Refrigerant flow equalizing distributor, heat exchanger assembly and refrigeration equipment

Abstract

The utility model provides a refrigerant flow equalizing distributor, a heat exchanger assembly and refrigeration equipment. The refrigerant flow equalizing distributor comprises a body and a partition plate. A liquid inlet pipe assembling hole is formed in the liquid inlet end of the body, the inner wall of the liquid inlet end of the body obliquely extends towards the liquid outlet end of the body, a bus of the inner wall is an arc line or an oblique straight line, and a plurality of branch pipe holes are formed in the liquid outlet end of the body. The partition plate divides the containing cavity into a first cavity and a second cavity, a plurality of partition plate holes annularly distributed around the center line of the body are formed in the partition plate, and the partition plate holes correspond to the branch pipe holes in a one-to-one mode and are located on the periphery of the liquid inlet pipe assembly hole when projected in the axial direction of the body. The connecting line between the projection position A of the outer edge of the downstream end of the partition plate hole on the inner wall of the liquid inlet end in the axial direction of the body and the center O of the downstream end of the liquid inlet pipe assembly hole forms an included angle alpha relative to the radial direction of the partition plate, and the included angle alpha is larger than or equal to 8 degrees and smaller than or equal to 17 degrees. The axial distance H1 from the surface of the partition plate where the upstream end of the partition plate hole is located to the projection position A is larger than or equal to 1 mm and smaller than or equal to 5 mm.

Description

Technical Field

[0001] The utility model relates to the technical field of refrigerant distribution, and particularly relates to a refrigerant flow equalizing distributor, a heat exchanger assembly and a refrigeration device. Background Art

[0002] The multi-channel heat exchanger has the advantages of small pressure drop and large heat transfer coefficient, and is widely used in refrigeration systems to improve the refrigeration and heating performance of the refrigeration system. To ensure good heat exchange performance of the multi-channel heat exchanger, the two-phase refrigerant should be evenly distributed to each flow path of the heat exchanger. Currently, distributors are mainly used in refrigeration systems for refrigerant distribution. The most common problem of distributors applied in refrigeration systems is uneven refrigerant flow distribution. The liquid refrigerant flow in some flow paths is small and evaporates prematurely. The heat transfer coefficient in the dry-out area is much smaller than that in the two-phase area, resulting in a decrease in the effective heat transfer area, which seriously affects the heat exchange performance of the heat exchanger. Experiments have shown that the decrease in heat exchange capacity caused by uneven refrigerant distribution can be as high as 25%.

[0003] Currently, the commonly used distributors in refrigeration systems include Venturi distributors, pressure drop distributors, and orifice distributors. Due to the limitation of the flow channel line type of the Venturi distributor, not only is the tool processing difficult, the cost high, but also the consistency after processing is difficult to guarantee. The pressure drop distributor is a simplified structure of the Venturi distributor. Although it has been improved to a certain extent in terms of processing difficulty and cost, it has problems such as large pressure loss, high noise, and serious influence of the installation angle on the flow splitting performance. The influence of the installation angle on the flow splitting performance is most serious in the orifice distributor.

[0004] To solve the problem of uneven liquid separation of the existing distributor, those skilled in the art have optimized and improved the structure of the existing distributor. The more complex Venturi distributor and pressure drop distributor mainly focus on the improvement of the flow channel as the main direction; while the simple structure and low-cost orifice distributor (as shown in Figure 1 ) mainly improves the installation structure of each branch pipe on the liquid separation side. However, for the orifice liquid separator, the two-phase refrigerant expands and diffuses rapidly after entering the inner cavity of the distributor. During the diffusion process, the two-phase refrigerant is extremely prone to two-phase separation segregation due to gravity, resulting in a large amount of liquid-phase refrigerant precipitating at the bottom of the distributor and being unable to be distributed into the branch pipes, thus leading to poor liquid separation performance; at the same time, this is also the main reason why the orifice distributor is most seriously affected by the installation angle.

[0005] To further improve the liquid separation performance, some people have proposed to provide a sieve plate or a filter screen in the distributor cavity. The number of liquid passing holes on the sieve plate or the filter screen is large but the aperture is small. This type of structure hopes to form a certain pressure of the refrigerant on the liquid inlet pipe side through the sieve plate or the filter screen so that the refrigerant flow rate passing through each liquid passing hole is uniform. However, on the sieve plate or the filter screen, some of the liquid passing holes are directly opposite to the liquid inlet pipe, and the refrigerant input by the liquid inlet pipe will preferentially enter the liquid separation side through the liquid passing holes opposite to it, and it is difficult to achieve uniform distribution of the refrigerant flow rate of each liquid passing hole. In addition, the liquid passing holes with very small apertures will inevitably hinder the passage of the refrigerant and cause excessive refrigerant pressure loss; for an evaporator, excessive refrigerant pressure loss means a decrease in the evaporation temperature, a decrease in the refrigerating capacity per unit mass of the refrigerant, and a decrease in the refrigerating capacity per unit volume of the compressor, which is unfavorable to the refrigeration cycle. Utility Model Content

[0006] In order to overcome at least one deficiency of the prior art, the present utility model provides a refrigerant uniform flow distributor, a heat exchanger assembly and a refrigeration device.

[0007] To achieve the above object, the present utility model provides a refrigerant uniform flow distributor, which includes a body and a partition plate. The body includes a liquid inlet end, a liquid outlet end, and a receiving cavity that respectively communicates with the liquid inlet end and the liquid outlet end. A liquid inlet pipe assembly hole is formed on the liquid inlet end of the body. The inner wall of the liquid inlet end extends obliquely towards the liquid outlet end of the body and the generatrix of its inner wall is an arc or an inclined straight line. A plurality of branch pipe holes for liquid separation are formed on the liquid outlet end of the body. The partition plate is arranged in the receiving cavity of the body to divide the receiving cavity into a first cavity and a second cavity. A plurality of partition plate holes that are annularly distributed around the center line of the body and communicate the first cavity and the second cavity are formed on the partition plate. The plurality of partition plate holes are configured to correspond to the plurality of branch pipe holes one by one, and when projected along the axial direction of the body, the plurality of partition plate holes are located on the outer periphery of the liquid inlet pipe assembly hole. Among them, the included angle α between the connecting line between the projection position A of the outer edge of the downstream end of the partition plate hole on the inner wall of the liquid inlet end along the axial direction of the body and the center O of the downstream end of the liquid inlet pipe assembly hole with respect to the radial direction of the partition plate is 8° ≤ α ≤ 17°. The axial distance H1 from the surface of the partition plate where the upstream end of the partition plate hole is located to the projection position A satisfies: 1 mm ≤ H1 ≤ 5 mm. The outer edge of the downstream end of the partition plate hole refers to the edge of the downstream end of the partition plate hole that is farthest from the center line of the body.

[0008] According to an embodiment of the present utility model, the plurality of partition plate holes are annularly distributed at equal intervals on the partition plate and the number thereof is the same as the number of branch pipe holes. Each partition plate hole is substantially coaxial with the branch pipe hole opposite to it. The ratio of the aperture D1 of the downstream end of the partition plate hole to the outer diameter D2 of the branch pipe inserted into the branch pipe hole is 0.8 to 1.2.

[0009] According to an embodiment of the present utility model, the refrigerant flow equalizing distributor further includes a plurality of branch pipes respectively welded and connected in a plurality of branch pipe holes. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section. The difference △d between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1 mm ≤ △d ≤ 3.5 mm; a reflection section is formed on the first pipe section and extends bent toward one side relative to the center line of the branch pipe hole. An included angle θ is formed between the axis at the upstream end of the reflection section and the axis at the downstream end of the reflection section, and 90° ≤ θ ≤ 175°. Based on the reflection section, the axis of the second pipe section intersects the center line of the branch pipe hole.

