Heat exchanger

Abstract

The application provides a heat exchanger, comprising: a core plate bundle, comprising a plurality of heat exchange plates arranged in a stack, each heat exchange plate is provided with a plurality of spaced heat exchange channels in the width direction of the core plate bundle, each heat exchange channel extends to the end of the heat exchange plate in the length direction of the core plate bundle, the heat exchange channels on two adjacent heat exchange plates are used for containing different heat exchange fluids respectively, and the flow directions of the heat exchange fluids are opposite; two end plates, respectively arranged on the opposite sides of the core plate bundle in the thickness direction; four fluid main pipes, the fluid main pipes are used for the heat exchange fluids to enter or leave the core plate bundle, each fluid main pipe is connected with a plurality of fluid branch pipes in the width direction, the fluid branch pipes connected with one fluid main pipe are in one-to-one correspondence with the heat exchange channels on the heat exchange plates containing the corresponding heat exchange fluids and are in communication. The heat exchanger provided by the application has the advantages of simple structure, convenient manufacturing, greatly improved heat exchange efficiency, uniform fluid distribution, good safety, long service life and the like.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat exchange, in particular to a heat exchanger. BACKGROUND

[0002] The heat exchanger is a device for transferring part of the heat of hot fluid to cold fluid, and plays an important role in chemical industry, petroleum industry, power industry, food industry and many other industrial productions. In recent years, the micro-channel heat exchanger (PCHE) has been paid more and more attention in the fields of petroleum and chemical industry, aerospace, nuclear power, hydrogen station, supercritical carbon dioxide power generation, and solar thermal power generation, because it has many advantages such as small volume, light weight, compact structure, high temperature and pressure resistance, and excellent heat exchange performance.

[0003] The plate of the micro-channel heat exchanger is generally etched by chemical etching technology, and a unit plate with millimeter-level channels is etched first, and then diffusion welding is used to connect each layer of etched plate to form a core channel. Since the core is formed by vacuum diffusion welding to form a heat exchanger, the welding quality between the plates is excellent, and the yield limit of the weld can reach more than 95% of the base material, so that the high pressure resistance is very outstanding, and the design pressure of some manufacturers has reached 100 MPa. The commonly used micro-channel heat exchanger has two main types of design structures, one is the design structure with a head outside the pipe box, and the other is the internal corner hole structure without a head and an external pipe box, but both have the defect of limited heat exchange effect. Therefore, a heat exchanger with better heat exchange effect is urgently needed. SUMMARY

[0004] Therefore, the purpose of the present application is to provide a heat exchanger to solve the problems mentioned in the background art.

[0005] In order to achieve the above purpose, the present application provides a heat exchanger, which comprises: a core plate bundle comprising a plurality of heat exchange plates stacked, each of the heat exchange plates is provided with a plurality of spaced heat exchange flow channels along the width direction of the core plate bundle, each of the heat exchange flow channels extends to the end of the heat exchange plate along the length direction of the core plate bundle, the heat exchange flow channels on adjacent two heat exchange plates are respectively used for containing different heat exchange fluids, and the flow directions of the heat exchange fluids are opposite; two end plates are respectively arranged on the opposite sides of the core plate bundle along the thickness direction thereof; four fluid main pipes are used for the heat exchange fluids to enter or leave the core plate bundle, each of the fluid main pipes is connected with a plurality of fluid branch pipes along the width direction, the fluid branch pipes connected with one of the fluid main pipes are arranged one by one corresponding to the heat exchange flow channels on the heat exchange plates containing the corresponding heat exchange fluid, each of the fluid branch pipes is connected with one of the end plates and only communicates with the end part of the corresponding heat exchange flow channel.

[0006] Furthermore, the heat exchange plate includes an overlapping first plate and a second plate. The heat exchange channel on the first plate is a first channel for containing a first fluid, and the heat exchange channel on the second plate is a second channel for containing a second fluid. The fluid manifold includes a first manifold and a second manifold. The fluid branch pipe connected to the first manifold is a first branch pipe for the first fluid to enter or leave the core plate bundle. Each first branch pipe connected to the first manifold is connected to a first channel on the first plate in a one-to-one correspondence. The fluid branch pipe connected to the second manifold is a second branch pipe for the second fluid to enter or leave the core plate bundle. Each second branch pipe connected to the second manifold is connected to a second channel on the second plate in a one-to-one correspondence.

