CN107367037A - Air conditioner and its efficiency computational methods - Google Patents
Air conditioner and its efficiency computational methods Download PDFInfo
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- CN107367037A CN107367037A CN201710776059.3A CN201710776059A CN107367037A CN 107367037 A CN107367037 A CN 107367037A CN 201710776059 A CN201710776059 A CN 201710776059A CN 107367037 A CN107367037 A CN 107367037A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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Abstract
The invention discloses a kind of air conditioner and its efficiency computational methods, this method to comprise the following steps：Obtain current working, the power and air conditioner power consumption of compressor；Obtain compressor return air mouth temperature t1, exhaust outlet of compressor temperature t2, indoor heat exchanger middle portion temperature t6With compressor tonifying Qi temperature t8；According to indoor environment temperature t10And t6Generate indoor heat exchanger first end temperature t7With the second end of indoor heat exchanger temperature t5；When current working is heating condition, according to t1、t2、t5、t7And t8The refrigerant enthalpy h of gas returning port is generated respectively1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to h1、h2、h5、h7、h8’And h8”Generate the heating capacity of air conditioner；According to the efficiency of air conditioner power consumption and heating 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, 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.
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 power and air conditioner power consumption of compressor of air conditioner；Obtain return-air in compressor
The gas returning port temperature t of mouth1, in the compressor exhaust outlet exhaust port temperatures t2, in indoor heat exchanger in the middle part of indoor heat exchanger
Portion temperature t6With the tonifying Qi temperature t of compressor tonifying Qi entrance8；According to indoor environment temperature t10In the middle part of the indoor heat exchanger
Indoor heat exchanger middle portion temperature t6Generate the indoor heat exchanger first end temperature t of indoor heat exchanger first end7With indoor heat exchanger
The second end of indoor heat exchanger temperature t at two ends5；When the current working of the air conditioner is heating condition, according to the compression
The gas returning port temperature t of gas returning port in machine1Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust of exhaust outlet in the compressor
Mouth temperature t2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the end of indoor heat exchanger second at the end of indoor heat exchanger second
Temperature t5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5, according to the indoor heat exchanger of the indoor heat exchanger first end
First end temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7With the fill temperature according to the compressor tonifying Qi entrance
Spend t8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the compressor
Power, the refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2, the indoor heat exchanger second
The refrigerant enthalpy h at end5, the indoor heat exchanger first end refrigerant enthalpy h7, the gaseous refrigerant for filling into compressor
Enthalpy h8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the heating capacity of air conditioner；And consumed according to the air conditioner
Electrical power and the heating capacity generate the efficiency of the air conditioner.
The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner
The power and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet in compressor, in the middle part of indoor heat exchanger,
The temperature and indoor environment temperature of compressor tonifying Qi entrance, and when air conditioner is in heating condition according to above-mentioned each temperature
Test point temperature generation gas returning port, exhaust outlet, the end of indoor heat exchanger second, indoor heat exchanger first end, fill into compressor and
The refrigerant enthalpy of flash vessel, power, above-mentioned refrigerant enthalpy and air conditioner power consumption then in conjunction with compressor obtain sky
The efficiency of device is adjusted, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating the real-time energy efficiency according to air conditioner
Optimize the running status of air conditioner, reach energy-conservation and improve the purpose of heating effect.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add
Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1Generate back
The refrigerant enthalpy h of gas port1Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to described time
Gas port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；According to the suction superheat Δ t1
With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the outdoor heat exchanger
Middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the amendment of the gas returning port refrigerant enthalpy
Factor D1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation row
The enthalpy h of the refrigerant of gas port2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to described
Indoor heat exchanger middle portion temperature t6With the exhaust port temperatures t of exhaust outlet in the compressor2Generate discharge superheat Δ t2；According to
The discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；
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 exhaust
The modifying factor D of mouth refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the exhaust outlet
Refrigerant enthalpy h2。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end
Temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：According to the indoor heat exchanger middle portion temperature t6
With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With the indoor heat exchanger
Middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to the indoor heat exchanger first end
The modifying factor D of refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the indoor heat exchanger
The refrigerant enthalpy h of first end7。
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：
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.
