Heat exchanger and refrigeration system

Abstract

The present application relates to the technical field of refrigeration, in particular to a heat exchanger and a refrigeration system. The present application provides a heat exchanger, comprising a plurality of heat exchange pipes, the plurality of heat exchange pipes are arranged at intervals along a first preset direction; a distributor and a plurality of capillary tubes, one end of each capillary tube is communicated with the distributor, and the other end of each capillary tube is communicated with an inlet section of each heat exchange pipe; and a balance assembly, the balance assembly comprises a header and a plurality of branch pipes communicated with the header, each branch pipe is arranged to be communicated with the inlet section of each heat exchange pipe, each capillary tube is communicated with each branch pipe, and the plurality of heat exchange pipes are communicated with each other through the plurality of branch pipes and the header. The present application also provides a refrigeration system. The present application has the advantages that the refrigerant with higher pressure can flow into the heat exchange pipe with lower pressure, the pressure of the refrigerant in each heat exchange pipe is balanced, the heat exchange of the heat exchanger is uniform, and thus the performance of the heat exchanger is improved.

Description

Technical Field

[0001] This invention relates to the field of refrigeration technology, and in particular to a heat exchanger and refrigeration system. Background Technology

[0002] In a refrigeration system, refrigerant exchanges heat with the outside environment through a heat exchanger. The heat exchanger typically includes a balancing component, which is used to evenly distribute the refrigerant. The balancing component includes a distributor and capillary tubes. The refrigerant is distributed through the distributor and then enters the heat exchange tubes through multiple capillary tubes.

[0003] In the existing technology, due to limited installation space, the heat exchanger is installed vertically, and the heat exchange tubes are arranged from top to bottom. The different positions of each heat exchange tube in the height direction result in different pressure drops when the refrigerant enters each heat exchange tube, which makes the heat exchanger uneven and affects its performance. Summary of the Invention

[0004] In view of this, it is necessary to provide a heat exchanger and refrigeration system that can improve the heat exchange performance of the heat exchanger.

[0005] A heat exchanger includes multiple heat exchange tubes, which are spaced apart along a first preset direction.

[0006] A distributor and multiple capillary tubes, one end of each capillary tube being connected to the distributor and the other end of each capillary tube being connected to the inlet section of each heat exchange tube.

[0007] The balancing component includes a manifold and multiple branch pipes connected to the manifold. Each branch pipe is connected to the inlet section of each heat exchange tube. Each capillary tube is connected to each branch pipe. The multiple heat exchange tubes are interconnected through the multiple branch pipes and the manifold.

[0008] This configuration allows the refrigerant with higher pressure in the heat exchange tubes to flow into the heat exchange tubes with lower pressure, balancing the refrigerant pressure in each heat exchange tube and making the heat exchange of each heat exchanger more uniform, thereby enhancing the performance of the heat exchangers and improving the energy efficiency ratio of the entire refrigeration system.

[0009] In one embodiment, the manifold has multiple connection ports, which correspond to multiple branch pipes. Each capillary tube passes through multiple connection ports and is fitted into a corresponding branch pipe. Each of the multiple branch pipes has a first channel that communicates with multiple heat exchange tubes, and the multiple first channels are interconnected.

[0010] In one embodiment, the outer wall of the capillary and the inner wall of the branch tube are fitted together to form the first channel.

[0011] This setup is simple and requires no additional structures to form the first channel.

[0012] In one embodiment, the capillary sleeved on the branch pipe is coaxially arranged with the branch pipe; or, the outer wall of the capillary sleeved on the branch pipe is partially fitted with the inner wall of the branch pipe; or, the axial direction of the capillary sleeved on at least part of the branch pipe is eccentric to the axial direction of the branch pipe.

[0013] In one embodiment, the capillary tube protrudes from one end of the branch tube relative to the end face of the branch tube.