[0007] Furthermore, each short side of the heat exchange plate is provided with a first connection hole group and a second connection hole group. The first connection hole group includes a plurality of first holes spaced apart along the width direction, and the first holes are used to connect the first branch pipe and the first flow channel. The second connection hole group includes a plurality of second holes spaced apart along the width direction, and the second holes are used to connect the second branch pipe and the second flow channel. The first holes and the second holes are staggered. In the first plate, the two ends of the first flow channel are respectively connected to the first holes one by one, and are spaced apart from the second holes. In the second plate, the two ends of the second flow channel are respectively connected to the second holes one by one, and are spaced apart from the first holes.

[0008] Furthermore, the first connection hole group and the second connection hole group are spaced apart along the length direction, the pressure of the first fluid is less than the pressure of the second fluid, and the first connection hole group is located between the short side of the heat exchange plate and the second connection hole group.

[0009] Furthermore, a first transition section is connected between the first hole and the first flow channel, and the width of the first transition section first decreases and then increases along the direction from the first hole to the first flow channel; a second transition section is connected between the second hole and the second flow channel, and the width of the second transition section gradually increases along the direction from the second hole to the second flow channel.

[0010] Furthermore, multiple flow dividers are spaced apart along the width direction within the heat exchange channel, and each flow divider extends along the length direction; a spacer is provided between adjacent heat exchange channels, and the spacer extends along the length direction.

[0011] Furthermore, the width of the spacer bar is greater than the width of the diversion bar.

[0012] Furthermore, the first transition section is provided with multiple guide blocks at intervals, and the guide blocks are spaced apart from the diverter bars; the second transition section is provided with multiple guide bars at intervals, and each guide bar is connected to the diverter bar in a one-to-one correspondence.

[0013] Furthermore, the thickness of the second plate is greater than the thickness of the first plate.

[0014] Furthermore, an integrated temperature and pressure sensor is provided at each of the first branch pipes corresponding to the point where the first fluid exits the core plate bundle.

[0015] As can be seen from the above description, the heat exchanger provided in this application includes: a core plate bundle, comprising multiple stacked heat exchange plates, each heat exchange plate having multiple spaced heat exchange channels along the width direction of the core plate bundle, each heat exchange channel extending to the end of the heat exchange plate along the length direction of the core plate bundle, the heat exchange channels on two adjacent heat exchange plates being used to accommodate different heat exchange fluids, and the flow directions of the heat exchange fluids being opposite; two end plates, respectively disposed on opposite sides of the core plate bundle along its thickness direction; and four fluid mains, the fluid mains being used for the heat exchange fluid to enter or leave the core plate bundle, each fluid main being connected to multiple fluid branch pipes along its width direction, the fluid branch pipes connected to a fluid main being configured one-to-one with the heat exchange channels on the heat exchange plates accommodating the corresponding heat exchange fluids, each fluid branch pipe being connected to an end plate and communicating only with the end of the corresponding heat exchange channel. By setting multiple independent flow channels along the length of each heat exchange plate and ensuring that the fluid flow directions of adjacent heat exchange plates are opposite, a pure counter-current heat exchange pattern can be formed, significantly improving the heat exchange effect. By connecting multiple fluid branch pipes to the corresponding heat exchange channels, a flow distribution effect can be ensured, improving the problem of uneven fluid distribution and further enhancing the heat exchange effect. Furthermore, independent monitoring of the heat exchange channels can be achieved subsequently, ensuring the safe operation of the heat exchanger. This heat exchanger has a simple structure, is easy to manufacture, greatly improves heat exchange efficiency, provides uniform fluid distribution, has good safety, and a long service life. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the 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.

[0017] Figure 1 This is a three-dimensional structural diagram of a heat exchanger according to an embodiment of this application.

[0018] Figure 2 for Figure 1 A schematic diagram of the cross-sectional structure of a heat exchanger.

[0019] Figure 3 This is an exploded structural diagram of the core plate bundle and end plate in the embodiments of this application.

[0020] Figure 4 This is a schematic diagram of the structure of the first plate in the embodiment of this application.

[0021] Figure 5 for Figure 4 An enlarged structural diagram of point A on the first plate.

[0022] Figure 6 for Figure 5 A schematic diagram of the cross-sectional structure of the first plate along the BB direction.

[0023] Figure 7 This is a schematic diagram of the structure of the second plate in the embodiment of this application.

[0024] Figure 8 for Figure 7 Enlarged structural diagram of point C on the second plate.

[0025] Figure 9 for Figure 8 A schematic diagram of the cross-sectional structure of the second plate along the DD direction.

