Plate heat exchanger

Abstract

The application provides a plate heat exchanger, comprising a plurality of first plates and a plurality of second plates, the first plates and the second plates each comprising two long edges, one of the two long edges being a first long edge and the other being a second long edge, the first plates and the second plates each having a first corner hole, the first corner hole being closer to the first long edge than to the second long edge; the first plates having first plate corrugations, the first plate corrugations comprising a first corrugation close to the first corner hole, the first corrugation at least partially having a first corrugation section, a first intermediate corrugation section and a second corrugation section, the first corrugation section extending obliquely towards the first long edge, the second corrugation section extending obliquely towards the second long edge, the first corrugation section and the second corrugation section forming a first included angle, the first intermediate corrugation section having a first corrugation angle, and the angle of the first included angle being smaller than the angle of the first corrugation angle. The first corrugation close to the two long edges has a bending structure, thereby improving the strength of the plate heat exchanger.

Description

Technical Field

[0001] This application belongs to the field of heat exchangers, and specifically relates to a plate heat exchanger. Background Technology

[0002] Plate heat exchangers are widely used in refrigeration and heating systems as evaporators, condensers, economizers, etc., due to their advantages such as compact structure, high heat transfer coefficient, high reliability, and low refrigerant charge.

[0003] Plate heat exchangers have herringbone patterns on their plates. The area where the corner holes are located needs to withstand high pressure. However, in related technologies, the herringbone pattern on the plates is consistent, and there are fewer welding points for the corrugations of adjacent plates in the area where the corner holes are located. This results in low strength and poor pressure resistance of the plate heat exchanger in the corner hole area, making it prone to fluid leakage during application. On the other hand, arranging more corrugations in the corner hole area will affect the fluid distribution and heat exchange performance at the corner holes. Summary of the Invention

[0004] To address the aforementioned problems, this application aims to provide a plate heat exchanger that can improve strength.

[0005] This application provides a plate heat exchanger, including a plurality of first plates and a plurality of second plates, which are alternately stacked along the thickness direction of the plate heat exchanger; each of the first and second plates includes two long sides, which extend along the length direction of the plate heat exchanger, one of which is a first long side and the other is a second long side; both the first and second plates have a first corner hole, which is closer to the first long side than the second long side;

[0006] The first plate has a first plate corrugation, the first plate corrugation includes a first corrugation near the first corner hole, the first corrugation at least partially has a first corrugated segment, a first intermediate corrugated segment and a second corrugated segment, the first intermediate corrugated segment connects the first corrugated segment and the second corrugated segment, the first corrugated segment extends obliquely toward the first long side, the second corrugated segment extends obliquely toward the second long side, the first corrugated segment and the second corrugated segment form a first included angle, the first intermediate corrugated segment has a first corrugation angle, the angle of the first included angle is smaller than the angle of the first corrugation angle.

[0007] The plate heat exchanger provided in this application has a first corrugated section, a first intermediate corrugated section and a second corrugated section near the first corner hole. The first included angle formed by the first corrugated section and the second corrugated section is smaller than the first corrugated angle of the first intermediate corrugated section. This makes the corrugated sections near the two long sides of the first corrugation have a bent structure, which extends the corrugation length and helps to increase the number of contact points between adjacent plates, thereby improving the strength of the plate heat exchanger. Attached Figure Description

[0008] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0009] Figure 1 A perspective view of a plate heat exchanger provided in an embodiment of this application;

[0010] Figure 2 An exploded view of a plate heat exchanger provided in an embodiment of this application;

[0011] Figure 3 A partial structural diagram of a plate heat exchanger provided in an embodiment of this application;

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

[0013] Figure 5 This is a front view of the second plate in the embodiments of this application;

[0014] Figure 6 for Figure 4 Enlarged view of the structure of section A in the middle circle;

[0015] Figure 7 for Figure 5 Enlarged view of the structure of section B in the middle circle;

[0016] Figure 8 This is a structural diagram of a plate heat exchanger with a network-like corrugation provided in the embodiments of this application;

[0017] Figure 9 This is a structural diagram showing a first protrusion between the third corrugation and the adjacent first corrugation segment in an embodiment of this application;

[0018] Figure 10 This is an exploded view of the back of the first plate and the adjacent second plate in this embodiment;

[0019] Figure 11 This is a structural diagram of the first connecting part in this embodiment;

[0020] Figure 12 This is an exploded view of the front of the first plate and the adjacent second plate in this embodiment;

[0021] Figure 13 This is an exploded view of the first and second plate corrugations in this embodiment. Detailed Implementation

[0022] 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.

[0023] 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.

[0024] like Figures 1 to 3 As shown, this embodiment provides a plate heat exchanger including multiple first plates 1 and multiple second plates 2, the multiple first plates 1 and multiple second plates 2 being arranged along the thickness direction of the plate heat exchanger (e.g., ...). Figure 2 The plates are alternately stacked (as shown in the TT direction); additionally, the plate heat exchanger has multiple first inter-plate channels 5 and multiple second inter-plate channels 6, which are alternately arranged along the thickness direction of the plate heat exchanger, and the first inter-plate channels 5 and the second inter-plate channels 6 are not interconnected. In this embodiment, the first inter-plate channel 5 is located between the front side of the first plate 1 and the back side of the adjacent second plate 2, and the second inter-plate channel 6 is located between the back side of the first plate 1 and the front side of the adjacent second plate 2.