[0010] According to an embodiment of the present utility model, the refrigerant flow equalizing distributor further includes a plurality of branch pipes respectively welded and connected in a plurality of branch pipe holes. Each branch pipe includes a connecting straight section, a jet section located downstream of the connecting straight section and having a reduced inner diameter relative to the inner diameter of the connecting straight section body, and a branch section located downstream of the jet section. An equal-diameter section with an inner diameter substantially close to the inner diameter of the connecting straight section body is formed on the branch section. The difference △d' between the inner diameter d11' of the connecting straight section body and the minimum inner diameter d12' at the jet section is: 0.1 mm ≤ △d' ≤ 3.5 mm.

[0011] According to an embodiment of the present utility model, the partition hole is a through hole with substantially the same aperture or its aperture gradually decreases along the flow direction of the refrigerant. The generatrix of the inner wall of the partition hole is linear or arc-shaped.

[0012] According to an embodiment of the present utility model, the partition is a plate body structure with both sides being substantially planar;

[0013] Alternatively, the area of the partition opposite to the liquid inlet pipe assembly hole is recessed toward the direction of the liquid outlet end of the body to form a reflection mixing cavity with an opening facing the liquid inlet pipe assembly hole.

[0014] According to an embodiment of the present utility model, the refrigerant flow equalizing distributor further includes a liquid inlet pipe welded and connected to the liquid inlet pipe assembly hole. The axial length L from the end face of the liquid outlet end of the liquid inlet pipe to the partition surface at the upstream end of the partition hole satisfies 3.5 mm ≤ L ≤ 11.5 mm.

[0015] According to an embodiment of the present utility model, a connecting section for welding and connecting the liquid inlet pipe assembly hole is formed on the liquid inlet pipe, and the connecting section is a straight section;

[0016] Alternatively, the connecting section is a gradually expanding structure with an arc-shaped curve as the generatrix of the outer wall. The connecting section extends into the first cavity through the liquid inlet pipe assembly hole, and the outer wall of the connecting section is welded and attached to the inner wall of the liquid inlet end of the body.

[0017] According to an embodiment of the present utility model, the branch pipe hole includes a diversion hole section and a connection hole section that are sequentially distributed along the refrigerant flow direction. The aperture of the diversion hole section gradually decreases along the refrigerant flow direction, and the inner wall generatrix thereof is linear or arc-shaped.

[0018] According to an embodiment of the present utility model, there is an included angle β between the tangent line at the inner wall generatrix of the diversion hole section and the center line of the branch pipe hole, and 10° ≤ β ≤ 65°.

[0019] According to an embodiment of the present utility model, the aperture of the downstream end of the diversion hole section is smaller than that of the connection hole section. A limiting portion that protrudes towards the center of the branch pipe hole is formed at the connection between the diversion hole section and the connection hole section. The limiting portion is configured to abut against the end face of the branch pipe inserted into the branch pipe hole, and the aperture of the limiting portion is substantially close to the inner diameter of the inserted branch pipe.

[0020] According to an embodiment of the present utility model, the refrigerant uniform flow distributor includes a baffle plate that is adhesively welded to the inner end wall of the liquid outlet end of the main body. A plurality of baffle plate holes that serve as the diversion hole section of the branch pipe hole are opened on the baffle plate;

[0021] Alternatively, the diversion hole section and the connection hole section are integrally formed on the end wall of the liquid outlet end of the main body.

[0022] On the other hand, the present utility model further provides a heat exchanger assembly, which is characterized in that it includes the above-mentioned refrigerant uniform flow distributor.

[0023] On the other hand, the present utility model further provides a refrigeration device, which includes the above-mentioned heat exchanger assembly.

[0024] In summary, the refrigerant uniform flow distributor provided by the present utility model divides the accommodation cavity in the main body into a first cavity and a second cavity through a partition plate to reduce the volume of each chamber in the main body. The first cavity provides a suitable expansion space for the gas-liquid two-phase refrigerant input by the liquid inlet pipe so that the two-phase refrigerant is fully mixed into a high-speed dispersed flow pattern, effectively solving the problem that the gas-liquid two-phase segregation of the mixed refrigerant occurs again due to the too large inner cavity of the existing distributor. At the same time, by setting the inner wall of the liquid inlet end to extend obliquely towards the liquid outlet end of the main body, a secondary reflection surface is formed on the inner wall of the liquid inlet end, and the dispersed refrigerant after reflection by the partition plate is secondarily reflected into a plurality of partition plate holes, realizing the uniform diversion and distribution of the refrigerant while further improving the mixing degree of the two-phase refrigerant through secondary reflection. The setting of the included angle α related to the projection position A realizes the control of the secondary reflection stroke from the partition plate to the inner wall of the liquid inlet end, ensuring that the refrigerant after reflection by the partition plate can be incident on the inner wall of the liquid inlet end again for secondary reflection. The axial distance H1 related to the projection position A determines the spatial position of the partition plate hole so that it is located on the exit path of the secondary reflection; at the same time, this setting also effectively avoids the obstruction of the inner wall of the main body to the refrigerant flow, so that the refrigerant can be evenly distributed into a plurality of partition plate holes.

[0025] In addition, by arranging a plurality of partition holes on the outer periphery of the projection area of the liquid inlet pipe assembly hole on the partition plate, the projection area of the liquid inlet pipe on the partition plate can block the input refrigerant and reflect it back into the first cavity to further promote the mixing of the two-phase refrigerant. At the same time, the staggered distribution of the partition holes and the liquid inlet holes also effectively avoids the refrigerant flowing directly into the second mixing cavity without having time to mix, thereby greatly improving the mixing uniformity of the two-phase refrigerant.

[0026] To make the above and other objects, features, and advantages of the present utility model more obvious and understandable, the following specifically enumerates preferred embodiments and, in conjunction with the accompanying drawings, provides a detailed description as follows. Description of the Drawings

[0027] Figure 1 Shown is a schematic structural diagram of an existing socket-type distributor.

[0028] Figure 2 Shown is a schematic structural diagram of a refrigerant uniform flow distributor provided in the first embodiment of the present utility model.

[0029] Figure 3 Shown is Figure 2 a schematic cross-sectional view of

[0030] Figure 4 Shown is Figure 3 a schematic structural diagram after removing the liquid inlet pipe and the branch pipes.

[0031] Figure 5 Shown is Figure 4 an enlarged schematic view of part B in

[0032] Figure 6 Shown is Figure 2 a schematic structural diagram of the partition plate in

[0033] Figure 7A , Figure 7B , Figure 7C , Figure 7D , Figure 7E and Figure 7F Shown is a schematic structural diagram of the partition plate in another embodiment of the present utility model.

[0034] Figure 8 Shown is Figure 2 a schematic structural diagram of the end cap in

[0035] Figure 9 Shown is a schematic structural diagram of the body in a refrigerant uniform flow distributor provided in another embodiment of the present utility model.

[0036] Figure 10 Shown is Figure 9 a schematic structural diagram of the baffle in

[0037] Figure 10A The structural schematic diagram of the baffle provided by another embodiment of the present utility model is shown as follows.

[0038] Figure 11 and Figure 12 The structural schematic diagram of the refrigerant flow equalizing distributor provided by another embodiment of the present utility model is shown as follows.

[0039] Figure 13 The structural schematic diagram of the refrigerant flow equalizing distributor provided by the second embodiment of the present utility model is shown as follows.

