Heat exchanger, flow distribution component of heat exchanger and refrigeration equipment

Abstract

The utility model provides a heat exchanger, a flow distribution component thereof and refrigeration equipment, the flow distribution component of the heat exchanger comprises a shell and a flow baffle, a fluid channel is arranged in the shell, the fluid channel is provided with a fluid inlet and a fluid outlet which are oppositely arranged, and the cross sectional area of the fluid outlet is larger than that of the fluid inlet; the flow baffle is arranged in the fluid channel and close to the fluid outlet, and the flow baffle covers the fluid outlet; the flow baffle is provided with a center area and an outer area, the center area is opposite to the fluid inlet of the fluid channel, and the outer area is located on the outer side of the center area; a plurality of flow distribution holes penetrating through the flow baffle in the thickness direction are formed in the flow baffle; the cross-sectional area of the largest flow distribution hole located in the central area is smaller than the cross-sectional area of the smallest flow distribution hole located in the outer area. The flow distribution component can effectively improve the distribution uniformity of fluid flow in each channel, and is a heat exchanger easy to process.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, specifically to a heat exchanger and its flow distribution component, and a refrigeration device. Background Technology

[0002] In practical applications, plate heat exchangers suffer from uneven fluid flow distribution across different channels due to flow resistance losses and gas-liquid phase stratification. This uneven distribution is particularly pronounced when used as an evaporator, leading to large overheated areas in localized regions. These areas result in lower heat transfer coefficients, smaller temperature differences between the refrigerant and the heat source fluid, and ultimately, reduced heat exchanger performance. To maximize heat exchanger performance, the flow distribution process needs to be adjusted to ensure a more uniform flow distribution across all channels.

[0003] Currently, the main methods for distributing and regulating refrigerant flow in plate heat exchangers rely on distributor technology, including but not limited to the application of guide pipes, guide rings, and embedded distributors. The main idea is to set different flow cross-sections at the inlet of each channel in the heat exchanger to control the mass flow rate of refrigerant entering different channels, thereby balancing the overall refrigerant distribution.

[0004] A flow distribution and regulation structure is currently installed at the refrigerant inlet. The main body of this structure is a circular tube with an internal spiral turbulence structure to increase fluid agitation, thereby preventing gas-liquid stratification and avoiding severe uneven flow distribution. Because the flow resistance losses of the refrigerant vary significantly across different channels in traditional heat exchanger structures, and the dryness of the refrigerant changes constantly during the splitting process, resulting in different gas-liquid two-phase flow ratios in each channel, the aforementioned flow regulation method cannot accurately control the flow distribution and can only rely on empirical predictions.

[0005] Another flow distribution and regulation structure that delivers refrigerant from the side reduces the uneven flow distribution caused by the sudden expansion effect at the manifold. However, this flow distribution structure does not consider the uneven distribution caused by the flow jet. In practical applications, the flow gradually decreases from the center of the distribution structure to the periphery, resulting in significant uneven distribution.

[0006] There is also a type of plate heat exchanger called the Coanda flow guide head, which, by setting layered flow guide plates inside, can effectively alleviate the jetting phenomenon caused when refrigerant is delivered from the side. However, the processing of the layered flow guide plates is relatively complex, and when the number of heat exchanger plates is large, the number of layered flow guide plates required is also larger, which is difficult to achieve through conventional processing. Utility Model Content

[0007] The primary objective of this invention is to provide a flow distribution component for a heat exchanger that can effectively improve the uniformity of fluid flow distribution in each channel and is easy to manufacture.

[0008] The second objective of this invention is to provide another flow distribution component for heat exchangers that can effectively improve the uniformity of fluid flow distribution in each channel and is easy to manufacture.

[0009] The third objective of this invention is to provide a heat exchanger employing the aforementioned flow distribution component.

[0010] The fourth objective of this invention is to provide a refrigeration device employing the aforementioned heat exchanger.

