Heat exchanger and air conditioning system

Abstract

The utility model provides a kind of heat exchanger and air conditioning system, including shunt part, multiple from top to bottom arrangement heat exchange pipe and injection head, shunt part has refrigerant inlet, shunt passage and reflux passage, refrigerant inlet and the bottom of shunt passage are communicated, each heat exchange pipe is communicated with shunt passage, the upper portion of reflux passage and the upper portion of shunt passage are communicated, the lower portion of reflux passage and the lower portion of shunt passage are communicated;At least a part of injection head is inserted into shunt passage from refrigerant inlet, injection head has injection hole, injection hole sprays refrigerant towards the upper portion of shunt passage;Wherein, under the action of injection pressure, the gas phase refrigerant gathered in the upper portion of shunt passage is refluxed to the lower portion of shunt passage by reflux passage.This scheme overcomes the problem of uneven liquid supply in the upper and lower passages caused by gravity stratification in the existing header.And the structure of shunt part is simple, and the manufacturing cost is low.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, and more specifically, to a heat exchanger and an air conditioning system. Background Technology

[0002] Microchannel heat exchangers are widely used in air conditioning, heat pumps, and refrigeration equipment due to their compact structure, high heat transfer efficiency, and low refrigerant charge. The operating efficiency of a microchannel heat exchanger largely depends on the uniformity of refrigerant distribution within the manifold and each flat tube. However, in related technologies, when the gas-liquid two-phase refrigerant enters the microchannel heat exchanger (used as an evaporator), gravity and other factors cause the gas and liquid phases to separate in the manifold, resulting in an uneven distribution of the refrigerant (gas phase on top, liquid phase deposited at the bottom). This prevents the refrigerant from entering the heat exchange tubes in a uniformly mixed gas-liquid two-phase state for heat exchange, ultimately leading to low heat exchange efficiency in the microchannel heat exchanger. Utility Model Content

[0003] This invention provides a heat exchanger and an air conditioning system to solve the above-mentioned problems.

[0004] To address the aforementioned problems, according to one aspect of this utility model, a heat exchanger is provided, comprising a flow divider and a plurality of heat exchange tubes arranged from top to bottom. The flow divider has a refrigerant inlet, a flow divider channel, and a return channel. The refrigerant inlet and the bottom of the flow divider channel are connected. Each heat exchange tube is connected to the flow divider channel. The upper part of the return channel is connected to the upper part of the flow divider channel. At least a portion of a spray head is inserted into the flow divider channel from the refrigerant inlet. The spray head has a spray hole that sprays refrigerant toward the upper part of the flow divider channel. Under the action of the spray pressure, the gaseous refrigerant accumulated in the upper part of the flow divider channel flows back to the lower part of the flow divider channel through the return channel.

[0005] Furthermore, the upper part of the return channel is connected to the upper part of the diversion channel via the upper guide channel, and the lower part of the return channel is connected to the lower part of the diversion channel via the lower guide channel. The radius of the upper guide channel is R. k1 The radius of the lower guide channel is R. k2 Where 1≤R k1 / R k2 .

[0006] Furthermore, the upper part of the return channel is connected to the upper part of the branch channel via the upper guide channel, and the lower part of the return channel is connected to the lower part of the branch channel via the lower guide channel. The lower guide channel is located above the refrigerant inlet. The distance between the centerline of the upper guide channel and the bottom surface of the branch section is H1, the distance between the centerline of the lower guide channel and the bottom surface of the branch section is H2, and the distance between the bottom and top surfaces of the branch section is H. j Where 0.6 ≤ H1 / H j Hj -H1≤H2,3≤H1 / H2。

[0007] Furthermore, the flow area of ​​the diversion channel is S1, and the flow area of ​​the return channel is S2, where S2 = (0.2~0.5)S1.

[0008] Furthermore, the heat exchanger also includes an adapter sleeve and an inlet pipe. One end of the adapter sleeve is connected to one end of the spray head, and the adapter sleeve and the spray head are in communication. The outer diameter of the adapter sleeve is larger than the outer diameter of the spray head. The adapter sleeve and the flow distribution section are fixedly connected. The adapter sleeve and the spray head are an integral structure, or the adapter sleeve and the spray head are separate structures. One end of the inlet pipe is inserted into the adapter sleeve and fixedly connected to the adapter sleeve.

[0009] Furthermore, in the direction in which the nozzle is inserted into the diversion section, the size of the diversion section is W2, the distance from the center of the nozzle to the adapter sleeve is Lp, the diameter of the nozzle is Rp, and the inner diameter of the input pipe is Dg, where Lp=(0.45~0.55)×W2, 2≤Dg / Rp≤6.5.

[0010] Furthermore, the flow distribution section also includes a cavity plate, which is located between multiple heat exchange tubes and flow distribution channels; the cavity plate has multiple flow distribution cavities spaced apart from top to bottom, one side of each flow distribution cavity is connected to a flow distribution channel, and the other side of each flow distribution cavity is connected to at least one heat exchange tube.

[0011] Furthermore, the flow distribution section also includes a positioning plate, one side wall of the flow distribution channel is the flow distribution plate, and the cavity plate is located between the positioning plate and the flow distribution plate; the positioning plate has multiple waist-shaped positioning holes, the heat exchange tube is a flat tube with a constricted section, each constricted section of the flat tube is inserted into a corresponding positioning hole, and the constricted section is welded to the positioning plate, each constricted section is connected to a corresponding flow distribution cavity; the flow distribution plate has multiple through flow distribution holes, each flow distribution hole is connected to a corresponding flow distribution cavity, so that the flow distribution cavity and the flow distribution channel are connected.

[0012] Furthermore, the width of the narrowed section is Ws, the thickness of the narrowed section is Ds, the length of the narrowed section is Ls, and the fillet radius of the narrowed section is Rs; the thickness of the positioning plate is Dd, and the length of the positioning hole is W. d The width of the positioning hole is H d The fillet radius of the positioning hole is R. d The area of ​​the positioning hole is A. d The thickness of the cavity plate is Dq, the flow area of ​​the branch cavity is Aq, and the minimum distance between the edge of the branch cavity and the edge of the cavity plate is Mq; the radius of the branch orifice is Rj; wherein, the heat exchanger satisfies at least one of the following dimensional relationships:

[0013] W d –Ws≤0.15;

[0014] Hd –Ds≤0.1;

[0015] Dd = Dq;

[0016] Ls≤Dd+Dq≤10;

[0017] R d -Rs≤0.06;

[0018] Mq≥1.3;

[0019] A d / Aq≥0.1;

[0020] Rj 2 / Aq≤0.4.

[0021] Furthermore, the diversion section includes a manifold, a return pipe, an upper connecting block, and a lower connecting block. The manifold has a diversion channel, and the return pipe has a return channel. The upper part of the manifold is connected to the upper part of the return pipe through the upper connecting block, and the lower part of the manifold is connected to the lower part of the return pipe through the lower connecting block. The upper connecting block has an upper guide channel that connects the return channel and the diversion channel, and the lower connecting block has a lower guide channel that connects the return channel and the diversion channel.

