Heat exchangers and air conditioners with them

Abstract

This utility model discloses a heat exchanger and an air conditioner having the same. The heat exchanger includes a heat exchange section and an inlet section. The heat exchange section has multiple refrigerant channels, and the inlet section includes a main pipe and multiple branch pipes. The branch pipes are connected to the multiple refrigerant channels. The two ends of the main pipe are an upstream end and a downstream end, respectively. The branch pipes are spaced apart along the length of the main pipe and are all connected to the main pipe. The main pipe has a reduced diameter section, and the flow area of ​​the main pipe decreases at the reduced diameter section from the upstream end to the downstream end. At least one branch pipe is arranged upstream and downstream of the reduced diameter section. In the above technical solution, the inlet section has a simple structure, does not require a distributor, occupies little space, is easy to arrange, and can save production and assembly costs. Furthermore, by setting a reduced diameter section in the main pipe of the inlet section, the flow velocity of the refrigerant flowing through the reduced diameter section increases, the dynamic pressure increases, and the static pressure decreases, resulting in a more balanced flow rate in the branch pipes along the main pipe, which is beneficial to improving the heat exchange effect of the heat exchanger.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning equipment, and in particular to a heat exchanger and an air conditioner having the same. Background Technology

[0002] From a performance and cost perspective, the trend in household air conditioner heat exchangers is to use smaller diameter refrigerant pipes (e.g., 5mm or 7mm in diameter) instead of larger diameter refrigerant pipes. Introducing smaller diameter refrigerant pipes means the heat exchanger needs more branch circuits. This necessitates a distributor at the heat exchanger's input end, using a distributor and manifolds to connect the multiple branch circuits within the heat exchanger. The more branch circuits there are, the more manifolds are needed. This results in a complex manifold system after the distributor, requiring more installation space. Furthermore, the thinner manifolds present greater challenges in the insertion and welding processes, leading to higher manufacturing costs. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a heat exchanger whose inlet section not only occupies a small space but also ensures a balanced refrigerant flow to each refrigerant channel, thereby improving the heat exchanger's heat exchange efficiency.

[0004] This utility model also proposes an air conditioner having the above-mentioned heat exchanger.

[0005] A heat exchanger according to a first aspect of the present invention includes: a heat exchange section having a plurality of refrigerant channels; an inlet section including a main pipe and a plurality of branch pipes, the plurality of branch pipes communicating with the plurality of refrigerant channels, the two ends of the main pipe being an upstream end and a downstream end, the plurality of branch pipes being spaced apart along the length direction of the main pipe and all being connected to the main pipe; wherein the main pipe has a reduced diameter section, the flow area of ​​the main pipe decreasing at the reduced diameter section along the direction from the upstream end to the downstream end, and at least one branch pipe being arranged upstream and downstream of the reduced diameter section respectively.

[0006] According to this invention, the heat exchanger delivers refrigerant to the heat exchange section via a main pipe and branch pipes, eliminating the need for a distributor. The inlet section has a simple structure, occupies little space, and is easy to arrange, thus saving production and assembly costs. Furthermore, by incorporating a narrowing section in the main pipe of the inlet section, the refrigerant flow velocity increases after passing through the narrowing section, resulting in higher dynamic pressure and lower static pressure. This ensures balanced flow across the branch pipes on the main pipe, improving the uniformity of heat exchange within the heat exchanger and enhancing its overall heat exchange performance.

[0007] In some embodiments, the inner diameter of the refrigerant channel is 2.5mm-7mm, the inner diameter of the main pipe is 6mm-20mm, the inner diameter of the branch pipe is 3mm-10mm, and the inner diameter of the reduced diameter section is 1mm-8mm.

[0008] In some embodiments, the main pipe includes a plurality of sub-pipe segments arranged sequentially along the length of the main pipe, wherein the flow area of ​​the downstream sub-pipe segment is smaller than that of the upstream sub-pipe segment, so as to form the diameter reduction at the connection of the two adjacent sub-pipe segments, and each sub-pipe segment is connected to at least one branch pipe.

[0009] In some embodiments, the main pipe includes two sub-pipe sections and a reduction in diameter, wherein the sub-pipe section located upstream of the reduction in diameter is the upstream pipe section, and the sub-pipe section located downstream of the reduction in diameter is the downstream pipe section.

[0010] In some embodiments, the total number of branch pipes connected to the upstream pipe segment is less than the total number of branch pipes connected to the downstream pipe segment, and the length L11 of the upstream pipe segment occupied by all the branch pipes connected to the upstream pipe segment is less than the length L21 of the downstream pipe segment occupied by all the branch pipes connected to the downstream pipe segment.

[0011] In some embodiments, the main pipe includes at least three of the sub-pipe segments and at least two of the reduced diameter sections.

[0012] In some embodiments, each of the sub-pipe segments is a straight circular pipe with a constant cross-section, and the ratio of the inner diameter of the downstream sub-pipe segment to the inner diameter of the upstream sub-pipe segment is 0.6-0.9; or, at least one of the sub-pipe segments is a pipe with a variable cross-section and the flow area gradually decreases along the direction from the upstream end to the downstream end.

