CN107514772A

CN107514772A - Air conditioner and its efficiency computational methods

Info

Publication number: CN107514772A
Application number: CN201710774349.4A
Authority: CN
Inventors: 杨亚新; 张�浩; 戚文端; 陈新; 刘燕飞; 汪亚涛
Original assignee: Guangdong Midea Refrigeration Equipment Co Ltd
Current assignee: GD Midea Air Conditioning Equipment Co Ltd
Priority date: 2017-08-31
Filing date: 2017-08-31
Publication date: 2017-12-26

Abstract

The invention discloses a kind of air conditioner and its efficiency computational methods, the described method comprises the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain the gas returning port temperature t of gas returning port in compressor₁, in compressor exhaust outlet exhaust port temperatures t₂, outdoor heat exchanger first end temperature t₄, indoor heat exchanger first end temperature t₇With the tonifying Qi temperature t of compressor₈；When the current working of air conditioner is cooling condition, according to t₁、t₂、t₄、t₇And t₈The refrigerant enthalpy and lubricating oil enthalpy of above-mentioned each temperature detecting point are generated respectively；The mixture enthalpy h of above-mentioned each temperature detecting point is generated according to the refrigerant enthalpy of above-mentioned each temperature detecting point and lubricating oil enthalpy₁、h₂、h₄、h₇、h_8’And h_8”；According to the power of compressor, h₁、h₂、h₄、h₇、h_8’And h_8”Generate the refrigerating capacity of air conditioner；And the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Description

Air conditioner and its efficiency computational methods

Technical field

The present invention relates to air conditioner technical field, the efficiency computational methods of more particularly to a kind of air conditioner, a kind of air conditioner With a kind of non-transitorycomputer readable storage medium.

Background technology

As country increasingly payes attention to energy-conservation, consumer comfortably requires also more and more higher to the energy-conservation of air conditioner.Mesh Before, during air conditioner is run, due to that can not detect the situation of change of energy efficiency of air conditioner in real time, thus air conditioner is difficult to tie up Hold in preferable running status, so that refrigeration, heating effect and energy-efficient performance are not ideal enough.

The content of the invention

It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.

Therefore, first purpose of the present invention is the efficiency computational methods for proposing a kind of air conditioner, can be accurate in real time Ground detects the efficiency of air conditioner.

Second object of the present invention is to propose a kind of air conditioner.

Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.

Fourth object of the present invention is the efficiency computational methods for proposing another air conditioner.

The 5th purpose of the present invention is to propose another air conditioner.

The 6th purpose of the present invention is to propose another non-transitorycomputer readable storage medium.

To reach above-mentioned purpose, first aspect present invention embodiment proposes a kind of efficiency computational methods of air conditioner, bag Include following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain return-air in compressor The gas returning port temperature t of mouth₁, in the compressor exhaust outlet exhaust port temperatures t₂, outdoor heat exchanger first end outdoor heat exchanger First end temperature t₄, indoor heat exchanger first end indoor heat exchanger first end temperature t₇With the fill temperature of compressor tonifying Qi entrance Spend t₈, wherein, the gas returning port temperature t₁According to the indoor heat exchanger first end temperature t₇Given birth to the running frequency f of compressor Into；When the current working of the air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in the compressor₁It is raw Into the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the exhaust port temperatures of exhaust outlet in the compressor t₂Generate the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the outdoor of the outdoor heat exchanger first end Heat exchanger first end temperature t₄Generate the refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}With lubricating oil enthalpy h_{4 lubricating oil}, according to The indoor heat exchanger first end temperature t of the indoor heat exchanger first end₇Generate the refrigerant enthalpy of indoor heat exchanger first end t_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}, and the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into compression respectively The gaseous refrigerant enthalpy h of machine_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}And lubricating oil Enthalpy h_{8 " lubricating oil}；According to the refrigerant enthalpy h of the gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}Generate the mixture of gas returning port Enthalpy h₁, according to the refrigerant enthalpy h of the exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy of exhaust outlet h₂, according to the refrigerant enthalpy h of the outdoor heat exchanger first end_{4 refrigerants}With lubricating oil enthalpy h_{4 lubricating oil}Generate outdoor heat exchanger the The mixture enthalpy h of one end₄, according to the refrigerant enthalpy t of the indoor heat exchanger first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil} Generate the mixture enthalpy h of indoor heat exchanger first end₇, according to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' refrigerants}With Lubricating oil enthalpy h_{8 ' lubricating oil}Generation fills into compressor mixture enthalpy h_8’, and the liquid refrigerant enthalpy according to the flash vessel h_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}Generate the mixture enthalpy h of flash vessel_8”；According to the power of the compressor, the return-air The mixture enthalpy h of mouth₁, the exhaust outlet mixture enthalpy h₂, the outdoor heat exchanger first end mixture enthalpy h₄、 The mixture enthalpy h of the indoor heat exchanger first end₇, described fill into compressor mixture enthalpy h_8’With mixing for the flash vessel Compound enthalpy h_8”Generate the refrigerating capacity of air conditioner；And the sky is generated according to the air conditioner power consumption and the refrigerating capacity Adjust the efficiency of device.

The efficiency computational methods of air conditioner according to embodiments of the present invention, current working, the compression of air conditioner are obtained first The power and air conditioner power consumption of machine, and obtain the row of exhaust outlet in the gas returning port temperature of gas returning port in compressor, compressor Gas port temperature, the outdoor heat exchanger first end temperature of outdoor heat exchanger first end, the indoor heat exchanger of indoor heat exchanger first end The tonifying Qi temperature of first end temperature and compressor tonifying Qi entrance, when the current working of air conditioner is cooling condition, according to above-mentioned The temperature of each temperature detecting point generates the refrigerant enthalpy and lubricating oil enthalpy of above-mentioned each temperature detecting point, and further gives birth to Into the mixture enthalpy of each temperature detecting point, power, the mixture of above-mentioned each temperature detecting point then in conjunction with compressor Enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, from And it is easy to optimize according to the real-time energy efficiency of air conditioner the running status of air conditioner, reach energy-conservation and improve the purpose of refrigeration.

In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：

According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor₁Generation institute State the refrigerant enthalpy h of gas returning port_{1 refrigerant}Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆；Root According to the gas returning port temperature t₁With the indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁；Changed according to the interior Hot device middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}；According to the suction superheat Δ t₁And interior Heat exchanger middle portion temperature t₆Generate the modifying factor D of gas returning port refrigerant enthalpy₁；According to repairing for the gas returning port refrigerant enthalpy Positive divisor D₁, the saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy h_{1 refrigerant}。

According to one embodiment of present invention, the enthalpy of saturation refrigerant under the suction temperature is generated according to below equation h_{Air-breathing saturation}：

Wherein, a₁-a₅For saturation region coefficient corresponding to refrigerant.