[0040] Figure 14 Shown as Figure 13 the structural schematic diagram of the middle partition board.

[0041] Figure 15A 、 Figure 15B 、 Figure 15C Figure 15D The structural schematic diagram of the middle partition board in another embodiment of the present utility model is shown as follows.

[0042] Figure 16 The structural schematic diagram of the refrigerant flow equalizing distributor provided by the third embodiment of the present utility model is shown as follows.

[0043] Figure 16A Shown as Figure 16 the structural schematic diagram of the liquid inlet pipe removed.

[0044] Figure 17 The structural schematic diagram of the branch pipe in the refrigerant flow equalizing distributor provided by the fourth embodiment of the present utility model is shown as follows.

[0045] Figures 18A to 18C The structural schematic diagram of the branch pipe in the refrigerant flow equalizing distributor provided by another embodiment of the present utility model is shown as follows.

[0046] Figure 19 The structural schematic diagram of the refrigerant flow equalizing distributor provided by the fifth embodiment of the present utility model is shown as follows.

[0047] Figures 20A to 20E The structural schematic diagram of the branch pipe in the refrigerant flow equalizing distributor provided by another embodiment of the present utility model is shown as follows. Detailed implementation manners

[0048] Embodiment 1

[0049] As Figure 1As shown in the figure, in a traditional jack - type distributor, when the refrigerant enters the inner cavity of the distributor for diffusion and mixing, the flow rate of the refrigerant slows down. Under the action of gravity, the liquid - phase refrigerant is extremely easy to separate from the gas - phase refrigerant and deposit at the bottom of the distributor, thus seriously affecting the liquid - separation uniformity. Moreover, for distributors with added filters or sieve plates, there are problems such as the refrigerant passing directly through the liquid - outlet holes to the liquid - separation side without sufficient mixing and excessive pressure loss when the refrigerant passes through the liquid - passing holes. In view of this, this embodiment provides a refrigerant flow - equalizing distributor with excellent flow - splitting uniformity and small pressure loss.

[0050] As Figures 2 to 6 shown, the refrigerant flow - equalizing distributor provided in this embodiment includes a body 1 and a partition 2. The body 1 includes a liquid - inlet end 101, a liquid - outlet end 102, and a receiving cavity 103 that communicates with the liquid - inlet end 101 and the liquid - outlet end 102 respectively. A liquid - inlet pipe assembly hole 104 is formed on the liquid - inlet end 101 of the body. The inner wall of the liquid - inlet end 101 extends obliquely towards the liquid - outlet end 102 of the body, and its inner - wall generatrix is an arc or an inclined straight line. A plurality of branch - pipe holes 105 for liquid - separation are formed on the liquid - outlet end 102 of the body. The partition 2 is disposed in the receiving cavity 103 of the body 1 to divide the receiving cavity 103 into a first cavity 1031 and a second cavity 1032. A plurality of partition holes 21 that are distributed in a ring around the center line of the body 1 and communicate the first cavity 1031 and the second cavity 1032 are formed on the partition 2. The plurality of partition holes 21 are configured to correspond to the plurality of branch - pipe holes 105 one by one, and when projected along the axial direction of the body 1, the plurality of partition holes 21 are located on the outer periphery of the liquid - inlet pipe assembly hole 104.

[0051] Among them, the projection of the outer edge of the downstream end of the partition hole 21 on the inner wall of the liquid - inlet end 101 along the axial direction of the body 1 is the projection position A. The connecting line between the projection position A and the center O of the downstream end of the liquid - inlet pipe assembly hole 104 forms an angle α with the radial direction of the partition 2, and 8° ≤ α ≤ 17°. The axial distance H1 from the surface of the partition 2 where the upstream end of the partition hole 21 is located to the projection position A satisfies: 1mm ≤ H1 ≤ 5mm. The outer edge of the downstream end of the partition hole 21 refers to the edge of the downstream end of the partition hole 21 that is farthest from the center line of the body 1.

[0052] The downstream or upstream is divided based on the flow direction of the refrigerant. Generally, the refrigerant flows from the upstream to the downstream, and the area located downstream receives the refrigerant from the upstream. In a refrigeration device, the distributor is generally installed vertically or obliquely. The liquid - inlet end of the distributor is located below the liquid - outlet end along the direction of gravity. The inertial force of the refrigerant in the distributor overcomes gravity and flows in the direction opposite to gravity; at this time, the upstream and downstream are still divided according to the flow direction of the refrigerant. According to the division of the upstream and downstream, the downstream end of the partition hole 21 refers to the end of the partition hole 21 facing the second cavity 1032, and the center O of the downstream end of the liquid - inlet pipe assembly hole 104 refers to the cross - section center at the intersection of the straight - section inner wall of the liquid - inlet pipe assembly hole 104 and the curved inner wall of the liquid - inlet end 101 of the body.

[0053] In the existing dispenser, when the refrigerant enters the inner cavity of the dispenser with an enlarged flow path through the liquid inlet pipe, due to inertia, the refrigerant diffuses, expands and forms a vortex in the inner cavity of the dispenser to promote the mixing of the gas-liquid two-phase refrigerant; at the same time, the enlarged chamber of the dispenser will also reduce the flow rate of the refrigerant. In the gas-liquid two-phase refrigerant, the flow of the liquid-phase refrigerant mainly depends on inertia force and gravity. The reduction of the refrigerant flow rate will inevitably weaken the inertia force of the liquid-phase refrigerant. After mixing, the liquid phase in the refrigerant will be separated from the gas phase again under the action of gravity, thereby affecting the uniformity of refrigerant distribution.

[0054] In the refrigerant uniform flow distributor provided in this embodiment, the partition plate 2 divides the accommodation cavity 103 in the body 1 into a first chamber 1031 and a second chamber 1032. While reducing the volume in the first chamber 1031, the input refrigerant is reflected by the partition plate 2, so that the two-phase refrigerant expands and mixes into a high-speed dispersed state in the first chamber 1031. On this basis, the inner wall of the liquid inlet end 101 is inclined and extended towards the liquid outlet end 102 of the body. This setting makes the inner wall of the liquid inlet end 101 form a secondary reflection surface. The refrigerant reflected back to the first chamber 1031 by the partition plate 2 is secondarily reflected by the inner wall of the liquid inlet end 101 to the position where the partition plate hole 21 is located, while realizing the uniform diversion and distribution of the refrigerant to the plurality of partition plate holes 21, and further promoting the collision and mixing of the two-phase refrigerant.

[0055] Among the position parameters related to the projection position A of the outer edge of the downstream end of the partition plate hole 21 on the inner wall of the liquid inlet end 101, the included angle α determines the extension slope of the inner wall of the liquid inlet end 101 and the secondary reflection travel of the partition plate 2 to the inner wall of the liquid inlet end 101. Specifically, the larger the included angle α, the larger the tangent slope at the position where the generatrix of the inner wall of the liquid inlet end 101 is located, and the larger the secondary reflection travel of the partition plate 2 to the inner wall of the liquid inlet end 101. In order to enable the refrigerant to enter the secondary reflection surface formed by the inner wall of the liquid inlet end 101 at a high speed, it is necessary to control the included angle α to avoid it being too large. If the included angle α is too small, it will compress the volume in the first cavity 1031, resulting in insufficient mixing space for the refrigerant, and at the same time, it will also increase the resistance of the refrigerant to enter the partition plate hole 21. Therefore, the included angle α is set to satisfy 8°≤α≤17°; preferably, the included angle α is set between 10° and 15°. However, the present invention does not make any limitation on this. In other embodiments, the included angle α can also be other angle values within 8° to 17°.

