Splitting assembly, heat exchanger assembly, air conditioning system and air conditioner

Abstract

The utility model discloses a kind of shunt components, heat exchanger components and air conditioning systems, shunt component is used for heat exchanger component, comprising: body part and flow resistance component.The body part has first port, second port, first communicating hole and second communicating hole, flow resistance component is located on the body part, first port and first communicating hole are located at the same side of flow resistance component, second port and second communicating hole are located at the same side of flow resistance component, first port and second port are located at the opposite side of flow resistance component, flow resistance component only allows refrigerant to flow from second port side to first communicating hole side.According to the shunt component of the utility model, the flow path of refrigerant can be changed, and in different modes of the air conditioning system, the automatic switching of different flow paths of refrigerant in the heat exchanger component is realized, so as to improve the heat exchange efficiency of the heat exchanger component and the performance of the air conditioning system.

Description

Technical Field

[0001] This utility model relates to the field of air handling equipment technology, and in particular to a flow distribution component, a heat exchanger component, an air conditioning system, and an air conditioner. Background Technology

[0002] In related technologies, the heat exchanger flow path design of an air conditioning system directly affects its performance. During cooling and heating processes, the outdoor heat exchanger acts as both a condenser and an evaporator, respectively. During these processes, the refrigerant undergoes evaporation (absorbing heat) and cooling (condensing heat) within the outdoor heat exchanger. Given a fixed area and volume of the outdoor heat exchanger, its optimal heat exchange flow path differs depending on whether it functions as a condenser or an evaporator. Current air conditioning systems use a single flow path for the outdoor heat exchanger, which cannot be adaptively adjusted according to the system's operating mode, thus affecting the heat exchange efficiency of the outdoor heat exchanger and the overall performance of the air conditioning system. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a flow-diverting component that can change the flow path of the refrigerant, enabling automatic switching of different flow paths of the refrigerant within the heat exchanger assembly under different modes of the air conditioning system, thereby improving the heat exchange efficiency of the heat exchanger assembly and the performance of the air conditioning system.

[0004] This utility model also proposes a heat exchanger assembly, which includes the above-mentioned flow splitter assembly.

[0005] This utility model also proposes an air conditioning system, which includes the heat exchanger assembly described above.

[0006] This utility model also proposes an air conditioner, which includes the above-mentioned air conditioning system.

[0007] A flow-diverting component according to an embodiment of the present invention is used in a heat exchanger assembly, comprising: a body portion and a flow-blocking component. The body portion has a first port, a second port, a first connecting hole, and a second connecting hole. The flow-blocking component is disposed on the body portion. The first port and the first connecting hole are located on the same side of the flow-blocking component, and the second port and the second connecting hole are also located on the same side of the flow-blocking component. The first port and the second port are located on opposite sides of the flow-blocking component. The flow-blocking component only allows refrigerant to flow from the second port side to the first connecting hole side. When the heat exchanger assembly functions as an evaporator, refrigerant flows into the heat exchanger assembly from the second port, and then flows into the heat exchange tubes or heat exchange channels of the heat exchanger assembly from the first connecting hole and the second connecting hole before flowing out of the heat exchanger assembly. In this case, the flow-blocking component is open, and the first port is closed. When the heat exchanger assembly functions as a condenser, refrigerant flows into the heat exchanger assembly from the first port, and then flows into the heat exchange tubes or heat exchange channels of the heat exchanger assembly from the first connecting hole before sequentially flowing out of the heat exchanger assembly from the second connecting hole and the second port. In this case, the flow-blocking component is closed.

[0008] According to an embodiment of the present invention, the flow-diverting component, by providing a first port, a second port, a first connecting hole, and a second connecting hole on its main body, and by providing a flow-blocking component on its main body, allows the flow-blocking component to allow refrigerant to flow only from the second port to the first port. This enables the automatic opening and closing or flow blocking of the flow-blocking component, thereby achieving automatic flow guidance of the refrigerant and changing its flow direction. When the flow-diverting component is used in heat exchanger assemblies and air conditioning systems, it can automatically switch the refrigerant flow paths within the heat exchanger assembly in different modes of the air conditioning system, thereby improving the heat exchange efficiency of the heat exchanger assembly, enhancing the cooling or heating performance of the air conditioning system, and improving energy efficiency. Furthermore, it requires no other control structures, is simple in structure, easy to implement, and low in cost.

[0009] In some embodiments of this utility model, there are multiple first connecting holes. When the heat exchanger assembly is used as an evaporator and when the heat exchanger assembly is used as a condenser, the multiple first connecting holes are used to distribute the refrigerant; and / or, the multiple first connecting holes are located above or diagonally above the flow-blocking component, and the multiple first connecting holes face horizontally, upward or diagonally upward.

[0010] According to some embodiments of the present invention, the main body includes a manifold, which includes a first manifold and a second manifold. The first port and the first connecting hole are disposed on the first manifold, and the second port and the second connecting hole are disposed on the second manifold. The first manifold and the second manifold are integral components, and the flow-blocking component is disposed inside the first manifold or the second manifold; or, the first manifold and the second manifold are separate components, and the flow-blocking component is connected between the first manifold and the second manifold.

[0011] In some embodiments of this utility model, the inner diameter of the first manifold is less than or equal to the inner diameter of the second manifold.

[0012] In some embodiments of this utility model, the end of the first manifold facing away from the flow-blocking component is open to form the first port; or the first port is located on the peripheral wall of the first manifold; or the first manifold includes a manifold body and a first tee pipe, the first end of the first tee pipe is connected to the flow-blocking component, the second end of the first tee pipe is connected to the manifold body, the first port is located at the third end of the first tee pipe, and the manifold body is provided with the first connecting hole; and / or the end of the second manifold facing away from the flow-blocking component is open to form the second port; or the second port is located on the peripheral wall of the second manifold.

[0013] According to some embodiments of the present invention, the first connecting hole is one or a plurality of holes spaced apart along the length direction of the first manifold; and / or, the second connecting hole is one or a plurality of holes spaced apart along the length direction of the second manifold.

[0014] According to some embodiments of the present invention, the diversion assembly further includes a first branch pipe, at least one of the first branch pipes being connected to the first connecting hole; and / or a second branch pipe, at least one of the second branch pipes being connected to the second connecting hole.

[0015] In some embodiments of this utility model, the inner diameter of the second branch pipe is less than or equal to the inner diameter of the first branch pipe; and / or the area of ​​the second connecting hole is less than the area of ​​the first connecting hole; and / or the number of the second branch pipes is less than the number of the first branch pipes.

[0016] In some embodiments of this utility model, the first branch pipe and the second branch pipe are spaced apart in a projection plane perpendicular to the axis of the second manifold.

[0017] In some embodiments of this utility model, the end of the first branch pipe facing away from the first connecting port and the end of the second branch pipe facing away from the second connecting hole have the same orientation.

[0018] In some embodiments of this utility model, the diversion assembly further includes a diversion component, and at least one of the first connecting holes is connected to a plurality of the first branch pipes through the diversion component.

[0019] In some embodiments of this utility model, the diversion component is a diversion pipe, one end of which is connected to the first connecting hole, and the other end of which is connected to multiple first branch pipes.

[0020] In some embodiments of this utility model, along the length of the first manifold, the distance between the first connecting hole connected to the flow divider and the outlet end of the flow blocking component is 15mm-300mm; and / or along the length of the second manifold, the distance between the second connecting hole and the inlet end of the flow blocking component is 15mm-100mm; and / or along the length of the second manifold, the distance between the second connecting hole and the inlet end of the flow blocking component is less than the distance between the first connecting hole connected to the flow divider and the outlet end of the flow blocking component.

[0021] In some embodiments of this utility model, at least one second branch pipe is connected to the second connecting hole, and the second branch pipe has a bent portion.

[0022] In some embodiments of this utility model, the second branch pipe has multiple sub-pipes connected in sequence, and two adjacent sub-pipes form the bend at an angle to each other.

[0023] In some embodiments of this utility model, the plurality of sub-tubes include a first sub-tube and a second sub-tube connected in sequence, one end of the first sub-tube is connected to the second communicating hole, and the first sub-tube and the second sub-tube are perpendicular to each other.

[0024] In some embodiments of this utility model, a first arc-shaped segment is provided between the first sub-tube and the second sub-tube.

[0025] In some embodiments of this utility model, the plurality of sub-tubes further include a third sub-tube, one end of which is connected to the end of the second sub-tube opposite to the first sub-tube, the third sub-tube being perpendicular to the second sub-tube, and the first sub-tube and the third sub-tube being located on opposite sides of the second sub-tube; or, the first sub-tube and the third sub-tube being located on the same side of the second sub-tube.

[0026] In some embodiments of this utility model, a second arc-shaped segment is provided between the second sub-tube and the third sub-tube.

[0027] In some embodiments of this utility model, the sub-tube directly connected to the second connecting hole among the plurality of sub-tubes is the first sub-tube. In the projection plane perpendicular to the axis of the main body, the angle between the first sub-tube and at least one first branch tube is A, and satisfies: 0°<A°≤180°.

[0028] In some embodiments of this utility model, the main body includes a connecting pipe and a distributor, the flow-blocking component is disposed on the connecting pipe, the second port and the second connecting hole are connected to the connecting pipe, at least one of the second port and the second connecting hole is connected to one end of the connecting pipe, the distributor has a main interface and a plurality of distributing holes, the main interface is connected to the other end of the connecting pipe, and at least some of the distributing holes are the first connecting holes.

[0029] In some embodiments of this utility model, there are multiple first connecting holes, each of which is connected to a first branch pipe, and the first port is located on the connecting pipe between the distributor and the flow-blocking component.

[0030] In some embodiments of this utility model, the number of the first connecting holes is multiple, the number of the distribution holes is N, N-1 of the distribution holes are respectively connected to a first branch pipe, and the remaining distribution hole forms the first port.

[0031] In some embodiments of this utility model, along the length of the connecting pipe, the distance between the main interface and the outlet end of the flow-blocking component is 15mm-500mm; and / or along the length of the connecting pipe, the distance between the second connecting hole and the inlet end of the flow-blocking component is 15mm-100mm; and / or along the length of the connecting pipe, the distance between the second connecting hole and the inlet end of the flow-blocking component is less than the distance between the main interface and the outlet end of the flow-blocking component.

[0032] In some embodiments of this utility model, at least one second branch pipe is connected to the second connecting hole, and the second branch pipe has a bent portion.

[0033] According to some embodiments of the present invention, the first port is formed by opening one end of the main body located on the side of the flow-blocking member away from the second port in the longitudinal direction; or, the first port is provided on the peripheral wall of the main body.

[0034] According to some embodiments of the present invention, the diversion assembly further includes an air intake pipe, one end of which is connected to the first port.

[0035] In some embodiments of this utility model, the air intake pipe is a U-shaped pipe, a V-shaped pipe, or an inverted U-shaped pipe.

[0036] According to some embodiments of the present invention, one end of the main body located on the side of the flow-blocking component away from the first port is open to form the second port; or, the second port is provided on the peripheral wall of the main body.

[0037] According to some embodiments of the present invention, the diversion component further includes an inlet / outlet pipe, one end of which is connected to the second port.

[0038] In some embodiments of this utility model, a first branch pipe is connected to the first connecting hole. In the projection plane perpendicular to the axis of the main body, the inlet and outlet pipe has at least one radial extension that extends obliquely along the radial direction of the main body. The angle between the radial extension closest to the second port and the first branch pipe is B and satisfies: 15°≤B°≤225°.

[0039] In some embodiments of this utility model, the angle between the tangent of the axis of the end of the inlet / outlet pipe connected to the second port and the axis of the main body is C, and satisfies: 0°≤C°≤135°.

[0040] In some embodiments of this utility model, the main body includes a flow divider located at one end of the main body. The flow divider has a first passage, a second passage, and a third passage. One end of the first passage, one end of the second passage, and one end of the third passage are interconnected. The other end of the first passage is connected to the inlet end of the flow-blocking component. The other end of the second passage is open to form a second port, and the other end of the third passage is open to form a second connecting hole. The resistance of fluid flowing from the second passage to the first passage is a first resistance, and the resistance of fluid flowing from the second passage to the third passage is a second resistance, wherein the second resistance is greater than the first resistance; or, the flow rate of fluid flowing from the second passage to the first passage is a first flow rate, and the flow rate of fluid flowing from the second passage to the third passage is a second flow rate, wherein the first flow rate is greater than the second flow rate.

[0041] In some embodiments of this utility model, the diverter has a diverting cavity, and one end of the first passage, one end of the second passage, and one end of the third passage are all connected to the diverting cavity.

[0042] In some embodiments of this utility model, the axes of the first path, the second path, and the third path extend along a straight line.

[0043] In some embodiments of this utility model, the second passage and the third passage are located on the same side of the splitter, and the first passage and the second passage are located on opposite sides of the splitter; and / or the opening of the second passage and the opening of the third passage face the same side, and the opening of the second passage and the opening of the first passage face opposite sides.

[0044] In some embodiments of this utility model, the axis of the second path is parallel to the axis of the third path, and the axis of the first path does not coincide with the axis of the second path.

[0045] In some embodiments of this utility model, the axis of the first passage is parallel to the axis of the second passage and is located between the axis of the second passage and the axis of the third passage.

[0046] In some embodiments of this utility model, there are multiple third channels, and the multiple third channels are spaced apart along the circumferential direction of the second channel, with the axis of the first channel coinciding with the axis of the second channel.

[0047] In some embodiments of this invention, the axis of the second path is parallel to the axis of the third path.

[0048] In some embodiments of this utility model, the axes of the first passage and the second passage coincide, and the axis of the third passage is perpendicular to the axis of the second passage; or the axes of the first passage and the second passage coincide, and the angle between the axis of the third passage and the axis of the second passage is smaller than the angle between the axis of the third passage and the axis of the first passage.

[0049] In some embodiments of this utility model, the inner diameter of the second passage is D2, the inner diameter of the third passage is D3, and the following conditions are met: D2≥D3; and / or the inner diameter of the first passage is D1, the inner diameter of the third passage is D3, and the following conditions are met: D1>D3; and / or the open end of the second passage is connected to an inlet / outlet pipe, the open end of the third passage is connected to a second branch pipe, and the inner diameter of the inlet / outlet pipe is greater than or equal to the inner diameter of the second branch pipe; and / or the open end of the first passage is connected to a second manifold or connecting pipe, and the inner diameter of the second manifold or the connecting pipe is greater than the inner diameter of the second branch pipe; and / or the open end of the first passage is connected to a second manifold or connecting pipe, the open end of the second passage is connected to an inlet / outlet pipe, and the inner diameter of the second manifold or the connecting pipe is greater than or equal to the inner diameter of the inlet / outlet pipe.

[0050] In some embodiments of this utility model, the open end of the third passage is connected to the right second branch pipe, and the minimum cross-sectional inner diameter of the second branch pipe is D0, and satisfies: D0≤D3.

[0051] In some embodiments of this utility model, the inner diameter of the third passage is D3, and satisfies: D3≥3mm.

[0052] According to some embodiments of this utility model, the flow-blocking component is a one-way valve, a solenoid valve, or a baffle.

[0053] A heat exchanger assembly according to an embodiment of the present invention includes: a heat exchanger body, a flow collector assembly, and the aforementioned flow divider assembly. The heat exchanger body has a plurality of heat exchange tubes forming a plurality of flow paths. The flow collector assembly is disposed on one side of the heat exchanger body and communicates with the plurality of flow paths. The flow collector assembly has a third port. A first connecting hole communicates with at least one end of a flow path away from the flow collector assembly, and a second connecting hole communicates with at least one end of a flow path away from the flow collector assembly.

[0054] According to the embodiments of the present invention, the heat exchanger assembly, by providing a first port, a second port, a first connecting hole, and a second connecting hole on the main body, and by providing a flow-blocking component on the main body, and ensuring that the flow-blocking component only allows refrigerant to flow from the second port to the first port, can automatically open and close or cut off the flow, thereby achieving automatic flow guidance of the refrigerant and changing the flow direction of the refrigerant. When the heat exchanger assembly is used in an air conditioning system, it can automatically switch the different flow paths of the refrigerant within the heat exchanger assembly in different modes of the air conditioning system, thereby improving the heat exchange efficiency of the heat exchanger assembly, improving the cooling or heating performance of the air conditioning system, and improving energy efficiency. Furthermore, no other control structures are required, making the structure simple, easy to implement, and low in cost.

[0055] In some embodiments of this utility model, when the heat exchanger assembly functions as an evaporator, refrigerant flows into the heat exchanger assembly from the second port, and then flows into the heat exchange tube of the heat exchanger assembly from the first and second connecting holes before flowing out of the heat exchanger assembly from the third port. The flow-blocking component is open, and the first port is closed. When the heat exchanger assembly functions as a condenser, refrigerant flows into the heat exchanger assembly from the first port, and then flows into the heat exchange tube of the heat exchanger assembly from the first connecting hole before flowing out of the heat exchanger assembly from the second connecting hole and the second port in sequence. Both the flow-blocking component and the third port are closed.

[0056] In some embodiments of this utility model, the current collection assembly includes a main pipe and branch pipes, the main pipe having a third port; one end of the branch pipe is connected to the main pipe, the inner diameter of the main pipe is greater than or equal to the inner diameter of the branch pipe, there are multiple branch pipes, and the ends of the multiple branch pipes facing away from the main pipe are respectively connected to multiple flow paths.

[0057] In some embodiments of this utility model, the branch pipe is connected to the main pipe through a second tee pipe.

[0058] In some embodiments of this utility model, the current collection assembly further includes a manifold, one end of which is connected to the main pipe and the other end is connected to a plurality of branch pipes.

[0059] In some embodiments of this utility model, the plurality of branch pipes include at least one third branch pipe and at least one fourth branch pipe, the third branch pipe and the fourth branch pipe being arranged at intervals along the length direction of the main pipe, the manifold assembly having a first state and a second state. In the first state, refrigerant enters the main pipe from the third branch pipe and flows out from the fourth branch pipe, and the third port is closed. In the second state, refrigerant enters the main pipe from the third branch pipe and the fourth branch pipe and flows out from the third port.

[0060] In some embodiments of this utility model, on a projection plane perpendicular to the axis of the main pipe, the third branch pipe and the fourth branch pipe are spaced apart or at an angle.

[0061] In some embodiments of this utility model, one end of the main pipe along its length is open to form the third port, and the third port is connected to an extension pipe.

[0062] In some embodiments of this utility model, the extension tube is U-shaped or inverted U-shaped.

[0063] In some embodiments of this utility model, the plurality of heat exchange tubes form at least one first flow path and at least one second flow path, and the plurality of branch tubes include at least one third branch tube and at least one fourth branch tube. The third branch tube is connected to the first flow path, and the fourth branch tube is connected to the second flow path. The first connecting hole is connected to at least one end of the first flow path away from the third branch tube, and the second connecting hole is connected to at least one end of the second flow path away from the fourth branch tube.

[0064] In some embodiments of this utility model, the heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body. Both the first flow path and the second flow path include multiple rows of the heat exchange tubes. The heat exchange tubes of the first flow path connected to the first connecting hole and the heat exchange tubes of the second flow path connected to the second connecting hole are located on opposite sides of the thickness direction of the heat exchanger body or in different rows.

[0065] In some embodiments of this utility model, the heat exchange tubes of the first flow path connected to the first connecting hole are located in a row on the leeward side of the heat exchanger body, and the heat exchange tubes of the second flow path connected to the second connecting hole are located in a row on the windward side of the heat exchanger body.

[0066] In some embodiments of this utility model, the heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body. Both the first flow path and the second flow path include multiple rows of the heat exchange tubes. The heat exchange tubes of the first flow path connected to the third branch pipe and the heat exchange tubes of the second flow path connected to the fourth branch pipe are located on opposite sides of the thickness direction of the heat exchanger body or in different rows.

[0067] In some embodiments of this utility model, the heat exchange tubes of the first flow path connected to the third branch pipe are located in a row on the windward side of the heat exchanger body, and the heat exchange tubes of the second flow path connected to the fourth branch pipe are located in a row on the leeward side of the heat exchanger body.

[0068] In some embodiments of this utility model, the heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body. The first flow path includes a row of windward heat exchange tubes located on the windward side of the heat exchanger body and a row of leeward heat exchange tubes located on the leeward side of the heat exchanger body. When the heat exchanger assembly functions as a condenser and as an evaporator, the refrigerant flowing into the first flow path first flows through the leeward heat exchange tubes and then through the windward heat exchange tubes; and / or, the heat exchange tubes are arranged along the thickness direction of the heat exchanger body. The heat exchanger assembly consists of multiple rows arranged along its thickness direction. The second flow path includes a row of air-facing heat exchange tubes on the air-facing side of the heat exchanger assembly and a row of leeward heat exchange tubes on the leeward side of the heat exchanger assembly. When the heat exchanger assembly functions as an evaporator, the refrigerant flowing into the second flow path first flows through the air-facing heat exchange tubes and then through the leeward heat exchange tubes. When the heat exchanger assembly functions as a condenser, the refrigerant flowing into the second flow path first flows through the leeward heat exchange tubes and then through the air-facing heat exchange tubes.

[0069] In some embodiments of this utility model, the first flow path is located above the second flow path; and / or, the air volume or average wind speed flowing through the first flow path is greater than the air volume or average wind speed flowing through the second flow path.

[0070] In some embodiments of this utility model, the flow collection assembly and the flow splitting assembly are located on the same side of the length direction of the heat exchanger body.

[0071] An air conditioning system according to an embodiment of the present invention includes: a compressor, an indoor heat exchanger, the aforementioned heat exchanger assembly, and a reversing assembly. The compressor has an exhaust port and a return port. One end of the indoor heat exchanger is connected to a second port. The reversing assembly has a first port, a second port, a third port, a fourth port, and a fifth port. The first port is connected to the exhaust port, the third port is connected to the return port, the second port is connected to the other end of the indoor heat exchanger, the fourth port is connected to the third port, and the fifth port is connected to the first port. The reversing assembly has a first switching state and a second switching state. When the reversing assembly is in the first switching state, the first port is connected to the fifth port, the second port is connected to the third port, and the fourth port is closed. When the reversing assembly is in the second switching state, the first port is connected to the second port, the third port is connected to the fourth port, and the fifth port is closed.

[0072] According to an embodiment of the present invention, the air conditioning system, by providing a first port, a second port, a first connecting hole, and a second connecting hole on the main body, and by providing a flow-blocking component on the main body, and ensuring that the flow-blocking component only allows refrigerant to flow from the second port to the first port, can automatically open and close or cut off the flow of the flow-blocking component, thereby achieving automatic flow guidance of the refrigerant and changing the flow direction of the refrigerant. In different modes of the air conditioning system, automatic switching of different flow paths of the refrigerant within the heat exchanger assembly can be achieved, thereby improving the heat exchange efficiency of the heat exchanger assembly, improving the cooling or heating performance of the air conditioning system, and improving energy efficiency. Furthermore, no other control structure is required, making the structure simple, easy to implement, and low in cost.

