Plate heat exchanger

Abstract

The application provides a plate heat exchanger, a distributor comprising a tube body and a partition, the partition being at least partially located in the tube body and connected with an inner wall of the tube body; a first chamber and a second chamber being respectively located on two sides of the partition, the first chamber and the second chamber being communicated; the tube body having a plurality of first holes and second holes, the first holes being communicated with the first flow paths and the first chamber, and the second holes being communicated with the first flow paths and the second chamber. In the application, the partition is at least partially located in the tube body, the first chamber and the second chamber are respectively located on two sides of the partition, and the first chamber and the second chamber are communicated; the tube body is divided into two chambers by the partition and is communicated, a loop is formed, the uniform distribution of fluid momentum is improved; and the tube body has a plurality of first holes and second holes, the first holes are communicated with the first flow paths and the first chamber, and the second holes are communicated with the first flow paths and the second chamber, the refrigerant is distributed into each first flow path through the first holes and the second holes in turn, and the uniformity of distribution is improved.

Description

Technical Field

[0001] This application relates to a plate heat exchanger, and more particularly to a distributor in a plate heat exchanger. Background Technology

[0002] Plate heat exchangers, also known as heat exchangers, are widely used in systems that require heat exchange. Their structure is usually formed by stacking multiple plates, which typically have corrugations or raised points. Usually, two channels for the medium to flow are formed between the plates, and the medium flowing through the two channels exchanges heat.

[0003] In related technologies, to improve the uniformity of medium distribution, a tubular distributor is installed at the refrigerant inlet of the plate. The distributor has holes corresponding to specific channels, allowing the refrigerant to be evenly distributed into each corresponding channel. Although this has some effect, the uniformity of distribution is still poor. As the refrigerant moves from the beginning to the end of the distributor, its momentum gradually increases, which is then converted into pressure. This results in a linear increase in the refrigerant distribution effect (i.e., less refrigerant is distributed in the channel corresponding to the beginning of the distributor, while more refrigerant is distributed in the channel corresponding to the end of the distributor), and the heat exchange effect is not ideal. Summary of the Invention

[0004] The purpose of this application is to provide a plate heat exchanger with more uniform heat distribution.

[0005] This application provides a plate heat exchanger, including a plurality of first plates and a plurality of second plates, wherein the first plates and second plates are alternately stacked along the thickness direction of the plate heat exchanger, and along the stacking direction of the first plates and second plates, the first plates include a first top surface and a first bottom surface, and the second plates include a second top surface and a second bottom surface; the plate heat exchanger includes a first flow path and a second flow path, wherein the first flow path is located between adjacent second bottom surfaces and first top surfaces, and the second flow path is located between adjacent first bottom surfaces and second top surfaces;

[0006] The plate heat exchanger includes a distributor, which includes a tube body and a partition. The partition is at least partially located inside the tube body and is connected to the inner wall of the tube body. The distributor has a first chamber and a second chamber, which are located on opposite sides of the partition and are in communication with each other.

[0007] The tube has multiple first holes and second holes, the first holes connecting the first flow path and the first chamber, and the second holes connecting the first flow path and the second chamber.

[0008] In this application, the separator is at least partially located inside the tube body and is connected to the inner wall of the tube body; the distributor has a first chamber and a second chamber, which are located on both sides of the separator and are connected to each other; the tube body is divided into two chambers by the separator and connected to form a loop, thereby improving the uniform distribution of fluid momentum; and the tube body has multiple first holes and second holes, the first holes connecting the first flow path and the first chamber, and the second holes connecting the first flow path and the second chamber, thereby distributing the refrigerant to each first flow path sequentially through the first holes and the second holes, thereby improving the uniformity of distribution. Attached Figure Description

[0009] Figure 1 This is a perspective view of the plate heat exchanger in this application;

[0010] Figure 2 This is a perspective sectional view of the plate heat exchanger in this application;

[0011] Figure 3 This is a cross-sectional side view of the plate heat exchanger in this application;

[0012] Figure 4 This is a front view of the plate heat exchanger in this application;

[0013] Figure 5 for Figure 4 Enlarged view of point A in the middle circle;

[0014] Figure 6 This is a perspective view of the dispenser in this application;

[0015] Figure 7 This is a perspective sectional view of the dispenser in this application;

[0016] Figure 8 This is a cross-sectional view of the dispenser in this application;

[0017] Figure 9 This is an exploded view of the structure of the first and second plates in this application.