[0025] Please see Figure 4 and Figure 5 and combined Figures 1 to 3 The first plate 1 and the second plate 2 each include two long sides 3, which are along the length of the plate heat exchanger (e.g., ...). Figure 2 , Figure 4 , Figure 5 Extending in the LL direction shown, one of the two long sides 3 is the first long side 3a, and the other is the second long side 3b. The first long side 3a and the second long side 3b are along the width direction of the plate heat exchanger (e.g., as shown in the figure). Figure 2 , Figure 4 , Figure 5 The plates 1 and 2 are arranged opposite each other (in the WW direction shown); both the first plate 1 and the second plate 2 have a first corner hole C1, which is closer to the first long side 3a than the second long side 3b. Both the first plate 1 and the second plate 2 include two short sides 4, which extend along the width direction of the plate heat exchanger. One of the two short sides 4 is the first short side 4a, and the other is the second short side 4b. The first short side 4a and the second short side 4b are arranged opposite each other along the length direction of the plate heat exchanger. The length of the long side 3 is greater than the length of the short side 4. The first corner hole C1 is closer to the first short side 4a than the second short side 4b. In other words, the first corner hole C1 is located at the corner formed by the first long side 3a and the first short side 4a.

[0026] In this embodiment, the length direction (LL direction), width direction (WW direction), and thickness direction (TT direction) of the plate heat exchanger are mutually perpendicular to each other.

[0027] In this embodiment, the first interplate channel 5 is used for the flow of refrigerant, the first corner hole C1 is used for the refrigerant to flow into the first interplate channel 5, and the second interplate channel 6 is used for the flow of heat exchange medium that exchanges heat with the refrigerant, such as water.

[0028] The first corner hole C1, serving as the refrigerant inlet, needs to withstand a certain pressure. Therefore, the fluid distribution area where the first corner hole C1 is located requires high pressure resistance. In related technologies, conventional herringbone corrugations are used. After adjacent plates are stacked and brazed, the ends of the corrugations (the ends near the plate edges) may not connect with the corrugations on adjacent plates, resulting in fewer weld points. This weakens the strength of the unconnected parts, leading to low pressure resistance and making the plates prone to desoldering, cracking, and fluid leakage during application. Furthermore, using more conventional herringbone corrugations (i.e., reducing the corrugation pitch) affects the fluid distribution performance at the corner hole and the overall heat exchange performance of the plate heat exchanger. Therefore, this embodiment adopts the following design:

[0029] Please refer to it again. Figure 4The first plate 1 has a first plate corrugation 10, and the second plate 2 has a second plate corrugation 20. In adjacent plates, the first plate corrugation 10 and the second plate corrugation 20 are arranged alternately, and the intersection of the crests and troughs of the corrugations is the welding surface. The first plate corrugation 10 includes a first corrugation 10a near the first corner hole C1. The first corrugation 10a has at least a first corrugated segment 10a1, a first intermediate corrugated segment 10a2, and a second corrugated segment 10a3. The first intermediate corrugated segment 10a2 connects the first corrugated segment 10a1 and the second corrugated segment 10a3. The first corrugated segment 10a1 extends obliquely toward the first long side 3a, and the second corrugated segment 10a3 extends obliquely toward the second long side 3b. The first corrugated segment 10a1 and the second corrugated segment 10a3 form a first included angle β1. The first intermediate corrugated segment 10a2 has a first corrugation angle α1, and the angle of the first included angle β1 is smaller than the angle of the first corrugation angle α1. In this embodiment, the first intermediate corrugated segment 10a2 is a herringbone wave, with the first included angle β1 and the first corrugation angle α1 both pointing towards the first short side 4a. The two ends of the first intermediate corrugated segment 10a2 extend obliquely towards the corresponding long side via the first corrugated segment 10a1 and the second corrugated segment 10a3, respectively. Furthermore, the angle β1 formed by the first corrugated segment 10a1 and the second corrugated segment 10a3 is smaller than the angle α1 of the first corrugation angle α1 of the first intermediate corrugated segment 10a2. In other words, the first corrugation 10a has a bent structure near the long side, forming a bend. This design, compared to conventional corrugations in related technologies, increases the extension length of the corrugation, allowing for more welding after mating with the adjacent second plate 2. This design increases the welding area of ​​adjacent plates in the fluid distribution zone where the first corner hole C1 is located, naturally improving the structural strength of the plate heat exchanger near the first corner hole C1. This, in turn, enhances the compressive strength of the plate heat exchanger at the first corner hole C1 location, reducing the probability of plate detachment, cracking, or fluid leakage due to pressure during application. Furthermore, the corrugated design at the distribution zone where the first corner hole C1 is located employs a bending design, eliminating the need for additional corrugations while simultaneously extending the corrugations. This extension allows for better fluid distribution of the refrigerant flowing into the first corner hole C1, contributing to improved fluid distribution and heat transfer performance at the first corner hole C1. In some embodiments, the first corrugation angle α1 is greater than or equal to 90°; the first included angle β1 is greater than or equal to 60° and less than the first corrugation angle α1, i.e., 60° ≤ β1 < α1.