[0073] An air conditioner according to an embodiment of the present invention includes: the air conditioning system described above.

[0074] According to an embodiment of the present invention, an air conditioner by providing a first port, a second port, a first connecting hole, and a second connecting hole on the main body, and by providing a flow-blocking component on the main body, allowing the flow-blocking component to allow refrigerant to flow only from the second port to the first port, can automatically open and close or cut off the flow of the refrigerant, thereby automatically guiding the refrigerant and changing its flow direction. This allows for automatic switching of different flow paths of the refrigerant within the heat exchanger assembly in different modes of the air conditioning system, improving the heat exchange efficiency of the heat exchanger assembly, enhancing the cooling or heating performance of the air conditioning system, and improving energy efficiency. Furthermore, no other control structures are required, resulting in a simple, easy-to-implement, and low-cost structure.

[0075] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0076] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0077] Figure 1 This is a schematic diagram of the structure of the diversion component according to an embodiment of the present utility model, wherein the first current collector and the second current collector are integral parts;

[0078] Figure 2 This is a schematic diagram of the structure of a current splitter assembly according to another embodiment of the present utility model, wherein the first current collector and the second current collector are separate components;

[0079] Figure 3 This is a schematic diagram of the structure of a current shunt component according to another embodiment of the present invention;

[0080] Figure 4 This is a schematic diagram of the structure of a current splitter assembly according to another embodiment of the present invention;

[0081] Figure 5 This is a partial perspective view of a diversion assembly according to an embodiment of the present utility model, wherein the inlet / outlet pipe and the second branch pipe are shown.

[0082] Figure 6 This is a top view of the diversion component according to Embodiment 1 of the present utility model, wherein the second branch pipe includes a first sub-pipe and a second sub-pipe;

[0083] Figure 7 This is a top view of the diversion component according to Embodiment 2 of the present utility model, wherein the second branch pipe includes a first sub-pipe, a second sub-pipe, and a third sub-pipe;

[0084] Figure 8 This is a perspective view of the diversion component according to Embodiment 3 of the present utility model, wherein the inlet and outlet pipes are arranged on the lower side of the main body.

[0085] Figure 9 This is a top view of the diversion component according to Embodiment 3 of the present utility model, wherein the inlet and outlet pipes are arranged on the lower side of the main body.

[0086] Figure 10 This is a perspective view of the diversion component according to Embodiment 4 of the present utility model, wherein the inlet and outlet pipes are arranged on one side of the main body in the radial direction.

[0087] Figure 11 This is a top view of the diversion assembly according to Embodiment 4 of the present utility model, wherein the inlet and outlet pipes are arranged on one side of the main body in the radial direction.

[0088] Figure 12 This is a schematic diagram of the structure of the shunt component according to an embodiment of the present utility model;

[0089] Figure 13 yes Figure 12 Enlarged view at point M;

[0090] Figure 14 This is a schematic diagram of the flow direction of the splitter, inlet / outlet pipe and second branch pipe according to an embodiment of the present utility model;

[0091] Figure 15 This is a schematic diagram of the structure of a shunt according to another embodiment of the present invention;

[0092] Figure 16 This is a schematic diagram of the structure of a shunt according to another embodiment of the present invention;

[0093] Figure 17 This is a schematic diagram of the structure of a distributor, inlet / outlet pipe and second branch pipe according to another embodiment of the present invention;

[0094] Figure 18 This is a schematic diagram of a shunt assembly according to another embodiment of the present invention, which includes a shunt;

[0095] Figure 19 yes Figure 18 A partial exploded view;

[0096] Figure 20 This is a structural schematic diagram of a flow splitter assembly according to another embodiment of the present invention, which includes an intake pipe and a flow splitter.

[0097] Figure 21 This is a perspective view of the manifold according to an embodiment of the present utility model;

[0098] Figure 22 This is a top view of the manifold according to an embodiment of the present utility model;

[0099] Figure 23 This is a flow path diagram of a heat exchanger assembly according to an embodiment of the present utility model;

[0100] Figure 24 This is a schematic diagram of the structure of a heat exchanger assembly according to an embodiment of the present utility model;

[0101] Figure 25 This is a structural schematic diagram of a heat exchanger assembly according to an embodiment of the present utility model from another perspective;

[0102] Figure 26 This is a schematic diagram of the structure of an air conditioning system according to an embodiment of the present utility model, wherein the air conditioning system is in cooling mode;

[0103] Figure 27 This is a schematic diagram of the structure of an air conditioning system according to an embodiment of the present utility model, wherein the air conditioning system is in heating mode;

[0104] Figure 28 This is a structural schematic diagram of the five-way valve of the reversing component of an air conditioning system according to an embodiment of the present utility model.

[0105] Figure label:

[0106] 100. Distributor components;

[0107] 1. Body; 101. Connecting pipe; 11. First port; 12. Second port; 13. First connecting hole; 14. Second connecting hole; 102. Manifold; 15. First manifold; 151. Manifold body; 152. First tee pipe; 16. Second manifold;

[0108] 2. Flow-blocking components;

[0109] 31. First branch pipe; 32. Second branch pipe; 321. First sub-pipe; 322. Second sub-pipe; 323. Third sub-pipe; 324. First arc-shaped section; 325. Second arc-shaped section; 326. Bend; 33. Inlet pipe; 331. Connecting pipe; 332. Inlet pipe; 34. Inlet / outlet pipe; 341. Radial extension;

[0110] 7. Diverter component; 71. Distributor; 711. Main interface; 712. Distribution hole; 72. Diverter pipe;

[0111] 8. Flow divider; 81. First passage; 82. Second passage; 83. Third passage; 84. Flow divider cavity;

[0112] 200. Heat exchanger assembly;

[0113] 4. Heat exchanger body; 41. Heat exchange tube; 42. First flow path; 43. Second flow path; 44. Leeward side heat exchange tube; 45. Windward side heat exchange tube;

[0114] 5. Current collector assembly; 51. Third port; 52. Main pipe; 53. Branch pipe; 531. Third branch pipe; 532. Fourth branch pipe; 54. Combination pipe; 55. Extension pipe;

[0115] 300. Air conditioning system;

[0116] 61. Compressor; 611. Exhaust port; 612. Return port; 62. Indoor heat exchanger; 63. Reversing assembly; 631. First port; 632. Second port; 633. Third port; 634. Fourth port; 635. Fifth port; 636. Five-way valve; 637. Pilot valve; 64. Throttling device; 601. First valve body; 602. First connecting member; 603. Moving member; 604. Connecting member; 605. Connecting shaft; 606. First partition; 607. Second partition; 608. Connecting part; 609. Stop part; 651. Sixth port; 652. Seventh port; 653. Connecting cavity; 654. Through port. Detailed Implementation

[0117] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0118] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0119] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0120] The shunt assembly 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

[0121] like Figure 1 and Figure 2 As shown, the diversion component 100 according to an embodiment of the present invention includes a main body 1 and a flow-blocking component 2.

[0122] Specifically, such as Figure 1 and Figure 2 As shown, combined with Figure 23 and Figure 25 The flow divider assembly 100 is used in the heat exchanger assembly 200. The body part 1 has a first port 11, a second port 12, a first connecting hole 13 and a second connecting hole 14. The flow blocking member 2 is provided on the body part 1. Along the length direction of the body part 1, the first port 11 and the first connecting hole 13 are located on the same side of the flow blocking member 2, the second port 12 and the second connecting hole 14 are located on the same side of the flow blocking member 2, and the first port 11 and the second port 12 are located on opposite sides of the flow blocking member 2. The flow blocking member 2 only allows the refrigerant to flow from the second port 12 side to the first connecting hole 13 side.

[0123] The main body 1 has a main channel, and the first port 11, the second port 12, the first connecting hole 13, and the second connecting hole 14 are all connected to the main channel. Refrigerant flows within the main channel. In a specific example, such as... Figure 1 and Figure 2 As shown, the first connecting hole 13 and the second connecting hole 14 are both provided on the peripheral wall of the body part 1 and are spaced apart along the length direction of the body part 1. The first port 11 and the second port 12 are respectively provided at both ends of the length direction of the body part 1, or the first port 11 and the second port 12 are both provided on the peripheral wall of the body part 1 and located on both sides of the flow blocking member 2.

[0124] The flow-blocking component 2 is unidirectional. It only opens when the pressure on the side of the flow-blocking component 2 near the second port 12 is greater than the pressure on the side of the flow-blocking component 2 near the first port 11, allowing refrigerant to flow from the second port 12 to the first port 11. When refrigerant enters the body part 1 from the second port 12, the flow-blocking component 2 opens, and some refrigerant flows from the second port 12 to the second connecting hole 14, while some refrigerant flows through the flow-blocking component 2 to the first connecting hole 13. When refrigerant enters the body part 1 from the first port 11, the flow-blocking component 2 closes off, and refrigerant cannot flow from the end of the flow-blocking component 2 near the first port 11 to the end of the flow-blocking component 2 near the second port 12; the refrigerant can only flow from the first port 11 to the first connecting hole 13.

[0125] Furthermore, when the heat exchanger assembly 200 functions as an evaporator, refrigerant flows into the heat exchanger assembly 200 from the second port 12, and then flows into the heat exchange tubes or heat exchange channels of the heat exchanger assembly 200 from the first connecting hole 13 and the second connecting hole 14 before flowing out of the heat exchanger assembly 200. The flow-blocking component 2 is open, and the first port 11 is closed. When the heat exchanger assembly 200 functions as a condenser, refrigerant flows into the heat exchanger assembly 200 from the first port 11, and then flows into the heat exchange tubes or heat exchange channels of the heat exchanger assembly 200 from the first connecting hole 13, and then flows out of the heat exchanger assembly 200 sequentially from the second connecting hole 14 and the second port 12. The flow-blocking component 2 is closed. In this embodiment, the first port 11 is closed by a valve in the air conditioner, for example, by a five-way valve 636.

[0126] For example, when the diversion assembly 100 is used in the heat exchanger assembly 200 and the air conditioning system 300, the heat exchanger assembly 200 includes a heat exchanger body 4 and a manifold assembly 5. The heat exchanger body 4 has a plurality of heat exchange tubes 41, which are refrigerant flow channels. The manifold assembly 5 is located on one side of the heat exchanger body 4 and communicates with the heat exchange tubes 41. A third port 51 is formed on the manifold assembly 5. The diversion assembly 100 is located on the side of the heat exchanger body 4 away from the manifold assembly 5, or the diversion assembly 100 and the manifold assembly 5 are located on the same side of the heat exchanger body 4. The diversion assembly 100 communicates with the heat exchange tubes 41, and the refrigerant is adapted to flow from one of the diversion assembly 100 and the manifold assembly 5 to the other.

[0127] like Figure 26 As shown, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser. The refrigerant cools and condenses within the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not open, and the refrigerant enters the heat exchange tube 41 from the first connecting hole 13. The third port 51 is closed. After being collected by the flow-collecting component 5, the refrigerant re-enters the heat exchange tube 41, then enters the main body 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12. The refrigerant entering the heat exchange tube 41 from the first connecting hole 13 and then re-entering it after being collected by the flow-collecting component 5 further reduces the refrigerant temperature and increases its subcooling, thus forming a subcooling tube design for the condenser and better enhancing the heat exchange efficiency of the heat exchanger assembly 200.

[0128] like Figure 27As shown, when the air conditioning system 300 is in heating mode, the heat exchanger assembly 200 acts as an evaporator. The refrigerant evaporates and absorbs heat in the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the second port 12. At this time, the flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 from the second connecting hole 14. Another part of the refrigerant passes through the flow-blocking component 2 within the body part 1, and then enters the heat exchange tube 41 through the first connecting hole 13. The third port 51 is open, and the refrigerant in the heat exchange tube 41 flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the flow-collecting component 5. Through the cooperation of the flow-dividing component 100 and the heat exchange tube 41, a multi-path heat exchange pattern can be formed, thereby improving the heat exchange efficiency of the heat exchanger assembly 200.

[0129] Furthermore, in heating mode, the refrigerant needs to pass through a subcooling pipe when entering the conventional outdoor heat exchanger, resulting in pressure loss. However, in this application, by setting a flow-diverting assembly 100 with a flow-blocking component 2, the heat exchanger assembly 200 can form a different flow path in heating mode than in cooling mode. In heating mode, the refrigerant does not need to pass through a subcooling pipe when entering the heat exchanger assembly 200, thus avoiding significant pressure loss.

[0130] In the air conditioning system 300, the heat exchanger assembly 200 serves as the outdoor heat exchanger. During cooling and heating modes, the heat exchanger assembly 200 functions as both the condenser and evaporator, respectively. In these modes, the refrigerant undergoes boiling evaporation and cooling condensation processes within the heat exchanger assembly 200. By incorporating a flow-diverting assembly 100 with flow-blocking components 2, given a fixed area and volume of the heat exchanger assembly 200, different flow paths can be created for the refrigerant, resulting in different optimal flow path designs for the heat exchange during the evaporation and condensation processes within the heat exchanger assembly 200.

[0131] This application adds a flow-blocking component 2 to the flow-diverting assembly 100. The flow-blocking component 2 automatically opens, closes, or cuts off the flow based on the pressure difference of the refrigerant on both sides, thereby enabling automatic flow guidance of the refrigerant and changing its flow direction. When the flow-blocking component 2 is used in the heat exchanger assembly 200 and the air conditioning system 300, it can automatically switch the refrigerant flow path within the heat exchanger assembly 200 in different modes of the air conditioning system 300, thereby improving the heat exchange efficiency of the heat exchanger assembly 200, enhancing the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, it eliminates the need for other control structures, is less susceptible to power failures, and features a simple, easy-to-implement, and low-cost structure.

[0132] According to an embodiment of the present invention, the flow-diverting component 100, by providing a first port 11, a second port 12, a first connecting hole 13, and a second connecting hole 14 on the main body 1, and by providing a flow-blocking component 2 on the main body 1, and by ensuring that the flow-blocking component 2 only allows refrigerant to flow from the second port 12 to the first port 11, can automatically open or close or cut off the flow, thereby achieving automatic flow guidance of the refrigerant by the flow-blocking component 2, thus changing the flow direction of the refrigerant. When the flow-diverting component 100 is used in the heat exchanger assembly 200 and the air conditioning system 300, it can automatically switch the different flow paths of the refrigerant in the heat exchanger assembly 200 in different modes of the air conditioning system 300, thereby improving the heat exchange efficiency of the heat exchanger assembly 200, improving the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, no other control structure is required, making the structure simple, easy to implement, and low in cost.

[0133] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, combined with Figure 26 and Figure 27 The number of first connecting holes 13 is multiple. When the heat exchanger assembly 200 functions as an evaporator and when it functions as a condenser, the multiple first connecting holes 13 are used to distribute the refrigerant. This improves the refrigerant flow distribution within the distribution assembly 100, achieving a better flow path distribution effect. When the distribution assembly 100 is applied to the heat exchanger assembly 200, it ensures that the refrigerant can be more evenly distributed into different flow paths of the heat exchanger assembly 200, thereby improving the heat exchange efficiency and energy efficiency of the heat exchanger assembly 200. Furthermore, the multiple first connecting holes 13 are located above or diagonally above the flow-blocking component 2, and the multiple first connecting holes 13 face horizontally, upwards, or diagonally upwards, thus facilitating the distribution of refrigerant to the multiple first connecting holes 13. Furthermore, the flow-blocking component 2 is arranged vertically or at an angle.

[0134] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the main body 1 includes a manifold 102, which includes a first manifold 15 and a second manifold 16. A first port 11 and a first connecting hole 13 are provided on the first manifold 15, and a second port 12 and a second connecting hole 14 are provided on the second manifold 16. The first manifold 15 and the second manifold 16 are integral parts, and a flow-blocking component 2 is provided inside the first manifold 15 or the second manifold 16. Further, the manifold 102 is a flute-shaped pipe, which is vertically or inclined, and the multiple first connecting holes 13 face the horizontal direction, thereby facilitating the distribution of refrigerant through the manifold 102 to the multiple first connecting holes 13.

[0135] The first manifold 15 and the second manifold 16 are integrally machined. During the machining process, the flow-blocking component 2 can be directly fixed inside the first manifold 15 or the second manifold 16 without the need for alignment and connection of multiple pipe sections. This simplifies the assembly process of the flow divider assembly 100, reduces the difficulty of disassembly and assembly of the flow divider assembly 100, improves the assembly efficiency and maintenance efficiency of the flow divider assembly 100, and also reduces potential leakage points, thereby reducing the risk of leakage of the flow divider assembly 100.

[0136] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the main body 1 includes a manifold 102, which includes a first manifold 15 and a second manifold 16. A first port 11 and a first connecting hole 13 are provided on the first manifold 15, and a second port 12 and a second connecting hole 14 are provided on the second manifold 16. The first manifold 15 and the second manifold 16 are separate components, and a flow-blocking component 2 is connected between the first manifold 15 and the second manifold 16.

[0137] The first manifold 15 and the second manifold 16 are manufactured separately. The first manifold 15 and the second manifold 16 are arranged along the length of the flow divider assembly 100 and connected to each other. The flow-blocking component 2 is connected between the first manifold 15 and the second manifold 16. This allows the first manifold 15 and the second manifold 16 to be manufactured separately, reducing manufacturing difficulty and improving production efficiency. When assembling the flow divider assembly 100, the first manifold 15, the flow-blocking component 2, and the second manifold 16 are connected sequentially, facilitating assembly. Furthermore, if the first manifold 15, the flow-blocking component 2, or the second manifold 16 is damaged or needs replacement, only the corresponding component needs to be replaced, rather than the entire flow divider assembly 100, thus reducing maintenance costs.

[0138] In some embodiments of this utility model, the inner diameter of the first manifold 15 is less than or equal to the inner diameter of the second manifold 16. When the refrigerant enters the second manifold 16 from the second port 12, the flow-blocking component 2 is activated, and part of the refrigerant flows from the second port 12 to the second connecting hole 14, while another part of the refrigerant flows from the second manifold 16 through the flow-blocking component 2 into the first manifold 15.

[0139] By increasing the inner diameter of the second manifold 16, the initial flow velocity of the refrigerant entering the distribution assembly 100 can be reduced, decreasing the dynamic head while maintaining a higher static head. As some refrigerant flows upward, the static pressure gradually decreases, allowing the inner diameter of the first manifold 15 to be smaller. This increases the refrigerant flow velocity and dynamic head, enabling more refrigerant to pass through the flow-blocking component 2 and enter the first manifold 15. This improves the refrigerant flow distribution within the distribution assembly 100, achieving a better distribution effect and ensuring more even distribution of refrigerant to the first connecting hole 13 and the second connecting hole 14. When the distribution assembly 100 is applied to the heat exchanger assembly 200, it can improve the heat exchange efficiency and energy efficiency of the heat exchanger assembly 200.

[0140] Furthermore, making the inner diameter of the first manifold 15 equal to the inner diameter of the second manifold 16 can effectively reduce the difficulty of production and processing, which is conducive to improving the production efficiency of the diverter assembly 100 and reducing costs.

[0141] In some embodiments, the body portion 1 is welded to the flow-blocking component 2, which ensures the reliability and stability of the connection between the body portion 1 and the flow-blocking component 2, reduces the impact of loose connection on the flow distribution effect, extends the service life of the flow distribution assembly 100, and ensures the normal operation of the heat exchanger assembly 200 when the flow distribution assembly 100 is applied to the heat exchanger assembly 200. Furthermore, since the welded connection is stable and reliable, the connection cost and maintenance cost between the body portion 1 and the flow-blocking component 2 can be relatively reduced. For example, when the body portion 1 includes a first manifold 15 and a second manifold 16 that are interconnected and separately processed, the flow-blocking component 2 can be welded to the first manifold 15 and the second manifold 16 respectively.

[0142] In some embodiments, the body portion 1 and the flow-blocking component 2 are interference-fitted. The body portion 1 has a main flow channel, and the actual size of the flow-blocking component 2 is slightly larger than the actual size of the main flow channel. During assembly, an external force is applied to achieve a tight connection between the body portion 1 and the flow-blocking component 2. The interference fit between the body portion 1 and the flow-blocking component 2 can generate huge contact pressure through the elastic deformation between the materials, thereby achieving a high-strength connection between the body portion 1 and the flow-blocking component 2. No additional fasteners are required, which simplifies the structure and reduces costs.

[0143] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the end of the first manifold 15 facing away from the flow-blocking component 2 is open to form a first port 11. Setting the first port 11 at one end of the length direction of the first manifold 15 has a simple structure, is easy to process and manufacture, and is conducive to improving production efficiency and reducing costs. Moreover, the first port 11 is located at the end of the length direction of the first manifold 15, which also facilitates installation and assembly, thereby improving assembly efficiency.

[0144] In some embodiments of this utility model, the first port 11 is located on the peripheral wall of the first manifold 15. The refrigerant enters from the first port 11 located on the peripheral wall of the first manifold 15, which can form strong vortices, secondary flows and turbulence in the first manifold 15, making the refrigerant temperature more uniform and helping to improve the convective heat transfer coefficient.

[0145] In some embodiments of this utility model, such as Figure 18 and Figure 19 As shown, the first manifold 15 includes a manifold body 151 and a first tee pipe 152. The first end of the first tee pipe 152 is connected to the flow-blocking component 2, and the second end of the first tee pipe 152 is connected to the manifold body 151. The first port 11 is located at the third end of the first tee pipe 152, and the manifold body 151 is provided with a first connecting hole 13. Thus, this arrangement allows the first port 11 to be positioned at different locations on the body 1, thereby improving versatility. Simultaneously, when the medium enters the body 1 from the first port 11, the flow-blocking component 2 is not conductive, and the medium cannot flow from the end of the flow-blocking component 2 near the first port 11 to the end of the flow-blocking component 2 near the second port 12; the medium can only flow from the first port 11 to the first connecting hole 13.

[0146] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the end of the second manifold 16 facing away from the flow-blocking component 2 is open to form a second port 12. Setting the second port 12 at one end of the second manifold 16 along its length is simple in structure and easy to manufacture, which helps to improve production efficiency and reduce costs. Moreover, the second port 12 is located at the end of the second manifold 16 along its length, which also facilitates installation and assembly, thereby improving assembly efficiency.

[0147] In some embodiments of this utility model, the second port 12 is located on the peripheral wall of the second manifold 16. The refrigerant enters from the second port 12 located on the peripheral wall of the second manifold 16, which can form strong vortices, secondary flows and turbulence within the main body 1, making the refrigerant temperature more uniform and improving the convective heat transfer coefficient.

