Refrigerant uniform-distributor, heat exchanger assembly and cooling device

Abstract

The present disclosure provides a refrigerant uniforming distributor, a heat exchanger assembly and a refrigeration device.SOLUTION: The refrigerant uniform distributor includes a body 1 and a partition plate 2. The liquid supply end 101 of the main body 1 is provided with a liquid supply tube mounting hole, the inner wall of the liquid supply end 101 of the main body 1 is inclinedly extended to the liquid discharge end 102 of the main body and the generatrix thereof is an arc line or an inclined straight line; The partition plate 2 partitions the accommodating chamber into a first chamber 1031 and a second chamber 1032, the partition plate 2 is provided with a plurality of partition plate holes 21 annularly distributed around a center line of the main body, the plurality of partition plate holes 21 are in one to-one correspondence with the plurality of branch pipe holes, and the plurality of partition plate holes 21 are located at a periphery of the liquid inlet pipe mounting hole when projected along an axial direction of the main body 1.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] The present invention relates to the technical field of refrigerant distribution, and more particularly to uniform refrigerant distributors, heat exchanger assemblies and cooling devices. [Background technology]

[0002] Multi-channel heat exchangers have the advantages of low pressure drop and a high heat transfer coefficient, and are widely used in air conditioning systems to improve the cooling and heating performance of the system. To ensure good heat exchange performance, the two-phase refrigerant must be evenly distributed among the heat exchanger's channels. Traditional air conditioning systems primarily use distributors to distribute the two-phase refrigerant. When distributors are used in air conditioning systems, the most common problem is uneven refrigerant flow distribution, low liquid refrigerant flow rates in some channels, rapid evaporation, and a much lower heat transfer coefficient in the evaporation-drying region than in the two-phase region, resulting in a reduced effective heat transfer area and severely impacting the heat exchanger's heat exchange performance. Experiments have shown that uneven refrigerant distribution can reduce heat exchange capacity by as much as 25%.

[0003] Commonly used distributors in conventional cooling systems include Venturi distributors, pressure drop distributors, and jack distributors. Due to the linear constraints of the flow path, Venturi distributors are difficult to machine, costly, and difficult to ensure consistency after machining. Pressure drop distributors are a Venturi distributor with a simple structure, and while they offer some improvements in terms of machining difficulty and cost, they suffer from problems such as high pressure loss, high noise, and flow distribution performance that is affected by the installation angle. The impact of installation angle on flow distribution performance is most severe in jack distributors.

[0004] To solve the problem of uneven liquid separation in conventional distributors, those skilled in the art have optimized and improved the conventional distributor structure. While the Venturi and pressure drop distributors, which have complex structures, primarily focus on improving the flow path, the simple and low-cost Jack distributor (shown in Figure 1) primarily focuses on improving the mounting structure of each branch pipe on the liquid separation side. However, in a Jack separator, the two-phase refrigerant rapidly expands and diffuses after entering the distributor chamber. During this diffusion, gravity can easily cause two-phase separation and segregation. Furthermore, a large amount of liquid refrigerant settles at the bottom of the distributor, preventing it from being distributed into the branch pipes, resulting in poor liquid separation performance. This is also the main reason why the mounting angle of a Jack distributor is the most serious factor.

[0005] To further improve liquid separation performance, it has also been proposed to install a screen or filter within the distributor chamber. The screen or filter has a large number of liquid flow holes but small pore diameters. In such a structure, it is desirable for the screen or filter to create a constant pressure on the liquid supply pipe side so that the refrigerant flow rate through each liquid flow hole is uniform. However, in a screen or filter, some liquid flow holes directly face the liquid supply pipe, and refrigerant entering from the liquid supply pipe preferentially enters the liquid separation side through the liquid flow holes facing them, making it difficult to achieve uniform refrigerant flow rate distribution through each liquid flow hole. Furthermore, liquid flow holes with very small pore diameters inevitably obstruct the passage of refrigerant, resulting in excessive refrigerant pressure loss. For the evaporator, excessive refrigerant pressure loss means a lower evaporation temperature, a lower cooling capacity per unit mass of refrigerant, and a lower cooling capacity per unit volume of the compressor, which is detrimental to the cooling cycle. Summary of the Invention [Problem to be solved by the invention]

[0006] SUMMARY OF THE INVENTION The present invention provides a uniform refrigerant distributor, a heat exchanger assembly, and a cooling device to overcome at least one of the shortcomings of the prior art. [Means for solving the problem]

[0007] In order to achieve the above object, the present invention provides a refrigerant uniform distributor, comprising: a main body including a liquid supply end, a liquid drain end, and a storage chamber that connects the liquid supply end and the liquid drain end, the liquid supply end of the main body being formed with a liquid supply pipe attachment hole, the liquid supply end of the main body having an inner wall that extends at an angle to the liquid drain end of the main body with the inner wall bus line presenting an arc line or an inclined straight line, and the main body having a plurality of branch pipe holes for liquid separation at the liquid drain end; and a partition plate provided within the storage chamber of the main body to divide the storage chamber into a first chamber and a second chamber, the partition plate having a plurality of partition plate holes that are distributed annularly around the center line of the main body and connect the first chamber and the second chamber. a partition plate configured to be located on the outer periphery of the liquid feed pipe mounting hole when projected along the axial direction of the body, wherein the plurality of partition plate holes correspond one-to-one to the plurality of branch pipe holes; a partition plate configured to be located on the outer periphery of the liquid feed pipe mounting hole when projected along the axial direction of the body; a line connecting a projection position A of the outer edge of the downstream end of the partition plate hole onto the inner wall of the liquid feed end along the axial direction of the body and a center O of the downstream end of the liquid feed pipe mounting hole forms an angle α with the radial direction of the partition plate, and the angle α is 8°≦α≦17°; an axial distance H1 from the surface of the partition plate at the upstream end of the partition plate hole to the projection position A satisfies 1 mm≦H1≦5 mm; and the outer edge of the downstream end of the partition plate hole is the edge of the downstream end of the partition plate hole at the point farthest from the center line of the body.

[0008] According to one embodiment of the present invention, the partition plate holes are distributed annularly at equal intervals on the partition plate, and their number is the same as the number of branch pipe holes, and each is approximately coaxial with the opposite branch pipe hole. The ratio of the hole diameter D1 at 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 invention, the uniform refrigerant distributor further includes a plurality of branch pipes welded to the plurality of branch pipes, respectively. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section, the second pipe section having an inner diameter smaller than that of a downstream end of the first pipe section. A difference Δd between an inner diameter d11 of the downstream end of the first pipe section and an inner diameter d12 of the downstream end of the second pipe section is in the range of 0.1 mm≦Δd≦3.5 mm. The first pipe section has a reflector section bent and extending to one side of the center line of the branch pipe section, and an axis line of the upstream end of the reflector section intersects with an axis line of the downstream end of the reflector section at an angle θ (90°≦θ≦175°). The reflector section allows the axis line of the second pipe section to intersect with the center line of the branch pipe section.

[0010] According to an embodiment of the present invention, the uniform refrigerant distributor further includes a plurality of branch pipes welded to the plurality of branch pipe holes, each branch pipe including a straight connection portion, a jet portion located downstream of the straight connection portion and having an inner diameter smaller than that of the straight connection portion body, and a branch portion located downstream of the jet portion, wherein the branch portion has a constant diameter portion whose inner diameter is approximately the same as that of the straight connection portion body, and a difference △d' between the inner diameter d11' of the straight connection portion body and the minimum inner diameter d12' of the jet portion satisfies 0.1 mm≦△d'≦3.5 mm.

[0011] According to one embodiment of the present invention, the partition plate holes are through holes having substantially the same hole diameter; Alternatively, the hole diameter gradually decreases along the flow direction of the refrigerant, and the inner wall generatrix of the partition plate hole is linear or arc-shaped; Alternatively, the partition plate hole is an arc-shaped bubble hole whose hole wall protrudes in an arc shape to one or both sides of the partition plate.

[0012] According to one embodiment of the present invention, the partition plate has a plate structure that is nearly flat on both sides, Alternatively, the area of ​​the partition plate facing the liquid supply tube mounting hole is recessed toward the liquid discharge end of the main body to form a reflective mixing chamber with an opening facing the liquid supply tube mounting hole.

[0013] According to one embodiment of the present invention, the refrigerant uniform distributor further includes a liquid supply pipe welded to the liquid supply pipe mounting hole, and the axial length L from the end face of the discharge end of the liquid supply pipe to the surface of the partition plate at the upstream end of the partition plate hole satisfies 3.5 mm≦L≦11.5 mm.

[0014] According to one embodiment of the present invention, the liquid supply pipe is provided with a connecting portion which is welded to the liquid supply pipe mounting hole, and the connecting portion is a straight portion; Alternatively, the connecting portion has a fan-shaped structure in which the outer wall generatrix forms an arc-shaped curve, and protrudes into the first chamber through the liquid supply pipe mounting hole, and the outer wall is tightly welded to the inner wall of the liquid supply end of the main body.

