Plate heat exchanger

Abstract

This application provides a plate heat exchanger, including a distributor. The distributor includes a distribution cylinder, which is connected to multiple plates. The distribution cylinder has a distribution channel that communicates with a refrigerant channel. The plate heat exchanger has a main inlet that communicates with the distribution channel. The main inlet has a first centerline, and the distribution channel has a third centerline. The first centerline is located on one side of the third centerline. The distribution cylinder has a hydraulic diameter and a first height, wherein 6≤H1 / Dh≤7. When the plate heat exchanger is working, the limitation of 6≤H1 / Dh≤7 can reduce the phenomenon of refrigerant accumulation near the inlet due to insufficient height of the distribution cylinder and limited refrigerant rebound height. It can also reduce the phenomenon of refrigerant rebound height being too small and unable to form swirling flow due to excessive height of the distribution cylinder. The limitation 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.

Description

Technical Field

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

[0002] Plate heat exchangers are devices used to transfer heat between different fluids, playing a vital role in industrial production, energy utilization, and environmental control. A plate heat exchanger consists of multiple plates stacked to form multiple flow channels between them. Fluids at different temperatures flow into these channels from the outside of the heat exchanger, exchanging heat through the temperature differences between the plates. To improve the heat exchange uniformity of plate heat exchangers, a distributor is installed. This distributor includes a distribution cylinder. The refrigerant enters the distribution cylinder through an eccentric inlet and undergoes swirling distribution, thus improving the uniformity of heat exchange. However, the stability of the refrigerant swirling within the distribution cylinder affects the overall uniformity of heat exchange. Summary of the Invention

[0003] This application aims to provide a plate heat exchanger with strong stability in the swirling flow of refrigerant in the distribution cylinder.

[0004] Therefore, this application provides a plate heat exchanger comprising a plurality of plates stacked along the height direction of the plate heat exchanger, with inter-plate channels formed between adjacent plates. The inter-plate channels include refrigerant channels and coolant channels, which are fluidly isolated from each other. The plate heat exchanger includes a distributor, which includes a distribution cylinder partially connected to the plurality of plates. The distribution cylinder has the distribution channel, which communicates with the refrigerant channel. The plate heat exchanger has a main inlet communicating with the distribution channel. The main inlet has a first centerline, and the distribution channel has a third centerline, with the first centerline located on one side of the third centerline. The distribution cylinder has a hydraulic diameter and a first height, where 6 ≤ H1 / Dh ≤ 7.

[0005] When the plate heat exchanger is working, the refrigerant can enter the distribution channel from the main inlet. The eccentric setting of the main inlet causes the refrigerant to rebound and form a swirling flow at the bottom of the distribution cylinder. Due to the restriction of 6≤H1 / Dh≤7, the phenomenon of refrigerant accumulation near the inlet can be reduced because the height of the distribution cylinder is insufficient and the rebound height of the refrigerant is limited. It can also reduce the phenomenon of the refrigerant rebounding too little and failing to form a swirling flow because the height of the distribution cylinder is too high. 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. Attached Figure Description

[0006] Figure 1A three-dimensional schematic diagram of a heat exchanger is provided for one embodiment of this application;

[0007] Figure 2 A perspective view of a dispenser is provided for one embodiment of this application;

[0008] Figure 3 for Figure 2 Explosion-proof diagram of the middle distributor;

[0009] Figure 4 for Figure 3 Enlarged schematic diagram of section T1;

[0010] Figure 5 for Figure 3 Enlarged schematic diagram of section T2;

[0011] Figure 6 A schematic projection of the perforated plate in a dispenser is provided for one embodiment of this application;

[0012] Figure 7 for Figure 2 A schematic diagram of the projection of the distributor;

[0013] Figure 8 for Figure 2 A cross-sectional view of the distributor;

[0014] Figure 9 for Figure 2 A cross-sectional view of the distributor from another angle;

[0015] Figure 10 for Figure 2 One embodiment of this application provides a projected schematic diagram of the distribution channel wall and the through-hole wall;

[0016] Figure 11 A cross-sectional schematic diagram of a heat exchanger is provided for one embodiment of this application;

[0017] Figure 12 for Figure 11 Enlarged view of the area indicated by the dashed line;

[0018] Figure 13 A cross-sectional schematic diagram of a heat exchanger is provided for one embodiment of this application;

[0019] Figure 14 A cross-sectional schematic diagram of a heat exchanger is provided for one embodiment of this application;

[0020] Figure 15 for Figure 1 Enlarged view of the dashed line area;

[0021] Figure 16 An exploded schematic diagram of the distribution cylinder of a plate heat exchanger is provided for one embodiment of this application;

[0022] Figure 17 This refers to heat exchangers in related technologies. Detailed Implementation

[0023] The heat exchanger of an exemplary embodiment of this application will now be described in detail with reference to the accompanying drawings. Unless otherwise specified, the features in the following embodiments and technical solutions can complement or combine with each other.