[0011] To achieve the aforementioned first objective, this utility model provides a flow distribution component for a heat exchanger, including a housing, a fluid channel disposed within the housing, the fluid channel having a fluid inlet and a fluid outlet disposed opposite to each other, the cross-sectional area of ​​the fluid outlet being larger than the cross-sectional area of ​​the fluid inlet; the flow distribution component further includes a baffle plate disposed within the fluid channel and near the fluid outlet, the baffle plate covering the fluid outlet; the baffle plate has a central region and an outer region, the central region being opposite to the fluid inlet of the fluid channel, and the outer region being located outside the central region; the baffle plate has a plurality of flow distribution holes penetrating the baffle plate in the thickness direction; the cross-sectional area of ​​the largest flow distribution hole located in the central region is smaller than the cross-sectional area of ​​the smallest flow distribution hole located in the outer region.

[0012] As can be seen from the above scheme, for plate heat exchangers and many other heat exchangers with parallel flow distribution structures, the uniformity of the gas and liquid two-phase fluid flow distribution in the internal channels directly affects the overall heat exchange performance. After the refrigerant flows into the flow distribution component of the utility model, it will experience significant disturbance due to the sudden expansion of the cross-section, resulting in a more uniform mixing of the gas and liquid two-phase refrigerant.

[0013] Furthermore, when the flow rate is large, the refrigerant forms a jet when entering the flow distribution structure from the fluid inlet. This results in a large flow rate in the central region of the flow distribution structure and a small flow rate in the peripheral region, leading to significant distribution unevenness. By installing a baffle at the outlet end of the fluid channel, a fluid mixing chamber is formed between the baffle and the fluid inlet to premix the fluid. At the same time, a certain number of flow distribution holes are opened on the baffle to distribute the flow rate passing through it. The cross-sectional area of ​​the largest flow distribution hole in the central region is smaller than that of the smallest flow distribution hole in the outer region. This arrangement makes the resistance of the refrigerant flowing through the central region significantly greater than the resistance of the flow distribution holes flowing through the surrounding outer regions. Therefore, the flow rate in the central region of the flow distribution component is reduced while the flow rate in the outer region is increased, and the distribution uniformity is significantly improved.

[0014] A preferred embodiment is that there are multiple flow distribution orifices in both the central region and the outer region; the cross-sectional area of ​​the flow distribution orifices gradually increases from the center of the central region to the edge of the outer region away from the center; or in the central region, at least two flow distribution orifices have equal cross-sectional areas, and in the outer region, the cross-sectional area of ​​the flow distribution orifices gradually increases from the position near the center to the position away from the center.

[0015] Therefore, the size of the flow distribution orifices in the central area can be the same, or they can gradually increase from the center outwards. The flow rate through each area can be adjusted by changing the number and size of the flow distribution orifices in the central and outer areas.

[0016] A preferred embodiment is that there are multiple flow distribution holes in the central area and two or more flow distribution holes in the outer area; the width of the flow distribution holes in the outer area gradually increases from the position closer to the central area to the position farther away from the central area.

[0017] Therefore, the outer region can be a long, narrow hole or a small hole. The flow rate through each region can be adjusted by changing the number, size, and shape of the flow distribution holes in the central and outer regions.

[0018] A preferred approach is to gradually increase the cross-sectional area of ​​the fluid channel from the fluid inlet to the fluid outlet.

[0019] It can be seen that when the gas-liquid two-phase refrigerant enters the fluid mixing chamber through the fluid inlet, the sudden expansion of the cross-section causes violent disturbance in the fluid, which ensures that the gas-liquid two-phase fluid is fully mixed and is less prone to flow stratification, thus facilitating the uniform distribution of the gas-liquid two-phase fluid.

[0020] A preferred embodiment is that the inner wall of the housing is provided with disturbance protrusions or disturbance grooves.

[0021] Therefore, by setting disturbance protrusions or disturbance grooves on the inner wall of the fluid channel, the mixing of gas and liquid two-phase fluids can be promoted, thereby further improving the uniformity of flow distribution.

