Core plate bundle and heat exchanger

Abstract

The application provides a core plate bundle and a heat exchanger. The core plate bundle comprises a plurality of stacked heat exchange plates, each heat exchange plate comprising two opposite surfaces, wherein each surface is provided with a plurality of flow channel grooves, the flow channel grooves of adjacent two heat exchange plates are matched to form closed heat exchange flow channels, and the heat exchange flow channels are used for containing heat exchange fluid. Along the extension direction of the flow channel grooves, each flow channel groove is provided with a plurality of turbulence ribs at intervals near the groove bottom inside the heat exchange plate. In each heat exchange flow channel, the turbulence ribs of the two matched flow channel grooves are staggered along the extension direction, and the orthographic projections of the turbulence ribs of the two matched flow channel grooves on the plane of one heat exchange plate are completely non-overlapping. The turbulence rib is a strip structure, and the strip structure is arranged obliquely to the extension direction. In the same heat exchange flow channel, the oblique directions of the turbulence ribs of the two matched flow channel grooves are opposite. The core plate bundle and the heat exchanger provided by the application have simple structures, better comprehensive performance, and can take into account heat exchange performance and energy saving effect.

Description

Technical Field

[0001] This application relates to the field of heat exchange technology, and in particular to a core plate bundle and a heat exchanger. Background Technology

[0002] Heat exchangers are devices that transfer some of the heat from a hot fluid to a cold fluid, playing a vital role in chemical, petroleum, power, food, and many other industrial production processes. Microchannel heat exchangers (PCHEs) have received increasing attention in recent years in fields such as petrochemicals, aerospace, nuclear power, hydrogen refueling stations, supercritical carbon dioxide power generation, and concentrated solar power due to their numerous advantages, including small size, light weight, compact structure, resistance to high temperatures and pressures, and excellent heat exchange performance.

[0003] Microchannel heat exchangers typically employ chemical etching technology to etch unit plates with millimeter-scale channels. These plates are then connected using diffusion welding to form the core channels, which are then welded together to form the heat exchanger. With technological advancements, the overall performance requirements for microchannel heat exchangers are becoming increasingly stringent. While existing microchannel heat exchangers improve heat transfer performance, they also significantly increase flow resistance and energy consumption. Therefore, there is an urgent need for a heat exchanger with superior overall performance. Summary of the Invention

[0004] In view of this, the purpose of this application is to provide a core plate bundle and heat exchanger to solve the related problems mentioned in the background art.

[0005] Based on the above objectives, a first aspect of this application provides a core plate bundle for use in a heat exchanger. The core plate bundle includes a plurality of stacked heat exchange plates, each heat exchange plate having two opposing sides, each side having a plurality of flow channel grooves. The flow channel grooves of two adjacent heat exchange plates cooperate to form a closed heat exchange flow channel for accommodating heat exchange fluid. Along the extension direction of the flow channel grooves, each flow channel groove has a plurality of baffles spaced apart near the bottom of the groove inside the heat exchange plate. In each heat exchange flow channel, the baffles of two cooperating flow channel grooves are staggered along the extension direction, and the orthographic projections of the baffles of two cooperating flow channel grooves on the plane of a heat exchange plate do not overlap. The baffles are strip-shaped structures, and the strip-shaped structures are inclined to the extension direction. In the same heat exchange flow channel, the inclination directions of the baffles of two cooperating flow channel grooves are opposite.

[0006] Furthermore, the angle between the bleed rib and the extending direction is greater than or equal to 30° and less than or equal to 60°.

[0007] Furthermore, in the same flow channel groove, the inclination angle of each of the turbulence ribs is the same along the extension direction.

[0008] Furthermore, the thickness of the turbulence rib is H1, and the depth of the flow channel groove is H0, satisfying 0.4H0≤H1≤H0.

[0009] Furthermore, in the same flow channel groove, the distance between two adjacent turbulence ribs is L1; in the same heat exchange flow channel, the distance between the turbulence ribs of two cooperating flow channel grooves along the extension direction is L2, satisfying L2=0.5L1.

[0010] Furthermore, the length of the turbulence rib is L3, satisfying 2L3≤L1≤10L3.

[0011] Furthermore, on the same side of the heat exchange plate, the turbulence ribs in adjacent flow channel grooves are arranged alternately or in an array, and the inclination directions of the turbulence ribs in adjacent flow channel grooves are opposite or the same.

[0012] Furthermore, on the same heat exchange plate, the flow channel groove on one side is a straight structure, and the flow channel groove on the other side is a Z-shaped structure.

[0013] A second aspect of this application provides a heat exchanger comprising a core plate bundle as described in the first aspect above, wherein pressure plates are respectively provided on the top and bottom surfaces of the core plate bundle, and tube boxes are provided on the sides of the core plate bundle.

