Heat exchanger

Abstract

A heat exchanger, comprising a distribution flow channel, a main inlet, an auxiliary inlet, distribution holes, and refrigerant flow channels. The distribution holes communicate with the distribution flow channels, the distribution holes connect the refrigerant flow channels with the distribution flow channel, and both the main inlet and the auxiliary inlet communicate with the distribution flow channel. The flow area of the main inlet is greater than the flow area of the auxiliary inlet. A plane perpendicular to the axial direction of the distribution flow channel is defined as an auxiliary projection plane, and the projection of the main inlet on the auxiliary projection plane is farther than the projection of the auxiliary inlet on the auxiliary projection plane from the projection of the distribution holes on the auxiliary projection plane. When the heat exchanger is in operation, the mixing uniformity of the refrigerant can be improved, and the uniformity of refrigerant distribution within the distribution chamber can be improved.

Description

heat exchanger Technical Field

[0001] This application relates to the field of refrigeration technology, and in particular to a refrigerant distribution structure for a heat exchanger. Background Technology

[0002] As shown in Figure 17, the heat exchanger includes a manifold 91, a flat tube 92, and a U-shaped tube 90. The U-shaped tube 90 is disposed in the manifold 91 and includes an inlet end 95 and multiple distribution holes. The refrigerant enters from the inlet end 95, passes through the distribution holes into the inner cavity of the manifold 91, and then enters the flat tube 92 to exchange heat with the outside air.

[0003] The U-shaped tube 90 forms a U-shaped flow path. The refrigerant flows in the U-shaped tube 90 and is distributed through the distribution hole. The U-shaped tube of the related technology is prone to refrigerant accumulation at the bottom of the U-shape, resulting in relatively less refrigerant at the end of the U-shaped tube far from its inlet, thus causing poor uniformity of refrigerant distribution. Summary of the Invention

[0004] This application aims to provide a heat exchanger with high refrigerant distribution uniformity.

[0005] This application provides a heat exchanger having a distribution channel, a main inlet, an auxiliary inlet, a distribution hole, and a refrigerant channel. The distribution hole is connected to the distribution channel, and the distribution hole connects the refrigerant channel and the distribution channel. Both the main inlet and the auxiliary inlet are connected to the distribution channel. The flow area of ​​the main inlet is larger than that of the auxiliary inlet. A surface perpendicular to the axial direction of the distribution channel is defined as an auxiliary projection surface. The projection of the main inlet 61 on the auxiliary projection surface is farther away from the projection of the distribution hole 52 on the auxiliary projection surface than the projection of the auxiliary inlet 62 on the auxiliary projection surface.

[0006] In the heat exchanger of this application, the flow area of ​​the main inlet is larger than that of the auxiliary inlet. The projection of the main inlet 61 on the auxiliary projection surface is farther away from the projection of the distribution hole 52 on the auxiliary projection surface than the projection of the auxiliary inlet 62 on the auxiliary projection surface. When the heat exchanger is working, the refrigerant can enter the heat exchanger from the main inlet and flow to the side near the auxiliary inlet to form a swirling flow, which improves the mixing uniformity of the refrigerant. The auxiliary inlet can supplement the refrigerant distribution at the distribution hole near the inlet, thereby improving the distribution uniformity of the refrigerant in the distribution channel. Attached Figure Description

[0007] Figure 1 is a perspective view of a heat exchanger provided in one embodiment of this application;

[0008] Figure 2 is a perspective view of a dispenser provided in one embodiment of this application;

[0009] Figure 3 is a schematic diagram of the explosion of the distributor in Figure 2;

[0010] Figure 4 is an enlarged schematic diagram of part T1 in Figure 3;

[0011] Figure 5 is an enlarged schematic diagram of part T2 in Figure 3;

[0012] Figure 6 is a schematic projection of the perforated plate in a dispenser provided according to one embodiment of this application;

[0013] Figure 7 is a schematic projection of the distributor in Figure 2;

[0014] Figure 8 is a cross-sectional schematic diagram of the distributor in Figure 2;

[0015] Figure 9 is a cross-sectional view of the distributor in Figure 2 from another angle;

[0016] Figure 10 is a schematic projection of the distribution channel wall and the through hole wall provided in one embodiment of this application in Figure 2;

[0017] Figure 11 is a cross-sectional schematic diagram of a heat exchanger provided in one embodiment of this application;

[0018] Figure 12 is an enlarged schematic diagram of part T3 in Figure 11;

[0019] Figure 13 is a cross-sectional schematic diagram of a heat exchanger provided in one embodiment of this application;

[0020] Figure 14 is a cross-sectional schematic diagram of a heat exchanger provided in one embodiment of this application;

[0021] Figure 15 is an enlarged schematic diagram of the dashed line portion in Figure 1;

[0022] Figure 16 is an exploded schematic diagram of the distribution cylinder of a plate heat exchanger provided in one embodiment of this application;

[0023] Figure 17 shows a heat exchanger in the related technology. Detailed Implementation

[0024] To better understand the technical solution of this application, the technical solution of this application will be described in detail below with reference to the accompanying drawings.

[0025] As shown in Figure 17, in the heat exchanger of the related technology, the refrigerant enters the inner cavity of the U-tube 90 through the port 93 of the U-tube 90, and then enters the refrigerant flow channel through a row of holes 94 on the side wall of the U-tube 90. The refrigerant tends to accumulate at the bottom 95 of the distribution tube, which is far away from the port 93. This results in less refrigerant flowing into the holes 94 near the port and more refrigerant flowing into the holes far away from the port 93, thus the refrigerant distribution uniformity of the heat exchanger is poor.