[0015] According to one embodiment of the present invention, the liquid feed pipe is a circular pipe member having a substantially uniform wall thickness, is connected to the liquid feed pipe mounting hole, and includes at least one Venturi tube section, each Venturi tube section including, in order along the refrigerant flow direction, a tapered section having a gradually decreasing inner diameter, a straight throat section having a substantially uniform inner diameter, and a divergent section having a gradually increasing inner diameter.

[0016] According to one embodiment of the present invention, the liquid feed pipe is formed with two venturi sections connected in series, namely an upstream venturi section and a downstream venturi section, and the inner diameter of the straight throat section of the downstream venturi section is equal to or smaller than the inner diameter of the straight throat section of the upstream venturi section.

[0017] According to one embodiment of the present invention, the liquid supply pipe further includes a variable diameter hole plate provided downstream of the Venturi tube portion, and the variable diameter hole plate is formed with variable diameter holes, and the variable diameter holes include a tapered hole portion whose hole diameter gradually decreases along the flow direction of the refrigerant, and a throat hole portion located downstream of the tapered hole portion and whose hole diameter remains almost constant.

[0018] According to an embodiment of the present invention, the branch pipe holes include suction holes and connection holes sequentially distributed along the refrigerant flow direction, and the suction holes have a diameter that gradually decreases along the refrigerant flow direction, and the inner wall generatrix thereof is linear or arc-shaped.

[0019] According to one embodiment of the present invention, there is an angle β between a tangent to the inner wall generatrix of the suction flow hole and the center line of the branch pipe, and 10°≦β≦65°.

[0020] According to one embodiment of the present invention, the diameter of the downstream end of the suction flow hole is smaller than the diameter of the connection hole; At the connection point between the suction flow hole and the connection hole, a stopper portion is formed which protrudes toward the center of the branch pipe hole and is configured to abut against the end face of the branch pipe inserted into the branch pipe hole, and whose hole diameter is approximately the same as the inner diameter of the branch pipe to be inserted.

[0021] According to one embodiment of the present invention, the refrigerant uniform distributor includes a baffle plate tightly welded to an inner end wall of the main body's discharge end, the baffle plate having a plurality of baffle plate holes which are branch pipe suction flow holes; Alternatively, the suction flow hole and the connecting hole are integrally formed in the end wall of the discharge end of the main body.

[0022] According to one embodiment of the present invention, the uniform refrigerant distributor further includes a flow path forming member disposed in the second chamber and positioned on the inner circumference of the plurality of branch pipe holes, the flow path forming member being a rotating member extending from the inner bottom wall of the drainage end of the main body toward the partition plate and rotating around the main body axis, the flow path forming member and the inner circumference wall of the second chamber surrounding an annular flow path connecting the partition plate hole and the plurality of branch pipe holes, the cross section of the flow path forming member being almost unchanged or gradually decreasing in its extending direction.

[0023] According to one embodiment of the present invention, the flow passage forming member is a spacer whose cross section does not change substantially in its extending direction and whose upper end abuts against the partition plate regions on the inner peripheries of the plurality of partition plate holes.

[0024] According to one embodiment of the present invention, the cross section of the flow path forming member gradually becomes smaller in its extension direction, and the vertical distance H2 from the extending tip of the flow path forming member to the downstream surface of the partition plate satisfies 1 mm≦H2≦2H0 / 3, where H0 is the height of the second chamber.

[0025] According to one embodiment of the present invention, the radial distance L1 from the outer periphery of the bottom of the flow path forming member to the inner circumferential wall of the second chamber satisfies L1≦28 mm.

[0026] According to one embodiment of the present invention, the partition plate holes are equally spaced in an annular row on the partition plate, the number of which is equal to the number of the branch pipe holes, and each of which is approximately coaxial with the corresponding branch pipe hole.

[0027] According to one embodiment of the present invention, the plurality of diaphragm holes are distributed on the diaphragm in a plurality of annular rows, each annular row having an equal number of the plurality of diaphragm holes distributed at equal intervals.

[0028] According to another aspect, the present invention further provides a heat exchanger assembly comprising the uniform refrigerant distributor described above.

[0029] According to another aspect, the present invention further provides a cooling device including the heat exchanger assembly described above. [Effects of the Invention]

[0030] As described above, the uniform refrigerant distributor of the present invention divides the storage chamber in the main body into a first chamber and a second chamber using a partition plate, thereby reducing the volume of each chamber. The first chamber provides an adequate expansion space for the gas-liquid two-phase refrigerant input from the supply pipe, allowing the two-phase refrigerant to be thoroughly mixed into a high-speed dispersed flow pattern. This effectively solves the problem of resegregation of the mixed refrigerant due to an oversized main body chamber, which is a problem of conventional distributors. Furthermore, the inner wall of the supply end extends at an angle toward the discharge end of the main body to form a secondary reflection surface. This secondary reflection of the dispersed refrigerant reflected and mixed by the partition plate into the multiple partition holes achieves uniform refrigerant distribution and further improves the degree of mixing of the two-phase refrigerant. The angle α relative to the projection position A can be adjusted to control the secondary reflection stroke from the partition plate to the inner wall of the supply end, ensuring that the refrigerant reflected by the partition plate can re-enter the inner wall of the supply end for secondary reflection. The spatial position of the partition plate holes is determined by the axial distance H1 relative to the projection position A, and the partition plate holes are positioned on the injection path of the secondary reflection. This configuration also effectively prevents the inner wall of the main body from interfering with the flow of the refrigerant, allowing the refrigerant to be distributed uniformly among the multiple partition plate holes.

[0031] The partition holes are located around the periphery of the projection of the liquid supply pipe hole onto the partition, so that the projection of the liquid supply pipe hole onto the partition can block the incoming refrigerant and reflect it back into the first chamber, further promoting the mixing of the two-phase refrigerant. The offset distribution of the partition holes and the liquid supply holes effectively prevents the refrigerant from reaching the second mixing chamber too early for mixing, further improving the mixing uniformity of the two-phase refrigerant.

[0032] In order to make the above and other objects, features and advantages of the present invention more clearly understandable, the following particularly preferred embodiments will be described in detail in conjunction with the drawings. [Brief explanation of the drawings]

[0033] [Figure 1]FIG. 1 is a structural schematic diagram of a conventional jack-type separator. [Figure 2] 1 is a structural schematic diagram of a refrigerant uniform distributor according to a first embodiment of the present invention; [Figure 3] FIG. 3 is a cross-sectional schematic view of FIG. 2. [Figure 4] FIG. 4 is a schematic diagram of the structure after the liquid supply pipe and branch pipe of FIG. 3 have been removed. [Figure 5] FIG. 5 is an enlarged schematic view of a portion B in FIG. [Figure 6] FIG. 3 is a structural schematic diagram of the partition plate in FIG. 2. [Figure 7A] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 7B] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 7C] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 7D] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 7E] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 7F] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 8] FIG. 3 is a structural schematic diagram of the end cap in FIG. 2. [Figure 9] FIG. 4 is a structural schematic diagram of a main body of a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 10] FIG. 10 is a schematic diagram of the structure of the baffle plate in FIG. [Figure 10A] FIG. 4 is a structural schematic diagram of a baffle plate according to another embodiment of the present invention. [Figure 11] FIG. 4 is a structural schematic diagram of a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 12] FIG. 4 is a structural schematic diagram of a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 13] 4 is a structural schematic diagram of a refrigerant uniform distributor according to a second embodiment of the present invention; FIG. [Figure 14] FIG. 14 is a structural schematic diagram of the partition plate in FIG. 13. [Figure 15A] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 15B] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 15C] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 15D] FIG. 10 is a structural schematic diagram of a partition plate according to another embodiment of the present invention. [Figure 16] 4 is a structural schematic diagram of a refrigerant uniform distributor according to a third embodiment of the present invention; [Figure 16A] FIG. 17 is a partial schematic view of FIG. 16. [Figure 17] 10 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to a fourth embodiment of the present invention; [Figure 18A] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 18B] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 18C] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 19] 5 is a structural schematic diagram of a refrigerant distributor according to a fifth embodiment of the present invention; [Figure 20A] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 20B] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 20C] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 20D] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 20E] FIG. 4 is a structural schematic diagram of a branch pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 21] 10 is a structural schematic diagram of a refrigerant uniform distributor according to a sixth embodiment of the present invention; [Figure 22] FIG. 4 is a structural schematic diagram of a partition plate in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 23] FIG. 4 is a structural schematic diagram of a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 24] FIG. 4 is a structural schematic diagram of a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 25] FIG. 10 is a structural schematic diagram of a refrigerant uniform distributor according to a seventh embodiment of the present invention. [Figure 26] 8 is a structural schematic diagram of a refrigerant uniform distributor according to an eighth embodiment of the present invention. [Figure 27] FIG. 4 is a structural schematic diagram of a liquid supply pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 28] FIG. 4 is a structural schematic diagram of a liquid supply pipe in a refrigerant uniform distributor according to another embodiment of the present invention. [Figure 29] FIG. 29 is a structural schematic diagram of the variable diameter hole plate in FIG. 28. DETAILED DESCRIPTION OF THE INVENTION

[0034] Example 1 As shown in Figure 1, in a conventional jack-type distributor, when the refrigerant enters the distributor chamber and diffuses and mixes, the refrigerant flow rate slows, and the liquid refrigerant tends to separate from the gas refrigerant due to gravity and accumulate at the bottom of the distributor, further affecting liquid separation uniformity. On the other hand, when a filter or screen-type distributor is added, the refrigerant may not be sufficiently mixed and may directly reach the liquid separation side through the branch pipe holes, and the pressure loss when the refrigerant passes through the liquid flow holes may be too large. In view of these issues, this embodiment provides a refrigerant distributor with excellent flow uniformity and low pressure loss.

