CN104422024A

CN104422024A - Automobile air conditioning system and control method thereof

Info

Publication number: CN104422024A
Application number: CN201310401335.XA
Authority: CN
Inventors: 谭永翔; 陈绍龙; 刘维华; 黄宁杰
Original assignee: Hangzhou Sanhua Research Institute Co Ltd
Current assignee: Hangzhou Sanhua Research Institute Co Ltd
Priority date: 2013-09-05
Filing date: 2013-09-05
Publication date: 2015-03-18
Anticipated expiration: 2033-09-05
Also published as: CN104422024B

Abstract

The invention discloses an automobile air conditioning system and a control method thereof. The air conditioning system comprises a compressor, a first heat exchanger, a first expansion device, a second heat exchanger, an outdoor heat exchanger and a second expansion device, wherein the compressor, the outdoor heat exchanger, the first expansion device and the first heat exchanger can be communicated in sequence to form a refrigerating circuit; the compressor, the second heat exchanger, the first heat exchanger, the second expansion device and the outdoor heat exchanger can be communicated in sequence to form a heating circuit. According to the automobile air conditioning system, the first heat exchanger takes part in refrigerating and also takes part in heating, when a heating mode is performed, an air flow can go through the first heat exchanger and the second heat exchanger for secondary heating, the heating capacity of the air conditioning is strengthened, and thus a sufficient heating air flow can be provided so that a comfortable riding environment can also be obtained under a low temperature environment.

Description

Automotive air-conditioning system and control method thereof

Technical field

The present invention relates to air-conditioning technical field, particularly a kind of automotive air-conditioning system and control method thereof.

Background technology

Please refer to Fig. 1, Fig. 1 is a kind of typical electric automobile air-conditioning system.

This electric automobile air-conditioning system comprises compressor 1 ', gas-liquid separator 2 ', outdoor heat exchanger 3 ', the first stop valve 4 ', the second stop valve 5 ', the 3rd stop valve 6 ', the 4th stop valve 7 ', expansion gear 9 ', and air-conditioning box 100 ' etc., each parts connect to form complete heat pump type air conditioning system by corresponding pipeline.

Air-conditioning box 100 ' specifically comprises cycle throttle 106 ', Inner eycle air port 107 ', outer circulation air port 108 ', air blast 104 ', First Heat Exchanger 101 ', temperature damper 105 ', the second heat exchanger 102 ', electric heater 103 ', and grid air channel 109 ' etc.What Inner eycle air port 107 ' and outer circulation air port 108 ' made to enter air-conditioning box 100 ' through cycle throttle 106 ' is mixing wind, and mixed proportion by system according to comfortableness requirement, can be controlled by cycle throttle 106 '.

The operation principle of this air-conditioning system is as follows:

Refrigeration mode:

First stop valve 4 ', the 3rd stop valve 6 ' are opened, and the second stop valve 5 ', the 4th stop valve 7 ' are closed.The gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP by compressor 1 ', and flow of refrigerant, through the second heat exchanger 102 ', enters outdoor heat exchanger 3 ' through the first stop valve 4 ';

The cold-producing medium of HTHP in outdoor heat exchanger 3 ' with flow of outside air D heat exchange, cold-producing medium release heat, the heat of release is taken in external environment air by air stream D, and cold-producing medium then undergoes phase transition and is condensed into liquid state or gas-liquid two-phase cold-producing medium;

Cold-producing medium flows out outdoor heat exchanger 3 ', and enter expansion gear 9 ' and expand, decrease temperature and pressure becomes the cold-producing medium of low-temp low-pressure;

The cold-producing medium of low-temp low-pressure enters First Heat Exchanger 101 ', carries out heat exchange, absorb the heat of this air-flow A with air-flow A or mixed airflow A, and air-flow A lowers the temperature as cold air B, and cold-producing medium then undergoes phase transition and major part flashes to the gaseous refrigerant of low-temp low-pressure.Now, because temperature damper 105 ' is closed, the cold air through First Heat Exchanger 101 ' heat exchange formation is directly walked around the second heat exchanger 102 ' and enters grid air channel 109 ', and is admitted to car indoor, reduces car indoor temperature, provides comfortable environment by bus; And when set temperature is higher, temperature damper 105 ' also can partially open and carry out heat exchange.

Low-temperature low-pressure refrigerant after First Heat Exchanger 101 ' phase transformation flows to gas-liquid separator 2 ', liquid refrigerant is stored in gas-liquid separator 2 ', the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, periodic duty like this again by compressor 1 '.

Heating mode:

First stop valve 4 ', the 3rd stop valve 6 ' are closed, and the second stop valve 5 ', the 4th stop valve 7 ' are opened.The gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP by compressor 1 ', and flow of refrigerant is through the second heat exchanger 102 '; Now, temperature damper 105 ' is opened, and the cold-producing medium of HTHP the second heat exchanger 102 ' in and air stream B heat exchange and cooling, is then admitted to car indoor by the air stream C heated through grid air channel 109 ', to improve car indoor temperature, provide comfortable environment by bus;

Because the 3rd stop valve 6 ' is closed, cold-producing medium can only flow to expansion gear 9 ' and expand, and decrease temperature and pressure becomes the cold-producing medium of low-temp low-pressure, and now, First Heat Exchanger 101 ' does not work;

The cold-producing medium of low-temp low-pressure enters outdoor heat exchanger 3 ', absorbs the heat in external air flow D, is phase-changed into low-pressure gaseous refrigerant;

Then refrigerant flow direction gas-liquid separator 2 ', liquid refrigerant is stored in gas-liquid separator 2 ', and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, periodic duty like this again by compressor 1 '.

But there is following technical problem in such scheme:

First, second heat exchanger 102 ' is subject to the restriction of air-conditioning box 100 ' structure, and exchange capability of heat is limited, at low ambient temperatures, as when close to subzero 20 DEG C, can not meet heat demand, cause wind pushing temperature low, cannot meet passenger comfort requirement;

The second, describe from above-mentioned operation principle and understand by reference to the accompanying drawings, fluid in this air-conditioning system pipeline, under heating and freezing two kinds of patterns, the direction flowing through outdoor heat exchanger 3 ' is contrary, be difficult to meet during fluid flows at two kinds and all have good thermodynamic property and dynamic performance, thus be difficult to take into account refrigeration and heat all have good performance.

In view of this, how improving automotive air-conditioning system, to make vehicle can obtain preferably by bus environment at low ambient temperatures, is those skilled in the art's technical problems urgently to be resolved hurrily.

Summary of the invention

For solving the problems of the technologies described above, object of the present invention is for providing automotive air-conditioning system and control method thereof.This automotive air-conditioning system makes vehicle can obtain relatively preferably environment by bus at low ambient temperatures.

Automotive air-conditioning system provided by the invention, comprise compressor, First Heat Exchanger, the first expansion gear, the second heat exchanger, and outdoor heat exchanger, the second expansion gear, described compressor, described outdoor heat exchanger, described first expansion gear, described First Heat Exchanger can form refrigerating circuit by sequential communication, and described compressor, described second heat exchanger, described First Heat Exchanger, described second expansion gear, described outdoor heat exchanger sequential communication formation can heat loop; And when heating mode, air stream first flows through described First Heat Exchanger and carries out heat exchange intensification, and then flow through described second heat exchanger.

This automotive air-conditioning system, its First Heat Exchanger had both participated in refrigeration and has also participated in heating, when performing heating mode, air fails to be convened for lack of a quorum through First Heat Exchanger, the second heat exchanger post bake, the heating capacity of air-conditioning system is strengthened, thus enough heated air flows can be provided, under making low temperature environment, also can obtain comfortable environment by bus.

The first concrete scheme, the import of the second heat exchanger described in the outlet of described compressor, the outlet of described second heat exchanger is communicated with described outdoor heat exchanger by a branch road, is communicated with the import of described First Heat Exchanger by another branch road; Described second heat exchanger place is provided with temperature damper, and described temperature damper is opened in time heating.

The second concrete scheme, the outlet of described compressor is communicated with described outdoor heat exchanger by a branch road, is communicated with the import of described second heat exchanger by another branch road.

The third concrete scheme, the outlet of described second heat exchanger is communicated with the import of described First Heat Exchanger by described first expansion gear, the first expansion gear is electric expansion valve.

4th kind of concrete scheme, described first expansion gear is parallel with by-passing valve.

5th kind of concrete scheme, a header of described outdoor heat exchanger is provided with refrigerating circuit import and heats loop import; Be provided with distributing pipe in header described in this, described in heat loop import and be directly communicated with described distributing pipe; Described refrigerating circuit import is directly communicated with described header, and described refrigerating circuit import and described distributing pipe are independent mutually.

6th kind of concrete scheme, also comprises the controller of default described First Heat Exchanger degree of supercooling, the described outdoor heat exchanger degree of superheat;

Described controller first obtains the degree of superheat of described outdoor heat exchanger, and compares with the degree of superheat preset the aperture regulating described second expansion gear; After adjustment, described controller also obtains the degree of supercooling of described First Heat Exchanger, and compares with the degree of supercooling preset the aperture regulating described first expansion gear;

Or described controller first obtains the degree of supercooling of described First Heat Exchanger, and compare with the degree of supercooling preset the aperture regulating described first expansion gear; After adjustment, described controller also obtains the degree of superheat of described outdoor heat exchanger, and compares with the degree of superheat preset the aperture regulating described second expansion gear.

