CN210980112U

CN210980112U - Air conditioner

Info

Publication number: CN210980112U
Application number: CN201922012624.6U
Authority: CN
Inventors: 刘晓蕾; 曹法立; 张恒; 刘敏; 邓玉平
Original assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Current assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date: 2019-11-20
Filing date: 2019-11-20
Publication date: 2020-07-10
Anticipated expiration: 2029-11-20

Abstract

The utility model discloses an air conditioner, a heat exchanger is arranged on a heat exchange loop; the heat exchanger comprises a flat pipe, a first collecting pipe, a separator, a gas distributing pipe group and a liquid distributing pipe group; an upper chamber and a lower chamber are formed in the first collecting pipe, and are communicated with the flat pipes; the separator is used for separating gas-phase refrigerant and liquid-phase refrigerant; the gas distributing pipe group is communicated between the separator and the lower chamber; the liquid separating pipe group is communicated between the separator and the lower chamber. When the heat exchanger is used as an evaporator, a gas-liquid two-phase refrigerant is effectively separated by the separator before entering the lower cavity, a gas-phase refrigerant enters the lower cavity through the gas-separating pipe group, and a liquid-phase refrigerant enters the lower cavity through the liquid-separating pipe group, so that the interaction and mutual separation of the two-phase refrigerants in the flowing process are fundamentally avoided, the gas-liquid separation phenomenon of the refrigerants does not exist in the lower cavity, and the distribution uniformity of the refrigerants in the flat pipes is improved.

Description

Air conditioner

Technical Field

The utility model relates to a refrigeration plant technical field especially relates to an even air conditioner of refrigerant reposition of redundant personnel.

Background

At present, a heat pump type air conditioner is a kind of cooling and heating air conditioner which is often used. When cooling in summer, the air conditioner cools indoors and radiates heat outdoors, and when heating in winter, the direction is opposite to that in summer, namely, the air conditioner heats indoors and cools outdoors. The air conditioner exchanges heat and cold between different environments through a heat pump. For example, in winter, outdoor air, ground water, underground water and the like are low-temperature heat sources, indoor air is a high-temperature heat source, and the heat pump type air conditioner is used for transferring heat of an outdoor environment into the indoor environment.

Referring to fig. 1, a schematic diagram of a heating cycle of a heat pump in the prior art is shown. The heat pump includes: the system comprises an evaporator 1, a compressor 2, a condenser 3, an expansion valve 4 and a four-way reversing valve C. The specific working process of the heat pump heating is as follows: first, a low-pressure two-phase refrigerant (a mixture of a liquid-phase refrigerant and a gas-phase refrigerant) in the evaporator 1 absorbs heat from a low-temperature environment; the gas refrigerant is sucked by the compressor 2 and then compressed into a high-temperature high-pressure gas refrigerant; then, the high-temperature and high-pressure gas refrigerant releases heat energy to the indoor environment in the condenser 3, and the temperature of the gas refrigerant is reduced; finally, the refrigerant is throttled by the expansion valve mechanism 4 to become a low-temperature low-pressure two-phase refrigerant, and the refrigerant enters the evaporator 1 again, and the above-described cycle heating process is repeated. The heat exchanger described herein comprises the evaporator 1 and the condenser 3 described above.

The heat pump air conditioner changes the working condition mode through the four-way reversing valve C. Under the refrigeration working condition in summer, the indoor heat exchanger is used as the evaporator 1, and the outdoor heat exchanger is used as the condenser 3. The indoor air is cooled down by the surface of the evaporator 1 to achieve the purpose of reducing the indoor temperature, and the heat is transmitted to the outdoor through the condenser 3. When heat is supplied in winter, the position of the valve block C of the four-way reversing valve is changed, so that the flow direction of the refrigerant is changed, and at the moment, the refrigerant absorbs heat in the environment through the outdoor heat exchanger and releases heat to the indoor environment, so that the purpose of heating is achieved.

The evaporator 1 is a device for outputting cold energy, and functions to evaporate the refrigerant liquid flowing in through the expansion valve 4 to absorb heat of the object to be cooled, thereby achieving the purpose of refrigeration. The condenser 3 is a device for outputting heat, and the heat absorbed from the evaporator 1 and the heat converted by the work consumed by the compressor 2 are carried away by the cooling medium in the condenser 3, so as to achieve the purpose of heating. The evaporator 1 and the condenser 3 are important parts for heat exchange in the air-conditioning heat pump unit, and the performance of the evaporator and the condenser directly affects the performance of the whole system.

Compared with a finned tube heat exchanger, the micro-channel heat exchanger has remarkable advantages in the aspects of material cost, refrigerant filling amount, heat flux density and the like, and accords with the development trend of energy conservation and environmental protection of the heat exchanger. The micro-channel heat exchanger comprises flat tubes, fins, collecting pipes, end covers and the like. A separation clapboard is also inserted into the collecting pipe of the multi-flow micro-channel heat exchanger, the collecting pipe is divided into a plurality of independent cavities by the clapboard, and each collecting pipe cavity is communicated with a certain number of flat pipes. When the microchannel heat exchanger is used as an evaporator, when a gas-liquid two-phase refrigerant enters a plurality of flat tubes from a flow collecting tube cavity, the flowing refrigerant is easily separated under the action of gravity and viscous force due to the difference between the density and the viscosity of a gas phase and a liquid phase, so that the refrigerant entering the plurality of flat tubes is uneven. Refrigerant non-uniformity not only deteriorates heat exchange efficiency but also causes fluctuation of the refrigeration system. Therefore, it is an important issue to achieve uniform distribution of two-phase refrigerant in different flat tubes in the same flow.

Disclosure of Invention

In view of this, the utility model provides an air conditioner, the double-phase refrigerant of gas-liquid effectively separates in the separator, makes the flat intraductal refrigerant reposition of redundant personnel homogeneity of same flow good, improves the heat transfer effect of air conditioner.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

an air conditioner comprises a heat exchange loop, a heat exchanger and a heat exchanger, wherein the heat exchange loop is used for exchanging indoor heat and outdoor heat; the heat exchanger includes: flat tubes for circulating a refrigerant; the first collecting pipe is internally provided with an upper chamber and a lower chamber for circulating the refrigerant, and the upper chamber and the lower chamber are both communicated with the flat pipes; a separator for separating a gas-phase refrigerant and a liquid-phase refrigerant; the gas distributing pipe group is communicated between the separator and the lower chamber and is used for circulating the gas-phase refrigerant; and the liquid separating pipe group is communicated between the separator and the lower cavity and is used for circulating the liquid-phase refrigerant.