[0018] Figure 10 This is an exploded view of the structure of the first and second plates mating from another perspective in this application;

[0019] Figure 11 This is a cross-sectional view showing the mating of the first and second plates in this application. Detailed Implementation

[0020] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0021] It should be understood that the described embodiments are merely some, not all, of the embodiments in this application. All other embodiments obtained by those skilled in the art based on the embodiments in this application without inventive effort are within the scope of protection of this application.

[0022] In related technologies, plate heat exchangers are composed of multiple alternating stacked first and second plates. Two independent flow channels are formed between adjacent plates: a first flow channel is formed between the first plate and a second plate on one side of it, and a second flow channel is formed between the first plate and a second plate on the other side of it. The first and second flow channels are stacked alternately, and the medium to be heat exchanged is introduced into the first and second flow channels respectively. Thus, when the medium flows through the first and second flow channels, the heat exchange effect can be achieved, and the heat exchange effect is better due to the alternating stacked flow channels.

[0023] In practical applications, a two-phase refrigerant (gas and liquid) is typically introduced. However, if this refrigerant is directly introduced into the first or second flow channel, for example, if the refrigerant is introduced into each of the first flow channels, the gaseous refrigerant, being lighter than the liquid refrigerant, will first enter the first flow channel closest to the refrigerant inlet. The first flow channels closest to the inlet will accumulate a larger amount of gaseous refrigerant. Due to the inertia of the liquid and the momentum of its introduction, the liquid refrigerant will enter the first flow channels farther from the inlet, while the middle flow channels will have less of both gaseous and liquid refrigerant. This results in uneven refrigerant distribution, thus affecting the heat exchange efficiency.

[0024] To prevent this from happening, related technologies incorporate a distributor within the refrigerant channel. The distributor is hollow, and its side walls have openings corresponding to the first flow channels. Since the refrigerant can only enter the corresponding first flow channels through these openings, compared to directly introducing the refrigerant into each channel, the openings reduce the amount of refrigerant entering each channel, thus improving the uniformity of refrigerant distribution. However, the distribution effect still has shortcomings. The reason is that the refrigerant enters the first flow channels through the openings on the distributor. From the opening at the beginning of the distributor to the end, the refrigerant, due to inertia, has a certain impulse. This impulse is converted into pressure at the end of the distributor. Therefore, the pressure at the beginning of the distributor is lower than the pressure at the end, and the pressure gradually increases along the path from the beginning to the end. Consequently, the amount of refrigerant distributed into each first flow channel shows a gradually increasing trend. Figure 3 As shown by curve Q1, the distribution effect is still not uniform enough.

[0025] This application provides a plate heat exchanger, such as Figures 1 to 11As shown, its specific structure includes multiple first plates 1 and multiple second plates 2. The first plates 1 and second plates 2 are alternately stacked along the thickness direction of the plate heat exchanger. Along the stacking direction of the first plates 1 and second plates 2, the first plate 1 includes a first top surface 101 and a first bottom surface 102, and the second plate 2 includes a second top surface 201 and a second bottom surface 202. The plate heat exchanger includes a first flow path 3 and a second flow path 4. The first flow path 3 is located between adjacent second bottom surfaces 202 and first top surfaces 101, and the second flow path 4 is located between adjacent first bottom surfaces 102 and second top surfaces 201. The converter includes a distributor 5, which includes a tube 501 and a separator 502. The separator 502 is at least partially located inside the tube 501 and is connected to the inner wall of the tube 501. The distributor 5 has a first chamber 503 and a second chamber 504, which are located on opposite sides of the separator 502 and are in communication with each other. The tube 501 has a plurality of first holes 505 and a plurality of second holes 506. The first holes 505 are connected to the first flow path 3 and the first chamber 503, and the second holes 506 are connected to the first flow path 3 and the second chamber 504.

[0026] Among them, such as Figure 2 and 3 As shown, the tube body 501 includes an open end 507 and a sealed end 508. The first chamber 503 and the second chamber 504 are connected on the side near the sealed end 508. The first chamber 503 is connected to the opening of the open end 507, and the end of the second chamber 504 near the open end 507 is not connected to the opening of the open end 507.