[0022] To achieve the second objective mentioned above, this utility model provides another flow distribution component for a heat exchanger, including a housing, a fluid channel disposed within the housing, the fluid channel having a fluid inlet and a fluid outlet disposed opposite to each other, the cross-sectional area of ​​the fluid outlet being larger than the cross-sectional area of ​​the fluid inlet; the flow distribution component also includes a baffle plate disposed within the fluid channel and near the fluid outlet, the baffle plate covering the fluid outlet; the baffle plate has a central region and an outer region, the central region being opposite to the fluid inlet of the fluid channel, and the outer region being located outside the central region; a flow distribution hole penetrating the baffle plate in the thickness direction is provided on the baffle plate; the flow distribution hole includes a first distribution hole portion located in the central region and a second distribution hole portion located in the outer region, the cross-sectional area of ​​the first distribution hole portion being smaller than the cross-sectional area of ​​the second distribution hole portion, and the width of the second distribution hole portion gradually increasing from the central region to the outer region.

[0023] As can be seen from the above scheme, after the refrigerant flows into the flow distribution component of the utility model, a large disturbance occurs due to the sudden expansion of the cross-section, resulting in a more uniform mixing of the gas-liquid two-phase refrigerant. Furthermore, by setting a baffle plate at the outlet end of the fluid channel, a fluid mixing chamber is formed between the baffle plate and the fluid inlet within the fluid channel for premixing the fluid. Simultaneously, flow distribution holes are formed on the baffle plate to distribute the flow rate passing through it. The cross-sectional area of ​​the first distribution hole located in the central region is smaller than that of the second distribution hole located in the outer region, and the width of the second distribution hole gradually increases from the central region to the outer region. This arrangement makes the resistance of the refrigerant flowing through the central region significantly greater than the resistance of the flow distribution holes flowing through the surrounding outer regions. Therefore, the flow rate in the central region of the flow distribution component is reduced, while the flow rate in the outer region is increased, significantly improving the uniformity of distribution.

[0024] A preferred embodiment is that the width of the first dispensing hole remains constant in the direction from the center of the central region to the edge of the central region near the outer region; or the width of the first dispensing hole gradually increases in the direction from the center of the central region to the edge of the central region near the outer region.

[0025] Therefore, the width of the first distribution orifice in the central region remains unchanged, or it can gradually increase from the center outwards. The flow rate through each region can be adjusted by changing the shape and size of the flow distribution orifices in the central and outer regions.

[0026] A preferred embodiment is that the width of the flow distribution orifice gradually increases from the center of the central region to the edge of the outer region away from the center.

[0027] To achieve the third objective mentioned above, this utility model provides a heat exchanger including the aforementioned flow distribution component.

[0028] In a preferred embodiment, the heat exchanger further includes a first end plate, a second end plate, and a heat exchange fin assembly, wherein the heat exchange fin assembly comprises a plurality of heat exchange fins arranged in a stacked manner; the first end plate and the second end plate are respectively disposed at both ends in the stacking direction of the heat exchange fins; the first end plate has a first medium inlet, a first medium outlet, and a second medium outlet; the heat exchange fin assembly has a first medium channel and a second medium channel, and both the first medium inlet and the second medium outlet are connected to the first medium channel; the first sidewall of the heat exchange fin assembly has a second medium inlet, and both the second medium inlet and the second medium outlet are connected to the second medium channel; a flow distribution component is disposed at the second medium inlet, and the fluid outlet of the flow distribution component is connected to the second medium inlet.

[0029] A further option is to provide a slot at the second medium inlet, with the slot recessed inward from the first sidewall of the heat exchanger assembly, and the flow distribution component interlocking with the slot.

[0030] Therefore, the slotting is used to position the flow distribution component, ensure the stability of the connection between the flow distribution component and the heat exchanger assembly, and prevent the medium from leaking from the connection point.

[0031] A further design involves placing the first sidewall where the slot is located parallel to the stacking direction of the heat exchange plates, forming a second medium channel between two adjacent heat exchange plates. Each second medium channel is interconnected, and each second medium channel is provided with a channel inlet located on the first sidewall. Each channel inlet constitutes a second medium inlet, and the flow distribution component is connected to each channel inlet.