[0013] In some embodiments, two adjacent sub-pipe segments are an upstream sub-pipe segment and a downstream sub-pipe segment, wherein the downstream end of the upstream sub-pipe segment is narrowed and fitted outside the upstream end of the downstream sub-pipe segment, or the upstream end of the downstream sub-pipe segment is widened and fitted outside the downstream end of the upstream sub-pipe segment.

[0014] In some embodiments, the input section satisfies at least one of the following four conditions: Condition 1, the distance between the reduced diameter section and its nearest upstream branch pipe is 1-60 mm; Condition 2, the distance between the reduced diameter section and its nearest downstream branch pipe is 1-60 mm; Condition 3, the distance between two adjacent branch pipes on the same sub-pipe segment is greater than 5 mm; Condition 4, the distance between the two nearest adjacent branch pipes on two adjacent sub-pipe segments is the cross-pipe distance, the distance between two adjacent branch pipes on the same sub-pipe segment is the same-pipe distance, and the same-pipe distance is less than the cross-pipe distance.

[0015] In some embodiments, at least two of the branch pipes have the same inner diameter; or, at least two of the branch pipes have different inner diameters, and in two adjacent branch pipes with different inner diameters, the branch pipe with the larger inner diameter is located upstream of the branch pipe with the smaller inner diameter.

[0016] In some embodiments, at least two of the branch pipes are of the same length; or, at least two of the branch pipes are of different lengths, wherein in two adjacent branch pipes of different lengths, the branch pipe with the larger length is located downstream of the branch pipe with the smaller length.

[0017] In some embodiments, at least one of the branch pipes includes an extension section extending into the main pipe, the end of the extension section defining an opening communicating with the main pipe; wherein the opening is a flat opening and the normal of the flat opening is orthogonal to the axial direction of the main pipe; or, the opening is an oblique opening, the normal of the oblique opening intersecting the axial direction of the main pipe at an acute angle, the oblique opening opening towards the upstream end or towards the downstream end.

[0018] In some embodiments, at least two of the branch pipes include the extension section; wherein the extension length of the extension section of the at least two branch pipes is the same; or, the extension length of the extension section of the at least two branch pipes is different, and of the two branch pipes with different extension lengths, the branch pipe with the larger extension length is located downstream of the branch pipe with the smaller extension length.

[0019] In some embodiments, the branch pipe furthest from the upstream end is a tail end branch pipe, which is connected to the side wall of the main pipe or to the shaft end of the main pipe.

[0020] An air conditioner according to a second aspect of the present invention includes a heat exchanger according to a first aspect of the present invention.

[0021] According to the present invention, by setting the heat exchanger of the first aspect, the space required for the heat exchanger can be reduced, which is beneficial to the miniaturization of the air conditioner.

[0022] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the structure of a heat exchanger according to an embodiment of the present invention;

[0024] Figure 2 This is a schematic diagram of the structure of the input section according to an embodiment of the present invention;

[0025] Figure 3 This is a schematic diagram of the total pressure distribution of the input section according to an embodiment of the present invention;

[0026] Figure 4 This is a schematic diagram of the static pressure distribution of the input section according to an embodiment of the present invention;

[0027] Figure 5 This is a schematic diagram of the dynamic pressure distribution of the input section according to an embodiment of the present invention;

[0028] Figure 6 This is another structural schematic diagram of the input section according to one embodiment of the present invention;

[0029] Figure 7 This is a schematic diagram of the input section according to another embodiment of the present invention;

[0030] Figure 8 It is based on Figure 6 The example shown is a cross-sectional view of section AA.

[0031] Figure 9 It is based on Figure 8 A magnified view of region B in the example shown;

[0032] Figure 10 It is based on Figure 8 A magnified view of region C in the example shown.

[0033] Figure label:

[0034] Heat exchanger 1000; heat exchange section 100; inlet section 200;

[0035] Main pipe 1; Upstream end 11; Downstream end 12; Narrowing section 13;

[0036] Sub-pipe section 1a; upstream sub-pipe section 1a1; downstream sub-pipe section 1a2; upstream pipe section 14; downstream pipe section 15;

[0037] Branch pipe 2; extension section 21; opening 211; tail end branch pipe 2a. Detailed Implementation

[0038] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0039] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0040] The heat exchanger 1000 of the first aspect of the present invention is described below with reference to the accompanying drawings.

[0041] According to the embodiment of the present utility model, the heat exchanger 1000, such as Figure 1 and Figure 2 As shown, the heat exchanger 1000 includes a heat exchange section 100 and an inlet section 200. The heat exchange section 100 has multiple refrigerant channels. The inlet section 200 includes a main pipe 1 and multiple branch pipes 2. The multiple branch pipes 2 are connected to the multiple refrigerant channels. The two ends of the main pipe 1 are an upstream end 11 and a downstream end 12, respectively. The multiple branch pipes 2 are spaced apart along the length of the main pipe 1 and are all connected to the main pipe 1. The main pipe 1 has a diameter reduction section 13. The flow area of ​​the main pipe 1 decreases at the diameter reduction section 13 along the direction from the upstream end 11 to the downstream end 12. At least one branch pipe 2 is arranged upstream and downstream of the diameter reduction section 13, respectively.

