CN107328042A

CN107328042A - Air conditioner and its efficiency computational methods

Info

Publication number: CN107328042A
Application number: CN201710772835.2A
Authority: CN
Inventors: 杨亚新; 张�浩; 戚文端; 陈新; 刘燕飞
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: 2017-11-07

Abstract

The invention discloses a kind of air conditioner and its efficiency computational methods, it the described method comprises the following steps：Obtain current working, the current frequency of compressor and the air conditioner power consumption of air conditioner；Obtain compressor return air mouthful temperature t₁, exhaust port temperatures t₂, outdoor heat exchanger first end temperature t₄, indoor heat exchanger first end temperature t₇With compressor tonifying Qi temperature t₈；When current working is cooling condition, according to t₁、t₂、t₄、t₇And t₈The mixture enthalpy h of gas returning port is generated respectively₁, exhaust outlet mixture enthalpy h₂, outdoor heat exchanger first end mixture enthalpy h₄, indoor heat exchanger first end mixture enthalpy h₇, fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of flash vessel_8”；The power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve；According to the power of compressor, h₁、h₂、h₄、h₇、h_8’And h_8”Generate the refrigerating capacity of air conditioner；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

It is comfortably the problem of user more pays close attention to that whether air conditioner, which saves,.

Current air conditioner is difficult to maintain and preferably transported operationally due to that can not know the situation of change of efficiency Row state, cooling or heating effect and energy-efficient performance are not ideal enough.

The content of the invention

It is contemplated that at least solving one of technical problem in above-mentioned technology to a certain extent.Therefore, the present invention First purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.

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

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

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

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

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

To reach above-mentioned purpose, a kind of efficiency computational methods for air conditioner that first aspect present invention embodiment is proposed, bag Include following steps：Obtain current working, the current frequency of compressor and the air conditioner power consumption of air conditioner；Obtain in compressor The gas returning port temperature t of gas returning port₁, in the compressor exhaust outlet exhaust port temperatures t₂, outdoor heat exchanger first end outdoor change Hot device first end temperature t₄, indoor heat exchanger first end indoor heat exchanger first end temperature t₇With the benefit of compressor tonifying Qi entrance Temperature degree t₈；When the current working of the air conditioner is cooling condition, according to the gas returning port temperature of gas returning port in the compressor Spend t₁Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the exhaust of exhaust outlet in the compressor Mouth temperature t₂Generate the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the outdoor heat exchanger first end Outdoor 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 system of indoor heat exchanger first end Cryogen enthalpy t_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}With the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into compression 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’, according to the liquid refrigerant enthalpy of 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 current frequency of the compressor and in advance If compressor performance curves obtain the power of the compressor；According to the power of the compressor, the mixture of the gas returning port Enthalpy h₁, the exhaust outlet mixture enthalpy h₂, the outdoor heat exchanger first end mixture enthalpy h₄, the interior changes The mixture enthalpy h of hot device first end₇, described fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of the flash vessel_8” Generate the refrigerating capacity of air conditioner；And the energy of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity Effect.

The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The current frequency and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet, outdoor heat exchanger first end, room The temperature of interior heat exchanger first end and the tonifying Qi temperature of compressor tonifying Qi entrance, and air conditioner current working for refrigeration During operating mode, the mixture enthalpy of each above-mentioned temperature detecting point, Ran Hougen are generated according to the temperature of each above-mentioned temperature detecting point According to compressor current frequency and preset compressor performance curve obtain compressor power, and combine compressor power, on The mixture enthalpy and air conditioner power consumption for stating each temperature detecting point obtain the efficiency of air conditioner, thereby, it is possible to accurate in real time The efficiency of air conditioner really is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, is reached Energy-conservation and the purpose for improving refrigeration.

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

According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor₁Generation is described to return The refrigerant enthalpy h of gas port_{1 refrigerant}Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆；According to institute State gas returning port temperature t₁With the indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁；According to the indoor heat exchanger Middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}；According to the suction superheat Δ t₁With indoor heat exchange Device middle portion temperature t₆Generate the modifying factor D of gas returning port refrigerant enthalpy₁；According to the modifying factor of the gas returning port refrigerant enthalpy Sub- D₁, the saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy h_{1 refrigerant}。

Further, the enthalpy h of saturation refrigerant under the suction temperature is generated according to below equation_{Air-breathing saturation}：

h_{Air-breathing saturation}=a₁+a₂t₆+a₃t² ₆+a₄t³ ₆+a₅, wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.

Further, the modifying factor D of the gas returning port refrigerant enthalpy is generated according to below equation₁：

Wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.