[0032] Therefore, it is evident that existing media inlets and outlets are typically located on the same end plate. This structure is prone to uneven refrigerant flow distribution and poor heat exchanger performance. The heat exchanger of this invention, by placing the flow distribution component on the side wall of the heat exchange plate assembly, allows the uniformly mixed fluid to flow into each plate channel as a parallel flow. Compared to designs where the refrigerant enters the heat exchanger through the end plate, this design, with the refrigerant entering through a side opening, ensures that the pressure drop in each channel is essentially the same, significantly improving the uniformity of flow distribution, increasing the effective heat exchange area, and enhancing the overall heat exchange capacity. Simultaneously, the heat exchange medium can enter multiple first-mode medium channels simultaneously through the flow distribution component, effectively reducing the problem of uneven distribution in different flow channels caused by the non-uniform gas-liquid two-phase state of the heat exchange medium.

[0033] To achieve the fourth objective mentioned above, this utility model provides a refrigeration device, including the heat exchanger described above. Attached Figure Description

[0034] Figure 1 This is a perspective view of the first embodiment of the heat exchanger of this utility model.

[0035] Figure 2 This is a right view of the first embodiment of the heat exchanger of this utility model.

[0036] Figure 3 This is a cross-sectional view of the first embodiment of the heat exchanger of this utility model.

[0037] Figure 4 This is a structural diagram of the heat exchange plate in the first embodiment of the heat exchanger of this utility model.

[0038] Figure 5 This is a perspective view of the flow distribution component in the first embodiment of the heat exchanger of this utility model.

[0039] Figure 6 This is a left view of the flow distribution component in the first embodiment of the heat exchanger of this utility model.

[0040] Figure 7 This is a schematic diagram of the second structure in the first embodiment of the heat exchanger of this utility model.

[0041] Figure 8 This is a schematic diagram of the third structure in the first embodiment of the heat exchanger of this utility model.

[0042] Figure 9 This is a schematic diagram of the fourth structure in the first embodiment of the heat exchanger of this utility model.

[0043] Figure 10 This is a schematic diagram of the fifth structure in the first embodiment of the heat exchanger of this utility model.

[0044] Figure 11 This is a perspective view of the flow distribution component in the second embodiment of the heat exchanger of this utility model.

[0045] Figure 12 This is a perspective view of the flow distribution component in the fourth embodiment of the heat exchanger of this utility model.

[0046] The present invention will be further described below with reference to the accompanying drawings and embodiments. Detailed Implementation

[0047] Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the present invention or its application or use. The present invention can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present invention thorough and complete, and to fully express the scope of the present invention to those skilled in the art. It should be noted that, unless otherwise specifically stated, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as merely exemplary and not as limiting.

[0048] The terms "first," "second," and similar words used in this invention do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Words such as "including" or "comprising" mean that the element preceding the word encompasses the element listed after it, and do not exclude the possibility of encompassing other elements as well. Terms such as "upper," "lower," "left," and "right" are only used to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0049] In this invention, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not exist between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may not be directly connected to the other devices but may have an intermediary device.

[0050] All terms used in this invention (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having the meaning consistent with their meaning in the context of the relevant art, and not as having an idealized or highly formalized meaning, unless expressly defined herein.

[0051] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0052] First embodiment of flow distribution component and heat exchanger:

[0053] See Figures 1 to 4 The heat exchanger in this embodiment includes a first end plate 1, a second end plate 2, a heat exchange fin assembly 3, and a flow distribution component 4. The heat exchanger is rectangular in shape.

[0054] The heat exchanger assembly 3 includes multiple stacked heat exchanger plates 30, with a first end plate 1 and a second end plate 2 respectively disposed at both ends of the stacking direction of the heat exchanger plates 30. The first end plate 1, the heat exchanger plates 30, and the second end plate 2 are formed into a whole by high-temperature welding after being stacked with brazing solder.

[0055] The first end plate 1 has a first medium inlet 11, a first medium outlet 12, and a second medium outlet 13 respectively located at three corner positions of the first end plate 1. The heat exchanger assembly 3 has a first medium channel (not shown) and a second medium channel 31. Both the first medium inlet 11 and the second medium outlet 13 are connected to the first medium channel. The first sidewall 32 of the heat exchanger assembly 3 has a second medium inlet 33, which is parallel to the stacking direction of the heat exchanger 30. Both the second medium inlet 33 and the second medium outlet 13 are connected to the second medium channel 31. In this embodiment, the first medium is water, and the second medium is refrigerant. The first medium flows in the first medium channel, and the second medium flows in the second medium channel 31. The first medium channel and the second medium channel 31 are not connected.