[0042] The heat exchanger 1000 includes a heat exchange section 100 and an inlet section 200. The heat exchange section 100 is used for heat exchange and has multiple refrigerant channels in which the refrigerant flows and exchanges heat. The inlet section 200 supplies refrigerant to the refrigerant channels of the heat exchanger 1000.

[0043] The method of defining the refrigerant passages included in the heat exchange section 100 is not limited. For example, the refrigerant passages can be defined by pipes or they can be channels processed on the plate. The specific method of connecting the multiple branch pipes 2 to the multiple refrigerant passages is not limited. It can be that the multiple branch pipes 2 are connected to the multiple refrigerant passages in a one-to-one correspondence, or that one branch pipe 2 is connected to at least two refrigerant passages in a corresponding correspondence.

[0044] The input section 200 of this embodiment is constructed as a pipeline. Refrigerant flows from the upstream end 11 to the downstream end 12 of the main pipe 1. Multiple branch pipes 2 connect the main pipe 1 and the refrigerant channel, guiding the refrigerant in the main pipe 1 into the refrigerant channel. By setting the main pipe 1 and branch pipes 2 to deliver refrigerant to the refrigerant channel of the heat exchange section 100, a distributor is not required. The input section 200 has a simple structure, occupies little space, and is easy to arrange. It can avoid the weld blockage problem caused by the springback of the inserted tube during the welding process of using finer flow tubes, and reduces the amount of copper tubes used, thus saving production and assembly costs.

[0045] It is worth noting that fluid pressure can be decomposed into dynamic pressure, static pressure, and total pressure, with static pressure truly determining the fluid splitting characteristics. As the refrigerant flows and gradually splits within the main pipe, the flow velocity decreases, the dynamic pressure decreases, and the static pressure increases. Therefore, the splitting pattern is as follows: for single-phase flow or two-phase flow with low dryness fraction, when the overall pressure drop within the pipe is not significant, the branch farther from the inlet receives a higher mass flow rate; that is, the flow rate of the branch closer to the downstream end is greater than that of the branch closer to the upstream end. Therefore, in related technologies, although the method of directly supplying refrigerant to the heat exchanger through pipelines is simple in structure and occupies less space, the different static pressures at various points in the pipeline result in different refrigerant flow rates at different points, leading to uneven heat exchange in the heat exchanger and affecting its normal operation.

[0046] In this embodiment of the heat exchanger 1000, a narrowing section 13 is provided at the main pipe 1 of the inlet section 200. The flow area of ​​the main pipe 1 decreases at the narrowing section 13 along the direction from the upstream end 11 to the downstream end 12, thereby increasing the refrigerant flow velocity through the narrowing section 13. The increased refrigerant velocity after flowing through the narrowing section 13 leads to increased dynamic pressure and decreased static pressure, thereby reducing the flow rate obtained by the branch pipe 2 near the downstream end 12.

[0047] like Figure 3 The diagram shown is a schematic representation of the total pressure distribution of the input section 200 according to an embodiment of the present invention. Figure 4 The diagram shown is a static pressure distribution diagram of the input section 200 according to an embodiment of the present invention. Figure 5 The diagram shown is a schematic representation of the dynamic pressure distribution of the input section 200 according to an embodiment of the present invention. (See attached diagram.) Figure 4 It can be clearly seen that the static pressure of the refrigerant after the narrowing section 13 is significantly reduced, and even at the downstream end 12, the static pressure does not rise excessively. (According to the attached...) Figure 5It can be clearly seen that the dynamic pressure of the refrigerant after passing through the narrowing section 13 increases significantly after a period of flow stabilization. This reduces the static pressure of the refrigerant near the downstream end 12, thereby balancing the flow rate of the multiple branch pipes 2. The balanced refrigerant flow rate delivered to the refrigerant channels by the branch pipes 2 improves the heat exchange uniformity of the refrigerant within the heat exchanger 1000, which is beneficial for improving the heat exchange effect of the heat exchanger 1000. The input section 200 of this embodiment not only occupies a small space but also ensures a balanced supply of refrigerant to each refrigerant channel, thus improving the heat exchange effect of the heat exchanger 1000.

[0048] In addition, the low pressure drop diversion design of the input section 200 in this embodiment of the present invention can also reduce refrigerant noise and reduce the operating noise of the heat exchanger 1000.

[0049] According to the embodiment of the present invention, the heat exchanger 1000 supplies refrigerant to the refrigerant channel of the heat exchange section 100 through a main pipe 1 and branch pipes 2, eliminating the need for a distributor. The input section 200 has a simple structure, occupies little space, and is easy to arrange, thus saving production and assembly costs. Furthermore, by providing a narrowing section 13 in the main pipe 1 of the input section 200, the flow velocity of the refrigerant after passing through the narrowing section 13 increases, the dynamic pressure increases, and the static pressure decreases. This ensures that the flow rate of the branch pipes 2 on the main pipe 1 is balanced, which improves the heat exchange uniformity of the refrigerant in the heat exchanger 1000 and is beneficial to improving the heat exchange effect of the heat exchanger 1000.

[0050] In some embodiments of this utility model, the inner diameter of the refrigerant channel is 2.5mm-7mm, the inner diameter of the main pipe 1 is 6mm-20mm, the inner diameter of the branch pipe 2 is 3mm-10mm, and the inner diameter of the reduced diameter section 13 is 1mm-8mm.