According to one embodiment of present invention, the modifying factor of the gas returning port refrigerant enthalpy is generated according to below equation D₁：

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 the indoor heat exchanger first end_{7 refrigerants}Specifically include：According to the indoor heat exchanger first Hold temperature t₇With the indoor heat exchanger middle portion temperature t₆Generate degree of superheat Δ t₇；According to the degree of superheat Δ t₇With the interior Heat exchanger middle portion temperature t₆Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇；According to the indoor heat exchanger The modifying factor D of first end refrigerant enthalpy₇With the enthalpy h of the saturation refrigerant_{Air-breathing saturation}Generate the refrigerant enthalpy h_{7 refrigerants}。

According to one embodiment of present invention, the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation Modifying factor D₇：

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 institute State the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃； According to the outdoor heat exchanger middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}；According to the compression The exhaust port temperatures t of exhaust outlet in machine₂With the outdoor heat exchanger middle portion temperature t₃Generate discharge superheat Δ t₂；According to described Discharge superheat Δ t₂With the outdoor heat exchanger middle portion temperature t₃Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂；According to The modifying factor D₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the enthalpy of the refrigerant of the exhaust outlet Value h_{2 refrigeration}Agent.

According to one embodiment of present invention, the modifying factor of the exhaust outlet refrigerant enthalpy is generated according to below equation D₂：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation Value h_{4 refrigerants}：

Wherein, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

According to one embodiment of present invention, the refrigerating capacity of the air conditioner is generated according to below equation：

Wherein, Q_{Refrigerating capacity}For the Air conditioner refrigerating capacity, P_CompressorFor compressor horsepower.

According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to below equation h_{I lubricating oil}, wherein, i is positive integer,

h_{I, lubricating oil}=-0.0808+1.7032t_i+0.0025t_i ²

Wherein, t_iFor the temperature of temperature detecting point.

According to one embodiment of present invention, the mixture enthalpy h of each point is calculated according to below equation_i, wherein, i is Positive integer,

h_i=(1-C_g)h_{I, refrigerant}+C_gh_{I, lubricating oil},

C_g=f/10⁴,

Wherein, Cg is oil content, and f is the running frequency of the compressor.

To reach above-mentioned purpose, second aspect of the present invention embodiment proposes a kind of air conditioner, and it includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, meter described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.

Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.

To reach above-mentioned purpose, third aspect present invention embodiment proposes a kind of non-transitory computer-readable storage medium Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor The efficiency computational methods of the air conditioner of proposition.

Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.

To reach above-mentioned purpose, fourth aspect present invention embodiment proposes the efficiency computational methods of another air conditioner, Comprise the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain in compressor and return The gas returning port temperature t of gas port₁, in the compressor exhaust outlet exhaust port temperatures t₂, outdoor heat exchanger in the middle part of outdoor heat exchanger Middle portion temperature t₃, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t₅, indoor heat exchanger first end indoor heat exchange Device first end temperature t₇With the tonifying Qi temperature t of compressor tonifying Qi entrance₈, wherein, the gas returning port temperature t₁Changed according to the outdoor Hot device middle portion temperature t₃Generated with the running frequency f of compressor；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 compressor₁Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, According to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second₅Generate the system at the end of indoor heat exchanger second Cryogen enthalpy h_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end t₇Generate the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}, and according to compressor benefit The tonifying Qi temperature t of gas entrance₈Generation fills into the gaseous refrigerant enthalpy h of compressor respectively_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, dodge The liquid refrigerant enthalpy h of steaming device_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}；According to the refrigerant enthalpy h of the gas returning port_{1 refrigerant}With Lubricating oil enthalpy h_{1 lubricating oil}Generate the mixture enthalpy h of gas returning port₁, according to the enthalpy h of the refrigerant of the exhaust outlet_{2 refrigerants}And profit Lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy h of exhaust outlet₂, according to the refrigerant enthalpy at the end of indoor heat exchanger second h_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}Generate the mixture enthalpy h at the end of indoor heat exchanger second₅, according to the indoor heat exchanger The refrigerant enthalpy h of first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}Generate the mixture enthalpy h of indoor heat exchanger first end₇, root According to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' chiller refrigeration agent}With lubricating oil enthalpy h_{8 ' lubricating oil}Generation fills into compressor mixing Thing enthalpy h_8’, and the liquid refrigerant enthalpy h according to the flash vessel_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}Generate flash vessel Mixture enthalpy h_8”；According to the power of the compressor, the mixture enthalpy h of the gas returning port₁, the exhaust outlet mixing Thing enthalpy h₂, the end of indoor heat exchanger second mixture enthalpy h₅, the indoor heat exchanger first end mixture enthalpy h₇, described fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of the flash vessel_8”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.

The efficiency computational methods of air conditioner according to embodiments of the present invention, current working, the compression of air conditioner are obtained first The power and air conditioner power consumption of machine, and obtain the row of exhaust outlet in the gas returning port temperature of gas returning port in compressor, compressor Gas port temperature, the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second, the indoor heat exchanger of indoor heat exchanger first end The tonifying Qi temperature of first end temperature and compressor tonifying Qi entrance, and when the current working of air conditioner is heating condition, according to The temperature of above-mentioned each temperature detecting point generates the refrigerant enthalpy and lubricating oil enthalpy of above-mentioned each temperature detecting point, goes forward side by side one Step generates the mixture enthalpy of each temperature detecting point, and the power, above-mentioned each temperature detecting point then in conjunction with compressor mix Compound enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect the energy of air conditioner Effect, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve heating effect Purpose.

According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor₁Generation institute State the refrigerant enthalpy h of gas returning port_{1 refrigerant}Specifically include：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 h_{Air-breathing saturation}；According to the modifying factor D of the gas returning port refrigerant enthalpy₁, under the suction temperature saturation refrigerant enthalpy Value h_{Air-breathing saturation}Generate the refrigerant enthalpy h of the gas returning port_{1 refrigerant}。

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 institute State the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆； According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆With the exhaust port temperatures t of exhaust outlet in the compressor₂ Generate discharge superheat Δ t₂；According to the discharge superheat Δ t₂With the indoor heat exchanger middle portion temperature t₆Generate exhaust outlet The modifying factor D of refrigerant enthalpy₂；According to the outdoor heat exchanger middle portion temperature t₆Generate saturation refrigerant under delivery temperature Enthalpy h_{It is vented saturation}；According to the modifying factor D of the exhaust outlet refrigerant enthalpy₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigerant enthalpy h of the exhaust outlet_{2 refrigerants}。

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 the indoor heat exchanger first end_{7 refrigerants}Specifically include：In the middle part of the indoor heat exchanger Indoor heat exchanger middle portion temperature t₆With the indoor heat exchanger first end temperature t₇Generate degree of superheat Δ t₇；According to the overheat Spend Δ t₇With the indoor heat exchanger middle portion temperature t₆Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇；Root According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy₇, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigerant enthalpy h_{7 refrigerants}。

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 h_{5 refrigerants}：

Wherein, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：

Wherein, Q_{Heating capacity}For the heating capacity of air conditioner, P_CompressorFor compressor horsepower.

h_{I, lubricating oil}=-0.0808+1.7032t_i+0.0025t_i ²,

Wherein, t_iFor the temperature of temperature detecting point.

h_i=(1-C_g)h_{I, refrigerant}+C_gh_{I, lubricating oil},

C_g=f/10⁴,

Wherein, Cg is oil content, and f is the running frequency of the compressor.

