CN107328054A

CN107328054A - Air conditioner and its efficiency computational methods

Info

Publication number: CN107328054A
Application number: CN201710775561.2A
Authority: CN
Inventors: 杨亚新; 张�浩; 刘燕飞; 徐振坤
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, the efficiency computational methods comprise the following steps：Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；Obtain gas returning port in compressor, exhaust outlet, outdoor heat exchanger first end, the temperature t in the middle part of indoor heat exchanger₁、t₂、t₄、t₆With indoor environment temperature t₉；According to t₆And t₉Generate the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇；When the current working of air conditioner is cooling condition, respectively according to t₁、t₂、t₄And t₇The refrigerant enthalpy h of correspondence generation gas returning port₁, exhaust outlet refrigerant enthalpy h₂, outdoor heat exchanger first end refrigerant enthalpy h₄With the refrigerant enthalpy h of indoor heat exchanger first end₇；According to the power of compressor, h₁、h₂、h₄And h₇Generate the refrigerating capacity of air conditioner；And the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Description

Air conditioner and its efficiency computational methods

Technical field

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

Background technology

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 One purpose is the efficiency computational methods for proposing a kind of air conditioner, can real-time and accurately detect the efficiency of air conditioner.

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

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

Fourth object of the present invention is the efficiency 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 include Following steps：Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；Obtain gas returning port in compressor Gas returning port temperature t₁, in the compressor exhaust outlet exhaust port temperatures t₂, outdoor heat exchanger first end outdoor heat exchanger One end temperature t₄, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆With indoor environment temperature t₉；Changed according to the interior Hot device middle portion temperature t₆With indoor environment temperature t₉Generate the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇；When 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 compressor₁Generate return-air The refrigerant enthalpy h of mouth₁, according to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the refrigerant enthalpy h of exhaust outlet₂, According to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end₄Generate the refrigerant of outdoor heat exchanger first end Enthalpy h₄With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end₇Generate indoor heat exchanger first end Refrigerant enthalpy h₇；According to the power of the compressor, the refrigerant enthalpy h of the gas returning port₁, exhaust outlet refrigerant enthalpy h₂, outdoor heat exchanger first end refrigerant enthalpy h₄With the refrigerant enthalpy h of indoor heat exchanger first end₇Generate air conditioner Refrigerating capacity；And the efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.

The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The power and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet, outdoor heat exchanger first end and interior and change The temperature of hot device first end, and air conditioner be in cooling condition when according to the temperature of each above-mentioned position generate it is above-mentioned each The refrigerant enthalpy of position, the refrigerant enthalpy and air conditioner power consumption work(of power, each above-mentioned position then in conjunction with compressor Rate obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air conditioner Real-time energy efficiency optimizes the running status of air conditioner, reaches energy-conservation and improves the purpose of refrigeration.

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

According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in the compressor₁Generate gas returning port Refrigerant enthalpy h₁Specifically include：According to the gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Generate suction superheat Spend Δ t₁；According to the suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Generate the amendment of gas returning port refrigerant enthalpy Factor D₁；According to the indoor heat exchanger middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}；According to institute State the modifying factor D of gas returning port refrigerant enthalpy₁, the saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy h₁。 Further, the enthalpy h of saturation refrigerant under 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 enthalpy h of saturation refrigerant under 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 gas returning port refrigerant enthalpy is generated according to below equation₁：

D₁=1+d₁Δt₁+d₂(Δt₁)²+d₃(Δt₁)t₆+d₄(Δt₁)²t₆+d₅(Δt₁)t² ₆+d₆(Δt₁)²t² ₆, wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.

Further, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end₇The indoor heat exchange of generation The refrigerant enthalpy h of device first end₇Specifically 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 t₆Generation is indoor The modifying factor D of heat exchanger first end refrigerant enthalpy₇；According to the modifying factor of the indoor heat exchanger first end refrigerant enthalpy Sub- D₇With the enthalpy h of the saturation refrigerant_{Air-breathing saturation}Generate the refrigerant enthalpy h₇。

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

Wherein, d₁-d₆ For the corresponding overheated zone coefficient of refrigerant.

According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor₂Generation institute State the refrigerant enthalpy h of exhaust outlet₂Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃；According to institute State the exhaust port temperatures t of exhaust outlet in compressor₂With the outdoor heat exchanger middle portion temperature t₃Generate discharge superheat Δ t₂；Root According to the discharge superheat Δ t₂With the outdoor heat exchanger middle portion temperature t₃Generate the modifying factor of exhaust outlet refrigerant enthalpy D₂：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 row The modifying factor D of gas port refrigerant enthalpy₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the exhaust outlet Refrigerant enthalpy h₂。

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

D₂=1+d₁Δt₂+d₂(Δt₂)²+d₃(Δt₂)t₃+d₄(Δt₂)²t₃+d₅(Δt₂)t² ₃+d₆(Δt₂)²t² ₃, wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.

According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation Value h₄：

Wherein, c₁-c₄For the corresponding supercooling fauna number of refrigerant.

According to one embodiment of present invention, the refrigerating capacity of air conditioner is generated according to below equation：Wherein, Q_{Refrigerating capacity}For the refrigerating capacity of the air conditioner, P_CompressorFor the power of compressor.

According to one embodiment of present invention, the indoor heat exchange of the indoor heat exchanger first end is generated by below equation Device first end temperature t₇：

t₇=a*t₉+b*t₆+ c*f, wherein, f is compressor operating frequency, a, and b, c is fitting coefficient.

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.

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 bag for another air conditioner that fourth aspect present invention embodiment is proposed Include following steps：Obtain current working, the power of compressor and the air conditioner power consumption of air conditioner；Obtain return-air in compressor The gas returning port temperature t of mouth₁, in the compressor exhaust outlet exhaust port temperatures t₂, the end of indoor heat exchanger second indoor heat exchanger Second end temperature t₅, indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆With indoor environment temperature t₉；According to the interior Heat exchanger middle portion temperature t₆With indoor environment temperature t₉Generate the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇； When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor₁Generate back The refrigerant enthalpy h of gas port₁, according to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the refrigerant enthalpy of exhaust outlet h₂, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second₅Generate the refrigeration at the end of indoor heat exchanger second Agent enthalpy h₅With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end₇Generate indoor heat exchanger first end Refrigerant enthalpy h₇；According to the power of the compressor, the refrigerant enthalpy h of the gas returning port₁, exhaust outlet refrigerant enthalpy Value h₂, the end of indoor heat exchanger second refrigerant enthalpy h₅With the refrigerant enthalpy h of indoor heat exchanger first end₇Generate air conditioner Heating capacity；And the efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.