Furthermore, a separator cavity is formed inside the separator, a refrigerant flow port is arranged on the side wall of the separator, and the refrigerant flow port is communicated with the separator cavity; the gas distribution pipe group comprises a gas distribution main pipe and a plurality of gas distribution branch pipes communicated with the gas distribution main pipe, the gas distribution main pipe extends into the cavity of the separator, and the gas distribution branch pipes are communicated with the lower cavity chamber; the liquid separation pipe group comprises a liquid separation main pipe and a plurality of liquid separation branch pipes communicated with the liquid separation main pipe, the liquid separation main pipe extends into the separator cavity, and the liquid separation branch pipes are communicated with the lower cavity.

Furthermore, one end of the main liquid-separating pipe is close to the bottom of the separator cavity and has a certain distance.

Further, one end of the gas distribution main pipe is close to the top of the separator cavity.

Furthermore, a first baffle is arranged in the cavity of the separator and is positioned below the end part of the gas distribution main pipe.

Furthermore, a second baffle is arranged in the cavity of the separator and is positioned above the first baffle, the first baffle and the second baffle are respectively arranged on two sides of the main liquid distribution pipe, and a certain gap is formed between the second baffle and the main liquid distribution pipe.

Further, the gas distribution main pipe comprises a first gas distribution main pipe and a second gas distribution main pipe which are communicated with each other, the first gas distribution main pipe is communicated with the separator cavity, and the gas distribution branch pipes are arranged at equal intervals along the height direction of the second gas distribution main pipe; divide liquid main pipe and second to divide liquid main pipe including the first liquid main pipe of intercommunication, first liquid main pipe with the separator cavity intercommunication, divide liquid branch pipe to follow the direction of height equidistance setting that the second divides liquid main pipe.

Further, be equipped with the first baffle that a plurality of equidistance intervals set up in the lower cavity, it is a plurality of first baffle will a plurality of locuses are separated into to the lower cavity, every locuses intercommunication has the same quantity flat pipe, every locuses intercommunication divide the gas branch pipe with divide liquid branch pipe.

Further, the other end of the flat pipe is communicated with a fourth collecting pipe, a chamber M1, a chamber M2, a chamber M3, a chamber M4 and a chamber M5 are formed in the fourth collecting pipe, a first connecting pipe is communicated between the chamber M1 and the chamber M5, and a second connecting pipe is communicated between the chamber M2 and the chamber M4.

Further, the number of the flat tubes communicated with the chamber M1 is less than that of the flat tubes communicated with the chamber M5, and the number of the flat tubes communicated with the chamber M2 is less than that of the flat tubes communicated with the chamber M4; when the heat exchanger is used as an evaporator, the number of flat tubes flowing into the chamber M3 is greater than the number of flat tubes flowing out of the chamber M3.

Further, one end of the first connection pipe is connected to the lower end of the chamber M1, and the other end is connected to the upper end of the chamber M5; one end of the second connection pipe is connected to the lower end of the chamber M2, and the other end is connected to the upper end of the chamber M4.

Further, the heat exchanger still includes the trachea group, the trachea group includes a plurality of trachea branches, and is a plurality of the trachea branch all with go up the cavity intercommunication.

The technical scheme of the utility model prior art relatively has following technological effect:

when the heat exchanger is used as an evaporator, a gas-liquid two-phase refrigerant is effectively separated by the separator before entering the lower cavity of the first collecting pipe, a gas-phase refrigerant enters the lower cavity through the gas-distributing pipe group, and a liquid-phase refrigerant enters the lower cavity through the liquid-distributing pipe group, so that the interaction and mutual separation of the two-phase refrigerants in the flowing process are fundamentally avoided, the quality and the flow of the gas-phase refrigerant and the liquid-phase refrigerant entering the lower cavity are approximately equal, the gas-liquid separation phenomenon of the refrigerant in the lower cavity is avoided, and the distribution uniformity of the refrigerant in the flat pipe is improved;

the refrigerant separated by the gas-liquid separating pipe group and the liquid-liquid separating pipe group enters the lower chamber from top to bottom and then flows into the flat pipe, and compared with the traditional bottom-to-top flow dividing mode, the refrigerant flow dividing device can inhibit the influence of gravity in the upward flow dividing process of the refrigerant and the separation phenomenon caused by the gravity.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to these drawings without creative efforts.

FIG. 1 is a schematic diagram of a prior art air conditioner;

fig. 2 is a schematic structural diagram of a first embodiment of the heat exchanger of the present invention;

FIG. 3 is an enlarged view of portion A of FIG. 2;

FIG. 4 is a top view of a separator according to an embodiment of the present invention;

fig. 5 is a schematic diagram of an internal structure of a separator according to an embodiment of the heat exchanger of the present invention;

FIG. 6 is a sectional view taken along line A-A of FIG. 5;

FIG. 7 is a sectional view taken along line B-B of FIG. 5;

fig. 8 is a schematic structural diagram of a second embodiment of the heat exchanger of the present invention;

fig. 9 is a first schematic structural diagram of a second collecting pipe according to an embodiment of the heat exchanger of the present invention;

fig. 10 is a second schematic structural diagram (a side plate is omitted) of a second collecting pipe according to a second embodiment of the heat exchanger of the present invention;

fig. 11 is a top view of a second header according to an embodiment of the heat exchanger of the present invention;

FIG. 12 is a cross-sectional view taken along line C-C of FIG. 11;

FIG. 13 is a sectional view taken along line D-D of FIG. 11;

fig. 14 is a schematic view of the refrigerant flow inside the second header according to the embodiment of the present invention;

fig. 15 is a schematic structural diagram of a second structural form of a second collecting pipe according to an embodiment of the heat exchanger of the present invention;

fig. 16 is a schematic structural diagram of a third structural form of the second collecting pipe according to the embodiment of the present invention;

fig. 17 is a first schematic structural diagram (evaporation condition) of a third embodiment of the heat exchanger of the present invention;

fig. 18 is a schematic structural diagram ii (condensation condition) of the third embodiment of the heat exchanger of the present invention;

fig. 19 is a schematic structural diagram of actual installation of a third embodiment of the heat exchanger of the present invention;

fig. 20 is a first schematic structural diagram of an intermediate collecting pipe according to a third embodiment of the heat exchanger of the present invention;

fig. 21 is a schematic structural diagram ii of another view angle of the intermediate collecting pipe according to the third embodiment of the heat exchanger of the present invention;

fig. 22 is a schematic structural view of a third intermediate collecting pipe communicating flat pipe in an embodiment of the heat exchanger of the present invention;

fig. 23 is a top view of a third intermediate collecting pipe according to an embodiment of the heat exchanger of the present invention;

fig. 24 is a top view of another structure of three intermediate collecting pipes according to the embodiment of the present invention;

FIG. 25 is a sectional view taken along line H1-H1 of FIG. 23;

FIG. 26 is a sectional view taken along line H2-H2 of FIG. 23;

FIG. 27 is a sectional view taken along line H3-H3 of FIG. 23.