[0051] For cases where the pipe diameter of the refrigerant path is small, the refrigerant flow rate through the reduced diameter section 13 can be significantly accelerated by setting the reduced diameter section 13, so that the refrigerant distribution balance effect of each branch pipe 2 is more obvious.

[0052] Optionally, the inner diameter of the refrigerant channel is 2.5mm, 3mm, 4mm, 5mm, 7mm, etc.

[0053] Optionally, the inner diameter of the main pipe 1 can be 6mm, 9.52mm, 12.7mm, 15.2mm, 20mm, etc.

[0054] Optionally, the inner diameter of branch pipe 2 can be 3mm, 5mm, 8mm, 9.52mm, 10mm, etc.

[0055] Optionally, the inner diameter of the reduced diameter 13 can be 1mm, 2.5mm, 4mm, 5mm, 8mm, etc.

[0056] In some embodiments of this utility model, such as Figure 2As shown, the main pipe 1 includes a plurality of sub-pipe segments 1a arranged sequentially along the length of the main pipe 1. The flow area of ​​the downstream sub-pipe segment 1a is smaller than that of the upstream sub-pipe segment 1a, so as to form a narrowing section 13 at the connection of the two adjacent sub-pipe segments 1a. Each sub-pipe segment 1a is connected to at least one branch pipe 2.

[0057] The refrigerant in the main pipe 1 flows from the upstream end 11 to the downstream end 12. In two adjacent sub-pipe sections 1a, the refrigerant flows from the upstream sub-pipe section 1a (e.g., Figure 2 The upstream pipe segment 14 shown flows to the downstream sub-pipe segment 1a (e.g. Figure 2 The downstream pipe section 15 shown has a smaller flow area than the upstream sub-pipe section 1a, and a narrowing section 13 is formed at the junction of the two sub-pipe sections 1a.

[0058] By setting the flow area of ​​the downstream sub-pipe section 1a to be smaller than that of the upstream sub-pipe section 1a, the refrigerant, which accelerates its flow through the narrowing section 13, naturally increases its velocity in the downstream sub-pipe section 1a. Furthermore, due to the reduced flow area in the downstream sub-pipe section 1a, the refrigerant velocity can be maintained at a relatively high speed. The increased refrigerant velocity in the downstream sub-pipe section 1a leads to increased dynamic pressure and decreased static pressure, resulting in a more balanced flow rate between the branch pipe 2 connected to the upstream sub-pipe section 1a and the branch pipe 2 connected to the downstream sub-pipe section 1a. This improves the heat exchange uniformity of the refrigerant within the heat exchanger 1000, thereby enhancing the heat exchange performance of the heat exchanger 1000.

[0059] In some embodiments of this utility model, the downstream sub-pipe segment 1a of two adjacent sub-pipe segments 1a (e.g.) Figure 2 The flow area of ​​the downstream pipe segment 15 shown is smaller than that of the upstream sub-pipe segment 1a (e.g., Figure 2 The flow area of ​​the upstream pipe section 14 shown is used to form a narrowing section 13 at the connection of two adjacent sub-pipe sections 1a. The flow area of ​​the downstream sub-pipe section 1a is less than or equal to the flow area of ​​the narrowing section 13, and the flow area of ​​the upstream sub-pipe section 1a is greater than or equal to the flow area of ​​the narrowing section 13. In this way, the flow velocity of the refrigerant increases after flowing through the narrowing section 13 and can quickly tend to stabilize. The increased flow velocity stabilizes the flow, which is beneficial to improving the distribution of refrigerant to multiple branch pipes 2.

[0060] In some other embodiments of this invention, the flow area of ​​the downstream sub-pipe section 1a in two adjacent sub-pipe sections 1a can also be greater than the flow area of ​​the narrowing section 13. Thus, when the refrigerant flows from the upstream sub-pipe section 1a to the downstream sub-pipe section 1a, the refrigerant velocity increases as it flows through the narrowing section 13 between adjacent sub-pipe sections 1a, while the refrigerant velocity flowing into the downstream sub-pipe section 1a remains relatively high. The increased refrigerant velocity in the downstream sub-pipe section 1a leads to increased dynamic pressure and decreased static pressure, resulting in a more balanced flow rate between the branch pipe 2 connected to the upstream sub-pipe section 1a and the branch pipe 2 connected to the downstream sub-pipe section 1a. This improves the heat exchange uniformity of the refrigerant within the heat exchanger 1000, thereby enhancing the heat exchange effect of the heat exchanger 1000.

[0061] In some embodiments of this utility model, the length of the reduced diameter portion 13 is 3mm-20mm. Optionally, the length of the reduced diameter portion 13 can be 3mm, 10mm, 12.5mm, 15mm, 20mm, etc.

[0062] In some embodiments of this utility model, such as Figure 2 As shown, the main pipe 1 includes two sub-pipe sections 1a and a narrowing section 13. The sub-pipe section 1a located upstream of the narrowing section 13 is the upstream pipe section 14, and the sub-pipe section 1a located downstream of the narrowing section 13 is the downstream pipe section 15.