According to one embodiment of present invention, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end t₇Generate the refrigerant enthalpy h of the indoor heat exchanger first end_{7 refrigerants}Specifically include：According to the indoor heat exchanger first end temperature Spend t₇With the indoor heat exchanger middle portion temperature t₆Generate degree of superheat Δ t₇；According to the degree of superheat Δ t₇With the indoor heat exchange Device middle portion temperature t₆Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇；According to the indoor heat exchanger first Hold the modifying factor D of refrigerant enthalpy₇With the enthalpy h of the saturation refrigerant_{Air-breathing saturation}Generate the refrigerant enthalpy h_{7 refrigerants}。

Further, the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation₇：

According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the row The enthalpy h of the refrigerant of gas port_{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 in the compressor The exhaust port temperatures t of exhaust outlet₂With the outdoor heat exchanger middle portion temperature t₃Generate discharge superheat Δ t₂；According to the exhaust Degree of superheat Δ t₂With the outdoor heat exchanger middle portion temperature t₃Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂：According to described Modifying factor D₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the enthalpy of the refrigerant of the exhaust outlet h_{2 refrigerants}。

Further, the modifying factor D of the exhaust outlet refrigerant enthalpy is generated according to below equation₂：

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 the corresponding supercooling fauna number of 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_comFor 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 mixture oil content, and f is the running frequency of the compressor.

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

Air conditioner according to embodiments of the present invention, real-time and accurately can be detected to efficiency, consequently facilitating according to reality Shi Nengxiao is optimized to running status, is reached energy-conservation and is improved the purpose of refrigeration.

To reach above-mentioned purpose, a kind of non-transitory computer-readable storage medium that third aspect present invention embodiment is proposed 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 performing its computer journey stored Sequence, can real-time and accurately detect the efficiency of air conditioner, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reaches energy-conservation and improves the purpose of refrigeration.

To reach above-mentioned purpose, the efficiency computational methods for another air conditioner that fourth aspect present invention embodiment is proposed, Comprise the following steps：Obtain current working, the current frequency of compressor and the air conditioner power consumption of air conditioner；Obtain compressor The gas returning port temperature t of middle gas returning port₁, in the compressor exhaust outlet exhaust port temperatures t₂, the end of indoor heat exchanger second interior The second end of heat exchanger temperature t₅, indoor heat exchanger first end indoor heat exchanger first end temperature t₇With compressor tonifying Qi entrance Tonifying Qi temperature t₈；When the current working of the air conditioner is heating condition, according to the gas returning port of gas returning port in the compressor Temperature t₁Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}With lubricating oil enthalpy h_{1 lubricating oil}, according to the row of exhaust outlet in the compressor Gas port temperature t₂Generate the enthalpy h of the refrigerant of exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}, according to the indoor heat exchanger The second end of indoor heat exchanger temperature t at two ends₅Generate the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}With lubricating oil enthalpy h_{5 lubricating oil}, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end₇Generate the system of indoor heat exchanger first end Cryogen enthalpy h_{7 refrigerants}With lubricating oil enthalpy h_{7 lubricating oil}With the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into compression 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 enthalpy h of the refrigerant of the exhaust outlet_{2 refrigerants}With lubricating oil enthalpy h_{2 lubricating oil}Generate the mixture enthalpy of exhaust outlet Value h₂, 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 indoor heat exchanger The mixture enthalpy h at the second end₅, according to the refrigerant enthalpy h 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 for filling into compressor h_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}Generation fills into compressor mixture enthalpy h_8’, according to the liquid refrigerant of the flash vessel Enthalpy h_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}Generate the mixture enthalpy h of flash vessel_8”；According to the current frequency of the compressor The power of the compressor is obtained with preset compressor performance curve；According to the power of the compressor, the gas returning port it is mixed Compound enthalpy h₁, the exhaust outlet mixture enthalpy h₂, the end of indoor heat exchanger second mixture enthalpy h₅, the room The mixture enthalpy h of interior heat exchanger first end₇, described fill into compressor mixture enthalpy h_8’With the mixture enthalpy of the flash vessel Value h_8”Generate the heating capacity of air conditioner；And the air conditioner is generated according to the air conditioner power consumption and the heating capacity Efficiency.

The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The current frequency and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet, the end of indoor heat exchanger second, room The temperature of interior heat exchanger first end and the tonifying Qi temperature of compressor tonifying Qi entrance, and air conditioner current working to heat During operating mode, the mixture enthalpy of each above-mentioned temperature detecting point, Ran Hougen are generated according to the temperature of each above-mentioned temperature detecting point According to compressor current frequency and preset compressor performance curve obtain compressor power, and combine compressor power, on The mixture enthalpy and air conditioner power consumption for stating each temperature detecting point obtain the efficiency of air conditioner, thereby, it is possible to accurate in real time The efficiency of air conditioner really is detected, consequently facilitating optimizing the running status of air conditioner according to the real-time energy efficiency of air conditioner, is reached Energy-conservation and the purpose for improving refrigeration.