[0026] As shown in Figures 11 and 12, the heat exchanger 100 in this application has a distribution channel 2, a main inlet 61, an auxiliary inlet 62, a distribution hole 52, and a refrigerant channel 103. The distribution hole 52 is connected to the distribution channel 2 and connects the refrigerant channel 103 with the distribution channel 2. Both the main inlet 61 and the auxiliary inlet 62 are connected to the distribution channel 2. The flow area of ​​the main inlet 61 is larger than that of the auxiliary inlet 62. The surface perpendicular to the axial direction of the distribution channel 2 is defined as the auxiliary projection surface. The projection of the main inlet 61 on the auxiliary projection surface is far away from the projection of the auxiliary inlet 62 on the auxiliary projection surface. The projection of the main inlet 61 onto the auxiliary projection surface is farther away from the projection of the distribution hole 52 onto the auxiliary projection surface than the projection of the auxiliary inlet 62. When the heat exchanger 100 is working, the refrigerant can enter the distribution channel 2 from the main inlet 61, and can also enter the distribution channel 2 from the auxiliary inlet 62, forming a swirling flow with the refrigerant entering from the main inlet 61, thus improving the mixing uniformity of the refrigerant. Furthermore, the auxiliary inlet 62 can supplement the refrigerant distribution at the distribution hole 52 near the inlet, thereby improving the distribution uniformity of the refrigerant within the distribution channel. In one embodiment, the main inlet 61 and the auxiliary inlet 62 can be irregular shapes or circular.

[0027] The positions of the main inlet 61, auxiliary inlet 62, and distribution hole 52 are arranged to make the refrigerant flow principle as shown in Figure 14.

[0028] As shown in Figures 12 and 14, the heat exchanger 100 is a microchannel heat exchanger. Specifically, the heat exchanger 100 includes a manifold 91, at least two flat tubes 92, and fins 99. The fins 99 are located between two adjacent flat tubes 92. The distribution channel 2 is provided in the manifold 91, and the refrigerant channel 103 is provided in the flat tubes 92.

[0029] As shown in Figure 1, the heat exchanger 100 is a plate heat exchanger, comprising multiple plates 101 stacked along the height direction H of the heat exchanger 100. The heat exchanger 100 has inter-plate flow channels, including at least two refrigerant flow channels 103 and a coolant flow channel 102. The distribution channel 2 and the at least two refrigerant flow channels 103 are fluidly isolated from the coolant flow channel 102. Water flows through the coolant flow channel 102.

[0030] Specifically, in one embodiment, as shown in Figures 1 and 10, the direction perpendicular to the axial direction of the distribution channel 2 is defined as the first direction, and the plane parallel to the height direction H of the heat exchanger 100 is defined as the projection plane. The orthographic projection of the wall of the distribution channel 2 onto the projection plane is the third projection P3, the orthographic projection of the wall of the main inlet 61 onto the projection plane is the first projection P1, and the orthographic projection of the wall of the auxiliary inlet 62 onto the projection plane is the second projection P2. The projection plane has a first straight line L, which intersects the inner contour of the third projection P3 at a first point O1 and a second point O2, and intersects the inner contour of the first projection P1 at a third point O3 and a fourth point O4. The inner contour of the second projection P2 intersects at the fifth point O5 and the sixth point O6; along the first straight line L, the third point O3 is closer to the first point O1 relative to the fourth point O4, and the fifth point O5 is closer to the second point O2 relative to the sixth point O6; along the first straight line L, the distance between the first point O1 and the third point O3 is the first distance S1, and the distance between the second point O2 and the fourth point O4 is the second distance S2, and the first distance S1 is less than the second distance S2; along the first straight line L, the distance between the first point O1 and the sixth point O6 is the third distance S3, and the distance between the second point O2 and the fifth point O5 is the fourth distance S4, and the fourth distance S4 is less than the third distance S3.

[0031] The heat exchanger 100 of this application includes a plurality of plates 101 stacked along the height direction of the heat exchanger 100. The heat exchanger 100 has a distribution channel 2, a coolant channel 102, and at least two refrigerant channels 103. The at least two refrigerant channels 103 are all in communication with the distribution channel 2, and both the distribution channel 2 and the refrigerant channels 103 are fluidly isolated from the coolant channel 102. The heat exchanger 100 has an inlet 104 in communication with the distribution channel 2, and the inlet 104 is used for refrigerant to enter the distribution channel 2. As shown in Figures 1 and 8, the heat exchanger 100 includes an orifice plate 6, which is located between the inlet 104 and the distribution channel 2 along the height direction of the heat exchanger 100. The orifice plate 6 has a main inlet 61 and an auxiliary inlet 62, both of which are connected to the inlet 104 and the distribution channel 2. That is, the refrigerant can enter from the inlet 104 and enter the distribution channel 2 through the holes on the orifice plate 6. The flow area of ​​the main inlet 61 is larger than that of the auxiliary inlet 62.

[0032] The main inlet 61 has a first centerline L1, the auxiliary inlet 62 has a second centerline L2, and the distribution channel 2 has a third centerline L3. There are gaps between each pair of the first centerline L1, the second centerline L2, and the third centerline L3. In other words, both the main inlet 61 and the auxiliary inlet 62 are eccentrically positioned relative to the distribution channel 2. Since the flow area of ​​the main inlet 61 is larger than that of the auxiliary inlet 62, the refrigerant mainly enters the distribution channel 2 from the main inlet 61. After impacting the wall of the distribution channel 2, the refrigerant bounces back, and is then distributed. Due to gravity, the bounced refrigerant has a limited bounce distance. Therefore, some refrigerant enters the distribution channel 2 through the auxiliary inlet 62 for distribution. This portion of the refrigerant compensates for the insufficient bounce distance of the refrigerant entering from the main inlet 61, effectively compensating for the refrigerant distribution. The flow area of ​​the auxiliary inlet 62 is smaller than that of the main inlet 61 to prevent excessive refrigerant flow from entering through the auxiliary inlet 62 from affecting the distribution of the bounced refrigerant.

