Plate heat exchangers and units

Abstract

The present invention provides a plate heat exchanger and a unit, the plate heat exchanger including a first end plate, a heat exchange plate group, and a second end plate stacked in sequence along a first direction, a boss being provided on the second end plate, at least one of a first fluid inlet manifold channel, a second fluid inlet manifold channel, a first fluid outlet manifold channel, and a second fluid outlet manifold channel being opposite to the boss, the boss protruding from the surface of the second end plate toward the heat exchange plate group into the corresponding manifold channel; the highest point of the boss is higher than the lowest point of the last layer fluid channel; a flow gap is formed between the boss and the inner circumferential wall of the corresponding manifold channel, and the last layer fluid channel is connected with the corresponding manifold channel through the corresponding flow gap.

Description

Technical Field

[0001] The present invention relates to the technical field of plate heat exchangers, and in particular to a plate heat exchanger and a unit. Background Art

[0002] Plate heat exchangers are widely used in the heating, ventilation, air conditioning, and refrigeration industries due to their compactness and high heat transfer coefficient. The main structure of a plate heat exchanger consists of three parts: an upper end plate, a lower end plate, and heat exchange plates. The heat exchange plates form the heat exchange channel of the plate heat exchanger, while the upper and lower end plates seal the heat exchange channel. In actual use, when the plate heat exchanger operates under high pressure, the corner holes at the lower end plate may experience internal leakage due to excessive pressure, reducing the heat exchange efficiency of the plate heat exchanger and even directly causing damage to the unit.

[0003] At present, the main method used internationally is to weld reinforcement plates to enhance the pressure-bearing capacity of the corner holes of the lower end plate, thereby avoiding internal leakage of the plate heat exchanger. There is a reinforcement plate structure installed on the outside of the end plate. The main body of the structure is a rectangular plate. It is welded to the outside of the corner holes of the reinforcement plate by brazing, which can effectively improve the pressure-bearing capacity of the corner holes of the end plate. There is also a reinforcement plate structure installed on the inside of the end plate. The main structure is similar to the reinforcement plate welded on the outside of the end plate. The difference is that the reinforcement plate is welded to the inside of the end plate, which saves some materials. Therefore, the traditional method of avoiding leakage from the corner holes of the lower end plate requires additional materials for the plate heat exchanger, which increases the material cost. The reinforcement structure and the end plate need to be welded, which adds an extra process and reduces production efficiency. In addition, the traditional reinforcement structure can only play a reinforcing role and cannot adjust the flow distribution.

[0004] In addition, the flow distribution uniformity of plate heat exchangers has always been a concern in the industry. Uneven flow distribution will directly lead to a decrease in heat exchange capacity. In order to improve the uniformity of flow distribution, it is often necessary to design a flow distribution adjustment structure. There is currently a flow distribution adjustment structure installed at the refrigerant inlet. The main body of the structure is a round tube, and a spiral turbulent structure is installed inside to increase the disturbance of the fluid, thereby preventing gas-liquid stratification and avoiding serious uneven flow distribution. However, flow regulation through this structure requires additional consumables, and the processing of the flow regulating tube is complicated, which increases production costs. In addition, the traditional flow distribution adjustment structure can only realize flow regulation of the water side channel or the refrigerant side channel separately, and cannot adjust the flow on both sides at the same time. Summary of the Invention

[0005] The first object of the present invention is to provide a plate heat exchanger that can affect the internal flow field of the heat exchanger, thereby effectively improving the flow distribution uniformity of water and refrigerant, which has a significant effect on improving the performance of the heat exchanger. At the same time, it can also improve the pressure bearing capacity of the corner holes of the lower end plate without the need for additional consumables.

[0006] A second object of the present invention is to provide a unit using the above-mentioned plate heat exchanger.