[0035] 2 to 6, the refrigerant uniform distributor according to this embodiment includes a main body 1 and a partition plate 2. The main body 1 includes a liquid supply end 101, a liquid drain end 102, and a storage chamber 103 that connects the liquid supply end 101 and the liquid drain end 102. The liquid supply end 101 of the main body is formed with a liquid supply pipe mounting hole 104, and the inner wall of the liquid supply end 101 extends at an angle toward the main body liquid drain end 102, with the inner wall generatrix presenting an arc line or an inclined straight line, and the main body liquid drain end 102 is formed with a plurality of branch pipe holes 105 for liquid separation. The partition plate 2 is provided in the storage chamber 103 of the main body 1 so as to divide the storage chamber 103 into a first chamber 1031 and a second chamber 1032, and the partition plate 2 has a plurality of partition plate holes 21 formed therein that are distributed in a ring shape around the center line of the main body 1 and that connect the first chamber 1031 and the second chamber 1032, and the plurality of partition plate holes 21 correspond one-to-one to the plurality of branch pipe holes 105 and are configured to be located on the outer periphery of the liquid supply pipe mounting hole 104 when projected along the axial direction of the main body 1.

[0036] The projection of the outer edge of the downstream end of partition plate hole 21 onto the inner wall of liquid supply end 101 along the axial direction of main body 1 is projection position A, and the line connecting projection position A and the downstream end center O of liquid supply pipe mounting hole 104 forms an angle α with respect to the radial direction of partition plate 2 and is 8°≦α≦17°, the axial distance H1 from the surface of partition plate 2 at the upstream end of partition plate hole 21 to projection position A satisfies 1 mm≦H1≦5 mm, and the outer edge of the downstream end of partition plate hole 21 is the edge of the downstream end of partition plate hole 21 at the point farthest from the center line of main body 1.

[0037] The downstream and upstream regions are distinguished based on the direction of refrigerant flow. Generally, refrigerant flows from upstream to downstream, and the downstream region receives refrigerant from upstream. In an air conditioner, a distributor is typically installed vertically or at an angle, with the supply end of the distributor positioned below the drain end in the direction of gravity. The inertial force of the refrigerant in the distributor overcomes gravity and flows in the opposite direction. In this case, the upstream and downstream regions are distinguished based on the direction of refrigerant flow. According to the distinction between upstream and downstream, the downstream end of the partition plate hole 21 is the end of the partition plate hole 21 facing the second chamber 1032, and the downstream end center O of the supply pipe mounting hole 104 is the center of the cross section where the inner wall of the straight portion of the supply pipe mounting hole 104 intersects with the curved inner wall of the supply end 101 of the main body.

[0038] In conventional distributors, refrigerant flows through a supply pipe into the expanded distributor chamber. Due to inertia, the refrigerant diffuses and expands in the distributor chamber, forming vortices that promote mixing of the gas-liquid two-phase refrigerant. The expanded distributor chamber also reduces the refrigerant flow rate. The liquid-phase refrigerant flow in a gas-liquid two-phase refrigerant system relies primarily on inertia and gravity. A reduction in the refrigerant flow rate inevitably weakens the inertial force of the liquid refrigerant. The liquid phase in the mixed refrigerant is then separated from the gas phase by gravity, affecting the uniformity of refrigerant distribution.

[0039] In the uniform refrigerant distributor of this embodiment, the partition plate 2 divides the storage chamber 103 in the main body 1 into a first chamber 1031 and a second chamber 1032, reducing the internal volume of the first chamber 1031 and reflecting the input refrigerant at the partition plate 2, causing the two-phase refrigerant to expand and mix rapidly in the first chamber 1031 in a dispersed manner. Furthermore, the inner wall of the liquid supply end 101 is configured to extend at an angle toward the main body's liquid discharge end 102, forming a secondary reflection surface on the inner wall of the liquid supply end 101. The refrigerant reflected by the partition plate 2 to the first chamber 1031 is then secondarily reflected by the inner wall of the liquid supply end 101 back to the partition plate holes 21, thereby achieving uniform distribution of the refrigerant to the multiple partition plate holes 21 and further promoting collisional mixing of the two-phase refrigerant.

[0040] Among the position parameters related to the projection position A of the outer edge of the downstream end of partition plate hole 21 onto the inner wall of liquid supply end 101, angle α determines the inclination of the inner wall of liquid supply end 101 and the secondary reflection stroke from partition plate 2 to the inner wall of liquid supply end 101. Specifically, the larger the angle α, the greater the tangent inclination at the generatrix of the inner wall of liquid supply end 101, and the greater the secondary reflection stroke from partition plate 2 to the inner wall of liquid supply end 101. To ensure that the refrigerant is incident on the secondary reflection surface formed by the inner wall of liquid supply end 101 at high speed, angle α must be controlled so that it is not excessively large. On the other hand, if angle α is too small, the internal volume of first chamber 1031 will be compressed, resulting in insufficient mixing space for the refrigerant and increased resistance to the refrigerant entering partition plate hole 21. Therefore, angle α is designed to be 8°≦α≦17°, preferably between 10° and 15°, but the present invention is not limited thereto. In other embodiments, the angle α may be other angle values ​​between 8° and 17°.

[0041] When the diameter and angle α of the main body storage chamber 103 are determined, the axial distance H1 relative to the projection position A determines the radial distance from the outer edge of the partition plate hole 21 to the inner wall of the main body 1. That is, the axial distance H1 relative to the projection position A determines the spatial position of the partition plate hole 21 within the main body 1 (including the axial and radial distances from the partition plate hole 21 to the inner wall of the main body 1). The smaller the axial distance H1, the closer the partition plate hole 21 is to the inner wall of the main body 1, and the inclined inner wall of the liquid supply end 101 hinders the refrigerant from entering the partition plate hole 21, increasing flow resistance. On the other hand, if the axial distance H1 is too large, the partition plate hole 21 is too close to the center of the main body, and the refrigerant will pass through the partition plate hole 21 into the second chamber 1032 without being sufficiently mixed, which will seriously affect the liquid separation uniformity. Therefore, the axial distance H1 is set to satisfy 1 mm≦H1≦5 mm, and is preferably set to 2 mm to 4 mm, but the present invention is not limited thereto. In other embodiments, the axial distance H1 may be set to another value between 1 mm and 5 mm.

[0042] Furthermore, as described above, by using the inner wall of the liquid supply end 101 of the main body as a secondary reflection surface, the thoroughly mixed dispersed refrigerant is distributed to the partition plate holes 21, and the refrigerant is uniformly distributed within the plurality of partition plate holes 21. For this reason, it is necessary to set the angle α of the projection position A and the axial distance H1 together so that the partition plate holes 21 are positioned on the injection path on the inner wall of the liquid supply end 101 of the main body.

[0043] Furthermore, in the uniform refrigerant distributor of this embodiment, the partition plate holes 21 are located on the periphery of the projection area of ​​the liquid feed pipe mounting hole 104 onto the partition plate 2. As shown in Figure 6, area C surrounded by a dashed line is the projection area of ​​the liquid feed pipe mounting hole 104 onto the partition plate 2, and this area is a blocked area for reflecting the refrigerant input through the liquid feed pipe mounting hole 104. Due to the staggered partition plate holes 21, the high-speed refrigerant input through the liquid feed pipe mounting hole 104 does not directly reach the second chamber 1032 and be directly distributed. Instead, it is reflected by the blocked area of ​​the partition plate 2 and returns to the first chamber 1031 to be remixed. The sufficiently dispersed and mixed refrigerant then uniformly enters the second chamber 1032 through the multiple partition plate holes 21 distributed in an annular pattern, achieving uniform refrigerant distribution. This solves the problem of conventional filter-type or screen-type distributors, where the refrigerant does not reach the discharge side in time for mixing, resulting in uneven refrigerant distribution.

[0044] The two-phase refrigerant is thoroughly mixed in the first chamber 1031 in a high-speed, dispersed flow pattern depending on the parameters related to the partition plate 2 and the projected position A of the outer edge of the downstream end of the partition plate holes 21, and the offset distribution between the multiple partition plate holes 21 and the liquid supply pipe mounting hole 104. The thoroughly mixed refrigerant must then be uniformly distributed among the multiple branch pipe holes 105. Therefore, in the uniform refrigerant distributor of this embodiment, the multiple partition plate holes 21 are configured to be distributed annularly at equal intervals on the partition plate 2, and the number of the multiple partition plate holes 21 is the same as the number of the branch pipe holes 105, so that they are approximately coaxial with the opposing branch pipe holes 105. The uniform distribution of the multiple partition plate holes 21 allows the refrigerant thoroughly mixed in the first chamber 1031 to be uniformly distributed among the multiple partition plate holes 21 in the circumferential direction. The partition plate holes 21 are approximately coaxial with the corresponding branch pipe holes 105, forming the shortest axial transmission path between them. This allows the high-speed refrigerant output from the partition plate holes 21 to quickly enter the corresponding branch pipe holes 105, thereby maintaining the flow pattern after refrigerant mixing as much as possible and further improving the uniformity of refrigerant distribution.