[0030] Furthermore, both the first plate 1 and the second plate 2 have a second corner hole C2, which is positioned closer to the second short side 4b than the first short side 4a. In this embodiment, the second corner hole C2 serves as the inlet for the heat exchange medium that exchanges heat with the refrigerant, allowing the heat exchange medium to enter the second inter-plate channel 6. Therefore, the fluid distribution area where the second corner hole C2 is located also needs to have good pressure resistance and structural strength to improve the pressure resistance of the fluid distribution area of ​​the second corner hole C2 in the plate heat exchanger during application. To this end, this embodiment is designed as follows:

[0031] Please see Figure 5 and Figure 7The second plate corrugation 20 includes a second corrugation 20a near the second corner hole C2. The second corrugation 20a at least partially has a third corrugated segment 20a1, a second intermediate corrugated segment 20a2, and a fourth corrugated segment 20a3. The second intermediate corrugated segment 20a2 connects the third corrugated segment 20a1 and the fourth corrugated segment 20a3. The third corrugated segment 20a1 extends obliquely towards the second long side 3b, and the fourth corrugated segment 20a3 extends obliquely towards the first long side 3a. The third corrugated segment 20a1 and the fourth corrugated segment 20a3 form a second included angle β2. The second intermediate corrugated segment 20a2 has a second corrugation angle α2, and the angle of the second included angle β2 is smaller than the angle of the second corrugation angle α2. Specifically, the angle of the second included angle β2 is towards the second short side 4b; the angle of the second corrugation angle α2 is towards the second short side 4b. In this embodiment, the second intermediate corrugated segment 20a2 is a herringbone wave. Both ends of the second intermediate corrugated segment 20a2 extend obliquely towards their corresponding long sides via the third corrugated segment 20a1 and the fourth corrugated segment 20a3, respectively. Furthermore, the angle β2 formed by the third corrugated segment 20a1 and the fourth corrugated segment 20a3 is smaller than the angle α2 of the second corrugation. In other words, the second corrugation 20a has a bent structure at its end near the long side, forming a bend. Compared to conventional corrugations in related technologies, this design increases the extension length of the corrugation, allowing for more welding points after docking with the adjacent first plate 1, thereby increasing the welding points of the adjacent plate at the second corner hole C2. The welded area of ​​the fluid distribution zone naturally increases the structural strength of the plate heat exchanger near the second corner hole C2, thereby improving the compressive strength of the plate heat exchanger at the second corner hole C2 location. This reduces the probability of plate desoldering, cracking, and fluid leakage occurring at the distribution area where the second corner hole C2 is located during application. Furthermore, the corrugations in the fluid distribution zone where the second corner hole C2 is located adopt a bent design, eliminating the need for additional corrugations while extending the corrugations. This extension of the corrugations allows for better fluid distribution of the heat exchange medium flowing into the second corner hole C2, contributing to improved fluid distribution and heat exchange performance at the second corner hole C2. In some embodiments, the second corrugation angle α2 is greater than or equal to 90°; the second included angle β2 is greater than or equal to 60° and less than the second corrugation angle α2, i.e., 60°≤β2<α2.

[0032] In addition, the first corrugation angle α1 is less than or equal to 130° and the second corrugation angle α2 is less than or equal to 130° to ensure that the pressure drop is not too large and to ensure heat exchange performance.

[0033] In the above embodiments, after the first plate 1 and the second plate 2 are stacked, the corrugations 10 of the first plate and the corrugations 20 of the second plate form a network distribution, such as... Figure 8As shown, the network-like corrugations induce turbulence in the fluid at lower flow velocities, resulting in a higher surface heat transfer coefficient and improved heat exchange efficiency of the plate heat exchanger. Since the angular direction of the first plate corrugation 10 is opposite to that of the second plate corrugation 20, the angular direction of the second corrugation angle α2 is opposite to that of the first corrugation angle α1. Referring again to section 4, the first plate corrugation 10 also includes a third corrugation 10b. The third corrugation 10b and the first corrugation 10a are arranged adjacent to each other along the length of the plate heat exchanger. The third corrugation 10b has a third corrugation angle α3, and the angular direction of the third corrugation angle α3 is the same as that of the first corrugation angle α1. Please refer to 5 again. The second plate corrugation 20 includes a fourth corrugation 20b. The fourth corrugation 20b and the second corrugation 20a are arranged adjacent to each other along the length of the plate heat exchanger. The fourth corrugation 20b has a fourth corrugation angle α4. The angle of the fourth corrugation angle α4 is the same as the angle of the second corrugation angle α2.