[0007] To achieve the above-mentioned first object, the present invention provides a plate heat exchanger, comprising a first end plate, a heat exchange plate group, and a second end plate stacked in sequence along a first direction, the heat exchange plate group comprising a plurality of heat exchange plates stacked in sequence along the first direction; a first fluid channel and a second fluid channel are formed between adjacent heat exchange plates, and fluid isolation between them is formed; the heat exchange plate group is provided with a first fluid inlet manifold channel, a first fluid outlet manifold channel, a second fluid inlet manifold channel, and a second fluid outlet manifold channel, all of which pass through the heat exchange plate group along the first direction, and the first fluid inlet manifold channel and the first fluid outlet manifold channel are both connected to the heat exchange plate group. The first fluid channel is connected, and the second fluid inlet manifold channel and the second fluid outlet manifold channel are both connected to the second fluid channel; a boss is provided on the second end plate, and at least one of the first fluid inlet manifold channel, the second fluid inlet manifold channel, the first fluid outlet manifold channel and the second fluid outlet manifold channel is opposite to the boss, and the boss protrudes from the surface of the second end plate toward the heat exchange plate group into the corresponding manifold channel; the highest point of the boss is higher than the lowest point of the last layer fluid channel; a flow gap is formed between the boss and the inner circumferential wall of the corresponding manifold channel, and the last layer fluid channel is connected to the corresponding manifold channel through the corresponding flow gap.

[0008] As can be seen from the above solution, by providing a boss on the second end plate that extends into the manifold channel and forming a flow gap between the boss and the inner circumferential wall of the manifold channel, the final fluid channel is prevented from being blocked. By occupying a portion of the flow area of ​​the manifold channel, the flow rate at that location is reduced, altering the overall pressure distribution of the manifold channel and significantly improving the uniformity of the flow distribution. This improved flow and pressure distribution not only enhances the overall heat exchange performance of the plate heat exchanger, but also reduces the pressure in the final channel, thereby reducing the pressure at the corner holes of the lower end plate and lowering the risk of internal leakage in the plate heat exchanger. Furthermore, the boss improves the compressive strength of the second end plate relative to the manifold channel. Compared to the existing flat surface of the lower end plate, the arc-shaped boss has better mechanical properties and can withstand greater pressure, effectively preventing internal leakage at the corner holes due to excessive pressure, thus resolving the leakage problem at the corner holes of the lower end plate of existing plate heat exchangers. Furthermore, the boss design eliminates the need for end plate gaskets during sealing, thereby reducing consumables, shortening production processes, and lowering costs. Compared with the existing solution of using welding reinforcement plates to enhance the pressure-bearing capacity of the corner holes of the lower end plate, the present invention reduces costs and production processes by setting a boss without the need for additional consumables, thereby improving production efficiency.

[0009] A preferred solution is that when the boss is located at the first fluid inlet manifold channel, the last layer of fluid channel is the first fluid channel farthest from the first end plate; when the boss is located at the second fluid inlet manifold channel, the last layer of fluid channel is the second fluid channel farthest from the first end plate; when the boss is located at the first fluid outlet manifold channel, the last layer of fluid channel is the first fluid channel farthest from the first end plate; when the boss is located at the second fluid outlet manifold channel, the last layer of fluid channel is the second fluid channel farthest from the first end plate.

[0010] A preferred solution is that the highest point of the boss is not higher than the highest point of the fluid channel of the last layer.

[0011] It can be seen from this that if the boss is too high, it is easy to damage the boss structure during stamping, resulting in leakage problems.

[0012] A preferred solution is that the boss is in the shape of a body of revolution, the axis of the boss is perpendicular to the second end plate, and the generatrix of the boss is a straight line segment or a curved line segment.

[0013] A further solution is that the cross-sectional radius of the boss gradually decreases from the lowest point of the boss to the highest point of the boss.

[0014] A further solution is that the boss is in the shape of a cone, a cylinder or a spherical crown.

[0015] A preferred solution is that the boss is interference fit with the corner hole of the heat exchange plate closest to the second end plate.

[0016] This shows that the sealing between the boss and the heat exchange plate is guaranteed.

[0017] A preferred solution is that the boss and the second end plate are stamped integrally.

[0018] As can be seen, the boss and the second end plate are integrally formed through stamping. Compared to the traditional lower end plate structure, this integrally formed curved protrusion effectively disperses pressure, allowing the plates at the corner holes to withstand greater pressure and significantly reducing the risk of leakage. Furthermore, because this structure is integrated with the lower end plate, it eliminates the need for additional reinforcement plates or other structures, eliminating the need for additional consumables, welding, or processing and assembly steps. This significantly reduces the production cost of the plate heat exchanger and improves production efficiency.