[0022] Furthermore, the flow distribution section also includes a cavity plate and a positioning plate. The flow collection pipe, cavity plate, and positioning plate are connected in sequence. The cavity plate has multiple flow distribution cavities spaced apart from top to bottom. One side of each flow distribution cavity is connected to a flow distribution channel, and the other side of each flow distribution cavity is connected to at least one heat exchange tube. The positioning plate has multiple positioning holes, and one end of each heat exchange tube is inserted into a corresponding positioning hole.

[0023] Furthermore, the heat exchange tube, positioning plate, cavity plate, manifold, connecting block and return pipe are welded together in sequence. The positioning plate, cavity plate and manifold are all made of aluminum alloy. At least one surface of the positioning plate, cavity plate and manifold has a welding material layer. The manifold is a round tube, square tube or D-shaped tube. The return pipe is a round tube, square tube or D-shaped tube.

[0024] Furthermore, the diversion section also includes an end cap, which covers the end opening of the manifold from the outside; or the end cap is embedded in the end opening of the manifold; or the end cap passes through the manifold, the cavity plate and the positioning plate in sequence, and the end cap blocks the end opening of the manifold.

[0025] Furthermore, the positioning plate, cavity plate, and manifold are all provided with connecting holes, and the diversion part also includes rivets. The rivets pass through the connecting holes on the positioning plate, cavity plate, and manifold to fix the positioning plate, cavity plate, and manifold; or, the edge of the positioning plate has a first positioning protrusion, and the edges of the cavity plate and manifold both have a first positioning groove. The first positioning protrusion is pressed into the first positioning groove of the cavity plate and manifold to fix the positioning plate, cavity plate, and manifold; or, the edge of the cavity plate has a second positioning protrusion, and the edge of the positioning plate has a second positioning groove. The second positioning protrusion is pressed into the second positioning groove to fix the positioning plate and cavity plate.

[0026] Alternatively, the flow distribution section includes a manifold and a baffle, with the baffle fixed inside the manifold. The flow distribution channel and the return channel are located on opposite sides of the baffle, and one end of the heat exchange tube is inserted into the manifold.

[0027] Furthermore, the flow distribution section also includes a flow distribution plate and a cavity plate, both of which are fixed inside the manifold. The flow distribution channel is located between the flow distribution plate and the baffle. One side wall of the manifold is a positioning plate, and the cavity plate is located between the positioning plate and the flow distribution plate. The cavity plate has multiple flow distribution cavities spaced apart from top to bottom. One side of each flow distribution cavity is connected to the flow distribution channel, and the other side of each flow distribution cavity is connected to at least one heat exchange tube. The positioning plate has multiple positioning holes, and one end of each heat exchange tube is inserted into a corresponding positioning hole.

[0028] Furthermore, the inner wall of the manifold has two opposing first inner grooves and two opposing second inner grooves, the two opposing sides of the baffle are respectively inserted into the two first inner grooves, and the two opposing sides of the diverter are respectively inserted into the two second inner grooves.

[0029] Alternatively, the manifold is an extruded profile; the manifold is an integral structure, or the manifold includes a first profile with an opening on one side and a second profile with an opening on the other side, the opening of the first profile has two first flanges on opposite sides, the opening of the second profile has two second flanges on opposite sides, the opening of the first profile and the opening of the second profile are arranged opposite to each other, and the two first flanges and the two second flanges are connected in a one-to-one correspondence.

[0030] According to another aspect of the present invention, an air conditioning system is provided, which includes the heat exchanger described above.

[0031] In this scheme, interconnected distribution channels and return channels are set up within the distribution section, connecting the upper part of the distribution channel with the upper part of the return channel, and simultaneously connecting the lower part of the distribution channel with the lower part of the return channel. A nozzle located at the lower part of the distribution channel sprays refrigerant towards the upper part of the distribution channel. The gaseous refrigerant, due to its lower density, accumulates in the upper part of the distribution channel, while the liquid refrigerant, due to its higher density, accumulates in the lower part. The pressure of the refrigerant sprayed from the nozzle is greater than that of the gaseous refrigerant accumulated in the upper part of the distribution channel. Driven by this pressure, this portion of the refrigerant flows back to the lower part of the distribution channel via the return channel. The returning gaseous refrigerant, driven by the refrigerant injected into the lower part of the distribution channel, flows upward and mixes with the injected refrigerant, thus achieving a re-homogenization of the gas and liquid phases within the distribution channel. This overcomes the problem of uneven liquid supply between the upper and lower channels caused by gravity stratification in existing manifolds. Furthermore, it ensures that the refrigerant entering under different dryness conditions maintains a relatively balanced gas-liquid ratio in the distribution channel, avoiding a significant decrease in distribution performance due to fluctuations in operating conditions. This improves the heat exchanger's adaptability and stability, and also enhances the heat exchange efficiency of the microchannel heat exchanger. In addition, the simple structure of the distribution section, which does not rely on complex multi-stage distribution heads or additional distribution elements, reduces the number of weld points and flow resistance, resulting in low manufacturing costs and contributing to improved overall reliability of the heat exchanger. Attached Figure Description

[0032] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0033] Figure 1 A schematic diagram of the structure of a heat exchanger provided in an embodiment of the present invention is shown;

[0034] Figure 2 It shows Figure 1 Schematic diagram of the middle flow divider;

[0035] Figure 3 It shows Figure 2 Dimensioning diagram of the upper and lower guide channels;

[0036] Figure 4 It shows Figure 2 A schematic diagram showing the height of the upper and lower guide channels in the diagram;

[0037] Figure 5 It shows Figure 2 Dimensional annotations of some structures in the diagram;

[0038] Figure 6 It shows Figure 2 The dimensioning diagram of the nozzle;

[0039] Figure 7 It shows Figure 2 A partial structural diagram;

[0040] Figure 8 It shows Figure 2 Dimensioning diagram of the constricted section of the heat exchanger tube;

[0041] Figure 9 It shows Figure 2 Dimensional diagram of the cavity plate and positioning plate in the middle;

[0042] Figure 10 A schematic diagram of the structure of a heat exchanger provided in another embodiment of the present invention is shown;

[0043] Figure 11 A schematic diagram of the structure of a heat exchanger provided in another embodiment of the present invention is shown;

[0044] Figure 12 A schematic diagram of the structure of a heat exchanger provided in another embodiment of the present invention is shown;

[0045] Figure 13 It shows Figure 12 Schematic diagram of the middle flow divider;

[0046] Figure 14 It shows Figure 13 Schematic diagram of the central flow tube;

[0047] Figure 15 A schematic diagram of the structure of a heat exchanger provided in another embodiment of the present invention is shown;

[0048] Figure 16 A schematic diagram of the structure of a heat exchanger provided in another embodiment of the present invention is shown.