[0027] In this embodiment, the first flow path 3 and the second flow path 4 are also formed in the first plate 1 and the second plate 2 that are stacked and alternately stacked, thus the first flow path 3 and the second flow path 4 also present an alternating stacked situation, improving the heat exchange effect. Furthermore, a separator 502 is provided in the distributor 5 of the plate heat exchanger. The separator 5 is connected to the inner wall of the distributor 5, and the separator 502 divides the inner cavity of the distributor 5 into a first chamber 503 and a second chamber 504. The first chamber 503 and the second chamber 504 are interconnected. The open end 507 of the tube 501 is the inlet for introducing refrigerant into the distributor 5. This inlet is connected to the first chamber 503, while the second chamber 504 is not connected to this inlet. The second chamber 504 is closed at the inlet position, thus forming a "U"-shaped flow path. The first chamber 503 is connected to the first flow path 3 through the first hole 505, and the second chamber 504 is connected to the first flow path 3 through the second hole 506. When refrigerant is introduced into distributor 5, it first enters the first chamber 503. The refrigerant flows from the open end 507 of pipe 501 towards the sealed end 508. As it passes through the first chamber 503, the amount of refrigerant distributed to each of the first flow paths 3 through the first hole 505 exhibits a linear increasing trend. Figure 3 Curve Q1; subsequently, refrigerant flows from the first chamber 503 into the second chamber 504. At this time, the flow direction of the refrigerant is opposite to that entering the first chamber 503, flowing from the sealed end 508 of the tube 501 towards the open end 507. The refrigerant is redistributed to each of the first flow paths 3 through the second hole 506. During the flow from the sealed end 508 to the open end 507, the amount of refrigerant distributed to each of the first flow paths 3 also shows a linear increasing trend, such as... Figure 3 The curve Q2 in the figure; the U-shaped flow path makes the refrigerant distribution more uniform. Even if there is a non-uniform trend of linear growth when the refrigerant flows through the first chamber 503, the refrigerant forms a linear growth trend that is opposite to that in the first chamber 503 when it flows through the second chamber 504. The two opposite growth trends complement each other, thus making the refrigerant distribution more uniform.

[0028] In this configuration, at least one first hole 505 is connected to at least one first flow path 3, and at least one second hole 506 is connected to at least one first flow path 3.

[0029] In practical applications, it is necessary to ensure that each layer of the first flow path 3 is connected to the first chamber 503, and each layer of the first flow path 3 is also connected to the second chamber 504. This allows the refrigerant to enter the corresponding first flow path 3 layer sequentially through the corresponding first hole 505 and second hole 506 during its flow. This ensures that the opposite increasing trends in refrigerant distribution within the first chamber 503 and the second chamber 504 can compensate for each other. Connecting one of the first holes 505 to two or more layers of the first flow path 3 can achieve the same effect while reducing the number of openings.

[0030] like Figure 8 As shown, the plane perpendicular to the center line of the tube 501 is defined as the projection plane. The projected area of ​​the first chamber 503 on the projection plane is S1, and the projected area of ​​the second chamber 504 on the projection plane is S2. The range of S1 / S2 is: 1≤S1 / S2≤5.

[0031] In actual operation, because the first chamber 503 and the second chamber 504 are connected in a "U" shape, the refrigerant experiences a bending and buffering phase when entering the second chamber 504 from the first chamber 503. Therefore, the initial flow of the refrigerant into the first chamber 503 is greater than that into the second chamber 504, resulting in a higher pressure. Consequently, the flow area of ​​the first chamber 503 must be larger than, or at least equal to, the flow area of ​​the second chamber 504. This ensures equal pressure within both chambers, resulting in a consistent linear growth trend of the refrigerant as it is distributed through each of the first flow paths 3, guaranteeing uniform refrigerant distribution. Conversely, if the flow area of ​​the first chamber 503 is smaller, the pressure will also be higher due to the larger initial flow area, further hindering uniform refrigerant distribution.

[0032] The diameter of the first hole 505 and the second hole 506 is defined as d, where the range of d is: 0.1mm≤d≤5mm.

[0033] The diameters of the first hole 505 and the second hole 506 should not be too large. If the diameter is too large, the refrigerant will be distributed to each of the first flow paths 3 more quickly, which will cause uneven distribution of the gas and liquid refrigerant, as described in the related art. On the other hand, a smaller hole diameter will make it easier for the amount of gas and liquid refrigerant distributed from the first hole 505 and the second hole 506 to the first flow path 3 to be in a balanced state, and there will be no uneven distribution of gaseous and liquid phases in the gas and liquid refrigerant.