[0024] The plate heat exchanger 1000 includes multiple plates 101 stacked along the height direction H of the plate heat exchanger 1000. Inter-plate flow channels are formed between adjacent plates 101, including refrigerant flow channels 103 and coolant flow channels 102. The refrigerant flow channels 103 and 102 are fluidly isolated, and heat exchange occurs due to the temperature difference between the fluids in the refrigerant flow channels 103 and 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.

[0025] Therefore, this application provides a plate heat exchanger 1000, such as Figure 1 , Figure 8 and Figure 9 As shown, the device includes a distributor 5, which includes a distribution cylinder 51. A portion of the distribution cylinder 51 is connected to multiple plates 101. The distribution cylinder 51 has a distribution channel 2, which is connected to a refrigerant channel 103. The plate heat exchanger 1000 has a main inlet 61, which is connected to the distribution channel 2. The main inlet 61 has a first centerline L1, and the distribution channel 2 has a third centerline L3. The first centerline L1 is located on one side of the third centerline L3. The distribution cylinder 51 has a hydraulic diameter Dh and a first height H1, where 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.

[0026] In one implementation, such as Figure 16As shown, 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.

[0027] To further improve the swirling stability of the refrigerant in the distribution cylinder, in one embodiment, such as Figure 9 As shown, 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 H of the plate heat exchanger 1000 and penetrating the distribution hole 52 is 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 working, 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 supplement the refrigerant distribution at the distribution hole 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 may be completely inside the distribution channel 2 and connected to the inner wall surface 56 of the distribution cylinder 51, or the orifice plate 6 may be located outside the distribution channel 2 and connected to the top of the distribution cylinder 51.

[0028] To facilitate the installation of the distribution cylinder 51 in the plate heat exchanger 1000, a gap is provided between the distribution cylinder 51 and the plate 101. Specifically, in one embodiment, as shown... Figure 16 As shown, 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.

[0029] On the other hand, the refrigerant enters the refrigerant flow 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, such as... Figure 16 As shown, the gap I is 0.5-1mm. When the gap I is small, the pressure drop is large, which is one of the important parameters of the plate heat exchanger 1000.

[0030] In one embodiment, the first height H1 is as follows: Figure 9As shown, 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 than the outer plate surface 65. The distribution cylinder 51 includes a bottom wall 512, which is 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 on both sides of the distribution channel 2. The distance from the bottom wall 512 to the inner plate surface 66 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.

[0031] Specifically, in one implementation, such as Figure 2 As shown, the flow area of ​​the main inlet 61 is A1, and the flow area of ​​the auxiliary inlet 62 is A2, where 4 ≤ A1 / A2 ≤ 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 this case, the flow area of ​​the auxiliary inlets 62 is the sum of the flow areas of all auxiliary inlets 62.

[0032] In one implementation, such as Figure 8 As shown, the auxiliary inlet 62 has a second centerline L2, and the distribution hole 52 is located on the same side of the second centerline L2 as the third centerline L3. The first centerline L1 is located on the other side of the third centerline L3. That is to say, the auxiliary inlet 62 is eccentrically set with respect to the distribution channel 2. After part of the 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.

[0033] In one implementation, such as Figure 6 As shown, the distance between the center of the main inlet 61 and the center of the auxiliary inlet 62 is S, and the radius of the orifice plate 6 is R, where S = (1~1.5)R. The distance between the main inlet 61 and the auxiliary inlet 62 is within this range, ensuring 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.

[0034] In one embodiment, the distribution cylinder 51 is welded to or expanded to a plurality of plates 101.

[0035] like Figure 17 As shown, in the heat exchanger of the related technology, the refrigerant enters the inner cavity of the distribution pipe 90 through the pipe port 93, and then enters the refrigerant flow channel through a row of holes 94 on the side wall of the distribution pipe 90. The refrigerant tends to accumulate at the bottom 95 of the distribution pipe cylinder, which is far away from the pipe port 93. This results in less refrigerant flowing into the holes 94 near the pipe port, while more refrigerant flows into the holes far away from the pipe port 93, thus the refrigerant distribution uniformity of the heat exchanger is poor.

