CN107388525A - Air conditioner and its efficiency computational methods - Google Patents
Air conditioner and its efficiency computational methods Download PDFInfo
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Abstract
The invention discloses a kind of air conditioner and its efficiency computational methods, this method to include：Obtain current working, the power and the housing heat dissipation capacity Q of air conditioner power consumption and compressor of compressorloss；Obtain compressor return air mouth temperature t1, exhaust outlet of compressor temperature t2, temperature t in the middle part of indoor heat exchanger6, indoor heat exchanger first end temperature t7, indoor environment temperature t10With compressor tonifying Qi temperature t8；According to t6And t10Generate indoor heat exchanger the second end 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 the power of compressor, Qloss、h1、h2、h5、h7、h8’And h8”Generate heating capacity；According to the efficiency of 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,
A kind of non-transitorycomputer readable storage medium.
Background technology
It is comfortably the problem of user more pays close attention to that whether air conditioner, which saves,.
Current air conditioner is difficult to maintain preferable fortune operationally due to that can not know the situation of change of efficiency
Row state, cooling or heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention
One purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
Fourth object of the present invention is the efficiency computing system for proposing a kind of air conditioner.
To reach above-mentioned purpose, a kind of efficiency computational methods for air conditioner that first aspect present invention embodiment proposes include
Following steps：The current working of air conditioner, the power of compressor and the housing of air conditioner power consumption and compressor is obtained to dissipate
Heat Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, room
Indoor heat exchanger middle portion temperature t in the middle part of interior heat exchanger6, indoor heat exchanger first end indoor heat exchanger first end temperature t7, room
Interior environment temperature t10With the tonifying Qi temperature t of compressor tonifying Qi entrance8；According in the indoor heat exchanger in the middle part of the indoor heat exchanger
Portion temperature t6With the indoor environment temperature t10Generate the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5；Work as institute
When the current working for stating air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1Generate gas returning port
Refrigerant enthalpy h1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the enthalpy h of the refrigerant of exhaust outlet2,
According to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigerant enthalpy at the end of indoor heat exchanger second
h5, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the refrigerant enthalpy of indoor heat exchanger first end
Value h7, according to the tonifying Qi temperature t of compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor respectively8’And flash distillation
The liquid refrigerant enthalpy h of device8”；According to the power of the compressor and the housing heat dissipation capacity Q of compressorloss, the return-air
The refrigerant enthalpy h of mouth1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5, interior changes
The refrigerant enthalpy h of hot device first end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy of flash vessel
h8”Generate the heating capacity of air conditioner；And the energy of the air conditioner is generated according to the air conditioner power consumption and the heating capacity
Effect.
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 the housing heat dissipation capacity Q of compressorloss, and obtain gas returning port in compressor, exhaust
Mouth, indoor heat exchanger middle part and the temperature of indoor heat exchanger first end, the tonifying Qi temperature of compressor tonifying Qi entrance, indoor environment temperature
Spend t10, and examined when air conditioner is in heating condition according to the above-mentioned each temperature of the temperature of above-mentioned each temperature detecting point generation
The refrigerant enthalpy of measuring point, the housing heat dissipation capacity Q of power and compressor then in conjunction with compressorloss, above-mentioned each temperature
The refrigerant enthalpy and air conditioner power consumption of test point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect
The efficiency of air conditioner, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve
The 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 refrigerant enthalpy h of the generation gas returning port1Specifically include：Obtain outdoor
Outdoor heat exchanger middle portion temperature t in the middle part of 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 return-air
The modifying factor D of mouth refrigerant enthalpy1；According to the outdoor heat exchanger middle portion temperature t3Generate saturation refrigerant under suction temperature
Enthalpy hAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy
Value hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equationAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation1：
Wherein, d1-d6For
Overheated zone coefficient corresponding to refrigerant.