[0045] In this embodiment, the number of partition plate holes 21 is the same as the number of branch pipe holes 105, and they are arranged coaxially, but the present invention is not limited to this. In other embodiments, the number of partition plate holes may be two or three times the number of branch pipe holes, and two or three partition plate holes form a pair that corresponds one-to-one with the corresponding branch pipe holes. In the uniform refrigerant distributor of this embodiment, the number of partition plate holes is limited and the hole diameters are large. Preferably, the ratio of the hole diameter D1 at 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 set to 0.8 to 1.2. The large diameter of the partition plate hole 21 is not only advantageous for the passage of the refrigerant but also effectively reduces the pressure loss of the refrigerant during distribution. Specifically, the ratio of the hole diameter D1 at 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 may be set to a ratio of 0.85, 0.9, 0.95, 1.0, 1.05, 1.1, 1.15, etc., but the present invention is not limited thereto. In other embodiments, D1 / D2 may be another ratio between 0.8 and 1.2.

[0046] 3 and 4, the partition plate holes 21 are circular through-holes whose diameters are substantially uniform along the refrigerant flow direction, but the present invention is not limited thereto. In other embodiments, the partition plate holes may be elliptical through-holes or elongated through-holes.

[0047] In another embodiment, as shown in Figures 7A and 7B, the partition holes 21 may be configured as a group of holes whose inner wall generatrix is ​​an inclined straight line and whose hole diameter gradually decreases along the refrigerant flow direction. Alternatively, as shown in Figure 7C, the partition plate 2 includes a partition plate main body 2a and a partition plate liner 2b superimposed on the partition plate main body 2a. The partition plate main body 2a has a plurality of through holes 2a1 formed therein. The partition plate liner 2b has a plurality of partition plate liner holes 2b1 distributed corresponding to the plurality of through holes 2a1. The diameters of the partition plate liner holes 2b1 gradually decrease along the refrigerant flow direction. The partition plate liner holes 2b1 and the corresponding through holes 2a1 form the partition plate hole 21. In Figure 7C, the partition plate 2 includes a plurality of partition plate liners 2b superimposed in regions near the through holes 2a1 and whose area is smaller than that of the partition plate main body 2a. However, the present invention is not limited to this. In other embodiments, the area of ​​the partition liner may be the same as that of the main partition body. The gradually decreasing inner diameter of the partition holes 21 accelerates the flow of the refrigerant, improving the refrigerant flow velocity and allowing it to quickly enter the corresponding branch pipe holes 105. The acceleration of the partition holes 21 can also further promote the mixing of the gas-liquid two-phase refrigerant, but the present invention is not limited to this.

[0048] In another embodiment, as shown in Figure 7D, the partition plate hole 21 may be configured as a burred hole whose inner wall busbar is arc-shaped and whose hole diameter gradually decreases along the refrigerant flow direction, or a straight perforated portion whose hole diameter is almost constant may be added to the end of the burred hole shown in Figure 7D, that is, the inner wall busbar of the partition plate hole may be a combination of an arc-shaped and a straight line.In addition, in another embodiment, as shown in Figures 7E and 7F, the partition plate hole 21 may be configured as an arc-shaped bubble hole whose hole wall protrudes in an arc to one or both sides of the partition plate.

[0049] In this embodiment, the partition plate 2 has a plate structure with both sides nearly flat and a circular cross section, but the present invention is not limited to this. In other embodiments, the projection area of ​​the supply pipe mounting hole onto the partition plate may be configured in other shapes, such as a reflective mixing chamber recessed toward the main body discharge end with an opening facing the supply pipe mounting hole.

[0050] 3 and 4, the uniform refrigerant distributor in this embodiment further includes a liquid supply pipe 4 welded into the liquid supply pipe mounting hole 104, and the axial length L from the end face of the discharge end of the liquid supply pipe 4 to the surface of the partition plate 2 at the upstream end of the partition plate hole 21 is set to satisfy the relationship 3.5 mm≦L≦11.5 mm. Specifically, the liquid supply pipe mounting hole 104 has a straight mounting hole portion 106 extending to the outside of the main body, and the liquid supply pipe 4 has a connection portion 41 welded to the straight mounting hole portion 106, and the connection portion 41 is a straight portion whose terminal end face is the end face of the liquid supply pipe's discharge end. This configuration, provided that the mounting strength of the liquid supply pipe 4 meets the requirements of the cooling system, prevents the discharge end of the liquid supply pipe 4 from protruding too far into the first chamber 1031, which will affect the available refrigerant mixing volume in the first chamber 1031 and the flow resistance of the refrigerant entering the partition plate holes 21. Furthermore, when the refrigerant enters the first chamber 1031, volume expansion inevitably occurs, reducing the refrigerant flow rate. Therefore, if the axial length L is too long, the kinetic energy of the impact on the partition plate 2 will decrease, reducing the primary reflective mixing effect of the partition plate 2 and the secondary reflective mixing effect on the inner wall of the liquid supply end 101, and further affecting the degree of refrigerant mixing and atomization.

[0051] Preferably, the axial length L from the end face of the discharge end of the liquid supply 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, or 10 mm, but the present invention is not limited to this. In other embodiments, the axial length L may be another value within the range of 3.5 mm≦L≦11.5 mm.

[0052] In this embodiment, the liquid supply pipe 4 is welded to the liquid supply pipe mounting hole 104. The present invention is not limited to any particular method for connecting the liquid supply pipe. In other embodiments, the liquid supply pipe may be integrally formed with the main body 1 at the liquid supply pipe mounting hole 104.

[0053] In the refrigerant uniform distributor of this embodiment, the uniformly dispersed flow output from the partition plate holes 21 collides with the corresponding branch pipe holes 105 under the action of inertia force. Some refrigerant still collides with the inner bottom wall of the main body discharge end 102 and flows back along the circumferential wall of the main body 1, inevitably generating a vortex region near the circumferential wall of the branch pipe hole 105 closest to the main body 1. The existence of the vortex region pushes the refrigerant flow path at the inlet of the branch pipe hole 105 and reduces the mass of the flow entering the branch pipe hole 105, thereby affecting not only the uniformity of refrigerant distribution but also its flow resistance. To reduce the adverse effect of the vortex region near the branch pipe hole 105 on the uniform flow distribution, in this embodiment, the branch pipe hole 105 includes suction flow holes 1051 and connection holes 1052 sequentially distributed along the refrigerant flow direction, and the hole diameter of the suction flow holes 1051 is gradually reduced along the refrigerant flow direction. Assuming that the inner diameter of the connection hole 1052 remains unchanged, gradually reducing the diameter of the suction hole 1051 will inevitably increase the diameter at the inlet of the suction hole (i.e., increase the refrigerant flow path at the inlet), allowing the refrigerant to better enter the suction hole 1051. In addition, increasing the diameter at the inlet of the suction hole 1051 reduces the area of ​​the refrigerant reflection by the inner bottom wall of the main body drain end 102, and further reduces the range of the vortex region, weakening the extrusion into the refrigerant flow path, further improving the uniformity of the divided flow and reducing the divided flow resistance.

[0054] In this embodiment, the refrigerant distributor further includes a branch pipe 3 inserted into the branch pipe connection hole 1052. Due to the thickness of the branch pipe 3, a step is formed at the front end of the branch pipe 3. When the refrigerant collides with this step, a vortex is generated, hindering the flow of the refrigerant. To solve this problem, as shown in FIGS. 4 and 5 , in this embodiment, the diameter of the downstream end of the suction flow hole 1051 is set smaller than the diameter of the connection hole 1052. A stopper 1053 protruding toward the center of the branch pipe 105 is formed at the connection between the suction flow hole 1051 and the connection hole 1052. The inner diameter D3 of the stopper 1053 is approximately equal to the inner diameter D4 of the branch pipe 3. The stopper 1053 is configured to abut against the insertion end face of the branch pipe 4 to provide a stopper for the branch pipe 3 during insertion. The inner diameter D3 of the stopper portion 1053 is approximately equal to the inner diameter D4 of the branch pipe, which eliminates a step on the front end face of the branch pipe 3. This allows the refrigerant that flows into the suction flow hole 1051 to smoothly enter the branch pipe 3, further reducing the flow resistance of the refrigerant.