To reach above-mentioned purpose, fifth aspect present invention embodiment proposes another air conditioner, and it includes memory, place Manage device and be stored in the computer program that can be run on the memory and on the processor, described in the computing device During computer program, the efficiency computational methods for the air conditioner that fifth aspect present invention embodiment proposes are realized.

To reach above-mentioned purpose, sixth aspect present invention embodiment proposes the computer-readable storage of another non-transitory Medium, is stored thereon with computer program, and the computer program realizes that fifth aspect present invention is implemented when being executed by processor The efficiency computational methods for the air conditioner that example proposes.

Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.

Brief description of the drawings

Fig. 1 is the structural representation of air conditioner according to an embodiment of the invention；

Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention；And

Fig. 3 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention.

Embodiment

Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.

Efficiency computational methods, air conditioner, the non-transitory of the air conditioner of the embodiment of the present invention described below in conjunction with the accompanying drawings The efficiency computing system of computer-readable recording medium and air conditioner.

In an embodiment of the present invention, air conditioner can be single-stage vapor compression formula air conditioner.

As shown in figure 1, the air conditioner of the embodiment of the present invention, it may include compressor 100, four-way valve 200, outdoor heat exchanger 300th, first throttle element 400, the second restricting element 700, flash vessel 600 and indoor heat exchanger 500.

When the current working of air conditioner is cooling condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A2 ends are directly connected with outdoor heat exchanger 300, and refrigerant is flowed to as shown in the solid arrow in Fig. 1.Specifically, from compressor 100 Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A2 ends flow into outdoor heat exchanger 300 (now As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after outdoor heat exchanger 300 condenses heat release Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of second restricting element 700, low-temp low-pressure liquid refrigerants passes through flash vessel 600 First port flows into flash vessel 600, and a part of liquid refrigerants quickly becomes gaseous coolant in flash vessel 600, and from flash vessel 600 second port enters compressor 100 and carries out tonifying Qi to compressor 100, so as to improve air conditioner operating efficiency, remaining liquid State refrigerant flows out from the 3rd port of flash vessel 600, and is getting in heat exchange after the reducing pressure by regulating flow of first throttle element 400 Device 500 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gas after the evaporation endothermic of indoor heat exchanger 500 A4 end of the state refrigerant through four-way valve 200 and A3 ends flow into the gas returning port of compressor 100, pass through the low of the gas returning port of compressor 100 Warm low-pressure gaseous refrigerant enters compressor 100, so far completes refrigerative circle system.

When the current working of air conditioner is heating condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A4 ends are directly connected with indoor heat exchanger 500, and refrigerant is flowed to as shown in the dotted arrow in Fig. 1.Specifically, from compressor 100 Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A4 ends flow into indoor heat exchanger 500 (now As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after indoor heat exchanger 500 condenses heat release Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of first throttle element 400, low-temp low-pressure liquid refrigerants passes through flash vessel 600 3rd port flows into flash vessel 600, and a part of liquid refrigerants quickly becomes gaseous coolant in flash vessel 600, and from flash vessel 600 second port enters compressor 100 and carries out tonifying Qi to compressor 100, so as to improve air conditioner operating efficiency, remaining liquid State refrigerant flows out from the first port of flash vessel 600, and is entering outdoor heat exchange after the reducing pressure by regulating flow of the second restricting element 700 Device 300 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gas after the evaporation endothermic of outdoor heat exchanger 300 A2 end of the state refrigerant through four-way valve 200 and A3 ends flow into the gas returning port of compressor 100, pass through the low of the gas returning port of compressor 100 Warm low-pressure gaseous refrigerant enters compressor 100, so far completes heating cyclic process.

Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention.As shown in Fig. 2 this The efficiency computational methods of the air conditioner of inventive embodiments, it may include following steps：

S101, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.

Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner P_CompressorWith air conditioner power consumption P_{Power consumption}。

S102, obtain the gas returning port temperature t of gas returning port in compressor₁, in compressor exhaust outlet exhaust port temperatures t₂, room The outdoor heat exchanger first end temperature t of external heat exchanger first end₄, indoor heat exchanger first end indoor heat exchanger first end temperature t₇With the tonifying Qi temperature t of compressor tonifying Qi entrance₈, wherein, gas returning port temperature t₁According to indoor heat exchanger first end temperature t₇And pressure The running frequency f generations of contracting machine.

In an embodiment of the present invention, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature Spend the temperature of test point.

Specifically, as shown in figure 1, can be by setting the temperature sensor of exhaust outlet within the compressor (as shown in Figure 1 02) exhaust port temperatures t is obtained₂；Obtained by the temperature sensor (as shown in Figure 1 04) for being disposed in the outdoor heat exchanger first end Outdoor heat exchanger first end temperature t₄；By the temperature sensor (as shown in Figure 1 07) for being disposed in the interior heat exchanger first end Obtain indoor heat exchanger first end temperature t₇；It is (as shown in Figure 1 by the temperature sensor for being arranged on compressor tonifying Qi entrance 08) the tonifying Qi temperature t of compressor tonifying Qi entrance is obtained₈.Then can be according to outdoor heat exchanger middle portion temperature t₃With the operation of compressor Frequency f generation gas returning port temperature t₁。

Wherein, above-mentioned each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, is testing During the temperature of refrigerant tube wall, refrigerant tube wall can take Insulation, and the installation site of temperature sensor is as close to temperature Spend test point.For example, temperature sensor can be arranged on to corresponding temperature detecting point and be close to copper pipe, and by being incubated glue Band is wound sealing to copper pipe.Thereby, it is possible to improve the reliability and accuracy of temperature detection.

According to one embodiment of present invention, can be according to following formula when the current working of air conditioner is cooling condition (1) gas returning port temperature t is generated₁：

t₁=a*t₇+b*f (1)

Wherein, f is compressor operating frequency, and a, b are fitting coefficient, and a, b can obtain according to lot of experimental data, can be led to The electric-control system for crossing air conditioner monitors the running frequency of compressor in real time.

S103, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor₁ Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the exhaust port temperatures t of exhaust outlet in compressor₂ Generate the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the outdoor heat exchanger of outdoor heat exchanger first end First end temperature t₄Generate the refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}With lubricating oil enthalpy h_{4 lubricating oil}, changed according to interior The indoor heat exchanger first end temperature t of hot device first end₇Generate the refrigerant enthalpy t of indoor heat exchanger first end_{7 refrigerants}And lubrication Oily enthalpy h_{7 lubricating oil}, and the tonifying Qi temperature t according to compressor tonifying Qi entrance₈Generation fills into the gaseous refrigerant enthalpy of compressor respectively Value h_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}。

Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.