[0026] Reference numerals in the attached drawings: 1. Core plate bundle; 2. Heat exchange plate; 2-1. First plate; 2-2. Second plate; 3. Heat exchange flow channel; 3-1. First flow channel; 3-2. Second flow channel; 3-3. First connecting hole group; 3-31. First hole; 3-4. Second connecting hole group; 3-41. Second hole; 3-5. First transition section; 3-6. Second transition section; 3-7. Flow divider; 3-8. Spacer; 3-9. Flow guide block; 3-10. Flow guide bar; 4. End plate; 4-1. Through hole; 5. Fluid main pipe; 5-1. First main pipe; 5-2. Second main pipe; 6. Fluid branch pipe; 6-1. First branch pipe; 6-2. Second branch pipe; 7. Integrated temperature and pressure sensor. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with specific embodiments and the accompanying drawings.

[0028] It should be noted that, unless otherwise defined, the technical or scientific terms used in the embodiments of this application should have the ordinary meaning understood by one of ordinary skill in the art to which this disclosure pertains. The terms "first," "second," and similar terms used in this disclosure do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Terms such as "comprising" or "including" mean that the element or object preceding the word encompasses the elements or objects listed following the word and their equivalents, without excluding other elements or objects. Terms such as "connected" or "linked" are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0029] Currently, there are two main types of overall design structures for commonly used microchannel heat exchangers: one is a design structure with an external tube box and a design structure without an external tube box and an internal corner hole structure.

[0030] The advantages of external tube box structures with end caps are high core area utilization and easy cleaning of some or all channels. The disadvantages are that the hot and cold fluids are generally partially counter-current or partially cross-flow, resulting in slightly poorer heat exchange performance. Furthermore, the larger the inlet, the more cross-flow occurs, and the more significant the impact on heat exchange performance. Additionally, the numerous welds between the end caps and core plates, as well as the upper and lower end plates, lead to high manufacturing costs and multiple stress concentration points, posing significant safety hazards. Therefore, these structures are rarely used in high-pressure applications such as hydrogen refueling stations.

[0031] For headless internal corner-hole structures, which are essentially built-in tube box designs, such as the typical four-corner-hole structure, the hot and cold fluids exchange heat in opposite directions through the corner holes. While this avoids the drawbacks of external tube box structures, such as multiple welds and stress concentration points, the four-corner-hole structure results in uneven fluid distribution within the flow channels due to the width of the tube box. Furthermore, the hot and cold flow channels exhibit partially counter-current or partially cross-flow heat exchange, affecting its heat transfer performance. In addition, the hot and cold side flow channels are a single, integral structure, with all channels connected to the same inlet and outlet corner holes, making leaks difficult to detect and repair. In high-pressure, flammable, and explosive applications such as hydrogen refueling stations, significant safety risks remain. Therefore, a heat exchanger that balances heat exchange efficiency and safety is urgently needed.

[0032] In the process of developing this application, it was discovered that the hot and cold side flow channels can be designed as purely counter-current channels. This changes the traditional pipe box and corner hole setup, allowing for the design of multiple independent flow channels and multiple inlets and outlets, reducing manufacturing difficulty and cost, and mitigating factors contributing to uneven fluid distribution. Furthermore, high and low pressure sides can be distinguished. Temperature and / or pressure sensors can be installed on each branch pipe at the low-pressure hot side outlet, dividing the hot and cold sides into multiple separate channels. If a leak occurs in any group of flow channels on the high-pressure cold side during operation, it can be detected and the channel closed promptly through monitoring and alarms, improving equipment safety and ensuring the heat exchanger can continue to be used after rapid repair, extending its service life. Simultaneously, the hot and cold side inlets and outlets can be located at both ends near the short side of the plate, allowing for purely counter-current heat exchange. Multiple inlets and outlets effectively improve the uniformity of fluid distribution, significantly increasing heat exchange efficiency, making the heat exchanger safer, more efficient, and more suitable for high-pressure, high-risk applications such as hydrogen refueling stations.

[0033] The following describes specific embodiments in conjunction with the appendix. Figures 1 to 9 The technical solution of this application will be further described in detail.

[0034] Some embodiments of this application provide a heat exchanger, such as Figures 1 to 3 As shown, it includes: a core plate bundle 1, comprising multiple stacked heat exchange plates 2, each heat exchange plate 2 having multiple spaced heat exchange channels 3 along the width direction of the core plate bundle 1, each heat exchange channel 3 extending along the length direction of the core plate bundle 1 to the end of the heat exchange plate 2, the heat exchange channels 3 on two adjacent heat exchange plates 2 respectively being used to accommodate different heat exchange fluids, and the flow directions of the heat exchange fluids being opposite; two end plates 4, respectively disposed on opposite sides of the core plate bundle 1 along its thickness direction; four fluid main pipes 5, the fluid main pipes 5 being used for the heat exchange fluid to enter or leave the core plate bundle 1, each fluid main pipe 5 being connected to multiple fluid branch pipes 6 along the width direction, the fluid branch pipes 6 connected to one fluid main pipe 5 being configured one-to-one with the heat exchange channels 3 on the heat exchange plate 2 accommodating the corresponding heat exchange fluid, each fluid branch pipe 6 being connected to one end plate 4 and communicating only with the end of the corresponding heat exchange channel 3.