7th kind of concrete scheme, also comprises the controller of default described First Heat Exchanger degree of supercooling, described second heat exchanger degree of supercooling;

Described controller first obtains the degree of supercooling of described second heat exchanger, and compares with the degree of supercooling preset the aperture regulating described first expansion gear; After adjustment, described controller also obtains the degree of supercooling of described First Heat Exchanger, and compares with the degree of supercooling preset the aperture regulating described second expansion gear;

Or described controller obtains the degree of supercooling of described First Heat Exchanger, and compare with the degree of supercooling preset the aperture regulating described second expansion gear; After adjustment, described controller also obtains the degree of supercooling of described second heat exchanger, and compares with the degree of supercooling preset the aperture regulating described first expansion gear.

8th kind of concrete scheme, the 3rd expansion gear also comprising battery, battery heat exchanger and be communicated with it, the import of described 3rd expansion gear can be communicated with the outlet of described outdoor heat exchanger and the outlet of described second heat exchanger; The import of compressor described in the outlet of described battery heat exchanger.

9th kind of concrete scheme, comprises the battery case holding described battery, described battery heat exchanger; The air inlet of described battery case be provided be communicated with car indoor Inner eycle air port, with the outer circulation air port be communicated with outside compartment, and the cycle throttle in adjustment Inner eycle air port and outer circulation air port.

Tenth kind of concrete scheme, is also provided with the first air channel and the second air channel, and controls the inside and outside air door of the air outlet of described battery case and described first air channel, described second air channel break-make; Described first air channel is communicated with described Inner eycle air port, outside described second air channel open car.

The application also provides a kind of control method of the automotive air-conditioning system as described in the third scheme above-mentioned, comprises the steps:

According to arranging operating mode and temperature draws the degree of superheat of corresponding outdoor heat exchanger and the degree of supercooling of First Heat Exchanger;

By the outlet pressure of sensing chamber's external heat exchanger, the actual degree of superheat of outlet temperature acquisition outdoor heat exchanger, by detecting the outlet pressure of First Heat Exchanger, the actual degree of supercooling of outlet temperature acquisition First Heat Exchanger;

Carry out aperture adjustment, wherein, the second expansion gear is heating power expansion valve or electric expansion valve:

The degree of superheat first comparing the actual degree of superheat of outdoor heat exchanger and preset, if the former is greater than the latter, then increases by the second expansion gear aperture; The former is less than the latter, reduces the second expansion gear aperture; The former equals the latter, then keep the current aperture of the second expansion gear constant;

The degree of supercooling comparing the actual degree of supercooling of First Heat Exchanger again and preset, if the former is greater than the latter, then reduces the first expansion gear aperture; The former is less than the latter, increases by the first expansion gear aperture; The former equals the latter, keeps the current aperture of the first expansion gear constant;

Or the degree of supercooling first comparing the actual degree of supercooling of First Heat Exchanger and preset, if the former is greater than the latter, then reduces the first expansion gear aperture; The former is less than the latter, then increase by the first expansion gear aperture; The former equals the latter, then keep the current aperture of the first expansion gear constant;

The degree of superheat comparing the actual degree of superheat of outdoor heat exchanger again and preset, if the former is greater than the latter, then increases by the second expansion gear aperture; The former is less than the latter, then reduce the second expansion gear aperture; The former equals the latter, keeps the current aperture of the second expansion gear constant.

The application also provides the control method of another kind of automotive air-conditioning system as described in the third scheme above-mentioned, comprises the steps:

According to arranging operating mode and temperature draws the corresponding degree of supercooling of the second heat exchanger and the degree of supercooling of First Heat Exchanger;

By the actual degree of supercooling detecting the outlet pressure of the second heat exchanger, outlet temperature obtains the second heat exchanger, by the actual degree of supercooling detecting the outlet pressure of First Heat Exchanger, outlet temperature obtains First Heat Exchanger;

Carry out aperture adjustment, wherein, the second expansion gear is electric expansion valve:

The degree of supercooling first comparing the actual degree of supercooling of the second heat exchanger and preset, if the former is greater than the latter, then increases by the first expansion gear aperture; The former is less than the latter, reduces the first expansion gear aperture; The former equals the latter, then keep the current aperture of the first expansion gear constant;

The degree of supercooling comparing the actual degree of supercooling of First Heat Exchanger again and preset, if the former is greater than the latter, then increases by the second expansion gear aperture; The former is less than the latter, reduces the second expansion gear aperture; The former equals the latter, keeps the current aperture of the second expansion gear constant;

Or the degree of supercooling first comparing the actual degree of supercooling of First Heat Exchanger and preset, if the former is greater than the latter, then increases by the second expansion gear aperture; The former is less than the latter, then reduce the second expansion gear aperture; The former equals the latter, then keep the current aperture of the second expansion gear constant;

The degree of supercooling comparing the actual degree of supercooling of the second heat exchanger again and preset, if the former is greater than the latter, then increases by the first expansion gear aperture; The former is less than the latter, then reduce the first expansion gear aperture; The former equals the latter, keeps the current aperture of the first expansion gear constant.

Above-mentioned two kinds of control methods control the aperture of an expansion gear successively, after an expansion gear regulates, certain influence can be produced to another expansion gear, now adjust another expansion gear aperture again, indeed achieve jointly controlling of two expansion gears, to make final adjustment result as far as possible close to practical adjustments demand, realize the optimized control of two expansion gears.

Accompanying drawing explanation

Fig. 1 is a kind of typical electric automobile air-conditioning system;

Fig. 2 is the structural representation of the first specific embodiment of automotive air-conditioning system provided by the present invention;

Fig. 3 is refrigerant flowpath schematic diagram when air-conditioning system is in refrigeration mode in Fig. 2, and wherein thickened portion represents flow path;

Fig. 4 is refrigerant flowpath schematic diagram when air-conditioning system is in heating mode in Fig. 2, and wherein thickened portion represents flow path;

Fig. 5 is refrigerant flowpath schematic diagram when air-conditioning system is in the first dehumidification mode in Fig. 2, and wherein thickened portion represents flow path;

Fig. 6 is refrigerant flowpath schematic diagram when air-conditioning system is in the second dehumidification mode in Fig. 2, and wherein thickened portion represents flow path;

Fig. 7 is refrigerant flowpath schematic diagram when air-conditioning system is in defrosting mode in Fig. 2, and wherein thickened portion represents flow path;

Fig. 8 is the structural representation of automotive air-conditioning system the second specific embodiment provided by the present invention;

Fig. 9 is the structural representation of the third specific embodiment of automotive air-conditioning system provided by the present invention;

Figure 10 is the structural representation of a kind of specific embodiment of outdoor heat exchanger in automotive air-conditioning system provided by the present invention;

Figure 11 is the first control principle drawing of expansion gear under heating mode in Fig. 4, and dotted line illustrates feedback signal;

Figure 12 is the control flow chart of two expansion gears in control Figure 11;

Figure 13 is the second control principle drawing of expansion gear under heating mode in Fig. 4, and dotted line illustrates feedback signal;

Figure 14 is the control flow chart of two expansion gears in control Figure 13;

Figure 15 is the structural representation of automotive air-conditioning system provided by the present invention 4th kind of specific embodiment;

Figure 16 is refrigerant flowpath schematic diagram when air-conditioning system is in refrigeration mode in Figure 15, and wherein thickened portion represents flow path;

Figure 17 is refrigerant flowpath schematic diagram when air-conditioning system is in heating mode in Figure 15, and wherein thickened portion represents flow path;

Figure 18 is refrigerant flowpath schematic diagram when air-conditioning system is in heating mode and is in battery waste heat recovery pattern in Figure 15, and wherein thickened portion represents flow path.

In Fig. 1:

1 ' compressor, 2 ' gas-liquid separator, 3 ' outdoor heat exchanger, the 4 ' first stop valve, the 5 ' second stop valve, the 6 ' the 3rd stop valve, the 7 ' the 4th stop valve, 9 ' expansion gear, 10 ' check valve, 100 ' air-conditioning box, 101 ' First Heat Exchanger, the 102 ' second heat exchanger, 103 ' electric heater, 104 ' air blast, 105 ' temperature damper, 106 ' cycle throttle, 107 ' Inner eycle air port, 108 ' outer circulation air port, 109 ' grid air channel

In Fig. 2-18:

1 compressor, 2 gas-liquid separators, 3 outdoor heat exchangers, 31 refrigerating circuit imports, 32 heat loop import, the outlet of 33 outdoor heat exchangers, 34 distributing pipes, 35 dispensing orifices, 36 inlet header, 37 outlet collection pipes, 38 flat tubes, 39 fins, 4 first stop valves, 5 second stop valves, 6 the 3rd stop valves, 7 the 4th stop valves, 8 first expansion gears, 81 by-passing valves, 9 second expansion gears, 10 check valves, 11 the 5th stop valves, 12 the 3rd expansion gears, 100 air-conditioning boxs, 101 First Heat Exchangers, the outlet of 1011 First Heat Exchangers, 102 second heat exchangers, the outlet of 1021 second heat exchangers, 103 first electric heaters, 104 first air blasts, 105 temperature dampers, 106 first cycle throttles, 107 first Inner eycle air ports, 108 first outer circulation air ports, 109 grid air channels, 200 battery cases, 201 battery heat exchangers, 202 second electric heaters, 203 second air blasts, 204 second cycle throttles, 205 second outer circulation air ports, 206 second Inner eycle air ports, 300 batteries, 401 wind inlet channels, 402 exhaust air flue, 403 first air channels, 404 second air channels, air door inside and outside 405

Detailed description of the invention

In order to make those skilled in the art understand technical scheme of the present invention better, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.