The efficiency computational methods of air conditioner according to embodiments of the present invention, by the current working, the compression that obtain air conditioner The power and air conditioner power consumption of machine, and obtain gas returning port in compressor, exhaust outlet, the end of indoor heat exchanger second and interior and change The temperature of hot device first end, and air conditioner be in heating condition when according to the temperature of each above-mentioned position generate it is above-mentioned each The refrigerant enthalpy of position, the refrigerant enthalpy and air conditioner power consumption work(of power, each above-mentioned position then in conjunction with compressor Rate obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air conditioner Real-time energy efficiency optimizes the running status of air conditioner, reaches energy-conservation and improves the purpose of heating effect.

According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor₁Generate back The refrigerant enthalpy h of gas port₁Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃；According to described time Gas port temperature t₁With the outdoor heat exchanger middle portion temperature t₃Generate suction superheat Δ t₁；According to the suction superheat Δ t₁ With the outdoor heat exchanger middle portion temperature t₃Generate the modifying factor D of gas returning port refrigerant enthalpy₁；According to the outdoor heat exchanger Middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}；According to the amendment of the gas returning port refrigerant enthalpy Factor D₁, under the suction temperature saturation refrigerant enthalpy h_{Air-breathing saturation}Generate the refrigerant enthalpy h of the gas returning port₁。

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

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.

Further, the exhaust port temperatures t according to exhaust outlet in the compressor₂Generate the refrigeration of the exhaust outlet Agent enthalpy h₂Specifically include：According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆Arranged with the compressor The exhaust port temperatures t of gas port₂Generate discharge superheat Δ t₂；According to the discharge superheat Δ t₂In the indoor heat exchanger Portion temperature t₆Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂；According in the indoor heat exchanger in the middle part of the indoor heat exchanger Portion temperature t₆Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}；According to the modifying factor of the exhaust outlet refrigerant enthalpy Sub- D₂, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigerant enthalpy h of the exhaust outlet₂。

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

D₂=1+d₁Δt₂+d₂(Δt₂)²+d₃(Δt₂)t₆+d₄(Δt₂)²t₆+d₅(Δt₂)t² ₆+d₆(Δt₂)²t² ₆, wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.

Further, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end₇The indoor heat exchange of generation The refrigerant enthalpy h of device first end₇Specifically include：According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆With The indoor heat exchanger first end temperature t₇Generate degree of superheat Δ t₇；According to the degree of superheat Δ t₇In the indoor heat exchanger Portion temperature t₆Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇；According to the indoor heat exchanger first end system The modifying factor D of cryogen enthalpy₇, under the delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the indoor heat exchanger The refrigerant enthalpy h of one end₇。

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, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation Value h₅：

h₅=c₁+c₂t₅+c₃t² ₅+c₄t³ ₅, wherein, c₁-c₄For the corresponding supercooling fauna number of refrigerant.

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

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

t₇=a*t₉+b*t₆+ c*f, wherein, f be the compressor running frequency, a, b, c is fitting coefficient.

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 flow chart of the efficiency computational methods of the air conditioner according to the embodiment of the present invention；

Fig. 2 is the structural representation of the air conditioner according to one embodiment of the invention；

Fig. 3 is the block diagram of the efficiency computing system of the air conditioner according to the embodiment of the present invention；

Fig. 4 is the flow chart of the efficiency computational methods of another air conditioner according to the embodiment of the present invention；

Fig. 5 is the block diagram of the efficiency computing system 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.

Fig. 1 is the flow chart of the efficiency computational methods of the air conditioner according to the embodiment of the present invention.

As shown in figure 1, the efficiency computational methods of the air conditioner of the embodiment of the present invention, comprise the following steps：

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

The current working of air conditioner, the power P of compressor can be monitored in real time by the electric-control system of air conditioner_CompressorAnd air-conditioning Device 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 middle portion temperature t in the middle part of indoor heat exchanger₆With Indoor environment temperature t₉。

The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor, four-way valve, outdoor heat exchanger, restricting element and indoor heat exchanger.

In one embodiment of the invention, can be by setting temperature sensor to detect respectively in corresponding temperature test point The temperature of the temperature detecting point.Specifically, as shown in Fig. 2 can be by setting gas returning port temperature to pass at gas returning port within the compressor Sensor is to detect gas returning port temperature t₁, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t₂, at outdoor heat exchanger first end outdoor heat exchanger first end temperature sensor is set to detect outdoor heat exchanger first end temperature Spend t₄, indoors set indoor heat exchanger middle portion temperature sensor in the middle part of heat exchanger to detect indoor heat exchanger middle portion temperature t₆With And at heat exchanger fin indoor temperature transmitter is set to detect indoor environment temperature t indoors₉。

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, according to indoor heat exchanger middle portion temperature t₆With indoor environment temperature t₉Generate the room of indoor heat exchanger first end Interior heat exchanger first end temperature t₇。

In one embodiment of the invention, the indoor heat exchanger of indoor heat exchanger first end can be generated by below equation First end temperature t₇：

S104, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor₁ Generate the refrigerant enthalpy h of gas returning port₁, according to the exhaust port temperatures t of exhaust outlet in compressor₂Generate the refrigerant enthalpy of exhaust outlet Value h₂, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end₄Generate the refrigerant of outdoor heat exchanger first end Enthalpy h₄With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end₇Generate the refrigeration of indoor heat exchanger first end Agent enthalpy h₇。

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

Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point It is different.In one embodiment of the invention, rule of thumb the enthalpy for obtaining refrigerant can be calculated by formula.

Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below₁, exhaust outlet refrigerant enthalpy h₂、 The refrigerant enthalpy h of outdoor heat exchanger first end₄With the refrigerant enthalpy h of indoor heat exchanger first end₇Detailed process.

For the refrigerant enthalpy h of gas returning port in compressor₁, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the gas returning port of machine, can combine the refrigerant enthalpy h that suction superheat calculates gas returning port₁。

Specifically, can be according to gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Generate suction superheat Δ t₁, and root According to suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Generate the modifying factor D of gas returning port refrigerant enthalpy₁, Yi Jigen According to indoor heat exchanger middle portion temperature t₆Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}.Wherein, suction superheat Δ t₁ For gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Difference, i.e. Δ t₁=t₁-t₆.The modifying factor of gas returning port refrigerant enthalpy Sub- D₁=1+d₁Δt₁+d₂(Δt₁)²+d₃(Δt₁)t₆+d₄(Δt₁)²t₆+d₅(Δt₁)t² ₆+d₆(Δt₁)²t² ₆, wherein, d₁-d₆For The corresponding overheated zone coefficient of refrigerant.The enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}=a₁+a₂t₆+a₃t² ₆+a₄t³ ₆+a₅, Wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.