[0148] In some embodiments of this utility model, such as Figure 1 and Figure 2As shown, the first connecting hole 13 can be one or multiple holes spaced apart along the length of the first manifold 15. Providing a single first connecting hole 13 reduces the processing difficulty of the distribution assembly 100, thereby improving its production efficiency and reducing costs. Providing multiple first connecting holes 13 on the first manifold 15 allows refrigerant entering the first manifold 15 to flow out through these holes. When the distribution assembly 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, the refrigerant enters multiple heat exchange tubes 41 in the heat exchanger assembly 200 through the multiple first connecting holes 13, forming multiple flow channels. This improves the heat exchange efficiency of the heat exchanger assembly 200, enhances the cooling or heating performance of the air conditioning system 300, and increases energy efficiency.

[0149] refer to Figure 1 and Figure 2 As shown, there are two first connecting holes 13. Of course, there can also be three, four, five or six first connecting holes 13, etc.

[0150] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the second connecting hole 14 can be one or multiple holes spaced apart along the length of the second manifold 16. Providing a single second connecting hole 14 reduces the processing difficulty of the distribution assembly 100, thereby improving its production efficiency and reducing costs. Multiple second connecting holes 14 on the second manifold 16 allow refrigerant to flow into or out of the manifold 16. When the distribution assembly 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, the multiple second connecting holes 14 connect with multiple heat exchange tubes 41 in the heat exchanger assembly 200. Refrigerant can enter the multiple heat exchange tubes 41 in the heat exchanger assembly 200 through the multiple second connecting holes 14, or enter the distribution assembly 100 from the heat exchanger assembly 200 through the multiple second connecting holes 14, forming multiple flow channels. This improves the heat exchange efficiency of the heat exchanger assembly 200, enhances the cooling or heating performance of the air conditioning system 300, and improves energy efficiency.

[0151] Specifically, the second connecting hole 14 can be one, two, three, four, five, or six, etc.

[0152] In some embodiments of this utility model, such as Figure 1 and Figure 2As shown, the flow distribution assembly 100 also includes a first branch pipe 31, and at least one first branch pipe 31 is connected to the first connecting hole 13. The first branch pipe 31 is connected to the main body 1 and communicates with the first connecting hole 13. The first branch pipe 31 can be used to indirectly connect the main body 1 to the heat exchange tube 41 of the heat exchanger assembly 200, which can relatively reduce the difficulty of connecting the flow distribution assembly 100 and the heat exchange tube 41, reduce the probability of refrigerant leakage, and ensure the normal operation of the heat exchanger assembly 200.

[0153] refer to Figure 1 and Figure 2 As shown, there are three first branch pipes 31. Furthermore, there are two first connecting holes 13, one of which connects to one first branch pipe 31, and the other connects to two first branch pipes 31. Of course, there can also be one, two, four, five, or six first branch pipes 31, etc., and each first connecting hole 13 can connect to one, two, three, four, five, or six first branch pipes 31, etc.

[0154] It should be noted that the welding connection between the multiple first branch pipes 31 and the main body 1 can ensure the connection strength between the first branch pipes 31 and the main body 1, improve the structural strength of the diversion assembly 100, and ensure the reliability and stability of the diversion assembly 100. Furthermore, during the welding process, the weld metal fills the gap between the main body 1 and the first branch pipes 31, forming a dense connection layer, which can effectively prevent refrigerant leakage.

[0155] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the flow distribution assembly 100 also includes a second branch pipe 32, and at least one second branch pipe 32 is connected to the second connecting hole 14. The second branch pipe 32 is connected to the main body 1 and communicates with the second connecting hole 14. The second branch pipe 32 can be used to indirectly connect the main body 1 to the heat exchange tube 41 of the heat exchanger assembly 200, which can relatively reduce the difficulty of connecting the flow distribution assembly 100 and the heat exchange tube 41, reduce the probability of refrigerant leakage, and ensure the normal operation of the heat exchanger assembly 200.

[0156] Specifically, the second branch pipe 32 can be one, two, three, four, five or six, etc., and each second connecting hole 14 can be connected to one, two, three, four, five or six, etc.

[0157] It should be noted that the welding connection between the multiple second branch pipes 32 and the main body 1 can ensure the connection strength between the second branch pipes 32 and the main body 1, improve the structural strength of the diversion assembly 100, and ensure the reliability and stability of the diversion assembly 100. In addition, during the welding process, the weld metal fills the gap between the main body 1 and the second branch pipes 32, forming a dense connection layer, which can effectively prevent refrigerant leakage.

[0158] In some embodiments of this utility model, the inner diameter of the second branch pipe 32 is less than or equal to the inner diameter of the first branch pipe 31. When the refrigerant enters the second manifold 16 from the second port 12, the flow-blocking component 2 is activated, and part of the refrigerant flows from the second port 12 to the second connecting hole 14, while the other part of the refrigerant flows to the first connecting hole 13 after passing through the flow-blocking component 2.

[0159] Understandably, by making the inner diameter of the second branch pipe 32 smaller than that of the first branch pipe 31, the flow resistance of the refrigerant flowing into the body 1 from the second port 12 will increase. This allows more refrigerant to continue flowing towards the first connecting hole 13 after passing through the flow-blocking component 2, thus meeting the flow requirements of the first connecting hole 13. This better achieves the flow-dividing effect, improves the uneven flow distribution caused by refrigerant dynamic pressure, and further enhances the flow-dividing effect of the flow-dividing component 100. When the flow-dividing component 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, it can improve the heat exchange efficiency of the heat exchanger assembly 200, improve the cooling or heating performance of the air conditioning system 300, and improve energy efficiency.

[0160] In some embodiments of this utility model, the area of ​​the second connecting hole 14 is smaller than the area of ​​the first connecting hole 13. When the refrigerant enters the second manifold 16 from the second port 12, the flow-blocking component 2 is open, and part of the refrigerant flows from the second port 12 to the second connecting hole 14, while the other part of the refrigerant flows to the first connecting hole 13 after passing through the flow-blocking component 2.

[0161] Understandably, by making the area of ​​the second connecting hole 14 smaller than that of the first connecting hole 13, the flow resistance of the refrigerant flowing into the body part 1 from the second port 12 will increase. This allows more refrigerant to continue flowing towards the first connecting hole 13 after passing through the flow-blocking component 2, thus meeting the flow requirements of the first connecting hole 13. This better achieves the flow-dividing effect, improves the problem of uneven flow distribution caused by refrigerant dynamic pressure, and further enhances the flow-dividing effect of the flow-dividing component 100. When the flow-dividing component 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, it can improve the heat exchange efficiency of the heat exchanger assembly 200, improve the cooling or heating performance of the air conditioning system 300, and improve energy efficiency.

[0162] In some embodiments of this invention, the number of second connecting holes 14 is less than the number of first connecting holes 13. Thus, when the diversion assembly 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, it can improve the heat exchange efficiency of the heat exchanger assembly 200, improve the cooling or heating performance of the air conditioning system 300, and improve energy efficiency.

[0163] In some embodiments of this utility model, such as Figure 1 , Figures 5-7 As shown, in the projection plane perpendicular to the axis of the second manifold 16, the first branch pipe 31 and the second branch pipe 32 are spaced apart. It can be understood that, in the projection plane perpendicular to the axis of the main body 1, the first branch pipe 31 and the second branch pipe 32 are spaced apart, which helps to avoid installation interference between the first branch pipe 31 and the second branch pipe 32.

[0164] On the other hand, since the end of the first branch pipe 31 away from the first connecting port 654 and the end of the second branch pipe 32 away from the second connecting hole 14 are both connected to heat exchange tubes 41, and the heat exchange tubes 41 are arranged in multiple rows along the thickness direction of the heat exchanger body 4, and by separating the first branch pipe 31 and the second branch pipe 32 in the projection plane perpendicular to the axis of the second manifold 16, the first branch pipe 31 and the second branch pipe 32 can be connected to heat exchange tubes 41 in different rows, thereby realizing the counter-current arrangement of the refrigerant and the heat exchange airflow. The counter-current arrangement can maintain a large temperature difference between the refrigerant and the heat exchange airflow on the heat exchange tubes 41, thereby maximizing the heat exchange efficiency. This can effectively improve the heat exchange efficiency of the heat exchanger assembly 200. When the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the cooling or heating performance of the air conditioning system 300 and improve energy efficiency.

[0165] For example, refer to Figure 23As shown, the heat exchanger body 4 has a plurality of heat exchange tubes 41, which form at least one first flow path 42 and at least one second flow path 43. The heat exchange tubes 41 on the first flow path 42 near the first branch pipe 31 and the heat exchange tubes 41 on the second flow path 43 near the second branch pipe 32 are located on opposite sides of the thickness direction of the heat exchanger body 4. The two sides of the thickness direction of the heat exchanger body 4 are the first side and the second side, respectively. The heat exchange tubes 41 on the first flow path 42 near the first connecting hole 13 are located on the first side of the thickness direction of the heat exchanger body 4, and the heat exchange tubes 41 on the second flow path 43 near the second connecting hole 14 are located on the second side of the thickness direction of the heat exchanger body 4. The refrigerant in the main body 1 enters the heat exchange tube 41 located on the first side of the first flow path 42 through the first connecting hole 13 and the first branch pipe 31, and flows from the first side to the second side. It then flows into the heat exchange tube 41 located on the first side of the second flow path 43 through components such as the manifold 5. The refrigerant flows from the first side to the second side in the second flow path 43, and flows out of the heat exchanger body 4 through the second branch pipe 32 and the second connecting hole 14 from the heat exchange tube 41 located on the second side of the second flow path 43, so as to enter the main body 1.

[0166] Therefore, it can be seen that along the thickness direction of the heat exchanger body 4, the refrigerant flows from the first side to the second side within the heat exchanger body 4. This facilitates the setting of the position and orientation of the heat exchanger assembly 200 and the control of the flow direction of the airflow exchanging heat with the heat exchanger assembly 200, ensuring that the flow direction of the airflow exchanging heat with the heat exchanger assembly 200 is opposite to the flow direction of the refrigerant within the heat exchanger body 4, thus facilitating a counter-flow arrangement of the refrigerant and the heat exchange airflow. This counter-flow arrangement allows the refrigerant and the heat exchange airflow to maintain a large temperature difference on the heat exchange tube 41, thereby maximizing the heat exchange efficiency. This can effectively improve the heat exchange efficiency of the heat exchanger assembly 200. When the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the cooling or heating performance of the air conditioning system 300 and increase energy efficiency.

[0167] In some embodiments of this invention, the first flow path 42 is located above the second flow path 43; and / or the airflow or average velocity flowing through the first flow path 42 is greater than the airflow or average velocity flowing through the second flow path 43. Thus, when the heat exchanger assembly 200 functions as a condenser, the refrigerant first passes through the first flow path 42 and then through the second flow path 43. Because the refrigerant flowing through the first flow path 42 has a higher temperature and a greater airflow or average velocity, the heat exchange efficiency of the first flow path 42 can be improved, thereby improving the heat exchange efficiency of the heat exchanger assembly 200 when it functions as a condenser, and thus improving energy efficiency.

[0168] In some embodiments of this utility model, such as Figure 1 , Figures 5-7As shown, the end of the first branch pipe 31 facing away from the first connecting port 654 and the end of the second branch pipe 32 facing away from the second connecting hole 14 have the same orientation. It can be understood that both the end of the first branch pipe 31 facing away from the first connecting port 654 and the end of the second branch pipe 32 facing away from the second connecting hole 14 need to be connected to the heat exchange tube 41. Since the inlets (or outlets) of the heat exchange tubes 41 on the same side of the heat exchanger body 4 have the same orientation, the fact that the end of the first branch pipe 31 facing away from the first connecting port 654 and the end of the second branch pipe 32 facing away from the second connecting hole 14 have the same orientation facilitates the installation and connection between the end of the first branch pipe 31 facing away from the first connecting port 654 and the end of the second branch pipe 32 facing away from the second connecting hole 14 and the heat exchange tube 41.

[0169] In some embodiments of this utility model, such as Figures 1-4 As shown, the flow distribution assembly 100 also includes a flow distribution component 7, through which at least one first connecting hole 13 connects to multiple first branch pipes 31. The first branch pipes 31 can be used to indirectly connect the main body 1 to the heat exchange tubes 41 of the heat exchanger assembly 200, which can relatively reduce the difficulty of connecting the flow distribution assembly 100 and the heat exchange tubes 41, reduce the probability of refrigerant leakage, and ensure the normal operation of the heat exchanger assembly 200. The flow distribution component 7 is used to distribute gas when the flow distribution assembly 100 is used as a gas pipe, and to distribute liquid when the flow distribution assembly 100 is used as a liquid pipe, so as to achieve uniform flow distribution among the multiple first branch pipes 31 connected to the flow distribution component 7, thereby ensuring the consistency of operating conditions of the multiple first branch pipes 31 and improving heat exchange stability.

[0170] like Figure 26 As shown, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser. The refrigerant is cooled and condensed inside the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not open. The refrigerant enters the heat exchange tube 41 through the first connecting hole 13 from the first branch pipe 31 directly connected to the first connecting hole 13. The refrigerant also enters the flow-dividing component 7 through the first connecting hole 13 and flows to the multiple first branch pipes 31 connected to the flow-dividing component 7 before entering the heat exchange tube 41. The third port 51 is closed. After being collected by the flow-collecting component 5, the refrigerant re-enters the heat exchange tube 41, then enters the main body 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12. The refrigerant enters the heat exchange tube 41 through the first connecting hole 13, and after being collected by the manifold 5, it re-enters the heat exchange tube 41. This can further reduce the temperature of the refrigerant and increase its subcooling, thereby forming a subcooling tube design for the condenser and better enhancing the heat exchange efficiency of the heat exchanger assembly 200.

[0171] like Figure 27As shown, when the air conditioning system 300 is in heating mode, the heat exchanger assembly 200 acts as an evaporator. The refrigerant evaporates and absorbs heat in the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the second port 12. At this time, the flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 from the second connecting hole 14. Another part of the refrigerant passes through the flow-blocking component 2 within the main body 1, then enters the heat exchange tube 41 through the first connecting hole 13 via the first branch pipe 31 directly connected to the first connecting hole 13. The refrigerant also enters the flow-dividing component 7 through the first connecting hole 13 and flows to multiple first branch pipes 31 connected to the flow-dividing component 7 before entering the heat exchange tube 41. The third port 51 is open, and the refrigerant in the heat exchange tube 41 flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the flow-collecting component 5. Through the cooperation of the flow-dividing component 100 and the heat exchange tube 41, a multi-path heat exchange pattern can be formed, thereby improving the heat exchange efficiency of the heat exchanger assembly 200.

[0172] The flow distribution component 7 of this application only plays a distribution role in the cooling mode and heating mode without converging the flow. This allows the refrigerant to be distributed to each distribution point at the main interface 711 and then directly enter the first branch pipe 31 without secondary mixing between branches. This avoids backflow and interference, ensures the consistency of each branch, and improves the distribution stability and heat exchange efficiency in the cooling and heating modes.

[0173] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the diversion component 7 is a diversion pipe 72. One end of the diversion pipe 72 is connected to the first connecting hole 13, and the other end of the diversion pipe 72 is connected to multiple first branch pipes 31.

[0174] Therefore, the refrigerant from the first connecting hole 13 first enters the distribution pipe 72 and is then distributed to each of the first branch pipes 31. The distribution pipe 72 only undertakes the distribution function and does not undertake the confluence function. After the refrigerant is distributed, there is no secondary mixing between the branches, thereby ensuring the consistency of the flow in each of the first branch pipes 31, reducing mixing losses and additional pressure drops, so that the distribution component 100 can improve the distribution stability and heat exchange efficiency in both cooling and heating conditions.

[0175] Furthermore, such as Figure 1 and Figure 2 As shown, multiple first branch pipes 31 connected to the shunt pipe 72 are located on the same side, so that the shunt pipe 72 concentrates the interfaces on the same side, thereby reducing the number of weld points and sealing surfaces, making the structure more compact and easier to assemble and maintain.

[0176] In some embodiments of this utility model, such as Figure 1 and Figure 2As shown, along the length of the first manifold 15, the distance between the first connecting hole 13, connected to the flow divider 7, and the outlet end of the flow blocking component 2 is 15mm-300mm. It is understandable that if the distance between the first connecting hole 13 and the flow blocking component 2 is too small, the welding / assembly interference between the flow divider 7 and the flow blocking component 2 on the connecting pipe 101 is likely to overlap, leading to a risk of leakage. Conversely, if the distance between the first connecting hole 13 and the flow blocking component 2 is too large, the refrigerant entering the second manifold 16 from the second port 12 will not reach the first connecting hole 13 near the first port 11 after being conducted through the flow blocking component 2, making timely replenishment difficult under low flow conditions. Furthermore, the excessive size of the flow divider assembly 100 increases space requirements and costs.

[0177] Therefore, by limiting the distance between the first connecting hole 13 connected to the diversion component 7 and the flow blocking component 2 to 15mm-500mm, the size of the diversion component 100 is reduced, while effectively avoiding problems such as assembly interference and unstable supply caused by insufficient pressure difference. This further ensures that the diversion component 100 distributes evenly, switches operating conditions smoothly, and improves energy efficiency and reliability.

[0178] It should be noted that, along the length of the first manifold 15, the distance between the first connecting hole 13 connected to the diverting component 7 and the flow blocking component 2 can be 15mm, 20mm, 30mm, 40mm, 50mm, 80mm, 100mm, 150mm, 200mm, 300mm, 400mm or 500mm.

[0179] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, along the length of the second manifold 16, the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is 15mm-100mm. It is understandable that if the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is too small, the welding / assembly interference between the second branch pipe 32 connected to the second connecting hole 14 and the flow-blocking component 2 on the connecting pipe 101 is likely to overlap, leading to a risk of leakage. Conversely, if the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is too large, the refrigerant entering the second manifold 16 from the second port 12 will flow to the flow-blocking component 2 after passing through the second connecting hole 14 to the second branch pipe 32, resulting in insufficient flow and difficulty in timely replenishment under low flow conditions.

[0180] Therefore, the distance between the second connecting hole 14 and the inlet end of the flow blocking component 2 is 15mm-100mm. This reduces the size of the flow splitter 100 while effectively avoiding problems such as assembly interference and unstable supply caused by insufficient pressure difference. This further ensures that the flow splitter 100 distributes evenly, switches operating conditions smoothly, and improves energy efficiency and reliability.

[0181] It should be noted that, along the length of the second manifold 16, the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 can be 15mm, 20mm, 30mm, 40mm, 50mm, 80mm or 100mm.

[0182] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, along the length of the second manifold 16, the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is less than the distance between the first connecting hole 13 connected to the flow-diverting component 7 and the outlet end of the flow-blocking component 2.

[0183] It is understandable that the refrigerant entering the second manifold 16 from the second port 12 passes sequentially through the second connecting hole 14, the inlet end of the flow-blocking component 2, and the first connecting hole 13 connected to the flow-dividing component 7, so that the refrigerant flows sequentially into the second branch pipe 32, the flow-blocking component 2, and the flow-dividing component 7. The distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is less than the distance between the first connecting hole 13 connected to the flow-dividing component 7 and the outlet end of the flow-blocking component 2, which effectively improves the problem of uneven flow distribution caused by refrigerant dynamic pressure and further improves the flow distribution effect of the flow-dividing component 100.

[0184] In some embodiments of this utility model, such as Figure 3 and Figure 4 As shown, combined with Figure 23 and Figure 25 The main body 1 includes a connecting pipe 101 and a distributor 71. A flow-blocking component 2 is disposed on the connecting pipe 101. A second port 12 and a second connecting hole 14 are connected to the connecting pipe 101. At least one of the second port 12 and the second connecting hole 14 is connected to one end of the connecting pipe 101. The distributor 71 has a main interface 711 and a plurality of distribution holes 712. The main interface 711 is connected to the other end of the connecting pipe 101. At least some of the distribution holes 712 are first connecting holes 13.

[0185] Furthermore, the connecting pipe 101 is arranged vertically or inclined, the flow-blocking component 2 is arranged vertically or inclined inside the connecting pipe 101, the distributor 71 forms a flow-dividing cavity, the main interface 711 and a plurality of first connecting holes 13 are respectively located on opposite sides of the distributor 71, the plurality of first connecting holes 13 are all connected to the flow-dividing cavity, the plurality of first connecting holes 13 face upward or obliquely upward, the main interface 711 is connected to the flow-dividing cavity and faces the plurality of first connecting holes 13, so that the refrigerant flowing in from the main interface 711 can be easily diverted to the plurality of first connecting holes 13.

[0186] It is understood that the connecting pipe 101 has a main channel, and the first port 11, the second port 12, the first connecting hole 13, and the second connecting hole 14 are all connected to the main channel. Refrigerant flows within the main channel. The distributor 71 has multiple first connecting holes 13, which connect to multiple first branch pipes 31. The first branch pipes 31 can be used to indirectly connect the connecting pipe 101 to the heat exchange tubes 41 of the heat exchanger assembly 200, thereby reducing the difficulty of connecting the distribution assembly 100 to the heat exchange tubes 41, reducing the probability of refrigerant leakage, and ensuring the normal operation of the heat exchanger assembly 200. Specifically, the distributor 71 is used to distribute gas when the distribution assembly 100 is used as a gas pipe, and to distribute liquid when the distribution assembly 100 is used as a liquid pipe, to achieve uniform flow distribution among the multiple first branch pipes 31 connected to the distributor 71, thereby ensuring consistent operating conditions of the multiple first branch pipes 31 and improving heat exchange stability.

[0187] Therefore, the refrigerant can flow between the main interface 711 of the distributor 71 and the first connecting hole 13 of the main body 1, so that the refrigerant in the main body 1 can be evenly distributed to the first branch pipe 31 connected to the distribution hole 712 via the distributor 71, thereby achieving uniform flow distribution through the distributor 71 and improving the heat exchange stability of the heat exchange component using the flow distribution component 100.

[0188] In addition, the distribution component 7 only undertakes distribution and does not merge. After the refrigerant is distributed to each distribution hole 712 at the main interface 711, it directly enters the corresponding first branch pipe 31. There is no secondary mixing and backflow interference between branches, and the mixing loss and additional pressure drop are reduced. Pressure pulsation and flow-induced noise are suppressed. In both cooling and heating modes, the distribution stability and heat exchange efficiency can be improved.

[0189] In some embodiments of this utility model, such as Figure 3 As shown, there are multiple first connecting holes 13, and each distribution hole 712 is connected to a first branch pipe 31. The first port 11 is located on the connecting pipe 101 between the distributor 71 and the flow blocking component 2.