[0019] A preferred solution is that the first end plate is provided with a first fluid inlet, a first fluid outlet, a second fluid inlet and a second fluid outlet, the first fluid inlet is opposite to and connected with the first fluid inlet collection pipe channel, the first fluid outlet is opposite to and connected with the first fluid outlet collection pipe channel, the second fluid inlet is opposite to and connected with the second fluid inlet collection pipe channel, and the second fluid outlet is opposite to and connected with the second fluid outlet collection pipe channel.

[0020] To achieve the second objective, the present invention provides a unit having the plate heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a three-dimensional diagram of the first embodiment of the plate heat exchanger of the present invention.

[0022] Figure 2 1 is a top view of a first embodiment of a plate heat exchanger according to the present invention.

[0023] Figure 3 yes Figure 2 Cross-section at AA in the middle.

[0024] Figure 4 yes Figure 3 A partial enlarged view of point D in the middle.

[0025] Figure 5 yes Figure 3 A partial enlarged view of point E in the middle.

[0026] Figure 6 yes Figure 2 Cross-section at BB.

[0027] Figure 7 yes Figure 6 A partial enlarged view of point J in the middle.

[0028] Figure 8 yes Figure 6 A local enlarged view of point K in the middle.

[0029] Figure 9 yes Figure 2 Cross-sectional view at CC.

[0030] Figure 10 It is a structural diagram of the second end plate in the first embodiment of the plate heat exchanger of the present invention.

[0031] Figure 11 It is a cross-sectional view of an existing plate heat exchanger.

[0032] Figure 12 It is a flow distribution curve diagram of the present invention and the existing 16-channel plate heat exchanger.

[0033] Figure 13 It is a partial cross-sectional view of the second end plate in the second embodiment of the plate heat exchanger of the present invention.

[0034] Figure 14 It is a partial cross-sectional view of the second end plate in the third embodiment of the plate heat exchanger of the present invention.

[0035] Figure 15 It is a partial cross-sectional view of the second end plate in the fourth embodiment of the plate heat exchanger of the present invention.

[0036] Figure 16 It is a structural diagram of the second end plate in other embodiments of the plate heat exchanger of the present invention.

[0037] The present invention will be further described below with reference to the accompanying drawings and embodiments. DETAILED DESCRIPTION

[0038] Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the present invention, its application, or use. The present invention can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present invention thorough and complete and to fully convey the scope of the present invention to those skilled in the art. It should be noted that unless otherwise specifically stated, the relative arrangement of components and steps, the composition of materials, numerical expressions, and numerical values ​​set forth in these embodiments should be interpreted as being merely exemplary and not as limiting.

[0039] The terms "first," "second," and similar terms used in this disclosure do not indicate any order, quantity, or importance, but are simply used to distinguish different parts. Terms such as "include" or "comprising" mean that the elements preceding the term include the elements listed after the term, and do not exclude the possibility of also including other elements. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships. When the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0040] In the present invention, when a specific device is described as being located between a first device and a second device, an intervening device may or may not be present between the specific device and the first device or the second device. When a specific device is described as being connected to another device, the specific device may be directly connected to the other device without an intervening device, or may be directly connected to the other device but with an intervening device.

[0041] All terms (including technical or scientific terms) used in the present invention have the same meaning as those understood by ordinary technicians in the field, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having the meaning consistent with their meaning in the context of the relevant technology, and should not be interpreted in an idealized or extremely formal sense, unless explicitly defined herein.

[0042] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered part of the specification.

[0043] Plate heat exchanger and unit first embodiment:

[0044] See also Figures 1 to 10 The unit of this embodiment is an air source heat pump water heater. The air source heat pump water heater includes a plate heat exchanger.

[0045] The plate heat exchanger comprises a first end plate 1, a heat exchange plate group 2 and a second end plate 3 stacked in sequence along a first direction. Figure 3 The vertical direction in .