[0056] The axial distance H1 related to the projection position A, when the diameter of the main body accommodation cavity 103 and the included angle α are determined, further determines the radial distance from the outer edge of the partition hole 21 to the inner wall of the main body 1; that is, the axial distance H1 determines the spatial position of the partition hole 21 within the main body 1 (including the axial distance and the radial distance from the partition hole 21 to the inner wall of the main body 1). The smaller the axial distance H1, the closer the partition hole 21 will be to the inner wall of the main body 1, and the inner wall of the inclined liquid inlet end 101 will hinder the refrigerant from entering the partition hole 21 and increase the flow resistance; while an excessive axial distance H1 will cause the partition hole 21 to be too close to the center of the main body, resulting in the refrigerant passing through the partition hole 21 and entering the second cavity 1032 without sufficient mixing, thus seriously affecting the liquid distribution uniformity. Therefore, the axial distance H1 is set to satisfy: 1 mm ≤ H1 ≤ 5 mm; preferably, the axial distance H1 is set to 2 mm to 4 mm. However, the present utility model does not make any limitation in this regard. In other embodiments, other values within the range of 1 mm to 5 mm may also be set for the axial distance H1.

[0057] Further, as described above, the inner wall of the liquid inlet end 101 of the main body serves as a secondary reflection surface to distribute the fully mixed diffused refrigerant into the partition hole 21, thereby achieving uniform distribution of the refrigerant in multiple partition holes 21. Therefore, the included angle α and the axial distance H1 of the projection position A need to be comprehensively set so that the partition hole 21 is located on the exit path of the inner wall of the liquid inlet end 101 of the main body.

[0058] Further, in the refrigerant flow equalizing distributor provided in this embodiment, the partition hole 21 is located on the outer periphery of the projection area of the liquid inlet pipe assembly hole 104 on the partition 2. As Figure 6 shown, the area C enclosed by the dashed line is the projection area of the liquid inlet pipe assembly hole 104 on the partition 2, and this area is a closed area to reflect the refrigerant input from the liquid inlet pipe assembly hole 104. The stagger - distributed partition holes 21 prevent the high - speed refrigerant input from the liquid inlet pipe assembly hole 104 from directly passing through to the second cavity 1032 for direct distribution. Instead, after being reflected by the closed area on the partition 2, it returns to the first cavity 1031 for re - mixing. After being fully mixed into a diffused refrigerant, it then evenly enters the second cavity 1032 through the multiple partition holes 21 distributed in a ring shape to achieve uniform distribution of the refrigerant, which well solves the problem of uneven refrigerant distribution caused by the refrigerant directly passing through to the liquid outlet side without sufficient mixing in the existing filter - type or sieve - type distributors.

[0059] The relevant parameters of the projection position A of the outer edge of the downstream end of the partition plate 2 and the partition plate hole 21, as well as the misaligned distribution of the multiple partition plate holes 21 and the liquid inlet pipe assembly holes 104, enable the two-phase refrigerant to be fully mixed into a high-speed dispersed flow pattern in the first cavity 1031. After that, it is necessary to evenly distribute the fully mixed refrigerant into the multiple branch pipe holes 105. Therefore, in the refrigerant flow equalizing distributor provided in this embodiment, a plurality of partition plate holes 21 are arranged in an equally spaced annular distribution on the partition plate 2 and the number thereof is the same as the number of the branch pipe holes 105, and each partition plate hole 21 is substantially coaxial with the corresponding branch pipe hole 105. The equally spaced distribution of the multiple partition plate holes 21 enables the refrigerant fully mixed in the first cavity 1031 to be evenly distributed into the multiple partition plate holes 21 in the circumferential direction. The basic coaxiality of the partition plate hole 21 and the corresponding branch pipe hole 105 forms the shortest axial transmission path therebetween, and the high-speed refrigerant output from the partition plate hole 21 can quickly enter the corresponding branch pipe hole 105, maintaining the flow pattern of the refrigerant after mixing as much as possible and further improving the uniformity of refrigerant distribution.

[0060] Although this embodiment is described by taking the number of the partition plate holes 21 being the same as the number of the branch pipe holes 105 and the two being coaxially arranged as an example. However, the present utility model does not make any limitation thereto. In other embodiments, the number of the partition plate holes may also be twice or three times the number of the branch pipe holes, and two or three partition plate holes form a group to correspond to the corresponding branch pipe holes one by one. In the refrigerant flow equalizing distributor provided in this embodiment, the number of the partition plate holes is limited and the aperture thereof is relatively large; preferably, the ratio of the aperture D1 of the downstream end of the partition plate hole 21 to the outer diameter D2 of the branch pipe 3 inserted into the branch pipe hole 105 is 0.8 to 1.2. The relatively large aperture of the partition plate hole 21 is not only more conducive to the passage of the refrigerant but also can effectively reduce the pressure loss of the refrigerant during the distribution process; specifically, the ratio of the aperture D1 of the downstream end of the partition plate hole 21 to the outer diameter D2 of the branch pipe 3 inserted into the branch pipe hole 105 can be set to ratios such as 0.85, 0.9, 0.95, 1.0, 1.05, 1.1, 1.15, etc. However, the present utility model does not make any limitation thereto. In other embodiments, D1 / D2 may also be other ratios within 0.8 to 1.2.

[0061] In this embodiment, as Figure 2 and Figure 3 shown, the partition plate hole 21 is a through hole with substantially the same aperture along the refrigerant flow direction and the shape of the through hole is circular. However, the present utility model does not make any limitation thereto. In other embodiments, the partition plate hole may also be set as an elliptical or waist-shaped through hole.

[0062] In other embodiments, as Figure 7A and Figure 7B shown, the partition plate hole 21 may also be set as a converging hole with an inclined straight inner wall generatrix and its aperture gradually decreasing along the refrigerant flow direction. Or, as Figure 7CAs shown, the partition plate 2 includes a partition plate body 2a and a partition plate liner 2b stacked on the partition plate body 2a. A plurality of through holes 2a1 are formed in the partition plate body 2a, and a plurality of partition plate liner holes 2b1 corresponding to the distribution of the plurality of through holes 2a1 are formed in the partition plate liner 2b. The aperture of the partition plate liner holes 2b1 gradually decreases along the flowing direction of the refrigerant. The partition plate liner holes 2b1 and the corresponding through holes 2a1 together form partition plate holes 21. In Figure 7C , the partition plate 2 includes a plurality of partition plate liners 2b stacked in the area near the through holes 2a1 and having an area smaller than that of the partition plate body 2a. However, the present invention does not make any limitation in this regard. In other embodiments, the area of the partition plate liner may be the same as that of the partition plate body. The gradual reduction of the inner diameter of the partition plate holes 21 can accelerate the refrigerant flowing through, increase the flow rate of the refrigerant so that it can quickly enter the corresponding branch pipe holes 105; in addition, the acceleration of the partition plate holes 21 can also further promote the mixing of the gas-liquid two-phase refrigerant. However, the present invention also does not make any limitation in this regard.

[0063] In other embodiments, such as Figure 7D shown, the partition plate holes 21 can also be set as flanging holes with the inner wall generatrix in an arc shape and the aperture gradually decreasing along the flowing direction of the refrigerant; or, in Figure 7D shown, a straight hole section with a substantially unchanged aperture is added to the end of the flanging hole, that is, the inner wall generatrix of the partition plate hole is a combination of an arc shape and a straight line. In addition, in other embodiments, the partition plate holes 21 can also be set as arc bubble holes with the hole wall arcuately protruding towards one side or both sides of the partition plate, such as Figure 7E and Figure 7F shown.