Please refer to Fig. 2, Fig. 2 is the structural representation of the first specific embodiment of automotive air-conditioning system provided by the present invention.

This automotive air-conditioning system, comprise compressor 1, First Heat Exchanger 101 and the first expansion gear 8, second heat exchanger 102 with its inlet communication, and outdoor heat exchanger 3 and the second expansion gear 9 with its inlet communication, expansion gear can play the effect of decrease temperature and pressure in air conditioner circulating system, generally has throttle pipe, common heating power expansion valve or electric expansion valve etc.Particularly, can arrange air-conditioning box 100, First Heat Exchanger 101 and the second heat exchanger 102 are all placed in air-conditioning box 100.

Wherein, compressor 1, outdoor heat exchanger 3, first expansion gear 8, First Heat Exchanger 101 can form refrigerating circuit by sequential communication.In the present embodiment, compressor 1, second heat exchanger 102, First Heat Exchanger 101, second expansion gear 9, outdoor heat exchanger 3 sequential communication formation can heat loop, and namely First Heat Exchanger 101 and the second heat exchanger 102 all can provide heat when heating mode.

In addition, the import department of compressor 1 can be provided with gas-liquid separator 2, to be separated backflow refrigerant, the liquid part be about to wherein is stored in gas-liquid separator 2, and the gaseous refrigerant part of low-temp low-pressure then enters compressor 1 and again compresses.Certainly, for the compressor that some are novel, also gas-liquid separator 2 can not be set.

Particularly, as shown in Figure 2, this air-conditioning system comprises the first stop valve 4, second stop valve 5, the 3rd stop valve 6, the 4th stop valve 7, first expansion gear 8, second expansion gear 9, First Heat Exchanger 101, second heat exchanger 102, outdoor heat exchanger 3, compressor 1.The import of the second heat exchanger 102 and the outlet of compressor 1, the outlet of the second heat exchanger 102 has two branch roads, and a branch road is the path that the second heat exchanger 102 exports between outdoor heat exchanger 3 import, and this branch road is located at by the first stop valve 4; Another branch road is that the second heat exchanger 102 exports the import with the first expansion gear 8, and the second stop valve 5 is arranged at this branch road.Above-mentioned each stop valve is specifically as follows hand stop valve, also can adopt electronic or pneumatic stopping valve.

The outlet of outdoor heat exchanger 3 also has two branch roads, and a branch road is the path between its outlet and first expansion gear 8 import, and this path can arrange the check valve 10 of one-way conduction outdoor heat exchanger 3 and the first expansion gear 8, in order to avoid back flow of refrigerant; Another branch road is the path that outdoor heat exchanger 3 exports between compressor 1 import, and the 3rd stop valve 6 is arranged at this branch road.

The outlet of First Heat Exchanger 101 also has two branch roads, and a branch road is communicated to the import of compressor 1, and this branch road is provided with the 4th stop valve 7; Another branch road is communicated to the import of outdoor heat exchanger 3, and this branch road is located at by the second expansion gear 9.

For ease of to entering First Heat Exchanger 101, the air stream of the second heat exchanger 102 carries out conservative control, air-conditioning box 100 can arrange the first Inner eycle air port 107 and the first outer circulation air port 108, first Inner eycle air port 107 is communicated with in car, outside first outer circulation air port 108 open car, first cycle throttle 106 controls the aperture in the first Inner eycle air port 107 and the second outer circulation air port 205, to regulate the mixing wind ratio entered from the first cycle throttle 106 place in air-conditioning box 100, mixed proportion can by system according to comfortableness requirement, controlled by the first cycle throttle 106, it is target that the ratio of Inner eycle wind can not cause vehicle window to tie mist, introduce Inner eycle wind and can save the energy further.

In addition, first air blast 104 can also be set, first air blast 104 can be arranged between the first cycle throttle 106 and First Heat Exchanger 101, to enable the air stream A at the first cycle throttle 106 place smoothly flow to First Heat Exchanger 101, and finally flow to the air outlet of air-conditioning box 100 swimmingly.In this embodiment, the air outlet place of air-conditioning box 100 is provided with grid air channel 109, and with air distribution stream C and its wind direction adjustable, air outlet is towards in passenger compartment.

Even if be appreciated that and do not arrange the first cycle throttle 106, directly the air stream introduced outside compartment or in compartment is also feasible.Just, so design makes Performance for Air Conditioning Systems more optimize.

The operation principle of this air-conditioning system is as follows:

Refrigeration mode:

Please refer to Fig. 3, Fig. 3 is refrigerant flowpath schematic diagram when air-conditioning system is in refrigeration mode in Fig. 2, and wherein thickened portion represents refrigerant flowpath.

First stop valve 4, the 4th stop valve 7 are opened, and the second stop valve 5, the 3rd stop valve 6 are closed.Compressor 1 consumes certain electric energy, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, and flow of refrigerant, through the second heat exchanger 102, enters outdoor heat exchanger 3 through the first stop valve 4; Now, temperature damper 105 can be closed, and is blocked completely by the second heat exchanger 102, and to stop air-flow B and the second heat exchanger 102 heat exchange, therefore the gaseous refrigerant of HTHP flows through the second heat exchanger 102 not heat exchange, but directly flows to the first stop valve 4;

The cold-producing medium of HTHP in outdoor heat exchanger 3 with flow of outside air D heat exchange, cold-producing medium release heat, the heat of release is taken in external environment air by air stream D, and cold-producing medium then cools and undergoes phase transition and be condensed into liquid state;

Cold-producing medium flows out outdoor heat exchanger 3, and enter the first expansion gear 8 and expand, decrease temperature and pressure becomes the cold-producing medium of low-temp low-pressure;

The cold-producing medium of low-temp low-pressure enters First Heat Exchanger 101, heat exchange is carried out with the air-flow A entered from the first cycle throttle 106, absorb the heat of this air-flow A, air-flow A lowers the temperature as cold air B, and cold-producing medium then has at least part undergo phase transition and flash to the gaseous refrigerant of low-temp low-pressure.Now, because temperature damper 105 is closed, the cold air through First Heat Exchanger 101 heat exchange formation is directly walked around the second heat exchanger 102 and enters grid air channel 109, and is admitted to car indoor, reduces car indoor temperature, provides comfortable environment by bus; And when car indoor temperature arranges higher, for avoiding the wind of blowout too low, temperature damper 105 can open a part, after air stream B is heated up, blow to car indoor again.

Low-temperature low-pressure refrigerant after First Heat Exchanger 101 phase transformation flows to gas-liquid separator 2, the liquid refrigerant contained is stored in gas-liquid separator 2, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, periodic duty like this again by compressor 1.

Heating mode:

Please refer to Fig. 4, Fig. 4 is refrigerant flowpath schematic diagram when air-conditioning system is in heating mode in Fig. 2, and wherein thickened portion represents refrigerant flowpath.

First stop valve 4, the 4th stop valve 7 are closed, and the second stop valve 5, the 3rd stop valve 6 are opened.Compressor 1 consumes certain electric energy, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, and flow of refrigerant is through the second heat exchanger 102; Now, temperature damper 105 is opened, the cold-producing medium of HTHP in the second heat exchanger 102 with air stream B heat exchange, cold-producing medium is released heat and cools;

Cold-producing medium continues to flow to the first expansion gear 8 and expands, now the aperture of the first expansion gear 8 is larger, cold-producing medium decrease temperature and pressure after preliminary expansion becomes the cold-producing medium of medium temperature and medium pressure, at this moment due to from the temperature of the car outdoor airflow temperature of coming in lower than the cold-producing medium in First Heat Exchanger 101, first there is heat exchange in cold-producing medium and air stream A, air stream A is heated for the first time, air stream B after preliminary heating through temperature damper 105 again with the high-temperature high-pressure refrigerant generation heat exchange flowing through the second heat exchanger 102, then air stream B is heated for the second time; The air stream C of post bake can be admitted to car indoor through grid air channel 109, to improve car indoor temperature, provides comfortable environment by bus;

Expand through the second expansion gear 9 from the cold-producing medium of First Heat Exchanger 101 medium temperature and medium pressure out, become the cold-producing medium of low-temp low-pressure specifically through abundant throttling; The flow of refrigerant of low-temp low-pressure, through outdoor heat exchanger 3, absorbs the heat in external air flow D, is phase-changed into low-temp low-pressure gaseous refrigerant;

The cold-producing medium of low-temp low-pressure flows to gas-liquid separator 2 through the 3rd stop valve 6, and the liquid refrigerant contained is stored in gas-liquid separator 2, and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, periodic duty like this again by compressor 1.

In this embodiment, First Heat Exchanger 101 had both participated in refrigeration and has also participated in heating, when performing heating mode, air stream A can through First Heat Exchanger 101, second heat exchanger 102 post bake, and air stream A first carries out heat exchange through the First Heat Exchanger 101 that refrigerant temperature is relatively low tentatively to heat up, and then heat up through the second heat exchanger 102 that temperature is high, the heating capacity of such air-conditioning system is able to further reinforcement, thus enough heated air flow C can be provided, under making low temperature environment, also can obtain comfortable environment by bus.