Specifically, because the refrigerant of different temperatures test point and the state of the mixture of lubricating oil are different therefore different The refrigerant enthalpy and lubricating oil enthalpy of temperature detecting point are different.In one embodiment of the invention, can be rule of thumb public Refrigerant enthalpy and lubricating oil enthalpy is calculated in formula.

Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}、 The refrigerant enthalpy h of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, outdoor heat exchanger first end refrigerant enthalpy h_{4 refrigerants}And profit Lubricating oil enthalpy h_{4 lubricating oil}, indoor heat exchanger first end refrigerant enthalpy t_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}, fill into compressor Gaseous refrigerant enthalpy h_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}Detailed process.

For the refrigerant enthalpy h of gas returning port in compressor_{1 refrigerant}, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the gas returning port of contracting machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined_{1 refrigerant}。

According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor₁Generate the system of gas returning port Cryogen enthalpy h_{1 refrigerant}Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆, and according to gas returning port temperature Spend t₁With indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁, and according to indoor heat exchanger middle portion temperature t₆Generation The enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}, according to suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Generate back The modifying factor D of gas port refrigerant enthalpy₁, finally according to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy Value h_{Air-breathing saturation}Generate refrigerant enthalpy h_{1 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 interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger Interior heat exchanger middle portion temperature t₆。

Getting gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Afterwards, air-breathing mistake is generated according to following formula (3) Temperature Δ t₁：

Δt₁=t₁-t₆ (3)

Getting suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Afterwards, return-air is generated according to above-mentioned formula (2) The modifying factor D of mouth refrigerant enthalpy₁, then can be according to the enthalpy of saturation refrigerant under following formula (4) generation suction temperature h_{Air-breathing saturation}：

Finally, according to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy h_{Air-breathing saturation}Generate refrigerant Enthalpy h_{1 refrigerant}, h_{1 refrigerant}=D₁·h_{Air-breathing saturation}+d₇, wherein, d₇For overheated zone coefficient corresponding to refrigerant.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}, when the current working of air conditioner is refrigeration During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the The refrigerant enthalpy h of one end_{7 refrigerants}。

According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇It is raw Into the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}Specifically include：According to indoor heat exchanger first end temperature t₇Changed with interior Hot device middle portion temperature t₆Generate degree of superheat Δ t₇, and according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generation interior is changed The modifying factor D of hot device first end refrigerant enthalpy₇And the modifying factor D according to indoor heat exchanger first end refrigerant enthalpy₇ With the enthalpy h of saturation refrigerant_{Air-breathing saturation}Generate refrigerant enthalpy h_{7 refrigerants}。

Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation (5)₇：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

Specifically, indoor heat exchanger first end temperature t is being got₇With indoor heat exchanger middle portion temperature t₆Afterwards, under State formula (6) generation degree of superheat Δ t₇：

Δt₇=t₇-t₆ (6)

Getting degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Afterwards, interior can be generated according to above-mentioned formula (5) to change The modifying factor D of hot device first end refrigerant enthalpy₇, saturation under suction temperature then can be generated according to above-mentioned formula (4) and is freezed The enthalpy h of agent_{Air-breathing saturation}。

Finally, according to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇With the enthalpy of saturation refrigerant h_{Air-breathing saturation}Generate refrigerant enthalpy h_{7 refrigerants}, h_{7 refrigerants}=D₇·h_{Air-breathing saturation}+d₇, wherein, d₇For overheated zone coefficient corresponding to refrigerant.

In addition, the refrigerant enthalpy h for exhaust outlet in compressor_{2 refrigerants}, when the current working of air conditioner is cooling condition When, the refrigerant superheat of the exhaust outlet of compressor, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined_{2 refrigerants}。

According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor₂Generate the system of exhaust outlet The enthalpy h of cryogen_{2 refrigerants}Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃, and changed according to outdoor Hot device middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}, and the row according to exhaust outlet in compressor Gas port temperature t₂With outdoor heat exchanger middle portion temperature t₃Generate discharge superheat Δ t₂, according to discharge superheat Δ t₂Changed with outdoor Hot device middle portion temperature t₃Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂, finally according to modifying factor D₂, satisfy under delivery temperature With the enthalpy h of refrigerant_{It is vented saturation}Generate the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}。

Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation (7)₂：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t₃。

The exhaust port temperatures t of exhaust outlet in compressor is got₂With outdoor heat exchanger middle portion temperature t₃Afterwards, can be under State formula (8) generation discharge superheat Δ t₂：

Δt₂=t₂-t₃ (8)

Getting discharge superheat Δ t₂With outdoor heat exchanger middle portion temperature t₃Afterwards, generated and be vented according to above-mentioned formula (7) The modifying factor D of mouth refrigerant enthalpy₂, then according to the enthalpy of saturation refrigerant under following formula (9) generation delivery temperature h_{It is vented saturation}：

Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation} Generate the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}, h_{2 refrigerants}=D₂·h_{It is vented saturation}+d₇, wherein, d₇To overheat fauna corresponding to refrigerant Number.

For the refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}, when the current working of air conditioner is cooling condition, The refrigerant supercooling of outdoor heat exchanger first end, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}, i.e. The refrigerant enthalpy h of outdoor heat exchanger first end is generated according to below equation (10)_{4 refrigerants}：

Wherein, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

In addition, based on same principle, the gaseous refrigerant enthalpy h for filling into compressor_{8 ' refrigerants}With the liquid of flash vessel Refrigerant enthalpy h_{8 " refrigerants}, the gaseous refrigerant enthalpy h of compressor can be calculated by following formula (11)_{8 ' refrigerants}, under State the liquid refrigerant enthalpy h that flash vessel is calculated in formula (12)_{8 " refrigerants}。

Wherein, a₁-a₅For the saturation region coefficient corresponding to refrigerant, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system The species of cryogen is relevant, and R410A refrigerants and saturation region coefficient, overheated zone corresponding to R32 refrigerants are respectively illustrated in table 1 Coefficient and supercooling fauna number：

Table 1

Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature The refrigerant enthalpy of measuring point.

In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is cooling condition Adjust low 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 External heat exchanger first end temperature t₄Respectively obtain the refrigerant enthalpy h of exhaust outlet₂With the refrigerant enthalpy of outdoor heat exchanger first end h₄, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure_8’And saturated liquid enthalpy h_8”。

According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to following formula (13) h_{I lubricating oil}：

h_{I, lubricating oil}=-0.0808+1.7032t_i+0.0025t_i ² (13)

Wherein, i is positive integer, t_iFor the temperature of temperature detecting point.