[0014] This configuration allows the capillary tube to extend into the heat exchange tube, prioritizing the refrigerant's entry into the heat exchange tube for heat exchange. Excess refrigerant is then returned through the first channel. This prevents refrigerant from flowing directly back to the expansion valve inlet from the first channel without entering the heat exchange tube, which would cause the refrigerant to enter the heat exchanger directly without undergoing throttling and pressure reduction. Consequently, the refrigerant would be unable to exchange heat with the outside environment, affecting the heat exchange effect and thus impacting the performance of the refrigeration system.

[0015] In one embodiment, the sum of the lengths L1 of the capillary extending into the manifold, the branch pipe, and the heat exchange tube is 110 mm to 120 mm.

[0016] This design saves materials while ensuring that a sufficiently long capillary tube can be inserted into the heat exchange tube.

[0017] In one embodiment, the manifold is provided with an annular protrusion that extends toward a direction away from the branch pipe, and the annular protrusion is arranged around the connection port and is sealed to the capillary.

[0018] This design increases the contact area between the connector and the capillary, thereby strengthening the connection between the capillary and the manifold.

[0019] In one embodiment, the manifold has an inner cavity, and multiple heat exchange tubes are interconnected through the inner cavity. The manifold has a return port communicating with the inner cavity, and the return port is unidirectionally connected to the inlets of multiple capillary tubes; and / or, the length L2 of the branch pipe is 50mm to 85mm.

[0020] This design allows the refrigeration system to adapt to harsh operating conditions, especially when used for heating in northern winters. Due to extremely low outdoor temperatures, the refrigerant in the heat exchanger cannot absorb heat and evaporate. The return port allows excess refrigerant to flow back to the expansion valve, preventing excessive refrigerant from failing to evaporate completely in the heat exchanger and causing liquid slugging in the compressor. Simultaneously, controlling the refrigerant flow into the heat exchanger optimizes its heat exchange performance, thereby improving the refrigeration system's energy efficiency ratio. Setting the branch pipe length to 50mm–85mm saves material while ensuring sufficient contact area between the branch pipe and the heat exchange tubes, increasing the connection strength.

[0021] The present invention also provides a refrigeration system, including an expansion valve and the heat exchanger described above, wherein the outlet of the expansion valve is connected to the inlet of the distributor, and the manifold has a return port connected to the heat exchange tube, the return port being connected to the inlet of the expansion valve.

[0022] This configuration allows the refrigerant that cannot be completely evaporated to be sent back to the expansion valve inlet. By adjusting the opening of the expansion valve, the refrigeration system can adapt to different operating conditions, especially during heating in northern winters. This prevents excessive refrigerant from failing to evaporate completely, which could cause liquid slugging in the compressor. At the same time, it controls the flow rate of refrigerant entering the heat exchanger, ensuring that the heat exchanger's heat exchange performance reaches its optimal level.

[0023] In one embodiment, the refrigeration system further includes a check valve, the inlet of which is connected to the return port, and the outlet of which is connected to the inlet of the expansion valve.

[0024] This configuration ensures that the refrigerant flows from the return port into the expansion valve inlet, preventing the refrigerant at the expansion valve inlet from directly entering the manifold and then the heat exchange tube through the return port. If the refrigerant enters the heat exchanger directly from the expansion valve inlet without passing through the expansion valve for throttling and pressure reduction, the refrigerant will not be able to exchange heat in the heat exchanger.

[0025] This invention connects the heat exchange tubes to each other to balance the pressure between them. In the heat exchange tubes, the refrigerant with higher pressure flows into the heat exchange tube with lower pressure, making the pressure in each heat exchange tube the same and improving the heat exchange uniformity of the heat exchanger. The manifold is provided with a return port, which allows excess refrigerant in the heat exchanger to flow back to the front end of the expansion valve. This can regulate the refrigerant flow rate entering the heat exchanger under different environmental conditions and improve the overall performance of the refrigeration system. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of the present invention or the conventional technology, the drawings used in the description of the embodiments or the conventional technology will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 A schematic diagram of the structure of the balancing component provided by the present invention;

[0028] Figure 2 This is a schematic diagram of the structure of a heat exchanger in the prior art;

[0029] Figure 3 This is a top view of the balancing component of the present invention;

[0030] Figure 4 This is a partial cross-sectional view of the balancing component of the present invention;

[0031] Figure 5 This is a schematic diagram of refrigerant reflux according to the present invention;

[0032] Figure 6 This is a schematic diagram of the process by which refrigerant in the first channel with higher pressure flows into the first channel with lower pressure according to the present invention.