According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor₁Generation is described to return The refrigerant enthalpy h of gas port_{1 refrigerant}Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃；According to institute State gas returning port temperature t₁With the outdoor heat exchanger middle portion temperature t₃Generate suction superheat Δ t₁；According to the suction superheat Δt₁With the outdoor heat exchanger middle portion temperature t₃Generate the modifying factor D of gas returning port refrigerant enthalpy₁；Changed according to the outdoor Hot device middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}；According to the gas returning port refrigerant enthalpy Modifying factor D₁, under the suction temperature saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy h of the gas returning port_{1 refrigerant}。

Wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.

According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the row The enthalpy h of the refrigerant of gas port_{2 refrigerants}Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆；According to Indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆With the exhaust port temperatures t of exhaust outlet in the compressor₂Generation Discharge superheat Δ t₂；According to the discharge superheat Δ t₂With the indoor heat exchanger middle portion temperature t₆Generate exhaust outlet refrigeration The modifying factor D of agent enthalpy₂；According to the indoor heat exchanger middle portion temperature t₆Generate the enthalpy of saturation refrigerant under delivery temperature 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}。

According to one embodiment of present invention, according to the indoor heat exchanger first end temperature of the indoor heat exchanger first end t₇The refrigerant enthalpy h of the indoor heat exchanger first end is generated respectively_{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 of the indoor heat exchanger first end_{7 refrigerants}。

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}：

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 air conditioner Heating capacity, P_comFor 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

To reach above-mentioned purpose, another air conditioner that fifth aspect present invention embodiment is proposed includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, is counted described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that fourth aspect present invention embodiment is proposed are realized.

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

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

Brief description of the drawings

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

Fig. 2 is a kind of flow chart of the efficiency computational methods of air conditioner according to the embodiment of the present invention；

Fig. 3 is the flow chart of the efficiency computational methods of another air conditioner according to the embodiment of the present invention.

Embodiment

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

The air conditioner and its efficiency computational methods of the embodiment of the present invention described below in conjunction with the accompanying drawings.

In an embodiment of the present invention, air conditioner can be twin-stage steam compressing air conditioner device.

As shown in figure 1, the air conditioner of the embodiment of the present invention may include compressor 100, four-way valve 200, outdoor heat exchanger 300th, restricting element 400, indoor heat exchanger 500, restricting element 600 and flash vessel 700.Wherein, the exhaust outlet of compressor 100 leads to Four-way valve 200 is crossed with the second end of outdoor heat exchanger 300 to be connected, the first end of outdoor heat exchanger 300 by restricting element 600 with The first end of flash vessel 700 is connected, and the second end of flash vessel 700 passes through the second end of restricting element 400 and indoor heat exchanger 500 It is connected, the first end of indoor heat exchanger 500 is connected by four-way valve 200 with the gas returning port of compressor 100, the of flash vessel 700 Three ends are connected with the tonifying Qi entrance of compressor 100.

When the current working of air conditioner is cooling condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A2 ends are directly connected with outdoor heat exchanger 300, and refrigerant is flowed to as shown in the solid arrow in Fig. 1；When the current working of air conditioner During for heating condition, the exhaust outlet of compressor 100 is directly connected by the A1 ends and A4 ends of four-way valve 200 with indoor heat exchanger 500 Logical, refrigerant is flowed to as shown in the dotted arrow in Fig. 1, is specifically not detailed here.

Fig. 2 is the flow chart of the efficiency computational methods of the air conditioner according to the embodiment of the present invention.As shown in Fig. 2 of the invention The efficiency computational methods of the air conditioner of embodiment comprise the following steps：

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

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

S102, obtains the gas returning port temperature t of gas returning port in compressor₁, in compressor exhaust outlet exhaust port temperatures t₂, room The outdoor heat exchanger first end temperature t of external heat exchanger first end₄, indoor heat exchanger first end indoor heat exchanger first end temperature t₇With the tonifying Qi temperature t of compressor tonifying Qi entrance₈。

Specifically, the temperature of the temperature detecting point can be detected by setting temperature sensor respectively in corresponding temperature test point Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature t₁；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t₂；By setting The temperature sensor (as shown in Figure 1 04) put in outdoor heat exchanger first end obtains outdoor heat exchanger first end temperature t₄；It is logical Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end t₇；Compressor tonifying Qi entrance is obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi porch Tonifying Qi temperature t₈。

Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, and to refrigerant Tube wall, especially sets the position of temperature sensor to take Insulation.For example, temperature sensor can be close to copper pipe setting, And sealing is wound to copper pipe by being incubated adhesive tape.Thereby, it is possible to improve the reliability and accuracy of temperature detection.

S103, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor₁ Generate the refrigerant enthalpy h of gas returning 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}With the tonifying Qi temperature t according to compressor tonifying Qi entrance₈Generation fills into the gaseous refrigerant enthalpy of compressor 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}。

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 and lubricating oil enthalpy of different temperatures test point are different.At one of the present invention In embodiment, rule of thumb formula calculating refrigerant enthalpy value and lubricating oil enthalpy can be obtained.