Reference numerals:

1-evaporator, 2-compressor, 3-condenser, 4-expansion valve, 5-four-way reversing valve;

01-a first collecting pipe, 011-an upper chamber, 012-a lower chamber, 013-a small chamber, and 014-a first clapboard;

02-a second collecting pipe, 021-a cavity part, 022-a channel part, 023-a turbulence part, 024-an inner wall, 025-an insertion part and 026-a bending part;

03-a third collecting pipe, 031-a third partition plate, 032-a third chamber;

04-a fourth collecting pipe;

05-middle collecting pipe, 051-sub cavity, 0511-first partition plate, 0512-second partition plate, 0513-third partition plate, 052-first cavity, 053-second cavity, 054-third cavity, 055-first circulation part, 056-second circulation part, 057-third circulation part, 058-first installation part and 059-second installation part;

06-separator, 061-separator cavity, 062-first baffle, 063-second baffle, 064-gap, 065-refrigerant flow port;

07-a gas distribution pipe group, 071-a gas distribution main pipe, 0711-a first gas distribution main pipe, 0712-a second gas distribution main pipe and 072-a gas distribution branch pipe;

08-liquid separation tube group, 081-liquid separation main tube;

09-connecting tube, 091-first connecting tube, 092-second connecting tube;

10-a fin;

11-flat tube;

12-trachea group, 121-trachea branch;

13-heat exchanging part, 131-first heat exchanging part, 132-second heat exchanging part.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are merely for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, are not to be construed as limiting the present invention.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art. In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.

The terms "first", "second", "third" and "fourth" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, features defined as "first", "second", "third", "fourth" may explicitly or implicitly include one or more of the features. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

The utility model discloses an air conditioner indicates heat pump type air conditioner especially, and the air conditioner includes heat transfer circuit for carry out indoor and outdoor heat exchange, in order to realize the air conditioner to indoor temperature's regulation.

The heat exchange circuit can adopt the heat exchange principle shown in the prior art fig. 1, that is, the heat exchange circuit comprises an evaporator 1, a compressor 2, a condenser 3, an expansion valve 4 and a four-way reversing valve C, the phase change processes of the refrigerants in the evaporator 1 and the condenser 3 are opposite, and the evaporator 1 and the condenser 3 are collectively called as a heat exchanger.

The utility model discloses an one of the purpose lies in carrying out institutional advancement to the heat exchanger, improves the balanced distribution of refrigerant in the heat exchanger, improves the heat transfer effect of heat exchanger, and then improves the holistic heat transfer effect of air conditioner.

The utility model discloses intercommunication transition department and the intercommunication transition department of heat exchanger side by side between inflow end, outflow end, the different processes to the refrigerant in the heat exchanger have all carried out the institutional advancement to improve the evenly distributed of refrigerant.

The heat exchanger comprises a plurality of flat pipes 11 and fins 10 which are arranged at equal intervals, wherein a plurality of micro channels used for circulating a refrigerant are formed in the flat pipes 11, the fins 10 are arranged between the two adjacent flat pipes 11, the flowing direction of air flowing through the fins 10 is perpendicular to the flowing direction of the refrigerant flowing through the flat pipes 11, and heat/cold released by the refrigerant in the flat pipes 11 is taken away through the radiating fins 10 and air flow.

The flat tube 11 is made of porous micro-channel aluminum alloy, and the fins 10 are made of aluminum alloy with brazing composite layers on the surfaces, so that the weight is light, and the heat exchange efficiency is high.

Example one

Fig. 2 to 7 are diagrams for explaining the structure of the first embodiment of the heat exchanger, in the first embodiment, the heat exchanger has a first flow path and a second flow path, the flow directions of the refrigerants in the two flow paths are opposite, and fig. 2 shows the flow direction of the refrigerant in the flat tube 11 when the heat exchanger is used as an evaporator.

The heat exchanger still includes first pressure manifold 01 and fourth pressure manifold 04, and one end of heat exchanger, the one end intercommunication with flat pipe 11 are located to first pressure manifold 01, and the other end of heat exchanger, the other end intercommunication with flat pipe 11 are located to fourth pressure manifold 04.

An upper chamber 011 and a lower chamber 012 for circulating refrigerants are formed in the first collecting pipe 01, the upper chamber 011 is communicated with the flat pipe 11 in the second flow path, and the lower chamber 012 is communicated with the flat pipe 11 in the first flow path.

The heat exchanger also comprises a separator 06, a gas separation tube group 07 and a liquid separation tube group 08.

Among them, the separator 06 serves to separate the gas-phase refrigerant and the liquid-phase refrigerant.

The gas-distributing tube group 07 is connected between the separator 06 and the lower chamber 012, and circulates a gas-phase refrigerant.

The liquid separation tube group 08 communicates between the separator 06 and the lower chamber 012, and is used for flowing a liquid-phase refrigerant.

When the heat exchanger is used as an evaporator, a gas-liquid two-phase refrigerant is effectively separated by the separator 06 before entering the lower cavity 012, the gas-phase refrigerant enters the lower cavity 012 by the gas-separating tube group 07, and the liquid-phase refrigerant enters the lower cavity 012 by the liquid-separating tube group 08, so that the interaction and separation of the two-phase refrigerant in the flowing process are fundamentally avoided, the quality and the flow rate of the gas-phase refrigerant and the liquid-phase refrigerant entering the lower cavity 012 are approximately equal, the gas-liquid separation phenomenon of the refrigerant does not exist in the lower cavity 012, and the distribution uniformity of the refrigerant in the flat tube 11 is improved.

Referring to fig. 4 and 5, a separator cavity 061 is formed inside the separator 06, a refrigerant flow port 065 is provided on a side wall of the separator 06, the refrigerant flow port 065 communicates with the separator cavity 061, and the refrigerant flows into the separator cavity 061 through the refrigerant flow port 065.

Referring to fig. 3 to 5, the gas distribution pipe group 07 includes a gas distribution main pipe 071 and a plurality of gas distribution branch pipes 072 communicated with the gas distribution main pipe 071, the gas distribution main pipe 071 extends into the separator cavity 061, the gas distribution branch pipes 072 extend in the horizontal direction and are communicated with the lower chamber 012, and the gas-phase refrigerant in the separator cavity 061 flows out of the gas distribution main pipe 071 and then enters the lower chamber 012 through the plurality of gas distribution branch pipes 072, so that the flow of the gas-phase refrigerant at each position in the lower chamber 012 is uniform.

Further, referring to fig. 3, the gas distribution main pipe 071 includes a first gas distribution main pipe 0711 and a second gas distribution main pipe 0712 which are communicated with each other, the first gas distribution main pipe 0711 is communicated with the separator cavity 061, the first gas distribution main pipe 0711 extends upward from the separator cavity 061 for a distance and then is communicated with the second gas distribution main pipe 0712 through an arc portion, the second gas distribution main pipe 0712 extends downward, the plurality of gas distribution branch pipes 072 are arranged at equal intervals along the height direction of the second gas distribution main pipe 0712, and the gas-phase refrigerant is distributed from top to bottom along the second gas distribution main pipe 0712 and enters the plurality of gas distribution branch pipes 072, so as to improve the uniform distribution of the gas-phase refrigerant.