[0033] Figure 7 This is a schematic diagram of the refrigeration system provided by the present invention.

[0034] Reference numerals: 100', heat exchanger; 10', distribution assembly; 11', capillary tube; 20', distributor; 30', heat exchange tube; 1000, refrigeration system; 100, heat exchanger; 10, balancing assembly; 11, capillary tube; 12, manifold; 121, connection port; 122, branch pipe; 123, inner cavity; 124, return port; 125, annular protrusion; 126, first channel; 20, distributor; 200, expansion valve; 300, check valve; 400, compressor; 500, four-way valve; 600, second heat exchanger; 700, connecting pipe. Detailed Implementation

[0035] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0036] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on the other component or there may be an intermediate component. When a component is considered to be "connected to" another component, it can be directly connected to the other component or there may be an intermediate component present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this specification are for illustrative purposes only and do not represent the only possible implementation.

[0037] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0038] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature and the second feature are in indirect contact through an intermediate medium. Furthermore, "above," "over," and "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0039] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0040] like Figure 1 and Figure 7 As shown, Figure 1 This is a schematic diagram of the structure of the balancing component 10 provided by the present invention. Figure 7 This is a schematic diagram of the refrigeration system 1000 provided by the present invention. The present invention provides a heat exchanger 100, which is installed in the refrigeration system 1000 for heat exchange with the outside environment.

[0041] The heat exchanger 100 includes multiple heat exchange tubes (not shown in the figure), multiple capillary tubes 11, and a balancing assembly 10. The multiple capillary tubes 11 are respectively connected to the multiple heat exchange tubes, and the multiple heat exchange tubes are spaced apart along a first preset direction. It should be noted that in one embodiment of the present invention, the first preset direction is a vertical direction, that is, the height direction. In other embodiments, it can be adjusted according to the installation direction of the heat exchanger 100, such as being a horizontal direction.

[0042] The balancing assembly 10 includes a manifold 12 and multiple branch pipes 122. The branch pipes 122 are disposed on the manifold 12 and connected to the manifold 12. Each branch pipe 122 corresponds to and is connected to multiple heat exchange tubes. Each capillary tube 11 is connected to each branch pipe 122. The multiple heat exchange tubes are connected to each other through the branch pipes 122 and the manifold 12.

[0043] like Figure 2 As shown, Figure 2 This is a schematic diagram of the structure of a heat exchanger 100' in the prior art. In the prior art, the heat exchanger 100' includes a distribution component 10' and heat exchange tubes 30'. The distribution component 10' is connected to the heat exchange tubes 30' and is used to distribute the refrigerant into the heat exchange tubes 30'. The distribution component 10' includes a distributor 20' and multiple capillary tubes 11'. The multiple capillary tubes 11' are connected to the distributor 20' and are respectively connected to multiple heat exchange tubes 30'. The refrigerant distributed by the distributor 20' enters each heat exchange tube 30' for heat exchange through the multiple capillary tubes 11'. Because the height positions of each heat exchange tube 30' are different, the pressure of the refrigerant entering each heat exchange tube 30' is different, resulting in uneven heat exchange in the heat exchanger 100', thus affecting the heat exchange performance of the heat exchanger 100'.

[0044] The present invention distributes refrigerant to multiple heat exchange tubes through multiple capillary tubes 11, and sets each heat exchange tube to be interconnected through branch pipes 122 and manifolds 12 to balance the pressure of refrigerant in each heat exchange tube, thereby making the heat exchanger 100 heat exchange uniform and enhancing the performance of the heat exchanger 100.