In the modifying factor D of generation gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy h_{Air-breathing saturation}Afterwards, can further root According to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy h_{Air-breathing saturation}Generate refrigerant enthalpy h₁, h₁=D₁· h_{Air-breathing saturation}+d₇, wherein, d₇For the corresponding overheated zone coefficient of refrigerant.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end₇, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end can combine the position refrigerant superheat degree and calculate indoor heat exchanger first The refrigerant enthalpy h at end₇。

Specifically, can be according to indoor heat exchanger first end temperature t₇With indoor heat exchanger middle portion temperature t₆Generated Temperature Δ t₇, and according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger first end system The modifying factor D of cryogen enthalpy₇, and the indoor heat exchanger first end refrigerant enthalpy according to generation modifying factor D₇ With the enthalpy h of saturation refrigerant_{Air-breathing saturation}Generate refrigerant enthalpy h₇.Wherein, Δ t₇=t₇-t₆,h₇=D₇·h_{Air-breathing saturation}+d₇, its In, d₁-d₇For the corresponding overheated zone coefficient of refrigerant.

For the refrigerant enthalpy h of exhaust outlet in compressor₂, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the exhaust outlet of machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet₂。

Specifically, the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger can be obtained₃, wherein, as shown in Fig. 2 outdoor Outdoor heat exchanger middle portion temperature t in the middle part of heat exchanger₃Temperature in the middle part of the outdoor heat exchanger that is set in the middle part of outdoor heat exchanger can be passed through Degree sensor detection is obtained.

Then, can be according to the exhaust port temperatures t of exhaust outlet in compressor₂With outdoor heat exchanger middle portion temperature t₃Generation exhaust Degree of superheat Δ t₂, and according to discharge superheat Δ t₂With outdoor heat exchanger middle portion temperature t₃Generate repairing for exhaust outlet refrigerant enthalpy Positive divisor D₂, and according to outdoor heat exchanger middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}.Wherein, Discharge superheat Δ t₂For the exhaust port temperatures t of exhaust outlet in compressor₂With outdoor heat exchanger middle portion temperature t₃Difference, i.e. Δ t₂ =t₂-t₃.The modifying factor D of exhaust outlet refrigerant enthalpy₂=1+d₁Δt₂+d₂(Δt₂)²+d₃(Δt₂)t₃+d₄(Δt₂)²t₃+d₅ (Δt₂)t² ₃+d₆(Δt₂)²t² ₃, wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.Saturation refrigerant under delivery temperature Enthalpy h_{It is vented saturation}=a₁+a₂t₃+a₃t² ₃+a₄t³ ₃+a₅, wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.

In the modifying factor D of generation exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Afterwards, Can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generation The refrigerant enthalpy h of exhaust outlet₂, h₂=D₂·h_{It is vented saturation}+d₇, wherein, d₇For the corresponding overheated zone coefficient of refrigerant.

For the refrigerant enthalpy h of outdoor heat exchanger first end₄, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end₄：Wherein, c₁-c₄For the corresponding supercooling fauna number of refrigerant.

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.

In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is cooling condition Adjust low pressure, the gas returning port temperature t in device₁, indoor heat exchanger first end temperature t₇Respectively obtain the refrigerant enthalpy of gas returning port h₁With the refrigerant enthalpy h of indoor heat exchanger first end₇, and can be in air conditioner high-pressure, exhaust port temperatures t₂, room External heat exchanger first end temperature t₄Respectively obtain the refrigerant enthalpy h of exhaust outlet₂With the refrigerant enthalpy of outdoor heat exchanger first end h₄。

S105, according to the power of compressor, the refrigerant enthalpy h of gas returning port₁, exhaust outlet refrigerant enthalpy h₂, outdoor changes The refrigerant enthalpy h of hot device first end₄With the refrigerant enthalpy h of indoor heat exchanger first end₇Generate the refrigerating capacity of air conditioner.

Specifically, the refrigerating capacity of air conditioner can be generated according to below equation：Wherein, Q_{Refrigerating capacity} For Air conditioner refrigerating capacity, P_CompressorFor compressor horsepower.

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

Because the current working of air conditioner is cooling condition, thus 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.

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.

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

As shown in figure 3, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port temperature sensor 01, Exhaust port temperatures sensor 02, outdoor heat exchanger first end temperature sensor 04, indoor heat exchanger middle portion temperature sensor 06, room Interior temperature sensor 09 and indoor heat exchanger first end temperature generation module 00, acquisition module 10, refrigerant enthalpy generation mould Block 20, refrigerating capacity generation module 30, efficiency generation module 40.

Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor₁；Exhaust outlet temperature Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor₂；Outdoor heat exchanger first end temperature sensor 04 is used In the outdoor heat exchanger first end temperature t for obtaining outdoor heat exchanger first end₄；Indoor heat exchanger middle portion temperature sensor 06 is used for Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆；Indoor temperature transmitter 09 is used to obtain indoor environment temperature t₉。

The air conditioner of the embodiment of the present invention can be single-stage vapor compression formula air conditioner, as shown in Fig. 2 the embodiment of the present invention Air conditioner may include compressor 100, four-way valve 200, outdoor heat exchanger 300, restricting element 400 and indoor heat exchanger 500.

As shown in Fig. 2 at the settable gas returning port within the compressor of gas returning port temperature sensor 01, exhaust port temperatures sensor 02 settable exhaust ports within the compressor, outdoor heat exchanger first end temperature sensor 04 may be provided at outdoor heat exchanger first End, indoor heat exchanger middle portion temperature sensor 06 can be set in the middle part of indoor heat exchanger, and indoor temperature transmitter 09 may be provided at room At interior heat exchanger fin.Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, and right Refrigerant tube wall, especially sets the position of temperature sensor to take Insulation.For example, temperature sensor can be close into copper pipe Set, 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.

