An air conditioner

Abstract

The present invention discloses an air conditioner, wherein a heat exchanger is provided on a heat exchange circuit, the heat exchanger comprises flat tubes, a second header, a third header and a connecting pipe, the second header is connected to the third header through the connecting pipe, the second header is connected to the flat tubes in a downward flow of the heat exchanger, the third header is connected to the flat tubes in an upward flow of the heat exchanger, the second header comprises a cavity portion, a channel portion and a spoiler portion, the cavity portion is connected to the connecting pipe, one end of the channel portion is connected to the cavity portion, and the other end is connected to the flat tube, the spoiler portion is arranged in the cavity portion, which can effectively avoid a flow blind area caused by eddy current in the cavity portion, can disturb the flow path of the refrigerant in the cavity portion, promote the mixing of the refrigerant in the high-pressure zone and the low-pressure zone in the cavity portion, and enable the refrigerant entering different channel portions to be evenly distributed, so as to achieve uniform refrigerant flow in different microchannels in the same flat tube and in different flat tubes in the same flow.

Description

Technical Field

[0001] The invention relates to the technical field of refrigeration equipment, and in particular to an air conditioner with uniform refrigerant flow distribution. Background Art

[0002] At present, heat pump air conditioners are a commonly used type of air conditioner for heating and cooling. In summer, the air conditioner cools indoors and dissipates heat outdoors. In winter, the direction is opposite to that in summer, that is, indoors are heated and outdoors are cooled. The air conditioner uses a heat pump to exchange heat between different environments. For example, in winter, outdoor air, ground water, groundwater, etc. are low-temperature heat sources, while indoor air is a high-temperature heat source. The function of heat pump air conditioners for heating is to transfer the heat from the outdoor environment to the indoor environment.

[0003] Reference Figure 1 As shown, a schematic diagram of a heating cycle of a heat pump in the prior art is shown. The heat pump includes: 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: first, the low-pressure two-phase refrigerant (a mixture of liquid refrigerant and gas refrigerant) in the evaporator 1 absorbs heat from the low-temperature environment; after being sucked in by the compressor 2, it is compressed into a high-temperature and high-pressure gas refrigerant; then, the high-temperature and high-pressure gas refrigerant releases heat energy to the indoor environment in the condenser 3, while its own temperature is reduced; finally, after throttling through the expansion valve mechanism 4, it becomes a low-temperature and low-pressure two-phase refrigerant, enters the evaporator 1 again, and repeats the above-mentioned cyclic heating process. The heat exchanger described in this article includes the above-mentioned evaporator 1 and condenser 3.

[0004] The heat pump air conditioner changes the working mode through the four-way reversing valve C. In the summer cooling condition, the indoor heat exchanger acts as the evaporator 1 and the outdoor heat exchanger acts as the condenser 3. The indoor air is cooled down by the surface of the evaporator 1 to reduce the indoor temperature, and the heat is transported to the outside through the condenser 3. When heating in winter, the position of the four-way reversing valve C is changed to change the flow direction of the refrigerant. At this time, the refrigerant absorbs heat from the environment through the outdoor heat exchanger and releases heat to the indoor environment to achieve the purpose of heating.

[0005] The evaporator 1 is a device for outputting cold. Its function is to evaporate the refrigerant liquid flowing in through the expansion valve 4 to absorb the heat of the cooled object to achieve the purpose of refrigeration. The condenser 3 is a device for outputting heat. The heat absorbed from the evaporator 1 and the heat converted by the work consumed by the compressor 2 are taken away by the cooling medium in the condenser 3 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. The quality of their performance will directly affect the performance of the entire system.

[0006] Compared with fin-tube heat exchangers, microchannel heat exchangers have significant advantages in terms of material cost, refrigerant charge and heat flux density, which is in line with the development trend of energy conservation and environmental protection of heat exchangers. Microchannel heat exchangers include flat tubes, fins, headers, end covers and other components. A partition is also inserted in the header of a multi-process microchannel heat exchanger, which divides the header into multiple independent cavities, and each header cavity is connected to a certain number of flat tubes. When the microchannel heat exchanger is used as an evaporator, when the gas-liquid two-phase refrigerant enters multiple flat tubes from the header cavity, due to the difference in density and viscosity between the gas phase and the liquid phase, the flowing refrigerant is easily separated under the action of gravity and viscous force, resulting in uneven refrigerant entering multiple flat tubes. Uneven refrigerant not only deteriorates the heat exchange efficiency, but also causes fluctuations in the refrigeration system. Therefore, it is an important issue to achieve uniform distribution of two-phase refrigerant inside different flat tubes in the same process. Summary of the invention

[0007] In view of this, the present invention provides an air conditioner, in which the refrigerant flow rates in different microchannels in the same flat tube and in different flat tubes in the same process on the heat exchanger are more uniform, thereby improving the heat exchange effect of the air conditioner.

[0008] In order to achieve the above object, the present invention adopts the following technical scheme:

[0009] An air conditioner, comprising: a heat exchange circuit for exchanging heat between indoor and outdoor, wherein a heat exchanger is provided on the heat exchange circuit, and the heat exchanger has an upward flow and a downward flow; the heat exchanger comprises: a flat tube having a plurality of microchannels therein for circulating a refrigerant; a second header connected to the flat tube in the downward flow for circulating the refrigerant; a third header connected to the flat tube in the upward flow for circulating the refrigerant; a connecting pipe connecting the second header and the third header for circulating the refrigerant; wherein the second header comprises: a cavity portion connected to the connecting pipe for circulating the refrigerant; a channel portion, one end of which is connected to the cavity portion and the other end of which is connected to the flat tube for circulating the refrigerant; a disturbing portion provided in the cavity portion for disturbing the flow path of the refrigerant in the cavity portion to promote mixing of the refrigerant in the high-pressure area and the low-pressure area in the cavity portion.

[0010] Furthermore, a plurality of the channel portions are formed in the second manifold and are evenly spaced apart, and one end of each of the channel portions is communicated with the cavity portion, and the other end is communicated with the flat tube.

[0011] Furthermore, the channel portion has a bending portion, a side of the channel portion close to the cavity portion is perpendicular to the cavity portion, and a side of the channel portion close to the flat tube is parallel to the flat tube.

[0012] Furthermore, an insertion portion is provided on the side wall of the second collecting pipe, the insertion portion is communicated with the channel portion, and the flat tube is inserted in the insertion portion.

[0013] Furthermore, the spoiler is a partition structure provided in the cavity, the partition structure extends in a direction parallel to the inflow direction of the refrigerant, and a certain gap is formed between the partition structure and the inner walls around the cavity.