[0014] As can be seen from the above description, the core plate bundle and heat exchanger provided in this application, wherein the core plate bundle is applied to a heat exchanger, includes multiple stacked heat exchange plates, each heat exchange plate includes two opposing sides, each side is provided with multiple flow channel grooves, the flow channel grooves of two adjacent heat exchange plates cooperate to form a closed heat exchange flow channel, the heat exchange flow channel is used to contain heat exchange fluid; along the extension direction of the flow channel groove, each flow channel groove is provided with multiple baffles at intervals near the bottom of the groove inside the heat exchange plate; in each heat exchange flow channel, the baffles of two cooperating flow channel grooves are staggered along the extension direction, and the orthographic projections of the baffles of two cooperating flow channel grooves on the plane of a heat exchange plate do not overlap at all; the baffles are strip-shaped structures, and the strip-shaped structures are inclined to the extension direction; in the same heat exchange flow channel, the inclination directions of the baffles of two cooperating flow channel grooves are opposite. By setting multiple turbulence ribs along the extension direction at the bottom of the flow channel, the disturbance to the fluid can be increased, improving the heat transfer effect. Setting turbulence ribs arranged alternately along the extension direction at the bottom of the two flow channel slots of the heat exchange channel not only further enhances the heat transfer effect but also conforms to the fluid flow trend, resulting in less fluid resistance and greater energy savings. Furthermore, by ensuring that the orthogonal projections of different turbulence ribs on the plane of the heat exchange plate do not overlap, resistance is further avoided. Tests show that this heat exchange channel significantly improves overall performance compared to traditional straight channels, Z-shaped channels, or channels with general protrusions, exhibiting better heat transfer performance, relatively less increase in resistance, and energy savings. This core plate bundle and heat exchanger has a simple structure, superior overall performance, and can balance heat transfer performance and energy saving, reducing energy consumption. Attached Figure Description

[0015] 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.

[0016] Figure 1 This is a three-dimensional structural diagram of a heat exchanger according to an embodiment of this application.

[0017] Figure 2 for Figure 1 A schematic diagram of the side structure of the core plate bundle.

[0018] Figure 3 for Figure 2 A schematic diagram of the first side of the first type of heat exchange plate.

[0019] Figure 4 for Figure 2 A schematic diagram of the second side of the first type of heat exchange plate.

[0020] Figure 5 for Figure 2 A schematic diagram of the structure of the first side of the second type of heat exchange plate.

[0021] Figure 6 for Figure 2 A schematic diagram of the second side of the second type of heat exchange plate.

[0022] Figure 7 for Figure 2 A magnified structural diagram of point A in the middle.

[0023] Figure 8 for Figure 2 Schematic diagram of the cross-sectional structure in the BB direction.

[0024] Figure 9 for Figure 8 A magnified structural diagram at point D.

[0025] Figure 10 for Figure 2 A schematic diagram of the cross-sectional structure in the CC direction.

[0026] Figure 11 for Figure 10 A magnified structural diagram at point E in the middle.

[0027] Figure 12 This is a schematic diagram of the vertical cross-sectional velocity distribution of a straight, unbumpy heat exchange channel in Comparative Example 1 of this application.

[0028] Figure 13 for Figure 12 A schematic diagram of the flow velocity distribution in the horizontal cross-section of the heat exchange channel.

[0029] Figure 14 This is a schematic diagram of the vertical cross-sectional velocity distribution of a wave-shaped, undisturbed heat exchange channel in Comparative Example 2 of this application.

[0030] Figure 15 for Figure 14 A schematic diagram of the flow velocity distribution in the horizontal cross-section of the heat exchange channel.

[0031] Figure 16 This is a schematic diagram of the vertical cross-sectional velocity distribution of a heat exchange channel with turbulence ribs on the side, as shown in Comparative Example 3 of this application.

[0032] Figure 17 for Figure 16 A schematic diagram of the flow velocity distribution in the horizontal cross-section of the heat exchange channel.

[0033] Figure 18 This is a schematic diagram of the vertical cross-sectional velocity distribution of a heat exchange channel with vertical turbulence ribs at the bottom of a straight trough, as shown in Comparative Example 4 of this application.

[0034] Figure 19 for Figure 18 A schematic diagram of the flow velocity distribution in the horizontal cross-section of the heat exchange channel.

[0035] Figure 20 This is a schematic diagram of the vertical cross-sectional velocity distribution of a heat exchange channel with inclined turbulence ribs at the bottom of a straight trough, as shown in Embodiment 1 of this application.

[0036] Figure 21 for Figure 20 A schematic diagram of the flow velocity distribution in the horizontal cross-section of the heat exchange channel.

[0037] Reference numerals in the attached diagram: 1. Core plate bundle; 2. Heat exchange plate; 2-1. Flow channel groove; 2-2. Turbulence rib; 3. Heat exchange flow channel; 4. Pressure plate; 5. Tube box. Detailed Implementation

[0038] 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.