Thus, the lubricating oil enthalpy h of gas returning port can be calculated out_{1 lubricating oil}, exhaust outlet lubricating oil enthalpy h_{2 lubricating oil}, it is outdoor The lubricating oil enthalpy h of heat exchanger first end_{4 lubricating oil}, indoor heat exchanger first end lubricating oil enthalpy h_{7 lubricating oil}, fill into the profit of compressor Lubricating oil enthalpy h_{8 ' lubricating oil}With the lubricating oil enthalpy h of flash vessel_{8 " lubricating oil}。

S104, according to the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}Generate the mixture enthalpy of gas returning port Value h₁, according to the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy h of exhaust outlet₂, according to The refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}With lubricating oil enthalpy h_{4 lubricating oil}Generate the mixture of outdoor heat exchanger first end Enthalpy h₄, according to the refrigerant enthalpy t of indoor heat exchanger first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}Generate indoor heat exchanger the The mixture enthalpy h of one end₇, according to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}Generation is mended Enter compressor mixture enthalpy h_8’, and the liquid refrigerant enthalpy h according to flash vessel_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}It is raw Into the mixture enthalpy h of flash vessel_8”。

According to one embodiment of present invention, the mixture enthalpy of each point is calculated according to following formula (14) and (15) h_i：

h_i=(1-C_g)h_{I, refrigerant}+C_gh_{I, lubricating oil} (14)

C_g=f/10⁴ (15)

Wherein, i is positive integer, and Cg is oil content, and f is the running frequency of compressor.

Thus, the mixture enthalpy h of gas returning port can be calculated out₁, exhaust outlet mixture enthalpy h₂, outdoor heat exchanger The mixture enthalpy h of first end₄, indoor heat exchanger first end mixture enthalpy h₇, fill into compressor mixture enthalpy h_8’With The mixture enthalpy h of flash vessel_8”。

S105, according to the power of compressor, the mixture enthalpy h of gas returning port₁, exhaust outlet mixture enthalpy h₂, outdoor changes The mixture enthalpy h of hot device first end₄, indoor heat exchanger first end mixture enthalpy h₇, fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of flash vessel_8”Generate the refrigerating capacity of air conditioner.

According to one embodiment of present invention, the refrigerating capacity of air conditioner is generated according to following formula (16)：

Wherein, Q_{Refrigerating capacity}For Air conditioner refrigerating capacity, P_CompressorFor compressor horsepower.

S106, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Because the current working of air conditioner is cooling condition, thus can be generated according to air conditioner power consumption and refrigerating capacity empty The refrigeration efficiency of device is adjusted, specifically, the refrigeration efficiency of air conditioner is the ratio between the refrigerating capacity of air conditioner and power consumption, i.e. EER= Q_{Refrigerating capacity}/P_{Power consumption}。

, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.

To sum up, the efficiency computational methods of air conditioner according to embodiments of the present invention, the first current working of acquisition air conditioner, The power and air conditioner power consumption of compressor, and obtain exhaust outlet in the gas returning port temperature of gas returning port in compressor, compressor Exhaust port temperatures, the outdoor heat exchanger first end temperature of outdoor heat exchanger first end, the interior of indoor heat exchanger first end change The tonifying Qi temperature of hot device first end temperature and compressor tonifying Qi entrance, when the current working of air conditioner is cooling condition, according to The temperature of above-mentioned each temperature detecting point generates the refrigerant enthalpy and lubricating oil enthalpy of above-mentioned each temperature detecting point, goes forward side by side one Step generates the mixture enthalpy of each temperature detecting point, and the power, above-mentioned each temperature detecting point then in conjunction with compressor mix Compound enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, and thereby, it is possible to real-time and accurately detect the energy of air conditioner Effect, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve refrigeration Purpose.

In addition, embodiments of the invention also proposed a kind of air conditioner, it includes memory, processor and is stored in storage On device and the computer program that can run on a processor, during computing device computer program, the above-mentioned implementation of the present invention is realized The efficiency computational methods for the air conditioner that example proposes.

In addition, embodiments of the invention also proposed a kind of non-transitorycomputer readable storage medium, it is stored thereon with Computer program, realize that the efficiency for the air conditioner that the above embodiment of the present invention proposes calculates when computer program is executed by processor Method.

The air conditioner and its efficiency computational methods of above-described embodiment can detect the refrigeration efficiency of air conditioner, to detect air-conditioning The heat efficiency of device, the present invention also propose the efficiency computational methods of another air conditioner.

Fig. 3 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention.As shown in figure 3, The efficiency computational methods of the air conditioner of the embodiment of the present invention may include following steps：

S201, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.

S202, obtain the gas returning port temperature t of gas returning port in compressor₁, in compressor exhaust outlet exhaust port temperatures t₂, room Outdoor heat exchanger middle portion temperature t in the middle part of external heat exchanger₃, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t₅, room The indoor heat exchanger first end temperature t of interior heat exchanger first end₇With the tonifying Qi temperature t of compressor tonifying Qi entrance₈, wherein, gas returning port Temperature t₁According to outdoor heat exchanger middle portion temperature t₃Generated with the running frequency f of compressor.

Specifically, as shown in figure 1, can be by setting the temperature sensor of exhaust outlet within the compressor (as shown in Figure 1 02) exhaust port temperatures t is obtained₂；Room is 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；Obtained by the temperature sensor (as shown in Figure 1 05) for being disposed in the interior the end of heat exchanger second Take the second end of indoor heat exchanger temperature t₅；It is (as shown in Figure 1 by the temperature sensor for being disposed in the interior heat exchanger first end 07) indoor heat exchanger first end temperature t is obtained₇；By being arranged on the temperature sensor of compressor tonifying Qi entrance (as shown in Figure 1 08) obtain compressor tonifying Qi entrance tonifying Qi temperature t₈.Then can be according to outdoor heat exchanger middle portion temperature t₃With the fortune of compressor Line frequency f generation gas returning port temperature t₁。

According to one embodiment of present invention, can be according to following formula when the current working of air conditioner is heating condition (17) gas returning port temperature t is generated₁：

t₁=c*t₃+d*f (17)

Wherein, f is compressor operating frequency, and c, d are fitting coefficient, and c, d can obtain according to lot of experimental data, can be led to The electric-control system for crossing air conditioner monitors the running frequency of compressor in real time.

S203, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor₁ Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the exhaust port temperatures t of exhaust outlet in compressor₂ Generate the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the indoor heat exchange at the end of indoor heat exchanger second The second end of device temperature t₅Generate the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}, according to interior The indoor heat exchanger first end temperature t of heat exchanger first end₇Generate the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}And profit Lubricating oil enthalpy h_{7 lubricating oil}, and the tonifying Qi temperature t according to compressor tonifying Qi entrance₈Generation fills into the gaseous refrigerant of compressor respectively Enthalpy h_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}。

Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.