[0034] like Figure 4 and 5As shown, the direction of gravity of the plate heat exchanger is defined as the Y direction, the center line of the tube 501 is perpendicular to the Y direction, the angle between the axial direction of the first hole 505 and the Y direction is defined as θ, and the angle between the axial direction of the second hole 506 and the Y direction is defined as α; where θ ranges from 0 to 45°, and α ranges from 0 to 45°.

[0035] When refrigerant is introduced into distributor 5, due to gravity, the gaseous refrigerant will be above the liquid refrigerant in the direction of gravity. If the angle between the axial direction of the first orifice 505 and the Y-direction is opposite to the direction of gravity, the gaseous refrigerant will overflow first, resulting in uneven refrigerant distribution. However, when the angle between the axial direction of the first orifice 505 and the direction of gravity is approximately the same as the direction of gravity, the liquid refrigerant will be below the gaseous refrigerant due to gravity, and the liquid refrigerant will be closer to the first orifice 505 and the second orifice 506. As the refrigerant flows within pipe 501, the liquid refrigerant mixes with the gaseous refrigerant and is distributed from the first orifice 505 and the second orifice 506 into the first flow path 3, thereby improving the uniformity of distribution.

[0036] like Figure 1 and Figures 9 to 11As shown, the plate heat exchanger includes a first channel 6 and a second channel 7, with the distributor 5 at least partially located within the first channel 6. The first channel 6 includes a first corner hole 103 and a fifth corner hole 203, with the first corner hole 103 located on the first plate 1 and the fifth corner hole 203 located on the second plate 2. The second channel 7 communicates with the first flow path 3 and includes a second corner hole 104 and a sixth corner hole 204, with the second corner hole 104 located on the first plate 1 and the sixth corner hole 204 located on the second plate 2. The first bottom surface 102 includes a first annular protrusion 107, and the second top surface 201 includes a second annular protrusion 207. In adjacent plates, both the first annular protrusion 107 and the second annular protrusion 207 protrude towards the second flow path 4, and are sealed together. The outer circumference of both the first corner hole 103 and the second corner hole 104 is provided with... The outer circumference of the first annular protrusion 107, the fifth corner hole 203, and the sixth corner hole 204 are all provided with a second annular protrusion 207; the plate heat exchanger includes a third channel 8 and a fourth channel 9, both of which are connected to the second flow path 4. The third channel 8 includes a third corner hole 105 and a seventh corner hole 205, and the fourth channel 9 includes a fourth corner hole 106 and an eighth corner hole 206; the first top surface 101 includes a third annular protrusion 108, and the second bottom surface 202 includes a fourth annular protrusion 208. The third annular protrusion 108 and the fourth annular protrusion 208 are sealed together, and the third annular protrusion 108 and the fourth annular protrusion 208 extend at least partially into the first flow path 3; the outer circumference of the third corner hole 105 and the fourth corner hole 106 are all provided with a third annular protrusion 108, and the outer circumference of the seventh corner hole 205 and the eighth corner hole 206 are all provided with a fourth annular protrusion 208.

[0037] Multiple first corner holes 103 on the first plate 1 and multiple fifth corner holes 203 on the second plate 2 together constitute a part of the first channel 6; multiple second corner holes 104 on the first plate 1 and multiple sixth corner holes 204 on the second plate 2 together constitute a part of the second channel 7; similarly, multiple third corner holes 105 on the first plate 1 and multiple seventh corner holes 205 on the second plate 2 together constitute a part of the third channel 8; multiple fourth corner holes 106 on the first plate 1 and multiple eighth corner holes 206 on the second plate 2 together constitute a part of the fourth channel 9. During the refrigerant flow process, such as... Figure 2 As shown by the dashed arrows, the refrigerant is first introduced into the distributor 5 in the first channel 6, then enters the first flow path 3 of each layer through the first hole 505 and the second hole 506, and then flows out from the second channel 7. Simultaneously, another fluid medium is introduced from the third channel 8, then flows into the second flow path 4 of each layer, and then flows out from the fourth channel 9. This allows for heat exchange between the refrigerant and the fluid medium. The sealing connection between the first annular protrusion 107 and the second annular protrusion 207, and the sealing connection between the third annular protrusion 108 and the fourth annular protrusion 208, ensures that the first flow path 3 and the second flow path 4 are independent and closed, preventing the mixing of refrigerant and fluid medium.