[0046] The heat exchange plate group 2 includes a plurality of heat exchange plates 20 stacked in sequence along a first direction, and an annular gasket 4 is provided between two adjacent heat exchange plates 20, so that a first fluid channel 21 and a second fluid channel 22 that are fluidically isolated from each other are formed between the adjacent heat exchange plates 20. The fluids are isolated from each other, that is, they are not connected. The first fluid flows in the first fluid channel 21, and the second fluid flows in the second fluid channel 22. The two perform heat exchange through the heat exchange plates 20. The first fluid channel 21 and the second fluid channel 22 are alternately arranged in sequence along the first direction. In this embodiment, the first fluid is a refrigerant and the second fluid is water.

[0047] The heat exchange plate assembly 2 is provided with a first fluid inlet manifold channel 23, a first fluid outlet manifold channel 24, a second fluid inlet manifold channel 25, and a second fluid outlet manifold channel 26, all of which extend through the heat exchange plate assembly 2 in a first direction. The first fluid inlet manifold channel 23 and the first fluid outlet manifold channel 24 are both in communication with the first fluid channel 21, while the second fluid inlet manifold channel 25 and the second fluid outlet manifold channel 26 are both in communication with the second fluid channel 22. The first fluid inlet manifold channel 23 is used to distribute refrigerant into each of the first fluid channels 21, the first fluid outlet manifold channel 24 is used to collect refrigerant from each of the first fluid channels 21, the second fluid inlet manifold channel 25 is used to distribute water into each of the second fluid channels 22, and the second fluid outlet manifold channel 26 is used to collect water from each of the second fluid channels 22.

[0048] The first end plate 1 is provided with a first fluid inlet 11, a first fluid outlet 12, a second fluid inlet 13 and a second fluid outlet 14. The first fluid inlet 11 is opposite to and connected with the first fluid inlet manifold channel 23, the first fluid outlet 12 is opposite to and connected with the first fluid outlet manifold channel 24, the second fluid inlet 13 is opposite to and connected with the second fluid inlet manifold channel 25, and the second fluid outlet 14 is opposite to and connected with the second fluid outlet manifold channel 26.

[0049] The second end plate 3 is provided with a first boss 31, a second boss 32, a third boss 33, and a fourth boss 34. Each of these four bosses is stamped integrally with the second end plate 3. The bosses and the second end plate 3 are formed integrally through stamping. Compared to conventional lower end plate structures, this integrally formed curved protrusion effectively disperses pressure, allowing the plates at the corner holes to withstand greater pressure and significantly reducing the risk of leakage. Furthermore, because this structure is integral with the lower end plate, it eliminates the need for additional reinforcement plates or other structures. This eliminates the need for additional consumables, welding, or machining and assembly processes, significantly reducing the production cost of the plate heat exchanger and improving production efficiency.

[0050] The first boss 31 faces the first fluid inlet manifold channel 23, the second boss 32 faces the first fluid outlet manifold channel 24, the third boss 33 faces the second fluid inlet manifold channel 25, and the fourth boss 34 faces the second fluid outlet manifold channel 26. All four bosses project from the surface of the second end plate 3 toward the heat exchange plate assembly 2 into the corresponding manifold channels. The highest point of each boss is higher than the lowest point of the last layer of fluid channels, but not higher than the highest point of the last layer of fluid channels. That is, the highest point of each boss is at the same height as or lower than the highest point of the last layer of fluid channels. When the boss is located at first fluid inlet manifold channel 23, the last fluid channel is first fluid channel 21, farthest from first end plate 1. When the boss is located at second fluid inlet manifold channel 25, the last fluid channel is second fluid channel 22, farthest from first end plate 1. That is, the highest points of first boss 31 and second boss 32 are both higher than the lowest points of first fluid channel 21, farthest from first end plate 1. The highest points of third boss 33 and fourth boss 34 are both higher than the lowest points of second fluid channel 22, farthest from first end plate 1. By adjusting the height of each boss, the boss is ensured to be located within the corresponding manifold channel without completely blocking the last fluid channel.

[0051] A first flow gap 35 is formed between the first boss 31 and the inner circumferential wall of the first fluid inlet manifold channel 23, through which the corresponding last-layer fluid channels communicate with the first fluid inlet manifold channel 23. A second flow gap 36 is formed between the second boss 32 and the inner circumferential wall of the first fluid outlet manifold channel 24, through which the corresponding last-layer fluid channels communicate with the first fluid outlet manifold channel 24. A third flow gap 37 is formed between the third boss 33 and the inner circumferential wall of the second fluid inlet manifold channel 25, through which the corresponding last-layer fluid channels communicate with the second fluid inlet manifold channel 25. A fourth flow gap 38 is formed between the fourth boss 34 and the inner circumferential wall of the second fluid outlet manifold channel 26, through which the corresponding last-layer fluid channels communicate with the second fluid outlet manifold channel 26.