In addition, the first expansion gear 8 is provided with between second heat exchanger 102 and First Heat Exchanger 101, first expansion gear 8 creates suitable flow resistance, the cold-producing medium in the second heat exchanger 102 is made to be in high pressure, corresponding condensation temperature is also higher, cold-producing medium is after the second heat exchanger 102 heat exchange, intermediate pressure is depressurized to through the first expansion gear 8, and again become the state of medium temperature and medium pressure, such one side can not be too high to pressure during First Heat Exchanger 101, tentatively can heat up to air stream A again, thus obtain higher heat exchange efficiency.With regard to air stream A, it is first heated to medium temperature through First Heat Exchanger 101, is more again heated to high temperature through the second heat exchanger 102, and achieve countercurrent flow, heat transfer effect is better.Therefore, during heating mode, the first expansion gear 8 is located between First Heat Exchanger 101 and the second heat exchanger 102, make use of First Heat Exchanger 101, improve the heat exchange efficiency of system, further enhance heat capacity, and can not significantly improve the requirement of withstand voltage of First Heat Exchanger 101.

The outlet of this embodiment second heat exchanger 102 is communicated with the import of First Heat Exchanger 101 by the first expansion gear 8, to realize above-mentioned post bake process in a heating mode.In fact, also can an expansion gear be set separately, second heat exchanger 102 is communicated with same feasible by this expansion gear and First Heat Exchanger 101, just, embodiments described above utilize existing former the first expansion gear 8 for freezing and can realize post bake demand, via design also comparatively simplifies.

In addition, first electric heater 103 can also be set, as shown in Figure 4, first electric heater 103 to be located in air-conditioning box 100 between second heat exchanger 102 and air-conditioning box 100 export, when ambient temperature is too low, heat pump performance is not enough or lower even the breaking down of heat pump efficiency and cannot normally work time, the first electric heater 103 auxiliary heating can be adopted, realize heating function together with heat pump.

This air-conditioning system can also perform the first dehumidification mode, the second dehumidification mode and defrosting mode:

First dehumidification mode:

Please refer to Fig. 5, Fig. 5 is refrigerant flowpath schematic diagram when air-conditioning system is in the first dehumidification mode in Fig. 2, and wherein thickened portion represents flow path.

First stop valve 4, the 4th stop valve 7 are opened, and the second stop valve 5, second expansion gear 9 cuts out (now, the second expansion gear 9 has keying function, such as electric expansion valve).Similar to refrigeration mode, now temperature damper 105 is partially or completely opened, and makes the cooling-air stream B formed with First Heat Exchanger 101 heat exchange can partially or completely by the second heat exchanger 102.The air stream A then entered through the first cycle throttle 106 is through First Heat Exchanger 101 by cool-down dehumidification, and become low temperature and low humidity air stream B, then be heated to form low-humidity air stream C through the second heat exchanger 102, this air stream C is admitted to car indoor and can reduces car humidity.

Obviously, in passenger compartment, relative humidity is comparatively large, and when not being very large to demand for heat amount, can perform the first dehumidification mode, to reach effect on moisture extraction, avoids steam condensation and affect the visual field on glass for vehicle window, improves security performance.

Second dehumidification mode:

Please refer to Fig. 6, Fig. 6 is refrigerant flowpath schematic diagram when air-conditioning system is in the second dehumidification mode in Fig. 2, and wherein thickened portion represents flow path.

Second stop valve 5, the 3rd stop valve 6, the 4th stop valve 7 are opened, and the first stop valve 4 is closed, and the second expansion gear 9 cuts out.Similar to the first dehumidification mode, unlike, directly enter the first expansion gear 8 expansion by the second stop valve 5 from the second heat exchanger 102 cold-producing medium out and carry out step-down cooling, now temperature damper 105 is partially or completely opened, and makes air stream B can partially or completely through the second heat exchanger 102.Air stream A by cool-down dehumidification by First Heat Exchanger 101, is become the air stream B of low temperature and low humidity, is heated as comfortable low-humidity air stream C, and is finally admitted to car indoor through the second heat exchanger 102, reduces indoor humidity, provides comfortable environment by bus.

It is comparatively large that second dehumidification mode is applicable to passenger compartment humidity, and use time larger to demand for heat amount.

Defrosting mode:

Please refer to Fig. 7, Fig. 7 is refrigerant flowpath schematic diagram when air-conditioning system is in defrosting mode in Fig. 2, and wherein thickened portion represents flow path.

Under low temperature environment, in a heating mode the working time long after, the easy frosting in surface of outdoor heat exchanger 3, can reduce and even lose heat exchange property, cause system effectiveness reduce even lose heat-production functions.Now, defrosting mode can be entered:

First stop valve 4, the 3rd stop valve 6 are opened, and the second stop valve 5 is closed, and the 4th stop valve 7 or the first expansion gear 8 are closed, and the second expansion gear 9 cuts out.Compressor 1 consumes certain electric energy, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of HTHP, flow of refrigerant is through the second heat exchanger 102, temperature damper 105 is partly or entirely opened, it is indoor that air stream B is heated rear feeding car, to increase indoor temperature, provide comfortable environment by bus;

Leave the cold-producing medium of the second heat exchanger 102, by the first stop valve 4, enter outdoor heat exchanger 3, release heat, the frost on outdoor heat exchanger 3 surface is removed rapidly, and cold-producing medium leaves outdoor heat exchanger 3 and enters gas-liquid separator 2 through the 3rd stop valve 6, gas-liquid separator 2 is separated the liquid refrigerant in cold-producing medium, gaseous refrigerant gets back to compressor 1, periodic duty like this, until the frost of outdoor heat exchanger 3 is effectively removed.

In this embodiment, no matter perform which kind of pattern, the high-temperature high-pressure refrigerant that compressor 1 provides all needs first through the second heat exchanger 102, then two branch roads through its exit flow to First Heat Exchanger 101 or outdoor heat exchanger 3, and control the second heat exchanger 102 by temperature damper 105 and whether participate in work.In fact, other modes can also be adopted.

As shown in Figure 8, Fig. 8 is the structural representation of automotive air-conditioning system the second specific embodiment provided by the present invention.

In this embodiment, the outlet of compressor 1 is provided with two branch roads, the import of a branch road communication chamber external heat exchanger 3, and the first stop valve 4 is arranged at this branch road; Another branch road is communicated with the import of the second heat exchanger 102, and the second stop valve 5 is arranged at the path that the second heat exchanger 102 is exported to the first expansion gear 8 import.All the other channel setting are similar to the first embodiment.

Operation principle and first embodiment of this air-conditioning system are similar, are succinct description, the flow path of cold-producing medium under each mode of operation are only shown herein, no longer describe in detail.

Refrigeration mode:

First stop valve 4, the 4th stop valve 7 are opened, and the second stop valve 5, the 3rd stop valve 6 are closed:

The flow path of cold-producing medium: compressor 1-first stop valve 4-outdoor heat exchanger 3-first expansion gear 8-First Heat Exchanger 101-the 4th stop valve 7-gas-liquid separator 2-compressor 1.

Heating mode:

First stop valve 4, the 4th stop valve 7 are closed, and the second stop valve 5, the 3rd stop valve 6 are opened;

The flow path of cold-producing medium: compressor 1-second heat exchanger 102-second stop valve 5-first expansion gear 8-First Heat Exchanger 101-second expansion gear 9-outdoor heat exchanger 3-the 3rd stop valve 6-gas-liquid separator 2-compressor 1.

First dehumidification mode:

First stop valve 4, second stop valve 5, the 4th stop valve 7 are opened, and the 3rd stop valve 6 is closed, and the second expansion gear 9 cuts out.

The flow path of cold-producing medium is divided into two:

1, compressor 1-second heat exchanger 102-second stop valve 5-first expansion gear 8-First Heat Exchanger 101-the 4th stop valve 7-gas-liquid separator 2-compressor 1;

2, compressor 1-first stop valve 4-outdoor heat exchanger 3-first expansion gear 8-First Heat Exchanger 101-the 4th stop valve 7-gas-liquid separator 2-compressor 1.

Namely the cold-producing medium that compressor 1 is exported to two branch roads of outdoor heat exchanger 3 and the second heat exchanger 102 converges at the first expansion gear 8 place, and the flow of concrete two branch roads can according to the temperature control and regulation of the indoor needs of car.

Second dehumidification mode:

Second stop valve 5, the 3rd stop valve 6, the 4th stop valve 7 are opened, and the first stop valve 4 is closed, and the second expansion gear 9 cuts out.

The flow path of cold-producing medium: compressor 1-second heat exchanger 102-second stop valve 5-first expansion gear 8-First Heat Exchanger 101-the 4th stop valve 7-gas-liquid separator 2-compressor 1.

Defrosting mode:

First stop valve 4, the 3rd stop valve 6 are opened, and the second stop valve 5 is closed, and the 4th stop valve 7 or the first expansion gear 8 are closed, and the second expansion gear 9 cuts out.

The flow path of cold-producing medium:

Compressor 1-first stop valve 4-outdoor heat exchanger 3-the 3rd stop valve 6-gas-liquid separator 2-compressor 1.

Compared with the first embodiment, in this embodiment, when second heat exchanger 102 does not participate in work, the high-temperature high-pressure refrigerant leaving compressor 1 directly can flow to outdoor heat exchanger 3 through the first stop valve 4, and do not need to flow to outdoor heat exchanger 3 again through the second heat exchanger 102, the pressure loss of cold-producing medium can be reduced.Certainly, compared to the first embodiment, under the first dehumidification mode, the cold-producing medium of the second embodiment compressor 1 needs to distribute to two branch roads, the first stop valve 4, second stop valve 5 preferred one of them be flow control valve, facilitate the control of sendout like this.