Indoor heat exchanger first end temperature generation module 00 is used for according to indoor heat exchanger middle portion temperature t₆And indoor environment Temperature t₉Generate the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇；Acquisition module 10 is used to obtain air conditioner Current working, the power of compressor and air conditioner power consumption；Refrigerant enthalpy generation module 20 is used to work as the current of air conditioner When operating mode is cooling condition, according to the gas returning port temperature t of gas returning port in compressor₁Generate the refrigerant enthalpy h of gas returning port₁, according to The exhaust port temperatures t of exhaust outlet in compressor₂Generate the refrigerant enthalpy h of exhaust outlet₂, according to the room of outdoor heat exchanger first end External heat exchanger first end temperature t₄Generate the refrigerant enthalpy h of outdoor heat exchanger first end₄With according to indoor heat exchanger first end Indoor heat exchanger first end temperature t₇Generate the refrigerant enthalpy h of indoor heat exchanger first end₇；Refrigerating capacity generation module 30 is used for According to the power of compressor, the refrigerant enthalpy h of gas returning port₁, exhaust outlet refrigerant enthalpy h₂, outdoor heat exchanger first end Refrigerant enthalpy h₄With the refrigerant enthalpy h of indoor heat exchanger first end₇Generate the refrigerating capacity of air conditioner；Efficiency generation module 40 Efficiency for generating air conditioner according to air conditioner power consumption and refrigerating capacity.

Wherein, indoor heat exchanger first end temperature generation module 00, acquisition module 10, refrigerant enthalpy generation module 20, Refrigerating capacity generation module 30 and efficiency generation module 40 may be disposed in the electric-control system of air conditioner.Acquisition module 10 can be supervised in real time Survey current working, the power P of compressor of air conditioner_CompressorWith air conditioner power consumption P_{Power consumption}。

In one embodiment of the invention, indoor heat exchanger first end temperature generation module 00 can be given birth to by below equation Into the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇：

Because the state of the refrigerant of different temperatures test point is different, therefore the enthalpy of the refrigerant of different temperatures test point It is different.In one embodiment of the invention, refrigerant enthalpy generation module 20 rule of thumb formula calculating can obtain refrigerant Enthalpy.

Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below₁、 The refrigerant enthalpy h of exhaust outlet₂, outdoor heat exchanger first end refrigerant enthalpy h₄With the refrigerant of indoor heat exchanger first end Enthalpy h₇Detailed process.

For the refrigerant enthalpy h of gas returning port in compressor₁, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port Enthalpy h₁。

Specifically, refrigerant enthalpy generation module 20 can be according to gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆It is raw Into suction superheat Δ t₁, and according to suction superheat Δ t₁With indoor heat exchanger middle portion temperature t₆Generate gas returning port refrigerant enthalpy The modifying factor D of value₁, and according to indoor heat exchanger middle portion temperature t₆Generate the enthalpy of saturation refrigerant under suction temperature h_{Air-breathing saturation}.Wherein, suction superheat Δ t1 is gas returning port temperature t₁With indoor heat exchanger middle portion temperature t₆Difference, i.e. Δ t₁=t₁- t₆.The modifying factor D of gas returning port refrigerant enthalpy₁=1+d₁Δt₁+d₂(Δt₁)²+d₃(Δt₁)t₆+d₄(Δt₁)²t₆+d₅(Δ t₁)t² ₆+d₆(Δt₁)²t² ₆, wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.The enthalpy of saturation refrigerant under suction temperature Value h_{Air-breathing saturation}=a₁+a₂t₆+a₃t² ₆+a₄t³ ₆+a₅, wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.

In the modifying factor D of generation gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy h_{Air-breathing saturation}Afterwards, refrigerant enthalpy Generation module 20 can be further according to the modifying factor D of gas returning port refrigerant enthalpy₁, saturation refrigerant enthalpy h_{Air-breathing saturation}Generation Refrigerant enthalpy h₁, h₁=D₁·h_{Air-breathing saturation}+d₇, wherein, d₇For the corresponding overheated zone coefficient of refrigerant.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end₇, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end, refrigerant enthalpy generation module 20 can combine the position refrigerant superheat Degree calculates the refrigerant enthalpy h of indoor heat exchanger first end₇。

Specifically, refrigerant enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t₇In indoor heat exchanger Portion temperature t₆Generate degree of superheat Δ t₇, and according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger the The modifying factor D of one end refrigerant enthalpy₇, and the indoor heat exchanger first end refrigerant enthalpy according to generation amendment Factor D₇With the enthalpy h of saturation refrigerant_{Air-breathing saturation}Generate refrigerant enthalpy h₇.Wherein, Δ t₇=t₇-t₆,h₇=D₇·h_{Air-breathing saturation}+d₇, its In, d₁-d₇For the corresponding overheated zone coefficient of refrigerant.

For the refrigerant enthalpy h of exhaust outlet in compressor₂, when the current working of air conditioner is cooling condition, compression The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet Enthalpy h₂。

Specifically, the outdoor heat exchanger in the middle part of outdoor heat exchanger can be obtained by outdoor heat exchanger middle portion temperature sensor 03 Middle portion temperature t₃, wherein, as shown in Fig. 2 outdoor heat exchanger middle portion temperature sensor 03 may be provided in the middle part of outdoor heat exchanger.

Then, refrigerant enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor₂And outdoor heat exchange Device middle portion temperature t₃Generate discharge superheat Δ t₂, and according to discharge superheat Δ t₂With outdoor heat exchanger middle portion temperature t₃Generation The modifying factor D of exhaust outlet refrigerant enthalpy₂, and according to outdoor heat exchanger middle portion temperature t₃Generate saturation system under delivery temperature The enthalpy h of cryogen_{It is vented saturation}.Wherein, discharge superheat Δ t₂For the exhaust port temperatures t of exhaust outlet in compressor₂And outdoor heat exchanger Middle portion temperature t₃Difference, i.e. Δ t₂=t₂-t₃.The modifying factor D of exhaust outlet refrigerant enthalpy₂=1+d₁Δt₂+d₂(Δt₂)²+d₃ (Δt₂)t₃+d₄(Δt₂)²t₃+d₅(Δt₂)t² ₃+d₆(Δt₂)²t² ₃, wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.Row The enthalpy h of saturation refrigerant at a temperature of gas_{It is vented saturation}=a₁+a₂t₃+a₃t² ₃+a₄t³ ₃+a₅, wherein, a₁-a₅It is corresponding full for refrigerant With fauna number.

In the modifying factor D of generation exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Afterwards, Refrigerant enthalpy generation module 20 can be further according to the modifying factor D of exhaust outlet refrigerant enthalpy₂, saturation system under delivery temperature The enthalpy h of cryogen_{It is vented saturation}Generate the refrigerant enthalpy h of exhaust outlet₂, h₂=D₂·h_{It is vented saturation}+d₇, wherein, d₇It is corresponding for refrigerant Overheated zone coefficient.