Further, the exhaust port temperatures t according to exhaust outlet in the compressor2Generate the refrigeration of the exhaust outlet
Agent enthalpy h2Specifically include：According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Arranged with the compressor
The exhaust port temperatures t of gas port2Generate discharge superheat Δ t2；According to the discharge superheat Δ t2In the indoor heat exchanger
Portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According in the indoor heat exchanger in the middle part of the indoor heat exchanger
Portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According to the modifying factor of the exhaust outlet refrigerant enthalpy
Sub- D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2。
Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation2：
D2=1+d1Δt2+d2(Δt2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein,
d1-d6For overheated zone coefficient corresponding to refrigerant.
Further, the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end7Generate respectively
The refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：According to the indoor heat exchanger in the middle part of the indoor heat exchanger
Middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δ t7With it is described
Indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；Changed according to the interior
The modifying factor D of hot device first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationDescribed in generation
The refrigerant enthalpy h of indoor heat exchanger first end7。
Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation7：
Wherein, d1-d6
For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation
Value h5：
h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：
Wherein, QHeating capacityFor the air conditioner
Heating capacity, PcomFor the power of compressor.
To reach above-mentioned purpose, a kind of air conditioner that second aspect of the present invention embodiment proposes includes memory, processor
And the computer program that can be run on the memory and on the processor is stored in, calculating described in the computing device
During machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected, consequently facilitating according to reality
Shi Nengxiao optimizes to running status, reaches energy-conservation and improves the purpose of refrigeration.
To reach above-mentioned purpose, a kind of non-transitory computer-readable storage medium that third aspect present invention embodiment proposes
Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor
The efficiency computational methods of the air conditioner of proposition.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage
Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner
Running status, reach energy-conservation and improve the purpose of heating effect.
To reach above-mentioned purpose, the efficiency computing system for the air conditioner that fourth aspect present invention embodiment proposes includes：Obtain
Modulus block, for obtaining the current working of air conditioner, the power of compressor and the housing of air conditioner power consumption and compressor
Heat dissipation capacity Qloss；Gas returning port temperature sensor, for obtaining the gas returning port temperature t of gas returning port in compressor1；Exhaust port temperatures pass
Sensor, for obtaining the exhaust port temperatures t of exhaust outlet in the compressor2；Tonifying Qi inlet temperature sensor, compressed for obtaining
The tonifying Qi temperature t of machine tonifying Qi entrance8；Indoor temperature transmitter, for obtaining indoor environment temperature t10；Temperature in the middle part of indoor heat exchanger
Sensor is spent, for obtaining the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger5；Indoor heat exchanger first end temperature passes
Sensor, for obtaining the indoor heat exchanger first end temperature t of indoor heat exchanger first end7；The temperature life of the second end of indoor heat exchanger
Into module, for according to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor environment temperature t10It is raw
Into the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5；Refrigerant enthalpy generation module, for when the air-conditioning
When the current working of device is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1, arrange in the compressor
The exhaust port temperatures t of gas port2, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, indoor heat exchanger first end
Indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8The refrigerant enthalpy of gas returning port is generated respectively
h1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5With the system of indoor heat exchanger first end
Cryogen enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；Heating capacity generates
Module, for the power according to the compressor and the housing heat dissipation capacity Q of compressorloss, the gas returning port refrigerant enthalpy
Value h1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5With indoor heat exchanger first end
Refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate air conditioner
Heating capacity；And efficiency generation module, for generating the air-conditioning according to the air conditioner power consumption and the heating capacity
The efficiency of device.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module
The housing heat dissipation capacity Q of condition, the power of compressor and air conditioner power consumption and compressorloss, and passed by corresponding temperature
Sensor obtains the temperature of gas returning port in compressor, exhaust outlet, indoor heat exchanger middle part and indoor heat exchanger first end, compressor is mended
The tonifying Qi temperature of gas entrance, indoor environment temperature t10, and generated when air conditioner is in heating condition by refrigerant enthalpy
Module, heating capacity generation module and efficiency generation module generate above-mentioned each temperature according to the temperature of above-mentioned each temperature detecting point
The refrigerant enthalpy of test point, the housing heat dissipation capacity Q of power and compressor then in conjunction with compressorloss, above-mentioned each temperature
The refrigerant enthalpy and air conditioner power consumption for spending test point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect
To the efficiency of air conditioner, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and carry
The purpose of high heating effect.