[0049] The above figures include the following reference numerals:

[0050] 10. Flow divider; 11. Refrigerant inlet; 12. Flow divider channel; 13. Return channel; 14. Upper guide channel; 15. Lower guide channel; 16. Cavity plate; 161. Flow divider cavity; 17. Positioning plate; 171. Positioning hole; 18. Flow divider plate; 181. Flow divider hole; 19. End cap; 20. Heat exchanger tube; 21. Narrow section; 30. Injector head; 31. Injection hole; 40. Adapter sleeve; 50. Input Pipe; 61. Combustion pipe; 62. Return pipe; 63. Upper connecting block; 64. Lower connecting block; 71. Connecting hole; 72. Rivet; 73. First positioning protrusion; 74. First positioning groove; 75. Second positioning protrusion; 76. Second positioning groove; 80. Baffle; 81. First inner groove; 82. Second inner groove; 83. First profile; 84. Second profile; 85. First flange; 86. Second flange. Detailed Implementation

[0051] The technical solutions in at least one embodiment will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. The following description of at least one embodiment is merely illustrative and is not intended to limit this application or its applications. Other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are all within the scope of protection of this application.

[0052] like Figures 1 to 16 As shown, an embodiment of the present invention provides a heat exchanger, including a flow divider 10 and at least two heat exchange tubes 20 arranged from top to bottom. The flow divider 10 has a refrigerant inlet 11, a flow divider channel 12 and a return channel 13. The refrigerant inlet 11 and the bottom of the flow divider channel 12 are connected. Each heat exchange tube 20 is connected to the flow divider channel 12. The upper part of the return channel 13 is connected to the upper part of the flow divider channel 12, and the lower part of the return channel 13 is connected to the lower part of the flow divider channel 12. The return channel 13 is used to return the refrigerant accumulated in the upper part of the flow divider channel 12 to the lower part of the flow divider channel 12.

[0053] In this embodiment, by providing a diversion channel 12 and a return channel 13 that are interconnected within the diversion section 10, the upper part of the diversion channel 12 is connected to the upper part of the return channel 13, and the lower part of the diversion channel 12 is connected to the lower part of the return channel 13. The nozzle 30 located at the lower part of the distribution channel 12 sprays refrigerant towards the upper part of the distribution channel 12. The gaseous refrigerant, due to its lower density, accumulates in the upper part of the distribution channel 12, while the liquid refrigerant, due to its higher density, accumulates in the lower part of the distribution channel 12. The pressure of the refrigerant sprayed from the nozzle 30 is greater than the pressure of the gaseous refrigerant accumulated in the upper part of the distribution channel 12. Driven by the pressure, this part of the refrigerant flows back to the lower part of the distribution channel 12 via the return channel 13. The returning gaseous refrigerant flows upward under the influence of the refrigerant sprayed into the lower part of the distribution channel 12 and mixes with the sprayed refrigerant, thereby achieving a re-homogenization of the gas and liquid phases in the distribution channel 12. This overcomes the problem of uneven liquid supply in the upper and lower channels caused by gravity stratification in the existing manifold 61. Furthermore, it ensures that the refrigerant entering under different dryness conditions maintains a relatively balanced gas-liquid ratio in the distribution channel 12, avoiding a significant decrease in distribution performance due to fluctuations in operating conditions. This improves the heat exchanger's adaptability and stability, and also enhances the heat exchange efficiency of the microchannel heat exchanger. In addition, the distribution section 10 has a simple structure, does not rely on complex multi-stage distribution heads or additional distribution elements, reduces the number of weld points and flow resistance, lowers manufacturing costs, and contributes to improving the overall reliability of the heat exchanger.

[0054] like Figure 2 and Figure 3As shown, the upper part of the return channel 13 is connected to the upper part of the diversion channel 12 via the upper guide channel 14, and the lower part of the return channel 13 is connected to the lower part of the diversion channel 12 via the lower guide channel 15. The radius of the upper guide channel 14 is R. k1 The radius of the lower guide channel 15 is R. k2 Where 1≤R k1 / R k2 .

[0055] In this embodiment, an upper guide channel 14 and a lower guide channel 15 are provided to connect the return channel 13 and the branch channel 12 at their upper and lower parts, respectively, thereby guiding the circulation path of the gas-liquid two-phase refrigerant between the branch channel 12 and the return channel 13. The upper guide channel 14 allows the gaseous refrigerant enriched in the upper part of the branch channel 12 to enter the return channel 13, preventing the gaseous refrigerant from directly entering the heat exchange tube 20 within the branch channel 12. The lower guide channel 15 ensures that the gaseous refrigerant can smoothly flow back from the return channel 13 to the lower part of the branch channel 12, fully mixing with the liquid phase enriched in the lower part, further achieving homogenization of the gas and liquid phases. Furthermore, the dimension between the radii of the upper guide channel 14 and the lower guide channel 15 is set to 1 ≤ R. k1 / R k2 This allows the gaseous refrigerant to enter the return channel 13 to the maximum extent possible, preventing the gaseous refrigerant from directly entering the heat exchange tube 20.

[0056] like Figure 2 and Figure 4 As shown, the upper part of the return channel 13 is connected to the upper part of the branch channel 12 via the upper guide channel 14, and the lower part of the return channel 13 is connected to the lower part of the branch channel 12 via the lower guide channel 15. The lower guide channel 15 is located above the refrigerant inlet 11. The distance between the centerline of the upper guide channel 14 and the bottom surface of the branch section 10 is H1, the distance between the centerline of the lower guide channel 15 and the bottom surface of the branch section 10 is H2, and the distance between the bottom surface and the top surface of the branch section 10 is H. j Where 0.6 ≤ H1 / H j H j -H1≤H2,3≤H1 / H2。

[0057] In this embodiment, the lower guide channel 15 is positioned above the refrigerant inlet 11, allowing the gaseous refrigerant flowing back from the lower part of the return channel 13 to the diversion channel 12 to be dispersed again into the liquid refrigerant. This avoids flow disturbance and uneven distribution near the inlet, further achieving homogenization of the gas and liquid phases. Furthermore, by rationally setting the height spacing between the upper guide channel 14 and the lower guide channel 15, the upper guide channel 14 is positioned in a relatively high area of ​​the diversion section 10, allowing the gaseous refrigerant accumulated at the top to smoothly enter the return channel 13. The lower guide channel 15 is positioned at an appropriate height, ensuring that the gaseous phase guided back through the return channel 13 can fully mix with the liquid phase in the middle to lower part of the diversion channel 12, preventing excessive liquid phase enrichment due to an excessively low position and gas phase re-stratification due to an excessively high position, thus improving the uniformity of gas-liquid mixing.