[0064] In this embodiment, the partition plate 2 is a plate structure with both side surfaces being close to a planar shape and a circular cross-section. However, the present invention does not make any limitation in this regard. In other embodiments, the projection area of the liquid inlet pipe assembly hole on the partition plate can also be set into other shapes, such as being recessed towards the direction of the liquid outlet end of the body to form a reflection mixing cavity with an opening facing the liquid inlet pipe assembly hole, etc.

[0065] In this embodiment, such as Figure 3 and Figure 4As shown, the refrigerant flow equalizing distributor further includes a liquid inlet pipe 4 welded and connected to the liquid inlet pipe assembly hole 104, and the axial length L from the end face of the liquid outlet end of the liquid inlet pipe 4 to the surface of the partition plate 2 at the upstream end of the partition plate hole 21 satisfies 3.5 mm ≤ L ≤ 11.5 mm. Specifically, the liquid inlet pipe assembly hole 104 has a welding assembly straight section 106 extending to the outside of the body, and the liquid inlet pipe 4 is formed with a connection section 41 welded and connected to the welding assembly straight section 106. The connection section 41 is a straight section, and the end face of the end of the connection section 41 is the end face of the liquid outlet end of the liquid inlet pipe. This setting, while ensuring that the assembly strength of the liquid inlet pipe 4 meets the requirements of the refrigeration system, on the one hand, avoids the liquid outlet end of the liquid inlet pipe 4 extending excessively into the first cavity 1031, which affects the effective refrigerant mixing volume in the first cavity 1031 and the flow resistance of the refrigerant entering the partition plate hole 21. On the other hand, since the refrigerant entering the first cavity 1031 is bound to face volume expansion, resulting in a decrease in the refrigerant flow rate, an overly long axial length L will cause a decrease in the kinetic energy impacting on the partition plate 2, reducing the primary reflection mixing effect of the partition plate 2 and the secondary reflection mixing effect on the inner wall of the liquid inlet end 101, and thus seriously affecting the mixing and atomization degree of the refrigerant.

[0066] Preferably, the axial length L from the end face of the liquid outlet end of the liquid inlet pipe 4 to the surface of the partition plate 2 at the upstream end of the partition plate hole 21 is set to 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, 10 mm, etc. However, the present utility model does not make any limitation in this regard. In other embodiments, the axial length L can also be other values within 3.5 mm ≤ L ≤ 11.5 mm.

[0067] In this embodiment, the liquid inlet pipe 4 is welded and connected to the liquid inlet pipe assembly hole 104. The present utility model does not make any limitation on the connection method of the liquid inlet pipe. In other embodiments, the liquid inlet pipe can also be integrally formed with the body where the liquid inlet pipe assembly hole is located.

[0068] In the refrigerant flow distributor provided in this embodiment, the homogeneous dispersed flow output by the partition hole 21 rushes toward the corresponding branch hole 105 under the action of inertial force, and part of the refrigerant will inevitably hit the inner bottom wall of the liquid outlet end 102 of the main body and flow back along the peripheral wall of the main body 1, thereby generating a vortex zone near the branch hole 105 near the peripheral wall of the main body 1. The existence of the vortex zone will squeeze the refrigerant flow channel at the entrance of the branch hole 105 and reduce the mass flow entering the branch hole 105, which not only affects the uniformity of the refrigerant distribution but also affects its flow resistance. In order to reduce the adverse effect of the vortex zone near the branch hole 105 on the uniform distribution of the flow, the branch hole 105 in this embodiment includes a drainage hole section 1051 and a connecting hole section 1052 distributed in sequence along the flow direction of the refrigerant, and the aperture of the drainage hole section 1051 gradually decreases along the flow direction of the refrigerant. Under the premise that the inner diameter of the connecting hole section 1052 remains unchanged, the gradual reduction of the diameter of the drainage hole section 1051 will inevitably increase the diameter at the entrance of the drainage hole section (i.e., increase the refrigerant flow channel at its entrance), so that the refrigerant can better enter the drainage hole section 1051. In addition, the increase in the diameter at the entrance of the drainage hole section 1051 also reduces the reflection area of ​​the inner bottom wall of the liquid outlet end 102 of the body to the refrigerant, thereby reducing the range of the vortex area and weakening its squeezing of the refrigerant flow channel, thereby further improving the diversion uniformity and reducing the diversion resistance.

[0069] In this embodiment, the refrigerant flow distributor further includes a branch pipe 3 inserted into the branch pipe hole connection hole section 1052. Due to the thickness of the branch pipe 3, a step is formed at the front end surface of the branch pipe 3. The refrigerant hits the step surface to generate eddy currents, thereby hindering the flow of the refrigerant. To solve this problem, Figure 4 and Figure 5 As shown, in this embodiment, the downstream end aperture of the drainage hole section 1051 is set to be smaller than the aperture of the connecting hole section 1052, and a stopper 1053 protruding toward the center direction of the branch pipe hole 105 is formed at the connection between the drainage hole section 1051 and the connecting hole section 1052, and the inner diameter D3 at the stopper 1053 is substantially close to the inner diameter D4 of the inserted branch pipe 3. The stopper 1053 is configured to abut against the insertion end surface of the branch pipe 4 to achieve the insertion assembly limit of the branch pipe 3, and the inner diameter D3 of the stopper 1053 is substantially close to the inner diameter D4 of the branch pipe, so that there is no step at the insertion front end surface of the branch pipe 3, and the refrigerant flowing into the drainage hole section 1051 can smoothly enter the branch pipe 3 to further reduce the flow resistance of the refrigerant.

[0070] In this embodiment, the inner wall generatrix of the drainage hole section 1051 is an inclined straight line, and the inner wall generatrix of the drainage hole section 1051 (the inner wall generatrix of the drainage hole section and the tangent at the inner wall generatrix coincide with each other) forms an angle β with the center line of the branch hole 105, and 10°≤β≤65°. Preferably, the angle β can be set to 45°, such as Figure 5As shown. However, the present utility model makes no limitation thereto. In other embodiments, the included angle β may be other angular values within 10° to 65°, such as 15°, 20°, 25°, 30°, 40°, 45°, 50°, 55°, and 60°, etc. Although this embodiment is described by taking the inner wall generatrix of the drainage hole as an inclined straight line as an example, however, the present utility model makes no limitation thereto. In other embodiments, the drainage hole section may also be a flanging hole shape with an arc-shaped inner wall generatrix, and the included angle β formed between the tangent line at the inner wall generatrix of the drainage hole section and the center line of the branch pipe hole satisfies 10° ≤ β ≤ 65°. Such as Figure 2 and Figure 8 As shown, in this embodiment, the body 1 includes a cylinder 11, an end cover 12, and a lining plate 13. The cylinder 1 is integrally formed and is in a single-end open shape, and a plurality of diversion holes 111 are formed at the bottom of the cylinder 11. The lining plate 13 is fitted and welded to the inner bottom surface of the cylinder 11, and together with the cylinder 11 forms the liquid outlet end wall of the body 1; a plurality of lining plate holes 131 coaxial with the plurality of diversion holes 111 are formed on the lining plate 13, and the lining plate holes 131 and the corresponding diversion holes 111 together form the branch pipe hole 105. Specifically, the section of the lining plate hole 131 close to the second cavity 1032 forms the drainage hole section 1051, and the section close to the bottom of the cylinder 11 and the diversion hole 111 together form the connection hole section 1052. The end cover 12 is in an arc-shaped curved surface shape, one end of which is welded and connected to the open end of the cylinder 11, and a liquid inlet pipe assembly hole 104 is formed at the other end.