In the separator cavity 061, the gas-phase refrigerant tends to flow toward the upper portion of the separator cavity 061, and referring to fig. 5, one end of the first gas distribution main pipe 0711 is provided near the top of the separator cavity 61 to facilitate the inflow of the upper gas-phase refrigerant.

With continued reference to fig. 3 to 5, the liquid separation tube group 08 includes a main liquid separation tube 081 and a plurality of branch liquid separation tubes (not shown) connected to the main liquid separation tube, the main liquid separation tube 081 extends into the separator cavity 61, the branch liquid separation tubes 081 extend in the horizontal direction and are connected to the lower chamber 012, the liquid-phase refrigerant in the separator cavity 061 flows out of the main liquid separation tube 081 and then enters the lower chamber 012 through the plurality of branch liquid separation tubes, so that the flow rate of the liquid-phase refrigerant in each position in the lower chamber 012 is uniform.

Further, the liquid distribution main pipe 081 comprises a first liquid distribution main pipe and a second liquid distribution main pipe which are communicated, the first liquid distribution main pipe is communicated with the separator cavity 061, the first liquid distribution main pipe extends upwards for a distance from the inside of the separator cavity 061 and then is communicated with the second liquid distribution main pipe through an arc portion, the second liquid distribution main pipe extends downwards, the plurality of liquid distribution branch pipes 082 are arranged at equal intervals along the height direction of the second liquid distribution main pipe, and liquid-phase refrigerant is distributed into the plurality of liquid distribution branch pipes from top to bottom along the second liquid distribution main pipe, so that the uniform distribution of the liquid-phase refrigerant is improved.

In the separator cavity 061, the liquid-phase refrigerant tends to flow toward the bottom of the separator cavity 061, and referring to fig. 5, one end of the first liquid-separation main pipe is located close to the bottom of the separator cavity 061 with a certain distance so as to facilitate the inflow of the lower liquid-phase refrigerant.

The refrigerant separated by the gas distributing pipe group 07 and the liquid distributing pipe group 08 enters the lower chamber 012 from top to bottom and then flows into the flat pipe 11, and compared with the traditional bottom-to-top flow distributing mode, the refrigerant flow distributing device can inhibit the influence of gravity and the separation phenomenon caused in the process of upward flow distribution of the refrigerant.

Referring to fig. 5 and 6, a first baffle 062 is arranged in the separator cavity 061, and is located below the end of the first gas distribution main pipe 0711 and is spaced from the end of the first gas distribution main pipe 0711, so that the first baffle 0662 can improve the separation efficiency of a gas-liquid two-phase refrigerant in an ascending process, and can prevent a liquid-phase refrigerant from entering the first gas distribution main pipe 0711 under the action of inertia.

In order to further improve the separation efficiency of the gas-liquid two-phase refrigerant, referring to fig. 5 and 7, a second baffle 063 is further disposed in the separator cavity 061, the first baffle 062 and the second baffle 063 are disposed on both sides of the main liquid separating pipe 081, and a gap 064 is provided between the second baffle 063 and the main liquid separating pipe 081, and the gas-phase refrigerant continues to flow upward from the gap 064.

Referring to fig. 3, a plurality of first baffles 014 are arranged in the lower chamber 012, the lower chamber 012 is divided into a plurality of small chambers 013 by the first baffles 014, each small chamber 013 is communicated with the same number of flat tubes 11, each small chamber 013 is communicated with a gas distribution branch tube 072 and a liquid distribution branch tube, so that the flow of the refrigerant entering each small chamber 013 is uniform, the refrigerant with the same flow is uniformly distributed to the same number of flat tubes 11, and the uniform flow of the refrigerant in each flat tube 11 is realized.

In this embodiment, 10 small cavities 013 are formed in the lower cavity 012, and two flat tubes 11 are connected in each small cavity 013. Of course, in other embodiments, the number of the small cavities 013 and the number of the flat tubes 11 in each small cavity 013 can be flexibly set according to practical situations, and this embodiment is not particularly limited.

In this embodiment, a specific implementation manner is given to the fourth header 04, referring to fig. 2, a chamber M1, a chamber M2, a chamber M3, a chamber M4, and a chamber M5 are formed in the fourth header 04, which are independent from each other, the chamber M1 and the chamber M5 are communicated through a first connecting pipe 091, the chamber M2 and the chamber M4 are communicated through a second connecting pipe 092, the refrigerant flowing into the chamber M1 enters the chamber M5 through the first connecting pipe 091, the refrigerant flowing into the chamber M2 enters the chamber M4 through the second connecting pipe 092, and the refrigerant flowing into the chamber M3 flows upward and enters the flat tubes 11 in the second flow path.

The lower chamber 012 and the fourth collecting pipe 04 are designed by a separate chamber, so that the on-way pressure loss and the local pressure loss of the refrigerant in the flow from entering the first collecting pipe 01 to leaving the first collecting pipe 01 are equal, and the heat exchanger has better distribution uniformity.

Further, when the two-phase refrigerant is subjected to boiling heat exchange in the flat tubes 11, the specific volume and the flow rate are gradually increased, the gas-liquid mixing degree is increased, and the separation uniformity is improved, so that the number of the flat tubes in the flowing direction of the refrigerant is gradually reduced; on the contrary, when the two-phase refrigerant condenses and exchanges heat in the flat tubes, the specific volume and the flow rate are gradually reduced, the gas and the liquid tend to be separated, and in order to reduce the separation of the gas and the liquid on the space, the number of the flat tubes along the flowing direction of the refrigerant is gradually increased. Therefore, in the present embodiment, when the heat exchanger is used as an evaporator, the number of flat tubes 11 communicated with the chamber M1 is smaller than the number of flat tubes 11 communicated with the chamber M5, the number of flat tubes 11 communicated with the chamber M2 is smaller than the number of flat tubes 11 communicated with the chamber M4, and when the heat exchanger is used as an evaporator, the number of flat tubes 11 flowing into the chamber M3 is larger than the number of flat tubes 11 flowing out of the chamber M3.

Further, one end of the first connection tube 091 is connected to the lower end of the chamber M1, so that the liquid-phase refrigerant in the lower portion of the chamber M1 flows into the first connection tube 091; the other end of the first connection tube 091 is connected to the upper end of the chamber M5, and the refrigerant in the first connection tube 091 flows into the chamber M5 from top to bottom, so that the flow uniformity of the refrigerant in the flat tube 11 communicated with the chamber M5 is improved by using gravity.

Likewise, one end of second connection pipe 092 is connected to the lower end of chamber M2, facilitating the flow of liquid-phase refrigerant in the lower portion of chamber M2 into second connection pipe 092; the other end of second connection pipe 092 is connected to the upper end of chamber M4, and the refrigerant in second connection pipe 092 flows into chamber M4 from top to bottom, so that the flow uniformity of the refrigerant in flat pipe 11 communicating with chamber M4 is improved by gravity.

