number8For compressor
The tonifying Qi temperature of tonifying Qi entrance, it can be obtained by being arranged on the temperature sensor (as shown in Figure 1 08) of compressor tonifying Qi entrance,
t2, can be by setting the temperature sensor of exhaust outlet within the compressor (such as Fig. 1 institutes for the exhaust port temperatures of exhaust outlet in compressor
Show 02).
S202, 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, can be by setting temperature sensor respectively in corresponding temperature test point to detect the temperature of the temperature detecting point
Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature
t1；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t2；By setting
The temperature sensor (as shown in Figure 1 05) for putting the end of heat exchanger second indoors obtains indoor heat exchanger the second end temperature t5；It is logical
Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end
t7；Compressor tonifying Qi entrance is obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi porch
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.
S203, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1
Generate the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures t of exhaust outlet in compressor2
Generate the enthalpy h of the refrigerant of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the indoor heat exchange at the end of indoor heat exchanger second
The second end of device temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oil, according to interior
The indoor heat exchanger first end temperature t of heat exchanger first end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsAnd profit
Lubricating oil enthalpy h7 lubricating oilWith the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor
h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oil。
Specifically, during air conditioner works, due to the mixing of the refrigerant and lubricating oil of different temperatures test point
The state of thing is different, therefore the refrigerant enthalpy of different temperatures test point and lubricating oil enthalpy are different.At one of the present invention
In embodiment, rule of thumb refrigerant enthalpy and lubricating oil enthalpy can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1 refrigerantWith lubricating oil enthalpy h1 lubricating oil、
The refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second refrigerant enthalpy h5 refrigerantsAnd profit
Lubricating oil enthalpy h5 lubricating oil, indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oil, fill into compressor
Gaseous refrigerant enthalpy h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy
h8 " lubricating oilDetailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1 refrigerant, when the current working of air conditioner is heating condition
When, the refrigerant superheat of the gas returning port of compressor, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1 refrigerant。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Generate the system of gas returning port
Cryogen enthalpy h1 refrigerantSpecifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to gas returning port temperature
t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to suction superheat Δ t1With outdoor heat exchanger middle part
Temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to outdoor heat exchanger middle portion temperature t3Generate under suction temperature
The enthalpy h of saturation refrigerantAir-breathing saturation；According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of gas returning port1 refrigerant。
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (6)Air-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (7)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger
External heat exchanger middle portion temperature t3, then according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ
t1=t1-t3, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy
Factor D1, such as shown in above-mentioned formula (7), while according to outdoor heat exchanger middle portion temperature t3Generate saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturation, such as shown in above-mentioned formula (6).Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigeration
The enthalpy h of agentAir-breathing saturationGenerate refrigerant enthalpy h1 refrigerant, h1 refrigerant=D1·hAir-breathing saturation+d7, wherein, d7For overheat corresponding to refrigerant
Fauna number.
For the refrigerant enthalpy h of exhaust outlet in compressor2 refrigerants, when the current working of air conditioner is heating condition, pressure
The refrigerant superheat of the exhaust outlet of contracting machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2 refrigerants。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the system of exhaust outlet
The enthalpy h of cryogen2 refrigerantsSpecifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to indoor heat exchange
Indoor heat exchanger middle portion temperature t in the middle part of device6With the exhaust port temperatures t of exhaust outlet in compressor2Generate discharge superheat Δ t2；
According to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to
Indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to exhaust outlet refrigerant enthalpy
Modifying factor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (8)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, the temperature sensor (as shown in Figure 1 06) being disposed in the interior in the middle part of heat exchanger can be first passed through and obtain room
Interior heat exchanger middle portion temperature t6, then according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6
Generate discharge superheat Δ t2=t2-t6, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet
The modifying factor D of refrigerant enthalpy2, such as shown in above-mentioned formula (8), meanwhile, according to indoor heat exchanger middle portion temperature t6Generation exhaust
At a temperature of saturation refrigerant enthalpy hIt is vented saturation,Wherein, a1-a5For refrigerant pair
The saturation region coefficient answered.Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy
Value hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2 refrigerants, h2 refrigerants=D2·hIt is vented saturation+d7, wherein, d7For mistake corresponding to refrigerant