[0071] Although this embodiment is described by taking the drainage hole section and the connection hole section being integrally formed on the liquid outlet end wall of the body as an example. However, the present utility model makes no limitation thereto. In other embodiments, such as Figure 9 and Figure 10 As shown, the refrigerant uniform flow distributor may also include a baffle 5 fitted and welded to the inner end wall of the liquid outlet end 102 of the body, and a plurality of baffle holes serving as the drainage hole section 1051 of the branch pipe hole are formed on the baffle 5. Figure 10A As shown is a schematic structural view of the baffle provided by another embodiment of the present utility model; in this structure, the hole depth of the baffle hole is formed based on the baffle thickness.

[0072] In this embodiment, the inner wall of the end cover 12 extends obliquely towards the liquid outlet end 102 of the body and is in an arc-shaped curved surface shape with an arc-shaped inner wall generatrix. However, the present utility model makes no limitation thereto. In other embodiments, such as Figure 11 As shown, it is also possible to set the inner wall generatrix of the liquid inlet end 101 of the body to be an inclined straight line, and the inner wall contour line of the end cover 12 to be in a frustum of a cone shape.

[0073] Figure 12The following is a schematic structural view of a refrigerant flow equalizing distributor provided by another embodiment of the present utility model. In this structure, the body 1' includes an end cover 12' and a lining plate 13'. One end of the end cover 12' is formed with a liquid inlet pipe assembly hole 104 and has a curved surface in the shape of an arc. The lining plate 13' is embedded in the other end of the end cover 12'. A plurality of lining plate holes serving as branch pipe holes 105 are formed on the lining plate 13'. Similarly, in other embodiments, it is also possible to set Figure 12 the inner wall generatrix of the end cover 12' to be an inclined straight line. In addition, although Figure 1 , Figure 9 , Figure 11 and Figure 12 the number of lining plates is one piece. However, the present utility model does not make any limitation in this regard. In other implementations, it is also possible to set the lining plate to be multiple pieces. After the multiple lining plates are stacked, they are welded to the inner wall of the cylinder, the outer wall of the cylinder or embedded in the open end of the end cover.

[0074] Correspondingly, this embodiment also provides a heat exchanger assembly, and this heat exchanger assembly includes the above-mentioned refrigerant flow equalizing distributor provided by this embodiment. Specifically, the heat exchanger assembly is a condenser or an evaporator.

[0075] On the other hand, this embodiment also provides a refrigeration device including a condenser or an evaporator.

[0076] Embodiment 2

[0077] This embodiment is basically the same as Embodiment 1 and its variations, the difference being that as shown in Figure 13 and Figure 14 , a concave cavity 201 with an opening facing the liquid inlet pipe assembly hole (not marked because the liquid inlet pipe 106 is assembled) is formed in the area of the partition plate 2 opposite to the liquid inlet pipe assembly hole 104, and the partition plate 2 at the concave cavity 201 bulges and extends towards the side where the liquid outlet end 102 of the body is located.

[0078] Compared with the first embodiment, in this embodiment, a concave cavity 201 is provided on the partition plate 2 to provide sufficient mixing space for the refrigerant after high-speed impact reflection to promote the full mixing of the two-phase refrigerant. At the same time, when the mass flow rate of the input refrigerant is relatively large, the setting of the concave cavity 201 can also effectively reduce the influence of the reflection force on the input refrigerant at the liquid inlet pipe assembly hole 104, and avoid the refrigerant reflux in the liquid inlet pipe caused by excessive reflection force. The partition plate 2 at the concave cavity 201 protrudes and extends toward the side where the body liquid outlet end 102 is located. This setting, on the one hand, reduces the volume in the second cavity 1032, and avoids the gas-liquid phase segregation of the homogeneous refrigerant output from the partition hole 21 due to re-expansion and deceleration in the second cavity 1032; on the other hand, it also makes the annular diversion groove formed between the outer wall of the concave cavity 201 and the second cavity 1032. The homogeneous refrigerant output from the partition hole 21 can be evenly distributed along the annular diversion groove into a plurality of branch pipe holes 105 distributed in a ring shape at the bottom of the body 1, realizing the symmetrical diversion of the refrigerant.

[0079] In this embodiment, the inner cavity shape of the concave cavity 201 is cylindrical and the outer bottom wall of the concave cavity 201 abuts against the inner bottom wall of the body liquid outlet end 102. However, the present utility model does not make any limitation in this regard. In other embodiments, the inner cavity shape of the concave cavity can also be a cone (as Figure 15A shown), a frustum of a cone (as Figure 15B shown), a prism, a frustum of a prism, a pyramid or a partial sphere (as Figure 15C shown), or a combination of one or more of them, such as a combination of a cylinder and a partial sphere (as Figure 15D shown), a combination of a frustum of a cone and a partial sphere, a combination of a prism and a partial sphere, etc.

[0080] Embodiment Three

[0081] This embodiment is basically the same as the first embodiment and its variations, the difference being that the structures of the liquid inlet pipe assembly hole 104 and the liquid inlet pipe 4 are different.

[0082] As Figure 16 and Figure 16A shown, in this embodiment, the liquid inlet pipe assembly hole 104 is a through hole with a non-welded assembly straight section. In this embodiment, the liquid inlet pipe 4 has a Venturi tube structure, and the connecting section 41' has an expanding structure with an arc-shaped curve for the outer wall generatrix. The connecting section 41' extends into the first cavity 1031 through the liquid inlet pipe assembly hole 104, and the outer wall of the connecting section 41' is welded and attached to the inner wall of the body liquid inlet end 102.

[0083] Definition: The extended line of the inner wall generatrix of the straight section 42' of the throat on the Venturi tube section intersects with the virtual extension surface of the inner wall of the liquid inlet end 101 at the liquid inlet tube assembly hole 104 at position K. The cross-section of the liquid inlet tube 4 passing through position K is the end face of the liquid outlet end of the liquid inlet tube 4. In addition, affected by the connection method of the liquid inlet tube 4, in this embodiment, the liquid inlet tube 4 is welded to the inner wall of the main body liquid inlet end 102 through an expanding connection section 41'. Therefore, it is defined that: the extended line of the outer wall generatrix of the straight section 42' of the throat on the Venturi tube section intersects with the virtual extension surface of the inner wall of the liquid inlet end 101 at the liquid inlet tube assembly hole 104 at position K'. The center of the cross-section of the liquid inlet tube 4 passing through position K' is defined as the center O of the downstream end of the liquid inlet tube assembly hole.

[0084] In this embodiment, the axial length L from the end face of the liquid outlet end of the liquid inlet tube 4 to the surface of the partition plate 2 at the upstream end of the partition plate hole 21 still satisfies 3.5 mm ≤ L ≤ 11.5 mm. Similarly, the included angle α between the line connecting the projection position A of the outer edge of the downstream end of the partition plate hole 21 along the axial direction of the main body on the inner wall of the liquid inlet end 102 and the center O of the downstream end of the liquid inlet tube assembly hole and the radial direction of the partition plate 2 still satisfies: 8° ≤ α ≤ 17°.

[0085] However, the present invention does not make any limitation on the specific structure of the liquid inlet tube assembly hole. In other embodiments, when there is a welding assembly straight section on the liquid inlet tube assembly hole, the connecting section on the liquid inlet tube can also be set to include a straight section and an expanding section located downstream of the straight section and fitting and welding to the inner wall of the main body liquid inlet end.

[0086] In this example, the number of the branch pipes 3 is ten. However, the present invention does not make any limitation on this.