[0058] In some embodiments, the flow area of ​​the diversion channel 12 is S1, and the flow area of ​​the return channel 13 is S2, where S2 = (0.2~0.5)S1. The return channel 13 needs to have sufficient flow area to allow the gaseous refrigerant to pass through smoothly. If S2 < 0.2S1, it will lead to excessive refrigerant flow resistance, affecting the return flow of gaseous refrigerant and thus affecting the gas-liquid mixing effect. If S2 > 0.5S1, it will encroach on the space of the diversion channel 12, which may lead to an abnormal increase in the refrigerant velocity within the diversion channel 12, increasing unnecessary pressure drop and affecting the uniform distribution of refrigerant within the multiple heat exchange tubes 20. Therefore, setting the flow area of ​​the return channel 13 and the flow area of ​​the branch channel 12 to the above relationship does not affect the uniform distribution of refrigerant in the multiple heat exchange tubes 20, and realizes the Venturi effect, that is, using the kinetic energy of the refrigerant injected in the branch channel 12, the return channel 13 is under negative pressure relative to the branch channel 12, so that the gas phase refrigerant can flow back smoothly and be remixed, avoiding gas-liquid stratification.

[0059] like Figure 2 As shown, by setting the injection head 30 and pointing the injection hole 31 towards the top of the distribution channel 12, the incoming refrigerant is guided to the upper region of the distribution channel 12 under the action of the injection, avoiding direct impact of high-speed gas-liquid two-phase refrigerant on the bottom or wall of the distribution channel 12, thereby preventing splashing or retention of the gas-liquid two-phase refrigerant in the flat tube at the refrigerant inlet 11. Furthermore, it can carry some droplets to the upper region, reducing the excessive accumulation of the gas phase in the upper part and promoting mixing of the gas and liquid phases within the distribution channel 12.

[0060] like Figure 2As shown, the heat exchanger also includes an adapter sleeve 40 and an inlet pipe 50. One end of the adapter sleeve 40 is connected to one end of the spray head 30, and the adapter sleeve 40 and the spray head 30 are in communication. The outer diameter of the adapter sleeve 40 is larger than the outer diameter of the spray head 30. The adapter sleeve 40 and the flow divider 10 are fixedly connected. The adapter sleeve 40 and the spray head 30 are an integral structure, or the adapter sleeve 40 and the spray head 30 are separate structures. One end of the inlet pipe 50 is inserted into the adapter sleeve 40 and fixedly connected to the adapter sleeve 40.

[0061] In this embodiment, the adapter sleeve 40 serves as an intermediate transition component between the injector head 30 and the inlet pipe 50. It not only provides support and positioning, but also, because its outer diameter is larger than that of the injector head 30 and it is fixedly connected to the flow divider 10, the injector head 30 can maintain a precise axial position and injection direction within the flow divider channel 12. This prevents displacement of the injector head 30 due to vibration or refrigerant impact during operation, thus ensuring the injection effect. Furthermore, the adapter sleeve 40 and the injector head 30 can be integrated to reduce connection points, leakage risk, and processing complexity, or they can be separate components for easier assembly, disassembly, and maintenance, giving the heat exchanger in this application greater flexibility and adaptability. The insertion and fixed connection of one end of the inlet pipe 50 into the adapter sleeve 40 ensures the sealing and flow continuity between the external refrigerant input and the internal injector head 30, preventing refrigerant leakage or unstable flow.

[0062] like Figure 5 and Figure 6 As shown, in the direction in which the nozzle 30 is inserted into the diversion section 10, the size of the diversion section 10 is W2, the distance from the center of the nozzle 31 to the adapter sleeve 40 is Lp, the diameter of the nozzle 31 is Rp, and the inner diameter of the input pipe 50 is Dg, where Lp=(0.45~0.55)×W2, 2≤Dg / Rp≤6.5.

[0063] manual PN327203DUNANRG

[0064] In this embodiment, the center distance between the injection hole 31 and the adapter sleeve 40 is defined as Lp = (0.45~0.55) × W2. This ensures that the injection hole 31 is located in the middle region of the distribution channel 12, preventing the injection hole 31 from being too close to the inlet and causing insufficient diffusion of the refrigerant in the distribution channel 12. Simultaneously, the ratio of the inner diameter Dg of the input pipe 50 to the diameter Rp of the injection hole 31 is limited to the range of 2 ≤ Dg / Rp ≤ 6.5. If the ratio is too small, the amount of refrigerant entering the injection head 30 is insufficient, resulting in inadequate refrigerant injection velocity and difficulty in overcoming the gas-liquid stratification effect. Conversely, if the ratio is too large, the jet flow becomes too concentrated, easily causing localized impacts and uneven distribution. This configuration in this application achieves a balance between the two, ensuring that the jet flow has sufficient kinetic energy while forming a suitable diffusion angle, thereby promoting uniform mixing of the gas and liquid phases within the distribution channel 12.

[0065] like Figure 7 As shown, the flow distribution section 10 also includes a cavity plate 16, which is located between a plurality of heat exchange tubes 20 and a flow distribution channel 12. The cavity plate 16 has a plurality of flow distribution cavities 161 arranged at intervals from top to bottom. One side of each flow distribution cavity 161 is connected to the flow distribution channel 12, and the other side of each flow distribution cavity 161 is connected to at least one heat exchange tube 20.

[0066] In this embodiment, the configuration of the flow distribution cavity 161 allows the refrigerant entering the flow distribution channel 12 to first enter the flow distribution cavity 161 in the cavity plate 16 for buffering and homogenization before flowing to each heat exchange tube 20. This reduces the uneven flow of the refrigerant caused by inertial impact, gas-liquid stratification, etc., thereby ensuring that the refrigerant flow state in each flow distribution cavity 161 is relatively stable, and then it is distributed to the corresponding heat exchange tube 20 in a more balanced state.

[0067] like Figure 7 As shown, the flow distribution section 10 also includes a positioning plate 17, one sidewall of the flow distribution channel 12 is a flow distribution plate 18, and the cavity plate 16 is located between the positioning plate 17 and the flow distribution plate 18; the positioning plate 17 has a plurality of waist-shaped positioning holes 171, the heat exchange tube 20 is a flat tube, the flat tube has a constricted section 21, the constricted section 21 of each flat tube is inserted into a corresponding positioning hole 171, and the constricted section 21 is welded to the positioning plate 17, and each constricted section 21 is connected to a corresponding flow distribution cavity 161; the flow distribution plate 18 has a plurality of through flow distribution holes 181, each flow distribution hole 181 is connected to a corresponding flow distribution cavity 161, so that the flow distribution cavity 161 is connected to the flow distribution channel 12.