Brief description of the drawings
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention；
Fig. 2 is the structural representation according to the air conditioner of one embodiment of the invention；
Fig. 3 is the block diagram according to the efficiency computing system of the air conditioner of the embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end
Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached
The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
The air conditioner of the embodiment of the present invention and its efficiency computational methods and system described below in conjunction with the accompanying drawings.
Fig. 1 is the flow chart according to the efficiency computational methods of the air conditioner of the embodiment of the present invention.
As shown in figure 1, the efficiency computational methods of the air conditioner of the embodiment of the present invention, comprise the following steps：
S101, obtain the current working of air conditioner, the power of compressor and the shell of air conditioner power consumption and compressor
Body heat dissipation capacity Qloss。
The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditionercomAnd air-conditioning
Device power consumption PPower consumption。
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 of compressor tonifying Qi entrance, t2To be arranged in compressor
The exhaust port temperatures of gas port, can be by setting the temperature sensor of exhaust outlet within the compressor to obtain.
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 exchanger6, indoor heat exchanger first end indoor heat exchanger first end temperature t7, room
Interior environment temperature t10With the tonifying Qi temperature t of compressor tonifying Qi entrance8。
The air conditioner of the embodiment of the present invention can be twin-stage steam compressing air conditioner device, as shown in Fig. 2 the embodiment of the present invention
Air conditioner may include compressor, four-way valve, outdoor heat exchanger, restricting element, flash vessel and indoor heat exchanger.
In one embodiment of the invention, can be by setting temperature sensor to detect respectively in corresponding temperature test point
The temperature of the temperature detecting point.Specifically, as shown in Fig. 2 by within the compressor at gas returning port gas returning port temperature can be set to pass
Sensor is to detect gas returning port temperature t1, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures
t2, indoors indoor heat exchanger middle portion temperature sensor is set to detect indoor heat exchanger middle portion temperature t in the middle part of heat exchanger6And
Indoor heat exchanger first end temperature sensor is set to detect indoor heat exchanger first end temperature at heat exchanger first end indoors
t7, in compressor tonifying Qi porch tonifying Qi inlet temperature sensor is set to detect the tonifying Qi temperature t of compressor tonifying Qi entrance8, with
And at heat exchanger fin indoor temperature transmitter is set to detect indoor environment temperature t indoors10。
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, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With indoor environment temperature t10Generation is indoor
The second end of indoor heat exchanger temperature t at the end of heat exchanger second5。
In one embodiment of the invention, indoor heat exchanger the second end temperature t can be generated by below equation5：
t5=a*t10+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
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 h7, according to the tonifying Qi temperature t of compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy h of compressor respectively8’
With the liquid refrigerant enthalpy h of flash vessel8”。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room
Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, is in the middle part of condenser in the middle part of indoor heat exchanger.
Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point
It is different.In one embodiment of the invention, rule of thumb the enthalpy of refrigerant can be calculated by formula.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2、
The refrigerant enthalpy h at the end of indoor heat exchanger second5With the refrigerant enthalpy h of indoor heat exchanger first end7Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, compression
The refrigerant superheat of the gas returning port of machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained3, wherein, as shown in Fig. 2 outdoor
Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger3Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through
Degree sensor detects to obtain.