[0052] Each boss is a body of revolution, meaning its cross-section is circular. The boss axis is perpendicular to the second end plate 3 and coaxial with the corresponding fluid inlet. The busbar is a straight or curved segment. In this embodiment, the cross-sectional radius of the boss gradually decreases from its lowest point to its highest point. The radius of the bottom circular cross-section of each of the four bosses is slightly larger than the radius of the corresponding corner holes. This ensures that, after assembly, the four bosses have an interference fit with the corresponding corner holes on the heat exchange plate 20 closest to the second end plate 3. When the heat exchange plates 20 are stacked, the corner holes on the heat exchange plates 20 form corresponding manifold channels. In this embodiment, the first and second bosses 31, 32 have the same shape and size, and the third and fourth bosses 33, 34 have the same shape and size. The height of the first and second bosses 31, 32 is higher than the height of the third and fourth bosses 33, 34.

[0053] See also Figures 3 to 5 In this embodiment, the first boss 31 and the second boss 32 each include a first step 311 and a second step 312 arranged along a first direction. The first step 311 protrudes upward from the surface of the second end plate 3, and the second step 312 protrudes upward from the inner circumference of the first step 311. The first step 311 is an annular column, and the second step 312 is cylindrical. The highest point is located on the upper surface of the second step 312. After the first boss 31 and the second boss 32 are assembled with the heat exchange plate assembly 2, the corner holes of the bottommost heat exchange plate 20 are sleeved outside the second step 312 and have an interference fit with the outer circumference of the second step 312. The bottommost heat exchange plate 20 is adjacent to the upper surface of the first step 311. One of the annular gaskets 4 surrounds the outside of the second step 312. The penultimate heat exchange plate 20 is lower than the upper surface of the second step 312.

[0054] See also Figures 6 to 8 In this embodiment, both the third and fourth bosses 33 and 34 include a third step 331 and a fourth step 332 arranged along the first direction. The third step 331 protrudes upward from the surface of the second end plate 3, while the fourth step 332 protrudes upward from the inner circumference of the third step 331. The third step 331 is an annular frustum, while the fourth step 332 is frustum. The highest point is located on the upper surface of the fourth step 332. After the third and fourth steps 331 and 332 are assembled with the heat exchange plate assembly 2, the corner holes of the bottommost heat exchange plate 20 are sleeved on the fourth step 332 and form an interference fit with the outer circumference of the fourth step 332. In the first direction, the heat exchange plate 20 is located in the middle of the fourth step 332.

[0055] The lower surface of the bottommost heat exchange plate 20, the upper surface of the second end plate 3, the outer peripheral surface of the first step 311, the outer peripheral surface and top surface of the third step 331, and the outer peripheral surface of the fourth step form a solder filling space 39 for filling with pure copper solder to achieve sealing of the plate heat exchanger through high-temperature brazing.

[0056] Figure 11 The figure shows a conventional lower end plate 51 with a flat surface facing the central heat exchange plate assembly 52, without a boss. Instead, a solid end plate gasket 53 is used to seal the corresponding manifold channel 54. This sealing method requires additional consumables and assembly steps, making it uneconomical. Furthermore, the conventional lower end plate 51 is flat, has limited pressure-bearing capacity, and is prone to deformation under high-pressure conditions. Furthermore, the conventional solid end plate gasket 5 only supports the central heat exchange plate assembly 52 and does not affect the internal flow.

[0057] The second end plate 3 of the present invention does not require a solid end plate gasket for sealing, saving material and simplifying the assembly process. Furthermore, the arc-shaped boss has a stronger pressure-bearing capacity, effectively preventing internal leakage. It also influences flow distribution, thereby improving flow distribution uniformity. By varying the height of the boss, different flow distribution effects can be achieved. The height of the boss can be set as needed in actual use.