[0063] Branch pipe 2 includes two upstream pipe sections 14 and a downstream pipe section 15. A narrowing section 13 is formed at the connection between the upstream pipe sections 14 and the downstream pipe section 15. Refrigerant flows from the upstream pipe section 14 to the downstream pipe section 15. After passing through the narrowing section 13, the refrigerant velocity increases. Since the flow area of ​​the downstream pipe section 15 is smaller than that of the upstream pipe section 14, the refrigerant velocity in the downstream pipe section 15 is greater than that in the upstream pipe section 14. The increased refrigerant velocity in the downstream sub-pipe section 1a leads to increased dynamic pressure and decreased static pressure, resulting in a balanced flow rate between the branch pipe 2 connected to the upstream pipe section 14 and the branch pipe 2 connected to the downstream pipe section 15.

[0064] In some embodiments of this utility model, such as Figure 6 As shown, the total number of branch pipes 2 connected to the upstream pipe segment 14 is less than the total number of branch pipes 2 connected to the downstream pipe segment 15, and the length L11 occupied by all branch pipes 2 connected to the upstream pipe segment 14 is less than the length L21 occupied by all branch pipes 2 connected to the downstream pipe segment 15. This is beneficial for achieving a more balanced flow distribution between the branch pipes 2 connected to the upstream pipe segment 14 and the branch pipes 2 connected to the downstream pipe segment 15.

[0065] In some embodiments of this utility model, the length L1 of the upstream pipe section 14 is less than the length L2 of the downstream pipe section 15. Since the number of branch pipes 2 connected to the downstream pipe section 15 is increased, the number of branch pipes 2 connected to the downstream pipe section 15 is larger, and the length L21 of the downstream pipe section 15 occupied is also larger. Setting the length L1 of the upstream pipe section 14 to be less than the length L2 of the downstream pipe section 15 makes the arrangement of the main pipe 1 and the branch pipes 2 reasonable.

[0066] It is worth noting that the present invention sets a reduction diameter section 13 on the main pipe 1, and then changes the number and arrangement range of the branch pipes 2, all for the purpose of balancing the flow of multiple branch pipes 2. Therefore, in some other embodiments of the present invention, the length L1 of the upstream pipe section 14 can be set to be greater than the length L2 of the downstream pipe section 15, and then the branch pipes 2 can be rearranged to balance the refrigerant flow of multiple inflowing branch pipes 2, which is also within the protection scope of the present invention.

[0067] In some embodiments of this utility model, such as Figure 7 As shown, the main pipe 1 includes at least three sub-pipe sections 1a and at least two diameter reduction sections 13. By setting at least three sub-pipe sections 1a, the refrigerant flow rate can be gradually increased, the dynamic pressure can be raised, and the static pressure can be lowered, thereby making the flow distribution of all branch pipes 2 more balanced.

[0068] In some embodiments of this utility model, such as Figure 2 As shown, each sub-pipe segment 1a is a straight circular pipe with a uniform cross-section, and the ratio of the inner diameter of the downstream sub-pipe segment to the inner diameter of the upstream sub-pipe segment in two adjacent sub-pipe segments 1a is 0.6-0.9.

[0069] Sub-pipe section 1a is a straight circular pipe with a constant cross-section, which can improve the flow stability of the refrigerant and reduce manufacturing costs.

[0070] The ratio of the inner diameter of the upstream sub-pipe segment 1a to the inner diameter of the downstream sub-pipe segment 1a in two adjacent sub-pipe segments 1a is 0.6-0.9, which can effectively improve the flow distribution balance of multiple branch pipes 2.

[0071] Optionally, the ratio of the inner diameter of the downstream sub-pipe segment 1a to the inner diameter of the upstream sub-pipe segment can be 0.6, 0.7, 0.75, 0.8, 0.9, etc.

[0072] In some embodiments of this utility model, at least one sub-pipe segment 1a is a variable cross-section pipe, and the flow area of ​​the variable cross-section pipe segment 1a gradually decreases along the direction from the upstream end 11 to the downstream end 12.

[0073] As the flow area of ​​sub-pipe section 1a gradually decreases, the refrigerant velocity flowing within sub-pipe section 1a gradually increases, thereby reducing the refrigerant flow rate of the downstream branch pipe 2 on sub-pipe section 1a and balancing the flow distribution among the multiple branch pipes 2 connected to the sub-pipe.

[0074] In some embodiments of this utility model, the main pipe 1 is a one-piece molded part, which can improve the overall reliability and sealing performance of the main pipe 1.

[0075] In some other embodiments of this utility model, the main pipe 1 includes a plurality of sub-pipe segments 1a connected in sequence, and two adjacent sub-pipe segments 1a are assembled and connected, thereby reducing the manufacturing difficulty of the input part 200 and saving manufacturing costs.

[0076] In some embodiments of this utility model, the main pipe 1 includes a plurality of sub-pipe segments 1a arranged sequentially along the length direction of the main pipe 1. Adjacent sub-pipe segments 1a can be connected by either narrowing or widening.