[0045] The manifold 12 has multiple connection ports 121, and each capillary tube 11 is inserted through each connection port 121. The manifold 12 has multiple branch pipes 122. Multiple capillary tubes 11 are inserted into the manifold 12 from multiple connection ports 121 and are inserted through the branch pipes 122, and are connected to the heat exchange tubes through the branch pipes 122. The branch pipes 122 are connected to the heat exchange tubes. Each of the multiple branch pipes 122 has multiple first channels 126, which are interconnected and are respectively connected to multiple heat exchange tubes.

[0046] like Figure 4 As shown, Figure 4This is a top view of the balancing component 10 of the present invention. The outer wall of the capillary 11 and the inner wall of the branch pipe 122 are fitted together to form a first channel 126. The structure is simple and does not require additional structures to form the first channel 126.

[0047] In one embodiment, the portion of the capillary tube 11 that extends into the branch pipe 122 is coaxial with the branch pipe 122, that is, the connection port 121 and the branch pipe 122 are coaxial. The periphery of the capillary tube 11 and the inner wall of the branch pipe 122 have gaps of equal size, so the refrigerant flow velocity is uniform and the flow resistance of the refrigerant can be reduced.

[0048] In another embodiment, one side of the outer wall of the capillary 11 can also be attached to the inner wall of the branch pipe 122, that is, part of the outer wall of the capillary 11 and the inner wall of the branch pipe 122 are attached to each other, thereby improving the stability of the capillary 11 structure installation.

[0049] In another embodiment, the sidewalls of the capillary tube 11 are all separated from the inner wall of the branch pipe 122 by gaps of different sizes. That is, the axial direction of the part of the capillary tube 11 fitted inside the branch pipe 122 is eccentrically set with respect to the axial direction of the branch pipe 122, so that the flow velocity of the refrigerant in the first channel 126 at different positions is different, which is beneficial to the disturbance of the refrigerant, improves the uniformity of refrigerant distribution, and improves the heat exchange efficiency.

[0050] like Figure 3 As shown, Figure 3 This is a partial cross-sectional view of the balancing assembly 10 of the present invention. The manifold 12 has an inner cavity 123, which communicates with each of the first channels 126. The first channels 126 are connected to each other through the inner cavity 123. A return port 124 is provided on the manifold 12, communicating with the inner cavity 123. The return port 124 is used for one-way connection to the inlet of the expansion valve 200. Thus, excess refrigerant can flow back to the expansion valve 200 from the return port 124. This configuration allows for adjustment of the refrigerant flow rate into the heat exchanger 100 under different environmental conditions, improving the overall performance of the refrigeration system 1000. It is understandable that when the outdoor temperature is low, especially in northern winters, the outdoor heat exchanger 100, used for heating, functions as an evaporator, requiring less refrigerant. However, when the outdoor temperature drops suddenly, a significant amount of refrigerant in the heat exchange tubes cannot absorb heat from the external environment and evaporates. This liquid refrigerant enters the compressor 400, causing liquid slugging. Simultaneously, the refrigerant parameters entering the compressor 400 cannot reach the designed state, preventing the refrigeration system 1000 from achieving its optimal energy efficiency ratio and resulting in energy waste.

[0051] Furthermore, the manifold 12 is ring-shaped, with the branch pipe 122 and the return port 124 located on both sides, so that the path of the refrigerant in each first channel 126 to the return port 124 is not too long, thereby avoiding excessive refrigerant flow loss.

[0052] The two ends of the manifold 12 extend to form a long strip, so that each branch pipe 122 can be aligned with the corresponding heat exchange tube, and the capillary tube 11 can be inserted vertically into the heat exchange tube, saving the cost of the capillary tube 11.

[0053] The branch pipe 122 is open at the end away from the manifold 12, so that the capillary tube 11 can be inserted into the heat exchange tube.