[0014] Furthermore, the connecting pipe is connected to a side of the cavity portion away from an air supply direction.

[0015] Furthermore, the spoiler portion is at least two partition structures arranged in the cavity portion and spaced apart from each other, the partition structures extend in a direction parallel to the inflow direction of the refrigerant, and the plurality of partition structures are symmetrically distributed relative to the position where the refrigerant flows into the cavity portion.

[0016] Furthermore, the second collecting pipe has at least one; a plurality of third partitions are arranged in the third collecting pipe, and the plurality of third partitions divide the internal space of the third collecting pipe into a plurality of independent third chambers, one of the third chambers is simultaneously connected to part of the flat tubes in the upward flow and part of the flat tubes in the downward flow, and the number of the remaining third chambers is the same as the number of the second collecting pipes, and each of the remaining third chambers is connected to each of the second collecting pipes one by one through the connecting pipe.

[0017] Furthermore, one end of the connecting pipe is connected to the lower end of the third chamber, and the other end is connected to the lower end of the second collecting pipe.

[0018] Furthermore, in the third chamber and the second header connected to two ends of the same connecting pipe, the number of the flat tubes connected to the third chamber is less than the number of the flat tubes connected to the second header.

[0019] The technical solution of the present invention has the following technical effects compared with the prior art:

[0020] When the heat exchanger is used as an evaporator, when the gas-liquid two-phase refrigerant enters the second collecting pipe from the third collecting pipe through the connecting pipe, the gas-liquid two-phase refrigerant first enters the cavity part. The larger the refrigerant flow rate, the more obvious the uneven distribution of the refrigerant. The inflow end of the refrigerant will generate low pressure, and then form high-pressure and low-pressure areas in the cavity part. The spoiler can effectively avoid the flow blind area caused by eddy current in the cavity part. The spoiler disturbs the flow path of the refrigerant in the cavity part, causing the refrigerant in the high-pressure area and the low-pressure area in the cavity part to mix, and the refrigerant circulates in the cavity part. The refrigerant circulation path formed by the spoiler can automatically adapt to the change of the refrigerant flow rate, so that the refrigerant entering different channel parts can be evenly distributed, so as to achieve uniform refrigerant flow in different microchannels in the same flat tube and different flat tubes in the same process. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other accompanying drawings can be obtained based on these accompanying drawings without paying creative work.

[0022] Figure 1 It is a schematic diagram of the principle of the air conditioner in the prior art;

[0023] Figure 2 This is a schematic structural diagram of a heat exchanger according to a first embodiment of the present invention;

[0024] Figure 3 for Figure 2 Enlarged view of part A in the middle;

[0025] Figure 4 A top view of a separator of a heat exchanger embodiment 1 of the present invention;

[0026] Figure 5 This is a schematic diagram of the internal structure of a separator in a first embodiment of a heat exchanger according to the present invention;

[0027] Figure 6 for Figure 5 Middle AA section view;

[0028] Figure 7 for Figure 5 Middle BB section view;

[0029] Figure 8 This is a schematic diagram of the structure of a heat exchanger according to a second embodiment of the present invention;

[0030] Fig. 9 The structure of the second header of the heat exchanger of the present invention is shown in FIG. Figure 1 ;

[0031] Fig.10 The structure of the second header of the heat exchanger of the present invention is shown in FIG. Figure 2 (Omit the side panels);

[0032] Fig.11 A top view of the second header of the heat exchanger embodiment 2 of the present invention;

[0033] Fig.12 for Fig.11 Middle CC section view;

[0034] Fig.13 for Fig.11 Middle DD section view;

[0035] Fig.14 This is a schematic diagram of the refrigerant flow inside the second header of the heat exchanger embodiment 2 of the present invention;

[0036] Fig.15 It is a schematic diagram of the structure of the second structural form of the second header of the heat exchanger embodiment 2 of the present invention;

[0037] Fig.16 It is a schematic structural diagram of a third structural form of the second header of the heat exchanger embodiment 2 of the present invention;

[0038] Fig.17 The structure of the heat exchanger of the present invention is shown in FIG. Figure 1 (Evaporation conditions);

[0039] Fig.18 The structure of the heat exchanger of the present invention is shown in FIG. Figure 2 (Condensation condition);

[0040] Fig.19 This is a schematic diagram of the actual installation structure of the heat exchanger embodiment 3 of the present invention;

[0041] Fig. 20 The structure of the intermediate header of the heat exchanger embodiment 3 of the present invention is shown in FIG. Figure 1 ;

[0042] Fig.21 The structure of the intermediate header of the heat exchanger embodiment 3 of the present invention is schematically shown from another perspective Figure 2 ;

[0043] Fig. 22 This is a schematic diagram of the structure of the intermediate header connected to the flat tubes in the third embodiment of the heat exchanger of the present invention;

[0044] Fig.23 A top view of the intermediate header of the heat exchanger embodiment 3 of the present invention;

[0045] Fig.24 A top view of another structural form of the intermediate header of the heat exchanger embodiment 3 of the present invention;

[0046] Fig.25 for Fig.23 Middle H1-H1 section view;

[0047] Fig.26 for Fig.23 Middle H2-H2 sectional view;

[0048] Fig. 27 for Fig.23 H3-H3 section view.

[0049] Reference numerals:

[0050] 1- evaporator, 2- compressor, 3- condenser, 4- expansion valve, 5- four-way reversing valve;

[0051] 01-first manifold, 011-upper chamber, 012-lower chamber, 013-small chamber, 014-first partition;

[0052] 02-second manifold, 021-cavity portion, 022-channel portion, 023-spoiler portion, 024-inner wall, 025-insertion portion, 026-bending portion;

[0053] 03-third manifold, 031-third partition, 032-third chamber;

[0054] 04-the fourth collecting pipe;

[0055] 05-intermediate manifold, 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 mounting part, 059-second mounting part;

[0056] 06-separator, 061-separator cavity, 062-first baffle, 063-second baffle, 064-gap, 065-refrigerant flow port;

[0057] 07-gas distribution pipe group, 071-gas distribution main pipe, 0711-first gas distribution main pipe, 0712-second gas distribution main pipe, 072-gas distribution branch pipe;

[0058] 08-dispensing tube set, 081-dispensing main tube;

[0059] 09-connecting pipe, 091-first connecting pipe, 092-second connecting pipe;

[0060] 10- fins;

[0061] 11-Flat tube;

[0062] 12-tracheal group, 121-tracheal tributary;

[0063] 13-heat exchange part, 131-first row of heat exchange parts, 132-second row of heat exchange parts. DETAILED DESCRIPTION

[0064] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0065] In the description of the present invention, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship are based on the orientation or position relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0066] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected" and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances. In the description of the above embodiments, specific features, structures, materials or characteristics can be combined in any one or more embodiments or examples in a suitable manner.