[0190] Understandably, when refrigerant flows into the distribution assembly 100 from the first port 11, since the flow-blocking component 2 is not conductive, the refrigerant enters the distributor 71 from the main interface 711 through the first connecting hole 13, and flows into the corresponding first branch pipe 31 through the multiple distribution holes 712 of the distributor 71, thereby achieving uniform flow distribution. Simultaneously, when refrigerant flows into the distribution assembly 100 from the second port 12, since the flow-blocking component 2 is conductive, part of the refrigerant flows out from the second connecting hole 14, while the other part of the refrigerant, after passing through the flow-blocking component 2 in the body part 1, enters the distributor 71 from the main interface 711 through the first connecting hole 13, and flows into the corresponding first branch pipe 31 through the multiple distribution holes 712 of the distributor 71, thereby achieving uniform flow distribution.

[0191] Thus, this configuration ensures that the refrigerant, whether entering the distribution assembly 100 from the first port 11 or the second port 12, converges to the first connecting hole 13, then flows into the distributor 71 through the first connecting hole 13 and the main interface 711, and is then distributed at equal pressure to each distribution hole 712. This effectively avoids the formation of bypasses and stagnation chambers that bypass the distributor 71, reduces energy loss, and improves the heat exchange efficiency of the heat exchanger assembly 200 using this distribution assembly 100.

[0192] In some embodiments of this utility model, such as Figure 4 As shown, there are multiple first connecting holes 13 and N distribution holes 712. N-1 distribution holes 712 are connected to a first branch pipe 31, and the remaining distribution hole 712 forms a first port 11.

[0193] Therefore, when the refrigerant flows into the distribution assembly 100 from the first port 11, all the refrigerant flows into the distributor 71. Since the flow-blocking component 2 is not conductive, the refrigerant flows from the distributor 71 through the other distribution holes 712 to the corresponding first branch pipes 31, thereby achieving uniform flow distribution. Furthermore, by integrating the first port 11 onto the distributor 71, the overall compactness of the distribution assembly 100 is improved, which is conducive to miniaturization and reduces the space occupied by the distribution assembly 100 on the heat exchange components. When the refrigerant enters the distribution assembly 100 from the second port 12 and reaches the first connecting hole 13 through the flow-blocking component 2, it is also evenly distributed to the other distribution holes 712 through the main interface 711, which ensures both compact arrangement and uniform supply to each first branch pipe 31, so that the distribution assembly 100 is suitable for miniaturized application scenarios.

[0194] In addition, when the refrigerant flows into the distribution assembly 100 from the first port 11, it forms the first port 11 through the other distribution hole 712. After entering from the first port 11, the refrigerant is directly distributed at the same pressure in the distributor 71 and is evenly distributed by the other distribution holes 712. The flow path of the refrigerant is short and the additional pressure drop is small, which improves the flow efficiency.

[0195] In some embodiments of this utility model, such as Figure 3 and Figure 4 As shown, a first connecting hole 13 is formed by opening one end of the main body 1 on the side of the flow-blocking component 2 away from the second port 12 along its length. Thus, by opening the first connecting hole 13 on the side of the main body 1 on the side of the flow-blocking component 2 away from the second port 12 along its length, it connects with the main interface 711 of the distributor 71, achieving a straight flow path. This allows the refrigerant in the main body 1 to enter the distributor 71 with a smaller additional pressure drop after reaching the first connecting hole 13, and to be distributed at equal pressure among the multiple distribution holes 712, achieving uniform supply to each first branch pipe 31 and stably completing the flow path switching and distribution of the flow distribution assembly 100 in cooling and heating modes.

[0196] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the first connecting hole 13 is provided on the peripheral wall of the main body 1. Thus, the first connecting hole 13 and the diversion pipe 72 are directly connected on the peripheral wall of the main body 1, and the refrigerant enters the diversion pipe 72 directly from the circumferential side wall of the main body 1, which reduces the number of turns in the flow path of the refrigerant, shortens the flow path, and effectively reduces local resistance and energy loss.

[0197] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, there are multiple first connecting holes 13 spaced apart along the length of the main body 1. It can be understood that at least one of the multiple first connecting holes 13 is connected to the branch pipe 72, and the first connecting hole 13 not connected to the branch pipe 72 is connected to the first branch pipe 31, so that the refrigerant in the main body 1 flows through the multiple first connecting holes 13 to the corresponding branch pipe 72 or the first branch pipe 31. This arrangement can improve the versatility of the distribution assembly 100, so that the distribution assembly 100 can be adapted to different application scenarios.

[0198] In one specific embodiment, such as Figure 1 and Figure 2 As shown, there are multiple first connecting holes 13 spaced apart along the length of the main body 1. At least one first connecting hole 13 is connected to multiple first branch pipes 31 through the diversion component 7, and the remaining first connecting holes 13 are connected to the first branch pipes 31. When the refrigerant flows from the second port 12 to the first port 11 and the gas volume is insufficient, the diversion component 7 can ensure that the first branch pipes 31 that are close to the first port 11 and connected to the first connecting holes 13 can also receive refrigerant supply, so that the diversion component 100 can achieve uniform distribution and improve the heat exchange efficiency of the heat exchange component using the diversion component 100.

[0199] In some embodiments of this utility model, such as Figure 3 and Figure 4 As shown, along the length of the connecting pipe 101, the distance between the main interface 711 and the outlet end of the flow-blocking component 2 is 15mm-500mm. It is understandable that if the distance between the first connecting hole 13 and the flow-blocking component 2 is too small, the welding / assembly interference between the distributor 71 and the flow-blocking component 2 on the connecting pipe 101 is likely to overlap, leading to a risk of leakage. Conversely, if the distance between the first connecting hole 13 connected to the distributor 71 and the flow-blocking component 2 is too large, the refrigerant entering the connecting pipe 101 from the second port 12 will not reach the first connecting hole 13 near the first port 11 after being conducted through the flow-blocking component 2, making timely replenishment difficult under low-flow conditions. Furthermore, the excessive size of the diversion component 100 leads to increased space occupation and cost.

[0200] Therefore, by limiting the distance between the first connecting hole 13 connected to the distributor 71 and the flow blocking component 2 to 15mm-500mm, the size of the flow distribution component 100 is reduced, while effectively avoiding problems such as assembly interference and unstable supply caused by insufficient pressure difference. This further ensures that the flow distribution component 100 distributes evenly, switches operating conditions smoothly, and improves energy efficiency and reliability.

[0201] It should be noted that, along the length of the connecting pipe 101, the distance between the first connecting hole 13 connected to the distributor 71 and the flow-blocking component 2 can be 15mm, 20mm, 30mm, 40mm, 50mm, 80mm, 100mm, 150mm, 200mm, 300mm, 400mm or 500mm.

[0202] In some embodiments of this utility model, such as Figure 3 and Figure 4 As shown, along the length of the connecting pipe 101, the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is 15mm-100mm. It is understandable that if the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is too small, the welding / assembly interference between the second branch pipe 32 connected to the second connecting hole 14 and the flow-blocking component 2 on the connecting pipe 101 is likely to overlap, leading to a risk of leakage. Conversely, if the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is too large, the refrigerant entering the connecting pipe 101 from the second port 12 will flow insufficiently through the second connecting hole 14 to the second branch pipe 32 before flowing to the flow-blocking component 2, making timely replenishment difficult under low-flow conditions.

[0203] Therefore, the distance between the second connecting hole 14 and the inlet end of the flow blocking component 2 is 15mm-100mm. This reduces the size of the flow splitter 100 while effectively avoiding problems such as assembly interference and unstable supply caused by insufficient pressure difference. This further ensures that the flow splitter 100 distributes evenly, switches operating conditions smoothly, and improves energy efficiency and reliability.

[0204] It should be noted that, along the length of the connecting pipe 101, the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 can be 15mm, 20mm, 30mm, 40mm, 50mm, 80mm or 100mm.

[0205] In some embodiments of this utility model, such as Figure 3 and Figure 4 As shown, along the length of the connecting pipe 101, the distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is less than the distance between the main interface 711 and the outlet end of the flow-blocking component 2.

[0206] It is understandable that the refrigerant entering the connecting pipe 101 from the second port 12 passes sequentially through the second connecting hole 14, the inlet end of the flow-blocking component 2, and the main interface 711, so that the refrigerant flows sequentially into the second branch pipe 32, the flow-blocking component 2, and the distributor 71. The distance between the second connecting hole 14 and the inlet end of the flow-blocking component 2 is less than the distance between the main interface 711 and the outlet end of the flow-blocking component 2, which effectively improves the problem of uneven flow distribution caused by the dynamic pressure of the refrigerant and further improves the flow distribution effect of the flow distribution component 100.

[0207] In some embodiments of this utility model, such as Figure 4 As shown, the intake pipe 33 includes a connecting pipe 331 and an inlet pipe 332. The connecting pipe 331 is connected in series with the connecting pipe 101, and one end of the inlet pipe 332 is connected to and communicates with the peripheral wall of the connecting pipe 331. Therefore, by connecting the connecting pipe 331 in series with the connecting pipe 101, direct openings in the thin-walled section of the connecting pipe 101 are avoided, improving structural strength and sealing reliability. Furthermore, the connecting pipe 331, as a transition section, straightens and buffers the laterally entering refrigerant, reducing vortices and impacts before entering the connecting pipe 101, and lowering additional pressure drop and flow-induced noise.

[0208] In some embodiments of this utility model, such as Figure 1 As shown, at least one second branch pipe 32 is connected to the second connecting hole 14, and the second branch pipe 32 has a bend 326. The bend 326 in the second branch pipe 32 increases the resistance to refrigerant entering the second branch pipe 32, allowing more refrigerant to continue flowing towards the first connecting hole 13 after passing through the flow-blocking component 2, thus meeting the flow rate requirement of the first connecting hole 13. This better achieves the flow-dividing effect, improves the uneven flow distribution caused by refrigerant dynamic pressure, and enhances the flow-dividing effect of the flow-dividing assembly 100. When the flow-dividing assembly 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, it can improve the heat exchange efficiency of the heat exchanger assembly 200, improve the cooling or heating performance of the air conditioning system 300, and improve energy efficiency.

[0209] In some embodiments of this utility model, such as Figure 1 , Figures 5-7 As shown, the second branch pipe 32 has multiple sub-pipes connected in sequence, with adjacent sub-pipes forming a bend 326 at an angle to each other. It should be noted that the second branch pipe 32 can be formed by bending into multiple sub-pipes, or by welding multiple independent sub-pipes in sequence.

[0210] The two adjacent sub-pipes form a bend 326 at an angle, which increases the resistance to the refrigerant entering the second branch pipe 32. This allows more refrigerant to continue flowing towards the first connecting hole 13 after passing through the flow-blocking component 2, thus meeting the flow requirements of the first connecting hole 13. This better achieves the flow-dividing effect, improves the uneven flow distribution caused by refrigerant dynamic pressure, and enhances the flow-dividing effect of the flow-dividing component 100. When the flow-dividing component 100 is applied to the heat exchanger assembly 200 and the air conditioning system 300, it can improve the heat exchange efficiency of the heat exchanger assembly 200, improve the cooling or heating performance of the air conditioning system 300, and improve energy efficiency.

[0211] For example in Figure 5 and Figure 7 In the example shown, the second branch pipe 32 has three sub-pipes. Figure 6 In the example shown, the second branch pipe 32 has two sub-pipes, but the present invention is not limited to this. The second branch pipe 32 may also have more sub-pipes, such as 4, 5, 6 or 7 sub-pipes.

[0212] In some embodiments of this utility model, such as Figure 1 , Figures 5-7 As shown, the multiple sub-pipes include a first sub-pipe 321 and a second sub-pipe 322 connected in sequence. One end of the first sub-pipe 321 is connected to the second connecting hole 14, and the first sub-pipe 321 and the second sub-pipe 322 are perpendicular. It can be understood that when the first sub-pipe 321 and the second sub-pipe 322 are perpendicular, on the one hand, the resistance of the bend 326 between the first sub-pipe 321 and the second sub-pipe 322 can be sufficiently large, thereby further improving the problem of uneven flow distribution caused by refrigerant dynamic pressure and improving the flow distribution effect of the flow distribution assembly 100. On the other hand, it can prevent the bend 326 between the first sub-pipe 321 and the second sub-pipe 322 from being too large and breaking.

[0213] In some embodiments of this utility model, such as Figure 1 , Figures 5-7 As shown, a first arc-shaped section 324 is provided between the first sub-pipe 321 and the second sub-pipe 322. It is understood that the arc-shaped design helps maintain uniform and stable airflow, reducing turbulence and eddies caused by sudden changes in direction, and improving the efficiency of the air conditioning system 300. The airflow is smoother as it passes through the first arc-shaped section 324, which helps reduce noise caused by airflow turbulence. Furthermore, the first arc-shaped section 324 reduces the impact and wear of the refrigerant on the inner wall of the pipe, extending the service life of the inlet and outlet pipes 34. The first arc-shaped section 324 makes the installation of the first sub-pipe 321 and the second sub-pipe 322 more flexible, making it easier to adapt to space constraints and layout requirements. The first arc-shaped section 324 helps prevent the accumulation of dust and debris inside the pipe, reducing maintenance problems caused by blockages, and also helps reduce damage to system components caused by impacts and vibrations.

[0214] In some embodiments of this utility model, such as Figure 1 and Figure 5 As shown, the multiple sub-tubes also include a third sub-tube 323. One end of the third sub-tube 323 is connected to the end of the second sub-tube 322 that is away from the first sub-tube 321. The third sub-tube 323 is perpendicular to the second sub-tube 322. The first sub-tube 321 and the third sub-tube 323 are located on opposite sides of the second sub-tube 322.

[0215] Understandably, by adding the third sub-pipe 323, the resistance to refrigerant flow to the second branch pipe 32 is further increased, thereby further improving the problem of uneven flow distribution caused by refrigerant dynamic pressure, improving the flow distribution effect of the flow distribution assembly 100, and improving the efficiency of the heat exchanger assembly 200. At the same time, since the first sub-pipe 321 and the third sub-pipe 323 are located on opposite sides of the second sub-pipe 322, installation interference between the first sub-pipe 321 and the third sub-pipe 323 can be avoided.

[0216] For example in Figure 1 and Figure 5 In the example shown, the first sub-pipe 321 and the third sub-pipe 323 are respectively located on both sides of the length of the second sub-pipe 322, and on opposite sides of the radial direction of the second sub-pipe 322, thus forming a Z-shaped structure for the second branch pipe 32. Figure 1 and Figure 5 In the example shown, the second sub-tube 322 extends along the axis of the body portion 1, but the present invention is not limited thereto, and the second sub-tube 322 may also extend along the radial direction of the body portion 1.

[0217] In some embodiments of this utility model, such as Figure 7 As shown, the multiple sub-tubes also include a third sub-tube 323. One end of the third sub-tube 323 is connected to the end of the second sub-tube 322 that is away from the first sub-tube 321. The third sub-tube 323 is perpendicular to the second sub-tube 322. The first sub-tube 321 and the third sub-tube 323 are located on the same side of the second sub-tube 322.

[0218] Understandably, by adding the third sub-pipe 323, the resistance to refrigerant flow to the second branch pipe 32 is further increased, thereby further improving the problem of uneven flow distribution caused by refrigerant dynamic pressure, improving the flow distribution effect of the flow distribution assembly 100, and improving the efficiency of the heat exchanger assembly 200. At the same time, since the first sub-pipe 321 and the third sub-pipe 323 are located on the same side of the second sub-pipe 322, they can share the space on the same side of the second sub-pipe 322 for installation, making the structure more compact and reducing the volume of the heat exchanger assembly 200.

[0219] For example in Figure 7In the example shown, the first sub-pipe 321 and the third sub-pipe 323 are respectively located on both sides of the second sub-pipe 322 along its length and on the same side of the second sub-pipe 322 in its radial direction, thus forming a U-shaped structure for the second branch pipe 32. Figure 7 In the example shown, the second sub-tube 322 extends in the radial direction of the body portion 1, but the present invention is not limited thereto, and the second sub-tube 322 may also extend in the axial direction of the body portion 1.

[0220] In some embodiments of this utility model, such as Figure 5 and Figure 7 As shown, a second arc-shaped section 325 is provided between the second sub-pipe 322 and the third sub-pipe 323. Understandably, the arc design helps maintain uniform and stable airflow, reducing turbulence and eddies caused by sudden changes in direction, and improving the efficiency of the air conditioning system 300. The airflow is smoother as it passes through the second arc-shaped section 325, which helps reduce noise caused by airflow turbulence. Furthermore, the second arc-shaped section 325 reduces the impact and wear of the refrigerant on the inner wall of the pipes, extending the service life of the inlet and outlet pipes 34. The second arc-shaped section 325 makes the installation of the second sub-pipe 322 and the third sub-pipe 323 more flexible, allowing for easier adaptation to space constraints and layout requirements. The second arc-shaped section 325 helps prevent the accumulation of dust and debris inside the pipes, reducing maintenance problems caused by blockages, and also helps reduce damage to system components caused by impacts and vibrations.

[0221] In some embodiments of this utility model, such as Figure 1 , Figures 5-7 As shown, the sub-tube directly connected to the second connecting hole 14 among the multiple sub-tubes is the first sub-tube 321. In the projection plane perpendicular to the axis of the main body 1, the angle between the first sub-tube 321 and at least one first branch tube 31 is A, and satisfies: 0°<A°≤180°. For example, A° can be 0°, 50°, 90° or 180°, etc.

[0222] It should be noted that there are multiple first branch pipes 31, and at least one of the multiple first branch pipes 31 extends in a straight line. The angle A° between the first sub-pipe 321 and at least one first branch pipe 31 refers to the angle A° between the first sub-pipe 321 and the straight-extending first branch pipe 31.

[0223] Since 0°≤A°≤180°, the end of the first branch pipe 31 facing away from the first connecting port 654 and the end of the second branch pipe 32 facing away from the second connecting hole 14 have the same orientation. When A° is greater than 180°, the end of the second branch pipe 32 facing away from the second connecting hole 14 will be bent too much, which may cause breakage and other problems. Therefore, 0°≤A°≤180° can avoid breakage caused by excessive bending angle between multiple sub-pipes.

[0224] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the first port 11 is formed by opening one end of the main body 1 on the side of the flow-blocking component 2 away from the second port 12 along its length. Setting the first port 11 at one end of the main body 1 along its length is simple in structure, convenient in processing and manufacturing, which is conducive to improving production and processing efficiency and reducing costs. Moreover, the first port 11 is located at the end of the main body 1 along its length, which is also convenient for installation and assembly, thereby improving assembly efficiency.

[0225] In some embodiments of this invention, the first port 11 is located on the peripheral wall of the main body 1. The refrigerant enters from the first port 11 located on the peripheral wall of the main body 1, which can form strong vortices, secondary flows and turbulence within the main body 1, making the refrigerant temperature more uniform and improving the convective heat transfer coefficient.

[0226] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the flow distribution assembly 100 also includes an intake pipe 33, one end of which is connected to the first port 11. The intake pipe 33 is connected to the main body 1 and communicates with the first port 11. The arrangement of the intake pipe 33 facilitates indirect connection between the main body 1 and components such as the four-way valve in the air conditioning system 300, which can relatively reduce the difficulty of connecting the flow distribution assembly 100 with other components, help reduce the probability of refrigerant leakage, and ensure the normal operation of the air conditioning system 300.

[0227] For example, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser. Refrigerant flows into the heat exchanger assembly 200 from the inlet pipe 33. At this time, the flow-blocking component 2 is not open, and the refrigerant enters the heat exchange tube 41 from the first connecting hole 13. The third port 51 is closed. After being collected by the flow-collecting component 5, the refrigerant re-enters the heat exchange tube 41, then enters the body part 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12.

[0228] When the air conditioning system 300 is in heating mode, the heat exchanger assembly 200 acts as an evaporator. Refrigerant flows into the heat exchanger assembly 200 from the second port 12. The flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 from the second connecting hole 14. The other part of the refrigerant passes through the flow-blocking component 2 in the body part 1, and then enters the heat exchange tube 41 through the first connecting hole 13. The third port 51 is open, and the refrigerant in the heat exchange tube 41 flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the flow-collecting component 5. At this time, the intake pipe 33 is set to an open circuit state and has a liquid storage function. Part of the liquid refrigerant in the body part 1 is stored in the intake pipe 33 and does not participate in the circulation of the air conditioning system 300, thus regulating the refrigerant flow rate in the air conditioning system 300. The length and diameter of the intake pipe 33 can be adjusted according to the specific operating requirements of the air conditioning system 300, thereby regulating the refrigerant flow rate in the air conditioning system 300 according to specific conditions.

[0229] It should be noted that the intake pipe 33 is welded to the main body 1, which can ensure the connection strength between the intake pipe 33 and the main body 1, improve the structural strength of the diversion assembly 100, and ensure the reliability and stability of the diversion assembly 100. In addition, during the welding process, the weld metal fills the gap between the main body 1 and the intake pipe 33, forming a dense connection layer, which can effectively prevent refrigerant leakage.

[0230] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the intake pipe 33 is a U-shaped pipe, a V-shaped pipe, or an inverted U-shaped pipe. When the refrigerant enters through the intake pipe 33, the U-shaped, V-shaped, or inverted U-shaped intake pipe 33 can accelerate the refrigerant under the action of centrifugal force, thereby increasing the refrigerant flow power within the body 1 and preventing the refrigerant from accumulating at the intake pipe 33. This can improve the refrigerant flow distribution within the distribution assembly 100. When the distribution assembly 100 is applied to the heat exchanger assembly 200, it can improve the heat exchange efficiency of the heat exchanger assembly 200 and increase energy efficiency.

[0231] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, a second port 12 is formed by opening one end of the main body 1 along the length direction on the side of the flow-blocking component 2 opposite to the first port 11. Providing a second port 12 at one end of the main body 1 along the length direction results in a simple structure, convenient manufacturing, improved production efficiency, and reduced costs. Furthermore, the location of the second port 12 at the end of the main body 1 along the length direction facilitates installation and assembly, thereby improving assembly efficiency.

[0232] In some embodiments of this invention, the second port 12 is located on the peripheral wall of the main body 1. The refrigerant enters through the second port 12 located on the peripheral wall of the main body 1, which can form strong vortices, secondary flows, and turbulence within the main body 1, making the refrigerant temperature more uniform and thus improving the convective heat transfer coefficient.

[0233] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the flow distribution assembly 100 also includes an inlet / outlet pipe 34, one end of which is connected to the second port 12. The inlet / outlet pipe 34 is connected to the main body 1 and communicates with the second port 12. The arrangement of the inlet / outlet pipe 34 facilitates indirect connection between the main body 1 and components such as throttling devices in the air conditioning system 300, which can relatively reduce the difficulty of connecting the flow distribution assembly 100 with other components, help reduce the probability of refrigerant leakage, and ensure the normal operation of the air conditioning system 300.