Specifically, during air conditioner works, due to the mixing of the refrigerant and lubricating oil of different temperatures test point The state of thing is different, therefore the refrigerant enthalpy of different temperatures test point and lubricating oil enthalpy are different.At one of the present invention In embodiment, rule of thumb refrigerant enthalpy and lubricating oil enthalpy can be calculated by formula.

Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}、 The enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, the end of indoor heat exchanger second refrigerant enthalpy h_{5 refrigerants}With Lubricating oil enthalpy h_{5 lubricating oil}, indoor heat exchanger first end refrigerant enthalpy h_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}, fill into compressor Gaseous refrigerant enthalpy h_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}With lubricating oil enthalpy Value h_{8 " lubricating oil}Detailed process.

For the refrigerant enthalpy h of gas returning port in compressor_{1 refrigerant}, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the gas returning port of contracting machine, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined_{1 refrigerant}。

According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor₁Generate the system of gas returning port Cryogen enthalpy h_{1 refrigerant}Specifically include：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, with And according to outdoor heat exchanger middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}, finally according to gas returning port The modifying factor D of refrigerant enthalpy₁, under suction temperature saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy of gas returning port h_{1 refrigerant}。

Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to below equation (18)₁：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

Specifically, gas returning port temperature t is being got₁With outdoor heat exchanger middle portion temperature t₃Afterwards, according to following formula (19) Generate suction superheat Δ t₁：

Δt₁=t₁-t₃ (19)

Getting suction superheat Δ t₁With outdoor heat exchanger middle portion temperature t₃Afterwards, according to above-mentioned formula (18) gas returning port The modifying factor D of refrigerant enthalpy₁, then can be according to the enthalpy of saturation refrigerant under following formula (20) generation suction temperature h_{Air-breathing saturation}：

Finally, according to the modifying factor D of gas returning port refrigerant enthalpy₁, under suction temperature saturation refrigerant enthalpy h_{Air-breathing saturation} Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}, h_{1 refrigerant}=D₁·h_{Air-breathing saturation}+d₇, wherein, d₇To overheat fauna corresponding to refrigerant Number.

For the refrigerant enthalpy h of exhaust outlet in compressor_{2 refrigerants}, when the current working of air conditioner is heating condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined_{2 refrigerants}。

According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor₂Generate the system of exhaust outlet The enthalpy h of cryogen_{2 refrigerants}Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆, and changed according to interior Indoor heat exchanger middle portion temperature t in the middle part of hot device₆With the exhaust port temperatures t of exhaust outlet in compressor₂Generate discharge superheat Δ t₂, and according to discharge superheat Δ t₂With indoor heat exchanger middle portion temperature t₆Generate the modifying factor of exhaust outlet refrigerant enthalpy D₂, then according to outdoor heat exchanger middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}, finally according to row The modifying factor D of gas port refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigerant of exhaust outlet Enthalpy h_{2 refrigerants}。

Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation (21)₂：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

Getting the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆With the exhaust outlet of exhaust outlet in compressor Temperature t₂Afterwards, discharge superheat Δ t can be generated according to following formula (22)₂：

Δt₂=t₂-t₆ (22)

Getting discharge superheat Δ t₂With indoor heat exchanger middle portion temperature t₆Afterwards, generated and arranged according to above-mentioned formula (21) The modifying factor D of gas port refrigerant enthalpy₂, then can be according to the enthalpy of saturation refrigerant under following formula (23) generation delivery temperature Value h_{It is vented saturation}：

Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation} Generate the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}, h_{2 refrigerants}=D₂·h_{It is vented saturation}+d₇, wherein, d₇To overheat fauna corresponding to refrigerant Number.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}, when the current working of air conditioner is heating During operating mode, the refrigerant superheat of indoor heat exchanger first end, position refrigerant superheat degree can be combined and calculate indoor heat exchanger the The refrigerant enthalpy h of one end_{7 refrigerants}。

According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇Point Not Sheng Cheng indoor heat exchanger first end refrigerant enthalpy h_{7 refrigerants}Specifically include：Indoor heat exchange in the middle part of indoor heat exchanger Device middle portion temperature t₆With indoor heat exchanger first end temperature t₇Generate degree of superheat Δ t₇, and according to degree of superheat Δ t₇With indoor heat exchange Device middle portion temperature t₆Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇, and according to indoor heat exchanger first Hold the modifying factor D of refrigerant enthalpy₇, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate refrigerant enthalpy h_{7 refrigerants}。

Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation (24)₇：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger is being got₆With indoor heat exchanger first Hold temperature t₇Afterwards, degree of superheat Δ t is generated according to following formula (25)₇：

Δt₇=t₇-t₆ (25)

Getting degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Afterwards, can be generated according to above-mentioned formula (24) indoor The modifying factor D of heat exchanger first end refrigerant enthalpy₇, then saturation system under delivery temperature can be generated according to above-mentioned formula (23) The enthalpy h of cryogen_{It is vented saturation}。

Finally, according to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇With the enthalpy of saturation refrigerant h_{It is vented saturation}Generate refrigerant enthalpy h_{7 refrigerants}, h_{7 refrigerants}=D₇·h_{It is vented saturation}+d₇, wherein, d₇For overheated zone coefficient corresponding to refrigerant.

For the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}, when the current working of air conditioner is heating condition, The refrigerant supercooling at the end of indoor heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}, i.e. The refrigerant enthalpy h at the end of indoor heat exchanger second is calculated according to following formula (26)_{5 refrigerants}：

Wherein, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

In addition, in one embodiment of the invention, the gaseous refrigerant enthalpy h for filling into compressor_{8 ' refrigerants}And flash distillation The liquid refrigerant enthalpy h of device_{8 " refrigerants}, the gaseous refrigerant enthalpy of compressor can be calculated by above-mentioned formula (11) h_{8 ' refrigerants}, the liquid refrigerant enthalpy h of flash vessel is calculated by above-mentioned formula (12)_{8 " refrigerants}, i.e.,Wherein, a₁-a₅For corresponding to refrigerant Saturation region coefficient, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system The species of cryogen is relevant, and R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, mistake are respectively illustrated in above-mentioned table 1 Hot-zone coefficient and supercooling fauna number.