[0067] The terms "first", "second", "third", and "fourth" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, a feature defined as "first", "second", "third", and "fourth" may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0068] The invention discloses an air conditioner, in particular a heat pump air conditioner. The air conditioner comprises a heat exchange circuit for performing heat exchange between indoor and outdoor areas so as to adjust the indoor temperature.

[0069] The heat exchange circuit can use existing technology Figure 1The heat exchange principle shown in the figure, that is, the heat exchange circuit includes 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. The evaporator 1 and the condenser 3 are collectively referred to as a heat exchanger.

[0070] One of the purposes of the present invention is to improve the structure of the heat exchanger, improve the balanced distribution of the refrigerant in the heat exchanger, improve the heat exchange effect of the heat exchanger, and further improve the overall heat exchange effect of the air conditioner.

[0071] The present invention improves the structures of the refrigerant inflow end, outflow end, connecting transitions between different processes, and connecting transitions of parallel heat exchangers in the heat exchanger, so as to improve the uniform distribution of the refrigerant.

[0072] The heat exchanger includes a plurality of equally spaced flat tubes 11 and fins 10. A plurality of microchannels for circulating refrigerant are formed in the flat tubes 11. The fins 10 are arranged between two adjacent flat tubes 11. The flow direction of air passing through the fins 10 is perpendicular to the flow direction of the refrigerant passing through the flat tubes 11. The heat / cold released by the refrigerant in the flat tubes 11 is taken away by the heat dissipation fins 10 and the air flow.

[0073] The flat tube 11 is made of porous microchannel aluminum alloy, and the fin 10 is made of aluminum alloy with a brazing composite layer on the surface, which is light in weight and high in heat exchange efficiency.

[0074] Embodiment 1

[0075] Figures 2 to 7 It is used to illustrate 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 refrigerant flows in opposite directions in the two flows. Figure 2 The figure shows the flow direction of the refrigerant in the flat tubes 11 when the heat exchanger is used as an evaporator.

[0076] The heat exchanger further includes a first header 01 and a fourth header 04 . The first header 01 is disposed at one end of the heat exchanger and communicates with one end of the flat tube 11 . The fourth header 04 is disposed at the other end of the heat exchanger and communicates with the other end of the flat tube 11 .

[0077] An upper chamber 011 and a lower chamber 012 for circulating refrigerant are formed in the first manifold 01 . The upper chamber 011 is connected to the flat tubes 11 in the second flow path, and the lower chamber 012 is connected to the flat tubes 11 in the first flow path.

[0078] The heat exchanger further includes a separator 06 , a gas distribution pipe group 07 , and a liquid distribution pipe group 08 .

[0079] The separator 06 is used to separate the gas phase refrigerant and the liquid phase refrigerant.

[0080] The gas distribution pipe group 07 is connected between the separator 06 and the lower chamber 012 and is used for circulating the gas-phase refrigerant.

[0081] The liquid distribution pipe group 08 is connected between the separator 06 and the lower chamber 012 and is used for circulating the liquid refrigerant.

[0082] When the heat exchanger is used as an evaporator, the gas-liquid two-phase refrigerant is effectively separated by the separator 06 before entering the lower chamber 012. The gas-phase refrigerant enters the lower chamber 012 through the gas separation pipe group 07, and the liquid-phase refrigerant enters the lower chamber 012 through the liquid separation pipe group 08. This fundamentally avoids the interaction and mutual separation of the two-phase refrigerants during the flow process, thereby ensuring that the mass and flow rate of the gas-phase and liquid-phase refrigerants entering the lower chamber 012 are approximately equal, so that there is no gas-liquid separation of the refrigerant in the lower chamber 012, thereby improving the uniformity of the distribution of the refrigerant in the flat tube 11.

[0083] See the structural diagram of separator 06 Figure 4 and Figure 5 A separator cavity 061 is formed inside the separator 06 , and a refrigerant flow port 065 is provided on the side wall of the separator 06 . The refrigerant flow port 065 is communicated with the separator cavity 061 , and the refrigerant flows into the separator cavity 061 through the refrigerant flow port 065 .

[0084] Reference Figures 3 to 5 The gas distribution pipe group 07 includes a gas distribution main pipe 071 and a plurality of water gas distribution branch pipes 072 connected to the gas distribution main pipe 071. The gas distribution main pipe 071 extends into the separator cavity 061, and the gas distribution branch pipes 072 extend in the horizontal direction and are connected to the lower chamber 012. The gas-phase refrigerant in the separator cavity 061 flows out from 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 gas-phase refrigerant flow rate at each location in the lower chamber 012 is uniform.

[0085] Further, see Figure 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 interconnected. The first gas distribution main pipe 0711 is connected to the separator cavity 061. The first gas distribution main pipe 0711 extends upward from the separator cavity 061 for a distance and then is connected to the second gas distribution main pipe 0712 through an arc portion. The second gas distribution main pipe 0712 extends downward, and a plurality of gas distribution branch pipes 072 are equidistantly arranged along the height direction of the second gas distribution main pipe 0712. The gas-phase refrigerant is diverted from top to bottom along the second gas distribution main pipe 0712 into the plurality of gas distribution branch pipes 072, thereby improving the uniform distribution of the gas-phase refrigerant.

[0086] In the separator cavity 061, the gas phase refrigerant tends to flow toward the upper part of the separator cavity 061, referring to Figure 5One end of the first gas distribution main pipe 0711 is arranged near the top of the separator cavity 61 to facilitate the inflow of the upper gas phase refrigerant.

[0087] Continue to refer to Figure 3 to Figure 5 The liquid separation pipe group 08 includes a liquid separation main pipe 081 and a plurality of liquid separation branch pipes (not shown) connected to the liquid separation main pipe. The liquid separation main pipe 081 extends into the separator cavity 61. The liquid separation branch pipe 081 extends in a horizontal direction and is connected to the lower chamber 012. The liquid-phase refrigerant in the separator cavity 061 flows out from the liquid separation main pipe 081, and then enters the lower chamber 012 through the plurality of liquid separation branch pipes, so that the flow rate of the liquid-phase refrigerant at each location in the lower chamber 012 is uniform.