[0035] like Figure 1 The diagram shows a schematic of a heat exchanger, which includes a core plate bundle 1, end plates 4, and a fluid manifold 5. The core plate bundle 1 is used for heat exchange, the end plates 4 are used to fix the core plate bundle 1, and the fluid manifold 5 allows different heat exchange fluids to enter or leave the core plate bundle 1 for heat exchange. In the diagram, the W direction represents the width of the core plate bundle 1, the L direction represents the length of the core plate bundle 1, and the T direction represents the thickness of the core plate bundle 1.

[0036] like Figure 2 andFigure 3 As shown, the core plate bundle 1 includes multiple heat exchange plates 2 stacked along the thickness direction, the shape of which is, for example, rectangular. Each heat exchange plate 2 has multiple spaced heat exchange channels 3 along the width direction, the number of which is, for example, 5, 10, or 20. Each heat exchange channel 3 extends along the length direction and extends to the ends of the heat exchange plate 2 to ensure effective heat exchange area. The heat exchange channels 3 on adjacent heat exchange plates 2 accommodate different heat exchange fluids, one cold-side fluid and one hot-side fluid, with the two heat exchange fluids flowing in opposite directions, thus forming a completely counter-current heat exchange mode, which greatly improves the heat exchange effect. In addition, the design of multiple heat exchange channels 3 also improves the uniformity of heat exchange fluid distribution, avoids local blockage or stagnation, and further improves the heat exchange effect.

[0037] like Figure 1 As shown, each fluid main 5 is connected to multiple fluid branch pipes 6 along its width. The number of fluid branch pipes 6 is equal to the number of heat exchange channels 3 on the corresponding heat exchange plate 2. Each fluid branch pipe 6 is connected to an end plate 4 and communicates with the end of the corresponding heat exchange channel 3 on the corresponding heat exchange plate 2. The multiple fluid branch pipes 6 are connected one-to-one with the heat exchange channels 3 on the heat exchange plate 2. That is, the fluid branch pipes 6 on the hot side are connected one-to-one with the heat exchange channels 3 on the hot side of the heat exchange plate 2, and the fluid branch pipes 6 on the cold side are connected one-to-one with the heat exchange channels 3 on the cold side of the heat exchange plate 2. This forms multiple independent heat exchange units. If any heat exchange unit fails, other heat exchange units can be used by sealing the inlet and outlet of that heat exchange unit, which facilitates maintenance and extends the service life of the equipment. Moreover, the manufacturing cost is lower, the safety is higher, and it is more suitable for high-pressure applications such as hydrogen refueling stations.

[0038] By setting multiple independent flow channels along the length of each heat exchange plate 2 and ensuring that the fluid flow directions of adjacent heat exchange plates 2 are opposite, a pure counter-current heat exchange pattern can be formed, significantly improving the heat exchange effect. By setting multiple fluid branch pipes 6 corresponding to the heat exchange channels 3, a flow distribution effect can be ensured, improving the problem of uneven fluid distribution and further enhancing the heat exchange effect. Furthermore, independent monitoring of the heat exchange channels 3 can be achieved subsequently, ensuring the safe operation of the heat exchanger. Compared to an external tube box structure, this heat exchanger is lighter, more compact, occupies less space, avoids stress concentration, and ensures that the heat exchange fluid undergoes pure counter-current heat exchange, resulting in high heat exchange efficiency. Compared to a four-corner hole structure, it improves the uniformity of fluid distribution and ensures that the heat exchange fluid undergoes pure counter-current heat exchange, thus improving heat exchange efficiency.

[0039] This heat exchanger has a simple structure, is easy to manufacture, greatly improves heat exchange efficiency, provides uniform fluid distribution, has good safety, and has a long service life.

[0040] In some embodiments, such as Figure 2 , Figure 3 ,Figure 4 and Figure 7 As shown, the heat exchange plate 2 includes a first plate 2-1 and a second plate 2-2 arranged in an overlapping manner. The heat exchange channel 3 on the first plate 2-1 is a first channel 3-1, which is used to contain a first fluid. The heat exchange channel 3 on the second plate 2-2 is a second channel 3-2, which is used to contain a second fluid. The fluid main pipe 5 includes a first main pipe 5-1 and a second main pipe 5-2. The fluid branch pipe 6 connected to the first main pipe 5-1 is a first branch pipe 6-1, which is used for the first fluid to enter or leave the core plate bundle 1. Each first branch pipe 6-1 connected to the first main pipe 5-1 is connected to a first channel 3-1 on the first plate 2-1. The fluid branch pipe 6 connected to the second main pipe 5-2 is a second branch pipe 6-2, which is used for the second fluid to enter or leave the core plate bundle 1. Each second branch pipe 6-2 connected to the second main pipe 5-2 is connected to a second channel 3-2 on the second plate 2-2.