[0036] like Figure 11 and12 As shown, the heat exchanger 100 in this application has a distribution channel 2, a main inlet 61, an auxiliary inlet 62, and a refrigerant channel 103. The distribution channel 2 has a distribution hole 52, which connects the refrigerant channel 103 and 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 direction perpendicular to the axial direction of the distribution channel 2 is 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. Since the flow area of ​​the main inlet 61 is larger than that 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, thereby improving the mixing uniformity of the refrigerant. 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 in the distribution channel.

[0037] The positions of the main inlet 61, auxiliary inlet 62, and distribution hole 52 are arranged to ensure the refrigerant flow principle is as follows: Figure 14 As shown.

[0038] Among them, such as Figure 12 , Figure 15 As shown, 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 93. The fins 93 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.

[0039] like Figure 1 As shown, 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.

[0040] Specifically, in one implementation, such as Figure 1 and Figure 10As shown, a 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. The first straight line L intersects the inner contour of the third projection P3 at the first point O1 and the second point O2. The first straight line L intersects the inner contour of the first projection P1 at the third point O3 and the fourth point O4. The first straight line L intersects the inner contour of the second projection P2 at the fifth point O5 and the second point O2. Point O6 is the sixth point; along the first straight line L, point O3 is closer to point O1 than point O4, and point O5 is closer to point O2 than point O6; along the first straight line L, the distance between point O1 and point O3 is the first distance S1, and the distance between point O2 and point O4 is the second distance S2, where the first distance S1 is less than the second distance S2; along the first straight line L, the distance between point O1 and point O6 is the third distance S3, and the distance between point O2 and point O5 is the fourth distance S4, where the fourth distance S4 is less than the third distance S3.

[0041] 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 connected to 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 connected to the distribution channel 2, and the inlet 104 is used for refrigerant to enter the distribution channel 2. Figure 1 and Figure 8 As shown, 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.

[0042] 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.

[0043] In one implementation, such as Figure 9 As shown, the distance from the center of the main inlet 61 to the distribution hole 52 is the first distance D1, and the distance from the center of the auxiliary inlet 62 to the distribution hole 52 is the second distance D2, where 2≤D1 / D2≤6.

[0044] To better compensate for the refrigerant entering from the main inlet 61, so that the refrigerant entering from the main inlet 61 and the refrigerant entering from the auxiliary inlet 62 form a mixture as follows: Figure 9 The closed loop shown, in one embodiment, is as follows: Figure 6 As shown, 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 this projection plane is the first projection P1, the orthographic projection of the wall corresponding to the auxiliary inlet 62 onto this projection plane is the second projection P2, and the orthographic projection of the wall corresponding to the distribution channel 2 onto this 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 L0.

[0045] In one implementation, such as Figure 3 and Figure 4As shown, 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 the third center point C3 as the center. 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.

[0046] There is a certain distance 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, such as... Figure 6 As shown, 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, with both the main inlet 61 and the auxiliary inlet 62 eccentric to the distribution channel 2, there is a certain distance 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.

[0047] To improve the heat distribution efficiency of heat exchanger 100 during heat exchange, in one embodiment, such as Figure 1 and Figure 2 As shown, the heat exchanger 100 includes a distribution cylinder 51, which forms part of the wall of the distribution channel 2. The heat exchanger 100 has a distribution hole 52 that penetrates the distribution cylinder 51 and communicates with at least two refrigerant channels 103. The distribution hole 52 is also connected to the distribution channel 2. The refrigerant flows in the distribution channel 2 and is precisely distributed to the refrigerant channels 103 through the distribution hole 52, which can improve the distribution efficiency of the heat exchanger 100 during heat exchange. Furthermore, in one embodiment, as... Figure 1 As shown, there are multiple distribution holes 52, each of which is directly connected to 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... Figure 3 As shown, the multiple distribution holes 52 can be arranged in multiple rows.

[0048] 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.

[0049] 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.