[0039] 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.

[0040] Microchannel heat exchangers (PCHEs), as a type of highly efficient and compact heat exchanger based on a microstructure (channel width / depth typically 0.1mm-2mm), are designed to maximize the heat exchange area per unit volume (up to 500m² / m³-2500m² / m³, approximately 3-8 times that of traditional shell-and-tube heat exchangers) through stacked assembly and diffusion welding of thin metal plates. This ensures high structural strength and sealing, thus overcoming the bottlenecks of traditional heat exchangers in extreme environments, compact spaces, and efficient heat transfer. In recent years, thanks to their comprehensive advantages of small size, light weight, compact structure, high temperature and pressure resistance, and excellent heat exchange performance, they have achieved breakthrough applications in high-end fields such as petrochemicals, aerospace, hydrogen refueling stations, and concentrated solar power generation.

[0041] For microchannel heat exchangers, the market demands products with better overall performance (the ratio of heat transfer to pressure drop) and higher energy efficiency, which is more conducive to carbon reduction and cost reduction. To address the performance issues of microchannel heat exchangers, many new microchannel flow channel designs have emerged in recent years. For example, some technologies use periodic semi-conical channels, relying on the jetting effect of the small-diameter cone to increase turbulence and thus improve heat transfer performance. Other technologies incorporate various raised turbulence structures within the flow channel to enhance heat transfer performance. Still others use semi-circular resistance ribs on both sides of the flow channel. The drawback of these three approaches is a significant increase in heat exchanger resistance, while heat transfer performance still needs further improvement. Several mature microchannel flow channel structures, such as straight channels, Z-shaped channels, rectangular channels, and trapezoidal channels, have been studied. It has been found that the Z-shaped channel has the best overall performance, but the increase in resistance is still significant and not conducive to energy saving and consumption reduction during operation.

[0042] In view of this, a novel microchannel design structure can be proposed that combines the comprehensive performance of flow and heat transfer. This structure can improve heat transfer while ensuring a small increase in pressure drop in the flow channel, making the overall performance of the heat exchanger superior to that of the aforementioned structures and more in line with the energy-saving and consumption-reducing goals of equipment operation.

[0043] The following describes specific embodiments in conjunction with the appendix. Figures 1 to 21 The technical solution of this application will be further described in detail.

[0044] Some embodiments of this application provide a core plate bundle 1, such as... Figures 2 to 11 As shown, the core plate bundle 1 includes multiple stacked heat exchange plates 2, each heat exchange plate 2 having two opposing sides, each side having multiple flow channel grooves 2-1. The flow channel grooves 2-1 of two adjacent heat exchange plates 2 cooperate to form a closed heat exchange flow channel 3, which is used to contain the heat exchange fluid. Along the extending direction of the flow channel grooves 2-1, each flow channel groove 2-1 has multiple turbulence ribs 2-2 spaced apart near the bottom of the groove inside the heat exchange plate 2. In the heat exchange channel 3, the turbulence ribs 2-2 of the two cooperating channel grooves 2-1 are staggered along the extension direction, and the orthographic projections of the turbulence ribs 2-2 of the two cooperating channel grooves 2-1 on the plane of a heat exchange plate 2 do not overlap at all; the turbulence ribs 2-2 are strip-shaped structures, and the strip-shaped structures are inclined to the extension direction; in the same heat exchange channel 3, the inclination directions of the turbulence ribs 2-2 of the two cooperating channel grooves 2-1 are opposite.

[0045] like Figure 1The diagram shows a schematic of a heat exchanger, which includes a core plate bundle 1. In the diagram, the L direction is the length direction of the core plate bundle 1, the W direction is the width direction of the core plate bundle 1, and the H direction is the thickness direction of the core plate bundle 1.

[0046] like Figure 2 As shown, the core plate bundle 1 includes multiple stacked heat exchange plates 2, which are, for example, rectangular structures, such as... Figure 3 and Figure 5 As shown, the core plate bundle 1 includes, for example, alternately stacked first type heat exchange plates 2 and second type heat exchange plates 2. Each heat exchange plate 2 includes two opposing sides, each side having a plurality of flow channel grooves 2-1, which are arranged, for example, at intervals along the width direction. Figure 7 As shown, the flow channels 2-1 of two adjacent heat exchange plates 2 cooperate to form a closed heat exchange channel 3, which is used to contain the heat exchange fluid.