[0077] In some embodiments of this utility model, such as Figure 8 and Figure 9 As shown, two adjacent sub-pipe segments 1a are respectively the upstream sub-pipe segment 1a1 and the downstream sub-pipe segment 1a2, wherein the downstream end of the upstream sub-pipe segment 1a1 is narrowed and fitted over the upstream end of the downstream sub-pipe segment 1a2. Alternatively, in some other embodiments of this utility model, the upstream end of the downstream sub-pipe segment 1a2 is widened and fitted over the downstream end of the upstream sub-pipe segment 1a1 (this embodiment is not shown in the figure).

[0078] This reduces the difficulty of processing and forming sub-pipe segment 1a, and also reduces the difficulty of connecting two adjacent sub-pipe segments 1a. In addition, the sleeve connection between two adjacent sub-pipe segments 1a can improve the sealing performance between the two adjacent sub-pipe segments 1a and improve the connection stability between the sub-pipe segments 1a.

[0079] The diameter of the upstream sub-pipe section 1a1 is larger than that of the downstream sub-pipe section 1a2. The downstream end of the upstream sub-pipe section 1a1 can be narrowed and fitted outside the upstream end of the downstream sub-pipe section 1a2, or the upstream end of the downstream sub-pipe section 1a2 can be widened and fitted outside the downstream end of the downstream sub-pipe section 1a2.

[0080] In some embodiments of this utility model, the materials of the main pipe 1 and the branch pipe 2 are not limited, for example, they can be copper pipes, stainless steel pipes, sprayed carbon steel pipes or aluminum pipes.

[0081] In some embodiments of this utility model, reference is made to Figures 8-9 The input unit 200 satisfies at least one of the following four conditions:

[0082] Condition 1: The distance D1 between the reduced diameter section 13 and its nearest upstream branch pipe 2 is 1-60mm;

[0083] Condition 2: The distance D2 between the reduced diameter section 13 and its nearest downstream branch pipe 2 is 1-60mm;

[0084] Condition 3: The distance L4 between two adjacent branch pipes 2 on the same sub-pipe segment 1a is greater than 5mm;

[0085] Condition 4: The distance between the two nearest adjacent branch pipes 2 on two adjacent sub-pipe segments 1a is the cross-pipe distance L3, and the distance between the two adjacent branch pipes 2 on the same sub-pipe segment 1a is the same-pipe distance L4. The same-pipe distance L4 is less than the cross-pipe distance L3.

[0086] It is understandable that the refrigerant flow state changes when it flows through the narrowing section 13, which affects the refrigerant flow rate of branch pipe 2 near the narrowing section 13. The refrigerant flow further away from the narrowing section 13 tends to be stable, having a smaller impact on the refrigerant flow rate of branch pipe 2. The refrigerant velocity increases when it flows through the narrowing section 13. If the distance from the nearest branch pipe 2 to the narrowing section 13 is too great, the flow rate at the branch pipe 2 furthest from the narrowing section 13 will be significantly reduced. Therefore, if... Figure 9 As shown, the distance D1 from the upstream branch pipe 2 to the narrowing point 13 is 1-60mm, and the distance D2 from the downstream branch pipe 2 to the narrowing point 13 is 1-60mm, so that the flow distribution of multiple branch pipes 2 on sub-pipe section 1a is balanced.

[0087] The spacing L4 between two adjacent branch pipes 2 on the same sub-pipe section 1a is greater than 5mm, which is beneficial to manufacturability.

[0088] like Figure 8 As shown, the distance between the two nearest branch pipes 2 on two adjacent sub-pipe sections 1a is the cross-pipe spacing L3, and the distance between two adjacent branch pipes 2 on the same sub-pipe section 1a is the same-pipe spacing L4. The same-pipe spacing L4 is smaller than the cross-pipe spacing L3. This is beneficial for improving structural compactness and has a good impact on the balanced flow distribution.

[0089] This invention increases the downstream flow velocity by setting a narrowing section 13 in the main pipe 1 of the inlet section 200, thereby increasing the dynamic pressure, decreasing the static pressure, and reducing the refrigerant flow rate into the downstream branch pipes 2, thus achieving a more balanced flow rate across the branch pipes 2 on the main pipe 1. Furthermore, some embodiments of this invention can adjust the size or position of the branch pipes 2 to regulate the flow rate of each branch, further enhancing the balance of flow rate across the branch pipes 2 on the main pipe 1.

[0090] For example, the diameter of the branch pipe 2 can be controlled to reduce the diameter of the branch with excessive flow or increase the diameter of the branch with insufficient flow; or, the flow of each branch can be precisely controlled by methods such as oblique cut of the branch pipe 2, adjusting the insertion depth of the branch pipe 2, or adjusting the arrangement position of the branch pipe 2.

[0091] In some embodiments of this utility model, at least two branch pipes 2 have the same inner diameter; or, at least two branch pipes 2 have different inner diameters, and among two adjacent branch pipes 2 with different inner diameters, the branch pipe 2 with the larger inner diameter is located upstream of the branch pipe 2 with the smaller inner diameter.

[0092] The inner diameter of branch pipe 2 can be set to be the same, and branch pipe 2 can be manufactured uniformly, which can reduce production and manufacturing costs.

[0093] The inner diameter of branch pipe 2 can also be different. Due to the flow characteristics of the fluid, the flow distribution of branch pipe 2 near the downstream end 12 will still be slightly greater than that of branch pipe 2 near the upstream end 11. Therefore, by increasing the inner diameter of the upstream branch pipe 2, the flow distribution of multiple branch pipes 2 can be further balanced.