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 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 h_{8 " lubricating oil}Detailed process.

Wherein, for the refrigerant enthalpy h of gas returning port in compressor_{1 refrigerant}, when the current working of air conditioner is cooling condition When, the refrigerant superheat of the gas returning port of compressor can combine the refrigerant enthalpy h that suction superheat calculates gas returning port_{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；According to gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁；According to indoor heat exchanger middle portion temperature t₆Generate air-breathing temperature The enthalpy h of the lower saturation refrigerant of degree_{Air-breathing saturation}；According to suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆The gas returning port system of generation The modifying factor D of cryogen enthalpy₁；According to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy h_{Air-breathing saturation}It is raw Into refrigerant enthalpy h_{1 refrigerant}。

Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (1)_{Air-breathing saturation}：

h_{Air-breathing saturation}=a₁+a₂t₆+a₃t² ₆+a₄t³ ₆+a₅ (1)

Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (2)₁：

D₁=1+d₁Δt₁+d₂(Δt₁)²+d₃(Δt₁)t₆+d₄(Δt₁)²t₆+d₅(Δt₁)t² ₆+d₆(Δt₁)²t² ₆ (2)

Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger Interior heat exchanger middle portion temperature t₆, then according to gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁=t₁-t₆, and according to suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Generate the amendment of gas returning port refrigerant enthalpy Factor D₁, such as shown in above-mentioned formula (2), while according to indoor heat exchanger middle portion temperature t₆Generate saturation refrigerant under suction temperature Enthalpy h_{Air-breathing saturation}, such as shown in above-mentioned formula (1).Finally, according to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigeration The enthalpy h of agent_{Air-breathing saturation}Generate refrigerant enthalpy h_{1 refrigerant}, h_{1 refrigerant}=D₁·h_{Air-breathing saturation}+d₇, wherein, d₇For the corresponding overheat of refrigerant Fauna number.

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 can combine position refrigerant superheat degree 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；According to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆The indoor heat exchange of generation The modifying factor D of device first end refrigerant enthalpy₇；According to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇With it is full With the enthalpy h of 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 following formula (3)₇：

Specifically, can be first according to indoor heat exchanger first end temperature t₇With indoor heat exchanger middle portion temperature t₆Generate the degree of superheat Δt₇=t₇-t₆, then according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger first end refrigerant The modifying factor D of enthalpy₇, such as shown in above-mentioned formula (3), while according to indoor heat exchanger middle portion temperature t₆Generate under suction temperature The enthalpy h of saturation refrigerant_{Air-breathing saturation}, such as shown in above-mentioned formula (1).Finally, according to the indoor heat exchanger first end refrigerant of generation The modifying factor D of enthalpy₇With the enthalpy h of saturation refrigerant_{Air-breathing saturation}Generate refrigerant enthalpy h_{7 refrigerants}, h_{7 refrigerants}=D₇·h_{Air-breathing saturation}+d₇, Wherein, d₇For the corresponding overheated zone coefficient of refrigerant.

For the refrigerant enthalpy h of exhaust outlet in compressor_{2 refrigerants}, when the current working of air conditioner is cooling condition, pressure The refrigerant superheat of the exhaust outlet of contracting machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet_{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；According to outdoor heat exchange Device middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}；According to the exhaust outlet temperature of exhaust outlet in compressor Spend t₂With outdoor heat exchanger middle portion temperature t₃Generate discharge superheat Δ t₂；According to discharge superheat Δ t₂In outdoor heat exchanger Portion temperature t₃Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂：According to modifying factor D₂, saturation refrigerant under delivery temperature Enthalpy h_{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 following formula (4)₂：

Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t₃, then according to the exhaust port temperatures t of exhaust outlet in compressor₂With outdoor heat exchanger middle portion temperature t₃ Generate discharge superheat Δ t₂=t₂-t₃, and according to discharge superheat Δ t₂With outdoor heat exchanger middle portion temperature t₃Generate exhaust outlet The modifying factor D of refrigerant enthalpy₂, such as shown in above-mentioned formula (4), while according to outdoor heat exchanger middle portion temperature t₃Generation exhaust At a temperature of saturation refrigerant enthalpy h_{It is vented saturation}=a₁+a₂t₃+a₃t² ₃+a₄t³ ₃+a₅, wherein, a₁-a₅For the corresponding saturation of refrigerant Fauna number.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, d₇For the corresponding overheat fauna of 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, can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end_{4 refrigerants}。

According to one embodiment of present invention, the refrigerant enthalpy of outdoor heat exchanger first end is generated according to following formula (5) Value h_{4 refrigerants}：

In addition, filling into the gaseous refrigerant enthalpy h of compressor_{8 ' refrigerants}It can be calculated according to below equation：

h_{8 ' refrigerants}=a₁+a₂*t₈+a₃*t₈ ²+a₄*t₈ ³+a₅, wherein, t₈For the tonifying Qi temperature of compressor tonifying Qi entrance, a₁-a₅ For the corresponding saturation region coefficient of refrigerant.