[0033] Specifically, in one embodiment, as shown in Figure 2, the flow area of ​​the main inlet 61 / the flow area of ​​the auxiliary inlet 62 is A, where 4 ≤ A ≤ 25. The shapes of the flow areas of the main inlet 61 and the auxiliary inlet 62 are not defined here. Furthermore, the orifice plate 6 has at least two auxiliary inlets 62, in which case the flow area of ​​the auxiliary inlets 62 is the sum of the flow areas of all auxiliary inlets 62.

[0034] In one embodiment, as shown in FIG2, the distribution hole 52 includes a first distribution hole 520, the distance from the center of the main inlet 61 to the first distribution hole 520 is a first distance D1, and the distance from the center of the auxiliary inlet 62 to the first distribution hole 520 is a second distance D2, wherein 2≤D1 / D2≤6.

[0035] To better compensate for the refrigerant entering from the main inlet 61, and to form a closed loop as shown in Figure 9 between the refrigerant entering from the main inlet 61 and the refrigerant entering from the auxiliary inlet 62, in one embodiment, as shown in Figure 6, a plane parallel to the stacking direction of the multiple plates 101 is defined as the projection plane. The orthographic projection of the wall corresponding to the main inlet 61 onto the projection plane is the first projection P1, the orthographic projection of the wall corresponding to the auxiliary inlet 62 onto the projection plane is the second projection P2, and the orthographic projection of the wall corresponding to the distribution channel 2 onto the projection plane is the third projection P3. The first projection P1 has a first center point C1, the second projection P2 has a second center point C2, and the third projection P3 has a third center point C3. The first center point C1, the second center point C2, and the third center point C3 are all located on the same second straight line L0. That is, the centers of the first projection P1 and the second projection P2 pass through the center of the third projection P3, and the centers of the first projection P1 and the second projection P2 are located on the diameter of the line L0.

[0036] In one embodiment, as shown in Figures 3 and 4, the orifice plate 6 has a first groove 63 and a second groove 64. The first groove 63 is recessed along the orifice plate 6 towards the main inlet 61, and the second groove 64 is recessed along the orifice plate 6 towards the main inlet 61. The first groove 63 and the second groove 64 are aligned with a third center point C3, that is, the first groove 63, the second groove 64 and the third center point C3 all pass through the second straight line L0. This arrangement facilitates the main inlet 61 and the auxiliary inlet 62 to be set along the second straight line L0.

[0037] A certain distance is maintained between the main inlet 61 and the auxiliary inlet 62 to reduce the interference of the refrigerant entering through the auxiliary inlet 62 on the rebounding refrigerant. In one embodiment, as shown in Figure 6, along the extension direction of the second straight line L0, the third center point C3 is located between the first center point C1 and the second center point C2. Thus, under the premise that both the main inlet 61 and the auxiliary inlet 62 are eccentric to the distribution channel 2, a certain distance is maintained between them. Preferably, the distance between the main inlet 61 and the auxiliary inlet 62 is greater than the radius of the third projection P3.

[0038] Furthermore, in one embodiment, as shown in Figure 6, the third projection P3 has a radius R, and the distance between the first center point C1 and the second center point C2 is S, where R ≤ S ≤ 1.5R. The distance between the main inlet 61 and the auxiliary inlet 62 is within this range, so that the refrigerant entering through the main inlet 61 and the refrigerant entering through the auxiliary inlet 62 form a closed loop. This requirement can also be met when the number of auxiliary inlets 62 is greater than or equal to two.

[0039] To improve the distribution efficiency of heat exchanger 100 during heat exchange, in one embodiment, as shown in Figures 1 and 2, heat exchanger 100 includes a distribution cylinder 51, which forms part of the wall of distribution channel 2. Heat exchanger 100 has distribution holes 52 that penetrate the distribution cylinder 51 and communicate with at least two refrigerant channels 103. The refrigerant flows in the distribution channel 2 and is precisely distributed to the refrigerant channels 103 through the distribution holes 52, thereby improving the distribution efficiency of heat exchanger 100 during heat exchange. Further, in one embodiment, as shown in Figure 1, there are multiple distribution holes 52, each directly communicating with each refrigerant channel 103. Each distribution hole 52 corresponds one-to-one with each refrigerant channel 103. The multiple distribution holes 52 are arranged sequentially along the height direction H, i.e., vertically. The distribution cylinder 51 has at least two rows of distribution holes 52. In one embodiment, as shown in Figure 3, the multiple distribution holes 52 can be arranged in multiple rows.

[0040] In one embodiment, the distribution cylinder 51 is connected to multiple plates 101 by welding. In another embodiment, the connection method is expansion tube connection. The advantage of expansion tube connection over welding connection is that there are no impurities such as welding slag, and the sealing performance and reliability are better.

[0041] Specifically, in another embodiment, the distribution cylinder 51 is connected to the orifice plate 6, and the connection between the distribution cylinder 51 and the orifice plate 6 is welded.