Then can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1, and according to
Suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1, and according to
Outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Wherein, suction superheat Δ t1For
Gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.The modifying factor of gas returning port refrigerant enthalpyWherein, d1-d6For refrigerant pair
The overheated zone coefficient answered.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+a3t2 3+a4t3 3+a5, wherein, a1-a5
For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, can further root
According to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1, h1=D1·
hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression
The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
Specifically, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Generation row
Gas degree of superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Saturation under delivery temperature is generated to freeze
The enthalpy h of agentIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigerant enthalpy
Modifying factor D2.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle part
Temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5,
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δ
t2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone corresponding to refrigerant
Coefficient.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, can further repairing according to exhaust outlet refrigerant enthalpy
Positive divisor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation
+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work
During condition, the refrigerant superheat of indoor heat exchanger first end, the refrigeration that discharge superheat calculates indoor heat exchanger first end can be combined
Agent enthalpy h7。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ
t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the amendment of indoor heat exchanger first end refrigerant enthalpy
Factor D7, and the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy according to generation7With the enthalpy of saturation refrigerant
hIt is vented saturationGenerate refrigerant enthalpy h7.Wherein, Δ t7=t7-t6,
h7=D7·hIt is vented saturation+
d7, wherein, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room
The refrigerant supercooling at the interior end of heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5：h5=c1+c2t5
+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant
Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone
Coefficient.
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.
Also, 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.
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.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach
The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is heating condition
Adjust high-pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port
h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room
Interior the second end of heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy at the end of indoor heat exchanger second
h5, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure8’And saturated liquid enthalpy h8”。
S105, according to the power of compressor and the housing heat dissipation capacity Q of compressorloss, gas returning port refrigerant enthalpy h1、
The refrigerant enthalpy h of exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy
Value h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating of air conditioner
Amount.
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 the housing heat dissipation capacity Q of compressorloss, and obtain gas returning port in compressor, exhaust
Temperature, tonifying Qi temperature, the indoor environment of compressor tonifying Qi entrance of mouth, the end of indoor heat exchanger second and indoor heat exchanger first end
Temperature t10, and above-mentioned each temperature is generated according to the temperature of above-mentioned each temperature detecting point when air conditioner is in heating condition
The refrigerant enthalpy of test point, the housing heat dissipation capacity Q of power and compressor then in conjunction with compressorloss, above-mentioned each temperature
The refrigerant enthalpy and air conditioner power consumption for spending test point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect
To the efficiency of air conditioner, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and carry
The purpose of high 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.
Corresponding above-described embodiment, the present invention also propose a kind of efficiency computing system of air conditioner.
As shown in figure 3, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port temperature sensor 01,
Exhaust port temperatures sensor 02, indoor heat exchanger middle portion temperature sensor 06, indoor heat exchanger first end temperature sensor 07, benefit
Gas inlet temperature sensor 08, indoor temperature transmitter 11 and the second end of indoor heat exchanger temperature generation module 30, obtain mould
Block 10, refrigerant enthalpy generation module 20, heating capacity generation module 50, efficiency generation module 40.
Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor1；Exhaust outlet temperature
Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor2；Tonifying Qi inlet temperature sensor 08, which is used to obtain, presses
The tonifying Qi temperature t of contracting machine tonifying Qi entrance8；Indoor temperature transmitter 11 is used to obtain indoor environment temperature t10；In indoor heat exchanger
Portion's temperature sensor 06 is used to obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；Indoor heat exchanger first end temperature
Degree sensor 07 is used for the indoor heat exchanger first end temperature t for obtaining indoor heat exchanger first end7。
The air conditioner of the embodiment of the present invention can be twin-stage steam compressing air conditioner device, as shown in Fig. 2 the embodiment of the present invention
Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element such as choke valve 400 and choke valve
600th, flash vessel 700 and indoor heat exchanger 500.