Referring to fig. 2, in the first embodiment, the heat exchanger further includes a gas tube set 12, the gas tube set 12 includes a plurality of gas tube branches 121, the plurality of gas tube branches 121 are all communicated with the upper chamber 011, and the refrigerant in the upper chamber 011 flows out after being collected from the plurality of gas tube branches 121.

In the first embodiment, when the heat exchanger is used as an evaporator, a refrigerant enters the separator 06 from the refrigerant flow opening 065, a gas-phase refrigerant enters the lower chamber 012 of the first header 01 through the gas dividing tube group 07, a liquid-phase refrigerant enters the lower chamber 012 of the first header 01 through the liquid dividing tube group 08, a gas-liquid two-phase refrigerant simultaneously enters the plurality of flat tubes 11 in the first flow path, then enters the plurality of flat tubes 11 in the second flow path through the first connection tube 091, the second connection tube 092, and the fourth header 04, and finally flows out of the gas tube group 12 through the upper chamber 011 of the first header 01.

In the first embodiment, when the heat exchanger is used as a condenser, the flow direction of the refrigerant in the heat exchanger is opposite to that of the refrigerant in the evaporator, and the description thereof is omitted.

Example two

Referring to fig. 8, the heat exchanger has an ascending flow path and a descending flow path, the ascending flow path and the descending flow path are taken with respect to the flow direction of the refrigerant, and for convenience of description, in the first embodiment, the first flow path may be referred to as an ascending flow path, and the second flow path may be referred to as a descending flow path.

In the second embodiment, the technical scheme is described by taking an example that the heat exchanger has a first flow and a second flow, where the first flow is an ascending flow and the second flow is a descending flow.

First flow and second flow communicate through second pressure manifold 02, third pressure manifold 03 between, and is specific, and the second pressure manifold 02 communicates with flat pipe 11 in the second flow, and the third pressure manifold simultaneously with flat pipe 11 in the first flow and the flat pipe 11 intercommunication of part in the second flow, communicates through connecting pipe 09 between second pressure manifold 02 and the third pressure manifold 03.

Referring to fig. 9 to 14, the second header 02 includes a cavity part 021, a channel part 022, and a turbulent flow part 023, the cavity part 021 communicates with the connection pipe 09, one end of the channel part 022 communicates with the cavity part 021, the other end of the channel part 022 communicates with the flat pipe 11 in the second flow path, and the turbulent flow part 023 is disposed in the cavity part 021 and is configured to disturb a flow path of the refrigerant in the cavity part 021, so as to promote mixing of the refrigerant in the high pressure region and the low pressure region in the cavity part 021.

Specifically, the refrigerant in the first flow flat tube 11 enters the second collecting tube 02 through the third collecting tube 03 and the connecting tube 09, when the refrigerant enters the second collecting tube 02, the gas-liquid two-phase refrigerant first enters the cavity part 021, the refrigerant flow rate is larger, the refrigerant distribution is more obvious, the inflow end of the refrigerant generates low pressure, and a high pressure region and a low pressure region are formed in the cavity part 021, the turbulence part 023 can effectively avoid a flow blind region in the cavity part 021 caused by vortex, the turbulence part 023 disturbs the flow path of the refrigerant in the cavity part 021, so that the high pressure region in the cavity part 021 is mixed with the refrigerant in the low pressure region, the refrigerant circularly flows in the cavity part 021, the refrigerant formed by the turbulence part 023 can automatically adapt to the change of the refrigerant flow rate, and further, the refrigerant circulating paths entering different channel parts 022 can be uniformly distributed, and different microchannel flat tubes, which are in the same root 11 can be realized, The refrigerant flow in different flat tubes 11 in the same flow path is uniform.

Referring to fig. 9 and 10, the second header 02 includes a header main body, a plurality of channel portions 022 are formed inside the header main body through a plurality of spaced inner walls 024, the channel portions 022 are uniformly spaced, a cavity portion 021 is formed at the bottom inside the header main body, a plurality of flat pipes 11 are connected to the side wall of the header main body, a connection pipe 09 is connected to the other side wall of the header main body opposite to the flat pipes, one end of the channel portion 022 is communicated with the cavity portion 021, and the other end of the channel portion 022 is communicated with the flat pipes 11.

In the second embodiment, the manifold main body has a square structure, and the channel portion 022 formed by the inner wall surfaces has a flat structure.

The plurality of channel parts 022 are arranged at uniform intervals, so that the refrigerant in the cavity part 021 can uniformly flow into different channel parts 022, and the uniform flow of the refrigerant in the flat tubes 11 communicated with the channel parts 022 is further ensured.

Channel portion 022 has bending part 026, and one side that channel portion 022 is close to cavity portion 021 is perpendicular with cavity portion 021, and one side that channel portion 022 is close to flat pipe 11 is parallel with flat pipe 11, the circulation of refrigerant between cavity portion 021 and channel portion 022, flat pipe 11 and channel portion 022 of being convenient for.

In other embodiments, the channel portion 022 can have other flow paths, such as circular arc flow paths, and the number of turns of the channel portion can be changed, the surface roughness of the channel portion can be changed, and the like, in order to balance the resistance between different channels.

Be equipped with insert 025 on the lateral wall of pressure manifold main part, insert 025 and channel portion 022 intercommunication, flat pipe 11 inserts and locates in insert 025, realizes the intercommunication of flat pipe 11 and channel portion 022.

The number of the flat tubes 11 that can be connected out of each second collecting pipe 02 can be flexibly set according to actual conditions, and in the second embodiment, the number of the flat tubes 11 that can be connected to each second collecting pipe 02 is 1 to 20.

Referring to fig. 10 to 14, fig. 12 is a sectional view taken along the direction C-C in fig. 11, fig. 13 is a sectional view taken along the direction D-D in fig. 11, the spoiler 023 is a partition structure disposed in the cavity part 021, the partition structure extends in a direction parallel to the inflow direction of the refrigerant, and the partition structure is an incomplete partition, that is, the partition structure and the inner wall of the periphery of the cavity part 021 have a certain gap.

An arrow in fig. 14 indicates a flow direction of the refrigerant, when the gas-liquid two-phase refrigerant is evaporated in the heat exchanger, a part of the refrigerant flowing into the cavity part 021 from the connection pipe 09 directly flows upward and directly enters the channel part 022, the other part of the refrigerant bypasses the spoiler part 023 and enters a side (i.e., a left side part in the orientation shown in fig. 14) far away from the refrigerant inflow port in the cavity part 021, while the part of the refrigerant flows around the spoiler part 023, a part of the refrigerant flows into the channel part 022, and the remaining part of the refrigerant bypasses the spoiler part 023 and then is mixed with the newly inflowing refrigerant and enters the next flow cycle. Because the refrigerant has a higher flow velocity when entering the cavity part 021 from the connecting pipe 09, and the pressure at the inlet of the refrigerant in the cavity part 021 is lower, the refrigerant which cannot flow into the channel part 022 in time can circularly flow around the burbling part 023, and a refrigerant circulating flow path formed in the cavity part 021 is beneficial to improving the uniform distribution of the refrigerant in the cavity part 021, so that the refrigerant entering different channel parts 022 is uniform, and further, the refrigerant in different flat pipes is uniform.