As shown in Figure 9, Fig. 9 is the structural representation of the third specific embodiment of automotive air-conditioning system provided by the present invention.

This embodiment and the first embodiment similar, unlike, be provided with the by-passing valve 81 in parallel with the first expansion gear 8.Then cold-producing medium can enter First Heat Exchanger 101 after the first expansion gear 8 expands, and also directly can enter First Heat Exchanger 101 through by-passing valve 81.

After arranging by-passing valve 81, other operational modes are substantially identical with the first embodiment, and just heating mode can have two kinds of operational modes:

The first method of operation, by-passing valve 81 cuts out, and the first expansion gear 8 is opened, consistent with the first embodiment method of operation:

The second method of operation, by-passing valve 81 is opened, and the first expansion gear 8 cuts out.The cold-producing medium flowed out through the second stop valve 5 directly enters First Heat Exchanger 101 by by-passing valve 81.Continued to the air stream A heat release entered from the first cycle throttle 106 by the cold-producing medium of First Heat Exchanger 101, after the second expansion gear 9 decrease temperature and pressure, become the cold-producing medium of low-pressure low-temperature after heat exchange, then flow to outdoor heat exchanger 3, finally flow to compressor 1.

The second method of operation, the cold-producing medium flowing to First Heat Exchanger 101 and the second heat exchanger 102 is all in high pressure conditions, therefore is applicable to use when First Heat Exchanger 101 is identical with the second heat exchanger 102 bearing capacity.Compared to the second method of operation, as in the first embodiment, owing to being provided with the first expansion gear 8 between First Heat Exchanger 101 and the second heat exchanger 102 in the first method of operation, make the cold-producing medium in First Heat Exchanger 101 be the gas-liquid two-phase cold-producing medium of medium temperature and medium pressure, heat exchange efficiency is high; And bearing capacity can be adopted to be less than the First Heat Exchanger 101 of the second heat exchanger 102, and intermediate condensation pressure is still in the safe-working pressure scope of First Heat Exchanger 101.

Certainly, by-passing valve 81 being set herein, providing another kind of operational mode, when meeting certain heating needs, the second method of operation can be adopted, to extend the service life of the first expansion gear 8; Or, when the first expansion gear 8 breaks down, can Emergency use the second method of operation, to keep good heat-production functions.

In the various embodiments described above, the outlet of the second expansion gear 9 and the first stop valve 4 can be communicated to the same header of outdoor heat exchanger 3, i.e. inlet header 36.Then no matter which kind of mode of operation, cold-producing medium all flows through outdoor heat exchanger 3 with equidirectional, identical flow direction ensure that cold-producing medium plays good thermodynamic property and dynamic performance all the time in outdoor heat exchanger 3, thus all has good service behaviour under taking into account each pattern.

Please refer to Figure 10, Figure 10 is the structural representation of a kind of specific embodiment of outdoor heat exchanger in automotive air-conditioning system provided by the present invention.

This outdoor heat exchanger 3 has the refrigerating circuit import 31 of being located at inlet header 36 and heats loop import 32.Heat in loop, cold-producing medium enters outdoor heat exchanger 3 through the second expansion gear 9, therefore the second expansion gear 9 can be communicated to and heats loop import 32; In refrigerating circuit, the cold-producing medium of relatively-high temperature enters outdoor heat exchanger 3 through the outlet of the first stop valve 4, therefore the first stop valve 4 can be communicated with refrigerating circuit import 31.In figure, same one end of inlet header 36 is located in two imports, makes cold-producing medium not only flow to unanimously along flat tube 38, flows to the outlet 33 being positioned at outlet collection pipe 37, and also consistent along the flow direction of inlet header 36.In addition, be designed to two independently imports, be also convenient to being communicated with of different branch and outdoor heat exchanger 3.

This outdoor heat exchanger 3 specifically comprises inlet header 36 and outlet collection pipe 37, distributing pipe 34 is fitted with in inlet header 36, some flat tubes 38 be arranged in parallel are provided with between inlet header 36 and outlet collection pipe 37, be provided with the fin 39 strengthening heat transfer effect between flat tube 38, fin 39 can be fixedly welded between flat tube 38.In addition, distributing pipe 34 is provided with the some dispensing orifices 35 distributed along its length, and dispensing orifice 35 is towards each flat tube 38, and cold-producing medium can evenly flow in each flat tube 38 after distributing pipe 34 distributes.During installation room external heat exchanger 3, preferably the inlet header 36 being provided with distributing pipe 34 is arranged in directly over outlet collection pipe 37 or oblique upper, so that cold-producing medium flows fast.

Now, heat loop import 32 and can be communicated with distributing pipe 34, refrigerating circuit import 31 can directly insert inlet header 36, and refrigerating circuit import 31 is independent of distributing pipe 34.Refrigerant flow direction distributing pipe 34 after the second expansion gear 9 decrease temperature and pressure, enters each flat tube 38 after distribution, then through outlet collection pipe 37 delivery chamber external heat exchanger 3; Cold-producing medium through relatively-high temperature high pressure then directly enters in inlet header 36, then through flat tube 38 delivery chamber external heat exchanger 3.

Design like this, under refrigeration mode, the first dehumidification mode and dehumidification mode, the gaseous refrigerant of HTHP, directly can enter in the inlet header 36 of outdoor heat exchanger 3 through the first stop valve 4, because cold-producing medium is now single gaseous state, there is good allocation performance, without the need to distributing through distributing pipe 34, just do not need, through dispensing orifice 35, can the pressure loss be reduced yet; And under other patterns, by the low-temperature low-pressure refrigerant formed after the second expansion gear 9 decrease temperature and pressure, evenly entering flat tube 38 after the distributing pipe 34 of outdoor heat exchanger 3 distributes carries out heat exchange, heat exchange efficiency can be improved.Therefore, this outdoor heat exchanger 3, according to the gaseous state of cold-producing medium and liquid two kinds of phases, sets out corresponding import respectively, realizes the optimized design of exchange capability of heat.

It should be noted that, in Figure 10, refrigerating circuit import 31 and heat one end that loop import 32 is all arranged at inlet header 36, in fact, the two other position being arranged at inlet header 36 is also the object that can realize cold-producing medium co-flow in each mode, such as, the central region of inlet header 36 can be all arranged at.

All participate in the embodiment of work for above-mentioned first expansion gear 8 and the second expansion gear 9, namely air-conditioning system is in heating mode, and two expansion gears can control in the following manner.

Please refer to the first control principle drawing that Figure 11-12, Figure 11 is expansion gear under heating mode in Fig. 4, dotted line illustrates feedback signal; Figure 12 is the control flow chart of two expansion gears in control Figure 11.

As shown in figure 11, outlet pressure, the outlet temperature of the outlet 1011 place cold-producing medium flowing out First Heat Exchanger 101 is detected, to obtain the degree of supercooling of First Heat Exchanger 101; Outlet pressure, the outlet temperature of the outlet 33 place cold-producing medium of sensing chamber's external heat exchanger 3, to obtain the degree of superheat of outdoor heat exchanger 3.The feedback signal controlling the first expansion gear 8 comes from the degree of supercooling of First Heat Exchanger 101, and the feedback signal controlling the second expansion gear 9 comes from the degree of superheat of outdoor heat exchanger 3.

The step controlling the first expansion gear 8 and the second expansion gear 9 comprises as follows:

S11, according to arranging operating mode and temperature draws the degree of superheat of corresponding preferably outdoor heat exchanger 3 and the degree of supercooling of First Heat Exchanger 101, specifically can by system according to verification experimental verification Post RDBMS in the controls;

The outlet pressure p3 of S12, sensing chamber's external heat exchanger 3 and outlet temperature t3;

S13, obtain the actual degree of superheat of outdoor heat exchanger 3 according to the outlet pressure p3 of outdoor heat exchanger 3 and outlet temperature t3;

Can calculated temperature according to the following equation:

Wherein, actual degree of superheat SH3=t3-ts3, ts3 are the saturation temperature that cold-producing medium is corresponding when pressure p 3;

S14, compare the actual degree of superheat of outdoor heat exchanger 3 and the default degree of superheat, if the former is greater than the latter, then enter step S141, be less than, then enter step S142, equal, then enter step S143;

S141, increase by the second expansion gear 9 aperture;

S142, reduce the second expansion gear 9 aperture;

S143, keep the current aperture of the second expansion gear 9 constant.

When concrete execution step S141, S142, by presetting and actual degree of superheat difference of calculating in S14, the adjustment stepping of the second expansion gear 9 can be controlled, with the degree of superheat making the actual degree of superheat reach default.

By step S141, S142, S143, after making the actual degree of superheat of outdoor heat exchanger 3 reach the default degree of superheat, can continue to perform step S15:

S15, the outlet pressure p101 detecting First Heat Exchanger 101 and outlet temperature t101;

S16, obtain the actual degree of supercooling of First Heat Exchanger 101 according to the outlet pressure of First Heat Exchanger 101 and outlet temperature;

Degree of supercooling can be calculated according to the following equation:

Wherein, actual degree of supercooling SC101=ts101-t101, ts101 are the saturation temperature that cold-producing medium is corresponding when pressure p 101;

S17, compare the actual degree of supercooling of First Heat Exchanger 101 and default degree of supercooling, if the former is greater than the latter, then enter step S171, be less than, then enter step S172, equal, then enter step S173;

S171, reduce the first expansion gear 8 aperture;

S172, increase by the first expansion gear 8 aperture;

S173, keep the current aperture of the first expansion gear 8 constant.