[0088] Furthermore, the liquid separation main pipe 081 includes a first liquid separation main pipe and a second liquid separation main pipe that are connected. The first liquid separation main pipe is connected to the separator cavity 061. The first liquid separation main pipe extends upward from the separator cavity 061 for a distance and then is connected to the second liquid separation main pipe through an arc portion. The second liquid separation main pipe extends downward, and multiple liquid separation branch pipes 082 are equidistantly arranged along the height direction of the second liquid separation main pipe. The liquid-phase refrigerant is diverted from top to bottom along the second liquid separation main pipe into multiple liquid separation branch pipes, thereby improving the uniform distribution of the liquid-phase refrigerant.

[0089] In the separator cavity 061, the liquid refrigerant tends to flow toward the bottom of the separator cavity 061. Figure 5 One end of the first liquid separation main pipe is placed close to the bottom of the separator cavity 061 at a certain distance to facilitate the inflow of the lower liquid phase refrigerant.

[0090] The refrigerant separated by the gas distribution pipe group 07 and the liquid distribution pipe group 08 enters the lower chamber 012 from top to bottom and then is diverted into the flat tube 11. Compared with the traditional bottom-up diversion method, the influence of gravity and the resulting separation phenomenon during the upward diversion of the refrigerant can be suppressed.

[0091] Reference Figure 5 and Figure 6 A first baffle 062 is provided in the separator cavity 061, which is located below the end of the first gas-dividing main pipe 0711 and has a certain distance from the end of the first gas-dividing main pipe 0711. The first baffle 0662 can improve the separation efficiency of the gas-liquid two-phase refrigerant during the upward process, and can prevent the liquid refrigerant from entering the first gas-dividing main pipe 0711 under the action of inertia.

[0092] In order to further improve the separation efficiency of gas-liquid two-phase refrigerant, refer to Figure 5 and Figure 7A second baffle 063 is also provided in the separator cavity 061. The first baffle 062 and the second baffle 063 are respectively provided on both sides of the liquid separation main pipe 081. There is a certain gap 064 between the second baffle 063 and the liquid separation main pipe 081, and the gas-phase refrigerant continues to flow upward from the gap 064.

[0093] Reference Figure 3 A plurality of first partitions 014 are arranged at equal intervals in the lower chamber 012, and the plurality of first partitions 014 divide the lower chamber 012 into a plurality of small chambers 013, each small chamber 013 is connected to the same number of flat tubes 11, and each small chamber 013 is connected to a gas branch pipe 072 and a liquid branch pipe, so that the refrigerant flow entering each small chamber 013 is uniform, and the refrigerant with the same flow rate is evenly distributed to the same number of flat tubes 11, so that the refrigerant flow in each flat tube 11 is uniform.

[0094] In this embodiment, 10 small chambers 013 are formed in the lower chamber 012, and each small chamber 013 is connected to two flat tubes 11. Of course, in other embodiments, the number of small chambers 013 and the number of flat tubes 11 in each small chamber 013 can be flexibly set according to actual conditions, and this embodiment does not make specific restrictions.

[0095] This embodiment provides a specific implementation method for the fourth header 04. Figure 2 The fourth collecting pipe 04 is formed with mutually independent chambers M1, M2, M3, M4, and M5. The chambers M1 and M5 are connected via the first connecting pipe 091, and the chambers M2 and M4 are connected via the second connecting pipe 092. The refrigerant flowing into the chamber M1 enters the chamber M5 via the first connecting pipe 091, and the refrigerant flowing into the chamber M2 enters the chamber M4 via the second connecting pipe 092. The refrigerant entering the chamber M3 flows upward and enters the flat tube 11 in the second process.

[0096] The interior of the lower chamber 012 and the fourth manifold 04 adopts a compartment design to ensure that the pressure loss along the refrigerant from entering the first manifold 01 to leaving the first manifold 01 is equal to the local pressure loss, ensuring that the heat exchanger as a whole has good diversion uniformity.

[0097] Furthermore, when the two-phase refrigerant is boiling and exchanging heat in the flat tubes 11, the specific volume and flow rate gradually increase, the gas-liquid mixing degree increases, and the separation uniformity improves. Therefore, the number of flat tubes along the refrigerant flow direction should be gradually reduced; on the contrary, when the two-phase refrigerant is condensing and exchanging heat in the flat tubes, the specific volume and flow rate gradually decrease, and the gas and liquid tend to separate. In order to reduce the separation of the gas and liquid phases in space, the number of flat tubes along the refrigerant flow direction should be gradually increased. Therefore, in this embodiment, when the heat exchanger is used as an evaporator, the number of flat tubes 11 connected to the chamber M1 is less than the number of flat tubes 11 connected to the chamber M5, the number of flat tubes 11 connected to the chamber M2 is less than the number of flat tubes 11 connected to 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 greater than the number of flat tubes 11 flowing out of the chamber M3.

[0098] Furthermore, one end of the first connecting tube 091 is connected to the lower end of the chamber M1, so as to facilitate the flow of liquid refrigerant in the lower part of the chamber M1 into the first connecting tube 091; the other end of the first connecting tube 091 is connected to the upper end of the chamber M5, and the refrigerant in the first connecting tube 091 flows from top to bottom into the chamber M5, and gravity is used to improve the flow uniformity of the refrigerant in the flat tube 11 connected to the chamber M5.

[0099] Similarly, one end of the second connecting tube 092 is connected to the lower end of the chamber M2, so as to facilitate the flow of liquid refrigerant in the lower part of the chamber M2 into the second connecting tube 092; the other end of the second connecting tube 092 is connected to the upper end of the chamber M4, and the refrigerant in the second connecting tube 092 flows into the chamber M4 from top to bottom, and gravity is used to improve the flow uniformity of the refrigerant in the flat tube 11 connected to the chamber M4.

[0100] Reference Figure 2 In the first embodiment, the heat exchanger further includes an air pipe group 12, the air pipe group 12 includes a plurality of air pipe branches 121, the plurality of air pipe branches 121 are all connected to the upper chamber 011, and the refrigerant in the upper chamber 011 is collected and then flows out.

[0101] In Example 1, when the heat exchanger is used as an evaporator, the refrigerant enters the separator 06 from the refrigerant flow port 065, the gas-phase refrigerant enters the lower chamber 012 of the first collecting pipe 01 through the gas distribution pipe group 07, and the liquid-phase refrigerant enters the lower chamber 012 of the first collecting pipe 01 through the liquid distribution pipe group 08, and then the gas-liquid two-phase refrigerant simultaneously enters the multiple flat tubes 11 in the first process, and then enters the multiple flat tubes 11 in the second process through the first connecting pipe 091, the second connecting pipe 092, and the fourth collecting pipe 04, and finally flows out from the gas pipe group 12 through the upper chamber 011 of the first collecting pipe 01.