[0056] A slot 34 is provided at the second medium inlet 33 of the first sidewall 32 of the heat exchanger assembly 3. The slot 34 is recessed inward from the first sidewall 32 of the heat exchanger assembly 3 and extends through the heat exchanger assembly 3 along the stacking direction of the heat exchanger 30. The flow distribution component 4 is inserted into the slot 34, and the fluid outlet of the flow distribution component 4 is connected to the second medium inlet 33. After insertion, the flow distribution component 4 is fixedly connected to the heat exchanger assembly 3 by welding. The depth of the slot 34 is greater than or equal to 2 mm to ensure that the flow distribution component 4 can make tight contact with it, so as to ensure that the refrigerant can smoothly enter the second medium channel 31 without leakage. The first medium inlet 11 and the second medium outlet 13 are both located at the first end of the length direction of the first end plate 1, and the first medium outlet 12 is located at the second end of the length direction of the first end plate 1. In the length direction of the heat exchanger assembly 3, the slot 34 is located near the second end of the first end plate 1. Preferably, the distance d1 between the centerline of the first medium outlet 12 and the second end face of the first end plate 1 is equal to the distance d2 between the centerline of the slot 34 and the second end face of the first end plate 1. In other embodiments, the specific position of the flow distribution component 4 on the first sidewall 32 can also be changed as needed, such as... Figure 9 As shown, the centerline of the first medium outlet 12 is parallel to the centerline of the first end plate 1.

[0057] The distance between the second end faces is less than the distance between the center line of the slot 34 and the second end face of the first end plate 1.

[0058] A water channel inlet connector 51 is provided at the first medium inlet 11, a water channel outlet connector 52 is provided at the first medium outlet 12, a refrigerant channel outlet connector 53 is provided at the second medium outlet 13, and a refrigerant channel inlet connector 54 is provided at the fluid inlet 412 of the flow distribution component 4.

[0059] A second medium channel 31 is formed between every two adjacent heat exchange plates 30. These second medium channels 31 are interconnected, and each second medium channel 31 is provided with a channel inlet 331 located on the first sidewall 32. These channel inlets 331 constitute a second medium inlet 33. The flow distribution component 4 is connected to each channel inlet 331. The second heat exchange medium enters each second medium channel 31 simultaneously through the flow distribution component 4, and the second heat exchange medium is evenly distributed into each layer of second medium channels 31 connected to the flow distribution component 4.

[0060] The flow distribution component 4 includes a housing 41 and a baffle 42. A fluid channel 411 is provided inside the housing 41. The fluid channel 411 has a fluid inlet 412 and a fluid outlet 413 arranged opposite to each other. The cross-sectional area of ​​the fluid outlet 413 is larger than that of the fluid inlet 412. From the fluid inlet 412 to the fluid outlet 413, the cross-sectional area of ​​the fluid channel 411 gradually increases. When the gas-liquid two-phase refrigerant enters the fluid mixing chamber through the fluid inlet 412, the sudden expansion of the cross-section causes severe turbulence in the fluid, resulting in thorough mixing of the gas and liquid phases and reducing the likelihood of flow stratification. This promotes uniform distribution of the gas and liquid phases.