When concrete execution step S171, S172, by presetting and actual degree of supercooling difference of calculating in S17, the adjustment stepping of the first expansion gear 8 can be controlled, with the degree of supercooling making actual degree of supercooling reach default.

By step S171, S172, S173, after making the actual degree of supercooling of First Heat Exchanger 101 reach default degree of supercooling, step S12 can be returned.

In above-mentioned control procedure, when systemic presupposition degree of supercooling and the degree of superheat, a predeterminable tolerance, namely preset value is value range.Relatively when preset value and actual value, as long as difference is in the margin of tolerance, just without the need to adjusting the aperture of expansion gear.Tolerance is set, can the accidental fluctuation of anti-locking system the measurement of the degree of superheat, degree of supercooling be affected, in order to avoid the adjustment of expansion gear is too frequent.

This control method first regulates the aperture of the second expansion gear 9, in fact this can produce certain influence to the first expansion gear 8, and then adjust the first expansion gear 8 aperture, be actually and achieve jointly controlling of two expansion gears, to make final adjustment result as far as possible close to practical adjustments demand, realize the optimized control of two expansion gears.

Regulate expansion gear according to the degree of superheat and degree of supercooling, combine pressure and temperature, regulate result the most accurate.Be appreciated that the control only carrying out expansion gear according to temperature or pressure is also feasible, just regulating effect is inferior to the adjustment according to the degree of superheat or degree of supercooling.

The first expansion gear 8 and the second expansion gear 9 can also be controlled by other means.

Please refer to the second control principle drawing that Figure 13-14, Figure 13 is expansion gear under heating mode in Fig. 4, two expansion gears are electric expansion valve, and in figure, dotted line illustrates feedback signal; Figure 14 is the control flow chart of two expansion gears in control Figure 13.

In this control mode, the feedback signal controlling the first expansion gear 8 comes from the degree of supercooling of the second heat exchanger 102, as shown in figure 13, detect outlet pressure and the outlet temperature at outlet 1021 place of the second heat exchanger 102, the feedback signal controlling the second expansion gear 9 comes from the degree of supercooling of First Heat Exchanger 101, detects outlet pressure, the outlet temperature at outlet 1011 place of First Heat Exchanger 101.

The step controlling the first expansion gear 8 and the second expansion gear 9 is as follows:

S21, according to arranging operating mode and temperature draws the corresponding preferably degree of supercooling of the second heat exchanger 102 and the degree of supercooling of First Heat Exchanger 101, specifically can by system according to verification experimental verification Post RDBMS in the controls;

S22, the outlet pressure p102 detecting the second heat exchanger 102 and outlet temperature t102;

S23, obtain the actual degree of supercooling of the second heat exchanger 102 according to the outlet pressure p102 of the second heat exchanger 102 and outlet temperature t102;

Degree of supercooling can be calculated according to the following equation:

Wherein, actual degree of supercooling SC102=ts102-t102, ts102 are the saturation temperature that cold-producing medium is corresponding when pressure p 102;

S24, compare the actual degree of supercooling of the second heat exchanger 102 and default degree of supercooling, if the former is greater than the latter, then enter step S242, be less than, then enter step S241, equal, then enter step S243;

S241, reduce the first expansion gear 8 aperture;

S242, increase by the first expansion gear 8 aperture;

S243, keep the current aperture of the first expansion gear 8 constant.

When concrete execution step S241, S242, by presetting and actual degree of supercooling difference of calculating in S24, the adjustment stepping of the first expansion gear 8 can be controlled, with the degree of supercooling making actual degree of supercooling reach default.

By step S241, S242, S243, after making the actual degree of supercooling of the second heat exchanger 102 reach default degree of supercooling, can continue to perform step S25:

S25, the outlet pressure p101 detecting First Heat Exchanger 101 and outlet temperature t101;

S26, obtain the actual degree of supercooling of First Heat Exchanger 101 according to the outlet pressure p101 of First Heat Exchanger 101 and outlet temperature t101;

Degree of supercooling can be calculated according to the following equation:

S27, compare the actual degree of supercooling of First Heat Exchanger 101 and default degree of supercooling, if the former is greater than the latter, then enter step S272, be less than, then enter step S271, equal, then enter step S273;

S271, reduce the second expansion gear 9 aperture;

S272, increase by the second expansion gear 9 aperture;

S273, keep the current aperture of the second expansion gear 9 constant.

When concrete execution step S271, S272, by presetting and actual degree of supercooling difference of calculating in S27, the adjustment stepping of the second expansion gear 9 can be controlled, with the degree of supercooling making actual degree of supercooling reach default.

By step S271, S272, S273, after making the actual degree of supercooling of First Heat Exchanger 101 reach default degree of supercooling, step S22 can be returned.

Identical with the first control mode, when systemic presupposition degree of supercooling and the degree of superheat, a predeterminable tolerance, namely preset value is value range.Relatively when preset value and actual value, as long as difference is in the margin of tolerance, just without the need to adjusting the aperture of expansion gear.

Because the first expansion gear 8 is arranged between First Heat Exchanger 101 and the second heat exchanger 102, then the aperture of the first expansion gear 8 can regulate according to the degree of supercooling of arbitrary heat exchanger in these two kinds; And the second expansion gear 9 is located between First Heat Exchanger 101 and outdoor heat exchanger 3, then the second expansion gear 9 aperture is opened and is regulated according to the degree of superheat of outdoor heat exchanger 3 or the degree of supercooling of First Heat Exchanger 101.So, in order to realize jointly controlling of two expansion gears, the first control mode above-mentioned or the second control mode can be taked.

It should be noted that, the first control mode above-mentioned, the degree of superheat of first conditioning chamber external heat exchanger 3, then regulate the degree of supercooling of First Heat Exchanger 101; The second control mode, first regulates the degree of supercooling of the second heat exchanger 102, then regulates the degree of supercooling of First Heat Exchanger 101.Why taking such priority adjustment order, is because consider the priority relationship of each heat exchanger in this air-conditioning system.Air-conditioning system in above-described embodiment, according to heat exchange amount from large to small, when heating mode, three kinds of heat exchangers on the sequencing of the impact of heating effect are: the second heat exchanger 102, outdoor heat exchanger 3, First Heat Exchanger.Therefore, during adjustment, first regulate priority the second heat exchanger 102 formerly or outdoor heat exchanger 3, then regulate the posterior First Heat Exchanger 101 of priority, adjustment efficiency can be promoted significantly, improve regulating effect.

Accordingly, even if be appreciated that the order not in accordance with the first control mode above-mentioned or the second control mode is also feasible.Such as, in the first control mode, first can regulate the aperture of the first expansion gear 8, then regulate the aperture of the second expansion gear 9; In the second control mode, first can regulate the aperture of the second expansion gear 9, then regulate the aperture of the first expansion gear 8, all can realize jointly controlling object, just regulate efficiency and effect inferior to above-described embodiment.

In view of above-mentioned control mode, be appreciated that the embodiment for arranging by-passing valve 81, cold-producing medium is when by-passing valve 81, and without the need to jointly controlling the first expansion gear 8 and the second expansion gear 9, only control the second expansion gear 9, control procedure is relatively simple.In addition, when the second heat exchanger 102 is communicated with First Heat Exchanger 101 by the expansion gear arranged separately, namely the first expansion gear 8 in above-mentioned control mode replaces with this expansion gear arranged separately, to jointly control with the second expansion gear 9.

For the various embodiments described above, further improvement can also be made.

As shown in figure 15, Figure 15 is the structural representation of automotive air-conditioning system provided by the present invention 4th kind of specific embodiment.

In this embodiment, air-conditioning system specifically also comprises battery case 200, and when automobile adopts electric power, such as electric automobile or hybrid vehicle, battery case 200 can be used for the heat management to battery 300.This embodiment, except battery case 200 and via design thereof, remainder and the first embodiment similar, be appreciated that other embodiments all can according to the present embodiment arrange battery case 200 and related pathways design, principle is identical, repeats no more.

Battery case 200 is provided with the second outer circulation air port 205, second, Inner eycle air port 206, second cycle throttle 204, similar with the first cycle throttle 106 being located at air-conditioning box 100 place, the second cycle throttle 204 can be controlled according to the actual requirements, control the mixing wind ratio entered through the second Inner eycle air port 206 and the second outer circulation air port 205, to form required air stream E.Battery 300 can be located in battery case 200, correspondingly in battery case 200, arranges battery heat exchanger 201.

In addition, the air stream G after battery 300 is introduced two branch roads by battery case 200, and a branch road can be communicated to the second Inner eycle air port 206 at the second cycle throttle 204 place, and another branch road is communicated to outside compartment.The flow direction of air stream G is controlled by inside and outside air door 405.

As shown in figure 15, wind inlet channel 401 is provided with between battery 300 and battery heat exchanger 201, exhaust air flue 402 is provided with between battery 300 and inside and outside air door 405, article two, branch road be respectively the first air channel 403 of being communicated with the second Inner eycle air port 206 and with the second air channel 404 be communicated with outside compartment, exhaust air flue 402 and the first air channel 404, air channel 403, second form trident path, arrange inside and outside air door 405 at fork place.In Figure 15, when inside and outside air door 405 is opened towards the right side, the second air channel 404 is closed, and the first air channel 403 is opened; When inside and outside air door 405 is opened towards a left side, the first air channel 403 is closed, and the second air channel 404 is opened.Design like this, the design in air channel is simplified, and be appreciated that design is non-interference separately for the first air channel 403 and the second air channel 404, and exhaust air flue 402 is also feasible by the break-make in two airdoor controls and the first air channel 404, air channel 403, second.