[0102] 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 when it is used as an evaporator, which will not be described in detail here.

[0103] Embodiment 2

[0104] Reference Figure 8 The heat exchanger has an upward flow and a downward flow. The upward flow and the downward flow refer to the flow direction of the refrigerant. They are only for the convenience of explaining the technical solution. For the above-mentioned embodiment 1, the first flow can be called the upward flow and the second flow can be called the downward flow.

[0105] In the second embodiment, the technical solution is explained by taking the heat exchanger having the first flow and the second flow as an example, the first flow is the upward flow, and the second flow is the downward flow.

[0106] The first flow path and the second flow path are connected via the second collecting pipe 02 and the third collecting pipe 03. Specifically, the second collecting pipe 02 is connected to the flat tubes 11 in the second flow path, and the third collecting pipe is simultaneously connected to the flat tubes 11 in the first flow path and part of the flat tubes 11 in the second flow path. The second collecting pipe 02 and the third collecting pipe 03 are connected via the connecting pipe 09.

[0107] Reference Figures 9 to 14 The second collecting pipe 02 includes a cavity portion 021, a channel portion 022, and a spoiler portion 023. The cavity portion 021 is connected to the connecting pipe 09, one end of the channel portion 022 is connected to the cavity portion 021, and the other end of the channel portion 022 is connected to the flat tube 11 in the second process. The spoiler portion 023 is arranged in the cavity portion 021, and is used to disturb the flow path of the refrigerant in the cavity portion 021, so as to promote the mixing of the refrigerant in the high-pressure area and the low-pressure area in the cavity portion 021.

[0108] Specifically, the refrigerant in the flat tube 11 of the first process 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 portion 021. The larger the refrigerant flow rate, the more obvious the uneven distribution of the refrigerant. The inflow end of the refrigerant will generate low pressure, and then a high-pressure area and a low-pressure area will be formed in the cavity portion 021. The spoiler 023 can effectively avoid the flow blind area caused by the eddy current in the cavity portion 021. The spoiler 023 disturbs the flow path of the refrigerant in the cavity portion 021, so that the refrigerant in the high-pressure area and the low-pressure area in the cavity portion 021 are mixed, and the refrigerant circulates in the cavity portion 021. The refrigerant circulation path formed by the spoiler 023 can automatically adapt to the change of the refrigerant flow rate, so that the refrigerant entering different channel portions 022 can be evenly distributed, so as to achieve uniform refrigerant flow in different microchannels in the same flat tube 11 and in different flat tubes 11 in the same process.

[0109] Reference Fig. 9 and Fig.10The second manifold 02 includes a manifold body, wherein a plurality of channel portions 022 are formed inside the manifold body through a plurality of spaced inner walls 024, wherein the plurality of channel portions 022 are evenly spaced, and a cavity portion 021 is formed at the bottom of the manifold body, wherein a plurality of flat tubes 11 are connected to the side wall of the manifold body, and a connecting tube 09 is connected to the other side wall of the manifold body opposite to the flat tubes, wherein one end of the channel portion 022 is connected to the cavity portion 021, and the other end of the channel portion 022 is connected to the flat tube 11, Fig.10 In order to conveniently illustrate the internal structure of the collecting tube body, one side wall thereof is hidden and not shown.

[0110] In the second embodiment, the collecting pipe body is a square structure, and the channel portion 022 formed by multiple inner wall surfaces is a flat structure. In other embodiments, the collecting pipe body can be a cylindrical structure, an elliptical cylindrical structure, etc. This embodiment does not make specific restrictions.

[0111] The multiple channel portions 022 are evenly spaced apart, so that the refrigerant in the cavity portion 021 can flow evenly into different channel portions 022 , thereby ensuring that the refrigerant flow in the flat tubes 11 connected to each channel portion 022 is even.

[0112] The channel portion 022 has a bending portion 026. The side of the channel portion 022 close to the cavity portion 021 is perpendicular to the cavity portion 021, and the side of the channel portion 022 close to the flat tube 11 is parallel to the flat tube 11, which facilitates the circulation of the refrigerant between the cavity portion 021 and the channel portion 022 and between the flat tube 11 and the channel portion 022.

[0113] In other embodiments, the channel portion 022 may be a flow channel of other structural forms, such as a flow channel with an arc surface. In order to balance the resistance between different channels, the number of channel turns may be changed, the surface roughness of the channel portion may be changed, etc.

[0114] An inserting portion 025 is provided on the side wall of the collecting pipe body. The inserting portion 025 is communicated with the channel portion 022 . The flat tube 11 is inserted into the inserting portion 025 to achieve communication between the flat tube 11 and the channel portion 022 .

[0115] The number of flat tubes 11 that can be connected to each second header 02 can be flexibly set according to actual conditions. In the second embodiment, the number of flat tubes 11 that can be connected to each second header 02 is 1-20.

[0116] Reference Figures 10 to 14 , Fig.12 for Fig.11 CC section view, Fig.13 for Fig.11In the DD-direction cross-sectional view, the spoiler 023 is a partition structure arranged in the cavity 021. The partition structure extends in a direction parallel to the inflow direction of the refrigerant. The partition structure is an incomplete partition, that is, there is a certain gap between the partition structure and the inner walls around the cavity 021.

[0117] Fig.14 The arrows in the figure indicate the flow direction of the refrigerant. When the gas-liquid two-phase refrigerant evaporates in the heat exchanger, part of the refrigerant flowing into the cavity 021 from the connecting pipe 09 flows directly upward and directly into the channel 022, while the other part of the refrigerant bypasses the spoiler 023 and enters the side of the cavity 021 away from the refrigerant inlet (i.e. Fig.14 The left part in the orientation shown in the figure) is that while this part of the refrigerant flows around the spoiler 023, part of the refrigerant will flow into the channel 022, and the remaining part of the refrigerant will bypass the spoiler 023 and then mix with the newly-flown refrigerant before entering the next flow cycle. Since the flow velocity of the refrigerant is high when it enters the cavity 021 from the connecting pipe 09, the pressure at the inlet of the refrigerant in the cavity 021 is low, which enables the refrigerant that cannot flow into the channel 022 in time to circulate around the spoiler 023. The refrigerant circulation flow path formed in the cavity 021 is conducive to improving the uniform distribution of the refrigerant in the cavity 021, making the refrigerant entering different channel parts 022 uniform, and then making the refrigerant in different flat tubes uniform.