[0094] In some embodiments of this utility model, at least two branch pipes 2 have the same length; or, at least two branch pipes 2 have different lengths, and among two adjacent branch pipes 2 with different lengths, the branch pipe 2 with the larger length is located downstream of the branch pipe 2 with the smaller length.

[0095] The lengths of each branch pipe 2 can be the same or different, and the flow rate of each branch can be controlled by the length of the branch pipe 2.

[0096] The length of branch pipe 2 can be set to be the same, and the branch pipe 2 can be manufactured uniformly, which can reduce production and manufacturing costs.

[0097] The lengths of the branch pipes 2 can also vary, thereby adjusting the positional relationship between the inlet section 200 and the heat exchange section 100, reducing the space occupied by the inlet section 200, and facilitating the arrangement of the inlet section 200. Furthermore, by increasing the length of the downstream branch pipes 2, the flow distribution among the multiple branch pipes 2 can be further balanced.

[0098] In some embodiments of this utility model, such as Figure 8 and Figure 9 As shown, at least one branch pipe 2 includes an extension section 21 extending into the main pipe 1, the end of which defines an opening 211 communicating with the main pipe 1; wherein, the opening 211 is a flat opening 211, and the normal of the flat opening 211 is orthogonal to the axis of the main pipe 1; or, the opening 211 is an oblique opening 211, the normal of the oblique opening 211 intersecting the axis of the main pipe 1 at an acute angle, the oblique opening 211 opening towards the upstream end 11 or towards the downstream end 12. The normal of the opening 211 refers to the direction perpendicular to the plane defined by the edge of the opening 211.

[0099] The extension section 21 of the branch pipe 2 extends into the main pipe 1, which can improve the connection stability between the branch pipe 2 and the main pipe 1. The end of the extension section 21 defines an opening 211, and the refrigerant flowing in the main pipe 1 flows into the branch pipe 2 only through the opening 211. The opening 211 can be a flat cut or a beveled cut, and the beveled surface of the cut can face, turn away from, or be lateral to the inflow end.

[0100] The opening 211 can be a flat opening 211, and the direction of the opening 211 of the flat opening 211 is orthogonal to the axis of the main pipe 1.

[0101] The opening 211 can also be an oblique opening 211. The direction of the oblique opening 211 intersects the axis of the main pipe 1 at an acute angle. When the oblique opening 211 is open towards the upstream end 11, the refrigerant flow into the branch pipe 2 can be increased; when the oblique opening 211 is open towards the downstream end 12, the refrigerant flow into the branch pipe 2 can be reduced. Therefore, by setting the opening 211 of the branch pipe 2 in different directions, the flow distribution of multiple branch pipes 2 can be further balanced.

[0102] In some embodiments of this utility model, at least two branch pipes 2 include an extension section 21; wherein the extension length of the extension section 21 of at least two branch pipes 2 is the same; or, the extension length of the extension section 21 of at least two branch pipes 2 is different, and among the two branch pipes 2 with different extension lengths, the branch pipe 2 with the larger extension length is located downstream of the branch pipe 2 with the smaller extension length.

[0103] The extension section 21 of the branch pipe 2 extends into the main pipe 1, which can improve the stability of the connection between the branch pipe 2 and the main pipe 1. The insertion depth of the branch pipe 2 can be the same or different.

[0104] The insertion length of the extension section 21 of the branch pipe 2 can be the same, which can reduce assembly and manufacturing costs.

[0105] The insertion length of the extension section 21 of branch pipe 2 can also be different, such as... Figure 10 As shown, the extension length L5 of the extension section 21 of the downstream branch pipe 2 is greater than the extension length L6 of the extension section 21 of the upstream branch pipe 2, which can further balance the flow distribution of multiple branch pipes 2.

[0106] In some embodiments of this utility model, the branch pipe 2 furthest from the upstream end 11 is the tail end branch pipe 2a, which is connected to the side wall of the main pipe 1 (see reference). Figure 7 ), or connected to the shaft end of main pipe 1 (see reference). Figure 2 and Figure 8 ).

[0107] Tail-end branch pipe 2a can be arranged from the side like other branch pipes 2, or it can be arranged as... Figure 2 and Figure 8 As shown, it flows directly out from the tail of pipe 1. This allows for processing flexibility and meets different practical needs.

[0108] An air conditioner according to a second aspect of the present invention includes a heat exchanger 1000 according to a first aspect of the present invention.

[0109] According to the embodiments of the present invention, by providing the heat exchanger 1000 of the first aspect of the present invention, the arrangement space of the heat exchanger 1000 can be reduced, which is beneficial to the miniaturization of the air conditioner.

[0110] The type of air conditioner is not limited; for example, it can be an integrated air conditioner or a split air conditioner. In some embodiments of this utility model, the heat exchanger 1000 is an indoor heat exchanger, which functions as an evaporator in cooling mode and as a condenser in heating mode.

[0111] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0112] 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 one or more of that feature. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0113] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0114] In this utility model, 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 is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply 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 that the first feature is at a lower horizontal level than the second feature.