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 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 the efficiency computational methods of the 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, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
Specifically, the current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionercom
With air conditioner power consumption PPower consumption。
S102, obtain the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room
Indoor heat exchanger middle portion temperature t in the middle part of interior heat exchanger6With 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
Put the temperature sensor in the middle part of heat exchanger (as shown in Figure 1 06) indoors and obtain indoor heat exchanger middle portion temperature t6；By setting
The temperature sensor (as shown in Figure 1 08) put in compressor tonifying Qi entrance obtains the tonifying Qi temperature t of compressor tonifying Qi entrance8；
Indoor environment temperature t is obtained by being disposed in the interior the temperature sensor at heat exchanger fin10。
Wherein, except indoor temperature transmitter, refrigerant tube wall of each temperature sensor with corresponding temperature test point
Effectively contact, and to refrigerant tube wall, especially set the position of temperature sensor to take Insulation.For example, can be by temperature
Sensor is close to copper pipe setting, and sealing is wound to copper pipe by being incubated adhesive tape.Can thereby, it is possible to improve temperature detection
By property and accuracy.
S103, according to indoor environment temperature t10With the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Generation is indoor
The indoor heat exchanger first end temperature t of heat exchanger first end7With the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second
t5。
In one embodiment of the invention, indoor heat exchanger the second end temperature t can be generated by below equation5：
t5=a01*t10+b01*t6+c01* f, wherein, f is compressor operating frequency, a01、b01、c01For fitting coefficient, specifically
It can be tested and obtained by many experiments.
In one embodiment of the invention, indoor heat exchanger first end temperature t can be generated by below equation7：
t7=a02*t10+b02*t6+c02* f, wherein, a02、b02、c02For fitting coefficient, can specifically be tested by many experiments
Obtain.
In addition, indoor heat exchanger first end temperature t7With the second end of indoor heat exchanger temperature t5Can also be otherwise
Obtain.For example, in general, during heating, the first end of indoor heat exchanger more connects equivalent to the entrance of heating with delivery temperature
Closely, so indoor heat exchanger first end temperature t can also be obtained using approximately equalised mode7；Meanwhile the of indoor heat exchanger
Two ends are closer to, so can also be obtained using approximately equalised mode equivalent to the outlet of heating with indoor environment temperature
The second end of indoor heat exchanger temperature t5。
S104, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1
Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant of exhaust outlet
Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigeration at the end of indoor heat exchanger second
Agent enthalpy h5, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the system of indoor heat exchanger first end
Cryogen enthalpy h7With the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor8’With
The liquid refrigerant enthalpy h of flash vessel8”。
Specifically, during air conditioner works, because the state of the refrigerant of different temperatures test point is different, therefore
The enthalpy of the refrigerant of different temperatures test point is different.In one embodiment of the invention, rule of thumb formula can calculate
To the enthalpy of refrigerant.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h at the end of indoor heat exchanger second5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous state of compressor
Refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition,
The refrigerant superheat of the gas returning port of compressor, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
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 h1Specifically 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 portion temperature
t3Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to outdoor heat exchanger middle portion temperature t3Generate saturation under suction temperature
The enthalpy h of refrigerantAir-breathing saturation；According to the modifying factor D of gas returning port refrigerant enthalpy1, under suction temperature saturation refrigerant enthalpy
hAir-breathing saturationGenerate the refrigerant enthalpy h of gas returning port1。
Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (1)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 (2)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 (2).Meanwhile 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 (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, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression
The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
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 cryogen2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According in indoor heat exchanger
Portion temperature t6With 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 t6
Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the modifying factor D of exhaust outlet refrigerant enthalpy2, delivery temperature
The enthalpy h of lower saturation refrigerantIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (3)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, can be first according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6It is raw
Into discharge superheat Δ t2=t2-t6, then 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 (3), 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, h2=D2·hIt is vented saturation+d7, wherein, d7To overheat fauna corresponding to refrigerant
Number.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work
During condition, the refrigerant superheat of indoor heat exchanger first end, the position refrigerant superheat degree can be combined and calculate indoor heat exchanger first
The refrigerant enthalpy h at end7。
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 end7Specifically include：According to indoor heat exchanger middle portion temperature t6And indoor heat exchanger
First end temperature t7Generate degree of superheat Δ t7；According to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger
The modifying factor D of first end refrigerant enthalpy7；According to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7, exhaust temperature
The enthalpy h of the lower saturation refrigerant of degreeIt is vented saturationGenerate the refrigerant enthalpy h of indoor heat exchanger first end7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (4)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, 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 (4), 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=D7·hIt is vented saturation+d7, wherein, d7For overheat corresponding to refrigerant
Fauna number.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room
The refrigerant supercooling at the interior end of heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5。
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to following formula (5)
Value h5：
h5=c1+c2t5+c3t2 5+c4t3 5 (5)
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, fill into the gaseous refrigerant enthalpy h of compressor8’It can be calculated according to below equation：
h8’=a1+a2*t8+a3*t8 2+a4*t8 3+a5, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, a1-a5For system
Saturation region coefficient corresponding to cryogen.