[0061] In this embodiment, the fluid inlet 412 is circular, the fluid outlet 413 is rectangular, and the outer casing 41 extends in a curved shape. The fluid inlet 412 is designed to be circular to facilitate welding and fixing with the circular copper pipe of the air conditioner. In other embodiments, the fluid inlet 412 may also be rectangular, elliptical, polygonal, or other irregular shapes. Figure 7 , 8 As shown in Figure 10, the shape and size of the housing of the flow distribution component 4 can be changed as needed, such as... Figure 7 and 8 As shown, by changing the shape of the transition surface of the outer shell 41, the size, shape, and dimensions of the fluid channel can be altered. Figure 7 In the flow distribution component shown, the distance between the fluid inlet 412 and the fluid outlet 413 of the flow distribution component 4 is greater than the distance between the fluid inlet 412 and the fluid outlet 413 in this embodiment. This can prolong the fluid redistribution time, allowing the fluid to mix more thoroughly. Figure 8 The distance between the fluid inlet 412 and the fluid outlet 413 of the flow distribution component 4 shown is smaller than the distance between the fluid inlet 412 and the fluid outlet 413 of the flow distribution component 4 in this embodiment, which can shorten the fluid redistribution time and speed up the refrigerant entering the heat exchanger. Figure 10 The shape of the outer shell of the flow distribution component 4 shown is not gradual; the end near the fluid outlet is cylindrical with an elliptical cross-section.

[0062] See Figure 3 , Figure 5 and Figure 6 A baffle plate 42 is disposed within the fluid channel 411 and near the fluid outlet 413, covering the fluid outlet 413. The baffle plate 42 has a central region 421 and an outer region 422. The central region 421 is opposite to the fluid inlet 412 of the fluid channel 411, and the outer region 422 is located outside the central region 421. The baffle plate 42 has multiple flow distribution holes 420 penetrating through it in the thickness direction. Both the central region 421 and the outer region 422 have multiple flow distribution holes 420. The cross-sectional area of ​​the largest flow distribution hole 420 in the central region 421 is smaller than the cross-sectional area of ​​the smallest flow distribution hole 420 in the outer region 422. Figure 6 As shown, when the baffle 42 is elongated, the central region 421 is a certain area in the middle of the length direction of the baffle 42, and the outer region 422 includes a first outer region segment 4221 and a second outer region segment 4222, which are respectively arranged on both sides of the outer region 422.

[0063] In this embodiment, within the central region 421, the cross-sectional areas of all flow distribution holes 420 are equal. Within the outer region 422, the cross-sectional areas of the flow distribution holes 420 gradually increase from a position close to the central region 421 to a position away from the central region 421. In other embodiments, at least two flow distribution holes 420 within the central region 421 may have equal cross-sectional areas; or the cross-sectional areas of the flow distribution holes 420 may gradually increase from the center of the central region 421 to an edge position away from the center position on the outer region 422.

[0064] As can be seen from the above, for plate heat exchangers and many other heat exchangers with parallel flow distribution structures, the uniformity of the gas and liquid two-phase fluid flow distribution in the internal channels directly affects the overall heat exchange performance. After the refrigerant flows into the flow distribution component of the utility model, it will experience significant disturbance due to the sudden expansion of the cross-section, resulting in a more uniform mixing of the gas and liquid two-phase refrigerant. Furthermore, when the flow rate is large, the refrigerant forms a jet when entering the flow distribution structure from the inlet, resulting in a large flow rate in the central region and a small flow rate in the peripheral region, leading to significant distribution unevenness. By installing a baffle at the outlet end of the fluid channel, a fluid mixing chamber is formed between the baffle and the inlet to premix the fluid. At the same time, a certain number of flow distribution holes are opened on the baffle to distribute the flow rate passing through it. The cross-sectional area of ​​the largest flow distribution hole in the central region is smaller than that of the smallest flow distribution hole in the outer region. This arrangement makes the resistance of the refrigerant flowing through the central region significantly greater than the resistance of the flow distribution holes flowing through the surrounding outer regions. Therefore, the flow rate in the central region of the flow distribution component is reduced while the flow rate in the outer region is increased, and the distribution uniformity is significantly improved.

[0065] Furthermore, by introducing refrigerant from the side, gas-liquid separation caused by resistance loss during refrigerant distribution is avoided, ensuring that the pressure drop of the refrigerant entering each channel from the inlet is essentially the same, thus improving the uniformity of flow distribution in each channel. Moreover, the side-feeding method reduces the footprint of the heat exchange fins, increasing the effective heat exchange area of ​​the fins and effectively enhancing the heat exchanger's performance.