[0115] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0116] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A heat exchanger, characterized in that, include: The heat exchange section has multiple refrigerant channels; The input section includes a main pipe and multiple branch pipes, the multiple branch pipes being connected to multiple refrigerant channels, the two ends of the main pipe being an upstream end and a downstream end, and the multiple branch pipes being spaced apart along the length of the main pipe and all being connected to the main pipe; The main pipe has a reduced diameter section, and the flow area of ​​the main pipe decreases at the reduced diameter section along the direction from the upstream end to the downstream end. At least one branch pipe is arranged upstream and downstream of the reduced diameter section, respectively.

2. The heat exchanger according to claim 1, characterized in that, The inner diameter of the refrigerant channel is 2.5mm-7mm, the inner diameter of the main pipe is 6mm-20mm, the inner diameter of the branch pipe is 3mm-10mm, and the inner diameter of the reduced diameter section is 1mm-8mm.

3. The heat exchanger according to claim 1, characterized in that, The main pipe includes a plurality of sub-pipe segments arranged sequentially along the length of the main pipe. The flow area of ​​the downstream sub-pipe segment is smaller than that of the upstream sub-pipe segment, so as to form the diameter reduction at the connection of the two adjacent sub-pipe segments. Each sub-pipe segment is connected to at least one branch pipe.

4. The heat exchanger according to claim 3, characterized in that, The main pipe includes two sub-pipe sections and a diameter reduction point. The sub-pipe section located upstream of the diameter reduction point is the upstream pipe section, and the sub-pipe section located downstream of the diameter reduction point is the downstream pipe section.

5. The heat exchanger according to claim 4, characterized in that, The total number of branch pipes connected to the upstream pipe segment is less than the total number of branch pipes connected to the downstream pipe segment, and the length of the upstream pipe segment occupied by all the branch pipes connected to the upstream pipe segment is less than the length of the downstream pipe segment occupied by all the branch pipes connected to the downstream pipe segment.

6. The heat exchanger according to claim 3, characterized in that, The main pipe includes at least three of the sub-pipe sections and at least two of the reduced diameter sections.

7. The heat exchanger according to claim 3, characterized in that, Each of the sub-pipe segments is a straight circular pipe with a constant cross-section, and the ratio of the inner diameter of the downstream sub-pipe segment to the inner diameter of the upstream sub-pipe segment is 0.6-0.9; or, at least one of the sub-pipe segments is a pipe with a variable cross-section and the flow area gradually decreases along the direction from the upstream end to the downstream end.

8. The heat exchanger according to claim 3, characterized in that, The two adjacent sub-pipe segments are an upstream sub-pipe segment and a downstream sub-pipe segment, wherein the downstream end of the upstream sub-pipe segment is narrowed and fitted outside the upstream end of the downstream sub-pipe segment, or the upstream end of the downstream sub-pipe segment is widened and fitted outside the downstream end of the upstream sub-pipe segment.

9. The heat exchanger according to claim 3, characterized in that, The input section satisfies at least one of the following four conditions. Condition 1: The distance between the reduced diameter section and the nearest upstream branch pipe is 1-60mm; Condition 2: The distance between the reduced diameter section and the nearest downstream branch pipe is 1-60mm; Condition 3: The distance between two adjacent branch pipes on the same sub-pipe segment is greater than 5 mm; Condition 4: The distance between the two nearest adjacent branch pipes on two adjacent sub-pipe segments is the cross-pipe distance, and the distance between the two adjacent branch pipes on the same sub-pipe segment is the same-pipe distance, wherein the same-pipe distance is less than the cross-pipe distance.

10. The heat exchanger according to claim 1, characterized in that, At least two of the branch pipes have the same inner diameter; Alternatively, at least two of the branch pipes have different inner diameters, and among two adjacent branch pipes with different inner diameters, the branch pipe with the larger inner diameter is located upstream of the branch pipe with the smaller inner diameter.

11. The heat exchanger according to claim 1, characterized in that, At least two of the branch pipes are of the same length; Alternatively, at least two of the branch pipes have different lengths, and of the two adjacent branch pipes with different lengths, the branch pipe with the larger length is located downstream of the branch pipe with the smaller length.

12. The heat exchanger according to claim 1, characterized in that, At least one of the branch pipes includes an extension section that extends into the main pipe, the end of the extension section defining an opening communicating with the main pipe; Wherein, the opening is a flat opening, and the normal of the flat opening is orthogonal to the axis of the main pipe; or, the opening is an oblique opening, and the normal of the oblique opening intersects the axis of the main pipe at an acute angle, and the oblique opening is open to the upstream end or to the downstream end.

13. The heat exchanger according to claim 12, characterized in that, At least two of the branch pipes include the extension section; wherein the extension length of the extension section of the at least two branch pipes is the same; or, the extension length of the extension section of the at least two branch pipes is different, and of the two branch pipes with different extension lengths, the branch pipe with the larger extension length is located downstream of the branch pipe with the smaller extension length.

14. The heat exchanger according to claim 1, characterized in that, The branch pipe furthest from the upstream end is the tail end branch pipe, which is connected to the side wall of the main pipe or to the shaft end of the main pipe.

15. An air conditioner, characterized in that, Includes the heat exchanger according to any one of claims 1-14.

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