The liquid refrigerant enthalpy h of flash vessel8”It can be calculated according to below equation：
h8"=c1+c2*t8+c3*t8 2+c4*t8 3, wherein, t8For the tonifying Qi temperature of compressor tonifying Qi entrance, c1-c4For refrigeration
Supercooling fauna number corresponding to agent.
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 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 mouth1With the refrigerant enthalpy h at the end of indoor heat exchanger second5, and can be according to the high-pressure in air conditioner, row
Gas port temperature t2, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy h of exhaust outlet2With indoor heat exchanger first
The refrigerant enthalpy h at end7, and saturated gas enthalpy h under the state obtained according to tonifying Qi temperature or pressure8’And saturated solution
Body enthalpy h8”。
S105, according to the power of compressor, the refrigerant enthalpy h of gas returning port1, exhaust outlet refrigerant enthalpy h2, it is indoor
The refrigerant enthalpy h at the end of heat exchanger second5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant of compressor
Agent enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner.
Specifically, the heating capacity of air conditioner can be generated according to below equation：
Wherein, QHeating capacityFor the heating of air conditioner
Amount, PcomFor the power of compressor.
S106, 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 power and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet in compressor, in the middle part of indoor heat exchanger,
The temperature and indoor environment temperature of compressor tonifying Qi entrance, and when air conditioner is in heating condition according to above-mentioned each temperature
Test point temperature generation gas returning port, exhaust outlet, the end of indoor heat exchanger second, indoor heat exchanger first end, fill into compressor and
The refrigerant enthalpy of flash vessel, power, above-mentioned refrigerant enthalpy and air conditioner power consumption then in conjunction with compressor obtain sky
The efficiency of device is adjusted, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating the real-time energy efficiency according to air conditioner
Optimize the running status of air conditioner, reach energy-conservation and improve the purpose of heating effect.
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, are followed by obtaining air conditioner refrigerant
The physical property of refrigerant in loop system, and the power of air conditioner is calculated according to the physical property of refrigerant, and enter one
The efficiency of air conditioner is calculated in step, so as to be able to real-time and accurately detect the refrigeration efficiency and heat efficiency of air conditioner.