For the refrigerant enthalpy h of outdoor heat exchanger first end₄, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, refrigerant enthalpy generation module 20 can directly calculate the system of outdoor heat exchanger first end Cryogen enthalpy h₄：Wherein, c₁-c₄For the corresponding supercooling fauna number of refrigerant.

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.

In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software Really, or by other approach the refrigerant enthalpy of each temperature detecting point is obtained.For example, when the current working of air conditioner is During cooling condition, low pressure that refrigerant enthalpy generation module 20 can also be in air conditioner, gas returning port temperature t₁, interior changes Hot device first end temperature t₇Respectively obtain the refrigerant enthalpy h of gas returning port₁With the refrigerant enthalpy h of indoor heat exchanger first end₇, And can be in air conditioner high-pressure, exhaust port temperatures t₂, outdoor heat exchanger first end temperature t₄Respectively obtain exhaust outlet Refrigerant enthalpy h₂With the refrigerant enthalpy h of outdoor heat exchanger first end₄。

In an embodiment of the present invention, refrigerating capacity generation module 30 can generate the refrigerating capacity of air conditioner according to below equation：Wherein, Q_{Refrigerating capacity}For Air conditioner refrigerating capacity, P_CompressorFor compressor horsepower.

Because the current working of air conditioner is cooling condition, thus efficiency generation module 40 can be according to air conditioner power consumption The refrigeration efficiency of air conditioner is generated with refrigerating capacity, specifically, the refrigeration efficiency of air conditioner is the refrigerating capacity and power consumption work(of air conditioner The ratio between rate, i.e. EER=Q_{Refrigerating capacity}/P_{Power consumption}。

The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor and air conditioner power consumption, and gas returning port in compressor, exhaust are obtained by corresponding temperature sensor The temperature of mouth, outdoor heat exchanger first end and indoor heat exchanger first end, and pass through system when air conditioner is in cooling condition Cryogen enthalpy generation module, refrigerating capacity generation module and efficiency generation module are above-mentioned each according to the generation of the temperature of each above-mentioned position The refrigerant enthalpy of individual position, the refrigerant enthalpy of power, each above-mentioned position then in conjunction with compressor and air conditioner power consumption Power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air conditioner Real-time energy efficiency optimize air conditioner running status, reach energy-conservation and improve refrigeration purpose.

The air conditioner and its efficiency computational methods and system of above-described embodiment can detect the refrigeration efficiency of air conditioner, for inspection The heat efficiency of air conditioner is surveyed, the present invention also proposes the efficiency computational methods of another air conditioner.

As shown in figure 4, the efficiency computational methods of another air conditioner of the embodiment of the present invention, comprise the following steps：

S401, obtains current working, the power of compressor and the air conditioner power consumption of air conditioner.

S402, 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 middle portion temperature t in the middle part of indoor heat exchanger₆With Indoor environment temperature t₉。

As shown in Fig. 2 gas returning port temperature can be detected by setting gas returning port temperature sensor at gas returning port within the compressor Spend t₁, within the compressor exhaust ports exhaust port temperatures sensor is set to detect exhaust port temperatures t₂, heat exchanger second indoors Indoor heat exchanger the second end temperature sensor is set to detect the second end of indoor heat exchanger temperature t at end₅, indoors in heat exchanger Portion sets indoor heat exchanger middle portion temperature sensor to detect indoor heat exchanger middle portion temperature t₆And heat exchanger fin indoors Place sets indoor temperature transmitter to detect indoor environment temperature t₉。

S403, according to indoor heat exchanger middle portion temperature t₆With indoor environment temperature t₉Generate the room of indoor heat exchanger first end Interior heat exchanger first end temperature t₇。

S404, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor₁ Generate the refrigerant enthalpy h of gas returning port₁, according to the exhaust port temperatures t of exhaust outlet in compressor₂Generate the refrigerant enthalpy of exhaust outlet Value h₂, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second₅Generate the refrigerant at the end of indoor heat exchanger second Enthalpy h₅With the indoor heat exchanger first end temperature t according to indoor heat exchanger first end₇Generate the refrigeration of indoor heat exchanger first end Agent enthalpy h₇。

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

Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below₁, exhaust outlet refrigerant enthalpy h₂、 The refrigerant enthalpy h at the end of indoor heat exchanger second₅With the refrigerant enthalpy h of indoor heat exchanger first end₇Detailed process.

For the refrigerant enthalpy h of gas returning port in compressor₁, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the gas returning port of machine, can combine the refrigerant enthalpy h that suction superheat calculates gas returning port₁。

Then can be according to gas returning port temperature t₁With outdoor heat exchanger middle portion temperature t₃Generate suction superheat Δ t₁, and according to Suction superheat Δ t₁With outdoor heat exchanger middle portion temperature t₃Generate the modifying factor D of gas returning port refrigerant enthalpy₁, and according to Outdoor heat exchanger middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}.Wherein, suction superheat Δ t₁For Gas returning port temperature t₁With outdoor heat exchanger middle portion temperature t₃Difference, i.e. Δ t₁=t₁-t₃.The modifying factor of gas returning port refrigerant enthalpyWherein, d₁-d₆For refrigerant pair The overheated zone coefficient answered.The enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}=a₁+a₂t₃+a₃t² ₃+a₄t³ ₃+a₅, wherein, a₁-a₅ For the corresponding saturation region coefficient of refrigerant.

For the refrigerant enthalpy h of exhaust outlet in compressor₂, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, can combine the refrigerant enthalpy h that discharge superheat calculates exhaust outlet₂。

Specifically, can be according to the exhaust port temperatures t of exhaust outlet in compressor₂With indoor heat exchanger middle portion temperature t₆Generation row Gas degree of superheat Δ t₂, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆Saturation under delivery temperature is generated to freeze The enthalpy h of agent_{It is vented saturation}, and according to discharge superheat Δ t₂With indoor heat exchanger middle portion temperature t₆Generate exhaust outlet refrigerant enthalpy Modifying factor D₂.Wherein, discharge superheat Δ t₂For the exhaust port temperatures t of exhaust outlet in compressor₂With indoor heat exchanger middle part Temperature t₆Difference, i.e. Δ t₂=t₂-t₆.The enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}=a₁+a₂t₆+a₃t² ₆+a₄t³ ₆+a₅, Wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.The modifying factor D of exhaust outlet refrigerant enthalpy₂=1+d₁Δt₂+d₂(Δ t₂)²+d₃(Δt₂)t₆+d₄(Δt₂)²t₆+d₅(Δt₂)t² ₆+d₆(Δt₂)²t² ₆, wherein, d₁-d₆For the corresponding overheated zone of refrigerant Coefficient.