Hot-zone coefficient.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerants, when the current working of air conditioner is heating
During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the
The refrigerant enthalpy h of one end7 refrigerants。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Point
Not Sheng Cheng indoor heat exchanger first end refrigerant enthalpy h7 refrigerantsSpecifically include：Indoor heat exchange in the middle part of indoor heat exchanger
Device middle portion temperature t6With indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to degree of superheat Δ t7And indoor heat exchanger
Middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；Freezed according to indoor heat exchanger first end
The modifying factor D of agent enthalpy7, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the system of indoor heat exchanger first end
Cryogen enthalpy h7 refrigerants。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (9)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, can be first according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generation overheat
Spend Δ t7=t7-t6, then according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigeration
The modifying factor D of agent enthalpy7, such as shown in above-mentioned formula (9), meanwhile, according to indoor heat exchanger middle portion temperature t6Generate delivery temperature
The enthalpy h of lower saturation refrigerantIt is vented saturation,Wherein, a1-a5For corresponding to refrigerant
Saturation region coefficient.Finally, according to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy of generation7Under delivery temperature
The enthalpy h of saturation refrigerantIt is vented saturationGenerate refrigerant enthalpy h7 refrigerants, h7 refrigerants=D7·hIt is vented saturation+d7, wherein, d7For refrigerant pair
The overheated zone coefficient answered.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, when the current working of air conditioner is heating condition,
The refrigerant supercooling at the end of indoor heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants。
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to following formula (10)
Value h5 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, fill into the gaseous refrigerant enthalpy h of compressor8 ' refrigerantsIt can be calculated according to below equation：
h8 ' refrigerants=a1+a2*t8+a3*t8 2+a4*t8 3+a5, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, a1-a5
For saturation region coefficient corresponding to refrigerant.
The liquid refrigerant enthalpy h of flash vessel8 " refrigerantsIt can be calculated according to below equation：
h8 " refrigerants=c1+c2*t8+c3*t8 2+c4*t8 3, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, c1-c4For system
Supercooling fauna number corresponding to cryogen.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant
Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone
Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection
The refrigerant enthalpy of point.
It should be noted that in other embodiments of the invention, can also directly invoke the result of calculation of software, or pass through
Other approach obtain the refrigerant enthalpy of each temperature detecting point.For example, when the current working of air conditioner is heating condition
When, can also be according to the low pressure in air conditioner, gas returning port temperature t1, the second end of indoor heat exchanger temperature t5Respectively obtain return-air
The refrigerant enthalpy h of mouth1 refrigerantWith the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants, and can be according to the high pressure in air conditioner
Pressure, exhaust port temperatures t2, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy h of exhaust outlet2 refrigerantsAnd interior
The refrigerant enthalpy h of heat exchanger first end7 refrigerants, and saturated air under the state can be obtained according to tonifying Qi temperature or pressure
Body enthalpy h8 ' refrigerantsAnd saturated liquid enthalpy h8 " refrigerants。
For the lubricating oil enthalpy h of each temperature detecting pointI lubricating oil, can be calculated according to below equation：
hI lubricating oil=-0.0808+1.7032ti+0.0025t2 i,
Wherein, i is positive integer, tiFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy of gas returning port can be calculated out
Value h1 lubricating oil, exhaust outlet lubricating oil enthalpy h2 lubricating oil, the end of indoor heat exchanger second lubricating oil enthalpy h5 lubricating oilAnd indoor heat exchanger
The lubricating oil enthalpy h of first end7 lubricating oil, fill into compressor and lubricating oil enthalpy h8 ' lubricating oil, flash vessel lubricating oil enthalpy h8”ProfitIt is sliding
Oil.
S204, according to the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy of gas returning port
Value h1, according to the enthalpy h of the refrigerant of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, root
According to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the mixed of the end of indoor heat exchanger second
Compound enthalpy h5, according to the refrigerant enthalpy h of indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGenerate indoor heat exchange
The mixture enthalpy h of device first end7, according to the gaseous refrigerant enthalpy h for filling into compressor8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oilIt is raw
Into filling into compressor mixture enthalpy h8’, according to the liquid refrigerant enthalpy h of flash vessel8 " refrigerantsWith lubricating oil enthalpy h8 " lubricating oilIt is raw
Into the mixture enthalpy h of flash vessel8”。
Specifically, the mixture enthalpy h of each point can be calculated according to below equationi：
hi=(1-Cg)hI, refrigerant+CghI, lubricating oil
Cg=f/104
Wherein, CgFor mixture oil content, f is the running frequency of compressor.Thus, the mixed of gas returning port can be calculated out
Compound enthalpy h1, exhaust outlet mixture enthalpy h2, the end of indoor heat exchanger second mixture enthalpy h5, indoor heat exchanger first
The mixture enthalpy h at end7, fill into compressor mixture enthalpy h8’With the mixture enthalpy h of flash vessel8”。
S205, the power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve.