[0041] like Figure 3 As shown, the heat exchange plate 2 includes multiple alternately stacked first plates 2-1 and second plates 2-2. The structure of the first plate 2-1 is as follows: Figure 4 As shown, multiple first flow channels 3-1 are provided, which are used to contain a first fluid, such as a hot-side fluid. The structure of the second plate 2-2 is as follows: Figure 7 As shown, multiple second flow channels 3-2 are provided, which are used to accommodate a second fluid, such as a cold-side fluid. The number of first flow channels 3-1 and second flow channels 3-2 can be equal or unequal; for example, the number of first flow channels 3-1 can be greater than the number of second flow channels 3-2, and the projected area of ​​the first flow channels 3-1 can cover the projected area of ​​the second flow channels 3-2 to ensure heat exchange efficiency. The first plate 2-1 and the second plate 2-2 can be connected by diffusion welding to form an integral core plate bundle 1.

[0042] like Figure 2 As shown, the fluid main pipe 5 includes two first main pipes 5-1 and two second main pipes 5-2. The two first main pipes 5-1 can be arranged on the same side or opposite sides, without any specific limitation. One first main pipe 5-1 is used for the input of the first fluid, and the other first main pipe 5-1 is used for the output of the first fluid. Each first main pipe 5-1 is welded (or connected by a high-pressure sealed thread) with multiple first branch pipes 6-1, and the first branch pipes 6-1 are connected one-to-one with the heat exchange channels 3 on the first plate 2-1.

[0043] The two second main pipes 5-2 can be set on the same side or opposite sides, and there is no specific limitation. One second main pipe 5-2 is used for the input of the second fluid, and the other second main pipe 5-2 is used for the output of the second fluid. Each second main pipe 5-2 has multiple second branch pipes 6-2 welded on (or connected by high-pressure sealed thread). The second branch pipes 6-2 are connected to the heat exchange channels 3 on the second plate 2-2 in a one-to-one correspondence.

[0044] The multi-fluid branch pipe design avoids the problems of significant flow deviation of heat exchange fluid between different heat exchange channels 3 of the plate due to distance, which leads to a decrease in heat exchanger performance, and the scaling and clogging problems caused by uneven distribution and local low flow velocity, as seen in the traditional four-corner hole design. The first branch pipe 6-1 and the second branch pipe 6-2 of the heat exchanger are arranged crosswise on the short sides of both sides of the heat exchange plate 2, ensuring that the hot and cold side heat exchange fluids can achieve complete counter-current heat exchange after entering each set of heat exchange channels 3. This not only guarantees the uniformity of fluid distribution but also significantly improves heat exchange performance.

[0045] In some embodiments, such as Figure 4 and Figure 7 As shown, each short side of the heat exchange plate 2 is provided with a first connecting hole group 3-3 and a second connecting hole group 3-4. The first connecting hole group 3-3 includes a plurality of first holes 3-31 spaced apart along the width direction, which are used to connect the first branch pipe 6-1 and the first flow channel 3-1. The second connecting hole group 3-4 includes a plurality of second holes 3-41 spaced apart along the width direction, which are used to connect the second branch pipe 6-2 and the second flow channel 3-2. The first holes 3-31 and the second holes 3-41 are staggered. In the first plate 2-1, the two ends of the first flow channel 3-1 are respectively connected to the first holes 3-31 one by one, and are spaced apart from the second holes 3-41. In the second plate 2-2, the two ends of the second flow channel 3-2 are respectively connected to the second holes 3-41 one by one, and are spaced apart from the first holes 3-31.

[0046] like Figure 3 As shown, the end plate 4 is provided with through holes 4-1 to facilitate the welding of the first branch pipe 6-1 and the second branch pipe 6-2. Each side end plate 4 can be provided with two sets of through holes 4-1 to realize the connection of four sets of fluid branch pipes 6.

[0047] like Figure 4 and Figure 7 As shown, a first set of connecting holes 3-3 and a second set of connecting holes 3-4 are provided at each short side of the heat exchange plate 2, that is, each heat exchange plate 2 is provided with two sets of first connecting holes and two sets of second connecting holes 3-4, and the connecting hole groups on the first plate 2-1 and the connecting hole groups on the second plate 2-2 are completely corresponding.