[0234] For example, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser. The refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not open, and the refrigerant enters the heat exchange tube 41 from the first connecting hole 13. The third port 51 is closed. After being collected by the flow-collecting component 5, the refrigerant re-enters the heat exchange tube 41, then enters the body part 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the inlet and outlet pipes 34.

[0235] When the air conditioning system 300 is in heating mode, the heat exchanger assembly 200 acts as an evaporator. Refrigerant flows into the heat exchanger assembly 200 from the inlet and outlet pipes 34. The flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 from the second connecting hole 14. Another part of the refrigerant passes through the flow-blocking component 2 in the body part 1 and then enters the heat exchange tube 41 through the first connecting hole 13. The third port 51 is open, and the refrigerant in the heat exchange tube 41 flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the flow-collecting component 5.

[0236] It should be noted that the welding connection between the inlet / outlet pipe 34 and the main body 1 can ensure the connection strength between the inlet / outlet pipe 34 and the main body 1, improve the structural strength of the diversion assembly 100, and ensure the reliability and stability of the diversion assembly 100. Furthermore, during the welding process, the weld metal fills the gap between the main body 1 and the inlet / outlet pipe 34, forming a dense connection layer, which can effectively prevent refrigerant leakage.

[0237] In some embodiments of this utility model, such as Figure 1 and Figure 2As shown, the inlet and outlet pipes 34 are U-shaped, V-shaped, or inverted U-shaped. When the refrigerant enters through the inlet and outlet pipes 34, the U-shaped, V-shaped, or inverted U-shaped inlet and outlet pipes 34 can accelerate the refrigerant under the action of centrifugal force, thereby increasing the refrigerant flow dynamics within the body 1 and preventing refrigerant accumulation at the inlet and outlet pipes 34. This can improve the refrigerant flow distribution within the flow distribution assembly 100. When the flow distribution assembly 100 is applied to the heat exchanger assembly 200, it can improve the heat exchange efficiency of the heat exchanger assembly 200 and increase energy efficiency.

[0238] In some embodiments of this utility model, such as Figure 9 and Figure 11 As shown, a first branch pipe 31 is connected to the first connecting hole 13. In the projection plane perpendicular to the axis of the main body 1, the inlet and outlet pipe 34 has at least one radial extension 341 that extends obliquely in the radial direction of the main body 1. The angle between the radial extension 341 closest to the second port 12 and the first branch pipe 31 is B and satisfies: 15°≤B°≤225°.

[0239] It is understandable that by having the radial extension 341 closest to the second port 12 and the first branch pipe 31 at an angle of B that satisfies: 15°≤B°≤225°, there is sufficient spacing between the first branch pipe 31 and the inlet / outlet pipe 34 in the circumferential direction of the main body 1, thereby avoiding installation interference between the first branch pipe 31 and the inlet / outlet pipe 34.

[0240] Furthermore, such as Figure 9 and Figure 11 As shown, the inlet / outlet pipe 34 extends in a direction away from the first branch pipe 31, thereby further avoiding installation interference between the inlet / outlet pipe 34 and the first branch pipe 31.

[0241] In some embodiments of this utility model, such as Figure 8 and Figure 10 As shown, the angle between the tangent of the axis of the inlet / outlet pipe 34 and the second port 12 and the axis of the main body 1 is C, and satisfies: 0°≤C°≤135°. For example, C° can be 0°, 40°, 50°, or 135°. It should be noted that the second port 12 can be located on the peripheral wall of the main body 1 or on the end face of the main body 1 along the axial direction, thus meeting different connection requirements. The 0°≤C°≤135° setting facilitates the installation of the inlet / outlet pipe 34.

[0242] In some embodiments of this utility model, such as Figure 12 and Figure 13As shown, the main body 1 includes a diverter 8 located at one end of the main body 1. The diverter 8 has a first passage 81, a second passage 82 and a third passage 83. One end of the first passage 81, one end of the second passage 82 and one end of the third passage 83 are connected to each other. The other end of the first passage 81 is connected to the inlet end of the flow-blocking component 2. The other end of the second passage 82 is open to form a second port 12, and the other end of the third passage 83 is open to form a second connecting hole 14.

[0243] It is understood that the main body 1 has a main channel, and the first port 11, the second port 12, the first connecting hole 13, and the second connecting hole 14 are all connected to the main channel. A refrigerant flows within the main channel; specifically, the refrigerant can be a coolant.

[0244] In some embodiments, the splitter 8 includes a splitter body, in which a first passage 81, a second passage 82 and a third passage 83 are formed. One end of the first passage 81, one end of the second passage 82 and one end of the third passage 83 are interconnected, and the other ends of the first passage 81, the second passage 82 and the third passage 83 are spaced apart or isolated from each other.

[0245] In other embodiments, the distributor 8 includes a distributor body and a refrigerant pipe at least partially inserted into the distributor body. The refrigerant pipe and the distributor body together form a first passage 81, a second passage 82, and a third passage 83, such that one end of the first passage 81, one end of the second passage 82, and one end of the third passage 83 are interconnected, and the other ends of the first passage 81, the second passage 82, and the third passage 83 are spaced apart or isolated from each other. The refrigerant pipe can be any one or more of the following: a piping, a manifold, a heat transfer pipe, an extension pipe 34, a second branch pipe 32, a second manifold 16, and a connecting pipe 101.

[0246] The flow-blocking component 2 is disposed on the main body 1 or in the first passage 81. Along the length direction of the main body 1, the first port 11 and the first connecting hole 13 are located on the side of the flow-blocking component 2 away from the second passage 82. The flow-blocking component 2 only allows the refrigerant to flow from the end of the first passage 81 away from the first port 11 to the side of the first port 11.

[0247] Understandably, the flow-blocking component 2 is unidirectional. It only opens when the pressure on the side of the flow-blocking component 2 closest to the second port 12 is greater than the pressure on the side closest to the first port 11, allowing refrigerant to flow from the second port 12 to the first port 11. Specifically, when refrigerant enters the body 1 from the second port 12, the flow-blocking component 2 opens, allowing some refrigerant to flow from the second port 12 to the second connecting hole 14, and some refrigerant to flow through the flow-blocking component 2 to the first connecting hole 13. When refrigerant enters the body 1 from the first port 11, the flow-blocking component 2 closes off, preventing refrigerant from flowing from the end of the flow-blocking component 2 closest to the first port 11 to the end closest to the second port 12; the refrigerant can only flow from the first port 11 to the first connecting hole 13.

[0248] The resistance to the fluid flowing from the second passage 82 to the first passage 81 is the first resistance, and the resistance to the fluid flowing from the second passage 82 to the third passage 83 is the second resistance. The second resistance is greater than the first resistance.

[0249] Therefore, when the refrigerant enters the distributor 8 through the second port 12, the refrigerant first enters the distributor cavity 84, which is interconnected with the first passage 81, the second passage 82 and the third passage 83. Since the second resistance is greater than the first resistance, most of the refrigerant enters the main body 1 through the second passage 82 and along the first passage 81, and flows to the first connecting hole 13 under the unidirectional conduction of the flow-blocking component 2, while the remaining small part of the refrigerant flows to the second connecting hole 14 through the second passage 82 and along the third passage 83.

[0250] Alternatively, the flow rate of fluid from the second passage 82 to the first passage 81 is the first flow rate, and the flow rate of fluid from the second passage 82 to the third passage 83 is the second flow rate, where the first flow rate is greater than the second flow rate. Therefore, when the medium enters the distributor 8 through the second port 12, the medium first enters the distribution cavity 84, which connects the first passage 81, the second passage 82, and the third passage 83. Because the second resistance is greater than the first resistance, most of the medium flows through the second passage 82 and along the first passage 81 into the main body 1, and under the unidirectional guidance of the flow-blocking component 2, flows towards the first connecting hole 13. The remaining small portion of the medium flows through the second passage 82 and along the third passage 83 towards the second connecting hole 14.

[0251] Therefore, the resistance of the fluid flowing from the second passage 82 to the first passage 81 is the first resistance, and the resistance of the fluid flowing from the second passage 82 to the third passage 83 is the second resistance. The second resistance is greater than the first resistance, so that most of the refrigerant entering the distributor 8 from the second passage 82 flows into the first connecting hole 13 through the first passage 81, and a small part of the refrigerant flows into the second connecting hole 14 through the third passage 83. This achieves that the refrigerant entering from the second port 12 is preferentially guided to the main body 1 and participates in heat exchange through the first connecting hole 13, ensuring a stable supply to the branch with the first connecting hole 13. This makes the flow path switching of the distributor 100 in the two modes of cooling / heating more stable, and the heat exchange efficiency and system energy efficiency are higher.

[0252] For example, when the diversion assembly 100 is used in the heat exchanger assembly 200 and the air conditioning system 300, the heat exchanger assembly 200 includes a heat exchanger body 4 and a manifold assembly 5. The heat exchanger body 4 has a plurality of heat exchange tubes 41, which are refrigerant flow channels. The manifold assembly 5 is located on one side of the heat exchanger body 4 and communicates with the heat exchange tubes 41. A third port 51 is formed on the manifold assembly 5. The diversion assembly 100 is located on the side of the heat exchanger body 4 away from the manifold assembly 5, or the diversion assembly 100 and the manifold assembly 5 are located on the same side of the heat exchanger body 4. The diversion assembly 100 communicates with the heat exchange tubes 41, and the refrigerant is adapted to flow from one of the diversion assembly 100 and the manifold assembly 5 to the other.

[0253] like Figure 26 As shown, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser. The refrigerant cools and condenses within the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not open, and the refrigerant enters the heat exchange tube 41 from the first connecting hole 13. The third port 51 is closed. After being collected by the flow-collecting component 5, the refrigerant re-enters the heat exchange tube 41, then enters the main body 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12. The refrigerant entering the heat exchange tube 41 from the first connecting hole 13 and then re-entering it after being collected by the flow-collecting component 5 further reduces the refrigerant temperature and increases its subcooling, thus forming a subcooling tube design for the condenser and better enhancing the heat exchange efficiency of the heat exchanger assembly 200.

[0254] like Figure 27As shown, when the air conditioning system 300 is in heating mode, the heat exchanger assembly 200 acts as an evaporator. The refrigerant evaporates and absorbs heat in the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the second port 12 and first flows into the distributor 8. At this time, the flow-blocking component 2 is open. The resistance of the fluid flowing from the second passage 82 to the first passage 81 is the first resistance, and the resistance of the fluid flowing from the second passage 82 to the third passage 83 is the second resistance. The second resistance is greater than the first resistance, so that most of the refrigerant entering the distributor 8 from the second passage 82 flows into the body part 1 through the first passage 81 and into the first connecting hole 13 through the flow-blocking component 2. Then, it enters the heat exchange tube 41 through the first connecting hole 13. A small part of the refrigerant flows into the second connecting hole 14 through the third passage 83 and then into the heat exchange tube 41 through the first connecting hole 13. The third port 51 is open, and the refrigerant in the heat exchange tube 41 flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the collector component 5. By combining the flow splitter 100 with the heat exchange tube 41, a multi-flow heat exchange pattern can be formed, thereby improving the heat exchange efficiency of the heat exchanger assembly 200.

[0255] Therefore, most of the refrigerant preferentially enters the first connecting hole 13 through the first passage 81, ensuring a stable and continuous supply to the evaporation circuit on one side of the main body 1. A small portion of the refrigerant enters the second connecting hole 14 through the third passage 83, forming a supply branch parallel to the first connecting hole 13, reducing the risk of "gas / liquid starvation". At the same time, by guiding the proportion of "large flow through the first passage 81 and small flow through the third passage 83", the pressure pulsation in the distributor 8 and the impact on the flow-blocking component 2 can be weakened, reducing bypass short circuits and secondary mixing, stabilizing the flow and phase distribution on the evaporation side, thereby improving the average evaporation temperature and heat exchange utilization, reducing additional pressure drop and flow-induced noise, and improving the heat exchange efficiency and system energy efficiency under heating conditions.

[0256] In some embodiments of this utility model, such as Figures 12-14 As shown, the diverter 8 has a diverter cavity 84, with one end of the first passage 81, one end of the second passage 82, and one end of the third passage 83 all connected to the diverter cavity 84. It can be understood that since the other end of the first passage 81 is connected to the main body 1, the other end of the second passage 82 is open to form a second port 12, and the other end of the third passage 83 is open to form a second connecting hole 14. The diverter cavity 84 enables the connection of the first passage 81, the second passage 82, and the third passage 83, thereby enabling the connection of the main body 1, the second port 12, and the second connecting hole 14.

[0257] Meanwhile, the diversion cavity 84 serves as a common cavity for the first passage 81, the second passage 82, and the third passage 83. The refrigerant entering through the second port 12 is first stabilized and rectified in the diversion cavity 84, and then enters the main body 1 through the first passage 81 according to the predetermined resistance matching relationship. Under the unidirectional conduction of the flow-blocking component 2, it flows to the first connecting hole 13. A small amount of refrigerant enters the second connecting hole 14 through the third passage 83 to form a replenishment branch.

[0258] In some embodiments of this utility model, such as Figure 14 and Figure 15 As shown, the axes of the first passage 81, the second passage 82, and the third passage 83 extend in a straight line. This arrangement allows the refrigerant, after entering the distributor 8 from the second port 12, to exit along the first passage 81 and the third passage 83 with fewer bends and lower local resistance, reducing separation and eddies within the distributor 8, thereby lowering additional pressure drop and noise. Simultaneously, the straight-line extension of the axes of the first passage 81, the second passage 82, and the third passage 83 allows for a more compact arrangement of the distributor 8, improves welding and sealing reliability, and reduces manufacturing and assembly difficulties.

[0259] In some embodiments of this utility model, such as Figure 14 and Figure 15 As shown, the second passage 82 and the third passage 83 are located on the same side of the distributor 8, while the first passage 81 and the second passage 82 are located on opposite sides of the distributor 8. Therefore, through the positional relationship of the first passage 81, the second passage 82, and the third passage 83, the resistance to fluid flowing from the second passage 82 to the first passage 81 is the first resistance, and the resistance to fluid flowing from the second passage 82 to the third passage 83 is the second resistance, with the second resistance being greater than the first resistance. This ensures that the refrigerant entering the distributor 8 from the second port 12 will preferentially enter the main body 1 via the first passage 81.

[0260] In some embodiments of this utility model, such as Figure 14 and Figure 15 As shown, the openings of the second passage 82 and the third passage 83 face the same side, while the openings of the second passage 82 and the first passage 81 face opposite sides. Therefore, through the positional relationship of the first passage 81, the second passage 82, and the third passage 83, the resistance to fluid flow from the second passage 82 to the first passage 81 is the first resistance, and the resistance to fluid flow from the second passage 82 to the third passage 83 is the second resistance, with the second resistance being greater than the first resistance. This ensures that the medium entering the diverter 8 from the second port 12 will preferentially enter the main body 1 via the first passage 81.

[0261] In some embodiments of this utility model, such as Figure 14As shown, the axis of the second passage 82 and the axis of the third passage 83 are parallel, while the axis of the first passage 81 and the axis of the second passage 82 do not coincide. Therefore, when the axis of the second passage 82 and the axis of the third passage 83 are parallel, the non-coincidence of the axes of the first passage 81 and the second passage 82 effectively prevents the refrigerant from flowing entirely into the first passage 81 after entering through the second passage 82, resulting in almost no flow in the third passage 83. This ensures that most of the refrigerant enters the first passage 81, and a small portion enters the third passage 83, achieving more stable distribution in the distributor 8 and improving the heat exchange uniformity and overall energy efficiency of the heat exchanger assembly 200 using this distributor component 100.

[0262] In some embodiments of this utility model, such as Figure 14 As shown, the axis of the first passage 81 is parallel to the axis of the second passage 82 and is located between the axes of the second passage 82 and the third passage 83. This arrangement further ensures that the resistance to fluid flow from the second passage 82 to the first passage 81 is a first resistance, and the resistance to fluid flow from the second passage 82 to the third passage 83 is a second resistance, with the second resistance being greater than the first resistance. This ensures that the refrigerant entering the distributor 8 from the second port 12 will preferentially enter the main body 1 via the first passage 81, reducing separation and eddies within the distributor 8, thereby reducing additional pressure drop and noise.

[0263] In some embodiments of this utility model, such as Figure 15 As shown, there are multiple third channels 83, which are spaced apart along the circumferential direction of the second channel 82, and the axis of the first channel 81 and the axis of the second channel 82 coincide.

[0264] It is understandable that, since the second passage 82 and the third passage 83 are located on the same side of the distributor 8, and the first passage 81 and the second passage 82 are located on opposite sides of the distributor 8, the axes of the first passage 81 and the second passage 82 are aligned so that the first passage 81 and the second passage 82 form a straight connection. The flow resistance from the second passage 82 to the first passage 81 is small. Meanwhile, multiple third passages 83 are spaced apart along the circumferential direction of the second passage 82 so that the flow resistance from the second passage 82 to the third passage 83 is large. Thus, the resistance of the fluid flowing from the second passage 82 to the first passage 81 is the first resistance, and the resistance of the fluid flowing from the second passage 82 to the third passage 83 is the second resistance, and the second resistance is greater than the first resistance.

[0265] Meanwhile, since the other end of the third passage 83 is open to form multiple second connecting holes 14, there are multiple second connecting holes 14 through the third passage 83. Each second connecting hole 14 is connected to a second branch pipe 32 connected to the heat exchange tube 41, so that there are multiple heat exchange tubes 41 corresponding to the third passage 83 one by one. Thus, the refrigerant entering the multiple third passages 83 through the second branch pipe 32 is dispersed to the multiple heat exchange tubes 41, achieving uniform supply, reducing "gas / liquid starvation", improving the two-phase distribution and temperature field, making the heat exchange more uniform, and the energy efficiency and operational stability higher.

[0266] In some embodiments of this utility model, such as Figure 15 As shown, the axis of the second passage 82 is parallel to the axis of the third passage 83. It can be understood that when multiple third passages 83 are spaced apart along the circumferential direction of the second passage 82, the parallelism between the axes of the second passage 82 and the third passage 83 reduces the resistance difference between the multiple third passages 83. The refrigerant can be evenly distributed into each third passage 83 according to a predetermined ratio, and enter the corresponding heat exchange tube 41 through the second connecting hole 14 and the second branch pipe 32, respectively, to achieve more uniform heat exchange and higher energy efficiency and operational stability.

[0267] In some embodiments of this utility model, such as Figure 16 As shown, the axes of the first passage 81 and the second passage 82 coincide, and the axis of the third passage 83 is perpendicular to the axis of the second passage 82; or the axes of the first passage 81 and the second passage 82 coincide, and the angle between the axis of the third passage 83 and the axis of the second passage 82 is smaller than the angle between the axis of the third passage 83 and the axis of the first passage 81. Therefore, this arrangement reduces the local flow loss from the second passage 82 to the first passage 81, and ensures that a small portion of the refrigerant can flow into the third passage 83 during the flow from the second passage 82 to the first passage 81. This achieves a first resistance for fluid flowing from the second passage 82 to the first passage 81 and a second resistance for fluid flowing from the second passage 82 to the third passage 83, with the second resistance being greater than the first resistance.

[0268] In some embodiments of this utility model, the inner diameter of the second passage 82 is D2, and the inner diameter of the third passage 83 is D3, satisfying: D2 ≥ D3. Therefore, by having the inner diameter of the second passage 82 greater than or equal to the inner diameter of the third passage 83, the connection resistance between the second passage 82 and the third passage 83 is greater, thereby increasing the flow resistance and reducing the flow rate from the second passage 82 into the third passage 83. Furthermore, the smaller inner diameter of the third passage 83 can further increase the flow resistance and reduce the flow rate from the second passage 82 into the third passage 83. Thus, the resistance to fluid flow from the second passage 82 to the first passage 81 is the first resistance, and the resistance to fluid flow from the second passage 82 to the third passage 83 is the second resistance, with the second resistance being greater than the first resistance. For example, as... Figure 1and Figure 2 As shown, the inner diameter of the second passage 82 is larger than the inner diameter of the third passage 83.

[0269] In some embodiments of this invention, the inner diameter of the first passage 81 is D1, and the inner diameter of the third passage 83 is D3, satisfying that D1 > D3. Therefore, this arrangement increases the flow rate from the second passage 82 into the first passage 81 and decreases the flow rate from the second passage 82 into the third passage 83, thereby achieving a first resistance for fluid flowing from the second passage 82 to the first passage 81 and a second resistance for fluid flowing from the second passage 82 to the third passage 83, with the second resistance being greater than the first resistance.

[0270] In some embodiments of this utility model, the open end of the second passage 82 is connected to an inlet / outlet pipe 34, and the open end of the third passage 83 is connected to a second branch pipe 32. The inner diameter of the inlet / outlet pipe 34 is greater than or equal to the inner diameter of the second branch pipe 32. Therefore, by making the inner diameter of the inlet / outlet pipe 34 greater than or equal to the inner diameter of the second branch pipe 32, the connection resistance between the second passage 82 and the third passage 83 is increased, thereby increasing the flow resistance and reducing the flow rate from the second passage 82 into the third passage 83. Furthermore, the smaller inner diameter of the third passage 83 can further increase the flow resistance and reduce the flow rate from the second passage 82 into the third passage 83. Thus, the resistance to fluid flow from the second passage 82 to the first passage 81 is the first resistance, and the resistance to fluid flow from the second passage 82 to the third passage 83 is the second resistance, and the second resistance is greater than the first resistance. For example, as... Figure 1 and Figure 2 As shown, the inner diameter of the second passage 82 is larger than the inner diameter of the third passage 83.

[0271] In some embodiments of this invention, the open end of the first passage 81 is connected to a second manifold 16 or a connecting pipe, the inner diameter of which is larger than the inner diameter of the second branch pipe 32. This arrangement increases the flow rate from the second passage 82 into the first passage 81 and decreases the flow rate from the second passage 82 into the third passage 83, thereby achieving a first resistance for fluid flowing from the second passage 82 to the first passage 81 and a second resistance for fluid flowing from the second passage 82 to the third passage 83, with the second resistance being greater than the first resistance.

[0272] In some embodiments of this invention, the open end of the first passage 81 is connected to a second manifold 16 or a connecting pipe 101, and the open end of the second passage 82 is connected to an inlet / outlet pipe 34. The inner diameter of the second manifold 16 or the connecting pipe 101 is greater than or equal to the inner diameter of the inlet / outlet pipe 34. This arrangement increases the flow rate from the second passage 82 into the first passage 81 and reduces the flow rate from the second passage 82 into the third passage 83, allowing more refrigerant entering through the inlet / outlet pipe 34 to flow into the second manifold 16 or the connecting pipe 101.