[0038] like Figures 9 to 10 As shown, the first plate 1 includes a first abutting portion 10, and the second plate 2 includes a second abutting portion 11. The first abutting portion 10 and the second abutting portion 11 abut and seal. The first flow path 3 has a first heat exchange zone 301 and a second heat exchange zone 302. The first abutting portion 10 and the second abutting portion 11 separate the first heat exchange zone 301 and the second heat exchange zone 302. The first heat exchange zone 301 and the second heat exchange zone 302 are connected on the side away from the first channel 6. The second flow path 4 has a third heat exchange zone 401 and a fourth heat exchange zone 402. The first abutting portion 10 and the second abutting portion 11 separate the third heat exchange zone 401 and the fourth heat exchange zone 402. The third heat exchange zone 401 and the fourth heat exchange zone 402 are connected on the side close to the first channel 6.

[0039] To further improve the heat exchange effect between the refrigerant and the fluid medium, the first flow path 3 is divided into a first heat exchange zone 301 and a second heat exchange zone 302. When the refrigerant flows through the first flow path 3, it first flows through the second heat exchange zone 302, then through the first heat exchange zone 301, and then flows out through the second channel 7, thus forming a "U"-shaped flow path. The second flow path 4 is also divided into a third heat exchange zone 401 and a fourth heat exchange zone 402. After entering through the third channel 8, the fluid medium first flows into the fourth heat exchange zone 402, then flows from the fourth heat exchange zone 402 into the third heat exchange zone 401, and then flows out through the fourth channel 9, thus also forming a "U"-shaped flow path and improving the heat exchange effect.

[0040] like Figures 9 to 10 As shown, the first abutting portion 10 includes a first concave surface 1001 and a first convex surface 1002, with the first concave surface 1001 located on the first top surface 101 and the first convex surface 1002 located on the first bottom surface 102; the second abutting portion 11 includes a second concave surface 1101 and a second convex surface 1102, with the second concave surface 1101 located on the second top surface 201 and the second convex surface 1102 located on the second bottom surface 202; the first concave surface 1001 abuts against the second convex surface 1102 of the adjacent second plate 2, and the first convex surface 1002 abuts against the second top surface 201 of the adjacent second plate 2.

[0041] The first abutting part 10 includes a first groove 1003 and a second groove 1004, which are connected. In the length direction of the first plate 1, the second groove 1004 extends from the end of the first groove 1003 to the edge of the first plate 1. The second abutting part 11 includes a third groove 1103 and a fourth groove 1104, which are connected. In the length direction of the second plate 2, the fourth groove 1104 extends from the end of the third groove 1103 to the edge of the second plate 2. The second groove 1004 and the fourth groove 1104 extend in opposite directions, and the bottom wall of the first groove 1003 abuts against the bottom wall of the third groove 1103.

[0042] The first heat exchange zone 301 and the second heat exchange zone 302, as well as the third heat exchange zone 401 and the fourth heat exchange zone 402, are all separated by the first abutting part 10 and the second abutting part 11. When multiple first plates 1 and multiple second plates 2 are stacked alternately, the first convex surface 1002 of the first plate 1 abuts against the second top surface 201 of the second plate 2. The first concave surface 1001 and the first convex surface 1002 have the same shape, and the second concave surface 1101 and the second convex surface 1102 also have the same shape. The width of the first convex surface 1002 is greater than that of the second concave surface 1101. Therefore, when the first convex surface 1002 abuts against the second top surface 201, the first convex surface 1002 covers the second concave surface 1101. The second convex surface 1102 of the second plate 2 abuts against the first concave surface 1001 of another adjacent first plate 1.