[0034] In the above embodiment, after the first corrugation 10a is bent, a gap appears between the bent section of the first corrugation 10a and the adjacent third corrugation 10b. If the gap is too large, it will reduce the structural strength of that part. Therefore, please refer to... Figure 9 The first corrugated plate 10 further includes at least one first protrusion 10c, and the third corrugation 10b has a first protrusion 10c between it and at least one of the adjacent first corrugated segment 10a1 and the adjacent second corrugated segment 10a3. Figure 9 The diagram only shows the first protrusion 10c between the third corrugation 10b and the adjacent first corrugation segment 10a1; the case where the first protrusion 10c between the third corrugation 10b and the adjacent second corrugation segment 10a3 is not shown. By adding the first protrusion 10c, the problem of low structural strength at the junction of the bent section of the first corrugation 10a and the third corrugation 10b due to excessive gaps is avoided. Similarly, after the second corrugation 20a is bent, a gap appears between the second corrugation 20a and the adjacent fourth corrugation 20b. Excessive gaps will also reduce the structural strength of this part. Therefore, please refer to the diagram again. Figure 7 The second plate corrugation 20 further includes at least one second protrusion 20c, and the fourth corrugation 20b has a second protrusion 20c between it and at least one of the adjacent third corrugation segment 20a1 and the adjacent fourth corrugation segment 20a3. Figure 7 The diagram only shows the second protrusion 20c between the third corrugated segment 20a1 and the adjacent fourth corrugation 20b; the case where the second protrusion 20c is between the fourth corrugated segment 20a3 and the adjacent fourth corrugation 20b is not shown. By adding the second protrusion 20c, the problem of low structural strength at the junction of the bent section of the second corrugation 20a and the fourth corrugation 20b due to excessively large gaps is avoided.

[0035] To further enhance the pressure resistance and structural strength of the plate heat exchanger in the inlet region, this embodiment also features the following design: Please refer to... Figure 13 The third corrugation 10b includes a first main heat exchange corrugation 10b1 near the first corrugation 10a and a first secondary heat exchange corrugation 10b2 near the second short side 4b. The corrugation contact surface width of at least one of the first corrugation 10a and the first secondary heat exchange corrugation 10b2 is (e.g., Figure 13 The w1 shown is greater than the contact width of the first main heat exchange corrugation 10b1 (e.g., w1). Figure 13 (as shown in w2). Similarly, the fourth corrugation 20b includes a second main heat exchange corrugation 20b1 near the second corrugation 20a and a second secondary heat exchange corrugation 20b2 near the first short side 4a, wherein the corrugation contact width of at least one of the second corrugation 20a and the second secondary heat exchange corrugation 20b2 is (e.g., w2). Figure 13 The width of w3 shown is greater than the width of the contact surface of the second main heat exchange corrugation 20b1 (e.g., w3). Figure 13 (as shown in w4). By increasing the width of the corrugated contact surface in the distribution area where the first corner hole C1 and the second corner hole C2 are located, the welding area of ​​the corrugations is increased, thereby improving the welding strength and pressure resistance.

[0036] Please refer to it again. Figure 1 , Figures 3 to 5 Both the first plate 1 and the second plate 2 have a third corner hole C1 and a fourth corner hole C4. The first corner hole C1 and the third corner hole C3 are connected to the first inter-plate channel 5, and the second corner hole C2 and the fourth corner hole C4 are connected to the second inter-plate channel 6. The third corner hole C3 is used for refrigerant to flow out of the first inter-plate channel 5, and the fourth corner hole C4 is used for heat exchange medium to flow out of the second inter-plate channel 6. In some embodiments, the first corner hole C1 and the third corner hole C3 are diagonally distributed, and the second corner hole C2 and the fourth corner hole C4 are also diagonally distributed. In this case, the refrigerant and the heat exchange medium flow cross-currently during the application of the plate heat exchanger. In other embodiments, the first corner hole C1 and the third corner hole C3 are distributed along one of the long sides 3, and the second corner hole C2 and the fourth corner hole C4 are distributed along the other long side 3 (not shown in the figure). In this case, the refrigerant and the heat exchange medium flow parallel to each other during the application of the plate heat exchanger. In this embodiment, both the first plate 1 and the second plate 2 include rounded corner edges 7, and adjacent long edges 3 and short edges 4 are connected by rounded corner edges 7.

[0037] The plate heat exchanger provided in this application can be used as both an evaporator and a condenser. When used as an evaporator, the temperature at the refrigerant inlet side (i.e., at the first corner hole C1) is low, and the heat exchange medium flowing to the corresponding position of the refrigerant inlet is at high risk of freezing. Once freezing occurs, it can easily lead to volume expansion, causing the heat exchange plates in the frozen area to crack, tear, or break under stress, resulting in refrigerant bypassing to the heat exchange medium side and causing the plate heat exchanger to fail. To reduce or prevent freezing of the heat exchange medium at this location, this embodiment is designed as follows: Please refer to... Figure 10 The plate heat exchanger has a first connecting part 100, and a first corner hole C1 is located inside the first connecting part 100. The first connecting part 100 includes a first flat part 100a and a second flat part 100b. The first flat part 100a is located around the first corner hole C1 of the first plate 1, and the second flat part 100b is located around the first corner hole C1 of the second plate 2. That is, the first corner hole C1 is located inside the first connecting part 100, and the first corner hole C1 penetrates the first connecting part 100 along the thickness direction of the plate heat exchanger. Furthermore, the back side of the first flush-joint portion 100a is in contact with the front side of the adjacent second flush-joint portion 100b, and the first connecting portion 100 is in contact with the rounded corner edge 7 around the first corner hole C1. That is, at least one of the first flush-joint portion 100a and the second flush-joint portion 100b protrudes towards the second inter-plate channel 6, thus separating the first corner hole C1 from the second inter-plate channel 6. This ensures that during the application of the plate heat exchanger, the low-temperature refrigerant flowing in from the first corner hole C1 maintains a distance from the heat exchange medium in the second inter-plate channel 6, preventing the heat exchange medium in the second inter-plate channel 6 from freezing due to the low temperature of the refrigerant at the first corner hole C1. This effectively reduces the risk of freezing, helps improve the durability of the plate heat exchanger, and enhances its performance. Further details can be found in the following sections. Figure 11 The edge 8 is defined as the side adjacent to the second plate channel 6 where the first flat joint 100a and the second flat joint 100b meet. The minimum distance between the edge 8 and the first corner hole C1 is ≥3mm; for example, 3mm, 3.5mm, 4mm, 5mm, etc. This ensures the connection strength at this point. By limiting the minimum distance between the edge 8 and the edge of the first corner hole C1, the heat exchange medium in the second plate channel 6 is kept at a distance from the first corner hole C1, reducing the risk of freezing and improving the effectiveness of anti-freezing. It also ensures the connection strength of adjacent plates at the first corner hole C1, thereby improving the durability of the plate heat exchanger.