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 (12)
1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, indoor heat exchange
Indoor heat exchanger middle portion temperature t in the middle part of device6With the tonifying Qi temperature t of compressor tonifying Qi entrance8；
According to indoor environment temperature t10With the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate indoor heat exchange
The indoor heat exchanger first end temperature t of device first end7With the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5；
When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1It is raw
Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet
Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the end of indoor heat exchanger second
Refrigerant enthalpy h5, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchanger
The refrigerant enthalpy h of first end7With the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gaseous state system of compressor
Cryogen enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h at the end of indoor heat exchanger second5, the indoor heat exchanger first end refrigerant enthalpy h7, described fill into
The gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate the heating capacity of air conditioner；With
And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be returned according in the compressor
The gas returning port temperature t of gas port1Generate the refrigerant enthalpy h of gas returning port1Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy
Factor D1；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationIt is raw
Into the refrigerant enthalpy h of the gas returning port1。
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：
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：
<mrow>
<msub>
<mi>D</mi>
<mn>1</mn>
</msub>
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<mi>&Delta;t</mi>
<mn>1</mn>
</msub>
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</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>
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<msub>
<mi>&Delta;t</mi>
<mn>1</mn>
</msub>
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</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>
</mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that described to be arranged according in the compressor
The exhaust port temperatures t of gas port2Generate the enthalpy h of the refrigerant of exhaust outlet2Specifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the indoor heat exchanger middle portion temperature t6With the exhaust port temperatures t of exhaust outlet in the compressor2Generate discharge superheat
Spend 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。
6. the efficiency computational methods of air conditioner as claimed in claim 5, 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>
</mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
7. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that described according to the indoor heat exchanger
The indoor heat exchanger first end temperature t of first end7Generate the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：
According to the indoor heat exchanger middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；
According to the degree of superheat Δ t7With 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。
8. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the room is generated according to below equation
The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
<mrow>
<msub>
<mi>D</mi>
<mn>7</mn>
</msub>
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<mn>1</mn>
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<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>
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<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>
</mrow>
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 calculated according to below equation
The refrigerant enthalpy h at the interior end of heat exchanger second5：
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 equation below
The heating capacity of air conditioner：
Wherein, QHeating capacityFor the air conditioner heat-production
Amount, PcomFor compressor horsepower.
11. 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 1-10
Any described method.
12. 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 1-10 is realized when calculation machine program is executed by processor.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0100210A2 (en) * | 1982-07-26 | 1984-02-08 | Honeywell Inc. | Coefficient of performance measuring device |
| CN103032996A (en) * | 2012-12-12 | 2013-04-10 | 宁波奥克斯电气有限公司 | Parallel compressor selection and configuration method for preventing compressor from being frequently started up and shut down |
| CN105091439A (en) * | 2014-05-07 | 2015-11-25 | 苏州必信空调有限公司 | Computing method of refrigerating capacity and refrigerating efficiency of oil-free refrigerating system and refrigerating system |
| CN106524551A (en) * | 2016-11-07 | 2017-03-22 | 清华大学 | Mass and flow measuring method and device of refrigerant in refrigerating system and measuring instrument |
| CN106949680A (en) * | 2016-01-07 | 2017-07-14 | 青岛海尔开利冷冻设备有限公司 | A kind of refrigeration system compressor group coefficient of performance detection method and detecting system |
-
2017
- 2017-08-31 CN CN201710776059.3A patent/CN107367037A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0100210A2 (en) * | 1982-07-26 | 1984-02-08 | Honeywell Inc. | Coefficient of performance measuring device |
| CN103032996A (en) * | 2012-12-12 | 2013-04-10 | 宁波奥克斯电气有限公司 | Parallel compressor selection and configuration method for preventing compressor from being frequently started up and shut down |
| CN105091439A (en) * | 2014-05-07 | 2015-11-25 | 苏州必信空调有限公司 | Computing method of refrigerating capacity and refrigerating efficiency of oil-free refrigerating system and refrigerating system |
| CN106949680A (en) * | 2016-01-07 | 2017-07-14 | 青岛海尔开利冷冻设备有限公司 | A kind of refrigeration system compressor group coefficient of performance detection method and detecting system |
| CN106524551A (en) * | 2016-11-07 | 2017-03-22 | 清华大学 | Mass and flow measuring method and device of refrigerant in refrigerating system and measuring instrument |
Non-Patent Citations (5)
| Title |
|---|
| （美）辛格（SINGH,R.P.）等著，许学勤译: "《食品工程导论（第三版）》", 31 August 2006, 北京：中国轻工业出版社 * |
| 周光辉等: "制冷剂HCFC-124热力性质计算研究", 《低温与超导》 * |
| 石文星等: "《小型空调热泵装置设计》", 31 October 2013 * |
| 苏晶等: "R410A热力性质的拟合计算", 《制冷与空调》 * |
| 郑兆志等: "《家用空调维修安装技术》", 31 March 2006, 中国科学技术出版社 * |
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