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 pressure_8’And saturated liquid enthalpy h_8”。

According to one embodiment of present invention, the lubricating oil enthalpy of each temperature detecting point is calculated according to following formula (27) h_{I lubricating oil}：

h_{I, lubricating oil}=-0.0808+1.7032t_i+0.0025t_i ² (27)

Thus, the lubricating oil enthalpy h of gas returning port can be calculated out_{1 lubricating oil}, exhaust outlet lubricating oil enthalpy h_{2 lubricating oil}, it is indoor The lubricating oil enthalpy h at the end of heat exchanger second_{5 lubricating oil}With the lubricating oil enthalpy h of indoor heat exchanger first end_{7 lubricating oil}, fill into compressor Lubricating oil enthalpy h_{8 ' lubricating oil}With the lubricating oil enthalpy h of flash vessel_{8 " lubricating oil}。

S204, according to the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}Generate the mixture enthalpy of gas returning port Value h₁, according to the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy h of exhaust outlet₂, root According to the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}Generate the mixed of the end of indoor heat exchanger second Compound enthalpy h₅, according to the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}Generate indoor heat exchange The mixture enthalpy h of device first end₇, according to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' chiller refrigeration agent}With lubricating oil enthalpy h_{8 ' lubricating oil}Generation fills into compressor mixture enthalpy h_8’, and the liquid refrigerant enthalpy h according to flash vessel_{8 " refrigerants}And lubricating oil Enthalpy h_{8 " lubricating oil}Generate the mixture enthalpy h of flash vessel_8”。

According to one embodiment of present invention, the mixture enthalpy of each point is calculated according to following formula (28) and (29) h_i：

h_i=(1-C_g)h_{I, refrigerant}+C_gh_{I, lubricating oil} (28)

C_g=f/10⁴ (29)

Wherein, i is positive integer, and Cg is oil content, and f is the running frequency of the compressor.

Thus, the mixture enthalpy h of gas returning port can be calculated out₁, exhaust outlet mixture enthalpy h₂, indoor heat exchanger The mixture enthalpy h at the second end₅With the mixture enthalpy h of indoor heat exchanger first end₇, fill into compressor mixture enthalpy h_8’With The mixture enthalpy h of flash vessel_8”。

S205, according to the power of compressor, the mixture enthalpy h of gas returning port₁, exhaust outlet mixture enthalpy h₂, interior changes The mixture enthalpy h at the hot end of device second₅, indoor heat exchanger first end mixture enthalpy h₇, fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of flash vessel_8”Generate the heating capacity of air conditioner.

According to one embodiment of present invention, the heating capacity of air conditioner is generated according to following formula (30)：

Wherein, Q_{Heating capacity}For heating capacity of air conditioner, P_CompressorFor compressor horsepower.

S206, 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= Q_{Heating capacity}/P_{Power 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.

To sum up, the efficiency computational methods of air conditioner according to embodiments of the present invention, the first current working of acquisition air conditioner, The power and air conditioner power consumption of compressor, and obtain exhaust outlet in the gas returning port temperature of gas returning port in compressor, compressor Exhaust port temperatures, the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second, the interior of indoor heat exchanger first end change The tonifying Qi temperature of hot device first end temperature and compressor tonifying Qi entrance, and when the current working of air conditioner is heating condition, The refrigerant enthalpy and lubricating oil enthalpy of above-mentioned each temperature detecting point are generated according to the temperature of above-mentioned each temperature detecting point, and The mixture enthalpy of each temperature detecting point is further generated, power, above-mentioned each temperature detecting point then in conjunction with compressor Mixture enthalpy and air conditioner power consumption obtain the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect air conditioner Efficiency, consequently facilitating according to the real-time energy efficiency of air conditioner optimize air conditioner running status, reach energy-conservation and improve heating effect The purpose of fruit.

In addition, embodiments of the invention also proposed another air conditioner, it includes memory, processor and is stored in On reservoir and the computer program that can run on a processor, during computing device computer program, the invention described above reality is realized Apply the efficiency computational methods of the air conditioner of example proposition.

In addition, embodiments of the invention also proposed another non-transitorycomputer readable storage medium, store thereon There is computer program, the efficiency meter for the air conditioner that the above embodiment of the present invention proposes is realized when computer program is executed by processor Calculation method.

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

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, outdoor heat exchange The outdoor heat exchanger first end temperature t of device first end₄, indoor heat exchanger first end indoor heat exchanger first end temperature t₇And pressure The tonifying Qi temperature t of contracting machine tonifying Qi entrance₈, wherein, the gas returning port temperature t₁According to the indoor heat exchanger first end temperature t₇With The running frequency f generations of compressor；

When the current working of the air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in the compressor₁It is raw Into the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the exhaust port temperatures of exhaust outlet in the compressor t₂Generate the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the outdoor of the outdoor heat exchanger first end Heat exchanger first end temperature t₄Generate the refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}With lubricating oil enthalpy h_{4 lubricating oil}, according to The indoor heat exchanger first end temperature t of the indoor heat exchanger first end₇Generate the refrigerant enthalpy of indoor heat exchanger first end t_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}, and the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into compression respectively The gaseous refrigerant enthalpy h of machine_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}And lubricating oil Enthalpy h_{8 " lubricating oil}；

According to the refrigerant enthalpy h of the gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}Generate the mixture enthalpy h of gas returning port₁, According to the refrigerant enthalpy h of the exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy h of exhaust outlet₂, according to The refrigerant enthalpy h of the outdoor heat exchanger first end_{4 refrigerants}With lubricating oil enthalpy h_{4 lubricating oil}Generate the mixed of outdoor heat exchanger first end Compound enthalpy h₄, according to the refrigerant enthalpy t of the indoor heat exchanger first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}Generation is indoor The mixture enthalpy h of heat exchanger first end₇, according to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' refrigerants}With lubricating oil enthalpy Value h_{8 ' lubricating oil}Generation fills into compressor mixture enthalpy h_8’, and the liquid refrigerant enthalpy h according to the flash vessel_{8 " refrigerants}With Lubricating oil enthalpy h_{8 " lubricating oil}Generate the mixture enthalpy h of flash vessel_8”；

According to the power of the compressor, the mixture enthalpy h of the gas returning port₁, the exhaust outlet mixture enthalpy h₂, institute State the mixture enthalpy h of outdoor heat exchanger first end₄, the indoor heat exchanger first end mixture enthalpy h₇, described fill into pressure Contracting machine mixture enthalpy h_8’With the mixture enthalpy h of the flash vessel_8”Generate the refrigerating capacity of air conditioner；And

The efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.