[0087] Embodiment Four

[0088] This embodiment is basically the same as Embodiment One and its variations, the difference being: the structure of the branch pipe 3 is different.

[0089] In this embodiment, as Figure 17 shown, each branch pipe 3 includes a first pipe section 31 and a second pipe section 32 located downstream of the first pipe section 31 and having an inner diameter smaller than that at the downstream end of the first pipe section 31. The difference △d between the inner diameter d11 at the downstream end of the first pipe section 31 and the inner diameter d12 at the downstream end of the second pipe section 32 is: 0.1 mm ≤ △d ≤ 3.5 mm. A reflection section 311 is formed on the first pipe section 31 and bends and extends to one side relative to the center line of the branch pipe hole 105. The included angle θ formed by the intersection of the axis at the upstream end of the reflection section 311 and the axis at the downstream end of the reflection section satisfies 90° ≤ θ ≤ 175°. Based on the reflection section 311, the axis of the second pipe section 32 intersects with the center line of the branch pipe hole 105.

[0090] The first pipe section 31 with a larger inner diameter increases the refrigerant flow rate distributed to each branch pipe 3 and reduces the distribution resistance of the refrigerant. The second pipe section 32 with a relatively smaller inner diameter can increase the refrigerant flow velocity in the branch pipe to meet the performance requirements of the rear heat exchanger assembly. On this basis, the inner diameter difference △d precisely controls the degree of pressure reduction and velocity increase of the refrigerant in the second pipe section 32, avoiding excessive pressure loss of the refrigerant due to excessive velocity increase. The setting of the reflection section 311 makes the second pipe section 32 no longer coaxial with the center line of the branch pipe hole 105. When there is a pressure wave downstream and it oscillates upstream, the reflection section 311 reflects and absorbs part of the pressure wave and changes the propagation direction of the remaining pressure wave to make it decay rapidly, effectively avoiding the influence of the downstream pressure wave on the upstream branch pipe hole 105 to further improve the distribution performance.

[0091] In this embodiment, the branch pipe 3 further includes a third pipe section 33 welded to the first pipe section 31, and the second pipe section 32 is located on the third pipe section 33. Specifically, as Figure 17 shown, the third pipe section 33 has a socket connection portion 331 that is sleeved on the end of the first pipe section 31 and has a flared structure. A second pipe section 32 with a gradually decreasing inner diameter is formed downstream of the socket connection portion 331. However, the present invention makes no limitation thereto. In other embodiments, it is also possible to set the end of the first pipe section 31 to be welded to the socket portion 331 sleeved on the third pipe section 33. At this time, the second pipe section is still a structure with a gradually decreasing inner diameter located downstream of the socket portion 331, as Figure 18A shown.

[0092] Figure 18B and Figure 18C shown is a schematic structural diagram of a branch pipe provided by another embodiment of the present utility model. Figure 18B In it, the first pipe section 31, the second pipe section 32, and the third pipe section 33 are integrally formed; Figure 18C In it, the first pipe section 31 and the second pipe section 32 are integrally formed, and the third pipe section 33 is welded to the end of the second pipe section. In other embodiments, it is also possible to directly form the second pipe section at the socket connection of the first pipe section and the second pipe section. In addition, it is also possible to provide a plurality of second pipe sections at the downstream end of the first pipe section. The third pipe section 33 can be set as a straight pipe or a bent pipe according to actual applications.

[0093] Embodiment Five

[0094] This embodiment is basically the same as Embodiment One and its variations, except that: the branch pipe 3 has another structure.

[0095] As Figure 19As shown in the figure, in this embodiment, each branch pipe 3 includes a connecting straight section 31', a jet section 32' located downstream of the connecting straight section 31' and having an inner diameter smaller than the inner diameter d11' of the connecting straight section body 311', and a branch section 33' located downstream of the jet section 32'. An equal-diameter section 331' with an inner diameter substantially close to the inner diameter d11' of the connecting straight section body is formed on the branch section 33'. The difference △d' between the inner diameter d11' of the connecting straight section body and the minimum inner diameter d12' at the jet section 32' is: 0.1mm ≤ △d' ≤ 3.5mm. The connecting straight section body 311' refers to the pipe section on the connecting straight section 31' where both the inner diameter and the outer diameter are substantially unchanged.

[0096] The refrigerant uniform flow distributor provided in this example improves the refrigerant flow rate in the branch pipe 3 by adding a jet section 32' to each branch pipe 3 to meet the performance requirements of the rear heat exchanger assembly. On this basis, the inner diameter difference △d' precisely controls the degree of pressure reduction and speed increase of the refrigerant by the jet section 32', avoiding excessive pressure loss of the refrigerant due to excessive speed increase. Further, an equal-diameter section 331' with an inner diameter d13' substantially close to the inner diameter d11' of the connecting straight section body is provided on the branch section 33' to reduce the flow resistance of the refrigerant in the branch pipe 3 and achieve balanced control of the refrigerant flow rate and pressure loss.

[0097] In this embodiment, the jet section 32' is a contraction section integrally formed upstream of the branch section 33', and the two are integrally formed and then welded to the connecting straight section 31'. However, the present utility model makes no limitation thereto. In other embodiments, as Figure 20A shown, the jet section 32' can also be integrally formed downstream of the connecting straight section 31' and then welded to the branch section 33'. Or, as Figure 20B shown, the connecting straight section 31', the jet section 32' and the branch section 33' are integrally formed.

[0098] Or, the jet section 32' is a jet orifice plate placed at the socket connection of the connecting straight section 31' and the branch section 33'. Specifically, as Figure 20C shown, the upstream end of the branch section 33' is flared and socket-connected to the downstream end of the connecting straight section 31', and the jet section 32' is placed at the flare of the branch section 33'. Similarly, when the downstream end of the connecting straight section 31' is flared and externally connected to the upstream end of the branch section 33', the jet section 32' can also be placed at the flare of the downstream end of the connecting straight section 31', as Figure 20D shown.

[0099] Or, the jet section 32' is set as a straight pipe section, and its two ends are respectively socket-connected to the connecting straight section 31' and the branch section 33', as Figure 20E shown. In Figure 19 , Figure 20A and Figure 20EIn [the figure], the jet part 32’ has a holding length L32 with a substantially constant inner diameter. However, the present utility model does not make any limitation in this regard.

[0100] The present utility model does not make any limitation on the forming manner of the jet part. Any jet part structure that can achieve a reduction in the inner diameter relative to the inner diameter of the connecting straight section body is within the protection scope of the present utility model.

[0101] To sum up, the refrigerant uniform flow distributor provided by the present utility model divides the accommodation cavity in the body into a first cavity and a second cavity through a partition plate to reduce the volume of each chamber in the body. The first cavity provides a suitable expansion space for the gas-liquid two-phase refrigerant input by the liquid inlet pipe so that the two-phase refrigerant is fully mixed into a high-speed dispersed flow pattern, effectively solving the problem that the mixed refrigerant in the existing distributor appears gas-liquid two-phase segregation again due to the too large inner cavity of the body. At the same time, by setting the inner wall of the liquid inlet end to extend obliquely towards the liquid outlet end of the body, the inner wall of the liquid inlet end forms a secondary reflection surface, and the dispersed refrigerant after being reflected by the partition plate is reflected into multiple partition plate holes again, realizing uniform diversion and distribution of the refrigerant and further improving the mixing degree of the two-phase refrigerant through secondary reflection. The setting of the angle α related to the projection position A realizes the control of the secondary reflection stroke from the partition plate to the inner wall of the liquid inlet end, ensuring that the refrigerant after being reflected by the partition plate can be incident on the inner wall of the liquid inlet end again for secondary reflection. And the axial distance H1 related to the projection position A determines the spatial position of the partition plate holes so that they are located on the outgoing path of the secondary reflection; at the same time, this setting also effectively avoids the obstruction of the refrigerant flow by the inner wall of the body, so that the refrigerant can be evenly distributed into multiple partition plate holes.