[0055] In this embodiment, the inner wall generatrix of the suction hole 1051 is an inclined straight line, and there is an angle β between the inner wall generatrix of the suction hole 1051 (in this case, the inner wall generatrix of the suction hole overlaps with a tangent to the inner wall generatrix) and the center line of the branch pipe 105, and the angle β is 10°≦β≦65°. Preferably, as shown in FIG. 5 , the angle β may be set to 45°, but the present invention is not limited thereto. In other embodiments, the angle β may be other angle values ​​between 10° and 65°, such as 15°, 20°, 25°, 30°, 40°, 45°, 50°, 55°, and 60°. In this embodiment, the inner wall generatrix of the suction hole is described as an inclined straight line, but the present invention is not limited thereto. In another embodiment, the suction flow hole may be a burring hole having an arc-shaped inner wall generatrix, and the angle β formed between the tangent to the inner wall generatrix of the suction flow hole and the center line of the branch pipe hole satisfies 10°≦β≦65°. As shown in FIGS. 2 and 8 , in this embodiment, the main body 1 includes a cylindrical body 11, an end cap 12, and a liner 13. The cylindrical body 11 is integrally molded and has an open end. A plurality of branch holes 111 are formed in the bottom of the cylindrical body 11. The liner 13 is tightly welded to the inner bottom surface of the cylindrical body 11, and the liner 13 and the cylindrical body 11 together form the end wall of the discharge end of the main body 1. A plurality of liner holes 131 are formed in the liner 13, each coaxial with the plurality of branch holes 111. The liner holes 131 and the corresponding branch holes 111 form the branch pipe hole 105. Specifically, a suction flow hole 1051 is formed in a region of the liner hole 131 close to the second chamber 1032, and the region close to the bottom of the cylindrical body 11 and the branch hole 111 form a connecting hole 1052. The end cap 12 has an arc-shaped curved surface, one end of which is welded to the open end of the cylindrical body 11, and the other end of which has a liquid supply pipe attachment hole 104 formed therein.

[0056] In this embodiment, the suction holes and the connection holes are integrally molded in the end wall of the main body discharge end, but the present invention is not limited to this. In another embodiment, as shown in Figures 9 and 10, the refrigerant uniform distributor may include a baffle plate 5 tightly welded to the inner end wall of the main body discharge end 102, and the baffle plate 5 has a plurality of baffle plate holes that are branch pipe suction holes 1051. Figure 10A is a structural schematic diagram of a baffle plate according to another embodiment of the present invention, and in this configuration, the depth of the baffle plate holes is formed according to the thickness of the baffle plate.

[0057] In this embodiment, the inner wall of end cap 12 extends at an incline toward main body discharge end 102, and the inner wall generatrix is ​​an arc-shaped curved surface, but the present invention is not limited to this. In another embodiment, as shown in Fig. 11, the inner wall generatrix of main body supply end 101 may be an inclined straight line, and the inner wall contour of end cap 12 may be a truncated cone.

[0058] FIG. 12 shows a schematic diagram of a refrigerant distributor according to another embodiment of the present invention. In this configuration, a main body 1' includes an end cap 12' and a liner 13'. One end of the end cap 12' is formed with a feed pipe mounting hole 104 and has an arc-shaped curved surface. A liner 13' is embedded in the other end of the end cap 12', and the liner 13' has multiple liner holes, which are branch pipe holes 105. Similarly, in other embodiments, the inner wall generatrix of the end cap 12' in FIG. 12 may be configured as an inclined straight line. Although FIGS. 1, 9, 11, and 12 all show a single liner, this is not a limitation of the present invention. In other embodiments, multiple liners may be provided, and the multiple liners may be stacked and welded to the inner or outer wall of the cylinder or fitted into the open ends of the end caps.

[0059] Accordingly, this embodiment further provides a heat exchanger assembly including the uniform refrigerant distributor according to this embodiment. Specifically, the heat exchanger assembly is a condenser or an evaporator.

[0060] In another aspect, the present embodiments further provide a cooling device including a condenser or an evaporator.

[0061] Example 2 This embodiment is basically the same as embodiment 1 and its variations, but differs in that, as shown in Figures 13 and 14, a recess 201 is formed in the area of ​​the partition plate 2 facing the liquid supply pipe mounting hole 104, with its opening facing the liquid supply pipe mounting hole 104 (not shown in Figures 13 and 14 because the liquid supply pipe 4 is mounted therein), and the partition plate 2 at the recess 201 protrudes and extends toward the main body liquid discharge end 102.

[0062] Compared to Example 1, in this example, the configuration of recess 201 in partition plate 2 provides a sufficient mixing space for the refrigerant after high-speed collision and reflection, promoting sufficient mixing of the two-phase refrigerant. In addition, when the mass flow rate of the input refrigerant is large, the configuration of recess 201 effectively reduces the influence of the reflecting force on the input refrigerant at feed pipe mounting hole 104, thereby preventing refrigerant from refluxing in the feed pipe due to an excessively large reflecting force. The partition plate 2 in the recess 201 protrudes and extends toward the main body discharge end 102. This configuration reduces the volume inside the second chamber 1032, thereby preventing the uniform refrigerant output from the partition plate hole 21 from re-expanding or slowing down inside the second chamber 1032, resulting in gas-liquid two-phase segregation. Furthermore, the outer wall of the recess 201 and the second chamber 1032 surround an annular flow dividing tank, and the uniform refrigerant output from the partition plate hole 21 is uniformly distributed along the annular flow dividing tank into multiple branch pipe holes 105 distributed annularly at the bottom of the main body 1, thereby achieving symmetrical refrigerant division.

[0063] In this embodiment, the lumen shape of the depression 201 is cylindrical, and the outer bottom wall of the depression 201 abuts against the inner bottom wall of the main body drainage end 102, but the present invention is not limited thereto. In other embodiments, the lumen shape of the depression may be one or a combination of a cone (shown in FIG. 15A), a truncated cone (shown in FIG. 15B), a prism, a truncated pyramid, a pyramid, or a partial sphere (shown in FIG. 15C), for example, a combination of a cylinder and a partial sphere (shown in FIG. 15D), a combination of a truncated cone and a partial sphere, a combination of a prism and a partial sphere, or the like.

[0064] Example 3 This embodiment is basically the same as the first embodiment and its modifications, but differs in the structure of the liquid supply pipe mounting hole 104 and the liquid supply pipe 4.

[0065] 16 and 16A, in this embodiment, the liquid supply pipe mounting hole 104 is a straight through-hole without a mounting hole. In this embodiment, the liquid supply pipe 4 has a Venturi tube structure, and the connecting portion 41' has a diverging structure with an outer wall generatrix exhibiting an arc-shaped curve. The liquid supply pipe 4 enters the first chamber 1031 through the liquid supply pipe mounting hole 104, and the outer wall of the connecting portion 41' is tightly welded to the inner wall of the liquid supply end 102 of the main body.

[0066] The definition is as follows: An extension of the inner wall busbar of the straight throat portion 40' in the Venturi tube section intersects with an imaginary extension plane of the feed pipe attachment hole 104 on the inner wall of the feed end 101 at position K, and the cross section of the feed pipe 4 passing through position K is the end face of the discharge end of the feed pipe 4. Note that this depends on the connection method of the feed pipe 4; in this embodiment, the feed pipe 4 is welded to the inner wall of the feed end 101 of the main body via a diverging connection portion 41'. Therefore, the definition is as follows: As shown in FIG. 16A , an extension of the outer wall busbar of the straight throat portion 40' in the Venturi tube section intersects with an imaginary extension plane of the feed pipe attachment hole 104 on the inner wall of the feed end 101 at position K', and the cross section center of the feed pipe 4 passing through position K' is defined as the center O of the downstream end of the feed pipe attachment hole.

[0067] In this embodiment, the axial length L from the end face of the discharge end of the liquid supply pipe 4 to the surface of the partition plate 2 at the upstream end of the partition plate hole 21 satisfies the range 3.5 mm≦L≦11.5 mm. Similarly, the angle α between the radial direction of the partition plate 2 and a line connecting the projection position A of the outer edge of the downstream end of the partition plate hole 21 onto the inner wall of the liquid supply end 102 along the axial direction of the main body and the downstream end center O of the liquid supply pipe mounting hole satisfies the range 8°≦α≦17°.

[0068] However, the present invention is not limited to the specific structure of the liquid supply tube attachment hole. In another embodiment, when the liquid supply tube attachment hole has a straight attachment hole portion, the connection portion of the liquid supply tube may be configured to include a straight portion and a divergent portion located downstream of the straight portion and tightly welded to the inner wall of the liquid supply end of the body.

[0069] In this embodiment, the number of branch pipes 3 is 10, but the present invention is not limited to this number.

[0070] Example 4 This embodiment is basically the same as the first embodiment and its modifications, but differs in the structure of the branch pipe 3.

[0071] 17 , 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 of the downstream end of the first pipe section 31, and the difference Δd between the inner diameter d11 of the downstream end of the first pipe section 31 and the inner diameter d12 of the downstream end of the second pipe section 32 is in the range of 0.1 mm≦Δd≦3.5 mm. The first pipe section 31 is formed with a reflecting section 311 that bends and extends to one side of the center line of the branch pipe hole 105, and the axis of the upstream end of the reflecting section 311 intersects the axis of the downstream end of the reflecting section at an angle θ that is 90°≦θ≦175°. The reflecting section 311 causes the axis of the second pipe section 32 to intersect with the center line of the branch pipe hole 105.