The liquid refrigerant enthalpy h of flash vessel_{8 " refrigerants}It can be calculated according to below equation：

h_{8 " refrigerants}=c₁+c₂*t₈+c₃*t₈ ²+c₄*t₈ ³, wherein, t₈For the tonifying Qi temperature of compressor tonifying Qi entrance, c₁-c₄For system The corresponding supercooling fauna number of cryogen.

The species of the corresponding saturation region coefficient of above-mentioned refrigerant, overheated zone coefficient and supercooling fauna number and refrigerant has Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and cold-zone is crossed Coefficient：

Table 1

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

It should be noted that in other embodiments of the invention, can also directly invoke the result of calculation of software, or pass through Other approach obtain the refrigerant enthalpy of each temperature detecting point.For example, when the current working of air conditioner is cooling condition When, low pressure that can also be in air conditioner, gas returning port temperature t₁, indoor heat exchanger first end temperature t₇Respectively obtain return-air The refrigerant enthalpy h of mouth_{1 refrigerant}With the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}, and can be in air conditioner high pressure Pressure, exhaust port temperatures t₂, outdoor heat exchanger first end temperature t₄Respectively obtain the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}And outdoor The refrigerant enthalpy h of heat exchanger first end_{4 refrigerants}, and saturated air under the state can be obtained according to tonifying Qi temperature or pressure Body enthalpy h_{8 ' refrigerants}And saturated liquid enthalpy h_{8 " refrigerants}。

For the lubricating oil enthalpy h of each temperature detecting point_{I lubricating oil}, can be calculated according to below equation：

h_{I lubricating oil}=-0.0808+1.7032t_i+0.0025t² _i,

Wherein, i is positive integer, t_iFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy for obtaining out gas returning port can be calculated Value h_{1 lubricating oil}, exhaust outlet lubricating oil enthalpy h_{2 lubricating oil}, outdoor heat exchanger first end lubricating oil enthalpy h_{4 lubricating oil}And indoor heat exchanger The lubricating oil enthalpy h of first end_{7 lubricating oil}, fill into the lubricating oil enthalpy h of compressor_{8 ' lubricating oil}, flash vessel lubricating oil enthalpy h_{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’, according to the liquid refrigerant enthalpy h of flash vessel_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}Generation is dodged The mixture enthalpy h of steaming device_8”。

Specifically, the mixture enthalpy h of each temperature detecting point can be calculated according to below equation_i：

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

C_g=f/10⁴,

Wherein, C_gFor mixture oil content, f is the running frequency of compressor.Thus, it can calculate and obtain out the mixed of gas returning port Compound enthalpy h₁, exhaust outlet mixture enthalpy h₂, outdoor heat exchanger first end mixture enthalpy h₄, indoor heat exchanger first The mixture enthalpy h at end₇, fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of flash vessel_8”。

S105, the power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve.

Specifically, (it can be provided by compressor producer according to preset compressor performance curve, and be stored in advance in compressor In) calculate the flow and compressor consumption power for obtaining compressor under different running frequencies.

S106, according to the power of compressor, the 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.

Specifically, the refrigerating capacity of air conditioner can be generated according to below equation：

Wherein, Q_{Refrigerating capacity}Freeze for air conditioner Amount, P_comFor compressor horsepower.

S107, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Because the current working of air conditioner is cooling condition, thus it 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 refrigerating capacity and power consumption of air conditioner, i.e. EER= Q_{Refrigerating capacity}/P_{Power consumption}。

, can also be according to the 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 can not only save, additionally it is possible to improve the comfortableness of user.

Correspondence above-described embodiment, the present invention also proposes a kind of air conditioner.

The air conditioner of the embodiment of the present invention, including memory, processor and store on a memory and can be on a processor The computer program of operation, during computing device computer program, can be achieved the air conditioner that the above embodiment of the present invention is proposed Efficiency computational methods.

Air conditioner according to embodiments of the present invention, can real-time and accurately detect to efficiency, be entered according to real-time energy efficiency Row running status optimizes, and reaches energy-conservation and improves the purpose of refrigeration.

Correspondence above-described embodiment, the present invention also proposes a kind of non-transitorycomputer readable storage medium.

The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, the efficiency computational methods for the air conditioner that the above embodiment of the present invention is proposed can be achieved.