Under high flow, refrigerant distribution unevenness is more obvious, and when the refrigerant flow is larger, the scheme has more obvious effect on uniform distribution of the refrigerant. Because the flow is bigger, the low pressure effect caused by the injection at the refrigerant inlet of the cavity part 021 is more obvious, the circulation loop which causes the refrigerant to flow around the turbulent flow part 023 is more obvious, the circulation loop of the refrigerant automatically adapts to the change of the external refrigerant flow, and the uniform distribution of the refrigerant is improved.

Because the channel portion 022 is the platykurtic structure, this platykurtic structure just in time matches with flat tube 11's structure, and the refrigerant is evenly distributed in channel portion 022, also is favorable to improving the refrigerant homogeneity that gets into in the different microchannels in the same flat tube 11.

Referring to fig. 11 and 14, the connection pipe 023 is preferably disposed at a side of the cavity part 021 away from the blowing direction, which is advantageous for improving heat dissipation efficiency.

Fig. 15 and 16 show two other modified forms of the spoiler portion 023, which further improve the uniform distribution effect of the refrigerant by increasing the number of the spoiler portions 023 to form multi-way returns and multi-way spoilers in the cavity portion 021.

In fig. 15, the spoiler portions 023 are two partition structures spaced apart from each other, and the partition structures are the same as those shown in fig. 14 except for the arrangement, and in fig. 15, the two spoiler portions 023 are symmetrically arranged in the cavity portion 021 at positions corresponding to positions where the refrigerant flows into the cavity portion 021. The refrigerant flowing into the cavity part 021 first enters between the two spoiler parts 023 and then is divided into two paths, one path of refrigerant forms a circulation loop around the left spoiler part 023, and the other path of refrigerant forms a circulation loop around the right spoiler part 023.

In fig. 16, the spoiler portions 023 are three partition structures arranged at intervals, the partition structures are the same as those shown in fig. 14 except for different arrangement modes, in fig. 16, the three spoiler portions 023 are symmetrically distributed in the cavity portion 021 at positions corresponding to positions where the refrigerant flows into the cavity portion 021, and the spoiler portion 023 in the middle is opposite to the connecting pipe 09. The refrigerant flowing into the cavity part 021 is divided into two paths, one path flows along a gap between the left spoiler portion 023 and the middle spoiler portion 023 and bypasses the left spoiler portion 023 to form a circulation loop, and the other path flows along a gap between the right spoiler portion 023 and the middle spoiler portion 023 and bypasses the right spoiler portion 023 to form a circulation loop.

Returning to fig. 8, the second collecting pipe 02 has at least one, a plurality of third partition plates 031 are arranged in the third collecting pipe 03, a plurality of third partition plates 031 divide the inner space of the third collecting pipe 03 into a plurality of independent third chambers 032, one of them third chamber 032 communicates with the flat pipe 11 of the part in the ascending flow (first flow) and the flat pipe 11 of the part in the descending flow (second flow) simultaneously, the quantity of the rest third chambers 031 is the same as that of the second collecting pipe 02, and each rest of the third chambers 031 communicates with each second collecting pipe 02 in a one-to-one correspondence manner through a connecting pipe 09.

In the second embodiment, the second collecting pipe 02 has two, three third partition plates 031 are arranged in the third collecting pipe 03, the third partition plates 031 divide the inside of the third collecting pipe 03 into three independent third chambers 032, which are sequentially marked as N1, N2, N3, wherein the second collecting pipe 02 located above is communicated with the third chamber N1 through a first connecting pipe 091, the second collecting pipe 02 located below is communicated with the third chamber N2 through a second connecting pipe 092, and the third chamber N3 is simultaneously communicated with the flat pipe 11 in the first flow and the flat pipe 11 in the second flow.

Through the cooperation of a plurality of third chambers 032 and a plurality of second pressure manifold 02, the even distribution of refrigerant is further improved.

One end of the first connecting pipe 091 is communicated with the lower end of the third chamber N1, so that the liquid-phase refrigerant in the third chamber N1 can flow into the first connecting pipe 091 conveniently, and the other end of the first connecting pipe 091 is communicated with the lower end of the second collecting pipe 02 and communicated with the cavity part 021, so that the gas-liquid two-phase refrigerant can be uniformly distributed through the second collecting pipe 02 conveniently.

Similarly, one end of the second connection pipe 092 is communicated with the lower end of the third chamber N2, so that the liquid-phase refrigerant in the third chamber N2 can flow into the second connection pipe 092, and the other end of the second connection pipe 092 is communicated with the lower end of the second collecting pipe 02 and is communicated with the cavity 021, so that the gas-liquid two-phase refrigerant can be uniformly distributed through the second collecting pipe 02.

Communicate in third chamber 032 and the second pressure manifold 02 at same connecting pipe 09 both ends, the flat pipe quantity that third chamber 032 communicates is less than the flat pipe 11 quantity that second pressure manifold 02 communicates. In the second embodiment, the number of the flat pipes communicated with the third chamber N1 is smaller than the number of the flat pipes communicated with the second collecting pipe 02, the number of the flat pipes communicated with the third chamber N2 is smaller than the number of the flat pipes communicated with the second collecting pipe 02, and the number of the flat pipes in the first flow connected with the third chamber N3 is smaller than the number of the flat pipes in the second flow connected with the first flow. The reason for this design is the same as the design reason for the multi-layer partition plate of the fourth header 04 in the first embodiment, and is not described herein again.

EXAMPLE III

In order to improve the heat exchange efficiency of heat exchanger, can communicate the setting with a plurality of heat exchangers side by side, one of the purpose of the third embodiment lies in improving the refrigerant evenly distributed between two heat exchangers of adjacent intercommunication to improve the heat transfer homogeneity of whole heat exchanger subassembly.

Referring to fig. 17 to 19, the heat exchanger includes a plurality of heat exchanging portions 13, the plurality of heat exchanging portions 13 are arranged in parallel and in communication, and the flat tubes 11 on two adjacent heat exchangers 13 are communicated through an intermediate collecting pipe 05.

The arrows in fig. 17 indicate the flow direction of the refrigerant when the heat exchanger is in the evaporation condition, the arrows in fig. 18 indicate the flow direction of the refrigerant when the heat exchanger is in the condensation condition, and fig. 19 is a schematic structural view of a plurality of heat exchange portions after being actually installed.