In the modifying factor D of generation exhaust outlet refrigerant enthalpy₂Afterwards, can further repairing according to exhaust outlet refrigerant enthalpy Positive divisor D₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigerant enthalpy h of exhaust outlet₂, h₂=D₂·h_{It is vented saturation} +d₇, wherein, d₇For the corresponding overheated zone coefficient of refrigerant.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end₇, when the current working of air conditioner is to heat work During condition, the refrigerant superheat of indoor heat exchanger first end can combine the position refrigerant superheat degree and calculate indoor heat exchanger first The refrigerant enthalpy h at end₇。

Specifically, can be according to indoor heat exchanger first end temperature t₇With indoor heat exchanger middle portion temperature t₆Generated Temperature Δ t₇, and according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger first end system The modifying factor D of cryogen enthalpy₇, and the indoor heat exchanger first end refrigerant enthalpy according to generation modifying factor D₇ With the enthalpy h of saturation refrigerant_{It is vented saturation}Generate refrigerant enthalpy h₇.Wherein, Δ t₇=t₇-t₆,h₇=D₇·h_{It is vented saturation}+d₇, its In, wherein, d₁-d₇For the corresponding overheated zone coefficient of refrigerant.

For the refrigerant enthalpy h at the end of indoor heat exchanger second₅, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second₅：h₅=c₁+c₂t₅ +c₃t² ₅+c₄t³ ₅, wherein, c₁-c₄For the corresponding supercooling fauna number of refrigerant.

In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is heating condition Adjust high-pressure, the gas returning port temperature t in device₁, indoor heat exchanger first end temperature t₇Respectively obtain the refrigerant enthalpy of gas returning port h₁With the refrigerant enthalpy h of indoor heat exchanger first end₇, and can be in air conditioner high-pressure, exhaust port temperatures t₂, room Interior the second end of heat exchanger temperature t₅Respectively obtain the refrigerant enthalpy h of exhaust outlet₂With the refrigerant enthalpy at the end of indoor heat exchanger second h₅。

S405, according to the power of compressor, the refrigerant enthalpy h of gas returning port₁, exhaust outlet refrigerant enthalpy h₂, interior changes The refrigerant enthalpy h at the hot end of device second₅With the refrigerant enthalpy h of indoor heat exchanger first end₇Generate the heating capacity of air conditioner.

Specifically, the heating capacity of air conditioner can be generated according to below equation：Wherein, Q_{Heating capacity} For heating capacity of air conditioner, P_CompressorFor compressor horsepower.

S406, 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.

Correspondence above-described embodiment, the present invention also proposes another 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 another sky that the above embodiment of the present invention is proposed Adjust the efficiency computational methods of device.

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 another air conditioner that the above embodiment of the present invention is proposed can be achieved.

Correspondence above-described embodiment, the present invention also proposes the efficiency computing system of another air conditioner.

As shown in figure 5, the efficiency computing system of the air conditioner of the embodiment of the present invention, including gas returning port temperature sensor 01, Exhaust port temperatures sensor 02, the second end of indoor heat exchanger temperature sensor 05, indoor heat exchanger middle portion temperature sensor 06, room Interior temperature sensor 09 and indoor heat exchanger first end temperature generation module 00, acquisition module 10, refrigerant enthalpy generation mould Block 20, heating capacity generation module 50, efficiency generation module 40.

Wherein, gas returning port temperature sensor 01 is used for the gas returning port temperature t for obtaining gas returning port in compressor₁；Exhaust outlet temperature Degree sensor 02 is used for the exhaust port temperatures t for obtaining exhaust outlet in compressor₂；The second end of indoor heat exchanger temperature sensor 05 is used In the second end of the indoor heat exchanger temperature t for obtaining the end of indoor heat exchanger second₅；Indoor heat exchanger middle portion temperature sensor 06 is used for Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆；Indoor temperature transmitter 09 is used to obtain indoor environment temperature t₉。

As shown in Fig. 2 at the settable gas returning port within the compressor of gas returning port temperature sensor 01, exhaust port temperatures sensor 02 settable exhaust ports within the compressor, the second end of indoor heat exchanger temperature sensor 05 may be provided at indoor heat exchanger second End, indoor heat exchanger middle portion temperature sensor 06 can be set in the middle part of indoor heat exchanger, and indoor temperature transmitter 09 may be provided at room At interior heat exchanger fin.Wherein, each temperature sensor is effectively contacted with the refrigerant tube wall of corresponding temperature test point, and right Refrigerant tube wall, especially sets the position of temperature sensor to take Insulation.For example, temperature sensor can be close into copper pipe Set, 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.

Indoor heat exchanger first end temperature generation module 00 is used for according to indoor heat exchanger middle portion temperature t₆And indoor environment Temperature t₉Generate the indoor heat exchanger first end temperature t of indoor heat exchanger first end₇；Acquisition module 10 is used to obtain air conditioner Current working, the power of compressor and air conditioner power consumption；Refrigerant enthalpy generation module 20 is used to work as the current of air conditioner When operating mode is heating condition, according to the gas returning port temperature t of gas returning port in compressor₁Generate the refrigerant enthalpy h of gas returning port₁, according to The exhaust port temperatures t of exhaust outlet in compressor₂Generate the refrigerant enthalpy h of exhaust outlet₂, 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 second₅With according to indoor heat exchanger first end Indoor heat exchanger first end temperature t₇Generate the refrigerant enthalpy h of indoor heat exchanger first end₇；Heating capacity generation module 50 is used for According to the power of compressor, the refrigerant enthalpy h of gas returning port₁, exhaust outlet refrigerant enthalpy h₂, indoor heat exchanger second end Refrigerant enthalpy h₅With the refrigerant enthalpy h of indoor heat exchanger first end₇Generate the heating capacity of air conditioner；Efficiency generation module 40 Efficiency for generating air conditioner according to air conditioner power consumption and heating capacity.