Enter battery heat exchanger 201 for the ease of air stream E through the second cycle throttle 204 place, the second air blast 203 can be set between the second cycle throttle 204 and battery heat exchanger 201.

The import of battery heat exchanger 201 cold-producing medium can the outlet of communication chamber external heat exchanger 3, the path of the two is provided with the 3rd expansion gear 12, the break-make of this path can be controlled by the 5th stop valve 11, when the 3rd expansion gear 12 has keying function, also can be controlled voluntarily by the 3rd expansion gear 12; The import of the outlet compressor 1 of battery heat exchanger 201, is generally then communicated with the gas-liquid separator 2 of compressor 1 import department.

Please refer to Figure 16, Figure 16 is refrigerant flowpath schematic diagram when air-conditioning system is in refrigeration mode in Figure 15, and wherein thickened portion represents flow path.

During refrigeration, the 5th stop valve 11 is opened, and air-conditioning box 100, outdoor heat exchanger 3 etc. are consistent with the refrigeration mode in the first embodiment.Herein, repeat no more.

The cold-producing medium that outdoor heat exchanger 3 flows out, the kind of refrigeration cycle that a road flows to the first expansion gear 8, First Heat Exchanger 101 carries out as in the first embodiment; Another road flows to the 3rd expansion gear 12 and expands, decrease temperature and pressure is the cold-producing medium of low-temp low-pressure, enter battery heat exchanger 201 and carry out heat exchange, absorb air stream E heat, form cold air stream F, air stream F flows through battery 300 and lowers the temperature to it, cold-producing medium is then phase-changed into low-pressure gaseous, converge with the cold-producing medium flowed out from the 4th stop valve 7 and enter gas-liquid separator 2 and be separated, and enter in compressor 1, periodic duty like this.

In fact, battery heat exchanger 201 and First Heat Exchanger 101 are in and are arranged in parallel, and the work of the two does not interfere with each other.According to system actual condition, the work of First Heat Exchanger 101 and battery heat exchanger 201 can be controlled, thus simultaneously for passenger compartment, battery 300 provide low-temperature receiver, or separately for passenger compartment or battery 300 provide low-temperature receiver.Such as:

When thermic load in ambient temperature and car is not very high, and when battery case 200 thermic load is higher, passenger compartment is without the need to refrigeration, battery case 200 needs cooling, then can close the first expansion gear 8, open the 5th stop valve 11, First Heat Exchanger 101 does not work, and battery heat exchanger 201 works; Namely independent battery 300 freezes;

When in ambient temperature or car, thermic load is high, and when battery case 200 thermic load is lower, then can open the first expansion gear 8, close the 5th stop valve 11 (when the 3rd expansion gear 12 has keying function, also can close the 3rd expansion gear 12); I.e. independent passenger compartment refrigeration;

When in ambient temperature or car, thermic load is higher, and when battery case 200 thermic load is higher, the first expansion gear 8 and the 5th stop valve 11 are all opened, and as shown in figure 16, namely freeze for passenger compartment and battery 300 simultaneously.

During refrigeration, battery case 200 can have two kinds of mode of operations:

Battery case 200 Inner eycle pattern:

When the leaving air temp of ambient temperature higher than battery 300, close the second outer circulation air port 205, and disconnect the second air channel 404 and exhaust air flue 402 by inside and outside air door 405, enter in battery case 200 to make battery 300 air-out lower than external environment temperature in exhaust air flue 402 through the first Inner eycle air port 206, air channel 403, second, in battery heat exchanger 201 place's heat exchange, thus save the energy;

Battery case 200 outer circulation pattern:

When the leaving air temp of ambient temperature lower than battery 300, close the second Inner eycle air port 206, and disconnect the first air channel 403 and exhaust air flue 402 by inside and outside air door 405, the air of extraneous lower temperature can enter in battery case 200 through the second outer circulation air port 205 and participate in heat exchange refrigeration, for battery 300 is lowered the temperature, the air stream G after being heated by battery 300 through exhaust air flue 402, second air channel 404 discharged in external environment.

Battery 300 outer circulation pattern is applicable to the operating mode of ambient temperature lower than battery 300 leaving air temp, therefore in this mode, can determine that battery heat exchanger 201 is the need of working on according to the temperature of battery 300.If battery 300 needs further cooling, then the 5th stop valve 11 continues to open, and carries out kind of refrigeration cycle; If battery 300 can be operated in suitable temperature range, then the 5th stop valve 11 can have been closed, and battery heat exchanger 201 does not work, further economize energy.

Please refer to Figure 17, Figure 17 is refrigerant flowpath schematic diagram when air-conditioning system is in heating mode in Figure 15, and wherein thickened portion represents flow path.

When heating, battery heat exchanger 201 does not work, and the 5th stop valve 11 is closed, and air-conditioning box 100, outdoor heat exchanger 3 etc. are consistent with the heating mode in the first embodiment.Herein, repeat no more.

Now, battery case 200 can have two kinds of mode of operations:

Battery 300 heating mode:

When ambient temperature is very low, when battery 300 needs to heat, the second electric heater 202 can be made to be energized, the air stream E then entered through the second cycle throttle 204 can heat through the second electric heater 202, air stream F after heating is sent in battery 300 by wind inlet channel 401, heats up to battery 300.

Inside and outside air door 405, cut off exhaust air flue 402 and the second air channel 404, but be communicated with the first air channel 403 and exhaust air flue 402, and second cycle throttle 204 cut off the second outer circulation air port 205, the air stream E then entered from the second cycle throttle 204 all comes from battery 300 air-out, can save the energy.

Battery 300 refrigerating mode:

When ambient temperature is lower, but when battery 300 self-heating needs to cool, outside air can be utilized to cool battery 300.Now, the second Inner eycle air port 206 can be closed, outside cold air enters the second battery case 200 through the second outer circulation air port 205, and according to this through battery heat exchanger 201, second electric heater 202, and then enter in battery 300 and carry out nature cooling, battery heat exchanger 201 and the second electric heater 202 do not work.In addition, control exhaust air flue 402 by inside and outside air door 405 and be communicated with the second air channel 404, battery 300 air-out through exhaust air flue 402, second air channel 404 discharged in the external environment condition outside compartment.

Please refer to Figure 18, Figure 18 is refrigerant flowpath schematic diagram when air-conditioning system is in heating mode and is in battery waste heat recovery pattern in Figure 15, and wherein thickened portion represents flow path.

Battery 300 waste heat recovery pattern:

When environment temperature is low-down time, but when the heating of battery 300 self can provide enough waste heats to utilize, battery 300 waste heat recovery pattern can also be used, further raising system heating efficiency, economize energy.

First stop valve 4, the 4th stop valve 7 are closed, and the second stop valve 5, the 3rd stop valve 6, the 5th stop valve 11 are opened.Flow out refrigerant flow direction two branch roads of the second stop valve 5, a branch road flows to the first expansion gear 8, carry out as in the first embodiment heat circulation; The high-pressure refrigerant of another article of branch road is expanded into the cold-producing medium of low-temp low-pressure through the 3rd expansion gear 12, enter battery heat exchanger 201, absorb and to be generated heat the heat compared with thermal air current formed by battery 300, be heated to be low-pressure gaseous refrigerant, the cold-producing medium flowed out with the 3rd stop valve 6 converges, and enters gas-liquid separator 2, thus can improve the intake air temperature of cold-producing medium here and improve system effectiveness, finally enter compressor 1, periodic duty like this.

Air stream after battery heat exchanger 201 place carries out heat exchange is cooled, and cooled air stream F is sent in battery 300 through wind inlet channel 401, lowers the temperature to battery 300, and the air stream of cooling is heated to be air stream G again, enters exhaust air flue 402.Now, inside and outside air door 405 cuts off the second air channel 404, and exhaust air flue 402 is communicated with the first air channel 403, and also cut off outer circulation air door, battery 300 air-out is entered in the second battery case 200 by the second Inner eycle air port 206, so circulates simultaneously.

Battery 300 waste heat recovery pattern, by battery 300 exhaust-heat absorption also by refrigerant system, can make compressor 1 delivery temperature relatively improve, improves the heat capacity of system, save the energy further.

After arranging battery case 200, it can carry out the first dehumidification mode, the second dehumidification mode and defrosting mode as in the first embodiment, repeats no more herein.

It should be noted that, specifically describe multiple stop valve in the various embodiments described above, realized the break-make of place branch road by the keying of stop valve, thus realize the switching of multiple mode of operation, stop valve structure is simple, and break-make controls reliable.Being appreciated that those skilled in the art can also realize the formation of each pattern underpass by other means, being not limited to above-mentioned stop valve embodiment, carrying out alternative two stop valves etc. as utilized three-way switch valve.Such as, for the first embodiment, when carrying out heating mode, the cold-producing medium flowing out First Heat Exchanger 101 needs the branch road flowing to the second expansion gear 9 place, and the 4th stop valve 7 is closed, for reaching this object, the 4th stop valve 7 can be cancelled, and transfer valve is directly set, refrigerant flow path to be switched to the branch road at the second expansion gear 9 place, or switch to the branch road (e.g., refrigeration mode) being communicated with compressor 1 import.