[0072] The first pipe section 31, which has a larger inner diameter, increases the refrigerant flow rate distributed to each branch pipe 3 and reduces refrigerant distribution resistance. Meanwhile, the second pipe section 32, which has a smaller inner diameter, improves the refrigerant flow velocity within the branch pipes to meet the performance requirements of the rear-end heat exchanger assembly. Furthermore, the inner diameter difference Δd accurately controls the degree to which the second pipe section 32 accelerates the refrigerant, thereby preventing excessive refrigerant pressure loss due to excessive acceleration. Due to the configuration of the reflecting section 311, the second pipe section 32 is not coaxial with the centerline of the branch pipe 105. When downstream pressure waves vibrate upstream, the reflecting section 311 reflects and absorbs a portion of the pressure wave, redirecting the propagation direction of the residual pressure wave and quickly attenuating it. This effectively prevents the downstream pressure wave from affecting the upstream branch pipe 105, further improving distribution performance.

[0073] In this embodiment, the branch pipe 3 further includes a third pipe section 33 welded to the first pipe section 31, where the second pipe section 32 is located. Specifically, as shown in FIG. 17 , the third pipe section 33 has a sleeve connection section 331 fitted onto the end of the first pipe section 31 and having a flared structure, and the second pipe section 32, whose inner diameter is tapered, is formed downstream of the sleeve connection section 331, but the present invention is not limited thereto. In other embodiments, the end of the first pipe section 31 may be configured to be fitted onto the sleeve connection section 331 of the third pipe section 33 and welded thereto. In this case, as shown in FIG. 18A , the second pipe section has a structure in which the inner diameter is tapered downstream of the sleeve connection section 331.

[0074] 18B and 18C are schematic diagrams of the structure of a branch pipe according to another embodiment of the present invention. In FIG. 18B, the first pipe section 31, the second pipe section 32, and the third pipe section 33 are integrally molded. In FIG. 18, the first pipe section 31 and the second pipe section 32 are integrally molded, and the third pipe section 33 is welded to the end of the second pipe section. In other embodiments, the second pipe section may be directly formed at the sleeve connection point between the first pipe section and the second pipe section. Furthermore, multiple second pipe sections may be provided at the downstream end of the first pipe section. The third pipe section 33 may be provided in a straight pipe or a bent pipe depending on the actual application.

[0075] Example 5 This embodiment is basically the same as the first embodiment and its modifications, but differs in that the branch pipe 3 has a different structure.

[0076] As shown in Figure 19, in this embodiment, each branch pipe 3 includes a straight connection section 31', a jet section 32' located downstream of the straight connection section 31' and having an inner diameter smaller than the inner diameter d11' of the straight connection section main body 311', and a branch section 33' located downstream of the jet section 32' and having a constant diameter section 331' whose inner diameter is approximately the same as the inner diameter d11' of the straight connection section main body. The difference Δd' between the inner diameter d11' of the straight connection section main body and the minimum inner diameter d12' of the jet section 32' is 0.1 mm ≤ Δd' ≤ 3.5 mm. The straight connection section main body 311' is a pipe section in the straight connection section 31' where both the inner diameter and outer diameter are essentially the same.

[0077] To meet the performance requirements of the rear-end heat exchanger assembly, the uniform refrigerant distributor of this embodiment adds a jet section 32' to each branch pipe 3 to increase the refrigerant flow velocity within the branch pipe 3. Furthermore, the inner diameter difference Δd' accurately controls the degree to which the jet section 32' accelerates the refrigerant, thereby preventing excessive refrigerant pressure loss due to excessive acceleration. Furthermore, to reduce the flow resistance of the refrigerant within the branch pipe 3 and achieve a good balance between refrigerant flow velocity and pressure loss, the inner diameter d13' of the constant diameter section 331' in the branch section 33' is set to be approximately equal to the inner diameter d11' of the straight connection body.

[0078] In this embodiment, the jet portion 32' is a constriction portion integrally molded upstream of the branch portion 33' and is welded to the straight connecting portion 31' after being integrally molded, but the present invention is not limited to this. In another embodiment, as shown in Figure 20A, the jet portion 32' may be integrally molded downstream of the straight connecting portion 31' and welded to the branch portion 33'. Alternatively, as shown in Figure 20B, the straight connecting portion 31', the jet portion 32', and the branch portion 33' may be integrally molded.

[0079] Alternatively, the jet section 32' may be a plate with jet holes disposed at the sleeve connection point between the straight connecting section 31' and the branching section 33'. Specifically, as shown in Fig. 20C, the upstream end of the branching section 33' is flared and then sleeve-connected to the downstream end of the straight connecting section 31', and the jet section 32' is disposed in the flare of the branching section 33'. Similarly, when the downstream end of the straight connecting section 31' is flared and externally connected to the upstream end of the branching section 33', the jet section 32' may be disposed in the flare at the downstream end of the straight connecting section 31', as shown in Fig. 20D.

[0080] Alternatively, as shown in Fig. 20E, the jet section 32' is configured as a straight pipe section whose ends are sleeve-connected to the straight connecting section 31' and branching section 33', respectively. In Figs. 19, 20A and 20E, the jet section 32' has a length L32 over which the inner diameter remains substantially constant, but the present invention is not limited thereto.

[0081] The present invention does not impose any limitations on the configuration of the jet part, and any other jet part structure that can achieve an inner diameter smaller than that of the straight connection part body is within the scope of protection of the present invention.

[0082] Example 6 This embodiment is basically the same as embodiment 2 and its modifications, but differs in that, as shown in FIG. 21 , the uniform refrigerant distributor of this embodiment further includes a flow path forming member 6 disposed in the second chamber 1032 and positioned on the inner periphery of the plurality of branch pipe holes 105, the flow path forming member 6 extends from the inner bottom wall of the main body discharge end 102 toward the partition plate 2, and its cross section remains almost unchanged or gradually becomes smaller in the extending direction, and an annular flow dividing tank is formed between the flow path forming member 6 and the inner wall of the second chamber 1032.

[0083] As in Example 2, in this example, the flow path forming member 6 forms an annular flow path within the second chamber 1032, achieving uniform distribution of the refrigerant, and the flow path forming member 6 is used to reduce the volume of the second chamber 1032, thereby avoiding the problem of gas-liquid two-phase segregation due to over-expansion of the refrigerant. Specifically, as shown in Figure 21, the flow path forming member 6 is a hollow spacer whose cross section remains almost constant in its extension direction, and the spacer is fitted onto the outside of the recess 201, with its upper end abutting against the partition plate regions on the inner peripheries of the multiple partition plate holes 21. In other words, when projected along the axial direction of the main body 1, the spacer, which is the flow path forming member 6, is located between the recess 201 and the multiple partition plate holes 21. The spacer and the inner wall of the second chamber 1032 enclose an annular flow passage connecting the partition plate holes 21 and the branch pipe holes 105. This reduces the cross-section of the flow passage between the partition plate holes 21 and the branch pipe holes 105 in the radial direction, controlling the volume change rate and flow velocity of the refrigerant within the second chamber 1032 and ensuring that the refrigerant flows in a dispersed state after mixing and is uniformly distributed among the branch pipe holes 105. Furthermore, by controlling the radial distance L1 from the outer periphery of the bottom of the flow passage-forming member 6 to the inner wall of the second chamber 1032, the volume ratio between the annular flow passage and the first chamber 1031 can be accurately controlled, thereby enabling accurate control of the refrigerant flow velocity within the annular flow passage. Preferably, L1 is set to satisfy the relationship L1≦28 mm, e.g., 11 mm, 15 mm, 18 mm, 20 mm, 23 mm, or 25 mm.

[0084] In the uniform refrigerant distributor of this embodiment, as the refrigerant enters the second chamber 1032 through the partition plate holes 21 and is distributed to the branch pipe holes 105, some of the refrigerant inevitably collides with the inner bottom wall of the main discharge end 102 and flows back along the inner circumferential wall of the second chamber 1032 and the outer wall of the flow path forming member 6. The refrigerant backflow generates a vortex region near the branch pipe holes 105, which pushes the refrigerant flow path at the inlet of the branch pipe holes 105, obstructing the inflow of refrigerant and affecting the performance of the distributor. In this embodiment, the radial spacing distance L1 reduces the refrigerant reflection area by the inner bottom wall of the main discharge end 102 and further reduces the range of action of the vortex region, weakening the pushing of the refrigerant into the refrigerant distribution flow path, improving the uniformity of refrigerant distribution and reducing distribution resistance.

[0085] As in Example 1, in this example, the partition plate holes 21 are equally spaced in one annular row on the partition plate 2, the number of which is the same as the number of branch pipe holes 105, and each is approximately coaxial with the corresponding branch pipe hole 105, but the present invention is not limited to this. In another example, as shown in Figure 22, eight partition plate holes 21 are distributed in two annular rows on the partition plate 2, with four partition plate holes 21 equally spaced in each annular row, and in this case, there are also four branch pipe holes 105 at the main body discharge end 102.