Wherein, indoor heat exchanger first end temperature generation module 00, acquisition module 10, refrigerant enthalpy generation module 20, Heating capacity generation module 50 and efficiency generation module 40 may be disposed in the electric-control system of air conditioner.Acquisition module 10 can be supervised in real time Survey current working, the power P of compressor of air conditioner_CompressorWith air conditioner power consumption P_{Power consumption}。

Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port to refrigerant enthalpy generation module 20 separately below₁、 The refrigerant enthalpy h of exhaust outlet₂, the end of indoor heat exchanger second refrigerant enthalpy h₅With the refrigerant of indoor heat exchanger first end Enthalpy h₇Detailed process.

For the refrigerant enthalpy h of gas returning port in compressor₁, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the gas returning port of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that suction superheat calculates gas returning port Enthalpy h₁。

Specifically, refrigerant enthalpy generation module 20 can obtain the outdoor heat exchanger middle portion temperature in the middle part of outdoor heat exchanger t₃, wherein, as shown in Fig. 2 the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger₃Can be by being set in the middle part of outdoor heat exchanger The outdoor heat exchanger middle portion temperature sensor detection put is obtained.

Then refrigerant enthalpy generation module 20 can be according to gas returning port temperature t₁With outdoor heat exchanger middle portion temperature t₃Generation is inhaled Gas degree of superheat Δ t₁, and according to suction superheat Δ t₁With outdoor heat exchanger middle portion temperature t₃Generate gas returning port refrigerant enthalpy Modifying factor D₁, and according to outdoor heat exchanger middle portion temperature t₃Generate the enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}.Its In, suction superheat Δ t₁For gas returning port temperature t₁With outdoor heat exchanger middle portion temperature t₃Difference, i.e. Δ t₁=t₁-t₃.Gas returning port The modifying factor of refrigerant enthalpy Wherein, d₁-d₆For the corresponding overheated zone coefficient of refrigerant.The enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}=a₁+a₂t₃+ a₃t² ₃+a₄t³ ₃+a₅, wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.

For the refrigerant enthalpy h of exhaust outlet in compressor₂, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, refrigerant enthalpy generation module 20 can combine the refrigerant that discharge superheat calculates exhaust outlet Enthalpy h₂。

Specifically, refrigerant enthalpy generation module 20 can be according to the exhaust port temperatures t of exhaust outlet in compressor₂Changed with interior Hot device middle portion temperature t₆Generate discharge superheat Δ t₂, and the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger₆It is raw The enthalpy h of saturation refrigerant under into delivery temperature_{It is vented saturation}, and according to discharge superheat Δ t₂With indoor heat exchanger middle portion temperature t₆ Generate the modifying factor D of exhaust outlet refrigerant enthalpy₂.Wherein, discharge superheat Δ t₂For the exhaust outlet temperature of exhaust outlet in compressor Spend t₂With indoor heat exchanger middle portion temperature t₆Difference, i.e. Δ t₂=t₂-t₆.The enthalpy h of saturation refrigerant under delivery temperature_{It is vented saturation}= a₁+a₂t₆+a₃t² ₆+a₄t³ ₆+a₅, wherein, a₁-a₅For the corresponding saturation region coefficient of refrigerant.The amendment of exhaust outlet refrigerant enthalpy Factor D₂=1+d₁Δt₂+d₂(Δt₂)²+d₃(Δt₂)t₆+d₄(Δt₂)²t₆+d₅(Δt₂)t² ₆+d₆(Δt₂)²t² ₆, wherein, d₁-d₆ For the corresponding overheated zone coefficient of refrigerant.

In the modifying factor D of generation exhaust outlet refrigerant enthalpy₂Afterwards, refrigerant enthalpy generation module 20 can further basis The modifying factor D of exhaust outlet refrigerant enthalpy₂, under delivery temperature saturation refrigerant enthalpy h_{It is vented saturation}Generate the refrigeration of exhaust outlet Agent enthalpy h₂, h₂=D₂·h_{It is vented saturation}+d₇, wherein, d₇For the corresponding overheated zone coefficient of refrigerant.

Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end₇, when the current working of air conditioner is to heat work During condition, the refrigerant superheat of indoor heat exchanger first end, refrigerant enthalpy generation module 20 can combine the position refrigerant superheat Degree calculates the refrigerant enthalpy h of indoor heat exchanger first end₇。

Specifically, refrigerant enthalpy generation module 20 can be according to indoor heat exchanger first end temperature t₇In indoor heat exchanger Portion temperature t₆Generate degree of superheat Δ t₇, and according to degree of superheat Δ t₇With indoor heat exchanger middle portion temperature t₆Generate indoor heat exchanger the The modifying factor D of one end refrigerant enthalpy₇, and the indoor heat exchanger first end refrigerant enthalpy according to generation amendment Factor D₇With the enthalpy h of saturation refrigerant_{It is vented saturation}Generate refrigerant enthalpy h₇.Wherein, Δ t₇=t₇-t₆,h₇=D₇·h_{It is vented saturation}+d₇, its In, wherein, d₁-d₇For the corresponding overheated zone coefficient of refrigerant.

For the refrigerant enthalpy h at the end of indoor heat exchanger second₅, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, refrigerant enthalpy generation module 20 can directly calculate the system at the end of indoor heat exchanger second Cryogen enthalpy h₅：h₅=c₁+c₂t₅+c₃t² ₅+c₄t³ ₅, wherein, c₁-c₄For the corresponding supercooling fauna number of refrigerant.

In other embodiments of the invention, refrigerant enthalpy generation module 20 can also directly invoke the calculating knot of software Really, or by other approach the refrigerant enthalpy of each temperature detecting point is obtained.For example, when the current working of air conditioner is During heating condition, high-pressure that refrigerant enthalpy generation module 20 can also be in air conditioner, gas returning port temperature t₁, interior changes Hot device first end temperature t₇Respectively obtain the refrigerant enthalpy h of gas returning port₁With the refrigerant enthalpy h of indoor heat exchanger first end₇, And can be in air conditioner high-pressure, exhaust port temperatures t₂, the second end of indoor heat exchanger temperature t₅Respectively obtain exhaust outlet Refrigerant enthalpy h₂With the refrigerant enthalpy h at the end of indoor heat exchanger second₅。

In an embodiment of the present invention, heating capacity generation module 50 can generate the heating capacity of air conditioner according to below equation：Wherein, Q_{Heating capacity}For heating capacity of air conditioner, P_CompressorFor compressor horsepower.