[0068] In this embodiment, the flow divider plate 18 is provided with multiple through-holes 181, each of which is connected to a corresponding flow divider cavity 161. A stable fluid channel exists between the flow divider channel 12 and the flow divider cavity 161, ensuring that the uniformly mixed gas-liquid two-phase refrigerant in the flow divider channel 12 can enter each flow divider cavity 161 uniformly through the flow divider holes 181, and then be rationally distributed to each heat exchanger tube 20 by the flow divider cavity 161. Moreover, through the synergistic effect of the positioning plate 17, the cavity plate 16, and the flow divider plate 18, not only is the precise positioning and stable connection between the heat exchanger tube 20 and the flow divider cavity 161 achieved in terms of structure, but the uniform distribution of the gas-liquid two-phase refrigerant is also ensured in the fluid distribution path. This improves the operability of the assembly process and the reliability of welding, and enhances the uniformity of refrigerant distribution and the overall heat transfer performance of the heat exchanger.

[0069] like Figures 7 to 9 As shown, the width of the narrowed section 21 is Ws, the thickness of the narrowed section 21 is Ds, the length of the narrowed section 21 is Ls, and the fillet radius of the narrowed section 21 is Rs; the thickness of the positioning plate 17 is Dd, and the length of the positioning hole 171 is W. d The width of positioning hole 171 is H d The fillet radius of positioning hole 171 is R. d The area of ​​positioning hole 171 is A. d The thickness of the cavity plate 16 is Dq, the flow area of ​​the flow distribution cavity 161 is Aq, and the minimum distance between the edge of the flow distribution cavity 161 and the edge of the cavity plate 16 is Mq; the radius of the flow distribution orifice 181 is Rj; wherein, the heat exchanger satisfies the following (as per the specification). PN327203DUNANRG One less size relationship: W d –Ws≤0.15; H d –Ds≤0.1; Dd=Dq; Ls≤Dd+Dq≤10; R d -Rs≤0.06;Mq≥1.3;A d / Aq≥0.1;Rj 2 / Aq≤0.4. By setting the above dimensions within a reasonable range, it is ensured that the flat tube constriction section 21 is easy to assemble when inserted into the positioning hole 171, and forms a tight fit with the positioning plate 17 after welding, thereby improving the installation accuracy and structural stability of the heat exchange tube 20 and preventing displacement or loosening during operation.

[0070] The diversion cavity 161 includes two oblong holes and a rectangular hole connecting the two oblong holes. Each oblong hole is connected to a constriction section 21, and the rectangular hole is connected to the corresponding diversion hole 181. The length of the oblong hole is Wq, and the width of the oblong hole is Hq. The width of the positioning plate 17 is W3, the width of the cavity plate 16 is W4, and the outer width directions of the manifold 61 are W1 (shortest distance) and W2 (longest distance) respectively (W1 = W2 when the manifold 61 is circular or square). Preferably, W3 = W4 ≤ W2.

[0071] like Figure 2 As shown, the diversion section 10 includes a manifold 61, a return pipe 62, an upper connecting block 63, and a lower connecting block 64. The manifold 61 has a diversion channel 12, and the return pipe 62 has a return channel 13. The upper part of the manifold 61 is connected to the upper part of the return pipe 62 through the upper connecting block 63, and the lower part of the manifold 61 is connected to the lower part of the return pipe 62 through the lower connecting block 64. The upper connecting block 63 has an upper guide channel 14 that connects the return channel 13 and the diversion channel 12, and the lower connecting block 64 has a lower guide channel 15 that connects the return channel 13 and the diversion channel 12.

[0072] In this embodiment, the manifold 61 and the return pipe 62 are fixedly connected by the upper connecting block 63 and the lower connecting block 64, forming a stable overall frame structure. This ensures the precise positioning of the distribution channel 12 and the return channel 13 during operation, preventing misalignment or leakage caused by vibration or thermal expansion and contraction. Furthermore, since the upper guide channel 14 and the lower guide channel 15 are directly integrated into the upper connecting block 63 and the lower connecting block 64, not only is the number of additional pipe fittings reduced, but the flow path of the refrigerant between the channels is also shortened, thereby reducing local flow resistance and improving refrigerant circulation efficiency. This arrangement also allows the gaseous refrigerant enriched in the upper part of the distribution channel 12 to smoothly enter the return channel 13 through the upper guide channel 14 and return to the lower part of the distribution channel 12 via the lower guide channel 15, achieving a re-homogenization of the refrigerant gas-liquid two-phase distribution and alleviating the problem of uneven liquid supply between the upper and lower channels caused by gravity stratification.

[0073] like Figure 2 As shown, the flow distribution section 10 also includes a cavity plate 16 and a positioning plate 17. The manifold 61, cavity plate 16 and positioning plate 17 are connected in sequence. The cavity plate 16 has a plurality of flow distribution cavities 161 arranged at intervals from top to bottom. One side of each flow distribution cavity 161 is connected to the flow distribution channel 12, and the other side of each flow distribution cavity 161 is connected to at least one heat exchange tube 20. The positioning plate 17 has a plurality of positioning holes 171, and one end of each heat exchange tube 20 is inserted into a corresponding positioning hole 171.

[0074] In this embodiment, by providing a cavity plate 16 within the flow distribution section 10, the refrigerant can be segmented and guided as it enters each flow distribution cavity 161, thereby alleviating the uneven distribution problem caused by gravity stratification or gas-liquid separation. This ensures that heat exchange tubes 20 at different heights can receive a relatively balanced refrigerant supply, improving overall heat exchange performance. Simultaneously, the flow distribution cavities 161 within the cavity plate 16 also provide buffering and remixing space for the refrigerant, allowing the gas and liquid phases to be uniformly distributed again before entering each flat tube, further enhancing the stability of gas-liquid distribution. Furthermore, the positioning plate 17 not only ensures that the heat exchange tubes 20 are accurately fixed in the flow distribution section 10, but also guarantees the sealing and stability of the connection points during subsequent welding, avoiding stress concentration or welding errors caused by misalignment.

[0075] Specifically, the heat exchange tube 20, positioning plate 17, cavity plate 16, manifold 61, connecting block and return pipe 62 are welded together in sequence. The positioning plate 17, cavity plate 16 and manifold 61 are all made of aluminum alloy. At least one surface of the positioning plate 17, cavity plate 16 and manifold 61 has a welding material layer. The manifold 61 is a round tube, square tube or D-shaped tube. The return pipe 62 is a round tube, square tube or D-shaped tube.

[0076] In this application, the positioning plate 17, cavity plate 16, and manifold 61 are all made of aluminum alloy, and a welding material layer is provided on at least one surface of each, which makes the welding process smoother and the weld joint stronger, thereby improving the welding quality and consistency. Furthermore, aluminum alloy has good thermal conductivity and corrosion resistance, improving the heat transfer efficiency of the heat exchanger. In addition, the manifold 61 and return pipe 62 can be selected from different structural forms such as round tubes, square tubes, or D-shaped tubes. Among them, the round tube structure has advantages in terms of pressure resistance and manufacturing convenience, the square tube structure is easy to weld to plates and improves space utilization, while the D-shaped tube is conducive to compact arrangement and uniform flow. This provides a flexible selection of various tube shapes to adapt to different application scenarios and process requirements, improving the product's adaptability and market competitiveness.