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

As shown in figure 3, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：

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

S202, obtains the gas returning port temperature t of gas returning port in compressor₁, in compressor exhaust outlet exhaust port temperatures t₂, room The second end of indoor heat exchanger temperature t at the interior end of heat exchanger second₅, indoor heat exchanger first end indoor heat exchanger first end temperature t₇With the tonifying Qi temperature t of compressor tonifying Qi entrance₈。

Specifically, the temperature of the temperature detecting point can be detected by setting temperature sensor respectively in corresponding temperature test point Degree.For example, can be by setting the temperature sensor (as shown in Figure 1 01) of gas returning port within the compressor to obtain gas returning port temperature t₁；By setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor to obtain exhaust port temperatures t₂；By setting The temperature sensor (as shown in Figure 1 05) for putting the end of heat exchanger second indoors obtains indoor heat exchanger the second end temperature t₅；It is logical Cross temperature sensor (as shown in Figure 1 07) the acquisition indoor heat exchanger first end temperature for being disposed in the interior heat exchanger first end t₇；Compressor tonifying Qi entrance is obtained by the temperature sensor (as shown in Figure 1 08) for being arranged on compressor tonifying Qi porch Tonifying Qi temperature t₈。

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}With the tonifying Qi temperature t according to compressor tonifying Qi entrance₈Generation fills into the gaseous refrigerant enthalpy of compressor 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}。

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}, the end of indoor heat exchanger second refrigerant enthalpy h_{5 refrigerants}And profit 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 h_{8 " lubricating oil}Detailed process.

Wherein, for the refrigerant enthalpy h of gas returning port in compressor_{1 refrigerant}, when the current working of air conditioner is heating condition When, the refrigerant superheat of the gas returning port of compressor can combine the refrigerant enthalpy h that suction superheat calculates gas returning port_{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 outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃；According to gas returning port temperature t₁With outdoor heat exchanger middle portion temperature t₃Generate suction superheat Δ t₁；According to suction superheat Δ t₁With outdoor heat exchanger middle part Temperature t₃Generate the modifying factor D of gas returning port refrigerant enthalpy₁；According to outdoor heat exchanger middle portion temperature t₃Generate under suction temperature The enthalpy h of saturation refrigerant_{Air-breathing saturation}；According to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigerant under suction temperature Enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy h of gas returning port_{1 refrigerant}。

Further, the enthalpy h of saturation refrigerant under suction temperature is generated according to following formula (6)_{Air-breathing saturation}：

Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (7)₁：

Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t₃, then according to gas returning port temperature t₁With outdoor heat exchanger middle portion temperature t₃Generate suction superheat Δ t₁=t₁-t₃, and according to suction superheat Δ t₁With outdoor heat exchanger middle portion temperature t₃Generate the amendment of gas returning port refrigerant enthalpy Factor D₁, such as shown in above-mentioned formula (7), while according to outdoor heat exchanger middle portion temperature t₃Generate saturation refrigerant under suction temperature Enthalpy h_{Air-breathing saturation}, such as shown in above-mentioned formula (6).Finally, according to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigeration The enthalpy h of agent_{Air-breathing saturation}Generate refrigerant enthalpy h_{1 refrigerant}, h_{1 refrigerant}=D₁·h_{Air-breathing saturation}+d₇, wherein, d₇For the corresponding overheat of refrigerant Fauna 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, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet_{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；According to indoor heat exchange Indoor heat exchanger middle portion temperature t in the middle part of device₆With the exhaust port temperatures t of exhaust outlet in compressor₂Generate discharge superheat Δ t₂； According to discharge superheat Δ t₂With indoor heat exchanger middle portion temperature t₆Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂；According to Indoor heat exchanger middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}；According to exhaust outlet refrigerant enthalpy Modifying factor D₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}。

Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to following formula (8)₂：

Specifically, the temperature sensor (as shown in Figure 1 06) being disposed in the interior in the middle part of heat exchanger can be first passed through and obtain room Interior heat exchanger middle portion temperature t₆, then according to the exhaust port temperatures t of exhaust outlet in compressor₂With indoor heat exchanger middle portion temperature t₆ Generate discharge superheat Δ t₂=t₂-t₆, and according to discharge superheat Δ t₂With indoor heat exchanger middle portion temperature t₆Generate exhaust outlet The modifying factor D of refrigerant enthalpy₂, such as shown in above-mentioned formula (8), meanwhile, according to indoor heat exchanger middle portion temperature t₆Generation exhaust At a temperature of saturation refrigerant enthalpy h_{It is vented saturation},Wherein, a₁-a₅For refrigerant pair The saturation region coefficient answered.Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy Value 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, d₇For the corresponding mistake of refrigerant Hot-zone coefficient.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end_{7 refrigerants}, when the current working of air conditioner is to heat During operating mode, the refrigerant superheat of indoor heat exchanger first end can combine position refrigerant superheat degree 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；According to degree of superheat Δ t₇And indoor heat exchanger Middle portion temperature t₆Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇；Freezed according to indoor heat exchanger first end The modifying factor D of agent enthalpy₇, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the system of indoor heat exchanger first end Cryogen enthalpy h_{7 refrigerants}。

Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to following formula (9)₇：

Specifically, can be first according to indoor heat exchanger first end temperature t₇With indoor heat exchanger middle portion temperature t₆Generation overheat Spend Δ t₇=t₇-t₆, then according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger first end refrigeration The modifying factor D of agent enthalpy₇, such as shown in above-mentioned formula (9), meanwhile, according to indoor heat exchanger middle portion temperature t₆Generate delivery temperature The enthalpy h of lower saturation refrigerant_{It is vented saturation},Wherein, a₁-a₅It is corresponding for refrigerant Saturation region coefficient.Finally, according to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy of generation₇Under delivery temperature The enthalpy h of saturation refrigerant_{It is vented saturation}Generate refrigerant enthalpy h_{7 refrigerants}, h_{7 refrigerants}=D₇·h_{It is vented saturation}+d₇, wherein, d₇For refrigerant pair The overheated zone coefficient answered.

For the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}, when the current working of air conditioner is heating condition, The refrigerant supercooling at the end of indoor heat exchanger second, can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}。

According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to following formula (10) Value h_{5 refrigerants}：

The species of the corresponding saturation region coefficient of above-mentioned refrigerant, overheated zone coefficient and supercooling fauna number and refrigerant has Close, R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, overheated zone coefficient are respectively illustrated in table 1 and cold-zone is crossed Coefficient.Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, to calculate each temperature detection The refrigerant enthalpy of point.

It should be noted that in other embodiments of the invention, can also directly invoke the result of calculation of software, or pass through Other approach obtain the refrigerant enthalpy of each temperature detecting point.For example, when the current working of air conditioner is heating condition When, low pressure that can also be in air conditioner, gas returning port temperature t₁, the second end of indoor heat exchanger temperature t₅Respectively obtain return-air The refrigerant enthalpy h of mouth_{1 refrigerant}With the refrigerant enthalpy h at the end of indoor heat exchanger second_{5 refrigerants}, and can be in air conditioner high pressure Pressure, exhaust port temperatures t₂, indoor heat exchanger first end temperature t₇Respectively obtain the refrigerant enthalpy h of exhaust outlet_{2 refrigerants}And interior The refrigerant enthalpy h of heat exchanger first end_{7 refrigerants}, and saturated air under the state can be obtained according to tonifying Qi temperature or pressure Body enthalpy h_{8 ' refrigerants}And saturated liquid enthalpy h_{8 " refrigerants}。

In addition, for the lubricating oil enthalpy h of each temperature detecting point_{I lubricating oil}, can be calculated according to below equation：

h_{I lubricating oil}=-0.0808+1.7032t_i+0.0025t² _i,

Wherein, i is positive integer, t_iFor the temperature of temperature detecting point.Thus, the lubricating oil enthalpy for obtaining out gas returning port can be calculated Value h_{1 lubricating oil}, exhaust outlet lubricating oil enthalpy h_{2 lubricating oil}, the end of indoor heat exchanger second lubricating oil enthalpy h_{5 lubricating oil}And indoor heat exchanger The lubricating oil enthalpy h of first end_{7 lubricating oil}, fill into compressor and lubricating oil enthalpy h_{8 ' lubricating oil}, flash vessel lubricating oil enthalpy h_{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}The indoor heat exchange of generation The mixture enthalpy h of device first end₇, according to the gaseous refrigerant enthalpy h for filling into compressor_{8 ' refrigerants}With lubricating oil enthalpy h_{8 ' lubricating oil}It is raw Into filling into compressor mixture enthalpy h_8’, according to the liquid refrigerant enthalpy h of flash vessel_{8 " refrigerants}With lubricating oil enthalpy h_{8 " lubricating oil}It is raw Into the mixture enthalpy h of flash vessel_8”。

Specifically, the mixture enthalpy h of each point can be calculated according to below equation_i：

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

C_g=f/10⁴

Wherein, C_gFor mixture oil content, f is the running frequency of compressor.Thus, it can calculate and obtain out the mixed of gas returning port Compound enthalpy h₁, exhaust outlet mixture enthalpy h₂, the end of indoor heat exchanger second mixture enthalpy h₅, indoor heat exchanger first The mixture enthalpy h at end₇, fill into compressor mixture enthalpy h_8’With the mixture enthalpy h of flash vessel_8”。

S205, the power of compressor is obtained according to the current frequency of compressor and preset compressor performance curve.

S206, 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 second₅With 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”Generate the heating capacity of air conditioner.

Specifically, the heating capacity of air conditioner can be generated according to equation below：

Wherein, Q_{Heating capacity}For the air conditioner system Heat, P_comFor compressor horsepower.