[0042] In one embodiment, as shown in FIG8, the distribution cylinder 51 includes a side wall 511 and a bottom wall 51, wherein both the side wall 511 and the bottom wall 51 form part of the wall of the distribution channel 2. The side wall 511 is closer to the inlet 104 relative to the bottom wall 512. The side wall 511 and the bottom wall 512 are connected. Along the thickness direction T of the side wall 511, the side wall 511 and the bottom wall 512 can be an integral part, or they can be connected by welding. The distribution hole 52 penetrates the side wall 511. In order to form a closed loop between the refrigerant entering through the main inlet 61 and the refrigerant entering through the auxiliary inlet 62 as shown in FIG9, in one embodiment, the main inlet 61 is farther away from the distribution hole 52 relative to the auxiliary inlet 62. Furthermore, to facilitate the connection between the distribution cylinder 51 and the orifice plate 6, as shown in Figure 5, the distribution cylinder 51 has a third groove 53, which is recessed along the side wall 511 towards the bottom wall 512. When the distribution cylinder 51 is connected to the orifice plate 6, the first groove 61 is at least partially aligned with the third groove 53, or the second groove 62 is at least partially aligned with the third groove 53, and the third groove 53 plays a positioning role.

[0043] To optimize the heat exchange rate of the heat exchanger 100 and improve the fluid distribution speed, in one embodiment, as shown in Figure 7, the orthographic projection of the distribution cylinder 51 on the projection plane is the fourth projection P4; the orthographic projection of the wall corresponding to the distribution hole 52 on the projection plane is the first point B1; the first ray L5 is defined to pass through the third center point C3 and the center B10 of the first point B1 in sequence; the second ray L4 is defined to pass through the third center point C3 and the first center point C1 in sequence; wherein, the angle between the first ray L5 and the second ray L4 is α, 0°≤α≤135°. Within this range, it can be ensured that the fluid enters the refrigerant channel 103 from the distribution channel 2 at a relatively fast speed; when α exceeds 135°, the fluid enters the distribution channel 2 at a significantly reduced speed.

[0044] A distributor 5 according to this application includes a distribution cylinder 51 and an orifice plate 6. The distributor 5 has a distribution channel 2 and a distribution hole 52. The distribution channel 2 communicates with the distribution hole 52, and the distribution hole 52 penetrates the distribution cylinder 51. The distribution cylinder 51 and the orifice plate 6 each form part of the wall of the distribution hole 52. The orifice plate 6 has a main inlet 61 and an auxiliary inlet 62. Both the main inlet 61 and the auxiliary inlet 62 are directly connected to the outside. Both the main inlet 61 and the auxiliary inlet 62 are connected to the distribution channel 2. The flow area of ​​the main inlet 61 is larger than that of the auxiliary inlet 62. The main inlet 61 has a first center line L1, the auxiliary inlet 62 has a second center line L2, and the distribution channel 2 has a third center line L3. There is a gap between each pair of the first center line L1, the second center line L2, and the third center line L3. In other words, the auxiliary inlet 62 is eccentrically positioned with respect to the distribution channel 2. After some fluid enters the distribution channel 2 from the auxiliary inlet 62, it is distributed, and the flow rate compensation is performed on the area where the rebounding fluid cannot be distributed, thereby improving the uniformity of fluid distribution in the distributor. In one embodiment, the distribution hole 52 and the second center line L2 are located on the same side of the third center line L3, and the first center line L1 is located on the other side of the third center line L3.

[0045] As shown in Figure 1, the heat exchanger 100 includes a fixing member 54, which is used to fix the distributor 5 and connects the distributor 5 to the plate 101.

[0046] The shapes of the main inlet 61, the auxiliary inlet 62, and the distribution hole 53 are not defined here.

[0047] The flow path of the fluid in distributor 5 is shown in Figure 9. Ideally, the fluid entering through the main inlet 61 and the auxiliary inlet 62 can form turbulence. The distributor 5 in this application can be used in heat exchangers to improve the uniformity of fluid distribution in the heat exchanger.

[0048] A heat exchanger 100 includes a body portion 81 and a distribution portion 82, as shown in Figures 1, 2, and 3. The body portion 81 has a refrigerant flow channel 83. The distribution portion 82 is at least partially located within the body portion 81. The distribution portion 82 has a main refrigerant inlet 84, an auxiliary refrigerant inlet 85, a distribution chamber 86, and a distribution hole 52. The main refrigerant inlet 84 communicates with the distribution chamber 86, the auxiliary refrigerant inlet 85 communicates with the distribution chamber 86, and the distribution hole 52 communicates with the distribution chamber 86 and the refrigerant flow channel 83. The main refrigerant inlet 84 and the auxiliary refrigerant inlet 85 are located on the same side of the distribution portion 82, and the distribution hole 52 is located on the other side of the distribution portion 82. The flow area of ​​the main refrigerant inlet 84 is larger than the flow area of ​​the auxiliary refrigerant inlet 85. The heat exchanger 100 of this application has two inlets: a main refrigerant inlet 84 and an auxiliary refrigerant inlet 85. The flow area of ​​the main refrigerant inlet 84 is larger than that of the auxiliary refrigerant inlet 85. In the direction perpendicular to the axial direction of the distribution chamber 86, the auxiliary refrigerant inlet 85 is closer to the distribution hole 52 than the main refrigerant inlet 84. When the heat exchanger is working, the refrigerant can enter the distribution chamber 86 from the main refrigerant inlet 84, and can also enter the distribution chamber 86 from the auxiliary refrigerant inlet 85 to form a swirling flow with the refrigerant entering from the main refrigerant inlet 84, thereby improving the mixing uniformity of the refrigerant. Furthermore, the auxiliary refrigerant inlet 85 can supplement the refrigerant distribution at the refrigerant outlet 84 near the refrigerant inlet, thereby improving the distribution uniformity of the refrigerant in the distribution chamber 86.