[0077] like Figure 2 As shown, the diversion section 10 also includes an end cap 19, which covers the end opening of the manifold 61 from the outside; or the end cap 19 is embedded in the end opening of the manifold 61; or the end cap 19 passes through the manifold 61, the cavity plate 16 and the positioning plate 17 in sequence, and the end cap 19 blocks the end opening of the manifold 61.

[0078] In this application, reliable sealing of the end of the manifold 61 can be achieved through different installation methods, thereby preventing refrigerant leakage and ensuring the long-term airtightness and safety of the system. When the end cap 19 adopts an external cover structure, its assembly is simple, allowing for quick end sealing and improving the overall strength of the end of the manifold 61. If the end cap 19 adopts an embedded structure, the external space occupied can be further reduced, making the overall distribution section 10 more compact, while also providing stronger resistance to internal pressure under high-pressure conditions. If the end cap 19 adopts an insert structure and simultaneously cooperates with the cavity plate 16 and the positioning plate 17, it not only improves the sealing performance and fixing reliability of the end but also enhances the overall structural stability of the end, preventing loosening due to vibration or thermal expansion and contraction during operation. This allows for flexible selection of sealing methods according to different application requirements, achieving a balance between assembly convenience and operational stability.

[0079] like Figure 10 and Figure 11 As shown, the positioning plate 17, cavity plate 16, and manifold 61 are all provided with connecting holes 71. The diversion section 10 also includes rivets 72, which pass through the connecting holes 71 on the positioning plate 17, cavity plate 16, and manifold 61 to fix the positioning plate 17, cavity plate 16, and manifold 61; or, the edge of the positioning plate 17 has a first positioning protrusion 73, and the edges of the cavity plate 16 and manifold 61 each have a first positioning groove 74. The first positioning protrusion 73 is pressed into the first positioning groove 74 of the cavity plate 16 and manifold 61 to fix the positioning plate 17, cavity plate 16, and manifold 61; or, the edge of the cavity plate 16 has a second positioning protrusion 75, and the edge of the positioning plate 17 has a second positioning groove 76. The second positioning protrusion 75 is pressed into the second positioning groove 76 to fix the positioning plate 17 and cavity plate 16.

[0080] In this embodiment, multiple fixing methods provide flexible options for the assembly of the diversion section 10, ensuring both structural stability and sealing while also accommodating diverse manufacturing process requirements. When rivets 72 are used for fixing through the connecting holes 71 on the positioning plate 17, cavity plate 16, and manifold 61, reliable fastening of the multi-layer structure can be achieved, improving the overall strength of the diversion section 10 and effectively preventing deformation caused by thermal stress during welding. Furthermore, the rivet 72 fixing method is characterized by simple assembly and precise positioning, making it suitable for mass production.

[0081] like Figure 10 As shown, the first positioning protrusion 73 and the first positioning groove 74 are press-fitted together. The first positioning protrusion 73 on the positioning plate 17 and the first positioning groove 74 on the cavity plate 16 and the manifold 61 engage with each other. This not only achieves high-precision positioning, but also enhances the bonding force between the parts, thereby reducing assembly tolerances and improving overall airtightness and durability.

[0082] like Figure 11 As shown, when the second positioning protrusion 75 and the second positioning groove 76 are used for pressing, the cavity plate 16 and the positioning plate 17 can be directly interlocked, the structure is more compact, the use of additional fasteners is reduced, the assembly process is further simplified, and the overall weight of the heat exchanger is reduced.

[0083] like Figure 12 and 13 As shown, the flow distribution section 10 includes a flow collector 61 and a baffle 80. The baffle 80 is fixed inside the flow collector 61. The flow distribution channel 12 and the return channel 13 are located on both sides of the baffle 80, and one end of the heat exchange tube 20 is inserted into the flow collector 61.

[0084] like Figure 13 As shown, the baffle 80 separates the distribution channel 12 from the return channel 13. The distribution channel 12 primarily distributes the refrigerant, while the return channel 13 collects and guides the return of the gaseous refrigerant, forming a closed circulation path. This achieves a re-homogenization of the gas and liquid phases within the distribution channel 12, overcoming the problem of uneven liquid supply in the upper and lower channels caused by gravity stratification in the existing manifold 61. Simultaneously, one end of the heat exchange tube 20 directly penetrates the manifold 61, enabling a smooth transition of the refrigerant from the distribution channel 12 to each heat exchange tube 20. This reduces additional transition components or fittings, thereby lowering structural complexity and flow resistance, and improving the ease of processing and assembly as well as overall compactness.

[0085] like Figure 13 As shown, the flow distribution section 10 also includes a flow distribution plate 18 and a cavity plate 16. Both the flow distribution plate 18 and the cavity plate 16 are fixed inside the manifold 61. The flow distribution channel 12 is located between the flow distribution plate 18 and the baffle 80. One side wall of the manifold 61 is a positioning plate 17, and the cavity plate 16 is located between the positioning plate 17 and the flow distribution plate 18. The cavity plate 16 has a plurality of flow distribution cavities 161 arranged at intervals from top to bottom. One side of each flow distribution cavity 161 is connected to the flow distribution channel 12, and the other side of each flow distribution cavity 161 is connected to at least one heat exchange tube 20. The positioning plate 17 has a plurality of positioning holes 171, and one end of each heat exchange tube 20 is inserted into a corresponding positioning hole 171.

[0086] In this embodiment, the cavity plate 16 is disposed between the positioning plate 17 and the flow divider plate 18, and has multiple flow dividers 161 spaced apart from top to bottom. One side of each flow divider 161 is connected to the flow divider channel 12, and the other side is connected to at least one heat exchanger tube 20, so that the refrigerant can be mixed again in the flow divider 161, thereby reducing the impact of gas-liquid stratification and ensuring that heat exchanger tubes 20 at different heights can obtain a uniform refrigerant supply, improving the stability of gas-liquid distribution and heat exchange efficiency. Moreover, the positioning plate 17, as a side wall of the manifold 61, has multiple positioning holes 171, and one end of each heat exchanger tube 20 is inserted into the corresponding positioning hole 171, ensuring the accuracy of the arrangement and consistency of the spacing of the heat exchanger tubes 20, and also improving the sealing reliability during the welding process, avoiding welding stress concentration or leakage risks caused by pipeline misalignment.

[0087] like Figure 14 As shown, the inner wall of the manifold 61 has two opposing first inner grooves 81 and two opposing second inner grooves 82. The two opposing sides of the baffle 80 are respectively inserted into the two first inner grooves 81, and the two opposing sides of the diverter 18 are respectively inserted into the two second inner grooves 82.