[0273] In some embodiments of this utility model, such as Figures 12-14 and Figure 17 As shown, the open end of the third passage 83 is connected to a second branch pipe 32. The minimum cross-sectional inner diameter of the second branch pipe 32 is D0, and it satisfies: D0 ≤ D3. It can be understood that when the inner diameter of the second passage 82 is greater than or equal to the inner diameter of the third passage 83, by further limiting the inner diameter of the second branch pipe 32 to be less than or equal to the inner diameter of the third passage 83, the resistance to fluid flow from the second passage 82 to the first passage 81 can be further increased, thereby reducing the flow rate from the second passage 82 into the third passage 83. For example, as... Figure 1 and Figure 2 As shown, the inner diameter of the second passage 82 is equal to the inner diameter of the third passage 83, and the inner diameter of the second branch pipe 32 is smaller than the inner diameter of the third passage 83.

[0274] In some embodiments of this utility model, the inner diameter of the third passage 83 is D3, and satisfies: D3≥3mm. Therefore, this limitation effectively prevents excessive resistance in the refrigerant flowing from the second passage 82 into the distributor 8 to the third passage 83, thus avoiding insufficient refrigerant flow into the third passage 83 and improving the overall reliability of the distributor assembly 100.

[0275] It should be noted that the inner diameter of the third passage 83 can be 3mm, 4mm, 5mm, 6mm or 7mm, etc.

[0276] In some embodiments of this utility model, the flow-blocking component 2 is a one-way valve, a solenoid valve, or a baffle. Depending on the specific operational requirements of the flow-diverting assembly 100, a one-way valve, a solenoid valve, or a baffle can be selected as the flow-blocking component 2. This method is simple in structure, easy to implement, and low in cost, and can meet the requirement of allowing only the refrigerant within the main body 1 to flow from the second port 12 to the first port 11.

[0277] The following describes a heat exchanger assembly 200 according to an embodiment of the present invention.

[0278] The heat exchanger assembly 200 according to an embodiment of the present utility model includes: a heat exchanger body 4, a flow collection assembly 5, and the aforementioned flow distribution assembly 100.

[0279] Specifically, such as Figure 23 and Figure 25 As shown, the heat exchanger body 4 has multiple heat exchange tubes 41, which form multiple flow paths. The flow collection assembly 5 is located on one side of the heat exchanger body 4 and is connected to the multiple flow paths. The flow collection assembly 5 has a third port 51. The first connecting hole 13 is connected to the end of at least one flow path away from the flow collection assembly 5, and the second connecting hole 14 is connected to the end of at least one flow path away from the flow collection assembly 5.

[0280] Among them, the manifold 5 has the function of collecting and distributing refrigerant, and the refrigerant is suitable to flow from one of the distributor 100 and the manifold 5 to the other.

[0281] For example, when the heat exchanger assembly 200 is applied to the air conditioning system 300, such as Figure 26 As shown, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser. Refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not conductive, and the refrigerant enters the heat exchange tube 41 of the first flow path 42 from the first connecting hole 13. The third port 51 is set to an open circuit state. After being collected by the flow-collecting component 5, the refrigerant enters the heat exchange tube 41 of the second flow path 43 from the first flow path 42, then enters the main body 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12. The refrigerant entering the heat exchange tube 41 from the first connecting hole 13 and then re-entering the heat exchange tube 41 after being collected by the flow-collecting component 5 can further reduce the temperature of the refrigerant and increase its subcooling, thus forming a subcooling tube design for the condenser and better enhancing the heat exchange efficiency of the heat exchanger assembly 200.

[0282] like Figure 27 As shown, when the air conditioning system 300 is in heating mode, the heat exchanger assembly 200 acts as an evaporator. The refrigerant evaporates and absorbs heat in the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the second port 12. At this time, the flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 of the second flow path 43 from the second connecting hole 14. Another part of the refrigerant passes through the flow-blocking component 2 within the body part 1, and then enters the heat exchange tube 41 of the first flow path 42 through the first connecting hole 13. At this time, the third port 51 is open, and the refrigerant in multiple flow paths flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the flow-collecting component 5. Through the cooperation of the flow-dividing component 100 and the heat exchange tube 41, a multi-flow heat exchange pattern can be formed, thereby improving the heat exchange efficiency of the heat exchanger assembly 200.

[0283] Furthermore, in heating mode, the refrigerant needs to pass through a subcooling pipe when entering the conventional outdoor heat exchanger, resulting in pressure loss. However, in this application, by setting a flow-diverting assembly 100 with a flow-blocking component 2, the heat exchanger assembly 200 can form a different flow path in heating mode than in cooling mode. In heating mode, the refrigerant does not need to pass through a subcooling pipe when entering the heat exchanger assembly 200, thus avoiding significant pressure loss.

[0284] In the air conditioning system 300, the heat exchanger assembly 200 serves as the outdoor heat exchanger. During cooling and heating modes, the heat exchanger assembly 200 functions as both the condenser and evaporator, respectively. In these modes, the refrigerant undergoes boiling evaporation and cooling condensation processes within the heat exchanger assembly 200. By incorporating a flow-diverting assembly 100 with flow-blocking components 2 and a flow-collecting assembly 5, given a fixed area and volume of the heat exchanger assembly 200, different flow paths can be created for the refrigerant, resulting in different optimal flow path designs for the heat exchange during the evaporation and condensation processes within the heat exchanger assembly 200.

[0285] According to an embodiment of the present invention, the heat exchanger assembly 200, by providing a first port 11, a second port 12, a first connecting hole 13, and a second connecting hole 14 on the main body 1, and by providing a flow-blocking component 2 on the main body 1, allowing the refrigerant to flow only from the second port 12 to the first port 11, can automatically open and close or cut off the flow, thereby automatically guiding the refrigerant and changing its flow direction. When the heat exchanger assembly 200 is used in an air conditioning system 300, it can automatically switch the refrigerant through different flow paths in the heat exchanger assembly 200 in different modes of the air conditioning system 300, thereby improving the heat exchange efficiency of the heat exchanger assembly 200, improving the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, no other control structures are required, making the structure simple, easy to implement, and low in cost.

[0286] In some embodiments of this utility model, reference is made to Figure 27 When the heat exchanger assembly is used as an evaporator, the refrigerant flows into the heat exchanger assembly from the second port 12, and then flows into the heat exchange tube 41 of the heat exchanger assembly from the first connecting hole 13 and the second connecting hole 14, and then flows out of the heat exchanger assembly from the third port 51. The flow-blocking component 2 is open, and the first port 11 is closed.

[0287] When the heat exchanger assembly 200 is applied to the air conditioning system 300, the air conditioning system 300 is in heating mode. The refrigerant evaporates and absorbs heat in the heat exchanger assembly 200. The refrigerant flows into the heat exchanger assembly 200 from the second port 12. At this time, the flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 of the second flow path 43 from the second connecting hole 14. Another part of the refrigerant passes through the flow-blocking component 2 in the body part 1, the first port 11 is closed, and then enters the heat exchange tube 41 of the first flow path 42 through the first connecting hole 13. At this time, the third port 51 is open, and the refrigerant in multiple flow paths flows out of the heat exchanger assembly 200 through the third port 51 after being collected by the flow-collecting component 5. By cooperating with the flow-dividing component 100 and the heat exchange tube 41, a multi-flow heat exchange pattern can be formed, thereby improving the heat exchange efficiency of the heat exchanger assembly 200.

[0288] Furthermore, in heating mode, the refrigerant needs to pass through a subcooling pipe when entering the conventional outdoor heat exchanger, resulting in pressure loss. However, in this application, by setting a flow-diverting assembly 100 with a flow-blocking component 2, the heat exchanger assembly 200 can form a different flow path in heating mode than in cooling mode. In heating mode, the refrigerant does not need to pass through a subcooling pipe when entering the heat exchanger assembly 200, thus avoiding significant pressure loss.

[0289] refer to Figure 26 When the heat exchanger assembly functions as a condenser, refrigerant flows into the heat exchanger assembly from the first port 11, and then flows into the heat exchange tube 41 of the heat exchanger assembly from the first connecting hole 13, and subsequently flows out of the heat exchanger assembly from the second connecting hole 14 and the second port 12. Both the flow-blocking component 2 and the third port 51 are blocked. In this embodiment, the third port 51 is blocked by a valve in the air conditioner, for example, by a five-way valve 636.

[0290] When the heat exchanger assembly 200 is applied to the air conditioning system 300, the air conditioning system 300 is in cooling mode. Refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not conductive. The refrigerant enters the heat exchange tube 41 of the first flow path 42 from the first connecting hole 13. The third port 51 is set to an open circuit state. After being collected by the flow-collecting component 5, the refrigerant enters the heat exchange tube 41 of the second flow path 43 from the first flow path 42, then enters the body part 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12. The refrigerant entering the heat exchange tube 41 from the first connecting hole 13 and then re-entering the heat exchange tube 41 after being collected by the flow-collecting component 5 can further reduce the temperature of the refrigerant and increase its subcooling, thus forming a subcooling tube design for the condenser and better enhancing the heat exchange efficiency of the heat exchanger assembly 200.

[0291] In the air conditioning system 300, the heat exchanger assembly 200 serves as the outdoor heat exchanger. During cooling and heating modes, the heat exchanger assembly 200 functions as both the condenser and evaporator, respectively. In these modes, the refrigerant undergoes boiling evaporation and cooling condensation processes within the heat exchanger assembly 200. By incorporating a manifold distribution assembly 100 with flow-blocking components 2, given a fixed area and volume of the heat exchanger assembly 200, different flow paths can be created for the refrigerant. This allows for different optimal flow path designs for the heat exchange during the evaporation and condensation processes within the heat exchanger assembly 200. This improves the heat exchange efficiency of the heat exchanger assembly 200, thereby enhancing the cooling or heating performance of the air conditioning system 300 and improving energy efficiency.

[0292] In some embodiments of this utility model, reference is made to Figure 21 and Figure 22The flow collection assembly 5 includes a main pipe 52 and branch pipes 53. The main pipe 52 has a third port 51. One end of the branch pipe 53 is connected to the main pipe 52. The inner diameter of the main pipe 52 is greater than or equal to the inner diameter of the branch pipe 53. There are multiple branch pipes 53. The ends of the multiple branch pipes 53 that are away from the main pipe 52 are respectively connected to multiple flow paths.

[0293] The main pipe 52 has a third port 51; there are multiple branch pipes 53, one end of which is connected to the main pipe 52. The inner diameter of the main pipe 52 is greater than or equal to the inner diameter of the branch pipe 53. It should be noted that in the prior art, due to installation considerations, the inner diameter of the main pipe 52 is larger than the inner diameter of the branch pipe 53, so that the branch pipe 53 can be inserted into the peripheral wall of the main pipe 52. However, this results in excessive material usage in the main pipe 52, leading to increased costs.

[0294] It is understandable that the manifold 5 is used to connect to the heat exchange tube 41 of the heat exchanger body 4. The inner diameter of the branch pipe 53 is the same as the inner diameter of the heat exchange tube 41. While keeping the inner diameter of the branch pipe 53 unchanged, that is, keeping the inner diameter of the heat exchange tube 41 unchanged, the inner diameter of the main pipe 52 is equal to the inner diameter of the branch pipe 53, thereby reducing the inner diameter of the main pipe 52, thereby reducing the material, weight and cost of the main pipe 52, which is beneficial to the economy and lightweight of the manifold 5, and thus beneficial to the economy and lightweight of the heat exchanger assembly 200.

[0295] Meanwhile, since the inner diameter of the heat exchange tube 41 remains unchanged, the material used in the heat exchange tube 41 is sufficient, and the manifold 5 does not participate in the heat exchange process, thus it will not affect the heat exchange efficiency of the heat exchanger assembly 200. In addition, as the inner diameter of the manifold 5 decreases, the refrigerant flows faster in the manifold 5, thereby reducing the pressure loss caused by the reduction in the inner diameter of the manifold 5, further avoiding any impact on the heat exchange efficiency of the heat exchanger assembly 200.

[0296] The arrangement of multiple branch pipes 53 further improves the heat exchange efficiency of the heat exchanger assembly 200, for example, in Figure 21 In the example shown, there are 4 branch pipes 53, but the present invention is not limited to this. The number of branch pipes 53 can also be other numbers, such as 2, 3, 5 or 6.

[0297] Optionally, the ratio of the inner diameter of the main pipe 52 to the inner diameter of the branch pipe 53 is 1:1 to 9:7. For example, the ratio of the inner diameter of the main pipe 52 to the inner diameter of the branch pipe 53 can be 9:7, 9:8 or 1:1.

[0298] In some embodiments of this utility model, the outer diameter of the main pipe 52 is greater than or equal to the outer diameter of the branch pipe 53, thereby reducing the inner diameter of the main pipe 52, which in turn reduces the material, weight and cost of the main pipe 52, which is beneficial to the economy and lightweight of the manifold 5, and thus to the economy and lightweight of the heat exchanger assembly 200.

[0299] Optionally, the ratio of the outer diameter of the main pipe 52 to the outer diameter of the branch pipe 53 is 1:1 to 9:7. For example, the ratio of the outer diameter of the main pipe 52 to the outer diameter of the branch pipe 53 is 9:7, 9:8 or 1:1.

[0300] The inner diameter of the main pipe 52 is greater than or equal to the inner diameter of the branch pipe 53, or the outer diameter of the main pipe 52 is greater than or equal to the outer diameter of the branch pipe 53. On the one hand, the inner diameter of the main pipe 52 is reduced, thereby reducing the material, weight and cost of the main pipe 52, which is beneficial to the economy and lightweight of the manifold assembly 5, and thus beneficial to the economy and lightweight of the heat exchanger assembly 200. On the other hand, the heat exchange efficiency of the heat exchanger assembly 200 is guaranteed.

[0301] In some embodiments of this utility model, the branch pipe 53 is connected to the main pipe 52 via a second tee pipe, the inner diameter of which is greater than or equal to the outer diameter of the main pipe 52. Since the outer diameters of the branch pipe 53 and the main pipe 52 are similar, they cannot be directly connected by inserting a pipe. Connecting the branch pipe 53 and the main pipe 52 via the second tee pipe facilitates the connection between the branch pipe 53 and the main pipe 52.

[0302] In addition, the inner diameter of the second tee pipe is greater than or equal to the outer diameter of the main pipe 52, and also greater than or equal to the outer diameter of the branch pipe 53, which facilitates the insertion of the main pipe 52 and the branch pipe 53 into the second tee pipe to achieve the connection between them.

[0303] It is understandable that the branch pipe 53 can be located at one end of the length direction of the main pipe 52. When the branch pipe 53 is located at one end of the length direction of the main pipe 52, the branch pipe 53 is directly connected to one end of the length direction of the main pipe 52 through a tee pipe, and one end of the tee pipe is closed.

[0304] When the branch pipe 53 is located between the two ends of the main pipe 52 along its length, the main pipe 52 includes multiple connecting pipe segments 331 spaced apart along its length. Adjacent connecting pipe segments 331 are connected to the branch pipe 53 via a tee pipe, meaning the three ports of the tee pipe are connected to the two adjacent connecting pipe segments 331 and the branch pipe 53 respectively. Therefore, installation between the main pipe 52 and the branch pipe 53 can be achieved when the inner diameter of the main pipe 52 is equal to the inner diameter of the branch pipe 53.

[0305] In some embodiments of this utility model, such as Figure 21As shown, the manifold assembly 5 also includes a manifold 54, one end of which is connected to the main pipe 52, and the other end is connected to multiple branch pipes 53. It is understood that the manifold is responsible for evenly distributing the refrigerant to various parts of the air conditioning system 300, such as the evaporator or condenser, ensuring uniform refrigerant flow in each part, thereby improving the efficiency and performance of the air conditioning system. The manifold helps balance the pressure in the air conditioning system 300, ensuring smooth refrigerant flow within the system and preventing performance degradation or damage caused by pressure fluctuations.

[0306] For example in Figure 21 In the example shown, the manifold 54 connects two branch pipes 53, but the present invention is not limited to this. The manifold 54 can also connect more branch pipes 53, such as 3, 4, 5 or 6, etc.

[0307] In some embodiments of this utility model, such as Figure 21 and Figure 22 As shown, the multiple branch pipes 53 include at least one third branch pipe 531 and at least one fourth branch pipe 532. The third branch pipe 531 and the fourth branch pipe 532 are arranged at intervals along the length of the main pipe 52. The manifold assembly 5 has a first state and a second state. In the first state, the refrigerant enters the main pipe 52 from the third branch pipe 531 and flows out from the fourth branch pipe 532, and the third port 51 is closed. In the second state, the refrigerant enters the main pipe 52 from the third branch pipe 531 and the fourth branch pipe 532 and flows out from the third port 51.

[0308] Therefore, the heat exchange tube 41 can be configured to accommodate different flow paths, for example in Figure 21 and Figure 22 In the example shown, there are 3 third branch pipes 531 and 1 fourth branch pipe 532. However, the present invention is not limited to this. The number of third branch pipes 531 and fourth branch pipes 532 can also be other numbers, such as 2, 4, 5 or 6.

[0309] Furthermore, such as Figure 21 , Figure 22 , Figure 26 and Figure 27 As shown, the current collector component 5 has a first state and a second state, as follows: Figure 21 and Figure 26 As shown, in the first state, the refrigerant enters the main pipe 52 from the third branch pipe 531 and flows out from the fourth branch pipe 532. When in the first state, the air conditioning system 300 of this utility model is in the cooling mode. At this time, the third port 51 is closed, the refrigerant enters the third branch pipe 531 from the heat exchange pipe 41, enters the main pipe 52 from the third branch pipe 531, and flows out from the fourth branch pipe 532, flowing towards the heat exchange pipe 41.

[0310] like Figure 21 and Figure 27As shown, in the second state, refrigerant enters the main pipe 52 from the third branch pipe 531 and the fourth branch pipe 532, and flows out from the third port 51. When in the second state, the air conditioning system 300 of this utility model is in heating mode. At this time, the third port 51 is open, and refrigerant enters the main pipe 52 from the third branch pipe 531 and the fourth branch pipe 532 of the heat exchange pipe 41, and then flows out from the third port 51, flowing to the return port 612 of the compressor 61.

[0311] Therefore, when the manifold 5 is used in the heat exchanger assembly 200 of the air conditioning system 300, it can automatically switch the refrigerant flow path within the heat exchanger assembly 200 in different modes of the air conditioning system 300, thereby improving the heat exchange efficiency of the heat exchanger assembly 200, enhancing the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, it requires no additional control structure, is less susceptible to power failures, and features a simple, easy-to-implement, and low-cost structure.

[0312] In some embodiments of this utility model, such as Figure 21 and Figure 22 As shown, on the projection plane perpendicular to the axis of the main pipe 52, the third branch pipe 531 and the fourth branch pipe 532 are spaced apart or at an angle. It can be understood that, on the projection plane perpendicular to the axis of the main pipe 52, the third branch pipe 531 and the fourth branch pipe 532 are spaced apart, which helps to avoid installation interference between the third branch pipe 531 and the fourth branch pipe 532.

[0313] On the other hand, since both the end of the third branch pipe 531 facing away from the main pipe 52 and the end of the fourth branch pipe 532 facing away from the main pipe 52 are connected to the heat exchange tubes 41, and the heat exchange tubes 41 are arranged in multiple rows along the thickness direction of the heat exchanger body 4, and by spacing the third branch pipe 531 and the fourth branch pipe 532 in the projection plane perpendicular to the axis of the main pipe 52, the third branch pipe 531 and the fourth branch pipe 532 can be connected to different rows of heat exchange tubes 41, thereby realizing the counter-current arrangement of the refrigerant and the heat exchange airflow. The counter-current arrangement can maintain a large temperature difference between the refrigerant and the heat exchange airflow on the heat exchange tubes 41, thereby maximizing the heat exchange efficiency. This can effectively improve the heat exchange efficiency of the heat exchanger assembly 200. When the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the cooling or heating performance of the air conditioning system 300 and improve energy efficiency.

[0314] In some embodiments of this utility model, such as Figure 21 and Figure 22 As shown, one end of the main pipe 52 is open in the length direction to form a third port 51, or the third port 51 is located on the peripheral wall of the main pipe 52, thereby accommodating different pipe connection methods.

[0315] Furthermore, such as Figure 21 and Figure 22As shown, the third port 51 is connected to an extension pipe 55. The extension pipe 55 facilitates the indirect connection between the main pipe 52 and components such as the throttling device 64 in the air conditioning system 300. This can relatively reduce the difficulty of connecting the manifold 5 to other components, which is beneficial to reducing the probability of refrigerant leakage and ensuring the normal operation of the air conditioning system 300.

[0316] For example, such as Figure 26 As shown, when the air conditioning system 300 is in cooling mode, the heat exchanger assembly 200 acts as a condenser, and the refrigerant flows from the heat exchange tube 41 to the main pipe 52. At this time, the extension pipe 55 is not conductive and is in an open circuit state, thus having a liquid storage function.

[0317] It should be noted that the extension pipe 55 is welded to the main pipe 52, which can ensure the connection strength between the extension pipe 55 and the main pipe 52, improve the structural strength of the manifold 5, and ensure the reliability and stability of the manifold 5. In addition, during the welding process, the weld metal fills the gap between the main pipe 52 and the extension pipe 55, forming a dense connection layer, which can effectively prevent refrigerant leakage.

[0318] In some embodiments of this utility model, the extension pipe 55 is U-shaped or inverted U-shaped. When the refrigerant enters from the inlet / outlet pipe 34, the U-shaped or inverted U-shaped extension pipe 55 can accelerate the refrigerant under the action of centrifugal force, thereby increasing the refrigerant flow power in the main pipe 52, preventing the refrigerant from accumulating at the extension pipe 55, and improving the refrigerant flow distribution in the manifold 5. When the manifold 5 is applied to the heat exchanger assembly 200, it can improve the heat exchange efficiency of the heat exchanger assembly 200 and improve energy efficiency.

[0319] In some embodiments of this utility model, a plurality of heat exchange tubes 41 form at least one first flow path 42 and at least one second flow path 43, and a plurality of branch tubes 53 include at least one third branch tube 531 and at least one fourth branch tube 532. The third branch tube 531 is connected to the first flow path 42, and the fourth branch tube 532 is connected to the second flow path 43. The first connecting hole 13 is connected to the end of at least one first flow path 42 away from the third branch tube 531, and the second connecting hole 14 is connected to the end of at least one second flow path 43 away from the fourth branch tube 532.