[0043] The first concave surface 1001 and the first convex surface 1002 of the first plate 1, and the second concave surface 1101 and the second convex surface 1102 of the second plate 2 are formed by stamping, thereby forming grooves at the stamping positions. The first abutting portion 10 is stamped into a first groove 1003 and a second groove 1004, which are integrally stamped. The second abutting portion 11 is stamped into a third groove 1103 and a fourth groove 1104, which are also integrally stamped. This further facilitates the integration of the first heat exchange zone 301 and the second heat exchange zone 302 with the third heat exchange zone 304. Zone 401 and the fourth heat exchange zone 402 are separated into "U"-shaped flow paths. The bottom wall of the second groove 1004 abuts against the second top surface 201 of the adjacent second plate 2, and the bottom wall of the fourth groove 1104 abuts against the first top surface 101 of another adjacent first plate 1. The second groove 1004 extends to the edge of the first plate 1, and the fourth groove 1104 extends to the edge of the second plate 2. Thus, a refrigerant flow gap is left at the other end of the first groove 1003 in the first flow path 3, and a fluid medium flow gap is left at the other end of the third groove 1103 in the second flow path 4. This allows the refrigerant to form a flow path as described above. Figure 9 The flow path of line L1 in the middle, at the same time, causes the fluid medium to form as Figure 9 The flow path of line L2 in the middle.

[0044] To further improve the heat exchange effect, multiple protrusions can be stamped on the second plate 2. The protrusion direction of the protrusions is all towards the second flow path 4. As a result, when the fluid medium flows through the second flow path 4, it can form a tortuous flow path, which slows down the outflow time of the fluid medium. The protrusions also increase the heat exchange area between the fluid medium and the refrigerant, thereby improving the heat exchange effect.

[0045] The second tank 1004 and the fourth tank 1104 extend in opposite directions, so that the flow direction of the refrigerant in the first flow path 3 is opposite to that of the fluid medium in the second flow path 4, which also greatly improves the heat exchange effect.

[0046] The above embodiments are only used to illustrate this application and are not intended to limit the technical solutions described in this application. The understanding of this specification should be based on those skilled in the art. For example, directional descriptions such as "front", "back", "left", "right", "up", and "down" are only used to describe the relationship between objects and are not substantial limitations. "Multiple" means at least two or more.

[0047] Although this specification has described the present application in detail with reference to the above embodiments, those skilled in the art should understand that they can still make modifications or equivalent substitutions to the present application, and all technical solutions and improvements that do not depart from the spirit and scope of the present application should be covered within the scope of the claims of the present application.

Claims

1. A plate heat exchanger, characterized in that The plate heat exchanger comprises a plurality of first plates (1) and a plurality of second plates (2), the first plates (1) and the second plates (2) being alternately stacked along the thickness direction of the plate heat exchanger. Along the stacking direction of the first plates (1) and the second plates (2), the first plate (1) includes a first top surface (101) and a first bottom surface (102), and the second plate (2) includes a second top surface (201) and a second bottom surface (202). The plate heat exchanger has a first flow path (3) and a second flow path (4), the first flow path (3) being located between adjacent second bottom surfaces (202) and first top surfaces (101), and the second flow path (4) being located between adjacent first bottom surfaces (102) and second top surfaces (201). The plate heat exchanger includes a distributor (5), which includes a tube body (501) and a partition (502). The partition (502) is at least partially located inside the tube body (501) and is connected to the inner wall of the tube body (501). The distributor (5) has a first chamber (503) and a second chamber (504), which are located on opposite sides of the partition (502) and are in communication with each other. The tube body (501) has a plurality of first holes (505) and a plurality of second holes (506), the first holes (505) connecting the first flow path (3) and the first chamber (503), and the second holes (506) connecting the first flow path (3) and the second chamber (504).

2. The plate heat exchanger according to claim 1, characterized in that, The tube body (501) includes an open end (507) and a sealed end (508). The first chamber (503) and the second chamber (504) are connected on the side near the sealed end (508). The first chamber (503) is connected to the opening of the open end (507), and the end of the second chamber (504) near the open end (507) is not connected to the opening of the open end (507).

3. The plate heat exchanger according to claim 1, characterized in that, At least one of the first holes (505) is connected to at least one of the first flow paths (3), and at least one of the second holes (506) is connected to at least one of the first flow paths (3).

4. The plate heat exchanger according to claim 1, characterized in that The plane perpendicular to the center line of the tube (501) is defined as the projection plane. The projection area of ​​the first chamber (503) on the projection plane is S1, and the projection area of ​​the second chamber (504) on the projection plane is S2. The range of S1 / S2 is: 1≤S1 / S2≤5.

5. The plate heat exchanger according to claim 1, characterized in that, The diameter of the first hole (505) and the second hole (506) is defined as d, where the range of d is: 0.1mm≤d≤5mm.