As shown in Fig. 2 gas returning port temperature sensor 01 can be set within the compressor at gas returning port, exhaust port temperatures sensor
02 settable exhaust ports, outdoor heat exchanger first end temperature sensor 04 may be provided at outdoor heat exchanger first within the compressor
End, indoor heat exchanger middle portion temperature sensor 06 may be provided in the middle part of indoor heat exchanger, indoor heat exchanger first end TEMP
Device 07 may be provided at indoor heat exchanger first end, and tonifying Qi inlet temperature sensor 08 is arranged on compressor tonifying Qi porch.Wherein,
Each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, and to refrigerant tube wall, especially sets
Take Insulation in the position for putting temperature sensor.For example, temperature sensor can be close to copper pipe setting, and by being incubated adhesive tape
Sealing is wound to copper pipe.Thereby, it is possible to improve the reliability and accuracy of temperature detection.Also, can heat exchanger indoors
Indoor temperature transmitter is set to detect indoor environment temperature t at fin10。
Acquisition module 10 is used to obtain the current working of air conditioner, the power of compressor and air conditioner power consumption and pressure
The housing heat dissipation capacity Q of contracting machineloss；The room that the second end of indoor heat exchanger temperature generation module 30 is used in the middle part of indoor heat exchanger
Interior heat exchanger middle portion temperature t6With indoor environment temperature t10Generate the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second
t5；Refrigerant enthalpy generation module 20 is used for when the current working of air conditioner is heating condition, according to gas returning port in compressor
Gas returning port temperature t1, in compressor exhaust outlet exhaust port temperatures t2, the end of indoor heat exchanger second the end of indoor heat exchanger second
Temperature t5, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8Point
Not Sheng Cheng gas returning port refrigerant enthalpy h1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5
With the refrigerant enthalpy h of indoor heat exchanger first end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid system of flash vessel
Cryogen enthalpy h8”；Heating capacity generation module 50 is used for according to the power of compressor and the housing heat dissipation capacity Q of compressorloss, return
The refrigerant enthalpy h of gas port1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5, interior changes
The refrigerant enthalpy h of hot device first end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy of flash vessel
h8”Generate the heating capacity of air conditioner；Efficiency generation module 40 is used to generate air conditioner according to air conditioner power consumption and heating capacity
Efficiency.
Wherein, acquisition module 10, refrigerant enthalpy generation module 20, the second end of indoor heat exchanger temperature generation module 30,
Heating capacity generation module 50 and efficiency generation module 40 may be disposed in the electric-control system of air conditioner.Acquisition module 10 can supervise in real time
Survey current working, the power P of compressor of air conditionerCompressorWith air conditioner power consumption PPower consumption。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room
Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, is in the middle part of condenser in the middle part of indoor heat exchanger.
In one embodiment of the invention, the second end of indoor heat exchanger temperature generation module 30 can be given birth to by below equation
Into the second end of indoor heat exchanger temperature t5：
t5=a*t10+b*t6+ c*f, wherein, f is compressor operating frequency, and a, b, c are fitting coefficient.
Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point
It is different.In one embodiment of the invention, rule of thumb refrigerant can be calculated by formula in refrigerant enthalpy generation module 20
Enthalpy.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below1、
The refrigerant enthalpy h of exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5With the refrigerant of indoor heat exchanger first end
Enthalpy h7Detailed process.
For the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, compression
The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port
Enthalpy h1。
Specifically, refrigerant enthalpy generation module 20 can obtain the outdoor heat exchanger middle portion temperature in the middle part of outdoor heat exchanger
t3, wherein, as shown in Fig. 2 the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3Can be by being set in the middle part of outdoor heat exchanger
The outdoor heat exchanger middle portion temperature sensor put detects to obtain.