[0038] Furthermore, please refer to [the relevant document] again. Figure 11The two ends of edge 8 are connected to the first long side 3a and the first short side 4a of the periphery of the first corner hole C1, respectively. The point where edge 8 connects with the first long side 3a is defined as O1, and the point where edge 8 connects with the first short side 4a is defined as O2. The minimum distance from the point along the line from O1 to O2 on edge 8 to the first short side 4a decreases. This avoids the problem of stagnation in the area of ​​the second interplate channel 6 near the first corner hole C1. When the heat exchange medium in the second interplate channel 6 flows to edge 8, it can flow smoothly, reducing the residence time of the heat exchange medium. This reduces the risk of the heat exchange medium freezing due to the low temperature of the refrigerant flowing into the first corner hole C1.

[0039] In the following embodiments, the first corner hole C1 and the fourth corner hole C4 are distributed along the first short side 4a, and the first corner hole C1 and the second corner hole C2 are distributed diagonally opposite each other.

[0040] Because the fourth corner hole C4 is close to the first corner hole C1, and the first corner hole C1 serves as the refrigerant inlet, the temperature near it is low. If the heat exchange medium remains in this area for an extended period, there is a risk of freezing. Furthermore, the second plate channel 6, located at the corners around the fourth corner hole C4, has limited flow space, making it prone to slow flow or even stagnation, which can lead to freezing. This freezing expansion of the heat exchange medium in adjacent plates can cause problems such as plate detachment and cracking, ultimately resulting in plate heat exchanger failure. Therefore, this embodiment is designed as follows: Please refer again... Figure 10 The plate heat exchanger has a second connecting portion 200, which is located between the fourth corner hole C4 and the rounded edge 7 on the periphery of the fourth corner hole C4. The second connecting portion 200 includes a third flat connecting portion 200a and a fourth flat connecting portion 200b. The third flat connecting portion 200a is located on the periphery of the fourth corner hole C4 of the first plate 1, and the fourth flat connecting portion 200b is located on the periphery of the fourth corner hole C4 of the second plate 2. The back side of the third flat connecting portion 200a is in contact with the front side of the adjacent fourth flat connecting portion 200b, and the second connecting portion 200 is in contact with the rounded edge 7 on the periphery of the fourth corner hole C4. In other words, the second interplate channel 6 is sealed at the corner of the fourth corner hole C4 by the second connection part 200. In this way, the heat exchange medium in the second interplate channel 6 cannot enter the corner of the fourth corner hole C4, thereby reducing the risk of the heat exchange medium freezing due to stagnation and low temperature environment at the corner, and further improving the reliability and durability of the plate heat exchanger.

[0041] Furthermore, since the second corner hole C2 serves as the inlet for the heat exchange medium, if the second interplate channel 6 has a flow channel at the corner of the second corner hole C2, the heat exchange medium will enter through the second corner hole C2 first. Because this flow channel is located at the corner of the second corner hole C2, it is close and has low flow resistance, so it will enter the flow channel first. Then, the flow rate of the heat exchange medium closer to the second long side 3b is larger, while the flow rate closer to the first long side 3a is smaller, causing uneven fluid distribution. This results in the heat exchange medium not fully utilizing the heat exchange surface of the plates, affecting the heat exchange effect. Therefore, to improve the uniformity of heat exchange medium distribution, this embodiment is designed as follows: Please refer again. Figure 10 The plate heat exchanger has a third connecting part 300, which is located between the rounded corner edge 7 on the periphery of the second corner hole C2 and the second corner hole C2. The third connecting part 300 includes a fifth flat connecting part 300a and a sixth flat connecting part 300b. The fifth flat connecting part 300a is located on the periphery of the second corner hole C2 of the first plate 1, and the sixth flat connecting part 300b is located on the periphery of the second corner hole C2 of the second plate 2. The back side of the fifth flat connecting part 300a is in contact with the front side of the adjacent sixth flat connecting part 300b, and the third connecting part 300 is in contact with the rounded corner edge 7 on the periphery of the fourth corner hole C4. In other words, the second interplate channel 6 is sealed at the corner of the second corner hole C2 via the third connecting part 300. This prevents the heat exchange medium in the second interplate channel 6 from entering the corner of the second corner hole C2. After entering through the second corner hole C2, the sealed corner allows the heat exchange medium to flow more smoothly and evenly along the first long side 3a, away from the second corner hole C2. This results in a more uniform flow within the main heat exchange zone, fully utilizing the heat exchange surface of the plates to exchange heat with the refrigerant in the adjacent interplate channels, thus improving the heat exchange effect and enhancing the heat exchange performance of the plate heat exchanger. Furthermore, since the second corner hole C2 serves as the inlet for the heat exchange medium and needs to withstand a certain pressure, the sealed corner design effectively improves the connection strength of the plates at the location of the second corner hole C2, enhancing the pressure resistance of this area.