[0088] In this embodiment, after the baffle 80 is inserted into the first inner groove 81, it can remain stable under the impact of refrigerant flow and operating vibration, without shifting or loosening, thereby ensuring the separation effect between the diversion channel 12 and the return channel 13. Moreover, by using the assembly method of the first inner groove 81 and the second inner groove 82, the baffle 80 and the diversion plate 18 can be fixed without additional fasteners, reducing the complexity of manufacturing and assembly, and reducing the number of welding points, thereby improving the overall processing efficiency and airtightness.

[0089] like Figure 15 and Figure 16 As shown, the manifold 61 is an extruded profile; the manifold 61 is an integral structure, or the manifold 61 includes a first profile 83 with an opening on the side and a second profile 84 with an opening on the side. The opening of the first profile 83 has two first flanges 85 on opposite sides, and the opening of the second profile 84 has two second flanges 86 on opposite sides. The openings of the first profile 83 and the second profile 84 are arranged opposite to each other, and the two first flanges 85 and the two second flanges 86 are connected one-to-one.

[0090] In embodiments of this utility model not shown, when the manifold 61 is an integral extrusion structure, it can be formed in one step through profile extrusion process, avoiding dimensional errors and potential leakage risks caused by multi-part assembly and welding processes.

[0091] like Figure 15 and Figure 16As shown, when the manifold 61 is spliced ​​from the first profile 83 and the second profile 84, the openings of the two profiles are arranged opposite each other, and the first flange 85 and the second flange 86 are respectively provided on their opposite sides. They are connected one-to-one through the flanges, which can form a stable locking effect during the splicing process, ensuring the sealing reliability and structural strength of the connection part.

[0092] Among them, the first profile 83 and the second profile 84 are extruded profiles without composite layers. Welding pads can be added to the connection of the profiles and then brazed in a furnace to ensure effective and reliable welding between the welds of the two profiles. The end cap 19 is designed as a double-sided composite layer. The diversion plate 18, cavity plate 16 and baffle 80 are double-sided composite to ensure that the internal structure of this manifold 61 is effectively welded to each other and no internal leakage occurs.

[0093] An embodiment of this utility model also provides an air conditioning system, which includes the heat exchanger described above.

[0094] In this embodiment, by using the heat exchanger described above in the air conditioning system, not only is the system's energy efficiency ratio improved, and the stability and comfort of operation enhanced, but the overall effect in terms of energy saving, environmental protection, and reliability is also achieved, which is superior to the traditional air conditioning system in the prior art.

[0095] The above descriptions are merely some embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

[0096] The technical features of the embodiments described above can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as the combination of these technical features does not contradict each other, it should be considered to be within the scope of this specification.

[0097] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0098] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as exemplary only and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0099] In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms 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 on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0100] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0101] manual PN327203DUNANRG

[0102] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this application.

Claims

1. A heat exchanger, characterized in that, The device includes a flow divider (10), multiple heat exchange tubes (20) arranged from top to bottom, and a nozzle (30). The flow divider (10) has a refrigerant inlet (11), a flow divider channel (12), and a return channel (13). The bottom of the refrigerant inlet (11) and the flow divider channel (12) are connected. Each heat exchange tube (20) is connected to the flow divider channel (12). The upper part of the return channel (13) is connected to the upper part of the flow divider channel (12). The lower part is connected to the lower part of the diversion channel (12); at least a portion of the injection head (30) is inserted into the diversion channel (12) from the refrigerant inlet (11), the injection head (30) has an injection hole (31), the injection hole (31) sprays refrigerant toward the upper part of the diversion channel (12); wherein, under the action of injection pressure, the gaseous refrigerant accumulated in the upper part of the diversion channel (12) flows back to the lower part of the diversion channel (12) through the return channel (13).

2. The heat exchanger according to claim 1, characterized in that, The upper part of the return channel (13) is connected to the upper part of the diversion channel (12) through the upper guide channel (14), and the lower part of the return channel (13) is connected to the lower part of the diversion channel (12) through the lower guide channel (15). The radius of the upper guide channel (14) is R. k1 The radius of the lower guide channel (15) is R. k2 Where 1≤R k1 / R k2 .

3. The heat exchanger according to claim 1, characterized in that, The upper part of the return channel (13) is connected to the upper part of the diversion channel (12) through the upper guide channel (14), and the lower part of the return channel (13) is connected to the lower part of the diversion channel (12) through the lower guide channel (15). The lower guide channel (15) is located above the refrigerant inlet (11). The distance between the center line of the upper guide channel (14) and the bottom surface of the diversion section (10) is H1, the distance between the center line of the lower guide channel (15) and the bottom surface of the diversion section (10) is H2, and the distance between the bottom surface and the top surface of the diversion section (10) is H. j Where 0.6 ≤ H1 / H j H j -H1≤H2,3≤H1 / H2。 4. The heat exchanger according to claim 1, characterized in that, The flow area of ​​the diversion channel (12) is S1, and the flow area of ​​the return channel (13) is S2, where S2 = (0.2~0.5)S1.

5. The heat exchanger according to claim 1, characterized in that, The heat exchanger also includes an adapter sleeve (40) and an inlet pipe (50). One end of the adapter sleeve (40) is connected to one end of the spray head (30), and the adapter sleeve (40) and the spray head (30) are in communication. The outer diameter of the adapter sleeve (40) is larger than the outer diameter of the spray head (30). The adapter sleeve (40) and the flow divider (10) are fixedly connected. The adapter sleeve (40) and the spray head (30) are an integral structure, or the adapter sleeve (40) and the spray head (30) are separate structures. One end of the inlet pipe (50) is inserted into the adapter sleeve (40) and fixedly connected to the adapter sleeve (40).

6. The heat exchanger according to claim 5, characterized in that, In the direction in which the spray head (30) is inserted into the diverter (10), the size of the diverter (10) is W2, the distance from the center of the spray hole (31) to the adapter sleeve (40) is Lp, the diameter of the spray hole (31) is Rp, and the inner diameter of the input pipe (50) is Dg, where Lp = (0.45~0.55)×W2, 2≤Dg / Rp≤6.

5.

7. The heat exchanger according to claim 1, characterized in that, The flow divider (10) further includes a cavity plate (16), which is located between the plurality of heat exchange tubes (20) and the flow divider channel (12). The cavity plate (16) has a plurality of flow divider cavities (161) spaced apart from top to bottom. One side of each flow divider cavity (161) is connected to the flow divider channel (12), and the other side of each flow divider cavity (161) is connected to at least one of the heat exchange tubes (20).