[0048] Each group of first connecting holes 3-3 includes multiple first holes 3-31, the number of which is equal to the number of first flow channels 3-1. These holes can connect to the first branch pipe 6-1 and the first flow channel 3-1, serving as the inlet and outlet of the first fluid. Each group of second connecting holes 3-4 includes multiple second holes 3-41, the number of which is equal to the number of second flow channels 3-2. These holes can connect to the second branch pipe 6-2 and the second flow channel 3-2, serving as the inlet and outlet of the second fluid.

[0049] The shapes of the first hole 3-31 and the second hole 3-41 are, for example, circular, rectangular, or arched, etc., and are not specifically limited. The first hole 3-31 and the second hole 3-41 are staggered, and the first flow channel 3-1 on the first plate 2-1 is only connected to the first hole 3-31, and the second flow channel 3-2 on the second plate 2-2 is only connected to the second hole 3-41. This can avoid interfering with the connection of the first branch pipe 6-1 or the second branch pipe 6-2, and avoid obstructing the flow of fluid.

[0050] In some embodiments, such as Figure 4 and Figure 7 As shown, the first connecting hole group 3-3 and the second connecting hole group 3-4 are spaced apart along the length direction. The pressure of the first fluid is less than the pressure of the second fluid. The first connecting hole group 3-3 is located between the short side of the heat exchange plate 2 and the second connecting hole group 3-4.

[0051] like Figure 4 and Figure 7 As shown, the first connecting hole group 3-3 and the second connecting hole group 3-4 are spaced apart along the length direction. This allows for a larger area of ​​the first hole 3-31 and the second hole 3-41, ensuring flow rate and reducing resistance. It also avoids interference between the first branch pipe 6-1 and the second branch pipe 6-2. While improving the utilization rate of the plate, it can also ensure the strength of the plate and reduce the impact of the branch pipe connection load. It also facilitates the welding connection between the end plate 4 and the fluid branch pipe 6.

[0052] The pressures of the first fluid and the second fluid can be equal or unequal. When the working pressure of the first fluid is less than that of the second fluid, the first connecting hole group 3-3 can be located between the short side of the heat exchange plate 2 and the second connecting hole group 3-4, that is, the first connecting hole group 3-3 surrounds the second connecting hole group 3-4. This allows the low-pressure side to be set on the outside and the high-pressure side to be set on the inside, ensuring sealing and heat exchange effects. Moreover, since the first flow channel 3-1 avoids the second hole 3-41, a necking structure can be set. This allows the first connecting hole group 3-3 to be set on the outside, avoiding excessive local resistance and ensuring safe operation.

[0053] In some embodiments, such as Figure 5 andFigure 8 As shown, a first transition section 3-5 connects the first hole 3-31 and the first flow channel 3-1. The width of the first transition section 3-5 first decreases and then increases along the direction from the first hole 3-31 to the first flow channel 3-1. A second transition section 3-6 connects the second hole 3-41 and the second flow channel 3-2. The width of the second transition section 3-6 gradually increases along the direction from the second hole 3-41 to the second flow channel 3-2.

[0054] like Figure 5 As shown, a first transition section 3-5 connects the first hole 3-31 and the first flow channel 3-1. The length of the first transition section 3-5 is, for example, 2 to 4 times the diameter of the first hole 3-31. The width of the first transition section 3-5 decreases and then increases from left to right. This facilitates increasing the area of ​​the second hole 3-41 while minimizing the impact on resistance, making the length of the narrowed section shorter and reducing frictional resistance.

[0055] like Figure 8 As shown, a second transition section 3-6 connects the second hole 3-41 and the second flow channel 3-2. The length of the second transition section 3-6 is, for example, 1 to 3 times the diameter of the second hole 3-41. The width of the second transition section 3-6 gradually increases from left to right, so that the second fluid enters the second flow channel 3-2 radially from the second hole 3-41, resulting in rapid and uniform fluid distribution.

[0056] In some embodiments, such as Figure 5 and Figure 8 As shown, multiple flow dividers 3-7 are spaced apart along the width direction in the heat exchange channel 3, and each flow divider 3-7 extends along the length direction; spacers 3-8 are provided between adjacent heat exchange channels 3, and the spacers 3-8 extend along the length direction.

[0057] like Figure 5 and Figure 8 As shown, each heat exchange channel 3 can also be provided with multiple flow dividers 3-7. The flow dividers 3-7 are, for example, ribs formed by etching, which can further subdivide the heat exchange channel 3 into multiple sub-channels along the width direction. Each sub-channel is set along the length direction and has an equal length. This can improve the design strength of the heat exchange channel 3 and ensure its safe operation under high pressure.