[0054] The opening of the branch pipe 122 is oriented opposite to that of the return port 124 so as to be properly installed in the heat exchanger 100. The orientation of the connection port 121 is the same as that of the return port 124. The connection port 121 and the return port 124 are respectively located on both sides, which can stagger the connection between the manifold 12 and the capillary tube 11 and the expansion valve 200 to prevent interference during installation.

[0055] One end of the capillary tube 11 protrudes from the end face of the branch pipe 122, allowing it to extend into the heat exchanger 100. The refrigerant flowing out of the capillary tube 11 preferentially enters the heat exchange tube for heat exchange, meeting the heat exchange requirements. Excess refrigerant then flows out through the first channel 126, preventing the refrigerant from flowing back to the inlet of the expansion valve 200 directly from the first channel 126 without entering the heat exchange tube. Otherwise, the refrigerant would not undergo throttling and pressure reduction before directly entering the heat exchanger 100, preventing heat exchange between the refrigerant and the outside environment, thus affecting the heat exchange effect and consequently the performance of the refrigeration system.

[0056] Please continue reading Figure 4 , Figure 4 This is a partial cross-sectional view of the balancing assembly 10 of the present invention. Preferably, the length L1 of the capillary tube 11 extending into the manifold 12 and the branch pipe 122 is 110mm to 120mm, so that the capillary tube 11 can be fully inserted into the heat exchange tube. L1 can be 110mm, 113mm, 115mm, 118mm, 120mm or any other value between 110mm and 120mm.

[0057] One end of the branch pipe 122 extends into the heat exchange tube, and the outer wall of the branch pipe 122 and the inner wall of the heat exchange tube are attached to each other and fixedly connected by welding. Alternatively, one end of the heat exchange tube extends into the branch pipe 122, and the outer wall of the heat exchange tube and the inner wall of the branch pipe 122 are attached to each other and fixedly connected by welding.

[0058] Specifically, the length L2 of the branch pipe 122 is 50mm to 85mm. This not only strengthens the connection between the branch pipe 122 and the heat exchange tube but also saves materials and reduces costs. Understandably, if the branch pipe 122 is too long, it increases material costs; if it is too short, the contact area between the branch pipe 122 and the heat exchange tube is reduced, affecting the connection strength. The length L2 of the branch pipe 122 can be 50mm, 55mm, 60mm, 65mm, 70mm, 75mm, 80mm, 85mm, or any other value between 50mm and 85mm.

[0059] The manifold 12 is provided with an annular protrusion 125, which surrounds the connection port 121, and the capillary tube 11 and the annular protrusion 125 are sealed together.

[0060] The outer wall of the capillary tube 11 and the inner wall of the annular protrusion 125 are attached and fixed by welding. The annular protrusion 125 can strengthen the connection between the manifold 12 and the capillary tube 11.

[0061] The annular protrusion 125 and the branch pipe 122 are coaxially arranged, so that the capillary tube 11 can be directly inserted into the branch pipe 122 after being inserted vertically without turning, which enhances the convenience of installation.

[0062] The heat exchanger 100 also includes a distributor 20. One end of the capillary tube 11 is connected to the distributor 20, and the other end is connected to the inlet section of the heat exchange tube. The manifold 12 is connected to the heat exchange tube. The refrigerant distributed by the distributor 20 enters each heat exchange tube through multiple capillary tubes 11. The refrigerant with higher pressure flows from the first channel 126 into the inner cavity 123 and then flows into the first channel 126 with lower pressure, thereby balancing the pressure of the refrigerant in each heat exchange tube.

[0063] During installation, the manifold 12 is vertically arranged along the height direction of the heat exchanger 100, so that the branch pipe 122 can be close to the corresponding heat exchange tube. This not only makes the overall structure of the heat exchanger 100 more compact, but also shortens the length of the capillary tube 11 and reduces costs.

[0064] Furthermore, the opening of the branch pipe 122 faces the heat exchange tube, and the return port 124 faces the expansion valve 200, which further makes the structure of the heat exchanger 100 more compact.