[0320] The first connecting hole 13 is connected to one end of at least one first flow path 42, and the second connecting hole 14 is connected to one end of at least one second flow path 43. The heat exchange tubes 41 are arranged in multiple rows along the thickness direction of the heat exchanger body 4. Both the first flow path 42 and the second flow path 43 include multiple rows of heat exchange tubes 41. The heat exchange tubes 41 of the first flow path 42 connected to the first connecting hole 13 and the heat exchange tubes 41 of the second flow path 43 connected to the second connecting hole 14 are located on opposite sides of the thickness direction of the heat exchanger body 4 or are located in different rows.

[0321] refer to Figure 23 As shown, multiple heat exchange tubes 41 form three first flow paths 42 and one second flow path 43. Of course, the number of first flow paths 42 formed by multiple heat exchange tubes 41 can also be one, two, four, five or six, etc., and the number of second flow paths 43 formed by multiple heat exchange tubes 41 can also be two, three, four, five or six, etc.

[0322] When the heat exchanger assembly 200 functions as a condenser, the refrigerant enters the body 1 from the first port 11. The flow-blocking component 2 is not open, so the refrigerant can only enter the heat exchange tube 41 through the first connecting hole 13, then return to the body 1 from the heat exchange tube 41 through the second connecting hole 14, and finally flow out of the heat exchanger assembly 200 from the second port 12. The heat exchange tube 41 of the first flow path 42 connected to the first connecting hole 13 and the heat exchange tube 41 of the second flow path 43 connected to the second connecting hole 14 are located on opposite sides of the thickness direction of the heat exchanger body 4. This can be understood as connecting the first connecting hole 13 and the second connecting hole 14 to both sides of the heat exchanger body 4 along the thickness direction of the body 4.

[0323] For example, refer to Figure 23 As shown, assuming the two sides of the heat exchanger body 4 in the thickness direction are the first side and the second side, the heat exchange tube 41 on the first flow path 42 near the first connecting hole 13 is located on the first side in the thickness direction of the heat exchanger body 4, and the heat exchange tube 41 on the second flow path 43 near the second connecting hole 14 is located on the second side in the thickness direction of the heat exchanger body 4. The refrigerant in the body part 1 enters the heat exchange tube 41 on the first side of the first flow path 42 through the first connecting hole 13, and flows from the first side to the second side. It then flows into the heat exchange tube 41 on the first side of the second flow path 43 through components such as the manifold 5. The refrigerant flows from the first side to the second side in the second flow path 43, and flows out of the heat exchanger body 4 through the second connecting hole 14 from the heat exchange tube 41 on the second side of the second flow path 43 to enter the body part 1.

[0324] Therefore, when the heat exchanger assembly 200 functions as a condenser, the refrigerant flows from the first side to the second side within the heat exchanger body 4 along its thickness direction. This facilitates the setting of the position and orientation of the heat exchanger assembly 200 and the control of the flow direction of the airflow exchanging heat with the heat exchanger assembly 200, ensuring that the flow direction of the airflow exchanging heat with the heat exchanger assembly 200 is opposite to the flow direction of the refrigerant within the heat exchanger body 4. This facilitates a counter-flow arrangement of the refrigerant and the heat exchange airflow. This counter-flow arrangement allows the refrigerant and the heat exchange airflow to maintain a large temperature difference on the heat exchange tube 41, thereby maximizing heat exchange efficiency. This effectively improves the heat exchange efficiency of the heat exchanger assembly 200. When the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the performance and energy efficiency of the air conditioning system 300.

[0325] In some embodiments of this utility model, such as Figure 23 and Figure 25 As shown, the heat exchange tubes 41 of the first flow path 42 connected to the first connecting hole 13 are located in a row on the leeward side of the heat exchanger body 4, and the heat exchange tubes 41 of the second flow path 43 connected to the second connecting hole 14 are located in a row on the windward side of the heat exchanger body 4.

[0326] It is understandable that the refrigerant in the main body 1 enters the heat exchange tube 41 located on the leeward side of the first flow path 42 through the first connecting hole 13, and then flows out of the heat exchanger body 4 through the second connecting hole 14 from the heat exchange tube 41 located on the windward side of the second flow path 43 to enter the main body 1.

[0327] In this way, when the heat exchanger assembly 200 functions as a condenser, the refrigerant can be ensured to flow from the leeward side to the windward side along the thickness direction of the heat exchanger body 4, thus achieving a counter-flow arrangement between the refrigerant and the heat exchange airflow. This counter-flow arrangement allows the refrigerant and the heat exchange airflow to maintain a large temperature difference on the heat exchange tube 41, thereby maximizing heat exchange efficiency. This effectively improves the heat exchange efficiency of the heat exchanger assembly 200, and when the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the performance and energy efficiency of the air conditioning system 300.

[0328] In some embodiments of this utility model, such as Figure 23 , Figure 24 and Figure 25 As shown, the heat exchange tubes 41 are arranged in multiple rows along the thickness direction of the heat exchanger body 4. The first flow path 42 and the second flow path 43 both include multiple rows of heat exchange tubes 41. The heat exchange tubes 41 of the first flow path 42 connected to the third branch pipe 531 and the heat exchange tubes 41 of the second flow path 43 connected to the fourth branch pipe 532 are located on opposite sides of the thickness direction of the heat exchanger body 4 or in different rows.

[0329] It is understandable that the refrigerant flows in the same direction within the heat exchanger body 4 along its thickness. This facilitates the setting of the position and orientation of the heat exchanger assembly 200 and the control of the flow direction of the airflow exchanging heat with the heat exchanger assembly 200, ensuring that the flow direction of the airflow exchanging heat with the heat exchanger assembly 200 is opposite to the flow direction of the refrigerant within the heat exchanger body 4. This facilitates a counter-flow arrangement of the refrigerant and the heat exchange airflow. This counter-flow arrangement allows the refrigerant and the heat exchange airflow to maintain a large temperature difference on the heat exchange tube 41, thereby maximizing heat exchange efficiency. This effectively improves the heat exchange efficiency of the heat exchanger assembly 200. When the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the cooling or heating performance of the air conditioning system 300 and increase energy efficiency.

[0330] In some embodiments of this utility model, such as Figure 23 , Figure 24 and Figure 25As shown, the heat exchange tubes 41 of the first flow path 42 connected to the third branch pipe 531 are located in a row on the windward side of the heat exchanger body 4, and the heat exchange tubes 41 of the second flow path 43 connected to the fourth branch pipe 532 are located in a row on the leeward side of the heat exchanger body 4.

[0331] Understandably, this arrangement allows the third branch to be adapted to the installation of the first branch pipe 31, and the fourth branch to be adapted to the installation of the second branch. This results in the heat exchange tube 41 on the first flow path 42, which is close to the first connecting hole 13, being located on the leeward side of the heat exchanger body 4, and the heat exchange tube 41 on the second flow path 43, which is close to the second connecting hole 14, being located on the windward side of the heat exchanger body 4.

[0332] In this way, when the heat exchanger assembly 200 functions as a condenser, the refrigerant can be ensured to flow from the leeward side to the windward side along the thickness direction of the heat exchanger body 4, thus achieving a counter-flow arrangement between the refrigerant and the heat exchange airflow. This counter-flow arrangement allows the refrigerant and the heat exchange airflow to maintain a large temperature difference on the heat exchange tube 41, thereby maximizing heat exchange efficiency. This effectively improves the heat exchange efficiency of the heat exchanger assembly 200, and when the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the performance and energy efficiency of the air conditioning system 300.

[0333] In some embodiments of this utility model, such as Figure 23 As shown, the heat exchange tubes 41 are arranged in multiple rows along the thickness direction of the heat exchanger body 4. The first flow path 42 includes a row of windward heat exchange tubes 45 located on the windward side of the heat exchanger body 4 and a row of leeward heat exchange tubes 44 located on the leeward side of the heat exchanger body 4. When the heat exchanger assembly 200 is used as a condenser and as an evaporator, the refrigerant flowing into the first flow path 42 first flows through the leeward heat exchange tubes 44 and then flows through the windward heat exchange tubes 45.

[0334] Understandably, the refrigerant in the main body 1 enters the leeward side heat exchange tube 44 of the first flow path 42 through the first connecting hole 13, and flows from the leeward side heat exchange tube 44 to the windward side heat exchange tube 45. This ensures that the refrigerant in the first flow path 42 flows from the leeward side to the windward side along the thickness direction of the heat exchanger body 4, thus achieving a counter-current arrangement of the refrigerant and the heat exchange airflow. This maintains a large temperature difference between the refrigerant and the heat exchange airflow on the heat exchange tube 41, thereby maximizing the heat exchange efficiency. This can effectively improve the heat exchange efficiency of the heat exchanger assembly 200. When the heat exchanger assembly 200 is applied to the air conditioning system 300, it can improve the performance and energy efficiency of the air conditioning system 300.

[0335] In some embodiments of this utility model, such as Figure 23As shown, the heat exchange tubes 41 are arranged in multiple rows along the thickness direction of the heat exchanger body 4. The second flow path 43 includes a row of windward heat exchange tubes 45 located on the windward side of the heat exchanger body 4 and a row of leeward heat exchange tubes 44 located on the leeward side of the heat exchanger body 4. When the heat exchanger assembly 200 is used as an evaporator, the refrigerant flowing into the second flow path 43 first flows through the windward heat exchange tubes 45 and then flows through the leeward heat exchange tubes 44. When the heat exchanger assembly 200 is used as a condenser, the refrigerant flowing into the second flow path 43 first flows through the leeward heat exchange tubes 44 and then flows through the windward heat exchange tubes 45. The refrigerant flowing out of the first flow path 42 flows into the leeward side heat exchange tube 44 of the second flow path 43. The refrigerant flows from the leeward side heat exchange tube 44 to the windward side heat exchange tube 45 in the second flow path 43, and flows out of the heat exchanger body 4 through the second connecting hole 14 from the windward side heat exchange tube 45 of the second flow path 43 to enter the body part 1.

[0336] This ensures that when the heat exchanger assembly 200 functions as a condenser, the refrigerant in the second flow path 43 flows from the leeward side to the windward side along the thickness direction of the heat exchanger body 4, achieving a counter-current arrangement between the refrigerant and the heat exchange airflow. This maintains a large temperature difference between the refrigerant and the heat exchange airflow on the heat exchange tube 41, thereby maximizing heat exchange efficiency. This effectively improves the heat exchange efficiency of the heat exchanger assembly 200, and when applied to the air conditioning system 300, it enhances the performance and energy efficiency of the air conditioning system 300.

[0337] In some embodiments, the refrigerant in the body 1 enters the leeward heat exchange tube 44 of the first flow path 42 through the first connecting hole 13, and flows from the leeward heat exchange tube 44 to the windward heat exchange tube 45. Then, the refrigerant flows from the first flow path 42 into the leeward heat exchange tube 44 of the second flow path 43 through components such as the manifold 5. The refrigerant flows from the leeward heat exchange tube 44 to the windward heat exchange tube 45 in the second flow path 43, and flows out of the heat exchanger body 4 through the second connecting hole 14 from the windward heat exchange tube 45 of the second flow path 43 to enter the body 1.

[0338] In some embodiments of this utility model, such as Figure 25 In the example shown, the flow collector 5 and the flow divider 100 are located on the same side along the length of the heat exchanger body 4. The positions of the flow collector 5 and the flow divider 100 can be selected according to the number of rows of heat exchange tubes 41 arranged along the thickness direction of the heat exchanger body 4 and the specific arrangement of the first flow path 42 and the second flow path 43, making the connection between the flow collector 5 and the flow divider 100 and the heat exchanger body 4 simpler and more convenient.

[0339] The following describes an air conditioning system 300 according to an embodiment of the present invention.

[0340] An air conditioning system 300 according to an embodiment of the present invention includes: a compressor 61, an indoor heat exchanger 62, the aforementioned heat exchanger assembly 200, and a reversing assembly 63.

[0341] Specifically, such as Figure 26 and Figure 27 As shown, the compressor 61 has an exhaust port 611 and a return port 612. One end of the indoor heat exchanger 62 is connected to the second port 12. The reversing assembly 63 has a first port 631, a second port 632, a third port 633, a fourth port 634, and a fifth port 635. The first port 631 is connected to the exhaust port 611, the third port 633 is connected to the return port 612, the second port 632 is connected to the other end of the indoor heat exchanger 62, the fourth port 634 is connected to the third port 51, and the fifth port 635 is connected to the first port 11. The commutator 63 has a first switching state and a second switching state. When the commutator 63 is in the first switching state, the first port 631 is connected to the fifth port 635, the second port 632 is connected to the third port 633, and the fourth port 634 is cut off to close the third port 51 (so that the third port 51 is cut off). When the commutator 63 is in the second switching state, the first port 631 is connected to the second port 632, the third port 633 and the fourth port 634 are connected, and the fifth port 635 is cut off to cut off the first port 11.

[0342] In the air conditioning system 300, during the specific operation of the air conditioning system 300, such as Figure 26 As shown in the example, when the air conditioning system 300 is in cooling mode, the commutator 63 is in the first switching state, and the first port 631 of the commutator 63 is connected to the fifth port 635, and the second port 632 is connected to the third port 633.

[0343] Therefore, compressor 61 compresses the refrigerant into a high-temperature, high-pressure gas. The high-pressure gaseous refrigerant enters the reversing assembly 63 through the compressor 61's exhaust port 611 and the first port 631, and then flows to the heat exchanger assembly 200 through the fifth port 635. The heat exchanger assembly 200 can exchange heat with the external environment and dissipate heat through condensation. The refrigerant flows within the heat exchanger assembly 200 and releases heat to the external environment, thus changing from a gaseous state to a liquid state. The high-pressure liquid refrigerant flowing out of the heat exchanger assembly 200 then flows to the throttling device 64, which reduces the refrigerant pressure, allowing the low-pressure liquid refrigerant to flow into the indoor heat exchanger 62. The indoor heat exchanger 62 absorbs heat. The refrigerant is heated and vaporized within the indoor heat exchanger 62, changing from a liquid state to a gaseous state, thereby carrying away the heat from the airflow flowing over the surface of the indoor heat exchanger 62. The low-temperature airflow is then delivered into the room by the indoor unit of the air conditioner to achieve the purpose of cooling. Meanwhile, the low-pressure gaseous refrigerant flows to the second port 632 of the reversing component 63, and from the third port 633 to the return port 612 to return to the compressor 61 for compression again, thereby forming a refrigerant cycle and achieving the cooling effect of the air conditioning system 300.

[0344] In this process, refrigerant flows into the heat exchanger assembly 200 from the first port 11. At this time, the flow-blocking component 2 is not conductive and the third port 51 is set to an open circuit state. The refrigerant enters the heat exchange tube 41 of the first flow path 42 from the first connecting hole 13, then enters the heat exchange tube 41 of the second flow path 43 through the collector component 5, then enters the body part 1 from the second connecting hole 14, and finally flows out of the heat exchanger assembly 200 from the second port 12. The refrigerant first enters the heat exchange tube 41 of the first flow path 42 from the first connecting hole 13, and then enters the heat exchange tube 41 of the second flow path 43 after being collected. This can further reduce the temperature of the refrigerant and increase the subcooling of the refrigerant, thereby forming a subcooling tube design for the condenser and better enhancing the heat exchange efficiency of the heat exchanger assembly 200.

[0345] Similarly, such as Figure 27 As shown in the example, when the air conditioning system 300 is in heating mode, the reversing component 63 is in the second switching state, and the first port 631 of the reversing component 63 is connected to the second port 632, and the third port 633 and the fourth port 634 are connected.

[0346] Therefore, compressor 61 compresses the refrigerant into a high-temperature, high-pressure gas. The high-pressure gaseous refrigerant enters the reversing assembly 63 through the compressor 61's exhaust port 611 and the first port 631, and then flows to the indoor heat exchanger 62 through the second port 632. The indoor heat exchanger 62 can exchange heat with the airflow flowing over its surface. The airflow absorbs heat, and the refrigerant condenses and dissipates heat. The high-temperature airflow is sent into the room by the indoor unit of the air conditioner to achieve the purpose of heating. The refrigerant flows in the indoor heat exchanger 62 and releases heat into the indoor environment, thus changing from a gaseous state to a liquid state. The high-pressure liquid refrigerant flowing out of the indoor heat exchanger 62 then flows to the throttling device 64. The throttling device 64 can throttle the flow, reduce the pressure of the refrigerant, and allow the low-pressure liquid refrigerant to flow into the heat exchanger assembly 200. The heat exchanger assembly 200 can absorb heat. The refrigerant absorbs heat and vaporizes in the heat exchanger assembly 200, changing from a liquid state to a gaseous state, thereby carrying away the heat flowing through the outdoor environment. The low-pressure gaseous refrigerant flows to the fourth port 634 of the reversing assembly 63, and from the third port 633 to the return port 612 to return to the compressor 61 for compression again, thus forming a refrigerant cycle and achieving the heating effect of the air conditioning system 300.

[0347] In this process, refrigerant flows into the heat exchanger assembly 200 from the second port 12. At this time, the flow-blocking component 2 is open, and part of the refrigerant enters the heat exchange tube 41 of the second flow path 43 from the second connecting hole 14. Another part of the refrigerant passes through the flow-blocking component 2 in the body part 1, and then enters the heat exchange tube 41 of the first flow path 42 through the first connecting hole 13. After the refrigerant in the multiple flow paths is collected by the flow-collecting component 5, it flows out of the heat exchanger assembly 200 through the third port 51 and flows to the fourth port 634 of the reversing component 63. By cooperating with the flow-diverting component 100 and the heat exchange tube 41 body, a multi-flow heat exchange pattern can be formed, thereby improving the heat exchange efficiency of the heat exchanger assembly 200.

[0348] By setting up the reversing assembly 63, the flow path of the air conditioning system 300 can be automatically switched without changing any components. This allows the refrigerant to automatically switch its flow direction within the reversing assembly 63, thereby enabling the air conditioning system 300 to automatically switch between cooling and heating modes to meet the needs of various environmental conditions. Furthermore, no manual adjustment is required, greatly improving the convenience and efficiency of operation, thus enhancing the reliability and efficiency of the air conditioning system 300 and ultimately improving user comfort.

[0349] By adding a flow-blocking component 2 to the flow distribution assembly 100, the flow-blocking component 2 automatically opens, closes, or cuts off the flow based on the pressure difference of the refrigerant on both sides. This allows for automatic flow guidance of the refrigerant by the flow-blocking component 2, changing the flow direction of the refrigerant. In different modes of the air conditioning system 300, automatic switching of the refrigerant's flow path within the heat exchanger assembly 200 can be achieved, improving the heat exchange efficiency of the heat exchanger assembly 200, enhancing the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, no other control structure is required, making it less susceptible to power failures, and the structure is simple, easy to implement, and low in cost.

[0350] According to an embodiment of the present invention, the air conditioning system 300, by providing a first port 11, a second port 12, a first connecting hole 13, and a second connecting hole 14 on the main body 1, and by providing a flow-blocking component 2 on the main body 1, and by ensuring that the flow-blocking component 2 only allows refrigerant to flow from the second port 12 to the first port 11, can automatically open and close or cut off the flow, thereby achieving automatic flow guidance of the refrigerant by the flow-blocking component 2, thus changing the flow direction of the refrigerant. In different modes of the air conditioning system 300, automatic switching of different flow paths of the refrigerant within the heat exchanger assembly 200 can be achieved, thereby improving the heat exchange efficiency of the heat exchanger assembly 200, improving the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, no other control structure is required, making the structure simple, easy to implement, and low in cost.

[0351] In some embodiments, the reversing assembly 63 includes a four-way valve, a pilot valve 637, and a three-way valve. The four-way valve has a first port 631, a second port 632, a third port 633, and a fourth branch port. The pilot valve 637 is used to control the first port 631 to communicate with one of the second port 632 and the third port 633, and the fourth branch port to communicate with the other of the second port 632 and the third port 633. The three-way valve has three ports, one of which is connected to the fourth branch port, and the other two ports are respectively formed as the fourth port 634 and the fifth port 635.

[0352] In some embodiments, the reversing assembly 63 includes a five-way valve 636 and a pilot valve 637. The five-way valve 636 has a first port 631, a second port 632, a third port 633, a fourth port 634, and a fifth port 635 disposed on the five-way valve 636. The pilot valve 637 is used to control the first port 631 to communicate with the fifth port 635 and the second port 632 to communicate with the third port 633, or to control the first port 631 to communicate with the second port 632 and the third port 633 to communicate with the fourth port 634.

[0353] In some embodiments, such as Figure 26 , Figure 27 and Figure 28 As shown, the five-way valve 636 includes a first valve body 601 and a first connecting member 602. The first valve body 601 has a first valve cavity, and a first port 631, a second port 632, a third port 633, a fourth port 634, and a fifth port 635 are all disposed on the first valve body 601. The first connecting member 602 is movably disposed in the first valve cavity and is used to control the connection between the first port 631 and the fifth port 635 and the connection between the second port 632 and the third port 633, or to control the connection between the first port 631 and the second port 632 and the connection between the third port 633 and the fourth port 634. The first valve body 601 has a sixth port 651 and a seventh port 652 on both sides along the moving direction of the first connecting member 602. A pilot valve 637 is used to control the connection between the first port 631 and one of the sixth port 651 and the seventh port 652, and the connection between the third port 633 and the other of the sixth port 651 and the seventh port 652, so as to drive the first connecting member 602 to move.

[0354] Understandably, the pilot valve 637 controls the connection between the first port 631 and one of the sixth port 651 and the seventh port 652, and the connection between the third port 633 and the other of the sixth port 651 and the seventh port 652. This allows the sixth port 651 and the seventh port 652 to achieve a pressure difference based on their connection status. The sixth port 651 and the seventh port 652 are located on opposite sides of the moving direction of the first connecting member 602. Thus, the pressure difference between the sixth port 651 and the seventh port 652 can drive the first connecting member 602 to move, thereby controlling the connection between the first port 631 and the fifth port 635, and the connection between the second port 632 and the third port 633, or controlling the connection between the first port 631 and the second port 632, and the connection between the third port 633 and the fourth port 634, to achieve the switching of the flow path of refrigerant into the five-way valve 636.

[0355] In some embodiments, such as Figure 26 , Figure 27 and Figure 28 As shown, the first connecting member 602 includes a movable member 603 and a communicating member 604. The movable member 603 is movably disposed in the first valve cavity. The movable member 603 includes a connecting shaft 605, a first partition 606 and a second partition 607. The connecting shaft 605 extends along the axial direction of the first valve body 601. The two ends of the connecting shaft 605 are respectively connected to the first partition 606 and the second partition 607. The outer peripheral walls of the first partition 606 and the second partition 607 are sealed to the first valve body 601. When the first partition 606 is spaced apart from the first valve body 601, it forms a first cavity, which communicates with the sixth port 651. When the second partition 607 is spaced apart from the first valve body 601, it forms a second cavity, which communicates with the seventh port 652. A third cavity is defined between the first partition 606 and the second partition 607.