[0118] Under high flow rate, the uneven distribution of refrigerant is more obvious. When the refrigerant flow rate is large, the uniform distribution effect of the solution on the refrigerant is more significant. Because the larger the flow rate, the more significant the low pressure effect caused by the injection at the refrigerant inlet of the cavity 021, the more significant the circulation loop that promotes the refrigerant to flow around the spoiler 023, and the refrigerant circulation loop automatically adapts to the change of the external refrigerant flow rate, thereby improving the uniform distribution of the refrigerant.

[0119] Since the channel portion 022 is a flat structure, which exactly matches the structure of the flat tube 11 , the uniform distribution of the refrigerant in the channel portion 022 is also conducive to improving the uniformity of the refrigerant entering different microchannels in the same flat tube 11 .

[0120] Reference Fig.11 and Fig.14 The connecting pipe 023 is preferably arranged on a side of the cavity portion 021 away from the air supply direction, which is beneficial to improving the heat dissipation efficiency.

[0121] Fig.15 and Fig.16 Two other deformation structures of the spoiler 023 are shown. By increasing the number of the spoiler 023 to form multi-path reflux and multi-path spoiler in the cavity 021, the uniform distribution effect of the refrigerant is further improved.

[0122] Fig.15 In the embodiment, the spoiler 023 is a partition structure arranged at two intervals, and the partition structure is Fig.14 The partitions shown are of the same structure, but arranged differently. Fig.15 In the embodiment, the two spoilers 023 are symmetrically distributed in the cavity 021 relative to the position where the refrigerant flows into the cavity 021. The refrigerant flowing into the cavity 021 first enters between the two spoilers 023 and then splits into two paths, one path of refrigerant forms a circulation loop around the spoiler 023 on the left, and the other path of refrigerant forms a circulation loop around the spoiler 023 on the right.

[0123] Fig.16 In the embodiment, the spoiler 023 is a partition structure arranged at three intervals. Fig.14 The partitions shown are of the same structure, but arranged differently. Fig.16 In the embodiment, three spoilers 023 are symmetrically distributed in the cavity 021 relative to the position where the refrigerant flows into the cavity 021, and the spoiler 023 in the middle is directly opposite to the connecting pipe 09. The refrigerant flowing into the cavity 021 is divided into two paths, one of which flows along the gap between the left spoiler 023 and the middle spoiler 023 and forms a circulation loop around the left spoiler 023, and the other flows along the gap between the right spoiler 023 and the middle spoiler 023 and forms a circulation loop around the right spoiler 023.

[0124] Back to Figure 8 The second collecting pipe 02 has at least one, and a plurality of third partitions 031 are arranged in the third collecting pipe 03. The plurality of third partitions 031 divide the internal space of the third collecting pipe 03 into a plurality of independent third chambers 032, wherein one third chamber 032 is simultaneously connected to part of the flat tubes 11 in the upward flow (first flow) and part of the flat tubes 11 in the downward flow (second flow), and the number of the remaining third chambers 031 is the same as the number of the second collecting pipes 02, and each of the remaining third chambers 031 is connected to each second collecting pipe 02 one by one through the connecting pipe 09.

[0125] In the second embodiment, there are two second manifolds 02, and three third partitions 031 are arranged in the third manifold 03. The third partitions 031 divide the interior of the third manifold 03 into three independent third chambers 032, which are marked as N1, N2, and N3 respectively. The second manifold 02 located at the top is connected to the third chamber N1 through the first connecting pipe 091, and the second manifold 02 located at the bottom is connected to the third chamber N2 through the second connecting pipe 092. The third chamber N3 is simultaneously connected to some flat tubes 11 in the first process and some flat tubes 11 in the second process.

[0126] The cooperation between the plurality of third chambers 032 and the plurality of second collecting pipes 02 is conducive to further improving the uniform distribution of the refrigerant.

[0127] One end of the first connecting tube 091 is connected to the lower end of the third chamber N1, so that the liquid refrigerant in the third chamber N1 can flow into the first connecting tube 091. The other end of the first connecting tube 091 is connected to the lower end of the second collecting pipe 02 and the cavity portion 021, so that the gas-liquid two-phase refrigerant can be evenly distributed through the second collecting pipe 02.

[0128] Similarly, one end of the second connecting pipe 092 is connected to the lower end of the third chamber N2, so that the liquid refrigerant in the third chamber N2 can flow into the second connecting pipe 092. The other end of the second connecting pipe 092 is connected to the lower end of the second collecting pipe 02 and the cavity portion 021, so that the gas-liquid two-phase refrigerant can be evenly distributed through the second collecting pipe 02.

[0129] In the third chamber 032 and the second manifold 02 connected at both ends of the same connecting pipe 09, the number of flat tubes connected to the third chamber 032 is less than the number of flat tubes 11 connected to the second manifold 02. In the second embodiment, the number of flat tubes connected to the third chamber N1 is less than the number of flat tubes connected to the second manifold 02, the number of flat tubes connected to the third chamber N2 is less than the number of flat tubes connected to the second manifold 02, and the number of flat tubes in the first flow path connected to the third chamber N3 is less than the number of flat tubes in the second flow path connected. The reason for such design is the same as the reason for the design of the multi-layer partition of the fourth manifold 04 in the first embodiment, which will not be repeated here.

[0130] Embodiment 3

[0131] In order to improve the heat exchange efficiency of the heat exchanger, multiple heat exchangers can be arranged in parallel. One of the purposes of the third embodiment is to improve the uniform distribution of refrigerant between two adjacent heat exchangers to improve the heat exchange uniformity of the entire heat exchanger assembly.

[0132] Reference Figures 17 to 19 The heat exchanger includes a plurality of heat exchange parts 13 , which are arranged in parallel and connected to each other, and the flat tubes 11 on two adjacent heat exchangers 13 are connected to each other through an intermediate header 05 .

[0133] Fig.17 The arrow in the figure indicates the flow direction of the refrigerant when the heat exchanger is in the evaporation condition. Fig.18 The arrow in the figure indicates the flow direction of the refrigerant when the heat exchanger is in condensing condition. Fig.19 This is a schematic diagram of the structure after multiple heat exchange parts are actually installed.