[0042] Furthermore, the third corner hole C3 and the first corner hole C1 are distributed along the first long side 3a. Therefore, the third corner hole C3 is relatively far from the first corner hole C1. The heat exchange medium in the second interplate channel 6 at the position corresponding to the third corner hole C3 is less affected by the low temperature of the refrigerant at the position of the first corner hole C1, and the risk of freezing is low. In order to increase the flow area of ​​the heat exchange medium, improve the uniformity of distribution, and enhance the heat exchange effect, this embodiment is designed as follows: Please refer to Figure 12The plate heat exchanger has a fourth connecting part 400, which is located between the third corner hole C3 and the rounded edge 7 on the periphery of the third corner hole C3. The fourth connecting part 400 includes a seventh flat connecting part 400a and an eighth flat connecting part 400b. The seventh flat connecting part 400a is located on the periphery of the third triangular hole C3 of the first plate 1, and the eighth flat connecting part 400b is located on the periphery of the third triangular hole C3 of the second plate 2. The back side of the seventh flat connecting part 400a and the front side of the eighth flat connecting part 400b are spaced apart, and the front side of the seventh flat connecting part 400a is in contact with the back side of the eighth flat connecting part 400b. The fourth connecting part 400 is in contact with the rounded edge 7 on the periphery of the third corner hole C3. In other words, the first inter-plate channel 5 is closed at the corner of the triangular hole C3, while the second inter-plate channel 6 is open at the corner of the triangular hole C3. Thus, when the heat exchange medium flows to the periphery of the third corner hole C3, some of the heat exchange medium can flow through the channel at the corner of the third corner hole C3 to the first long side 3a close to the first corner hole C1. This can further enhance the uniformity of heat exchange medium distribution, increase the flow area of ​​heat exchange medium, and improve heat exchange efficiency.

[0043] In the above embodiments, the first flat joint portion 100a, the third flat joint portion 200a, the fifth flat joint portion 300a, and the seventh flat joint portion 400a are all part of the first plate 1, that is, the first flat joint portion 100a, the third flat joint portion 200a, the fifth flat joint portion 300a, and the seventh flat joint portion 400a are pressed and formed during the processing of the first plate 1. Similarly, the second flat joint portion 100b, the fourth flat joint portion 200b, the sixth flat joint portion 300b, and the eighth flat joint portion 400b are all part of the second plate 2, that is, the second flat joint portion 100b, the fourth flat joint portion 200b, the sixth flat joint portion 300b, and the eighth flat joint portion 400b are pressed and formed during the processing of the second plate 2. At least one of the first flat joint portion 100a and the second flat joint portion 100b protrudes toward the second inter-plate channel 6, at least one of the third flat joint portion 200a and the fourth flat joint portion 200b protrudes toward the second inter-plate channel 6, at least one of the fifth flat joint portion 300a and the sixth flat joint portion 300b protrudes toward the second inter-plate channel 6, and at least one of the seventh flat joint portion 400a and the eighth flat joint portion 400b protrudes toward the first inter-plate channel 5.

[0044] In the above embodiments, a plane perpendicular to the thickness direction of the plate heat exchanger is defined as the projection plane. The projected area of ​​the first connecting portion 100 on the projection plane is greater than the projected area of ​​any one of the second connecting portion 200, the third connecting portion 300, and the fourth connecting portion 400 on the projection plane. In other words, the area of ​​the first connecting portion 100 at the first corner hole C1 is greater than the area of ​​the connecting portions at the other corner hole positions, ensuring that the second interplate channel 6 is spaced from the first corner hole C1, achieving the anti-freezing effect of the plate heat exchanger, improving the actual performance of the plate heat exchanger, and helping to extend the service life of the plate heat exchanger.

[0045] To achieve better heat transfer performance and reduce the pressure drop of the structure, one of the first plate corrugations and the second plate corrugations is asymmetrical, that is, the peaks of one of them are high and low, forming a single-sided asymmetrical channel structure (i.e., forming two inter-plate channels with different volumes). Without affecting the heat transfer performance, the pressure drop of the structure can be effectively reduced.

[0046] Some of the technical implementation methods described above can be combined or replaced.