[0102] In addition, by arranging a plurality of partition plate holes on the outer periphery of the projection area of the liquid inlet pipe assembly hole on the partition plate, the projection area of the liquid inlet pipe on the partition plate can block the input refrigerant and reflect it back into the first cavity to further promote the mixing of the two-phase refrigerant. At the same time, the staggered distribution of the partition plate holes and the liquid inlet holes also effectively avoids the refrigerant flowing directly into the second mixing cavity without being mixed in time, thereby greatly improving the mixing uniformity of the two-phase refrigerant.

[0103] Although the present utility model has been disclosed above with the preferred embodiments, it is not intended to limit the present utility model. Any person skilled in this art can make some modifications and refinements without departing from the spirit and scope of the present utility model. Therefore, the protection scope of the present utility model shall be subject to the scope claimed in the claims.

Claims

1. A refrigerant flow equalizing distributor, characterized in that, Comprising: A body, including a liquid inlet end, a liquid outlet end, and a receiving cavity respectively communicating with the liquid inlet end and the liquid outlet end. A liquid inlet pipe assembly hole is formed on the liquid inlet end of the body. The inner wall of the liquid inlet end extends obliquely towards the liquid outlet end of the body and its inner wall generatrix is an arc or an inclined straight line. A plurality of branch pipe holes for liquid distribution are formed on the liquid outlet end of the body; A partition plate, arranged in the receiving cavity of the body to divide the receiving cavity into a first cavity and a second cavity. A plurality of partition plate holes are formed on the partition plate, which are annularly distributed around the central axis of the body and communicate the first cavity and the second cavity. The plurality of partition plate holes are configured to correspond to the plurality of branch pipe holes one by one, and when projected along the axial direction of the body, the plurality of partition plate holes are located on the outer periphery of the liquid inlet pipe assembly hole; Wherein, the included angle α between the connection line between the projection position A of the outer edge of the downstream end of the partition plate hole on the inner wall of the liquid inlet end along the axial direction of the body and the center O of the downstream end of the liquid inlet pipe assembly hole relative to the radial direction of the partition plate is 8° ≤ α ≤ 17°, and the axial distance H1 from the surface of the partition plate where the upstream end of the partition plate hole is located to the projection position A satisfies: 1mm ≤ H1 ≤ 5mm. The outer edge of the downstream end of the partition plate hole refers to the edge of the downstream end of the partition plate hole farthest from the central axis of the body.

2. The refrigerant uniform flow distributor according to claim 1, characterized in that, The plurality of partition plate holes are equally spaced and annularly distributed on the partition plate and have the same number as the number of branch pipe holes. Each partition plate hole is substantially coaxial with the corresponding branch pipe hole. The ratio of the downstream end aperture D1 of the partition plate hole to the outer diameter D2 of the branch pipe inserted into the branch pipe hole is 0.8 - 1.

2.

3. The refrigerant uniform flow distributor according to claim 1, characterized in that, The refrigerant uniform flow distributor further includes a plurality of branch pipes respectively welded and connected in the plurality of branch pipe holes. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section. The difference △d between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1mm ≤ △d ≤ 3.5mm; A reflection section is formed on the first pipe section and extends bent towards one side relative to the central axis of the branch pipe hole. The included angle θ formed by the intersection of the axis at the upstream end of the reflection section and the axis at the downstream end of the reflection section is 90° ≤ θ ≤ 175°. Based on the reflection section, the axis of the second pipe section intersects the central axis of the branch pipe hole.

4. The refrigerant uniform flow distributor according to claim 1, wherein The refrigerant uniform flow distributor further includes a plurality of branch pipes respectively welded and connected in the plurality of branch pipe holes. Each branch pipe includes a connecting straight section, a jetting part located downstream of the connecting straight section and having a reduced inner diameter relative to the inner diameter of the connecting straight section in the body, and a branch section located downstream of the jetting part. An equal-diameter section with an inner diameter substantially close to the inner diameter of the connecting straight section in the body is formed on the branch section. The difference △d' between the inner diameter d11' of the connecting straight section in the body and the minimum inner diameter d12' at the jetting part is: 0.1mm ≤ △d' ≤ 3.5mm.

5. The refrigerant uniform flow distributor according to claim 1, characterized in that The partition plate hole is a through hole with substantially the same aperture; Or, its aperture gradually decreases along the flow direction of the refrigerant. The inner wall generatrix of the partition plate hole is linear or arc-shaped; Or, the partition plate hole is an arc bubble hole with the hole wall convexly curved towards one side or both sides of the partition plate; 6. The refrigerant uniform flow distributor according to claim 1, wherein The partition plate is a plate structure with both sides being substantially planar; Or, the area of the partition plate opposite to the liquid inlet pipe assembly hole is recessed towards the direction where the liquid outlet end of the body is located to form a reflection mixing cavity with an opening facing the liquid inlet pipe assembly hole.

7. The refrigerant uniform flow distributor according to claim 1, characterized in that, The refrigerant flow equalizing distributor further includes a liquid inlet pipe welded to the liquid inlet pipe assembly hole, and the axial length L from the end face of the liquid outlet end of the liquid inlet pipe to the surface of the partition where the upstream end of the partition hole is located satisfies 3.5 mm ≤ L ≤ 11.5 mm.

8. The refrigerant uniform flow distributor according to claim 7, wherein, A connection section for welding and connecting to the liquid inlet pipe assembly hole is formed on the liquid inlet pipe, and the connection section is a straight section; Alternatively, the connection section is a gradually expanding structure with an arc-shaped curve on the outer wall generatrix. The connection section extends into the first cavity through the liquid inlet pipe assembly hole, and the outer wall of the connection section is welded and fitted to the inner wall of the liquid inlet end of the body.

9. The refrigerant uniform flow distributor according to claim 1, wherein The branch pipe hole includes a diversion hole section and a connection hole section that are sequentially distributed along the refrigerant flow direction. The aperture of the diversion hole section gradually decreases along the refrigerant flow direction, and the inner wall generatrix thereof is linear or arc-shaped.

10. The refrigerant uniform flow distributor according to claim 9, characterized in that, The tangent line at the inner wall generatrix of the diversion hole section forms an angle β with the center line of the branch pipe hole, and 10° ≤ β ≤ 65°.

11. The refrigerant even flow distributor according to claim 9, wherein, The aperture of the downstream end of the diversion hole section is smaller than the aperture of the connection hole section. A limiting portion protruding towards the center of the branch pipe hole is formed at the connection of the diversion hole section and the connection hole section. The limiting portion is configured to abut against the end face of the branch pipe inserted into the branch pipe hole, and the aperture of the limiting portion is substantially close to the inner diameter of the inserted branch pipe.

12. The refrigerant uniform flow distributor according to claim 9, characterized in that, The refrigerant flow equalizing distributor includes a baffle plate welded and fitted to the inner end wall of the liquid outlet end of the body, and a plurality of baffle holes serving as the diversion hole section of the branch pipe hole are formed on the baffle plate; Alternatively, the diversion hole section and the connection hole section are integrally formed on the liquid outlet end wall of the body.

13. A heat exchanger assembly, characterized in that, It includes the refrigerant flow equalizing distributor according to any one of claims 1 to 12.

14. A refrigeration device, characterized in that, It includes the heat exchanger assembly according to claim 13.

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