[0134] In Example 3, the technical solution is explained by taking a heat exchanger with two heat exchange parts 13 as an example. The two heat exchange parts 13 are defined as a first row of heat exchange parts 131 and a second row of heat exchange parts 132. The first row of heat exchange parts 131 is located in the downwind area in the air supply direction, and the second row of heat exchange parts 132 is located in the upwind area in the air supply direction. The first row of heat exchange parts 131 and the second row of heat exchange parts 132 both include a number of equidistantly arranged flat tubes 11 and fins 10. Air flows through the gaps between the flat tubes 11 and the fins 10 to achieve a heat exchange effect.

[0135] The two heat exchange parts are connected through the intermediate collecting pipe 05. The heat exchanger includes a first process, a second process, a third process, and a fourth process. The first process and the fourth process are located on the first row of heat exchange parts 131, and the second process and the third process are located on the second row of heat exchange parts 132. The flat tubes in the first process are connected with the flat tubes in the second process through the intermediate collecting pipe 05, and the flat tubes in the third process are connected with the flat tubes in the fourth process through the intermediate collecting pipe 05.

[0136] The configuration of one end of the first row of heat exchange parts 131 can refer to Figure 2 The structural arrangement of the first embodiment shown will not be described in detail here.

[0137] The configuration of one end of the second row heat exchange portion 132 can refer to Figure 8 The structural arrangement of the second embodiment shown will not be described in detail here.

[0138] Reference Fig.17 When the heat exchanger is in the evaporating condition, the refrigerant enters the lower chamber 012 of the first collecting pipe 01 through the separator 06, the gas distribution pipe group 07, and the liquid distribution pipe group 08, and then flows through the first process, the intermediate collecting pipe 05, and the second process in turn to enter the third collecting pipe 03, and then enters the second collecting pipe 02 through the first connecting pipe 091 and the second connecting pipe 092, and then flows through the third process, the intermediate collecting pipe 05, and the fourth process in turn to enter the upper chamber 011 of the first collecting pipe 01, and finally flows out from the gas pipe group 12.

[0139] Reference Fig.18 When the heat exchanger is in the condensing condition, the refrigerant enters the upper chamber 011 of the first collecting pipe 01 through the gas pipe group 12, and then flows through the fourth process, the intermediate collecting pipe 05, and the third process in sequence to enter the second collecting pipe 02, and then enters the third collecting pipe 03 through the first connecting pipe 091 and the second connecting pipe 092, and then flows through the second process, the intermediate collecting pipe 05, and the first process in sequence to enter the lower chamber 012 of the first collecting pipe 01, and finally flows out through the gas distribution pipe group 07, the liquid distribution pipe group 08, and the separator 06.

[0140] As for the number of flat tubes in each process, the number of flat tubes in the first process, the second process, the third process, and the fourth process gradually increases, that is, the number of flat tubes in the fourth process is greater than the number of flat tubes in the third process, the number of flat tubes in the third process is greater than the number of flat tubes in the second process, and the number of flat tubes in the second process is greater than the number of flat tubes in the first process.

[0141] A plurality of sub-cavities 051 are formed inside the middle manifold 05 by partitions and arranged along the height direction of the middle manifold 05. The plurality of sub-cavities 051 are independent of each other, and the structure of each sub-cavity 051 is the same. Figures 20 to 27 The figure shows a schematic diagram of the structure of a single sub-cavity 051, wherein Fig.21 For Fig. 20 The view observed in the Q direction.

[0142] Reference Figure 20 to Figure 23 Each sub-cavity 051 includes a first cavity 052, a second cavity 053, a third cavity 054, a first circulation portion 055, and a second circulation portion 056. The first cavity 052 is communicated with some flat tubes on the first row of heat exchange parts 131, the second cavity 053 is communicated with some flat tubes on the second row of heat exchange parts 132, the third cavity 054 is communicated with the first cavity 052, the first circulation portion 055 is located below the third cavity 054 and is used to connect the second cavity 053 and the third cavity 054, and the second circulation portion 056 is located above the second cavity 052 and is used to connect the first cavity 052 and the second cavity 053.

[0143] When the heat exchanger is used as an evaporator, the refrigerant first enters the first cavity 052, and most of the refrigerant in the first cavity 052 will flow into the third cavity 054. The gas-liquid two-phase refrigerant entering the third cavity 054 tends to separate under the action of gravity and the uniformity becomes worse. The refrigerant in the third cavity 054 enters the second cavity 053 through the first circulation part 055 below. Since the flow rate of the gas-phase refrigerant is higher than the flow rate of the liquid-phase refrigerant, the gas-phase refrigerant above the third cavity 054 will mix with the liquid-phase refrigerant below during the process of flowing downward through the first circulation part 055, and then enters the second cavity 053 due to the acceleration effect of the first circulation part 055, and flows from bottom to top into the flat tube connected to the second cavity 053, thereby realizing the uniform distribution of the gas-liquid two-phase refrigerant in the flat tube. The speed of the refrigerant decreases during the flow from bottom to top in the second cavity 053, and a vortex is formed in the upper part of the second cavity 053. The refrigerant flow rate of the flat tube at the vortex is relatively small, and the second circulation part 056 will allow the excess refrigerant in the upward process of the refrigerant to be introduced into the first cavity 052, mixed with the high-speed refrigerant in the first cavity 052, and 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.

[0144] The diameter of the first circulation portion 055 is preferably larger than the diameter of the flat tube 11 , so that the refrigerant in the third cavity 054 can smoothly enter the second cavity 053 through the first circulation portion 055 .

[0145] A plurality of first mounting portions 058 for mounting the flat tubes 11 are provided on the side wall of the first cavity 052, and a plurality of second mounting portions 059 for mounting the flat tubes 11 are provided on the side wall of the second cavity 053. The first mounting portions 058 and the second mounting portions 059 are located on the same side of the sub-cavity 051. In this way, after the first row of heat exchange portions 131 and the second row of heat exchange portions 132 are connected via the intermediate collecting pipe 05, a front-to-back side-by-side structure can be formed, which is more compact and helps to reduce the volume of the entire heat exchanger.

[0146] The first mounting portion 058 and the second mounting portion 059 may be insertion holes provided on the side wall of the sub-cavity 051 , and the flat tube 11 may be directly plugged into the insertion holes, which is convenient for installation and has a reliable structure.

[0147] The number of the first mounting parts 058 and the number of the second mounting parts 059 are the same, so that the number of the flat tubes connected to the first cavity 052 is the same as the number of the flat tubes connected to the second cavity 053, so as to improve the uniformity of the refrigerant in the flat tubes of different processes.