[0047] The technical principles of this application have been described above in conjunction with specific embodiments. However, it should be noted that these descriptions are merely for explaining the principles of this application and should not be construed as limiting the scope of protection of this application in any way. Based on this explanation, other specific embodiments or equivalent substitutions of this application that can be conceived by those skilled in the art without creative effort will fall within the scope of protection of this application.

Claims

1. A plate heat exchanger, characterized in that: The plate heat exchanger comprises multiple first plates (1) and multiple second plates (2), which are stacked alternately along the thickness direction of the plate heat exchanger. Each of the first plates (1) and the second plates (2) includes two long sides (3), which extend along the length direction of the plate heat exchanger. One of the two long sides (3) is a first long side (3a) and the other is a second long side (3b). Each of the first plates (1) and the second plates (2) has a first corner hole (C1), which is closer to the first long side (3a) than the second long side (3b). The first plate (1) has a first plate corrugation (10), the first plate corrugation (10) includes a first corrugation (10a) near the first corner hole (C1), the first corrugation (10a) at least partially has a first corrugated segment (10a1), a first intermediate corrugated segment (10a2) and a second corrugated segment (10a3), the first intermediate corrugated segment (10a2) connects the first corrugated segment (10a1) and the second corrugated segment (10a3), the first corrugated segment (10a1) extends obliquely toward the first long side (3a), the second corrugated segment (10a3) extends obliquely toward the second long side (3b), the first corrugated segment (10a1) and the second corrugated segment (10a3) form a first included angle (β1), the first intermediate corrugated segment (10a2) has a first corrugated angle (α1), the angle of the first included angle (β1) is smaller than the angle of the first corrugated angle (α1).

2. The plate heat exchanger according to claim 1, characterized in that: The first long side (3a) and the second long side (3b) are arranged opposite each other along the width direction of the plate heat exchanger; The first plate (1) and the second plate (2) each include two short sides (4), which extend along the width direction of the plate heat exchanger. One of the two short sides (4) is the first short side (4a) and the other is the second short side (4b). The first short side (4a) and the second short side (4b) are arranged opposite to each other along the length direction of the plate heat exchanger. The length of the long side (3) is greater than the length of the short side (4). The first corner hole (C1) is positioned closer to the first short side (4a) than the second short side (4b); The angle of the first included angle (β1) is greater than or equal to 60°, and the angle of the first included angle (β1) is directed toward the first short side (4a). The angle of the first corrugation angle (α1) is greater than or equal to 90° and less than or equal to 130°; the angle of the first corrugation angle (α1) is directed toward the first short side (4a).

3. The plate heat exchanger according to claim 2, characterized in that: Both the first plate (1) and the second plate (2) have a second corner hole (C2), which is located closer to the second short side (4b) than the first short side (4a). The second plate (2) has a second plate corrugation (20), the second plate corrugation (20) includes a second corrugation (20a) near the second corner hole (C2), the second corrugation (20a) at least partially has a third corrugation segment (20a1), a second intermediate corrugation segment (20a2) and a fourth corrugation segment (20a3), the second intermediate corrugation segment (20a2) connects the third corrugation segment (20a1) and the fourth corrugation segment (20a3), the third corrugation segment (20a1) extends obliquely toward the second long side (3b), the fourth corrugation segment (20a3) extends obliquely toward the first long side (3a), the third corrugation segment (20a1) and the fourth corrugation segment (20a3) form a second included angle (β2), the second intermediate corrugation segment (20a2) has a second corrugation angle (α2), the angle of the second included angle (β2) is smaller than the angle of the second corrugation angle (α2); The angle of the second included angle (β2) is greater than or equal to 60°, and the angle of the second included angle (β2) is directed toward the second short side (4b). The second corrugation angle (α2) is greater than or equal to 90° and less than or equal to 130°; the angle of the second corrugation angle (α2) is directed toward the second short side (4b); The orientation of the second corrugation angle (α2) is opposite to that of the first corrugation angle (α1).

4. The plate heat exchanger according to claim 3, characterized in that: The first plate corrugation (10) includes a third corrugation (10b), the third corrugation (10b) and the first corrugation (10a) are arranged adjacent to each other along the length direction of the plate heat exchanger, the third corrugation (10b) has a third corrugation angle (α3), and the angle of the third corrugation angle (α3) is the same as the angle of the first corrugation angle (α1). The first plate corrugation (10) further includes at least one first protrusion (10c), and the third corrugation (10b) has the first protrusion (10c) between it and at least one of the adjacent first corrugation segment (10a1) and the adjacent second corrugation segment (10a3).

5. The plate heat exchanger according to claim 3, characterized in that: The second plate corrugation (20) includes a fourth corrugation (20b), the fourth corrugation (20b) and the second corrugation (20a) are arranged adjacent to each other along the length direction of the plate heat exchanger, the fourth corrugation (20b) has a fourth corrugation angle (α4), and the angle of the fourth corrugation angle (α4) is the same as the angle of the second corrugation angle (α2); The second plate corrugation (20) further includes at least one second protrusion (20c), and the fourth corrugation (20b) has the second protrusion (20c) between it and at least one of the adjacent third corrugation segment (20a1) and the adjacent fourth corrugation segment (20a3).