Specifically, (it can be provided by compressor producer according to preset compressor performance curve, and be stored in advance in compressor
In) calculate the flow and compressor consumption power for obtaining compressor under different running frequencies.
S206, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port mixture enthalpy h1, exhaust
The mixture enthalpy h of mouth2, the end of indoor heat exchanger second mixture enthalpy h5With the mixture enthalpy of indoor heat exchanger first end
h7, fill into compressor mixture enthalpy h8’With the mixture enthalpy h of flash vessel8”Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to equation below：
Wherein, QHeating capacityFor air conditioner heat-production
Amount, PcomFor compressor horsepower.
S207, the efficiency of air conditioner is generated according to air conditioner power consumption and heating capacity.
Because the current working of air conditioner is heating condition, thus can be generated according to air conditioner power consumption and heating capacity empty
The heat efficiency of device is adjusted, specifically, the heat efficiency of air conditioner is the ratio between the heating capacity of air conditioner and power consumption, i.e. COP=
QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner
State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner
Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner
The housing heat dissipation capacity of the current frequency of machine, air conditioner power consumption and compressor, and obtain gas returning port in compressor, exhaust outlet,
The tonifying Qi temperature at the end of indoor heat exchanger second, the temperature of indoor heat exchanger first end and compressor tonifying Qi entrance, and in sky
When adjusting the current working of device to be heating condition, above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point
Mixture enthalpy, the power of compressor is then obtained according to the current frequency of compressor and preset compressor performance curve, and
The housing heat dissipation capacity of power, compressor with reference to compressor, the mixture enthalpy of above-mentioned each temperature detecting point and air conditioner consumption
Electrical power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air-conditioning
The running status of the real-time energy efficiency optimization air conditioner of device, reaches energy-conservation and improves the purpose of refrigeration.
Corresponding above-described embodiment, the present invention also propose a kind of air conditioner.
The air conditioner of the embodiment of the present invention, including memory, processor and storage are on a memory and can be on a processor
The computer program of operation, during computing device computer program, a kind of air-conditioning that the above embodiment of the present invention proposes can be achieved
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, a kind of efficiency computational methods for 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.
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 (28)
1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the current frequency and air conditioner power consumption of compressor of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
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 compressor1It is raw
Into the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures of exhaust outlet in the compressor
t2Generate the refrigerant enthalpy h of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the outdoor of the outdoor heat exchanger first end
Heat exchanger first end temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oil, according to
The indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end
t7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilWith the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gaseous state of compressor
Refrigerant enthalpy h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy
h8 " lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1,
According to the refrigerant enthalpy h of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, according to
The refrigerant enthalpy h of the outdoor heat exchanger first end4 refrigerantsWith lubricating oil enthalpy h4 lubricating oilGenerate the mixed of outdoor heat exchanger first end
Compound enthalpy h4, according to the refrigerant enthalpy t of the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration is indoor
The mixture enthalpy h of heat exchanger first end7, according to the gaseous refrigerant enthalpy h for filling into compressor8 ' refrigerantsWith lubricating oil enthalpy
Value h8 ' lubricating oilGeneration fills into compressor mixture enthalpy h8’, according to the liquid refrigerant enthalpy h of the flash vessel8 " refrigerantsAnd lubrication
Oily enthalpy h8 " lubricating oilGenerate the mixture enthalpy h of flash vessel8”；
The power of the compressor is obtained according to the current frequency of the compressor and preset compressor performance curve；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port mixture enthalpy h1、
The mixture enthalpy h of the exhaust outlet2, the outdoor heat exchanger first end mixture enthalpy h4, the indoor heat exchanger first
The mixture enthalpy h at end7, described fill into compressor mixture enthalpy h8’With the mixture enthalpy h of the flash vessel8”Generate air-conditioning
The refrigerating capacity of device；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 the gas returning port1 refrigerantSpecifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；
According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor of gas returning port refrigerant enthalpy
D1；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigeration
Agent enthalpy h1 refrigerant。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that the suction is generated according to below equation
The enthalpy h of saturation refrigerant at a temperature of gasAir-breathing saturation：
hAir-breathing saturation=a1+a2t6+a3t2 6+a4t3 6+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
4. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that returned according to below equation generation
The modifying factor D of gas port refrigerant enthalpy1：
D1=1+d1Δt1+d2(Δt1)2+d3(Δt1)t6+d4(Δt1)2t6+d5(Δt1)t2 6+d6(Δt1)2t2 6,
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 3, it is characterised in that according to the indoor heat exchanger first
The indoor heat exchanger first end temperature t at end7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerantsSpecifically include：
According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy
Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturation
Generate the refrigerant enthalpy h7 refrigerants。
6. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that the room is generated according to below equation
The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
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Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to exhaust outlet in the compressor
Exhaust port temperatures t2Generate the enthalpy h of the refrigerant of the exhaust outlet2 refrigerantsSpecifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the exhaust port temperatures t of exhaust outlet in the compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat
Spend Δ t2；
According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the amendment of exhaust outlet refrigerant enthalpy
Factor D2：
According to the modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of the exhaust outlet
The enthalpy h of agent2 refrigerants。
8. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the row is generated according to below equation
The modifying factor D of gas port refrigerant enthalpy2：
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Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated according to below equation
The refrigerant enthalpy h of external heat exchanger first end4 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation
The refrigerating capacity of air conditioner：
Wherein, QRefrigerating capacityFreeze for the air conditioner
Amount, PcomFor compressor horsepower.