6. The plate heat exchanger according to claim 1, characterized in that The direction of gravity of the plate heat exchanger is defined as the Y direction, the center line of the tube (501) is perpendicular to the Y direction, the angle between the axial direction of the first hole (505) and the Y direction is defined as θ, and the angle between the axial direction of the second hole (506) and the Y direction is defined as α; wherein, the range of θ is: 0 < θ ≤ 45°, and the range of α is: 0 < α ≤ 45°.

7. The plate heat exchanger according to claim 1, characterized in that The plate heat exchanger includes a first channel (6) and a second channel (7), and the distributor (5) is at least partially located in the first channel (6); the first channel (6) includes a first corner hole (103) and a fifth corner hole (203), the first corner hole (103) being located on the first plate (1) and the fifth corner hole (203) being located on the second plate (2); The second channel (7) is connected to the first flow path (3). The second channel (7) includes a second corner hole (104) and a sixth corner hole (204). The second corner hole (104) is located on the first plate (1), and the sixth corner hole (204) is located on the second plate (2). The first bottom surface (102) includes a first annular protrusion (107), and the second top surface (201) includes a second annular protrusion (207). In adjacent plates, the first annular protrusion (107) and the second annular protrusion (207) both protrude toward the second flow path (4), and the first annular protrusion (107) and the second annular protrusion (207) are sealed together. The outer circumference of the first corner hole (103) and the second corner hole (104) are provided with the first annular protrusion (107), and the outer circumference of the fifth corner hole (203) and the sixth corner hole (204) are provided with the second annular protrusion (207). The plate heat exchanger includes a third channel (8) and a fourth channel (9), both of which are connected to the second flow path (4). The third channel (8) includes a third corner hole (105) and a seventh corner hole (205), and the fourth channel (9) includes a fourth corner hole (106) and an eighth corner hole (206). The first top surface (101) includes a third annular protrusion (108), and the second bottom surface (202) includes a fourth annular protrusion (208). The third annular protrusion (108) and the fourth annular protrusion (208) are sealed together, and the third annular protrusion (108) and the fourth annular protrusion (208) extend at least partially into the first flow path (3). The outer circumference of the third corner hole (105) and the fourth corner hole (106) are provided with a third annular protrusion (108), and the outer circumference of the seventh corner hole (205) and the eighth corner hole (206) are provided with a fourth annular protrusion (208).

8. The plate heat exchanger according to claim 7, characterized in that The first plate (1) includes a first abutting part (10), and the second plate (2) includes a second abutting part (11). The first abutting part (10) and the second abutting part (11) abut and seal. The first flow path (3) has a first heat exchange zone (301) and a second heat exchange zone (302), the first contact portion (10) and the second contact portion (11) separate the first heat exchange zone (301) and the second heat exchange zone (302), and the first heat exchange zone (301) and the second heat exchange zone (302) are connected on the side away from the first channel (6); The second flow path (4) has a third heat exchange zone (401) and a fourth heat exchange zone (402), the first contact portion (10) and the second contact portion (11) separate the third heat exchange zone (401) and the fourth heat exchange zone (402), and the third heat exchange zone (401) and the fourth heat exchange zone (402) are connected on the side near the first channel (6).

9. The plate heat exchanger according to claim 8, characterized in that, The first abutting part (10) includes a first concave surface (1001) and a first convex surface (1002), the first concave surface (1001) being located on the first top surface (101) and the first convex surface (1002) being located on the first bottom surface (102); the second abutting part (11) includes a second concave surface (1101) and a second convex surface (1102), the second concave surface (1101) being located on the second top surface (201) and the second convex surface (1102) being located on the second bottom surface (202); The first concave surface (1001) abuts against the second convex surface (1102) of the adjacent second plate (2), and the first convex surface (1002) abuts against the second top surface (201) of the adjacent second plate (2).

10. The plate heat exchanger according to claim 9, characterized in that, The first abutting part (10) includes a first groove (1003) and a second groove (1004). The first groove (1003) communicates with the second groove (1004). In the length direction of the first plate (1), the second groove (1004) extends from the end of the first groove (1003) to the edge of the first plate (1). The second abutting part (11) includes a third groove (1103) and a fourth groove (1104), the third groove (1103) and the fourth groove (1104) are connected, and in the length direction of the second plate (2), the fourth groove (1104) extends from the end of the third groove (1103) to the edge of the second plate (2); The second groove (1004) extends in the opposite direction to the fourth groove (1104), and the bottom wall of the first groove (1003) abuts against the bottom wall of the third groove (1103).

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