[0049] In one embodiment, the distribution section 82 includes a cylindrical section 821 and a cover section 822. The cover section 822 covers one side of the cylindrical section 821. The distribution chamber 86 is located inside the cylindrical section 821. The main refrigerant inlet 84 and the auxiliary refrigerant inlet 85 are disposed through the cover section 822. The side wall of the cylindrical section 821 is provided with at least one row of distribution holes 52 arranged along the axial direction of the cylindrical section 821. The distribution holes 52 penetrate the side wall of the cylindrical section 821. The extending direction of the distribution holes 52 is perpendicular to the extending direction of the main refrigerant inlet 84, and the extending direction of the main refrigerant inlet 84 is parallel to the extending direction of the auxiliary refrigerant inlet 85.

[0050] Furthermore, to better supplement the refrigerant distribution at the refrigerant outlet 84 near the refrigerant inlet, in one embodiment, a row of distribution holes 52 is arranged along the axial direction of the cylindrical portion 821, and in the radial direction of the cylindrical portion 821, the auxiliary refrigerant inlet 85 is located between the main refrigerant inlet 84 and the distribution holes 52.

[0051] In one embodiment, the cylindrical body 821 is cylindrical, the cover 822 is plate-shaped, and both the main refrigerant inlet 84 and the auxiliary refrigerant inlet 85 are circular holes. The central axis of the main refrigerant inlet 84 does not coincide with the central axis of the distribution chamber 86, and the central axis of the auxiliary refrigerant inlet 85 does not coincide with the central axis of the distribution chamber 86. In other words, the main refrigerant inlet 84, the auxiliary refrigerant inlet 85, and the distribution chamber 86 are eccentrically arranged, so that the refrigerant forms a U-shaped path in the distribution chamber 86, improving the uniformity of refrigerant distribution in the distribution chamber 86, thereby enhancing the heat exchange uniformity of the heat exchanger 100.

[0052] Furthermore, all of the row of distribution holes 52 are circular holes, and the center line connecting the row of distribution holes 52, the central axis of the main refrigerant inlet 84, and the central axis of the auxiliary refrigerant inlet 85 are located on the same plane.

[0053] In one embodiment, the heat exchanger 100 is a plate heat exchanger. Specifically, the body part 81 includes a plurality of stacked plates 101, with refrigerant flow channels 83 and coolant flow channels 102 formed between the plates 101. Each plate 101 is provided with a corner hole 1011, and a distribution part 82 is at least partially located in the corner hole 1011. The distribution part 82 is welded to the plate 101, and the axial direction of the distribution part 82 is parallel to the stacking direction of the plates 101.

[0054] In another embodiment, the heat exchanger 100 is a microchannel heat exchanger. Specifically, the body 81 includes a plurality of microchannel flat tubes 881, a first manifold 882 and a second manifold 883, and a plurality of fins 884. One end of the microchannel flat tube 881 is connected to the first manifold 882, and the other end of the microchannel flat tube 881 is connected to the second manifold 883. The microchannel flat tube 881 has a refrigerant channel 83, which connects the cavity 8821 of the first manifold 882 and the cavity 8831 of the second manifold 883. The fins 884 are disposed between adjacent microchannel flat tubes 881. The distribution part 82 is at least partially located in the cavity 8821 of the first manifold 882. The distribution part 82 is welded to the first manifold 882. The distribution hole 52 of the distribution part 82 is connected to the cavity of the first manifold 882. The axial direction of the distribution part 82 is parallel to the arrangement direction of the plurality of microchannel flat tubes 881.

[0055] The plate heat exchanger 1000 includes multiple plates 101 stacked along the height direction H of the plate heat exchanger 1000. Inter-plate channels 105 are formed between adjacent plates 101. The inter-plate channels 105 include refrigerant channels 103 and coolant channels 102. The refrigerant channels 103 and coolant channels 102 are fluidly isolated, and heat exchange occurs due to the temperature difference between the fluids in the refrigerant channels 103 and coolant channels 102. To improve the heat exchange uniformity of the plate heat exchanger 1000, a distributor 5 is installed. The distributor 5 includes a distribution cylinder 51. The refrigerant enters the distribution cylinder 51 through the eccentric main inlet 61 and undergoes swirling distribution, thereby improving the distribution uniformity of the plate heat exchanger 1000. However, the stability of the refrigerant swirling in the distribution cylinder affects the distribution uniformity of the plate heat exchanger.

[0056] Therefore, this application provides a plate heat exchanger 1000, as shown in Figures 1, 8 and 9, including a distributor 5, the distributor 5 including a distribution cylinder 51, a portion of the distribution cylinder 51 being connected to a plurality of plates 101; the distribution cylinder 51 having a distribution channel 2, the distribution channel 2 being connected to a refrigerant channel 103; the plate heat exchanger 1000 having a main inlet 61, the main inlet 61 being connected to the distribution channel 2, the main inlet 61 having a first centerline L1, the distribution channel 2 having a third centerline L3, the first centerline L1 being located on one side of the third centerline L3; the distribution cylinder 51 having a hydraulic diameter Dh and a first height H1, the first height H1 being the shortest distance from the bottom wall 512 to the main inlet 61, wherein 6≤H1 / Dh≤7. When the plate heat exchanger 1000 is working, the refrigerant can enter the distribution channel 2 from the main inlet 61. The first center line L1 is located on one side of the third center line L3, that is, the eccentric setting of the main inlet 61 causes the refrigerant to rebound at the bottom of the distribution cylinder and form a swirling flow. Due to the restriction of 6≤H1 / Dh≤7, the phenomenon of refrigerant accumulation near the inlet can be reduced due to insufficient height of the distribution cylinder, which limits the height of the refrigerant rebound. It can also reduce the phenomenon of insufficient height of the distribution cylinder, which results in a small height of refrigerant rebound and failure to form a swirling flow. The restriction of 6≤H1 / Dh≤7 makes the swirling flow of refrigerant in the distribution cylinder more stable, thereby improving the distribution uniformity of the plate heat exchanger.