For another example, still for the first embodiment, the first stop valve 4 and the second stop valve 5 can be substituted by a transfer valve.The like, no longer enumerate herein.Expansion gear in addition in the present invention is preferably electric expansion valve, thus can realize the interlock with controller, thus realizes preferably control effects.

It should be noted that, the set-up mode of First Heat Exchanger 101, second heat exchanger 102, outdoor heat exchanger 3 in the application, under making arbitrary pattern, the import and export of each heat exchanger all can not occur not only as import but also as situation about exporting, thus the ability of heat exchanger is played.

Above automotive air-conditioning system provided by the present invention and control method thereof are all described in detail.Apply specific case herein to set forth principle of the present invention and embodiment, the explanation of above embodiment just understands method of the present invention and core concept thereof for helping.It should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention, can also carry out some improvement and modification to the present invention, these improve and modify and also fall in the protection domain of the claims in the present invention.

Claims

1. an automotive air-conditioning system, comprise compressor (1), First Heat Exchanger (101), first expansion gear (8), second heat exchanger (102), and outdoor heat exchanger (3), second expansion gear (9), described compressor (1), described outdoor heat exchanger (3), described first expansion gear (8), described First Heat Exchanger (101) can form refrigerating circuit by sequential communication, it is characterized in that, described compressor (1), described second heat exchanger (102), described First Heat Exchanger (101), described second expansion gear (9), described outdoor heat exchanger (3) sequential communication formation can heat loop, and when heating mode, air stream first flows through described First Heat Exchanger (101) and carries out heat exchange intensification, and then flow through described second heat exchanger (102).

2. automotive air-conditioning system as claimed in claim 1, it is characterized in that, the import of the second heat exchanger (102) described in the outlet of described compressor (1), the outlet of described second heat exchanger (102) is communicated with described outdoor heat exchanger (3) by a branch road, is communicated with the import of described First Heat Exchanger (101) by another branch road; Described second heat exchanger (102) place is provided with temperature damper (105), and described temperature damper (105) is opened in time heating.

3. automotive air-conditioning system as claimed in claim 1, it is characterized in that, the outlet of described compressor (1) is communicated with described outdoor heat exchanger (3) by a branch road, is communicated with the import of described second heat exchanger (102) by another branch road.

4. automotive air-conditioning system as claimed in claim 2 or claim 3, it is characterized in that, the outlet of described second heat exchanger (102) is communicated with the import of described First Heat Exchanger (101) by described first expansion gear (8), the first expansion gear (8) is electric expansion valve.

5. automotive air-conditioning system as claimed in claim 4, it is characterized in that, described first expansion gear (8) is parallel with by-passing valve (81).

6. the automotive air-conditioning system as described in as arbitrary in claim 1-5, it is characterized in that, a header of described outdoor heat exchanger (3) is provided with refrigerating circuit import (31) and heats loop import (32); Be provided with distributing pipe (35) in header described in this, described in heat loop import (32) and be directly communicated with described distributing pipe (35); Described refrigerating circuit import (31) is directly communicated with described header, and described refrigerating circuit import (31) and described distributing pipe (35) are independent mutually.

7. automotive air-conditioning system as claimed in claim 1, is characterized in that, also comprise the controller of default described First Heat Exchanger (101) degree of supercooling, described outdoor heat exchanger (3) degree of superheat;

Described controller first obtains the degree of superheat of described outdoor heat exchanger (3), and compares with the degree of superheat preset the aperture regulating described second expansion gear (9); After adjustment, described controller also obtains the degree of supercooling of described First Heat Exchanger (101), and compares with the degree of supercooling preset the aperture regulating described first expansion gear (8);

Or described controller first obtains the degree of supercooling of described First Heat Exchanger (101), and compare with the degree of supercooling preset the aperture regulating described first expansion gear (8); After adjustment, described controller also obtains the degree of superheat of described outdoor heat exchanger (3), and compares with the degree of superheat preset the aperture regulating described second expansion gear (9).

8. automotive air-conditioning system as claimed in claim 1, is characterized in that, also comprise the controller of default described First Heat Exchanger (101) degree of supercooling, described second heat exchanger (102) degree of supercooling;

Described controller first obtains the degree of supercooling of described second heat exchanger (102), and compares with the degree of supercooling preset the aperture regulating described first expansion gear (8); After adjustment, described controller also obtains the degree of supercooling of described First Heat Exchanger (101), and compares with the degree of supercooling preset the aperture regulating described second expansion gear (9);

Or described controller obtains the degree of supercooling of described First Heat Exchanger (101), and compare with the degree of supercooling preset the aperture regulating described second expansion gear (9); After adjustment, described controller also obtains the degree of supercooling of described second heat exchanger (102), and compares with the degree of supercooling preset the aperture regulating described first expansion gear (8).

9. the automotive air-conditioning system as described in claim 1-3, any one of 6-8, it is characterized in that, the 3rd expansion gear (12) also comprising battery (300), battery heat exchanger (201) and be communicated with it, the import of described 3rd expansion gear (12) can be communicated with the outlet of described outdoor heat exchanger (3) and the outlet of described second heat exchanger (102); The import of compressor (1) described in the outlet of described battery heat exchanger (201).

10. automotive air-conditioning system as claimed in claim 9, is characterized in that, comprises the battery case (200) holding described battery (300), described battery heat exchanger (201); The air inlet of described battery case (200) be provided be communicated with car indoor Inner eycle air port, with the outer circulation air port be communicated with outside compartment, and the cycle throttle in adjustment Inner eycle air port and outer circulation air port.

11. automotive air-conditioning systems as claimed in claim 10, it is characterized in that, also be provided with the first air channel (403) and the second air channel (404), and control the inside and outside air door (405) of the air outlet of described battery case (200) and described first air channel (403), described second air channel (404) break-make; Described first air channel (403) is communicated with described Inner eycle air port, outside described second air channel (404) open car.

The control method of 12. 1 kinds of automotive air-conditioning systems as claimed in claim 4, is characterized in that, comprises the steps:

According to arranging operating mode and temperature draws the degree of superheat of corresponding outdoor heat exchanger (3) and the degree of supercooling of First Heat Exchanger (101);

By the outlet pressure of sensing chamber's external heat exchanger (3), the actual degree of superheat of outlet temperature acquisition outdoor heat exchanger (3), by detecting the outlet pressure of First Heat Exchanger (101), the actual degree of supercooling of outlet temperature acquisition First Heat Exchanger (101);

Carry out aperture adjustment, wherein, the second expansion gear (9) is heating power expansion valve or electric expansion valve:

The degree of superheat first comparing outdoor heat exchanger (3) the actual degree of superheat and preset, if the former is greater than the latter, then increases the second expansion gear (9) aperture; The former is less than the latter, reduces the second expansion gear (9) aperture; The former equals the latter, then keep the current aperture of the second expansion gear (9) constant;

The degree of supercooling comparing First Heat Exchanger (101) actual degree of supercooling again and preset, if the former is greater than the latter, then reduces the first expansion gear (8) aperture; The former is less than the latter, increases the first expansion gear (8) aperture; The former equals the latter, keeps the current aperture of the first expansion gear (8) constant;

Or the degree of supercooling first comparing First Heat Exchanger (101) actual degree of supercooling and preset, if the former is greater than the latter, then reduces the first expansion gear (8) aperture; The former is less than the latter, then increase the first expansion gear (8) aperture; The former equals the latter, then keep the current aperture of the first expansion gear (8) constant;

The degree of superheat comparing outdoor heat exchanger (3) the actual degree of superheat again and preset, if the former is greater than the latter, then increases the second expansion gear (9) aperture; The former is less than the latter, then reduce the second expansion gear (9) aperture; The former equals the latter, keeps the current aperture of the second expansion gear (9) constant.

The control method of 13. 1 kinds of automotive air-conditioning systems as claimed in claim 4, is characterized in that, comprises the steps:

According to arranging operating mode and temperature draws the degree of supercooling of corresponding second heat exchanger (102) and the degree of supercooling of First Heat Exchanger (101);

By the actual degree of supercooling detecting the outlet pressure of the second heat exchanger (102), outlet temperature obtains the second heat exchanger (102), by the actual degree of supercooling detecting the outlet pressure of First Heat Exchanger (101), outlet temperature obtains First Heat Exchanger (101);

Carry out aperture adjustment, wherein, the second expansion gear (9) is electric expansion valve:

The degree of supercooling first comparing the second heat exchanger (102) actual degree of supercooling and preset, if the former is greater than the latter, then increases the first expansion gear (8) aperture; The former is less than the latter, reduces the first expansion gear (8) aperture; The former equals the latter, then keep the current aperture of the first expansion gear (8) constant;

The degree of supercooling comparing First Heat Exchanger (101) actual degree of supercooling again and preset, if the former is greater than the latter, then increases the second expansion gear (9) aperture; The former is less than the latter, reduces the second expansion gear (9) aperture; The former equals the latter, keeps the current aperture of the second expansion gear (9) constant;

Or the degree of supercooling first comparing First Heat Exchanger (101) actual degree of supercooling and preset, if the former is greater than the latter, then increases the second expansion gear (9) aperture; The former is less than the latter, then reduce the second expansion gear (9) aperture; The former equals the latter, then keep the current aperture of the second expansion gear (9) constant;

The degree of supercooling comparing the second heat exchanger (102) actual degree of supercooling again and preset, if the former is greater than the latter, then increases the first expansion gear (8) aperture; The former is less than the latter, then reduce the first expansion gear (8) aperture; The former equals the latter, keeps the current aperture of the first expansion gear (8) constant.