[0058] Under high-flow conditions, fluid tends to be distributed in the last few fluid channels, which can easily lead to high pressure on the second end plate 3. By using the boss to improve flow distribution, the flow in the last few fluid channels will be reduced, thereby reducing the pressure on the second end plate 3 and significantly reducing the risk of leakage.

[0059] Figure 12 The flow distribution curves for a 16-channel plate heat exchanger with the existing lower end plate structure (i.e., the original heat exchanger) and a 16-channel plate heat exchanger equipped with the curved raised structure of the lower end plate designed according to the present invention (i.e., the heat exchanger with the lower end plate raised structure) are shown. As can be seen, the addition of the curved raised structure reduces the flow rates in channels 1-5 and the last channel, while increasing the flow rates in channels 6-15. The overall distribution becomes smoother, and flow distribution becomes more uniform.

[0060] The overall standard deviation of flow distribution is usually used to evaluate the uniformity of flow distribution. The calculation formula is as follows:

[0061]

[0062] Where, N is the number of channels; m ch, i It is i Channel flow rate; m ave is the average flow rate of each channel.

[0063] The smaller the overall standard deviation of the flow distribution, the more uniform the flow distribution. According to calculations, compared with the original heat exchanger, the heat exchanger with the arc-shaped convex structure on the lower end plate has a larger overall standard deviation of the flow distribution. The flow distribution uniformity was significantly improved by reducing the convex structure from 0.56 to 0.49. Therefore, by extending the protrusion into the manifold channel, the flow distribution was regulated to a certain extent, which improved the flow distribution uniformity. This not only increased the heat transfer capacity of the heat exchanger, but also improved the overall pressure distribution and significantly reduced the risk of internal leakage near the corner holes.

[0064] As can be seen above, by providing a boss on the second end plate that extends into the manifold channel and forming a flow gap between the boss and the inner circumferential wall of the manifold channel, the last layer of fluid channels is prevented from being blocked. By occupying a portion of the flow area of ​​the manifold channel, the flow rate at that location is reduced, changing the overall pressure distribution of the manifold channel, and significantly improving the uniformity of the flow distribution. This improvement in flow and pressure distribution not only enhances the overall heat exchange performance of the plate heat exchanger, but also reduces the pressure in the last channel, thereby reducing the pressure at the corner holes of the lower end plate and lowering the risk of internal leakage in the plate heat exchanger. Furthermore, the boss improves the compressive strength of the second end plate relative to the manifold channel. Compared to the existing flat surface of the lower end plate, the arc-shaped boss has better mechanical properties and can withstand greater pressure. This effectively prevents internal leakage at the corner holes due to excessive pressure, thus solving the leakage problem at the corner holes of the lower end plate of the existing plate heat exchanger. Furthermore, the boss design eliminates the need for end plate gaskets during sealing, thereby reducing consumables, reducing production steps, and lowering costs. Compared with the existing solution of using welding reinforcement plates to enhance the pressure-bearing capacity of the corner holes of the lower end plate, the present invention reduces costs and production processes by setting a boss without the need for additional consumables, thereby improving production efficiency.

[0065] The second embodiment of the heat exchange plate:

[0066] As an explanation of the second embodiment of the heat exchange plate of the present invention, only the differences from the first embodiment of the heat exchange plate described above are described below.

[0067] See also Figure 13 In this embodiment, the boss 230 is conical.

[0068] The third embodiment of the heat exchange plate:

[0069] As an explanation of the third embodiment of the heat exchange plate of the present invention, only the differences from the first embodiment of the heat exchange plate described above are described below.

[0070] See also Figure 14 In this embodiment, the boss 330 is cylindrical.

[0071] The fourth embodiment of the heat exchange plate:

[0072] As an explanation of the fourth embodiment of the heat exchange plate of the present invention, only the differences from the third embodiment of the heat exchange plate described above are described below.

[0073] See also Figure 15 In this embodiment, the boss 430 is in the shape of a spherical crown.

[0074] Other embodiments of heat exchange plates:

[0075] In other embodiments, the boss may be provided on only at least one of the first fluid inlet manifold channel, the second fluid inlet manifold channel, the first fluid outlet manifold channel, and the second fluid outlet manifold channel. For example, the boss may be provided on only one of the first fluid inlet manifold channel and the second fluid inlet manifold channel, and the boss may be opposite to the boss. The boss may be provided on at least one of the first fluid outlet manifold channel and the second fluid outlet manifold channel, or both of the first fluid outlet manifold channel and the boss may be provided only on the inlet manifold channel.