[0057] In one embodiment, as shown in FIG16, the distribution cylinder 51 is cylindrical and perpendicular to the height direction H of the plate heat exchanger 1000. The hydraulic diameter Dh is the cross-sectional diameter Dh1 of the distribution cylinder 51. That is, the cross-section of the distribution cylinder 51 is circular, and the hydraulic diameter Dh is the diameter.

[0058] To further improve the swirling stability of the refrigerant in the distribution cylinder, in one embodiment, as shown in FIG9, the plate heat exchanger 1000 includes an orifice plate 6, which forms part of the wall of the distribution channel 2. The orifice plate 6 has an auxiliary inlet 62 and a main inlet 61. The distribution cylinder 51 has a distribution hole 52, which penetrates part of the wall of the distribution cylinder 51 and communicates with at least two refrigerant channels 103 and the distribution channel 2. The flow area of ​​the main inlet 61 is larger than that of the auxiliary inlet 62. The direction perpendicular to the height direction H of the plate heat exchanger 1000 and the direction through the distribution hole 52 are defined as the first direction. Along the first direction, the main inlet 61 is farther away from the distribution hole 52 relative to the auxiliary inlet 62. When the plate heat exchanger 1000 is operating, the refrigerant can enter the distribution channel 2 from the main inlet 61 and flow to the side near the auxiliary inlet 62 to form a swirling flow, which improves the mixing uniformity of the refrigerant. The auxiliary inlet 62 can also supplement the refrigerant distribution at the distribution orifice near the inlet, thereby improving the swirling stability of the refrigerant in the distribution channel 2. In one embodiment, the orifice plate 6 is connected to the distribution cylinder 51. The orifice plate 6 can be completely inside the distribution channel 2 and connected to the inner wall 56 of the distribution cylinder 51, or the orifice plate 6 can be located outside the distribution channel 2 and connected to the top of the distribution cylinder 51.

[0059] To facilitate the installation of the distribution cylinder 51 in the plate heat exchanger 1000, a gap exists between the distribution cylinder 51 and the plate 101. Specifically, in one embodiment, as shown in FIG16, the distribution cylinder 51 includes an outer wall surface 55 and an inner wall surface 56. The inner wall surface 56 is closer to the distribution channel 2 than the outer wall surface 55. The plate 101 includes a connecting portion 1011, and the distribution cylinder 51 is connected to the connecting portion 1011. In a direction perpendicular to the height direction H of the plate heat exchanger 1000, at least a portion of the outer wall surface 55 and the connecting portion 1011 have a gap I. The gap I ensures that the distribution cylinder 51 can be inserted into the plate heat exchanger 1000 without interference.

[0060] On the other hand, the refrigerant enters the refrigerant channel 103 through the distribution hole 52 in the distribution channel 2. Controlling the refrigerant pressure drop is beneficial for smooth refrigerant flow. In another embodiment, as shown in Figure 16, the gap I is 0.5-1mm. When the gap I is small, the pressure drop is large, and the pressure drop is one of the important parameters in the plate heat exchanger 1000.

[0061] As shown in Figure 9 in one embodiment, the first height H1 is achieved by the orifice plate 6, which includes an outer plate surface 65 and an inner plate surface 66. The inner plate surface 66 is closer to the distribution channel 2 than the outer plate surface 65. The distribution cylinder 51 includes a bottom wall 512, which forms part of the wall of the distribution channel 2. Along the height direction H of the plate heat exchanger 1000, the bottom wall 512 and the inner plate surface 66 are located at opposite ends in the axial direction of the distribution channel 2. The distance from the bottom wall 512 to the inner plate surface 66 in the axial direction of the distribution channel 2 is the first height H1. In simple terms, when the length-to-diameter ratio of the distribution cylinder 51 is 6 to 7, the refrigerant has better swirling stability in the distribution cylinder 51, thereby improving the heat exchange performance of the plate heat exchanger 1000.

[0062] Although the technical solutions of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and variations can be made to these technical solutions without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A heat exchanger, wherein, The heat exchanger (100) has a distribution channel (2), a main inlet (61), an auxiliary inlet (62), a distribution hole (52), and a refrigerant channel (103). The distribution hole (52) is connected to the distribution channel (2), and the distribution hole (52) is connected to the refrigerant channel (103) and the distribution channel (2). The main inlet (61) and the auxiliary inlet (62) are both connected to the distribution channel (2). The flow area of ​​the main inlet (61) is larger than the flow area of ​​the auxiliary inlet (62). The surface perpendicular to the axial direction of the distribution channel (2) is defined as the auxiliary projection surface. The projection of the main inlet (61) on the auxiliary projection surface is farther away from the projection of the distribution hole (52) on the auxiliary projection surface than the projection of the auxiliary inlet (62) on the auxiliary projection surface.