[0356] The first port 631 communicates with the third cavity. The second port 632, the third port 633, the fourth port 634, and the fifth port 635 are always located between the first partition 606 and the second partition 607. The connecting member 604 is connected to the connecting shaft 605. The connecting member 604 includes a connecting part 608 and a stop part 609. The connecting part 608 forms a connecting cavity 653. There are two stop parts 609, which are located at both ends of the connecting part 608 along the axial direction of the connecting shaft 605. The stop parts 609 are sealed to the inner wall of the first valve body 601. The connecting shaft 605 is provided with two through ports 654, which are respectively located on both sides of the connecting member 604.

[0357] The connecting member 604 is movable. When the connecting cavity 653 connects to the second port 632 and the third port 633, the stop part 609 blocks the fourth port 634, and the first port 631 connects to the fifth port 635 through the through port 654. When the connecting cavity 653 connects to the third port 633 and the fourth port 634, the stop part 609 blocks the fifth port 635, and the first port 631 connects to the second port 632 through the through port 654. This allows for the switching of the connecting flow path, thereby enabling the change of the refrigerant flow path within the five-way valve 636. The structure is simple and easy to implement.

[0358] The pilot valve 637 controls the connection between the first port 631 and one of the sixth port 651 and the seventh port 652, and the connection between the third port 633 and the other of the sixth port 651 and the seventh port 652, so that the sixth port 651 and the seventh port 652 can achieve a pressure difference according to the connection status.

[0359] When the pressure at the sixth port 651 is less than the pressure at the seventh port 652, the moving member 603 moves toward the sixth port 651, and the second partition 607 is separated from the first valve body 601 to form a second chamber. At this time, the connecting member 604 moves with the moving member 603 toward the direction closer to the sixth port 651. When the connecting chamber 653 connects the second port 632 and the third port 633, the stop part 609 blocks the fourth port 634, and the first port 631 is connected to the fifth port 635 through the through port 654.

[0360] When the pressure at the sixth port 651 is greater than the pressure at the seventh port 652, the moving member 603 moves toward the seventh port 652. The first partition 606 is separated from the first valve body 601 to form a first cavity. At this time, the connecting member 604 moves with the moving member 603 toward the direction closer to the seventh port 652. The connecting cavity 653 connects the third port 633 and the fourth port 634. The stop part 609 blocks the fifth port 635. The first port 631 is connected to the second port 632 through the through port 654.

[0361] The following describes an air conditioner according to an embodiment of the present invention.

[0362] An air conditioner according to an embodiment of the present invention includes: the air conditioning system 300 described above.

[0363] According to the embodiment of this utility model, the air conditioner, by providing a first port 11, a second port 12, a first connecting hole 13, and a second connecting hole 14 on the main body 1, and by providing a flow-blocking component 2 on the main body 1, and by ensuring that the flow-blocking component 2 only allows refrigerant to flow from the second port 12 to the first port 11, can automatically open and close or cut off the flow, thereby achieving automatic flow guidance of the refrigerant by the flow-blocking component 2, thus changing the flow direction of the refrigerant. In different modes of the air conditioning system 300, automatic switching of different flow paths of the refrigerant within the heat exchanger assembly 200 can be achieved, thereby improving the heat exchange efficiency of the heat exchanger assembly 200, improving the cooling or heating performance of the air conditioning system 300, and improving energy efficiency. Furthermore, no other control structure is required, making the structure simple, easy to implement, and low in cost.

[0364] Other components of the air conditioning system 300 according to embodiments of the present invention, such as the throttling device 64, the compressor 61, and the pilot valve 637, as well as their operation, are known to those skilled in the art and will not be described in detail here.

[0365] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0366] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A flow splitter assembly for a heat exchanger assembly, characterized in that, include: The body portion has a first port, a second port, a first connecting hole, and a second connecting hole; A flow-blocking component is provided on the main body. The first port and the first connecting hole are located on the same side of the flow-blocking component, and the second port and the second connecting hole are located on the same side of the flow-blocking component. The first port and the second port are located on opposite sides of the flow-blocking component. The flow-blocking component only allows refrigerant to flow from the second port side to the first connecting hole side. When the heat exchanger assembly is used as an evaporator, the refrigerant flows into the heat exchanger assembly from the second port, and flows out of the heat exchanger assembly from the first connecting hole and the second connecting hole into the heat exchange tube or heat exchange channel of the heat exchanger assembly. The flow-blocking component is open, and the first port is closed. When the heat exchanger assembly is used as a condenser, the refrigerant flows into the heat exchanger assembly from the first port, and then flows into the heat exchange tube or heat exchange channel of the heat exchanger assembly from the first connecting hole, and then flows out of the heat exchanger assembly from the second connecting hole and the second port in sequence, and the flow-blocking component stops the flow.

2. The shunt component according to claim 1, characterized in that, The number of the first connecting holes is multiple, and when the heat exchanger assembly is used as an evaporator and when the heat exchanger assembly is used as a condenser, the multiple first connecting holes are used to distribute the refrigerant; and / or The plurality of first connecting holes are located above or diagonally above the flow-blocking component, and the plurality of first connecting holes face horizontally, upward or diagonally upward.

3. The shunt assembly according to claim 1 or 2, characterized in that, The main body includes a manifold, which comprises a first manifold and a second manifold. The first port and the first connecting hole are disposed on the first manifold, and the second port and the second connecting hole are disposed on the second manifold. The first manifold and the second manifold are integral components, and the flow-blocking component is disposed inside the first manifold or the second manifold; Alternatively, the first manifold and the second manifold may be separate components, with the flow-blocking component connected between the first manifold and the second manifold.

4. The shunt component according to claim 3, characterized in that, The inner diameter of the first manifold is less than or equal to the inner diameter of the second manifold.

5. The shunt component according to claim 3, characterized in that, The end of the first manifold facing away from the flow-blocking component is open to form the first port; or The first port is located on the peripheral wall of the first manifold; or The first manifold includes a manifold body and a first tee pipe. A first end of the first tee pipe is connected to the flow-blocking component, a second end of the first tee pipe is connected to the manifold body, and a first port is located at the third end of the first tee pipe. The manifold body is provided with the first connecting hole; and / or The end of the second manifold facing away from the flow-blocking component is open to form the second port; or The second port is located on the peripheral wall of the second manifold.

6. The shunt component according to claim 3, characterized in that, The first connecting hole is one or multiple holes spaced apart along the length of the first manifold. And / or, the second connecting hole is one or a plurality of holes spaced apart along the length of the second manifold.

7. The shunt component according to claim 1, characterized in that, Also includes: The first branch pipe is connected to at least one of the first branch pipes at the first connecting hole; And / or, a second branch pipe, at least one of the second branch pipes is connected at the second connecting hole.

8. The shunt assembly according to claim 7, characterized in that, The inner diameter of the second branch pipe is less than or equal to the inner diameter of the first branch pipe; and / or The area of ​​the second connecting hole is smaller than the area of ​​the first connecting hole; and / or The number of the second branch pipes is less than the number of the first branch pipes.

9. The shunt component according to claim 7, characterized in that, In the projection plane perpendicular to the axis of the second manifold, the first branch pipe and the second branch pipe are spaced apart.

10. The shunt assembly according to claim 7, characterized in that, The end of the first branch pipe facing away from the first connecting hole and the end of the second branch pipe facing away from the second connecting hole have the same orientation.

11. The shunt assembly according to claim 7, characterized in that, The diversion assembly further includes a diversion component, and at least one of the first connecting holes is connected to a plurality of the first branch pipes through the diversion component.

12. The shunt assembly according to claim 11, characterized in that, The diversion component is a diversion pipe, one end of which is connected to the first connecting hole, and the other end of which is connected to multiple first branch pipes.

13. The shunt assembly according to claim 11, characterized in that, Along the length of the first manifold, the distance between the first connecting hole of the diverting component and the outlet end of the flow-blocking component is 15mm-300mm; and / or Along the length of the second manifold, the distance between the second connecting hole and the inlet end of the flow-blocking component is 15mm-100mm; and / or Along the length of the second manifold, the distance between the second connecting hole and the inlet end of the flow-blocking component is less than the distance between the first connecting hole connected to the flow-dividing component and the outlet end of the flow-blocking component.

14. The shunt assembly according to claim 7, characterized in that, At least one second branch pipe is connected to the second connecting hole, and the second branch pipe has a bend.

15. The shunt assembly according to claim 14, characterized in that, The second branch pipe has multiple sub-pipes connected in sequence, with two adjacent sub-pipes forming the bend at an angle to each other.

16. The shunt assembly according to claim 15, characterized in that, The plurality of sub-tubes include a first sub-tube and a second sub-tube connected in sequence, one end of the first sub-tube being connected to the second communicating hole, and the first sub-tube and the second sub-tube being perpendicular to each other.

17. The shunt assembly according to claim 16, characterized in that, A first arc-shaped segment is provided between the first sub-tube and the second sub-tube.

18. The shunt assembly according to claim 16, characterized in that, The plurality of sub-tubes further includes a third sub-tube, one end of which is connected to the end of the second sub-tube opposite to the first sub-tube, and the third sub-tube is perpendicular to the second sub-tube. The first sub-tube and the third sub-tube are located on opposite sides of the second sub-tube; Alternatively, the first sub-tube and the third sub-tube are located on the same side of the second sub-tube.

19. The shunt assembly according to claim 18, characterized in that, A second arc-shaped segment is provided between the second sub-tube and the third sub-tube.

20. The shunt assembly according to claim 15, characterized in that, The sub-tube that is directly connected to the second connecting hole among the plurality of sub-tubes is the first sub-tube. In the projection plane perpendicular to the axis of the main body, the angle between the first sub-tube and at least one of the first branch tubes is A, and satisfies: 0°<A°≤180°.

21. The shunt assembly according to claim 1 or 2, characterized in that, The main body includes a connecting pipe and a distributor. The flow-blocking component is disposed on the connecting pipe. The second port and the second connecting hole are connected to the connecting pipe. At least one of the second port and the second connecting hole is connected to one end of the connecting pipe. The distributor has a main interface and a plurality of distributing holes. The main interface is connected to the other end of the connecting pipe. At least some of the distributing holes are the first connecting holes.

22. The shunt assembly according to claim 21, characterized in that, There are multiple first connecting holes, and each of the distribution holes is connected to a first branch pipe. The first port is located on the connecting pipe between the distributor and the flow-blocking component.

23. The shunt assembly according to claim 21, characterized in that, The number of first connecting holes is multiple, the number of distribution holes is N, N-1 of the distribution holes are respectively connected to a first branch pipe, and the remaining distribution hole forms the first port.

24. The shunt assembly according to claim 21, characterized in that, Along the length of the connecting pipe, the distance between the main inlet and the outlet end of the flow-blocking component is 15mm-500mm; and / or Along the length of the connecting pipe, the distance between the second connecting hole and the inlet end of the flow-blocking component is 15mm-100mm; and / or Along the length of the connecting pipe, the distance between the second connecting hole and the inlet end of the flow-blocking component is less than the distance between the main interface and the outlet end of the flow-blocking component.

25. The shunt assembly according to claim 21, characterized in that, At least one second branch pipe is connected to the second connecting hole, and the second branch pipe has a bend.

26. The shunt assembly according to claim 1 or 2, characterized in that, The first port is formed by opening one end of the main body on the side of the flow-blocking component away from the second port along its length. Alternatively, the first port may be located on the peripheral wall of the main body.

27. The shunt assembly according to claim 1 or 2, characterized in that, Also includes: An air intake pipe, one end of which is connected to the first port.

28. The shunt assembly according to claim 27, characterized in that, The intake pipe is a U-shaped pipe, a V-shaped pipe, or an inverted U-shaped pipe.

29. The shunt assembly according to claim 1 or 2, characterized in that, The second port is formed by opening one end of the main body on the side of the flow-blocking component away from the first port along its length. Alternatively, the second port may be located on the peripheral wall of the main body.

30. The shunt assembly according to claim 1 or 2, characterized in that, Also includes: An inlet / outlet pipe, one end of which is connected to the second port.

31. The shunt assembly according to claim 30, characterized in that, A first branch pipe is connected to the first connecting hole. In the projection plane perpendicular to the axis of the main body, the inlet and outlet pipe has at least one radial extension that extends obliquely along the radial direction of the main body. The angle between the radial extension closest to the second port and the first branch pipe is B and satisfies: 15°≤B°≤225°.

32. The shunt assembly according to claim 30, characterized in that, The angle between the tangent of the axis of the inlet / outlet pipe connected to the second port and the axis of the main body is C, and satisfies: 0°≤C°≤135°.

33. The shunt component according to claim 1, characterized in that, The main body includes a flow divider located at one end of the main body. The flow divider has a first passage, a second passage, and a third passage. One end of the first passage, one end of the second passage, and one end of the third passage are interconnected. The other end of the first passage is connected to the inlet end of the flow-blocking component. The other end of the second passage is open to form a second port, and the other end of the third passage is open to form a second connecting hole. Wherein, the resistance to the fluid flowing from the second passage to the first passage is the first resistance, and the resistance to the fluid flowing from the second passage to the third passage is the second resistance, and the second resistance is greater than the first resistance; Alternatively, the flow rate of fluid from the second passage to the first passage is the first flow rate, and the flow rate of fluid from the second passage to the third passage is the second flow rate, wherein the first flow rate is greater than the second flow rate.

34. The shunt assembly according to claim 33, characterized in that, The distributor has a splitting cavity, and one end of the first passage, one end of the second passage, and one end of the third passage are all connected to the splitting cavity.

35. The shunt assembly according to claim 33, characterized in that, The axes of the first path, the second path, and the third path extend in a straight line.

36. The shunt assembly according to claim 33, characterized in that, The second and third paths are located on the same side of the splitter, while the first and second paths are located on opposite sides of the splitter; and / or The openings of the second passage and the third passage face the same side, while the openings of the second passage and the first passage face opposite sides.

37. The shunt assembly according to claim 36, characterized in that, The axis of the second path is parallel to the axis of the third path, while the axis of the first path does not coincide with the axis of the second path.

38. The shunt assembly according to claim 37, characterized in that, The axis of the first path is parallel to the axis of the second path and is located between the axis of the second path and the axis of the third path.

39. The shunt assembly according to claim 36, characterized in that, There are multiple third paths, which are spaced apart along the circumferential direction of the second path, and the axis of the first path coincides with the axis of the second path.

40. The shunt assembly according to claim 39, characterized in that, The axis of the second path is parallel to the axis of the third path.

41. The shunt assembly according to claim 33, characterized in that, The axes of the first and second pathways coincide, and the axis of the third pathway is perpendicular to the axis of the second pathway; or The axes of the first path and the second path coincide, and the angle between the axis of the third path and the axis of the second path is smaller than the angle between the axis of the third path and the axis of the first path.

42. The shunt assembly according to any one of claims 33-41, characterized in that, The inner diameter of the second passage is D2, and the inner diameter of the third passage is D3, satisfying: D2 ≥ D3; and / or The inner diameter of the first passage is D1, and the inner diameter of the third passage is D3, satisfying: D1 > D3; and / or The open end of the second passage is connected to an inlet / outlet pipe, and the open end of the third passage is connected to a second branch pipe. The inner diameter of the inlet / outlet pipe is greater than or equal to the inner diameter of the second branch pipe. and / or The open end of the first passage is connected to a second manifold or connecting pipe, and the inner diameter of the second manifold or the connecting pipe is larger than the inner diameter of the second branch pipe. and / or The open end of the first passage is connected to a second manifold or a connecting pipe, and the open end of the second passage is connected to an inlet / outlet pipe. The inner diameter of the second manifold or the connecting pipe is greater than or equal to the inner diameter of the inlet / outlet pipe.

43. The shunt assembly according to claim 42, characterized in that, The open end of the third passage is connected to a second branch pipe, the minimum cross-sectional inner diameter of the second branch pipe is D0, and satisfies: D0≤D3.

44. The shunt assembly according to any one of claims 33-41, characterized in that, The inner diameter of the third passage is D3, and it satisfies the condition: D3≥3mm.

45. The shunt assembly according to any one of claims 1 or 2, characterized in that, The flow-blocking component is a one-way valve, a solenoid valve, or a baffle.

46. ​​A heat exchanger assembly, characterized in that, include: A heat exchanger body having multiple heat exchange tubes forming multiple flow paths; A flow collector assembly is disposed on one side of the heat exchanger body and communicates with multiple flow paths, and the flow collector assembly has a third port; According to any one of claims 1-45, the first connecting hole is connected to at least one end of the flow path away from the current collecting component, and the second connecting hole is connected to at least one end of the flow path away from the current collecting component.

47. The heat exchanger assembly according to claim 46, characterized in that, When the heat exchanger assembly is used as an evaporator, the refrigerant flows into the heat exchanger assembly from the second port, and flows into the heat exchange tube of the heat exchanger assembly from the first connecting hole and the second connecting hole, and then flows out of the heat exchanger assembly from the third port. The flow-blocking component is open, and the first port is closed. When the heat exchanger assembly is used as a condenser, the refrigerant flows into the heat exchanger assembly from the first port, and then flows into the heat exchange tube of the heat exchanger assembly from the first connecting hole, and then flows out of the heat exchanger assembly from the second connecting hole and the second port in sequence. The flow-blocking component and the third port are both shut off.

48. The heat exchanger assembly according to claim 46, characterized in that, The current collection component includes: The main pipe has a third port; A branch pipe, one end of which is connected to the main pipe, the inner diameter of the main pipe being greater than or equal to the inner diameter of the branch pipe, and there are multiple branch pipes, with the ends of the multiple branch pipes facing away from the main pipe respectively connected to multiple flow paths.

49. The heat exchanger assembly according to claim 48, characterized in that, The branch pipe is connected to the main pipe via a second tee pipe.

50. The heat exchanger assembly according to claim 48, characterized in that, The current collection component also includes: A manifold, one end of which is connected to the main pipe and the other end of which is connected to multiple branch pipes.

51. The heat exchanger assembly according to claim 48, characterized in that, The plurality of branch pipes include at least one third branch pipe and at least one fourth branch pipe, the third branch pipe and the fourth branch pipe being arranged at intervals along the length of the main pipe, and the current collection assembly having a first state and a second state. In the first state, the refrigerant enters the main pipe from the third branch pipe and flows out from the fourth branch pipe, while the third port is shut off; In the second state, refrigerant enters the main pipe from the third branch pipe and the fourth branch pipe, and flows out from the third port.

52. The heat exchanger assembly according to claim 51, characterized in that, On a projection plane perpendicular to the axis of the main pipe, the third branch pipe and the fourth branch pipe are spaced apart or at an angle.

53. The heat exchanger assembly according to claim 48, characterized in that, One end of the main pipe along its length is open to form the third port, and the third port is connected to an extension pipe.

54. The heat exchanger assembly according to claim 53, characterized in that, The extension tube is U-shaped or inverted U-shaped.

55. The heat exchanger assembly according to claim 48, characterized in that, The plurality of heat exchange tubes form at least one first flow path and at least one second flow path. The plurality of branch tubes include at least one third branch tube and at least one fourth branch tube. The third branch tube is connected to the first flow path, and the fourth branch tube is connected to the second flow path. The first connecting hole is connected to at least one end of the first flow path away from the third branch tube, and the second connecting hole is connected to at least one end of the second flow path away from the fourth branch tube.

56. The heat exchanger assembly according to claim 55, characterized in that, The heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body. Both the first flow path and the second flow path include multiple rows of the heat exchange tubes. The heat exchange tubes in the first flow path connected to the first connecting hole and the heat exchange tubes in the second flow path connected to the second connecting hole are located on opposite sides of the thickness direction of the heat exchanger body or in different rows.

57. The heat exchanger assembly according to claim 56, characterized in that, The heat exchange tubes of the first flow path connected to the first connecting hole are located in a row on the leeward side of the heat exchanger body, and the heat exchange tubes of the second flow path connected to the second connecting hole are located in a row on the windward side of the heat exchanger body.

58. The heat exchanger assembly according to claim 55, characterized in that, The heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body. Both the first flow path and the second flow path include multiple rows of the heat exchange tubes. The heat exchange tubes in the first flow path connected to the third branch pipe and the heat exchange tubes in the second flow path connected to the fourth branch pipe are located on opposite sides of the thickness direction of the heat exchanger body or in different rows.

59. The heat exchanger assembly according to claim 58, characterized in that, The heat exchange tubes of the first flow path connected to the third branch pipe are located in a row on the windward side of the heat exchanger body, and the heat exchange tubes of the second flow path connected to the fourth branch pipe are located in a row on the leeward side of the heat exchanger body.

60. The heat exchanger assembly according to any one of claims 55-59, characterized in that, The heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body. The first flow path includes a row of windward heat exchange tubes located on the windward side of the heat exchanger body and a row of leeward heat exchange tubes located on the leeward side of the heat exchanger body. When the heat exchanger assembly is used as a condenser and as an evaporator, the refrigerant flowing into the first flow path first flows through the leeward heat exchange tubes and then through the windward heat exchange tubes. And / or, the heat exchange tubes are arranged in multiple rows along the thickness direction of the heat exchanger body, and the second flow path includes a row of windward heat exchange tubes located on the windward side of the heat exchanger body and a row of leeward heat exchange tubes located on the leeward side of the heat exchanger body. When the heat exchanger assembly is used as an evaporator, the refrigerant flowing into the second flow path first flows through the windward heat exchange tubes and then through the leeward heat exchange tubes. When the heat exchanger assembly is used as a condenser, the refrigerant flowing into the second flow path first flows through the leeward heat exchange tubes and then through the windward heat exchange tubes.

61. The heat exchanger assembly according to claim 60, characterized in that, The first flow path is located above the second flow path; and / or The air volume or average wind speed flowing through the first flow path is greater than the air volume or average wind speed flowing through the second flow path.

62. The heat exchanger assembly according to claim 48, characterized in that, The flow collection assembly and the flow splitting assembly are located on the same side along the length of the heat exchanger body.

63. An air conditioning system, characterized in that, include: The compressor has an exhaust port and an exhaust port; Indoor heat exchanger; The heat exchanger assembly according to any one of claims 46-62, wherein one end of the indoor heat exchanger is connected to the second port; A reversing assembly having a first port, a second port, a third port, a fourth port, and a fifth port, wherein the first port is connected to the exhaust port, the third port is connected to the return port, the second port is connected to the other end of the indoor heat exchanger, the fourth port is connected to the third port, and the fifth port is connected to the first port; the reversing assembly has a first switching state and a second switching state. When the commutation component is in the first switching state, the first port is connected to the fifth port, the second port is connected to the third port, and the fourth port is cut off; When the commutation component is in the second switching state, the first port is connected to the second port, the third port is connected to the fourth port, and the fifth port is cut off.

64. An air conditioner, characterized in that, Including the air conditioning system according to claim 63.

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