Then refrigerant enthalpy generation module 20 can be according to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generation is inhaled
Gas degree of superheat Δ t1, and according to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate gas returning port refrigerant enthalpy
Modifying factor D1, and according to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation.Its
In, suction superheat Δ t1For gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Difference, i.e. Δ t1=t1-t3.Gas returning port
The modifying factor of refrigerant enthalpy
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation=a1+a2t3+
a3t2 3+a4t3 3+a5, wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
In the modifying factor D of generation gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationAfterwards, refrigerant enthalpy
Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGeneration
Refrigerant enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression
The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet
Enthalpy h2。
Specifically, can be according to the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle portion temperature t6Generation row
Gas degree of superheat Δ t2, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6Saturation under delivery temperature is generated to freeze
The enthalpy h of agentIt is vented saturation, and according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigerant enthalpy
Modifying factor D2.Wherein, discharge superheat Δ t2For the exhaust port temperatures t of exhaust outlet in compressor2With indoor heat exchanger middle part
Temperature t6Difference, i.e. Δ t2=t2-t6.The enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation=a1+a2t6+a3t2 6+a4t3 6+a5,
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.The modifying factor D of exhaust outlet refrigerant enthalpy2=1+d1Δt2+d2(Δ
t2)2+d3(Δt2)t6+d4(Δt2)2t6+d5(Δt2)t2 6+d6(Δt2)2t2 6, wherein, d1-d6For overheated zone corresponding to refrigerant
Coefficient.
In the modifying factor D of generation exhaust outlet refrigerant enthalpy2Afterwards, can further repairing according to exhaust outlet refrigerant enthalpy
Positive divisor D2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation
+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work
During condition, the refrigerant superheat of indoor heat exchanger first end, the refrigeration that discharge superheat calculates indoor heat exchanger first end can be combined
Agent enthalpy h7。
Specifically, can be according to indoor heat exchanger first end temperature t7With indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ
t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate the amendment of indoor heat exchanger first end refrigerant enthalpy
Factor D7, and the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy according to generation7With the enthalpy of saturation refrigerant
hIt is vented saturationGenerate refrigerant enthalpy h7.Wherein, Δ t7=t7-t6,
h7=D7·hIt is vented saturation+
d7, wherein, wherein, d1-d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room
The refrigerant supercooling at the interior end of heat exchanger second, refrigerant enthalpy generation module 20 can directly calculate the system at the end of indoor heat exchanger second
Cryogen enthalpy h5：h5=c1+c2t5+c3t2 5+c4t3 5, wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
Saturation region coefficient, overheated zone coefficient and the species of supercooling fauna number and refrigerant have corresponding to above-mentioned refrigerant
Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and crosses cold-zone
Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection
The refrigerant enthalpy of point.
Also, 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.
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.
In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software
Fruit, or the refrigerant enthalpy by each temperature detecting point of other approach acquisition.For example, when the current working of air conditioner is
During heating condition, refrigerant enthalpy generation module 20 can also be according to the high-pressure in air conditioner, gas returning port temperature t1, interior changes
Hot device first end temperature t7Respectively obtain the refrigerant enthalpy h of gas returning port1With the refrigerant enthalpy h of indoor heat exchanger first end7,
And can be according to the high-pressure in air conditioner, exhaust port temperatures t2, the second end of indoor heat exchanger temperature t5Respectively obtain exhaust outlet
Refrigerant enthalpy h2With the refrigerant enthalpy h at the end of indoor heat exchanger second5, and can be obtained according to tonifying Qi temperature or pressure
Saturated gas enthalpy h under the state8’And saturated liquid enthalpy h8”。
In an embodiment of the present invention, heating capacity generation module 50 can generate the heating capacity of air conditioner according to below equation：Wherein, QHeating capacityFor the heating capacity of air conditioner, Pcom
For the power of compressor.