2. The heat exchanger according to claim 1, wherein, The main inlet (61) has a first centerline (L1), the auxiliary inlet (62) has a second centerline (L2), the distribution channel (2) has a third centerline (L3), the distribution hole (52) and the second centerline (L2) are located on the same side of the third centerline (L3), and the first centerline (L1) is located on the other side of the third centerline (L3); There is a gap between each of the first center line (L1), the second center line (L2), and the third center line (L3).

3. The heat exchanger according to any one of claims 1-2, wherein, The distribution hole (52) includes a first distribution hole (520), the distance from the center of the projection of the main inlet (61) on the auxiliary projection surface to the center of the first distribution hole (520) on the auxiliary projection surface is a first distance (D1), and the distance from the center of the projection of the auxiliary inlet (62) on the auxiliary projection surface to the center of the projection of the first distribution hole (520) on the auxiliary projection surface is a second distance (D2), wherein 2≤D1 / D2≤6; And / or, the heat exchanger (100) has an inlet (104), the heat exchanger (100) includes an orifice plate (6) forming a portion of the wall of the distribution channel (2), the orifice plate (6) being located between the inlet (104) and the distribution channel (2) along the height direction (H) of the heat exchanger (100); The main inlet (61) and the auxiliary inlet (62) are both located on the perforated plate (6), and both the main inlet (61) and the auxiliary inlet (62) are connected to the inlet (104); both the main inlet (61) and the auxiliary inlet (62) are circular holes.

4. The heat exchanger according to claim 3, wherein, The heat exchanger (100) includes a distributor (5), the distributor (5) includes a distribution cylinder (51), the distribution cylinder (51) is connected to the orifice plate (6); The distribution cylinder (51) forms part of the wall of the distribution channel (2), and the distributor (5) has a distribution hole (52) that penetrates part of the wall of the distribution cylinder (51) and is connected to the at least two refrigerant channels (103).

5. The heat exchanger according to claim 4, wherein, The distribution cylinder (51) includes a side wall (511) and a bottom wall (512). The side wall (511) is closer to the inlet (104) than the bottom wall (512). The side wall (511) is connected to the bottom wall (512). The distribution hole (52) penetrates the side wall (511). The orifice plate (6) has at least two auxiliary inlets (62). There are multiple distribution holes (52). Each distribution hole (52) is connected to each refrigerant channel (103) in a one-to-one correspondence. The multiple distribution holes (52) are arranged sequentially along the axial direction of the distribution channel (2). Alternatively, the distribution cylinder (51) has at least two rows of distribution holes (52). And / or, define a plane perpendicular to the axial direction of the distribution channel (2) as a projection plane, the orthographic projection of the wall forming the distribution channel (2) onto the projection plane as a third projection (P3), the orthographic projection of the wall forming the main inlet (61) onto the projection plane as a first projection (P1), and the orthographic projection of the wall forming the auxiliary inlet (62) onto the projection plane as a second projection (P2); the first projection (P1) has a first center point (C1), the second projection (P2) has a second center point (C2), the third projection (P3) has a third center point (C3), and the first center point (C1), the second center point (C2), and the... All third center points (C3) are located on the same second straight line (L0); along the extension direction of the second straight line (L0), the third center point (C3) is located between the first center point (C1) and the second center point (C2); the orthographic projection of the distribution cylinder (51) on the projection plane is the fourth projection (P4); the orthographic projection of the wall corresponding to the distribution hole (52) on the projection plane is the first point (B1); the first ray (L5) is defined to pass through the center (B10) of the third center point (C3) and the first point (B1) in sequence; the second ray (L4) is defined to pass through the third center point (C3) and the first center point (C1) in sequence. The angle between the first ray (L4) and the second ray (L5) is α, where 0°≤α≤135°.

6. The heat exchanger according to any one of claims 1 to 5, wherein, The heat exchanger (100) includes a manifold (91), at least two flat tubes (92) and fins (99). The fins (99) are located between two adjacent flat tubes (92). The distribution channel (2) is disposed in the manifold (91), and the refrigerant channel (103) is disposed in the flat tubes (92). The refrigerant channel (103) is connected to the distribution channel (2).

7. The heat exchanger according to any one of claims 1 to 5, wherein, The heat exchanger (100) includes a plate heat exchanger (1000), which includes a plurality of plates (101). The plurality of plates (101) are stacked along the height direction of the heat exchanger (100), and an inter-plate flow channel (105) is formed between adjacent plates (101). The inter-plate flow channel (105) includes a refrigerant flow channel (103) and a coolant flow channel (102). The distribution flow channel (2) and the refrigerant flow channel (103) are connected, and the refrigerant flow channel (103) is fluidly isolated from the coolant flow channel (102).

8. The heat exchanger according to claim 1, wherein, The device includes a body (81) and a distribution section (82). The body (81) has a refrigerant flow channel (83). The distribution section (82) is connected to the body (81). The distribution section (82) has a main refrigerant inlet (84), an auxiliary refrigerant inlet (85), a distribution chamber (86), and a distribution hole (52). The main refrigerant inlet (84) communicates with the distribution chamber (86). The auxiliary refrigerant inlet (85) communicates with the distribution chamber (86). The distribution hole (52) communicates with the distribution chamber (86) and the refrigerant flow channel (83). The main refrigerant inlet (84) and the auxiliary refrigerant inlet (85) are located on the same side of the distribution section (82), and the distribution hole (52) is located on the other side of the distribution section (82). The flow area of ​​the main refrigerant inlet (84) is larger than that of the auxiliary refrigerant inlet (85). In the direction perpendicular to the axial direction of the distribution chamber (86), the auxiliary refrigerant inlet (85) is closer to the distribution hole (52) than the main refrigerant inlet (84).