[0066] Second embodiment of flow distribution component and heat exchanger:

[0067] As a description of the second embodiment of the flow distribution component and heat exchanger of this utility model, the following description only focuses on the differences from the first embodiment of the flow distribution component and heat exchanger described above.

[0068] See Figure 11 In this embodiment, the flow distribution hole 21 on the baffle 20 is one. This flow distribution hole 21 includes a first distribution hole portion 211 located in the central region 22 and a second distribution hole portion 212 located in the outer region 23. The cross-sectional area of ​​the first distribution hole portion 211 is smaller than that of the second distribution hole portion 212. The width of the second distribution hole portion 212 gradually increases from the central region 22 to the outer region 23. Furthermore, the width of the flow distribution hole 21 gradually increases from the center of the central region 22 to the edge of the outer region 23 away from the center.

[0069] Third embodiment of flow distribution component and heat exchanger:

[0070] As a description of the third embodiment of the flow distribution component and heat exchanger of this utility model, the following description only focuses on the differences from the second embodiment of the flow distribution component and heat exchanger described above.

[0071] In the second embodiment, the width of the first dispensing hole 211 gradually increases in the direction from the center of the central region 22 to the edge of the central region 22 near the outer region 23.

[0072] In this embodiment, the width of the first dispensing hole remains unchanged in the direction from the center of the central region to the edge of the central region near the outer region.

[0073] Fourth embodiment of flow distribution component and heat exchanger:

[0074] As a description of the fourth embodiment of the flow distribution component and heat exchanger of this utility model, the following description only focuses on the differences from the second embodiment of the flow distribution component and heat exchanger described above.

[0075] See Figure 12 In this embodiment, there are multiple flow distribution holes 4420 in the central region 410 and two flow distribution holes 4420 in the outer region 430. These two flow distribution holes 4420 are respectively disposed on both sides of the central region 410, and the width of the two flow distribution holes 4420 in the outer region 430 gradually increases from the position close to the central region 410 to the position far away from the central region 410. In other embodiments, there may be more than two flow distribution holes 4420 in the outer region 430. For example, when the cross-section of the fluid channel is triangular, there may be three flow distribution holes 4420 in the outer region 430, and these three flow distribution holes 4420 are arranged along the outer periphery of the central region 410 with the center position as the center.

[0076] Fifth embodiment of flow distribution component and heat exchanger:

[0077] As a description of the fifth embodiment of the flow distribution component and heat exchanger of this utility model, the following description only focuses on the differences from the first embodiment of the flow distribution component and heat exchanger described above.

[0078] The inner wall of the outer casing is provided with disturbance protrusions or disturbance grooves. By providing disturbance protrusions or disturbance grooves on the inner wall of the fluid channel, the mixing of the gas-liquid two-phase fluid can be promoted, thereby further improving the uniformity of flow distribution.

[0079] Refrigeration equipment example:

[0080] The refrigeration equipment in this embodiment includes the heat exchangers from the above-described heat exchanger embodiments.

[0081] Furthermore, the shape, number, size, and arrangement of the flow distribution orifices can all be changed as needed. The number and size of the heat exchange fins in the heat exchanger can also be changed as needed. The size, shape, and position of the slots can all be changed as needed. The size, shape, and position of the baffle plate within the casing can also be changed as needed. These modifications can also achieve the purpose of this utility model.

[0082] Finally, it should be emphasized that the above are only preferred embodiments of the present utility model and are not intended to limit the present utility model. For those skilled in the art, the present utility model can have various changes and modifications. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A flow distribution component for a heat exchanger, comprising a housing, wherein a fluid channel is provided within the housing, the fluid channel having a fluid inlet and a fluid outlet disposed opposite to each other, the cross-sectional area of ​​the fluid outlet being larger than the cross-sectional area of ​​the fluid inlet; Its features are: The flow distribution component further includes a baffle plate, which is disposed within the fluid channel and near the fluid outlet, and covers the fluid outlet; The baffle has a central region and an outer region, the central region being opposite to the fluid inlet of the fluid channel, and the outer region being located outside the central region; The baffle plate is provided with a plurality of flow distribution holes that penetrate the baffle plate in the thickness direction; The cross-sectional area of ​​the largest flow distribution orifice located in the central region is smaller than the cross-sectional area of ​​the smallest flow distribution orifice located in the outer region.