S207, the efficiency of air conditioner is generated according to air conditioner power consumption and heating capacity.

Because the current working of air conditioner is heating condition, thus it 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 heating capacity and power consumption of air conditioner, i.e. COP= Q_{Heating capacity}/P_{Power consumption}。

, can also be according to the 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 can not only save, additionally it is possible to improve the comfortableness of user.

The air conditioner of the embodiment of the present invention, including memory, processor and store on a memory and can be on a processor The computer program of operation, during computing device computer program, can be achieved a kind of air-conditioning that the above embodiment of the present invention is proposed The efficiency computational methods of device.

Air conditioner according to embodiments of the present invention, can real-time and accurately detect to efficiency, be easy to according to real-time energy Effect optimization running status, reaches energy-conservation and improves the purpose of heating effect.

The non-transitorycomputer readable storage medium of the embodiment of the present invention, is stored thereon with computer program, the calculating When machine program is executed by processor, a kind of efficiency computational methods for air conditioner that the above embodiment of the present invention is proposed can be achieved.

In summary, the air conditioner of the embodiment of the present invention and its efficiency computational methods and system, by obtaining air conditioner system The physical property of refrigerant in refrigerant cycle system, and the power for obtaining air conditioner is calculated according to the physical property of refrigerant, with And the efficiency for obtaining air conditioner is further calculated, so as to be able to real-time and accurately detect the refrigeration efficiency of air conditioner and heat energy Effect.

In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom ", " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, is for only for ease of the description present invention and simplifies description, rather than indicate or imply that the device or element of meaning 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 indicating or implying relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express 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 to 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 are directly contacted, 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 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 to combine specific features, structure, material or the spy that the embodiment or example are described Point is contained at least one embodiment of the present invention or example.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 not be the same as Example or the feature of example and non-be the same as Example 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 current frequency of compressor and the air conditioner power consumption 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；

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}With the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into the gaseous state of compressor 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}；

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’, according to the liquid refrigerant enthalpy h of the flash vessel_{8 " refrigerants}And lubrication Oily enthalpy h_{8 " lubricating oil}Generate the mixture enthalpy h of flash vessel_8”；

The power of the compressor is obtained according to the current frequency of the compressor and preset compressor performance curve；

According to the power of the compressor, the 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 according to gas returning port in the compressor Gas returning port temperature t₁Generate 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}The generation refrigeration Agent enthalpy h_{1 refrigerant}。

3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that inhaled according to below equation generation is described 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：

D₁=1+d₁Δt₁+d₂(Δt₁)²+d₃(Δt₁)t₆+d₄(Δt₁)²t₆+d₅(Δt₁)t² ₆+d₆(Δt₁)²t² ₆,

5. the efficiency computational methods of air conditioner as claimed in claim 3, it is characterised in that according to the indoor heat exchanger first The indoor heat exchanger first end temperature t at end₇Generate the refrigerant enthalpy h of the indoor heat exchanger first end_{7 refrigerants}Specifically 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>

7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to exhaust outlet in the compressor Exhaust port temperatures t₂Generate the enthalpy h of the refrigerant of the exhaust 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>

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}：

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

Wherein, Q_{Refrigerating capacity}Freeze for the air conditioner Amount, P_comFor compressor horsepower.

11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that each is calculated according to below equation 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 each is calculated according to below equation 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

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, is realized 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, indoor heat exchange The second end of indoor heat exchanger temperature t at the end of device second₅, indoor heat exchanger first end indoor heat exchanger first end temperature t₇And pressure The tonifying Qi temperature t of contracting machine tonifying Qi entrance₈；

When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor₁It is raw Into the refrigerant enthalpy h of gas returning 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}With the tonifying Qi temperature t according to the compressor tonifying Qi entrance₈Generation fills into the gas of compressor State 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}；

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 ' refrigerants}And lubrication Oily enthalpy h_{8 ' lubricating oil}Generation fills into compressor mixture enthalpy h_8’, according to the liquid refrigerant enthalpy h of 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 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 according to return-air in the compressor The gas returning port temperature t of mouth₁Generate 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 below equation generation 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 below equation generation 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>

19. the efficiency computational methods of air conditioner as claimed in claim 16, it is characterised in that be vented according in the compressor The exhaust port temperatures t of mouth₂Generate the enthalpy h of the refrigerant of the exhaust 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 indoor 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>

21. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that according to the indoor heat exchanger The indoor heat exchanger first end temperature t of one end₇The refrigerant enthalpy h of the indoor heat exchanger first end is generated respectively_{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 of the indoor heat exchanger first end_{7 refrigerants}。

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

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

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

Wherein, Q_{Heating capacity}For the air conditioner heat-production Amount, P_comFor compressor horsepower.

25. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that each is calculated according to below equation 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 each is calculated according to below equation 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

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, is realized 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.