2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be returned according in the compressor The gas returning port temperature t of gas port₁Generate the refrigerant enthalpy h of the gas returning port_{1 refrigerant}Specifically include：

Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆；

According to the gas returning port temperature t₁With the indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁；

According to the indoor heat exchanger middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}；

According to the suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Generate the modifying factor of gas returning port refrigerant enthalpy D₁；

According to the modifying factor D of the gas returning port refrigerant enthalpy₁, the saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigeration Agent enthalpy h_{1 refrigerant}。

3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that the suction is generated according to below equation The enthalpy h of saturation refrigerant at a temperature of gas_{Air-breathing saturation}：

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> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

5. the efficiency computational methods of air conditioner as claimed in claim 3, 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 end_{7 refrigerants}Specific bag Include：

According to the indoor heat exchanger first end temperature t₇With the indoor heat exchanger middle portion temperature t₆Generate degree of superheat Δ t₇；

According to the degree of superheat Δ t₇With the indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D₇；

According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy₇With the enthalpy h of the saturation refrigerant_{Air-breathing saturation} Generate the refrigerant enthalpy h_{7 refrigerants}。

6. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that the room is generated according to below equation The modifying factor D of interior heat exchanger first end refrigerant enthalpy₇：

<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be arranged according in the compressor The exhaust port temperatures t of gas port₂Generate the enthalpy h of the refrigerant of the exhaust outlet_{2 refrigerants}Specifically include：

Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃；

According to the outdoor heat exchanger middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}；

According to the exhaust port temperatures t of exhaust outlet in the compressor₂With the outdoor heat exchanger middle portion temperature t₃Generate discharge superheat Spend Δ t₂；

According to the discharge superheat Δ t₂With the outdoor heat exchanger middle portion temperature t₃Generate the amendment of exhaust outlet refrigerant enthalpy Factor D₂；

According to the modifying factor D₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigeration of the exhaust outlet The enthalpy h of agent_{2 refrigerants}。

8. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy₂：

<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>3</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>3</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>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>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated according to below equation The refrigerant enthalpy h of external heat exchanger first end_{4 refrigerants}：

Wherein, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation The refrigerating capacity of air conditioner：

11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each The lubricating oil enthalpy h of temperature detecting point_{I lubricating oil}, wherein, i is positive integer,

h_{I, lubricating oil}=-0.0808+1.7032t_i+0.0025t_i ²,

Wherein, t_iFor the temperature of temperature detecting point.

12. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that calculated according to below equation each The mixture enthalpy h of point_i, wherein, i is positive integer,

h_i=(1-C_g)h_{I, refrigerant}+C_gh_{I, lubricating oil},

C_g=f/10⁴,

Wherein, Cg is oil content, and f is the running frequency of the compressor.

13. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, realize as in claim 1-12 Any described method.

14. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 1-12 is realized when calculation machine program is executed by processor.

15. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：

Obtain the gas returning port temperature t of gas returning port in compressor₁, in the compressor exhaust outlet exhaust port temperatures t₂, outdoor heat exchange Outdoor heat exchanger middle portion temperature t in the middle part of device₃, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t₅, indoor heat exchange The indoor heat exchanger first end temperature t of device first end₇With the tonifying Qi temperature t of compressor tonifying Qi entrance₈, wherein, the gas returning port temperature Spend t₁According to the outdoor heat exchanger middle portion temperature t₃Generated with the running frequency f of compressor；

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 port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the exhaust port temperatures of exhaust outlet in the compressor t₂Generate the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the room at the end of indoor heat exchanger second Interior the second end of heat exchanger temperature t₅Generate the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}, root According to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end₇Generate the refrigerant enthalpy of indoor heat exchanger first end Value h_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}, and the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into pressure respectively The gaseous refrigerant enthalpy h of contracting machine_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel liquid refrigerant enthalpy h_{8 " refrigerants}And lubrication Oily enthalpy h_{8 " lubricating oil}；

According to the refrigerant enthalpy h of the gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}Generate the mixture enthalpy h of gas returning port₁, According to the enthalpy h of the refrigerant of the exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy h of exhaust outlet₂, root According to the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}Generate the end of indoor heat exchanger second Mixture enthalpy h₅, according to the refrigerant enthalpy h of the indoor heat exchanger first end_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}Generation The mixture enthalpy h of indoor heat exchanger first end₇, according to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' chiller refrigeration agent}And profit Lubricating oil enthalpy h_{8 ' lubricating oil}Generation fills into compressor mixture enthalpy h_8’, and the liquid refrigerant enthalpy according to the flash vessel h_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}Generate the mixture enthalpy h of flash vessel_8”；

According to the power of the compressor, the mixture enthalpy h of the gas returning port₁, the exhaust outlet mixture enthalpy h₂, institute State the mixture enthalpy h at the end of indoor heat exchanger second₅, the indoor heat exchanger first end mixture enthalpy h₇, described fill into pressure Contracting machine mixture enthalpy h_8’With the mixture enthalpy h of the flash vessel_8”Generate the heating capacity of air conditioner；And

The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.

16. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that described according in the compressor The gas returning port temperature t of gas returning port₁Generate the refrigerant enthalpy h of the gas returning port_{1 refrigerant}Specifically include：

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 temperature_{Air-breathing saturation}；

According to the modifying factor D of the gas returning port refrigerant enthalpy₁, under the suction temperature saturation refrigerant enthalpy h_{Air-breathing saturation}It is raw Into the refrigerant enthalpy h of the gas returning port_{1 refrigerant}。

17. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that according to generating below equation The enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}：

18. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that according to generating below equation The modifying factor D of gas returning port refrigerant enthalpy₁：

<mrow> <msub> <mi>D</mi> <mn>1</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

19. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that described according in the compressor The exhaust port temperatures t of exhaust outlet₂Generate the enthalpy h of the refrigerant of the exhaust outlet_{2 refrigerants}Specifically 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 outdoor heat exchanger middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}；

According to the modifying factor D of the exhaust outlet refrigerant enthalpy₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}It is raw Into the refrigerant enthalpy h of the exhaust outlet_{2 refrigerants}。

20. the efficiency computational methods of the air conditioner described in claim 19, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy₂：

<mrow> <msub> <mi>D</mi> <mn>2</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&Delta;t</mi> <mn>2</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

21. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that described according to the indoor heat exchange The indoor heat exchanger first end temperature t of device first end₇Generate the refrigerant enthalpy h of the indoor heat exchanger first end_{7 refrigerants}Specifically Including：

According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆With the indoor heat exchanger first end temperature t₇It is raw Into degree of superheat Δ t₇；

According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy₇, saturation refrigerant under the delivery temperature Enthalpy h_{It is vented saturation}Generate the refrigerant enthalpy h_{7 refrigerants}。

22. the efficiency computational methods of air conditioner as claimed in claim 21, it is characterised in that according to generating below equation The modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇：

Wherein, d₁-d₆For overheated zone coefficient corresponding to refrigerant.

23. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to calculating below equation The refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}：

Wherein, c₁-c₄For fauna number is subcooled corresponding to refrigerant.

24. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to generating equation below The heating capacity of air conditioner：

25. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that calculated according to below equation each The lubricating oil enthalpy h of temperature detecting point_{I lubricating oil}, wherein, i is positive integer,

h_{I, lubricating oil}=-0.0808+1.7032t_i+0.0025t_i ²,

Wherein, t_iFor the temperature of temperature detecting point.

26. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that calculated according to below equation each The mixture enthalpy h of point_i, wherein, i is positive integer,

h_i=(1-C_g)h_{I, refrigerant}+C_gh_{I, lubricating oil},

C_g=f/10⁴,

Wherein, Cg is oil content, and f is the running frequency of the compressor.

27. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, realize as in claim 15-26 Any described method.

28. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 15-26 is realized when calculation machine program is executed by processor.