[0058] like Figure 5 and Figure 8 As shown, a spacer bar 3-8 is provided between adjacent heat exchange channels 3. The spacer bar 3-8 is, for example, a raised rib formed by etching. Its length can be equal to the length of the flow divider bar 3-7, which can separate different heat exchange channels 3 and avoid mutual interference.

[0059] In some embodiments, such asFigure 6 and Figure 9 As shown, the width of the spacer bar 3-8 is greater than the width of the diversion bar 3-7.

[0060] like Figure 6 and Figure 9 As shown, D1 is the width of the spacer bar 3-8, and D2 is the width of the flow divider bar 3-7. The width of the spacer bar 3-8 is greater than the width of the flow divider bar 3-7, for example, D1≤2D2. This can make the spacer bar 3-8 stronger, making it less likely for leaks to occur between different heat exchange channels 3. This avoids subsequent leakage failures that could cause liquid to cross into adjacent branch pipes, leading to misjudgments in monitoring, and also avoids insufficient heat exchange performance due to excessive blocking of failed branch pipes.

[0061] In some embodiments, such as Figure 5 and Figure 8 As shown, the first transition section 3-5 is provided with a plurality of guide blocks 3-9 at intervals, and the guide blocks 3-9 are provided with intervals from the diverter strips 3-7; the second transition section 3-6 is provided with a plurality of guide strips 3-10 at intervals, and each guide strip 3-10 is connected to the diverter strip 3-7 in a one-to-one correspondence.

[0062] like Figure 5 As shown, multiple short guide blocks 3-9 are spaced apart within the first transition section 3-5. These guide blocks 3-9, for example, are ribs formed by etching, and can be arranged in an array that varies with the width of the first transition section 3-5. Because the first hole 3-31 is located on the outer side, and the first transition section 3-5 has a necking structure, the resistance is relatively increased. By setting loosely spaced guide blocks 3-9, the flow can be evened out while mitigating the effect of reduced resistance. Here, the first hole 3-31 can be set as an arched structure. Compared to a circular structure, the edge width of the first hole 3-31 facing the first transition section 3-5 is larger, which helps to balance the resistance effect.

[0063] like Figure 8 As shown, the second transition section 3-6 is provided with multiple relatively long guide strips 3-10 at intervals. The guide strips 3-10 are, for example, ribs formed by etching. Each guide strip 3-10 is connected to the flow distribution strip 3-7 in a one-to-one correspondence to ensure the distribution of each channel. Here, the second hole 3-41 can be set as a circular structure, and the guide strips 3-10 are arranged radially, making the arc distribution line longer, which is more conducive to the distribution of multiple channels and ensures the flow uniformity effect.

[0064] In some embodiments, the thickness of the second plate 2-2 is greater than the thickness of the first plate 2-1.

[0065] The thickness of the second plate 2-2 is greater than the thickness of the first plate 2-1. For example, the thickness of the second plate 2-2 is set to be greater than or equal to twice the thickness of the first plate 2-1, so that the high-voltage side plate has higher strength and better pressure resistance.

[0066] In some embodiments, such as Figure 1 and Figure 2 As shown, a temperature and pressure integrated sensor 7 is provided at each of the first branch pipes 6-1 corresponding to the point where the first fluid leaves the core plate bundle 1.

[0067] like Figure 2 As shown, an integrated temperature and pressure sensor 7 can be installed at each heat exchange branch pipe at the outlet of the low-pressure side heat exchange fluid to monitor the temperature and pressure changes of the low-pressure fluid and evaluate the heat exchange effect. When failure occurs on the high-pressure side due to fatigue, stress, or corrosion, the temperature and pressure will change significantly. The corresponding fluid branch pipe 6 can be shut off to ensure the safety of the heat exchanger during real-time operation, facilitate maintenance, and extend the service life of the equipment. This solves the drawbacks of traditional tube box or four-corner hole structures where leaks cannot be detected and dealt with in a timely manner or where downtime for maintenance leads to production stoppages. The integrated temperature and pressure sensor 7 is not installed at the high-pressure side fluid because the temperature and pressure on the high-pressure side do not change significantly after a leak occurs, while the fluid on the high-pressure side will flow into the low-pressure side after a leak, causing a significant change in the temperature and pressure on the low-pressure side. In addition, a valve can also be installed on each fluid branch pipe 6 to facilitate the independent opening and closing of the corresponding heat exchange flow channel 3.

[0068] Those skilled in the art should understand that the discussion of any of the above embodiments is merely exemplary and is not intended to imply that the scope of this application (including the claims) is limited to these examples; under the concept of this application, the technical features of the above embodiments or different embodiments can also be combined, the steps can be implemented in any order, and there are many other variations of different aspects of the above embodiments of this application, which are not provided in detail for the sake of brevity.