[0086] In this embodiment, an example in which a recess 201 is formed in the partition plate 2 will be described, but the present invention is not limited to this. In other embodiments, as shown in Fig. 23, the partition plate 2 may have a plate-like structure in which both side surfaces are nearly flat, or as shown in Fig. 24, a recess may be formed in the side of the partition plate 2 facing the liquid supply pipe mounting hole (i.e., the upstream surface) and the other side surface (i.e., the downstream surface) may remain nearly flat.

[0087] Example 7 This embodiment is basically the same as the sixth embodiment and its modifications, but differs in the structure of the partition plate 2 and the structure of the flow path forming member 6.

[0088] As shown in Figure 25, in this embodiment, the partition plate 2 has a plate-like structure with both side surfaces nearly flat. The flow path forming member 6 has a tapered cross section that gradually decreases in its extension direction. The tapered flow path forming member 6 and the inner peripheral wall of the second chamber 1032 enclose an annular flow path with a gradually decreasing flow path cross section. The inclined peripheral wall of the flow path forming member 6 forms the inner wall of the annular flow path and uniformly distributes the high-speed refrigerant entering the second chamber 1032 into the multiple branch pipe holes 105. Furthermore, the gradually decreasing flow path cross section increases the refrigerant flow velocity, allowing it to quickly enter the branch pipe holes 105 and preventing gas-liquid two-phase separation of the refrigerant during the distribution process after mixing.

[0089] Specifically, as shown in FIG. 25 , the vertical distance H2 from the extending tip of the flow path forming member 6 to the downstream surface of the partition plate 2 is set to satisfy 1 mm≦H2≦2H0 / 3, where H0 is the height of the second chamber 1032. The determined inner diameter of the main body 1, the height H0 of the second chamber, and the vertical distance H2 enable accurate control of the internal volume of the second chamber 1032. In this embodiment, the flow path forming member 6 is nearly conical, and in a longitudinal cross section of the flow path forming member 6 passing through the axis of the main body 1, the angle γ formed by the extensions of the generatrix on both sides of the flow path forming member 6 satisfies 20°≦γ≦115°. The angle γ limits the inclination of the peripheral wall of the flow path forming member 6, i.e., enables accurate control of the rate of change of the annular flow path cross section, allowing the divided refrigerant to be quickly distributed into the branch pipe holes 105. Preferably, the angle γ is set to 45°, 50°, or 60°, but the present invention is not limited thereto.

[0090] Furthermore, in order to allow the refrigerant to smoothly enter the annular flow path, the extending tip of the flow path forming member 6 is configured to present an arcuate curved surface with a curvature radius R satisfying 0.5 mm≦R≦5 mm, but the present invention is not limited to this. In other embodiments, the flow path forming member 6 may be configured to have a truncated cone structure with an extending tip presenting a flat surface.

[0091] In this embodiment, both side surfaces of the partition plate 2 are plate-like structures that are nearly flat, and the cross section of the flow path forming member 6 is tapered in the extension direction, but the present invention is not limited to this. In other embodiments, when the partition plate 2 has a recess in which the projected area of ​​the liquid supply pipe mounting hole on the partition plate protrudes toward the launch pipe hole 105 (e.g., the partition plate structures in Examples 2 and 6) or a protrusion toward the liquid supply pipe mounting hole 104 (i.e., the partition plate structure in Example 3), the flow path forming member 6 may be configured as a cone or truncated cone. In this case, the vertical distance H2 is the vertical distance from the extending tip of the flow path forming member 6 to the downstream surface of the protrusion on the partition plate, and the height H0 of the second chamber is the vertical distance from the inner bottom wall of the main body discharge end 102 to the downstream surface of the protrusion on the partition plate.

[0092] Example 8 This embodiment is basically the same as the first embodiment and its modifications, but differs in the structure of the liquid supply pipe 4.

[0093] As shown in Figure 26, in this embodiment, a Venturi tube section 42 is formed in the liquid supply pipe 4, and a connecting section 41 is further formed at the downstream end of the Venturi tube section 42. The connecting section 41 is a straight pipe section that is welded and connected to the straight mounting hole section 106 in the liquid supply pipe mounting hole, but the present invention is not limited to this in any way.

[0094] In this embodiment, the liquid supply pipe 4 is a circular pipe member with a nearly uniform wall thickness, and the venturi tube section 42 of the liquid supply pipe 4 is formed by processing and shaping the circular pipe material using a flaring and drawing process. This configuration precisely controls the rate of change in the inner diameter of the tapered section 421 and the divergent section 423 and the transition structure between adjacent pipe sections, forming a smooth line within the venturi tube section 42, promoting gas-liquid two-phase mixing and reducing refrigerant pressure loss. Furthermore, the venturi structure formed from the pipe member is formed using a scrap-free processing method that does not require cutting. This processing method has advantages such as high processing precision, excellent product consistency, high processing efficiency, and few consumables.

[0095] 27 is a structural schematic diagram of a refrigerant uniform distributor according to another embodiment of the present invention. In this configuration, the liquid supply pipe 4 is formed with two Venturi tube sections connected in series, namely, an upstream Venturi tube section 42' and a downstream Venturi tube section 42. The two Venturi tube sections connected in series improve the flow pattern of the refrigerant at the inlet, step by step, enhancing the uniformity of refrigerant mixing at the inlet and improving distributor performance. Preferably, the inner diameter D42 of the straight throat section of the downstream Venturi tube section 42 is set smaller than the inner diameter D42' of the straight throat section of the upstream Venturi tube section 42'. This setting further accelerates the refrigerant at the straight throat section 422 of the downstream Venturi tube section 42, improving the kinetic energy of the refrigerant entering the main body 1, enhancing the gas-liquid two-phase mixing effect, and providing the refrigerant with a larger inertia force to maintain the mixed flow pattern.

[0096] However, the series connection of the two Venturi tube sections 42, 42' increases the length of the liquid supply pipe 4, making it difficult to apply to air conditioners with limited installation space. For this reason, the uniform refrigerant distributor shown in FIG. 28 further provides a liquid supply pipe structure that can achieve two-stage mixing and is short in length. In this configuration, the liquid supply pipe 4 includes a Venturi tube section 42 and a variable diameter hole plate 43 located downstream of the Venturi tube section 42. Specifically, a connecting section 41, which is a straight pipe section, is formed downstream of the Venturi tube section 42, and the variable diameter hole plate 43 is provided within the connecting section 41. As shown in FIG. 29, the variable diameter hole plate 43 has variable diameter holes 430, which include a tapered hole section 431 whose hole diameter gradually decreases along the refrigerant flow direction, and a throat hole section 432 located downstream of the tapered hole section 431 and whose hole diameter remains almost constant. The uniform refrigerant distributor in FIG. 28 uses a thin variable diameter hole plate 43 instead of the long downstream Venturi tube section in FIG. 27 to achieve two-stage mixing and shorten the length of the liquid supply pipe 4, making it applicable to air conditioning devices with different installation spaces, including air conditioning devices with limited installation spaces (for example, 1HP or 1.5HP indoor units of home air conditioners).

[0097] As described above, the uniform refrigerant distributor of the present invention divides the storage chamber in the main body into a first chamber and a second chamber using a partition plate, thereby reducing the volume of each chamber. The first chamber provides an adequate expansion space for the gas-liquid two-phase refrigerant input from the supply pipe, allowing the two-phase refrigerant to be thoroughly mixed into a high-speed dispersed flow pattern. This effectively solves the problem of resegregation of the mixed refrigerant due to an oversized main body chamber, which is a problem of conventional distributors. Furthermore, the inner wall of the supply end extends at an angle toward the discharge end of the main body to form a secondary reflection surface. This secondary reflection of the dispersed refrigerant reflected and mixed by the partition plate into the multiple partition holes achieves uniform refrigerant distribution and further improves the degree of mixing of the two-phase refrigerant. The angle α relative to the projection position A can be adjusted to control the secondary reflection stroke from the partition plate to the inner wall of the supply end, ensuring that the refrigerant reflected by the partition plate can re-enter the inner wall of the supply end for secondary reflection. The spatial position of the partition plate holes is determined by the axial distance H1 relative to the projection position A, and the partition plate holes are positioned on the injection path of the secondary reflection. This configuration also effectively prevents the inner wall of the main body from interfering with the flow of the refrigerant, allowing the refrigerant to be distributed uniformly among the multiple partition plate holes.

[0098] The partition holes are located around the periphery of the projection of the liquid supply pipe hole onto the partition, so that the projection of the liquid supply pipe hole onto the partition can block the incoming refrigerant and reflect it back into the first chamber, further promoting the mixing of the two-phase refrigerant. The offset distribution of the partition holes and the liquid supply holes effectively prevents the refrigerant from reaching the second mixing chamber too early for mixing, further improving the mixing uniformity of the two-phase refrigerant.

[0099] Although the present invention has been disclosed as above by means of preferred embodiments, it is not used to limit the present invention, and any person skilled in the art can make slight modifications and refinements without departing from the spirit and scope of the present invention, so the protection scope of the present invention should be in accordance with the protection scope set forth in the claims.