8. The heat exchanger according to claim 7, characterized in that, The diversion section (10) further includes a positioning plate (17), one sidewall of the diversion channel (12) is a diversion plate (18), and the cavity plate (16) is located between the positioning plate (17) and the diversion plate (18); the positioning plate (17) has a plurality of waist-shaped positioning holes (171), the heat exchange tube (20) is a flat tube, the flat tube has a constricted section (21), each constricted section (21) of the flat tube is inserted into a corresponding positioning hole (171), and the constricted section (21) is welded to the positioning plate (17), and each constricted section (21) is connected to a corresponding diversion cavity (161); the diversion plate (18) has a plurality of through diversion holes (181), each diversion hole (181) is connected to a corresponding diversion cavity (161) so that the diversion cavity (161) and the diversion channel (12) are connected.

9. The heat exchanger according to claim 8, characterized in that, The width of the constricted section (21) is Ws, the thickness of the constricted section (21) is Ds, the length of the constricted section (21) is Ls, and the radius of the rounded corner of the constricted section (21) is Rs; the thickness of the positioning plate (17) is Dd, and the length of the positioning hole (171) is W. d The width of the positioning hole (171) is H. d The fillet radius of the positioning hole (171) is R. d The area of ​​the positioning hole (171) is A. d The thickness of the cavity plate (16) is Dq, the flow area of ​​the flow-dividing cavity (161) is Aq, and the minimum distance between the edge of the flow-dividing cavity (161) and the edge of the cavity plate (16) is Mq; the radius of the flow-dividing orifice (181) is Rj; wherein, the heat exchanger satisfies at least one of the following dimensional relationships: IN d –Ws≤0.15; H d –Ds≤0.1; Dd = Dq; Ls≤Dd+Dq≤10; R d -Rs≤0.06; Mq≥1.3; A d / Aq≥0.1; Rj 2 / Aq≤0.4。 10. The heat exchanger according to claim 1, characterized in that, The diversion section (10) includes a collector pipe (61), a return pipe (62), an upper connecting block (63), and a lower connecting block (64). The collector pipe (61) has the diversion channel (12), and the return pipe (62) has the return channel (13). The upper part of the collector pipe (61) is connected to the upper part of the return pipe (62) through the upper connecting block (63), and the lower part of the collector pipe (61) is connected to the lower part of the return pipe (62) through the lower connecting block (64). The upper connecting block (63) has an upper guide channel (14) that connects the return channel (13) and the diversion channel (12), and the lower connecting block (64) has a lower guide channel (15) that connects the return channel (13) and the diversion channel (12).

11. The heat exchanger according to claim 10, characterized in that, The diversion section (10) further includes a cavity plate (16) and a positioning plate (17). The manifold (61), the cavity plate (16) and the positioning plate (17) are connected in sequence. The cavity plate (16) has a plurality of diversion cavities (161) spaced apart from top to bottom. One side of each diversion cavity (161) is connected to the diversion channel (12), and the other side of each diversion cavity (161) is connected to at least one heat exchange tube (20). The positioning plate (17) has a plurality of positioning holes (171), and one end of each heat exchange tube (20) is inserted into a corresponding positioning hole (171).

12. The heat exchanger according to claim 11, characterized in that, The heat exchange tube (20), the positioning plate (17), the cavity plate (16), the manifold (61), the connecting block, and the return pipe (62) are welded together in sequence. The positioning plate (17), the cavity plate (16), and the manifold (61) are all made of aluminum alloy. At least one surface of the positioning plate (17), the cavity plate (16), and the manifold (61) has a welding material layer. The manifold (61) is a round tube, a square tube, or a D-shaped tube, and the return pipe (62) is a round tube, a square tube, or a D-shaped tube.

13. The heat exchanger according to claim 11, characterized in that, The diversion section (10) also includes an end cap (19). The end cap (19) covers the end opening of the manifold (61) from the outside; or the end cap (19) is embedded in the end opening of the manifold (61); or the end cap (19) passes through the manifold (61), the cavity plate (16) and the positioning plate (17) in sequence, and the end cap (19) blocks the end opening of the manifold (61).

14. The heat exchanger according to claim 11, characterized in that, The positioning plate (17), the cavity plate (16), and the manifold (61) are all provided with connection holes (71). The diversion part (10) also includes a rivet (72). The rivet (72) passes through the connection holes (71) on the positioning plate (17), the cavity plate (16), and the manifold (61) to fix the positioning plate (17), the cavity plate (16), and the manifold (61). Alternatively, the edge of the positioning plate (17) has a first positioning protrusion (73), and the edges of the cavity plate (16) and the manifold (61) both have a first positioning groove (74). The first positioning protrusion (73) is pressed into the first positioning groove (74) of the cavity plate (16) and the manifold (61) to fix the positioning plate (17), the cavity plate (16) and the manifold (61). Alternatively, the edge of the cavity plate (16) has a second positioning protrusion (75), and the edge of the positioning plate (17) has a second positioning groove (76). The second positioning protrusion (75) is pressed into the second positioning groove (76) to fix the positioning plate (17) and the cavity plate (16).

15. The heat exchanger according to claim 1, characterized in that, The diversion section (10) includes a collector pipe (61) and a baffle (80). The baffle (80) is fixed inside the collector pipe (61). The diversion channel (12) and the return channel (13) are located on both sides of the baffle (80). One end of the heat exchange tube (20) is inserted into the collector pipe (61).

16. The heat exchanger according to claim 15, characterized in that, The diversion section (10) further includes a diversion plate (18) and a cavity plate (16). The diversion plate (18) and the cavity plate (16) are both fixed inside the manifold (61). The diversion channel (12) is located between the diversion plate (18) and the baffle (80). One side wall of the manifold (61) is a positioning plate (17). The cavity plate (16) is located between the positioning plate (17) and the diversion plate (18). The cavity plate (16) has a plurality of diversion cavities (161) spaced apart from top to bottom. One side of each diversion cavity (161) is connected to the diversion channel (12), and the other side of each diversion cavity (161) is connected to at least one heat exchange tube (20). The positioning plate (17) has a plurality of positioning holes (171). One end of each heat exchange tube (20) is inserted into a corresponding positioning hole (171).

17. The heat exchanger according to claim 16, characterized in that, The inner wall of the manifold (61) has two opposing first inner grooves (81) and two opposing second inner grooves (82). The two opposing sides of the baffle (80) are respectively inserted into the two first inner grooves (81), and the two opposing sides of the diverter (18) are respectively inserted into the two second inner grooves (82).

18. The heat exchanger according to claim 15, characterized in that, The manifold (61) is an extruded profile; the manifold (61) is an integral structure, or the manifold (61) includes a first profile (83) with an opening on the side and a second profile (84) with an opening on the side. The opening of the first profile (83) has two first flanges (85) on opposite sides, and the opening of the second profile (84) has two second flanges (86) on opposite sides. The openings of the first profile (83) and the second profile (84) are arranged opposite to each other, and the two first flanges (85) and the two second flanges (86) are connected one-to-one.

19. An air conditioning system, characterized in that, The air conditioning system includes the heat exchanger according to any one of claims 1 to 18.

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