In the third embodiment, the heat exchanger is exemplified by two heat exchanging portions 13, the two heat exchanging portions 13 are defined as a first heat exchanging portion 131 and a second heat exchanging portion 132, the first heat exchanging portion 131 is located in a downwind area of the air supply direction, the second heat exchanging portion 132 is located in an upwind area of the air supply direction, the first heat exchanging portion 131 and the second heat exchanging portion 132 both include a plurality of flat tubes 11 and fins 10 arranged at equal intervals, and air flows through gaps between the flat tubes 11 and the fins 10 to achieve the heat exchanging effect.

Through middle pressure manifold 05 intercommunication between two heat transfer portions, the heat exchanger includes first flow, the second flow, the third flow, and the fourth flow, first flow and fourth flow are located first row heat transfer portion 131, second flow and third flow are located second row heat transfer portion 132, locate flat pipe in the first flow and locate through middle pressure manifold 05 intercommunication between the flat pipe in the second flow, locate flat pipe in the third flow and locate through middle pressure manifold 05 intercommunication between the flat pipe in the fourth flow.

The arrangement of one end of the first heat exchanging part 131 may refer to the structure arrangement of the first embodiment shown in fig. 2, and is not described herein again.

The arrangement of one end of the second heat exchanging part 132 can refer to the second embodiment shown in fig. 8, and is not described herein again.

Referring to fig. 17, when the heat exchanger is in an evaporation condition, after entering a lower chamber 012 of a first header 01 through a separator 06, a gas distribution tube group 07, and a liquid distribution tube group 08, a refrigerant sequentially flows through a first flow, an intermediate header 05, and a second flow, enters a third header 03, then enters a second header 02 through a first connection tube 091 and a second connection tube 092, and then sequentially flows through the third flow, the intermediate header 05, and a fourth flow, enters an upper chamber 011 of the first header 01, and finally flows out of a gas tube group 12.

Referring to fig. 18, when the heat exchanger is in a condensation condition, after entering an upper chamber 011 of a first header 01 through a gas pipe group 12, a refrigerant sequentially flows through a fourth flow, an intermediate header 05 and a third flow, enters a second header 02, then enters a third header 03 through a first connecting pipe 091 and a second connecting pipe 092, then sequentially flows through the second flow, the intermediate header 05 and the first flow, enters a lower chamber 012 of the first header 01, and finally flows out through a gas distribution pipe group 07, a liquid distribution pipe group 08 and a separator 06.

For the number of the flat pipes in each flow, the number of the flat pipes in the first flow, the second flow, the third flow and the fourth flow is gradually increased, that is, the number of the flat pipes in the fourth flow is greater than the number of the flat pipes in the third flow, the number of the flat pipes in the third flow is greater than the number of the flat pipes in the second flow, and the number of the flat pipes in the second flow is greater than the number of the flat pipes in the first flow.

A plurality of sub-cavities 051 distributed along the height direction of the intermediate collecting pipe 05 are formed in the intermediate collecting pipe 05 through partition plates, the sub-cavities 051 are independent of one another, the structure of each sub-cavity 051 is the same, and fig. 20 to 27 are schematic structural diagrams of a single sub-cavity 051, wherein fig. 21 is a view observed from the Q direction of fig. 20.

Referring to fig. 20 to 23, each sub-cavity 051 includes a first cavity 052, a second cavity 053, a third cavity 054, a first circulation part 055 and a second circulation part 056, the first cavity 052 is communicated with a part of flat pipes on the first heat exchanging part 131, the second cavity 053 is communicated with a part of flat pipes on the second heat exchanging part 132, the third cavity 054 is communicated with the first cavity 052, the first circulation part 055 is located below the third cavity 054 and is used for communicating the second cavity 053 with the third cavity 054, and the second circulation part 056 is located above the second cavity 052 and is used for communicating the first cavity 052 with the second cavity 053.

When the heat exchanger is used as an evaporator, a refrigerant firstly enters the first cavity 052, most of the refrigerant in the first cavity 052 flows into the third cavity 054, a gas-liquid two-phase refrigerant entering the third cavity 054 tends to be separated under the action of gravity and has poor uniformity, the refrigerant in the third cavity 054 enters the second cavity 053 through the first circulation part 055 below, and the gas-phase refrigerant above the third cavity 054 is mixed with the liquid-phase refrigerant below in the process of flowing downwards through the first circulation part 055 because the flow rate of the gas-phase refrigerant is higher than that of the liquid-phase refrigerant, and then the acceleration effect of the first circulation part 055 enters the second cavity 053 and flows into the flat tube communicated with the second cavity 053 from bottom to top, so that the gas-liquid two-phase refrigerant is uniformly distributed in the flat tube. The speed of the refrigerant in the flowing process from bottom to top in the second cavity 053 is decreased progressively, the upper part of the second cavity 053 forms a vortex, the flow of the refrigerant at the flat pipe at the vortex is smaller, and the second circulation part 056 leads the refrigerant which is excessive in the refrigerant ascending process into the first cavity 052 to be mixed with the high-speed refrigerant in the first cavity 052 to participate in the distribution process of the next cycle, so as to further improve the uniform distribution of the refrigerant and further improve the heat exchange effect of the air conditioner.

The aperture of the first communicating portion 055 is preferably larger than the aperture of the flat tube 11, so that the refrigerant in the third chamber 054 can smoothly flow through the first communicating portion 055 into the second chamber 053.

Be equipped with a plurality of first installation department 058 that are used for installing flat pipe 11 on the lateral wall of first cavity 052, be equipped with a plurality of second installation departments 059 that are used for installing flat pipe 11 on the lateral wall of second cavity 053, first installation department 058 and second installation department 059 are located the homonymy of sub-cavity 051, like this, first row heat transfer portion 131 and second row heat transfer portion 132 behind middle pressure manifold 05 intercommunication, structure side by side around can forming, the structure is compacter, be favorable to reducing the volume of whole heat exchanger.

First installation department 058 and second installation department 059 can be for locating the patchhole on the lateral wall of subcavity 051, and flat pipe 11 can directly be pegged graft with the patchhole, and the installation of being convenient for, the structure is reliable.

The quantity of first installation department 058 and second installation department 059 is the same for flat tub quantity that first cavity 052 communicates is the same with the flat tub quantity that second cavity 053 communicates, in order to improve the intraductal refrigerant homogeneity of different processes flat.

As a preferred embodiment, a first partition plate 0511, a second partition plate 0512 and a third partition plate 0513 are arranged in the sub-cavity 051, and the interior of the sub-cavity 051 is divided into a first cavity 052, a second cavity 053 and a third cavity 054 through the first partition plate 0511, the second partition plate 0512 and the third partition plate 0513.

The second partition plate 0512 is preferably in the same plane as the third partition plate 0513, and the first partition plate 0511 is preferably perpendicular to the second partition plate 0512 and the third partition plate 0513, so that a first cavity 052 and a second cavity 053 which are equal in volume are formed, and uniform distribution of the refrigerant is facilitated.