Claims

1. A refrigerant uniform distributor, a main body including a liquid supply end, a liquid discharge end, and a storage chamber communicating the liquid supply end and the liquid discharge end, wherein a liquid supply pipe attachment hole is formed in the liquid supply end of the main body, the inner wall of the liquid supply end extends at an angle to the liquid discharge end of the main body with the inner wall generatrix presenting an arc line or an inclined straight line, and a plurality of branch pipe holes for separating liquid are formed in the liquid discharge end of the main body; a partition plate provided in the storage chamber of the main body to separate the storage chamber into a first chamber and a second chamber, the partition plate having a plurality of partition plate holes formed therein that are distributed annularly around the center line of the main body and that allow the first chamber and the second chamber to communicate with each other, the plurality of partition plate holes corresponding one-to-one to the plurality of branch pipe holes, and the partition plate configured to be located on the outer periphery of the liquid supply pipe mounting hole when projected along the axial direction of the main body; a line connecting a projection position A of the outer edge of the downstream end of the partition plate hole onto the inner wall of the liquid supply end along the axial direction of the main body and a center O of the downstream end of the liquid supply pipe mounting hole forms an angle α with respect to the radial direction of the partition plate, and the angle α is 8°≦α≦17°; an axial distance H1 from the surface of the partition plate at the upstream end of the partition plate hole to said projection position A satisfies 1 mm≦H1≦5 mm; and the outer edge of the downstream end of the partition plate hole is the edge of the downstream end of the partition plate hole at a point farthest from the center line of the main body.

2. 2. The uniform refrigerant distributor according to claim 1, wherein the plurality of partition plate holes are distributed annularly at equal intervals on the partition plate, the number of the partition plate holes is the same as the number of the branch pipe holes, each of the partition plate holes is approximately coaxial with the opposite branch pipe hole, and a ratio of a diameter D1 of a downstream end of the partition plate hole to an outer diameter D2 of a branch pipe inserted into the branch pipe hole is 0.8 to 1.

2.

3. 2. The uniform refrigerant distributor according to claim 1, further comprising a plurality of branch pipes welded to the respective branch pipes, each branch pipe comprising a first pipe section and a second pipe section located downstream of the first pipe section, the second pipe section having an inner diameter smaller than that of a downstream end of the first pipe section, a difference Δd between an inner diameter d11 of the downstream end of the first pipe section and an inner diameter d12 of the downstream end of the second pipe section being in a range of 0.1 mm≦Δd≦3.5 mm, the first pipe section having a reflecting section bent and extending to one side of a center line of the branch pipe section, the axis of the upstream end of the reflecting section intersecting with the axis of the downstream end of the reflecting section at an angle θ (90°≦θ≦175°), and the reflecting section allowing the axis of the second pipe section to intersect with the center line of the branch pipe section.

4. 2. The uniform refrigerant distributor according to claim 1, further comprising a plurality of branch pipes welded to the respective branch pipe holes, each branch pipe including a straight connection portion, a jet portion located downstream of the straight connection portion and having an inner diameter smaller than that of the straight connection portion body, and a branch portion located downstream of the jet portion, wherein the branch portion has a constant diameter portion whose inner diameter is approximately the same as that of the straight connection portion body, and a difference Δd' between the inner diameter d11' of the straight connection portion body and the minimum inner diameter d12' of the jet portion satisfies 0.1 mm≦Δd'≦3.5 mm.

5. The partition plate holes are through holes having substantially the same hole diameter, Alternatively, the hole diameter gradually decreases along the flow direction of the refrigerant, and the inner wall generatrix of the partition plate hole is linear or arc-shaped, 2. The refrigerant uniform distributor according to claim 1, wherein the partition plate holes are arc-shaped bubble holes whose hole walls protrude in an arc shape to one or both sides of the partition plate.

6. The partition plate has a plate structure that is nearly flat on both sides, 2. The refrigerant uniform distributor according to claim 1, wherein the partition plate has a region facing the liquid supply pipe mounting hole that is recessed toward the liquid discharge end of the main body, forming a reflective mixing chamber with an opening facing the liquid supply pipe mounting hole.

7. 2. The uniform refrigerant distributor according to claim 1, further comprising a liquid supply pipe welded to the liquid supply pipe mounting hole, wherein an axial length L from an end face of the discharge end of the liquid supply pipe to a surface of the partition plate at an upstream end of the partition plate hole satisfies 3.5 mm≦L≦11.5 mm.

8. The liquid supply pipe has a connecting portion formed thereon that is welded to the liquid supply pipe mounting hole, and the connecting portion is a straight portion; 8. The refrigerant uniform distributor according to claim 7, wherein the connecting part has an outer wall busbar with a diverging structure, the busbar being curved in an arc shape and projecting into the first chamber through the liquid supply pipe mounting hole, and the outer wall is tightly welded to the inner wall of the liquid supply end of the main body.

9. the liquid supply pipe is a circular pipe member having a substantially uniform wall thickness, connected to the liquid supply pipe mounting hole, and including at least one Venturi tube portion; 8. The refrigerant uniform distributor according to claim 7, wherein each Venturi tube section includes, in order along the flow direction of the refrigerant, a tapered section whose inner diameter gradually decreases, a straight throat section whose inner diameter is approximately the same, and a divergent section whose inner diameter gradually increases.

10. 10. The refrigerant uniform distributor according to claim 9, wherein the liquid supply pipe is formed with two Venturi tube sections, namely, an upstream Venturi tube section and a downstream Venturi tube section, which are connected in series, and the inner diameter of the straight throat section of the downstream Venturi tube section is equal to or smaller than the inner diameter of the straight throat section of the upstream Venturi tube section.

11. 10. The refrigerant uniform distributor according to claim 9, wherein the liquid supply pipe further includes a variable diameter hole plate provided downstream of the Venturi tube portion, the variable diameter hole plate having variable diameter holes, the variable diameter holes including tapered hole portions whose hole diameters gradually decrease in a flow direction of the refrigerant, and throat hole portions located downstream of the tapered hole portions and whose hole diameters are substantially constant.

12. 2. The refrigerant uniform distributor according to claim 1, wherein the branch pipe holes include suction holes and connection holes sequentially distributed along the refrigerant flow direction, the suction holes have a diameter that gradually decreases along the refrigerant flow direction, and the inner wall generatrix thereof is linear or arc-shaped.

13. 13. The refrigerant uniform distributor according to claim 12, wherein an angle β exists between a tangent to an inner wall generatrix of the suction flow hole portion and a center line of the branch pipe hole, and the angle β satisfies 10°≦β≦65°.

14. The diameter of the downstream end of the suction flow hole is smaller than the diameter of the connection hole, At the connection point between the suction flow hole and the connection hole, 13. The refrigerant uniform distributor according to claim 12, further comprising a stopper portion protruding toward the center of the branch pipe hole and configured to abut against an end face of the branch pipe inserted into the branch pipe hole, the stopper portion having a diameter substantially equal to an inner diameter of the branch pipe to be inserted.

15. The refrigerant uniform distributor includes a baffle plate tightly welded to an inner end wall of the main body discharge end, the baffle plate having a plurality of baffle plate holes which are branch pipe suction flow holes; 13. The refrigerant uniform distributor according to claim 12, wherein the suction flow hole and the connection hole are integrally formed in an end wall of the liquid discharge end of the main body.

16. the refrigerant uniform distributor further includes a flow path forming member disposed in the second chamber and positioned on inner peripheries of the plurality of branch pipe holes; 2. The refrigerant uniform distributor according to claim 1, wherein the flow path forming member is a rotating member that extends from the inner bottom wall of the main body discharge end toward the partition plate and is formed by rotating around the main body axis, the flow path forming member and the inner peripheral wall of the second chamber enclose an annular flow path that connects the partition plate hole and the plurality of branch pipe holes, and the cross section of the flow path forming member remains almost unchanged or gradually becomes smaller in its extending direction.

17. The flow path forming member is 17. The refrigerant uniform distributor according to claim 16, wherein the spacer has a cross section that does not change substantially in its extending direction and an upper end of the spacer abuts against partition plate regions on the inner peripheries of the plurality of partition plate holes.

18. 17. The refrigerant uniform distributor according to claim 16, wherein a cross section of the flow path forming member gradually decreases in an extending direction thereof, and a vertical distance H2 from an extending tip of the flow path forming member to a downstream surface of the partition plate satisfies 1 mm≦H2≦2H0 / 3, where H0 is a height of the second chamber.

19. 17. The refrigerant uniform distributor according to claim 16, wherein a radial distance L1 from an outer periphery of the bottom of the flow path forming member to an inner circumferential wall of the second chamber satisfies L1≦28 mm.

20. 17. The refrigerant uniform distributor according to claim 16, wherein the plurality of partition plate holes are equally spaced and arranged in an annular row on the partition plate, the number of the partition plate holes is the same as the number of the branch pipe holes, and each partition plate hole is approximately coaxial with the corresponding branch pipe hole.

21. 17. The refrigerant uniform distributor according to claim 16, wherein the plurality of partition holes are distributed in the partition plate in the form of a plurality of annular rows, and each annular row has the same number of partition holes distributed at equal intervals.

22. A heat exchanger assembly comprising the refrigerant uniform distributor of claim 1.

23. 23. A cooling device comprising the heat exchanger assembly of claim 22.

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