Because the current working of air conditioner is heating condition, thus efficiency generation module 40 can be according to air conditioner power consumption
With the heat efficiency of heating capacity generation air conditioner, specifically, the heat efficiency of air conditioner is the heating capacity and power consumption work(of air conditioner
The ratio between rate, i.e. COP=QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner
State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner
Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module
The housing heat dissipation capacity Q of condition, the power of compressor and air conditioner power consumption and compressorloss, and passed by corresponding temperature
Sensor obtains the temperature of gas returning port in compressor, exhaust outlet, indoor heat exchanger middle part and indoor heat exchanger first end, compressor is mended
The tonifying Qi temperature of gas entrance, indoor environment temperature t10, and generated when air conditioner is in heating condition by refrigerant enthalpy
Module, heating capacity generation module and efficiency generation module generate above-mentioned each temperature according to the temperature of above-mentioned each temperature detecting point
The refrigerant enthalpy of test point, the housing heat dissipation capacity Q of power and compressor then in conjunction with compressorloss, above-mentioned each temperature
The refrigerant enthalpy and air conditioner power consumption for spending test point obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect
To the efficiency of air conditioner, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and carry
The purpose of high 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 (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 the housing heat dissipation capacity of air conditioner power consumption and compressor of compressor of air conditioner
Qloss；
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 device6, indoor heat exchanger first end indoor heat exchanger first end temperature t7, indoor environment
Temperature t10With the tonifying Qi temperature t of compressor tonifying Qi entrance8；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor environment temperature t10Generation is indoor
The second end of indoor heat exchanger temperature t at the end of 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 system at the end of indoor heat exchanger second
Cryogen enthalpy h5, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate indoor heat exchanger first end
Refrigerant enthalpy h7, according to the tonifying Qi temperature t of compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor respectively
h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor and the housing heat dissipation capacity Q of compressorloss, the gas returning port refrigerant enthalpy h1, row
The enthalpy h of the refrigerant of gas port2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy
Value h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8" generation air conditioner heating
Amount；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 the refrigerant of the generation gas returning port
Enthalpy h1Specifically 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：
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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 the exhaust outlet2Specifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor
Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy
Factor D2；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6Generate the enthalpy of saturation refrigerant under delivery temperature
hIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw
Into the refrigerant enthalpy h of the exhaust outlet2。
6. the efficiency computational methods of the air conditioner described in claim 5, it is characterised in that the exhaust is generated according to below equation
The modifying factor D of mouth refrigerant enthalpy2：
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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 the indoor heat exchanger first end7Specifically include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor heat exchanger first end temperature t7It is raw
Into degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy
Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation refrigerant under the delivery temperature
Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the indoor heat exchanger first end7。
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：
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</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>
</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 system of the air conditioner
Heat, PcomFor the power of compressor.
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 (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104848504A (en) * | 2015-03-20 | 2015-08-19 | 江苏盈方智能科技有限公司 | Date computer room precise air-conditioning energy-saving system based on enthalpy value intelligent temperature control optimization algorithm and operating method thereof |
| 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 |
| CN106524548A (en) * | 2016-11-07 | 2017-03-22 | 清华大学 | Refrigerant mass and flow measuring method and device and measuring instrument |
| CN106595004A (en) * | 2017-02-04 | 2017-04-26 | 青岛海尔空调器有限总公司 | Control method and control device for air conditioner, and air conditioner |
-
2017
- 2017-08-31 CN CN201710776021.6A patent/CN107388525A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN104848504A (en) * | 2015-03-20 | 2015-08-19 | 江苏盈方智能科技有限公司 | Date computer room precise air-conditioning energy-saving system based on enthalpy value intelligent temperature control optimization algorithm and operating method thereof |
| CN106524548A (en) * | 2016-11-07 | 2017-03-22 | 清华大学 | Refrigerant mass and flow measuring method and device and measuring instrument |
| CN106595004A (en) * | 2017-02-04 | 2017-04-26 | 青岛海尔空调器有限总公司 | Control method and control device for air conditioner, and air conditioner |
Non-Patent Citations (4)
| Title |
|---|
| （美）辛格（SINGH,R.P.）: "《食品工程导论（第三版）》", 31 August 2006 * |
| 周光辉: "制冷剂HCFC-124热力性质计算研究", 《低温与超导》 * |
| 石文星: "《小型空调热泵装置设计》", 30 October 2013, 中国建筑工业出版社 * |
| 郑兆志: "《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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