[0065] Please continue reading Figure 7 The present invention also provides a refrigeration system 1000, including an expansion valve 200 and the heat exchanger 100 described above. The inlet of the expansion valve 200 is connected to the return port 124, and the outlet of the expansion valve 200 is connected to the inlet of the distributor 20.

[0066] Specifically, the refrigeration system 1000 also includes a check valve 300, which is located between the return port 124 and the expansion valve 200. The inlet of the check valve 300 is connected to the return port 124, and the outlet is connected to the inlet of the expansion valve 200. The check valve 300 ensures that the refrigerant can only flow from the manifold 12 to the inlet of the expansion valve 200, and cannot flow directly from the inlet of the expansion valve 200 to the manifold 12. It is understandable that without the check valve 300, the refrigerant would flow directly from the manifold 12 into the heat exchange tubes without passing through the throttling and pressure reduction of the expansion valve 200.

[0067] In one embodiment, the expansion valve 200 is an electronic expansion valve 200, which can automatically adjust the opening size according to the parameters of the refrigeration system 1000, thereby automatically adjusting the refrigerant flow rate.

[0068] In one embodiment, the check valve 300 is a one-way valve, which is inexpensive.

[0069] The refrigeration system 1000 also includes a connecting pipe 700, and a check valve 300 is provided on the connecting pipe 700. One end of the connecting pipe 700 is connected to the inlet of the expansion valve 200, and the other end is connected to the return port 124. The connecting pipe is installed vertically and parallel to the manifold 12, making the overall structure of the refrigeration system 1000 compact.

[0070] In one embodiment, a shut-off element (not shown) can be provided on the connecting pipe 700. During refrigeration operation, if it is necessary to disconnect this branch of the connecting pipe 700, the shut-off element can be closed to achieve the shutdown. The shut-off element can be a solenoid valve, a gate valve, or other shut-off element capable of achieving shutdown.

[0071] Furthermore, the refrigeration system 1000 also includes a compressor 400, a four-way valve 500, and a second heat exchanger 600. The inlet and outlet of the compressor 400 are respectively connected to the four-way valve 500. The four-way valve 500 is connected to the second heat exchanger 600 and the heat exchanger 100 of this application. The second heat exchanger 600 is connected to the expansion valve 200. The second heat exchanger 600 is installed indoors, while the heat exchanger 100 of this application is installed outdoors. Of course, the heat exchanger 100 of this application can also be installed indoors. The four-way valve 500 can be reversed, enabling the refrigeration system 1000 to provide heating in summer and heating in winter.

[0072] Taking the heating mode as an example, the refrigerant absorbs heat and evaporates in the outdoor heat exchanger 100, forming a low-pressure, low-temperature gaseous refrigerant. It then enters the compressor 400 through the passage of the four-way valve 500. After the compressor 400 performs work, it becomes a high-temperature, high-pressure gaseous refrigerant, which then enters the indoor second heat exchanger 600. The refrigerant releases heat in the second heat exchanger 600, raising the indoor temperature. The refrigerant condenses in the second heat exchanger 600 to form a liquid refrigerant, which mixes with the refrigerant from the return port 124 and enters the expansion valve 200 for throttling and pressure reduction. It then enters the balance assembly 10 and subsequently enters the heat exchange tubes to absorb heat and evaporate.

[0073] Please see Figure 5 , Figure 6 and Figure 7 , Figure 5 This is a schematic diagram of the refrigerant reflux process according to the present invention. Figure 6 This is a schematic diagram illustrating the process of refrigerant flowing from the higher-pressure first channel 126 into the lower-pressure first channel 126 according to the present invention. Figure 7 This is a schematic diagram of the refrigeration system 1000 provided by the present invention. During operation, the refrigerant is throttled and depressurized by the expansion valve 200, then distributed by the distributor 20 into each capillary tube 11, and then into each heat exchange tube. Due to the different heights of the heat exchange tubes, the refrigerant pressures entering each heat exchange tube are different. After entering the heat exchange tubes, the refrigerant with higher pressure enters the lower pressure first channel 126 through the corresponding first channel 126 and inner cavity 123, achieving pressure equalization of the refrigerant in each heat exchange tube. When encountering severe operating conditions, especially when the refrigeration system 1000 is used for heating in northern winters, due to the sudden drop in temperature, the refrigerant in the heat exchanger 100 cannot evaporate completely. The excess refrigerant enters the inner cavity 123 through the first channel 126, and then returns to the inlet of the expansion valve 200 through the return port 124.