[0050] In one implementation, such as Figure 8As shown, 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 are part of the distribution channel 2. The side wall 511 is closer to the inlet 104 than the bottom wall 512. The side wall 511 and the bottom wall 512 are connected. The side wall 511 and the bottom wall 512 can be a single piece, or they can be connected by welding. The distribution hole 52 penetrates the side wall 511. To ensure that the refrigerant entering through the main inlet 61 and the refrigerant entering through the auxiliary inlet 62 are as follows... Figure 9 As shown, a closed loop is formed. In one embodiment, the main inlet 61 is located 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... Figure 5 As shown, the dispensing cylinder 51 has a third groove 53, which is recessed along the side wall 511 toward the bottom wall 512. When the dispensing 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. The third groove 53 plays a positioning role.

[0051] To optimize the heat exchange rate of heat exchanger 100, the fluid distribution rate is increased. In one embodiment, such as... Figure 7 As shown, 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 L4 is defined to include the third center point C3 and the first point B1; the second ray L5 is defined to include the third center point C3 and the first center point C1; wherein, the angle between the first ray L4 and the second ray L5 is α, 0°≤α≤135°. Within this range, α can ensure 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.

[0052] 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 is connected to the distribution hole 52, and the distribution hole 52 penetrates the distribution cylinder 51. The distribution cylinder 51 and the orifice plate 6 are both 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.

[0053] like Figure 1 As shown, the heat exchanger 100 includes a fixing member 54 for fixing the distributor 5 and the fixing member 54 connects the distributor 5 and the plate 101.

[0054] The shapes of the main inlet 61, the auxiliary inlet 62, and the distribution hole 53 are not defined here.

[0055] The fluid flows through distributor 5 as follows: Figure 9 As shown, 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 a heat exchanger to improve the uniformity of fluid distribution within the heat exchanger.

[0056] A heat exchanger, heat exchanger 100 including a body portion 81 and a distribution portion 82, such as Figure 1 , Figure 2 and Figure 3 As shown, the main body 81 has a refrigerant flow channel 83, and the distribution section 82 is at least partially located within the main 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, and the distribution hole 52 connects 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. 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. In addition, 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.

[0057] 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.

[0058] 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.

[0059] 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.

[0060] 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.

[0061] In one embodiment, the heat exchanger 100 is a plate heat exchanger 1000. 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 connecting part 1011, and a distribution part 82 is at least partially located in the connecting part 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.

[0062] 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 of the first manifold 882 and the cavity 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 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 communicates with 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.

[0063] 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 plate heat exchanger comprising a plurality of plates (101) stacked along the height direction of the plate heat exchanger (1000), with adjacent plates (101) forming inter-plate flow channels, the inter-plate flow channels including refrigerant flow channels (103) and coolant flow channels (102), the refrigerant flow channels (103) and the coolant flow channels (102) being fluidly isolated. Its features are: 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), wherein 6 ≤ H1 / Dh ≤ 7.

2. The plate heat exchanger according to claim 1, characterized in that, 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 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).

3. The plate heat exchanger according to claim 2, characterized in that, The gap (I) is 0.5-1 mm.

4. The plate heat exchanger according to claim 1, characterized in that, 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).

5. The plate heat exchanger according to any one of claims 1-4, characterized in that, The plate heat exchanger (1000) includes an orifice plate (6), which is 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). The distribution hole (52) communicates with the at least two refrigerant channels (103) and the distribution channel (2). The circulation area of ​​the main import (61) is larger than that of the auxiliary import (62); A first direction is defined as the direction perpendicular to the height of the plate heat exchanger (1000) and extending through the distribution hole (52). Along the first direction, the main inlet (61) is away from the distribution hole (52) relative to the auxiliary inlet (62).

6. The plate heat exchanger according to claim 5, characterized in that, 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) is 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 on both sides of the distribution channel (2). The distance from the bottom wall (512) to the inner plate surface (66) is the first height (H1).

7. The plate heat exchanger according to claim 5, characterized in that, The circulation area of ​​the main inlet (61) is A1, and the circulation area of ​​the auxiliary inlet (62) is A2, wherein 4≤A1 / A2≤25.

8. The plate heat exchanger according to claim 5, characterized in that, The auxiliary inlet (62) has a second center line (L2), 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).

9. The plate heat exchanger according to claim 5, characterized in that, The distance between the center of the main inlet (61) and the center of the auxiliary inlet (62) is S, and the radius of the orifice plate (6) is R, where S = (1~1.5)R.

10. The plate heat exchanger according to claim 5, characterized in that, The distribution cylinder (51) is welded to or expanded to the plurality of plates (101).

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