[0148] As a preferred embodiment, a first partition plate 0511, a second partition plate 0512, and a third partition plate 0513 are provided in the sub-cavity 051, and the first partition plate 0511, the second partition plate 0512, and the third partition plate 0513 divide the interior of the sub-cavity 051 into a first cavity 052, a second cavity 053, and a third cavity 054.

[0149] 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 as to form a first cavity 052 and a second cavity 053 of equal volume, so as to achieve uniform distribution of the refrigerant.

[0150] Reference Fig.23 , Figure 25 to Figure 27 The first partition plate 0511 is arranged between the first cavity 052 and the second cavity 053, the second circulation portion 056 is arranged at the upper part of the first partition plate 0511, the second partition plate 0512 is arranged between the first cavity 052 and the third cavity 054, the second partition plate 0512 is provided with a plurality of third circulation portions 057 for the circulation of refrigerant, the third partition plate 0513 is arranged between the second cavity 053 and the third cavity 054, and the first circulation portion 055 is arranged at the lower part of the third partition plate 0513.

[0151] When the heat exchanger is used as an evaporator, the refrigerant in the first cavity 052 flows into the plurality of flat tubes, and most of it enters the third cavity 054 through the third circulation portion 057. The refrigerant in the third cavity 054 enters the second cavity 053 through the first circulation portion 055 below. The first circulation portion 055 is arranged below, so that the gas-phase refrigerant above the third cavity 054 will mix with the liquid-phase refrigerant below during the process of flowing downward through the first circulation portion 055, and then enter the second cavity 053 through the acceleration effect of the first circulation portion 055, and flow from bottom to top into the flat tube connected to the second cavity 053, thereby realizing uniform distribution of the gas-liquid two-phase refrigerant in the flat tube. The speed of the refrigerant decreases during the flow from bottom to top in the second cavity 053, and a vortex is formed in the upper part of the second cavity 053. The refrigerant flow rate of the flat tube at the vortex is relatively small, and the second circulation part 056 located at the top will guide the excess refrigerant in the upward process of the refrigerant into the first cavity 052, mix with the high-speed refrigerant in the first cavity 052, and 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.

[0152] The number of third circulation portions 057 is preferably the same as the number of flat tubes connected to the first cavity 052. The ends of the flat tubes in the first cavity 052 are at a certain distance from the third circulation portions 057 and are directly opposite to the third circulation portions 057, so that most of the refrigerant ejected from the flat tubes can be injected into the third cavity 054.

[0153] also, Figure 20 to Figure 23 The sub-cavity 051 shown is a rectangular structure. In other embodiments, the third cavity 054 can be a D-type, O-type or other structural forms, which are not specifically limited in this embodiment. Fig.24 As shown, the third cavity 054 is D-shaped.

[0154] In the third embodiment, when the gas-liquid two-phase refrigerant flows between the first row of heat exchange parts 131 and the second row of heat exchange parts 132, regardless of whether the upstream refrigerant is evenly distributed, after passing through the intermediate collecting pipe 05, it can be ensured that the refrigerant entering the next process flat tube is dynamically adjusted and evenly distributed.

[0155] In the description of the above embodiments, specific features, structures, materials or characteristics may be combined in a suitable manner in any one or more embodiments or examples.

[0156] The above are only specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed by the present invention should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. An air conditioner, comprising: A heat exchange circuit is used for exchanging heat between indoor and outdoor. A heat exchanger is provided on the heat exchange circuit. The heat exchanger has an upward flow and a downward flow. Characterized in that the heat exchanger comprises: A flat tube having a plurality of microchannels therein for circulating a refrigerant; a second header, connected to the flat tubes in the downward flow process, for circulating the refrigerant; a third header, connected to the flat tubes in the upward flow path, for circulating the refrigerant; a connecting pipe, connecting the second header and the third header, and used for circulating the refrigerant; Wherein, the second header comprises: A cavity portion, communicated with the connecting pipe, for circulating the refrigerant; A channel portion, one end of which is in communication with the cavity portion and the other end of which is in communication with the flat tube, for circulating the refrigerant; a flow disturbance portion, disposed in the cavity portion, for disturbing a flow path of the refrigerant in the cavity portion, so as to promote mixing of the refrigerant in the high-pressure area and the low-pressure area in the cavity portion; The second header includes a header body, wherein a plurality of channel portions are formed through a plurality of spaced inner walls inside the header body, the bottom of the header body forms the cavity portion, a plurality of flat tubes are connected to the side wall of the header body, the connecting tube is connected to the other side wall of the header body opposite to the flat tubes, one end of the channel portion is connected to the cavity portion, and the other end of the channel portion is connected to the flat tube; The channel portion has a bending portion, a side of the channel portion close to the cavity portion is perpendicular to the cavity portion, and a side of the channel portion close to the flat tube is parallel to the flat tube.

2. The air conditioner according to claim 1, characterized in that , An inserting portion is provided on the side wall of the second collecting pipe, the inserting portion is communicated with the channel portion, and the flat tube is inserted in the inserting portion.

3. The air conditioner according to claim 1, characterized in that , The spoiler is a partition structure disposed in the cavity, the partition structure extends in a direction parallel to the inflow direction of the refrigerant, and a certain gap is formed between the partition structure and the inner walls around the cavity.

4. The air conditioner according to claim 3, characterized in that , The connecting pipe is connected to a side of the cavity away from the air supply direction.

5. The air conditioner according to claim 1, characterized in that , The spoiler is at least two partition structures arranged in the cavity and spaced apart from each other. The partition structures extend in a direction parallel to the inflow direction of the refrigerant. The plurality of partition structures are symmetrically distributed relative to the position where the refrigerant flows into the cavity.

6. The air conditioner according to any one of claims 1 to 5, characterized in that , The second header has at least one; A plurality of third partitions are provided in the third collecting pipe, and the plurality of third partitions divide the internal space of the third collecting pipe into a plurality of independent third chambers, wherein one of the third chambers is simultaneously connected to part of the flat tubes in the upward flow and part of the flat tubes in the downward flow, and the number of the remaining third chambers is the same as the number of the second collecting pipes, and each of the remaining third chambers is connected to each of the second collecting pipes one by one through the connecting pipe.

7. The air conditioner according to claim 6, characterized in that , One end of the connecting pipe is connected to the lower end of the third chamber, and the other end is connected to the lower end of the second collecting pipe.

8. The air conditioner according to claim 6, characterized in that , In the third chamber and the second header connected to two ends of the same connecting pipe, the number of the flat tubes connected to the third chamber is less than the number of the flat tubes connected to the second header.

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