Because the current working of air conditioner is heating condition, thus efficiency generation module 40 can be according to air conditioner power consumption The heat efficiency of air conditioner is generated with heating capacity, specifically, the heat efficiency of air conditioner is the heating capacity and power consumption work(of air conditioner The ratio between rate, i.e. COP=Q_{Heating capacity}/P_{Power consumption}。

The efficiency computing system of air conditioner according to embodiments of the present invention, the current work of air conditioner is obtained by acquisition module Condition, the power of compressor and air conditioner power consumption, and gas returning port in compressor, exhaust are obtained by corresponding temperature sensor The temperature of mouth, the end of indoor heat exchanger second and indoor heat exchanger first end, and pass through system when air conditioner is in heating condition Cryogen enthalpy generation module, heating capacity generation module and efficiency generation module are above-mentioned each according to the generation of the temperature of each above-mentioned position The refrigerant enthalpy of individual position, the refrigerant enthalpy of power, each above-mentioned position then in conjunction with compressor and air conditioner power consumption Power obtains the efficiency of air conditioner, thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to air conditioner Real-time energy efficiency optimize air conditioner running status, reach energy-conservation and improve heating effect purpose.

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 power 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 middle portion temperature t in the middle part of indoor heat exchanger₆With indoor ring Border temperature t₉；

According to the indoor heat exchanger middle portion temperature t₆With the indoor environment temperature t₉Generate the interior of indoor heat exchanger first end Heat exchanger first end temperature t₇；

When the current working of the air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in the compressor₁It is raw Into the refrigerant enthalpy h of gas returning port₁, according to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the refrigerant of exhaust outlet Enthalpy h₂, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end₄Generate outdoor heat exchanger first end Refrigerant enthalpy h₄With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end₇Generate indoor heat exchanger the The refrigerant enthalpy h of one end₇；

According to the power of the compressor, the refrigerant enthalpy h of the gas returning port₁, the exhaust outlet refrigerant enthalpy h₂, institute State the refrigerant enthalpy h of outdoor heat exchanger first end₄With the refrigerant enthalpy h of the indoor heat exchanger first end₇Generate air conditioner Refrigerating capacity；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 gas returning port₁Specifically include：

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

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

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 modifying factor D of the gas returning port refrigerant enthalpy₁, the saturation refrigerant enthalpy h_{Air-breathing saturation}The generation refrigeration Agent enthalpy h₁。

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 1, 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 indoor heat exchanger first end₇Specifically 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 h₇。

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 refrigerant enthalpy h of exhaust outlet₂Specifically include：

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

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 outdoor heat exchanger middle portion temperature t₃Generate 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 outlet₂。

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：

D₂=1+d₁Δt₂+d₂(Δt₂)²+d₃(Δt₂)t₃+d₄(Δt₂)²t₃+d₅(Δt₂)t² ₃+d₆(Δt₂)²t² ₃,

9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated according to below equation The refrigerant enthalpy h of external heat exchanger first end₄：

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}For the refrigerating capacity of the air conditioner, P_CompressorFor the power of the compressor.

11. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that generated by below equation described The indoor heat exchanger first end temperature t of indoor heat exchanger first end₇：

12. 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 1-11 The efficiency computational methods of any described air conditioner.

13. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The efficiency computational methods of the air conditioner as described in any in claim 1-11 are realized when calculation machine program is executed by processor.

14. 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 middle portion temperature t in the middle part of indoor heat exchanger₆With indoor ring Border temperature t₉；

According to the indoor heat exchanger middle portion temperature t₆With indoor environment temperature t₉Generate the indoor heat exchange of indoor heat exchanger first end Device first end temperature t₇；

When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor₁It is raw Into the refrigerant enthalpy h of gas returning port₁, according to the exhaust port temperatures t of exhaust outlet in the compressor₂Generate the refrigerant of exhaust outlet Enthalpy h₂, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second₅Generate the end of indoor heat exchanger second Refrigerant enthalpy h₅With the indoor heat exchanger first end temperature t according to the indoor heat exchanger first end₇Generate indoor heat exchanger the The refrigerant enthalpy h of one end₇；

According to the power of the compressor, the refrigerant enthalpy h of the gas returning port₁, the exhaust outlet refrigerant enthalpy h₂, institute State the refrigerant enthalpy h at the end of indoor heat exchanger second₅With the refrigerant enthalpy h of the indoor heat exchanger first end₇Generate air conditioner Heating capacity；And

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

15. the efficiency computational methods of air conditioner as claimed in claim 14, 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 gas returning port₁Specifically 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 port₁。

16. the efficiency computational methods of air conditioner as claimed in claim 15, it is characterised in that according to below equation generation The enthalpy h of saturation refrigerant under suction temperature_{Air-breathing saturation}：

17. the efficiency computational methods of air conditioner as claimed in claim 15, 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>

18. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that be vented according in the compressor The exhaust port temperatures t of mouth₂Generate the refrigerant enthalpy h of exhaust outlet₂Specifically include：

According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆With the exhaust outlet temperature of exhaust outlet in the compressor Spend t₂Generate discharge superheat Δ t₂；

According to the discharge superheat Δ t₂With the indoor heat exchanger middle portion temperature t₆Generate the amendment of exhaust outlet refrigerant enthalpy Factor D₂；

According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger₆Generate the enthalpy of saturation refrigerant under delivery temperature h_{It is vented saturation}；

19. the efficiency computational methods of the air conditioner described in claim 18, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy₂：

D₂=1+d₁Δt₂+d₂(Δt₂)²+d₃(Δt₂)t₆+d₄(Δt₂)²t₆+d₅(Δt₂)t² ₆+d₆(Δt₂)²t² ₆,

20. the efficiency computational methods of air conditioner as claimed in claim 18, it is characterised in that according to the indoor heat exchanger The indoor heat exchanger first end temperature t of one end₇Generate the refrigerant enthalpy h of indoor heat exchanger first end₇Specifically include：

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

According to the 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 end₇。

21. the efficiency computational methods of air conditioner as claimed in claim 20, it is characterised in that according to below equation generation The modifying factor D of indoor heat exchanger first end refrigerant enthalpy₇：

22. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to being calculated below equation The refrigerant enthalpy h at the end of indoor heat exchanger second₅：

23. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to equation below generation The heating capacity of air conditioner：

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

24. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that generated by below equation described The indoor heat exchanger first end temperature t of indoor heat exchanger first end₇：

t₇ =a*t₉+b*t₆+ c*f, wherein, f be the compressor running frequency, a, b, c is fitting coefficient.

25. 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 14-24 Any described method.

26. 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 14-24 is realized when calculation machine program is executed by processor.