[0076] For example, Figure 16 As shown, the boss 530 may be provided only on the second fluid inlet manifold channel and the second fluid outlet manifold channel, while no boss is provided on the first fluid inlet manifold channel and the first fluid outlet manifold channel. Alternatively, the boss may be provided only on the first fluid inlet manifold channel and the first fluid outlet manifold channel, while no boss is provided on the second fluid inlet manifold channel and the second fluid outlet manifold channel.

[0077] In addition, the highest point of the boss may be no lower than the highest point of the last layer of fluid channels, and the highest point of the boss may be no higher than the highest point of the last two layers of fluid channels, which are the second most distant fluid channels from the fluid communication port connector. The above changes can also achieve the purpose of the present invention.

[0078] Finally, it should be emphasized that the above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various changes and modifications. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A plate heat exchanger comprising a first end plate, a heat exchange plate group, and a second end plate stacked sequentially along a first direction, wherein the heat exchange plate group comprises a plurality of heat exchange plates stacked sequentially along the first direction; A first fluid channel and a second fluid channel that are fluidically isolated from each other are formed between adjacent heat exchange plates; The heat exchange plate group is provided with a first fluid inlet manifold channel, a first fluid outlet manifold channel, a second fluid inlet manifold channel, and a second fluid outlet manifold channel, all of which pass through the heat exchange plate group along the first direction; the first fluid inlet manifold channel and the first fluid outlet manifold channel are both connected to the first fluid channel, and the second fluid inlet manifold channel and the second fluid outlet manifold channel are both connected to the second fluid channel; Its characteristics are: A boss is provided on the second end plate, at least one of the first fluid inlet header channel, the second fluid inlet header channel, the first fluid outlet header channel, and the second fluid outlet header channel is opposite to the boss, and the boss protrudes from the surface of the second end plate toward the heat exchange plate assembly into the corresponding header channel; The highest point of the boss is higher than the lowest point of the last layer of fluid channel; A flow gap is formed between the boss and the inner peripheral wall of the corresponding manifold channel, and the last layer fluid channel is connected to the corresponding manifold channel through the corresponding flow gap; When the boss is located at the first fluid inlet manifold channel, the last layer of fluid channels is the first fluid channel farthest from the first end plate; When the boss is located at the second fluid inlet manifold channel, the last layer of fluid channels is the second fluid channel farthest from the first end plate; When the boss is located at the first fluid outlet manifold channel, the last layer of fluid channels is the first fluid channel farthest from the first end plate; When the boss is located at the second fluid outlet manifold channel, the last layer of fluid channels is the second fluid channel farthest from the first end plate.

2. The plate heat exchanger according to claim 1, characterized in that: The highest point of the boss is no higher than the highest point of the last layer fluid channel.

3. The plate heat exchanger according to claim 1, characterized in that: The boss is in the shape of a body of revolution.

4. The plate heat exchanger according to claim 3, characterized in that: The cross-sectional radius of the boss gradually decreases from the lowest point of the boss to the highest point of the boss.

5. The plate heat exchanger according to claim 3, characterized in that: The boss is in the shape of a cone, a cylinder or a spherical crown.

6. The plate heat exchanger according to any one of claims 1 to 5, characterized in that: The boss is interference-fitted with a corner hole of the heat exchange plate closest to the second end plate.

7. The plate heat exchanger according to any one of claims 1 to 5, characterized in that: The boss and the second end plate are integrally stamped and formed.

8. The plate heat exchanger according to any one of claims 1 to 5, characterized in that: A first fluid inlet, a first fluid outlet, a second fluid inlet, and a second fluid outlet are provided on the first end plate. The first fluid inlet is opposite to and communicated with the first fluid inlet manifold channel, the first fluid outlet is opposite to and communicated with the first fluid outlet manifold channel, the second fluid inlet is opposite to and communicated with the second fluid inlet manifold channel, and the second fluid outlet is opposite to and communicated with the second fluid outlet manifold channel.

9. The unit is characterized in that: The method comprises the plate heat exchanger according to any one of claims 1 to 8.

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