[0069] Furthermore, given that details have been set forth to describe exemplary embodiments of this application, it will be apparent to those skilled in the art that embodiments of this application may be practiced without these details or with variations thereof. Therefore, these descriptions should be considered illustrative rather than restrictive.

[0070] Although this application has been described in conjunction with embodiments thereof, many substitutions, modifications and variations of these embodiments will be apparent to those skilled in the art from the foregoing description.

[0071] The embodiments of this application are intended to cover all such substitutions, modifications, and variations that fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the embodiments of this application should be included within the protection scope of this application.

Claims

1. A heat exchanger, characterized in that, include: The core plate bundle includes multiple stacked heat exchange plates. Each heat exchange plate has multiple spaced heat exchange channels along the width direction of the core plate bundle. Each heat exchange channel extends to the end of the heat exchange plate along the length direction of the core plate bundle. The heat exchange channels on two adjacent heat exchange plates are used to accommodate different heat exchange fluids, and the flow directions of the heat exchange fluids are opposite. Two end plates are respectively disposed on opposite sides of the core plate bundle along its thickness direction; Four fluid mains are provided for the heat exchange fluid to enter or leave the core plate bundle. Each fluid main is connected to multiple fluid branch pipes along the width direction. The fluid branch pipes connected to each fluid main are arranged one-to-one with the heat exchange channels on the heat exchange plate that contain the corresponding heat exchange fluid. Each fluid branch pipe is connected to an end plate and communicates only with the end of the corresponding heat exchange channel. The heat exchange plate includes a first plate and a second plate arranged in an overlapping manner. The heat exchange channel on the first plate is a first channel for containing a first fluid, and the heat exchange channel on the second plate is a second channel for containing a second fluid. Each short side of the heat exchange plate is provided with a first connection hole group and a second connection hole group. The first connection hole group includes a plurality of first holes spaced apart along the width direction, and the second connection hole group includes a plurality of second holes spaced apart along the width direction. The first and second connecting hole groups are spaced apart along the length direction. The pressure of the first fluid is less than the pressure of the second fluid. The first connecting hole group is located between the short side of the heat exchange plate and the second connecting hole group. A first transition section connects the first hole and the first flow channel. The width of the first transition section first decreases and then increases along the direction from the first hole to the first flow channel. The first connecting hole group surrounds the second connecting hole group. The first flow channel avoids the second hole by setting a necking structure.

2. The heat exchanger according to claim 1, characterized in that, The fluid main includes a first main and a second main. The fluid branch pipes connected to the first main are called first branch pipes. The first branch pipes are used for the first fluid to enter or leave the core plate bundle. Each first branch pipe connected to the first main is connected to a first flow channel on the first plate. The fluid branch pipes connected to the second main are called second branch pipes. The second branch pipes are used for the second fluid to enter or leave the core plate bundle. Each second branch pipe connected to the second main is connected to a second flow channel on the second plate.

3. The heat exchanger according to claim 2, characterized in that, The first hole is used to connect the first branch pipe and the first flow channel; the second hole is used to connect the second branch pipe and the second flow channel; the first hole and the second hole are staggered. In the first plate, the two ends of the first flow channel are respectively connected to the first hole one by one, and are spaced apart from the second hole; in the second plate, the two ends of the second flow channel are respectively connected to the second hole one by one, and are spaced apart from the first hole.

4. The heat exchanger according to claim 3, characterized in that, A second transition section is connected between the second hole and the second flow channel, and the width of the second transition section gradually increases along the direction from the second hole to the second flow channel.

5. The heat exchanger according to claim 4, characterized in that, Multiple flow dividers are spaced apart along the width direction within the heat exchange channel, and each flow divider extends along the length direction; a spacer is provided between adjacent heat exchange channels, and the spacer extends along the length direction.

6. The heat exchanger according to claim 5, characterized in that, The width of the spacer bar is greater than the width of the diversion bar.

7. The heat exchanger according to claim 5, characterized in that, The first transition section is provided with multiple guide blocks at intervals, and the guide blocks are spaced apart from the flow dividers; the second transition section is provided with multiple guide bars at intervals, and each guide bar is connected to the flow divider in a one-to-one correspondence.

8. The heat exchanger according to claim 3, characterized in that, The thickness of the second plate is greater than the thickness of the first plate.

9. The heat exchanger according to claim 3, characterized in that, An integrated temperature and pressure sensor is provided at each of the first branch pipes corresponding to the point where the first fluid leaves the core plate bundle.

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