2. The flow distribution component according to claim 1, characterized in that: The number of flow distribution holes in the central area and the number of flow distribution holes in the outer area are both multiple; The cross-sectional area of ​​the flow distribution orifice gradually increases from the center of the central region to the edge of the outer region away from the center; or Within the central region, at least two of the flow distribution orifices have equal cross-sectional areas, and within the outer region, the cross-sectional area of ​​the flow distribution orifices gradually increases from a position close to the central region to a position far from the central region.

3. The flow distribution component according to claim 1, characterized in that: The number of flow distribution holes in the central area is multiple, and the number of flow distribution holes in the outer area is two or more; The width of the flow distribution hole in the outer region gradually increases from the position near the central region to the position away from the central region.

4. The flow distribution component according to any one of claims 1 to 3, characterized in that: The cross-sectional area of ​​the fluid channel gradually increases from the fluid inlet to the fluid outlet.

5. The flow distribution component according to any one of claims 1 to 3, characterized in that: The inner wall of the outer casing is provided with disturbance protrusions or disturbance grooves.

6. A flow distribution component for a heat exchanger, comprising a housing, wherein a fluid channel is provided within the housing, the fluid channel having a fluid inlet and a fluid outlet disposed opposite to each other, the cross-sectional area of ​​the fluid outlet being larger than the cross-sectional area of ​​the fluid inlet; Its features are: The flow distribution component further includes a baffle plate, which is disposed within the fluid channel and near the fluid outlet, and covers the fluid outlet; The baffle has a central region and an outer region, the central region being opposite to the fluid inlet of the fluid channel, and the outer region being located outside the central region; The baffle plate is provided with a flow distribution hole that penetrates the baffle plate in the thickness direction; The flow distribution orifice includes a first distribution orifice located in the central region and a second distribution orifice located in the outer region. The cross-sectional area of ​​the first distribution orifice is smaller than that of the second distribution orifice. The width of the second distribution orifice gradually increases from the central region to the outer region.

7. The flow distribution component according to claim 6, characterized in that: The width of the first dispensing hole remains unchanged in the direction from the center of the central region to the edge of the central region near the outer region; or The width of the first dispensing hole gradually increases from the center of the central region to the edge of the central region near the outer region.

8. The flow distribution component according to claim 6, characterized in that: The width of the flow distribution orifice gradually increases from the center of the central region to the edge of the outer region away from the center.

9. A heat exchanger, characterized in that, Includes the flow distribution component as described in any one of claims 1 to 8.

10. The heat exchanger according to claim 9, characterized in that: The heat exchanger also includes a first end plate and a heat exchange plate assembly, the heat exchange plate assembly including a plurality of heat exchange plates arranged in a stacked manner; The first end plate is disposed at one end in the stacking direction of the heat exchange fins; The first end plate is provided with a first medium inlet, a first medium outlet and a second medium outlet, and the heat exchange plate assembly is provided with a first medium channel and a second medium channel, and the first medium inlet and the second medium outlet are both connected to the first medium channel; The first sidewall of the heat exchanger assembly is provided with a second medium inlet, and both the second medium inlet and the second medium outlet are connected to the second medium channel. The flow distribution component is located at the second medium inlet, and the fluid outlet of the flow distribution component is connected to the second medium inlet.

11. The heat exchanger according to claim 10, characterized in that: A slot is provided at the second medium inlet, the slot being recessed inward from the first sidewall of the heat exchanger assembly, and the flow distribution component is inserted into the slot.

12. The heat exchanger according to claim 11, characterized in that: The first sidewall where the slot is located is parallel to the stacking direction of the heat exchange plates. A second medium channel is formed between two adjacent heat exchange plates. Each second medium channel is interconnected. Each second medium channel is provided with a channel inlet located on the first sidewall. Each channel inlet constitutes a second medium inlet. The flow distribution component is connected to each channel inlet.

13. A refrigeration device, characterized in that, Includes the heat exchanger as described in any one of claims 9 to 12.

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