11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each
The lubricating oil enthalpy h of temperature detecting pointI lubricating oil, wherein, i is positive integer,
hI, lubricating oil=-0.0808+1.7032ti+0.0025ti 2
Wherein, tiFor the temperature of temperature detecting point.
12. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each
The mixture enthalpy h of pointi, wherein, i is positive integer,
hi=(1-Cg)hI, refrigerant+CghI, lubricating oil
Cg=f/104
Wherein, Cg is mixture oil content, and f is the running frequency of the compressor.
13. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described
The computer program run on processor, described in the computing device during computer program, realize as in claim 1-12
Any described method.
14. 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 1-12 is realized when calculation machine program is executed by processor.
15. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the current frequency and air conditioner power consumption of compressor of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
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 compressor1It is raw
Into the refrigerant enthalpy h of gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oil, according to the exhaust port temperatures of exhaust outlet in the compressor
t2Generate the enthalpy h of the refrigerant of exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oil, according to the room at the end of indoor heat exchanger second
Interior the second end of heat exchanger temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oil, root
According to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end
Value h7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilWith the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gas of compressor
State refrigerant enthalpy h8 ' refrigerantsWith lubricating oil enthalpy h8 ' lubricating oil, flash vessel liquid refrigerant enthalpy h8 " refrigerantsWith lubricating oil enthalpy
h8 " lubricating oil；
According to the refrigerant enthalpy h of the gas returning port1 refrigerantWith lubricating oil enthalpy h1 lubricating oilGenerate the mixture enthalpy h of gas returning port1,
According to the enthalpy h of the refrigerant of the exhaust outlet2 refrigerantsWith lubricating oil enthalpy h2 lubricating oilGenerate the mixture enthalpy h of exhaust outlet2, root
According to the refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerantsWith lubricating oil enthalpy h5 lubricating oilGenerate the end of indoor heat exchanger second
Mixture enthalpy h5, according to the refrigerant enthalpy h of the indoor heat exchanger first end7 refrigerantsWith lubricating oil enthalpy h7 lubricating oilGeneration
The mixture enthalpy h of indoor heat exchanger first end7, according to the gaseous refrigerant enthalpy h for filling into compressor8 ' refrigerantsAnd lubrication
Oily enthalpy h8 ' lubricating oilGeneration fills into compressor mixture enthalpy h8’, according to the liquid refrigerant enthalpy h of the flash vessel8 " refrigerantsWith
Lubricating oil enthalpy h8 " lubricating oilGenerate the mixture enthalpy h of flash vessel8”；
The power of the compressor is obtained according to the current frequency of the compressor and preset compressor performance curve；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port mixture enthalpy h1、
The mixture enthalpy h of the exhaust outlet2, the end of indoor heat exchanger second mixture enthalpy h5, the indoor heat exchanger first
The mixture enthalpy h at end7, described fill into compressor mixture enthalpy h8’With the mixture enthalpy h of the flash vessel8”Generate air-conditioning
The heating capacity of device；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
16. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to return-air in the compressor
The gas returning port temperature t of mouth1Generate the refrigerant enthalpy h of the gas returning port1 refrigerantSpecifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy
Factor D1；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationIt is raw
Into the refrigerant enthalpy h of the gas returning port1 refrigerant。
17. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that according to generating below equation
The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
18. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that according to generating below equation
The modifying factor D of gas returning port refrigerant enthalpy1：
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<msub>
<mi>&Delta;t</mi>
<mn>1</mn>
</msub>
<mo>)</mo>
</mrow>
<msub>
<mi>t</mi>
<mn>3</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>4</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>1</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<msub>
<mi>t</mi>
<mn>3</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>5</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>1</mn>
</msub>
<mo>)</mo>
</mrow>
<msubsup>
<mi>t</mi>
<mn>3</mn>
<mn>2</mn>
</msubsup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>6</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>1</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<msubsup>
<mi>t</mi>