9. The heat exchanger according to claim 8, wherein, The distribution section (82) includes a cylindrical section (821) and a cover section (822). The cover section (822) covers one side of the cylindrical section (821). The distribution chamber (86) is located inside the cylindrical section (821). The main refrigerant inlet (84) and the auxiliary refrigerant inlet (85) penetrate both sides of the cover section (822) in the axial direction. The side wall of the cylindrical section (821) is provided with the distribution holes (52) arranged in the axial direction of the cylindrical section (821). The distribution holes (52) penetrate the side wall of the cylindrical section (821). The extension direction of the distribution hole (52) is perpendicular to the extension direction of the main refrigerant inlet (84), and the extension direction of the main refrigerant inlet (84) is parallel to the extension direction of the auxiliary refrigerant inlet (85); the cylindrical body (821) is cylindrical, and both the main refrigerant inlet (84) and the auxiliary refrigerant inlet (85) are circular holes. The central axis of the main refrigerant inlet (84) does not coincide with the central axis of the distribution chamber (86), and the central axis of the auxiliary refrigerant inlet (85) does not coincide with the central axis of the distribution chamber (86); the row of distribution holes (52) are all circular holes, and the center line connecting the rows of distribution holes (52), the central axis of the main refrigerant inlet (84), and the central axis of the auxiliary refrigerant inlet (85) are located in the same plane.

10. The heat exchanger according to any one of claims 8 to 9, wherein, The main body (81) includes a plurality of stacked plates (101), with the refrigerant channel (83) and coolant channel (102) formed between the plates (101). Each plate (101) is provided with a corner hole (1011), and the distribution part (82) is at least partially located in the corner hole (1011). The distribution part (82) is welded to the plate (101), and the axial direction of the distribution part (82) is parallel to the stacking direction of the plates (101).

11. The heat exchanger according to any one of claims 8 to 9, wherein, The main body (81) includes a microchannel flat tube (881), a first manifold (882), a second manifold (883), and fins (884). One end of the microchannel flat tube (881) is connected to the first manifold (882), and the other end of the microchannel flat tube (881) is connected to the second manifold (883). The microchannel flat tube (881) has the refrigerant channel (83), which connects the cavity (8821) of the first manifold (882) and the second manifold (884). The cavity (8831) of the two manifolds (883) has fins (884) disposed between adjacent microchannel flat tubes (881), the distribution part (82) is at least partially located in the cavity of the first manifold (882), the distribution part (82) is welded to the first manifold (882), the distribution hole (52) communicates with the cavity (8821) of the first manifold (882), and the axial direction of the distribution part (82) is parallel to the arrangement direction of the plurality of microchannel flat tubes (881).

12. The heat exchanger according to claim 5, wherein: The plate heat exchanger (1000) includes a distributor (5), the distributor (5) includes a distribution cylinder (51), a portion of the distribution cylinder (51) is connected to the plurality of plates (101); the distribution cylinder (51) has a distribution channel (2), the distribution channel (2) and the refrigerant channel (103) are connected; The plate heat exchanger (1000) has a main inlet (61) that is connected to the distribution channel (2). The main inlet (61) has a first center line (L1) and the distribution channel (2) has a third center line (L3). The first center line (L1) is located on one side of the third center line (L3). The distribution cylinder (51) has a hydraulic diameter (Dh) and a first height (H1), the first height (H1) being the shortest distance from the bottom wall (512) to the main inlet (61), wherein 6 ≤ H1 / Dh ≤ 7.

13. The heat exchanger according to claim 12, wherein: The distribution cylinder (51) includes an outer wall surface (55) and an inner wall surface (56). The inner wall surface (56) is closer to the distribution channel (2) relative to the outer wall surface (55). The plate (101) includes a connecting part (1011). The distribution cylinder (51) is connected to the connecting part (1011). In a direction perpendicular to the height direction of the plate heat exchanger (1000), at least a portion of the outer wall surface (55) has a gap (I) between it and the connecting portion (1011); The distribution cylinder (51) is cylindrical and is perpendicular to the height direction of the plate heat exchanger (1000). The hydraulic diameter (Dh) is the cross-sectional diameter (Dh1) of the distribution cylinder (51).

14. The heat exchanger according to any one of claims 7, 12 and 13, wherein: The plate heat exchanger (1000) includes an orifice plate (6), which forms part of the wall of the distribution channel (2). The orifice plate (6) has an auxiliary inlet (62) and a main inlet (61). The distribution cylinder (51) has a distribution hole (52). The orifice plate (6) includes an outer plate surface (65) and an inner plate surface (66). The inner plate surface (66) is closer to the distribution channel (2) relative to the outer plate surface (65). The distribution cylinder (51) includes a bottom wall (512). The bottom wall (512) forms part of the wall of the distribution channel (2). Along the height direction of the plate heat exchanger (1000), the bottom wall (512) and the inner plate surface (66) are located at both ends of the distribution channel (2) in the axial direction. In the axial direction of the distribution channel (2), the distance from the bottom wall (512) to the inner plate surface (66) is the first height (H1). The distribution cylinder (51) is welded to or expanded to the plurality of plates (101).

15. The heat exchanger according to any one of claims 1-14, wherein: The flow area of ​​the main inlet (61) is A1, and the flow area of ​​the auxiliary inlet (62) is A2, wherein 4≤A1 / A2≤25; The distance between the center of the main inlet (61) and the center of the auxiliary inlet (62) is S. The heat exchanger (100) includes an orifice plate (6), which forms part of the wall of the distribution channel (2). The radius of the orifice plate (6) is R, where R≤S≤1.5R.

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