[0074] The technical features of the above-described embodiments 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 there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0075] Those skilled in the art should recognize that the above embodiments are merely illustrative of the present invention and are not intended to limit the present invention. Any appropriate changes and variations made to the above embodiments within the essential spirit of the present invention fall within the scope of protection claimed by the present invention.

Claims

1. A heat exchanger, characterized in that, include: Multiple heat exchange tubes are arranged at intervals along a first preset direction; A distributor (20) and multiple capillary tubes (11), one end of each capillary tube (11) is connected to the distributor (20), and the other end of each capillary tube (11) is connected to the inlet section of each heat exchange tube. And a balancing component (10), the balancing component (10) includes a manifold (12) and a plurality of branch pipes (122) connected to the manifold (12), each branch pipe (122) is connected to the inlet section of each heat exchange tube, each capillary tube (11) is connected to each branch pipe (122), and the plurality of heat exchange tubes are interconnected through the plurality of branch pipes (122) and the manifold (12).

2. The heat exchanger according to claim 1, characterized in that, The manifold (12) has multiple connection ports (121), each of which corresponds to a number of branch pipes (122). Each capillary tube (11) passes through the multiple connection ports (121) and is fitted into the branch pipe (122). Each of the multiple branch pipes (122) has a first channel (126) that communicates with multiple heat exchange tubes. The multiple first channels (126) are interconnected.

3. The heat exchanger according to claim 2, characterized in that, The outer wall of the capillary (11) and the inner wall of the branch (122) are fitted together to form the first channel (126).

4. The heat exchanger according to claim 3, characterized in that, The capillary tube (11) sleeved on the branch pipe (122) is coaxially arranged with the branch pipe (122); or, the outer wall of the capillary tube (11) sleeved on the branch pipe (122) is partially fitted with the inner wall of the branch pipe (122); or, the axial direction of the capillary tube (11) sleeved on the branch pipe (122) is at least partially eccentric to the axial direction of the branch pipe (122).

5. The heat exchanger according to claim 2, characterized in that, The capillary tube (11) is inserted through one end of the branch tube (122) and protrudes from the end face of the branch tube (122).

6. The heat exchanger according to claim 2, characterized in that, The sum of the lengths L1 of the capillary tube (11) extending into the manifold (12), the branch tube (122), and the heat exchange tube is 110mm to 120mm.

7. The heat exchanger according to claim 2, characterized in that, The manifold (12) is provided with an annular protrusion (125), which extends in a direction away from the branch pipe (122). The annular protrusion (125) is arranged around the connection port (121) and is sealed to the capillary tube (11).

8. The heat exchanger according to claim 1, characterized in that, The manifold (12) has an inner cavity (123), and multiple heat exchange tubes are interconnected through the inner cavity (123). The manifold (12) has a return port (124) that communicates with the inner cavity (123). The return port (124) is unidirectionally connected to the inlet of multiple capillary tubes (11); and / or, the length L2 of the branch pipe (122) is 50mm to 85mm.

9. A refrigeration system, characterized in that, The device includes an expansion valve (200) and a heat exchanger as described in any one of claims 1-8, wherein the outlet of the expansion valve (200) is connected to the inlet of the distributor (20), and the manifold (12) is provided with a return port (124) connected to the heat exchange tube, and the return port (124) is unidirectionally connected to the inlet of the expansion valve (200).

10. The refrigeration system according to claim 9, characterized in that, The refrigeration system also includes a check valve (300), the inlet of which is connected to the return port (124), and the outlet of which is connected to the inlet of the expansion valve (200).

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