6. The plate heat exchanger according to claim 3, characterized in that: The first plate (1) and the second plate (2) both have a third corner hole (C3) and a fourth corner hole (C4). The plate heat exchanger has multiple first inter-plate channels (5) and multiple second inter-plate channels (6). The multiple first inter-plate channels (5) and multiple second inter-plate channels (6) are arranged alternately along the thickness direction of the plate heat exchanger. The first inter-plate channels (5) and the second inter-plate channels (6) are not interconnected. The first corner hole (C1) and the third corner hole (C3) are both connected to the first inter-plate channel (5), and the second corner hole (C2) and the fourth corner hole (C4) are both connected to the second inter-plate channel (6). The first inter-plate channel (5) is located between the front of the first plate (1) and the back of the adjacent second plate (2), and the second inter-plate channel (6) is located between the back of the first plate (1) and the front of the adjacent second plate (2). The first corner hole (C1) and the third corner hole (C3) are distributed diagonally opposite each other, or the first corner hole (C1) and the third corner hole (C3) are distributed along one of the long sides (3); The first plate (1) and the second plate (2) both include rounded corner edges (7), and adjacent long sides (3) and short sides (4) are connected by the rounded corner edges (7).

7. The plate heat exchanger according to claim 6, characterized in that: The plate heat exchanger has a first connecting part (100), and the first corner hole (C1) is located inside the first connecting part (100). The first connecting part (100) includes a first flat part (100a) and a second flat part (100b). The first flat part (100a) is located on the periphery of the first corner hole (C1) of the first plate (1), and the second flat part (100b) is located on the periphery of the first corner hole (C1) of the second plate (2). The back side of the first flat part (100a) is in contact with the front side of the adjacent second flat part (100b). The first connecting part (100) is in contact with the rounded corner edge (7) on the periphery of the first corner hole (C1). The side where the first flat part (100a) and the second flat part (100b) are in contact and adjacent to the second inter-plate channel (6) is defined as the edge (8). The minimum distance between the edge (8) and the first corner hole (C1) is ≥3mm. The two ends of the edge (8) are connected to the first long side (3a) and the first short side (4a) on the periphery of the first corner hole (C1), respectively. The point where the edge (8) connects with the first long side (3a) is defined as O1, and the point where the edge (8) connects with the first short side (4a) is defined as O2. The minimum distance from the point on the edge (8) along the line from O1 to O2 to the first short side (4a) decreases.

8. The plate heat exchanger according to claim 6, characterized in that: The plate heat exchanger has a second connecting part (200), which is located between the fourth corner hole (C4) and the rounded corner edge (7) around the fourth corner hole (C4); the second connecting part (200) includes a third flat part (200a) and a fourth flat part (200b), the third flat part (200a) is located around the fourth corner hole (C4) of the first plate (1), the fourth flat part (200b) is located around the fourth corner hole (C4) of the second plate (2), the back side of the third flat part (200a) is in contact with the front side of the adjacent fourth flat part (200b), and the second connecting part (200) is in contact with the rounded corner edge (7) around the fourth corner hole (C4); The plate heat exchanger has a third connecting part (300), which is located between the second corner hole (C2) and the rounded corner edge (7) on the periphery of the second corner hole (C2). The third connecting part (300) includes a fifth flat part (300a) and a sixth flat part (300b). The fifth flat part (300a) is located on the periphery of the second corner hole (C2) of the first plate (1), and the sixth flat part (300b) is located on the periphery of the second corner hole (C2) of the second plate (2). The back side of the fifth flat part (300a) is connected to the front side of the adjacent sixth flat part (300b), and the third connecting part (300) is connected to the rounded corner edge (7) on the periphery of the fourth corner hole (C4).

9. The plate heat exchanger according to claim 6, characterized in that: The plate heat exchanger has a fourth connecting part (400), which is located between the third corner hole (C3) and the rounded edge (7) around the third corner hole (C3). The fourth connecting part (400) includes a seventh flat part (400a) and an eighth flat part (400b). The seventh flat part (400a) is located around the third triangular hole (C3) of the first plate (1), and the eighth flat part (400b) is located around the third triangular hole (C3) of the second plate (2). The back side of the seventh flat part (400a) and the front side of the eighth flat part (400b) are spaced apart. The front side of the seventh flat part (400a) and the back side of the eighth flat part (400b) are connected. The fourth connecting part (400) is connected to the rounded edge (7) around the third corner hole (C3).

10. The plate heat exchanger according to claim 7, characterized in that: The third corrugation (10b) includes a first main heat exchange corrugation (10b1) near the first corrugation (10a) and a first secondary heat exchange corrugation (10b2) near the second short side (4b). The corrugation contact width of at least one of the first corrugation (10a) and the first secondary heat exchange corrugation (10b2) is greater than the contact width of the first main heat exchange corrugation (10b1). The fourth corrugation (20b) includes a second main heat exchange corrugation (20b1) near the second corrugation (20a) and a second secondary heat exchange corrugation (20b2) near the first short side (4a). The width of the corrugation interface of at least one of the second corrugation (20a) and the second secondary heat exchange corrugation (20b2) is greater than the width of the interface of the second main heat exchange corrugation (20b1).

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