<mn>3</mn>
<mn>2</mn>
</msubsup>
<mo>,</mo>
</mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
19. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that be vented according in the compressor
The exhaust port temperatures t of mouth2Generate the enthalpy h of the refrigerant of the exhaust outlet2 refrigerantsSpecifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor
Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy
Factor D2；
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 refrigerants。
20. the efficiency computational methods of the air conditioner described in claim 19, it is characterised in that the row is generated according to below equation
The modifying factor D of gas port refrigerant enthalpy2：
<mrow>
<msub>
<mi>D</mi>
<mn>2</mn>
</msub>
<mo>=</mo>
<mn>1</mn>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>1</mn>
</msub>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>3</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<msub>
<mi>t</mi>
<mn>6</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>4</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<msub>
<mi>t</mi>
<mn>6</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>5</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<msubsup>
<mi>t</mi>
<mn>6</mn>
<mn>2</mn>
</msubsup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>6</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>2</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<msubsup>
<mi>t</mi>
<mn>6</mn>
<mn>2</mn>
</msubsup>
<mo>,</mo>
</mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
21. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that according to the indoor heat exchanger
The indoor heat exchanger first end temperature t of one end7The refrigerant enthalpy h of the indoor heat exchanger first end is generated respectively7 refrigerantsSpecifically
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 refrigerants。
22. the efficiency computational methods of air conditioner as claimed in claim 21, it is characterised in that according to generating below equation
The modifying factor D of indoor heat exchanger first end refrigerant enthalpy7：
<mrow>
<msub>
<mi>D</mi>
<mn>7</mn>
</msub>
<mo>=</mo>
<mn>1</mn>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>1</mn>
</msub>
<msub>
<mi>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>2</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>3</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>)</mo>
</mrow>
<msub>
<mi>t</mi>
<mn>6</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>4</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<msub>
<mi>t</mi>
<mn>6</mn>
</msub>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>5</mn>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>)</mo>
</mrow>
<msubsup>
<mi>t</mi>
<mn>6</mn>
<mn>2</mn>
</msubsup>
<mo>+</mo>
<msub>
<mi>d</mi>
<mn>6</mn>
</msub>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>&Delta;t</mi>
<mn>7</mn>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<msubsup>
<mi>t</mi>
<mn>6</mn>
<mn>2</mn>
</msubsup>
<mo>,</mo>
</mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
23. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to calculating below equation
The refrigerant enthalpy h at the end of indoor heat exchanger second5 refrigerants：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
24. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to generating equation below
The heating capacity of air conditioner：
Wherein, QHeating capacityFor the air conditioner heat-production
Amount, PcomFor compressor horsepower.
25. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that calculated according to below equation each
The lubricating oil enthalpy h of temperature detecting pointI lubricating oil, wherein, i is positive integer,
hI, lubricating oil=-0.0808+1.7032ti+0.0025ti 2
Wherein, tiFor the temperature of temperature detecting point.
26. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that calculated according to below equation each
The mixture enthalpy h of pointi, wherein, i is positive integer,
hi=(1-Cg)hI, refrigerant+CghI, lubricating oil
Cg=f/104
Wherein, Cg is mixture oil content, and f is the running frequency of the compressor.
27. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described
The computer program run on processor, described in the computing device during computer program, realize as in claim 15-26
Any described method.
28. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter
The method as described in any in claim 15-26 is realized when calculation machine program is executed by processor.
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| CN105091439A (en) * | 2014-05-07 | 2015-11-25 | 苏州必信空调有限公司 | Computing method of refrigerating capacity and refrigerating efficiency of oil-free refrigerating system and refrigerating system |
| CN206192418U (en) * | 2016-11-04 | 2017-05-24 | 清华大学 | Refrigerant mass flow measuring apparatu and collection system among refrigerating system of basis |
| CN106524548A (en) * | 2016-11-07 | 2017-03-22 | 清华大学 | Refrigerant mass and flow measuring method and device and measuring instrument |
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