Referring to fig. 23 and 25 to 27, a first partition plate 0511 is disposed between a first cavity 052 and a second cavity 053, a second circulation portion 056 is disposed on the upper portion of the first partition plate 0511, a second partition plate 0512 is disposed between the first cavity 052 and a third cavity 054, a plurality of third circulation portions 057 for circulation of a refrigerant are disposed on the second partition plate 0512, the third partition plate 0513 is disposed between the second cavity 053 and the third cavity 054, and a first circulation portion 055 is disposed on the lower portion of the third partition plate 0513.

When the heat exchanger is used as an evaporator, a large part of refrigerant flowing into the first cavity 052 flows into the third cavity 054 through the third circulation part 057, the refrigerant in the third cavity 054 flows into the second cavity 053 through the first circulation part 055 on the lower side, and the first circulation part 055 is arranged on the lower side, so that the gas-phase refrigerant above the third cavity 054 flows downwards through the first circulation part 055 and is mixed with the liquid-phase refrigerant on the lower side, then flows into the second cavity 053 through the acceleration effect of the first circulation part 055, and flows into the flat tubes communicated with the second cavity 053 from bottom to top, and the uniform distribution of the gas-liquid two-phase refrigerant in the flat tubes is realized. The speed of the refrigerant in the flowing process from bottom to top in the second cavity 053 is decreased progressively, the upper part of the second cavity 053 forms a vortex, the flow of the refrigerant at the flat pipe at the vortex is smaller, and the second circulation part 056 positioned above leads the refrigerant which is excessive in the upward process of the refrigerant into the first cavity 052 to be mixed with the high-speed refrigerant in the first cavity 052 to participate in the distribution process of the next cycle, thereby further improving the uniform distribution of the refrigerant and further improving the heat exchange effect of the air conditioner.

The number of the third circulating parts 057 is preferably the same as that of the flat pipes communicated with the first cavity 052, a certain distance is reserved between the end part of the flat pipe positioned in the first cavity 052 and the third circulating parts 057, and the third circulating parts 057 are just opposite to each other, so that the refrigerant jetted out of the flat pipe can be mostly jetted into the third cavity 054.

In addition, the sub-cavity 051 shown in fig. 20 to 23 has a rectangular structure, in other embodiments, the third cavity 054 may have other structure forms such as a D-type structure, an O-type structure and the like, the embodiment is not particularly limited, and as shown in fig. 24, the third cavity 054 is a D-type structure.

In the third embodiment, when the gas-liquid two-phase refrigerant flows between the first heat exchanging unit 131 and the second heat exchanging unit 132, no matter whether the upstream refrigerant is uniformly split, the refrigerant flowing into the next flat tube can be ensured to be dynamically adjusted and uniformly distributed after passing through the intermediate collecting pipe 05.

In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.

The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims

1. An air conditioner comprising:

the heat exchange loop is used for exchanging heat indoors and outdoors, and a heat exchanger is arranged on the heat exchange loop;

characterized in that the heat exchanger comprises:

flat tubes for circulating a refrigerant;

the first collecting pipe is internally provided with an upper chamber and a lower chamber for circulating the refrigerant, and the upper chamber and the lower chamber are both communicated with the flat pipes;

a separator for separating a gas-phase refrigerant and a liquid-phase refrigerant;

the gas distributing pipe group is communicated between the separator and the lower chamber and is used for circulating the gas-phase refrigerant;

and the liquid separating pipe group is communicated between the separator and the lower cavity and is used for circulating the liquid-phase refrigerant.

2. The air conditioner according to claim 1,

a separator cavity is formed inside the separator, a refrigerant flow port is arranged on the side wall of the separator, and the refrigerant flow port is communicated with the separator cavity;

the gas distribution pipe group comprises a gas distribution main pipe and a plurality of gas distribution branch pipes communicated with the gas distribution main pipe, the gas distribution main pipe extends into the cavity of the separator, and the gas distribution branch pipes are communicated with the lower cavity chamber;

the liquid separation pipe group comprises a liquid separation main pipe and a plurality of liquid separation branch pipes communicated with the liquid separation main pipe, the liquid separation main pipe extends into the separator cavity, and the liquid separation branch pipes are communicated with the lower cavity.

3. The air conditioner according to claim 2,

one end of the main liquid-separating pipe is close to the bottom of the cavity of the separator and has a certain distance.

4. The air conditioner according to claim 3,

one end of the gas distribution main pipe is close to the top of the separator cavity.

5. The air conditioner according to claim 4,

a first baffle is arranged in the cavity of the separator and is positioned below the end part of the gas distribution main pipe.

6. The air conditioner according to claim 5,

a second baffle is arranged in the cavity of the separator and is positioned above the first baffle, the first baffle and the second baffle are respectively arranged at two sides of the main liquid-separating pipe, and a certain gap is reserved between the second baffle and the main liquid-separating pipe.

7. The air conditioner according to any one of claims 2 to 6,

the gas distribution main pipe comprises a first gas distribution main pipe and a second gas distribution main pipe which are communicated with each other, the first gas distribution main pipe is communicated with the separator cavity, and the gas distribution branch pipes are arranged at equal intervals along the height direction of the second gas distribution main pipe;

divide liquid main pipe and second to divide liquid main pipe including the first liquid main pipe of intercommunication, first liquid main pipe with the separator cavity intercommunication, divide liquid branch pipe to follow the direction of height equidistance setting that the second divides liquid main pipe.

8. The air conditioner according to claim 7,

the interior first baffle that is equipped with a plurality of equidistance intervals and sets up of cavity down, it is a plurality of first baffle will cavity down is separated into a plurality of locules, every loculus intercommunication has the same quantity flat pipe, every loculus intercommunication divide the gas branch pipe with divide liquid branch pipe.

9. The air conditioner according to claim 8,

the other end of the flat pipe is communicated with a fourth collecting pipe, a cavity M1, a cavity M2, a cavity M3, a cavity M4 and a cavity M5 are formed in the fourth collecting pipe, a first connecting pipe is communicated between the cavity M1 and the cavity M5, and a second connecting pipe is communicated between the cavity M2 and the cavity M4.

10. The air conditioner according to claim 9,

the number of the flat tubes communicated with the chamber M1 is less than that of the flat tubes communicated with the chamber M5, and the number of the flat tubes communicated with the chamber M2 is less than that of the flat tubes communicated with the chamber M4;

when the heat exchanger is used as an evaporator, the number of flat tubes flowing into the chamber M3 is greater than the number of flat tubes flowing out of the chamber M3.

11. The air conditioner according to claim 10,

one end of the first connection pipe is connected to the lower end of the chamber M1, and the other end is connected to the upper end of the chamber M5;

one end of the second connection pipe is connected to the lower end of the chamber M2, and the other end is connected to the upper end of the chamber M4.

12. The air conditioner according to claim 7,

the heat exchanger still includes the trachea group, the trachea group includes a plurality of trachea branch roads, and is a plurality of the trachea branch road all with go up the cavity intercommunication.