[0047] Specifically, such as Figure 3 and Figure 4 As shown, the first heat exchange plate 2 has a Z-shaped flow channel groove 2-1 on its first surface and a straight flow channel groove 2-1 on its second surface, as shown. Figure 5 and Figure 6 As shown, the second type of heat exchange plate 2 has a straight flow channel groove 2-1 on its first surface and a Z-shaped flow channel groove 2-1 on its second surface, as shown. Figure 10 As shown, the first surface of the first type of heat exchange plate 2 and the second surface of the second type of heat exchange plate 2 abut against each other to form a complete Z-shaped heat exchange channel 3, as shown. Figure 8 As shown, the second surface of the first type of heat exchange plate 2 and the first surface of the second type of heat exchange plate 2 abut against each other to form a complete straight heat exchange channel 3. The heat exchange channels 3 are stacked alternately in this manner. This arrangement allows for the convenient placement of tube boxes 5 for different heat exchange fluids on different sides of the core plate bundle 1. The above arrangement of the heat exchange channels 3 is just an example. They can also be set as straight heat exchange channels 3, or as Z-shaped heat exchange channels 3, or as other types of heat exchange channels 3 as needed. The specific arrangement is not limited.

[0048] For the straight flow channel 2-1, such as Figure 4 As shown, its extension direction is the L direction. For the Z-shaped flow channel 2-1, as... Figure 3 As shown, its extension direction is also Z-shaped. Along the extension direction of the flow channel 2-1, each flow channel 2-1 has multiple baffles 2-2 spaced apart near the bottom of the heat exchange plate 2. That is, baffles 2-2 are only provided at the bottom of the flow channel 2-1, and not on the sidewalls of the flow channel 2-1. This increases the heat transfer effect and makes it easier to manufacture. The cross-section of the flow channel 2-1 is, for example, rectangular or trapezoidal, and is not specifically limited.

[0049] For example, the flow-dispersing ribs 2-2 are strip-shaped structures, such as... Figure 9 As shown, the length of the turbulence rib 2-2 is L3, as... Figure 7 As shown, the bottom width of the flow channel 2-1 is W0. The length of the turbulence rib 2-2 can be greater than or equal to the bottom width of the flow channel 2-1. The turbulence rib 2-2 fully covers the bottom of the channel in the width direction, guiding the flow of heat exchange fluid and ensuring the heat transfer effect.

[0050] like Figure 9 and Figure 11 As shown, in each heat exchange channel 3, the turbulence ribs 2-2 of the two cooperating channel grooves 2-1 are staggered along the extension direction. By setting the turbulence ribs 2-2 staggered along the extension direction at the bottom of the two channel grooves 2-1 of the heat exchange channel 3, not only can the heat transfer effect be further increased, but it also conforms to the fluid flow trend, has less fluid resistance, and is more energy-efficient.

[0051] like Figure 9 and Figure 11 As shown, the orthographic projections of the two cooperating flow channel grooves 2-1 on the plane of a heat exchange plate 2 do not overlap at all. By setting different orthographic projections of the 2-2 on the plane of the heat exchange plate 2 at intervals, the resistance is further avoided.

[0052] like Figure 9 As shown, in the heat exchange channel 3, the angle between the baffle 2-2 on one channel groove 2-1 and the extension direction is A1, and the angle between the baffle 2-2 on the other channel groove 2-1 and the extension direction is A2. Both A1 and A2 are greater than 0°, that is, the strip structure is inclined to the extension direction. According to the test, compared with the setting of the strip structure perpendicular to the extension direction, the heat exchange channel 3 of this embodiment has a higher comprehensive performance index, better heat transfer effect, and lower energy consumption.

[0053] In the same heat exchange channel 3, the turbulence ribs 2-2 of the two mating channel grooves 2-1 are inclined in opposite directions, such as... Figure 9 and Figure 11 As shown, the fluid flows in the lower channel 2-1 and gradually undergoes upward turbulence, mixing with the central fluid. Then, it flows in the upper channel 2-1 and undergoes downward turbulence, mixing with the central fluid again. This turbulence and mixing process is repeated periodically, resulting in more uniform mixing of fluids at different temperatures and better heat transfer. Furthermore, compared to the arrangement where the turbulence ribs 2-2 of the two mating channel channels 2-1 in the same heat exchange channel 3 have the same inclination direction, the heat exchange channel 3 in this embodiment has better heat transfer performance and avoids flow deviation.

[0054] Tests showed that the heat exchange channel 3 of this core plate bundle 1 significantly improved overall performance compared to traditional straight channels, Z-shaped channels, or channels with general protrusions. It exhibited better heat transfer performance, less increased resistance, and reduced energy consumption. This core plate bundle 1 has a simple structure and superior overall performance, balancing heat exchange performance and energy saving, thus reducing energy consumption.

[0055] In some embodiments, the angle between the bleeder 2-2 and the extending direction is greater than or equal to 30° and less than or equal to 60°.

[0056] like Figure 9 As shown, A1=A2, and the angle is set to 30°≤A1≤60°. This avoids setting the included angle too small, which would reduce the effect of enhancing turbulence, and also avoids setting the included angle too large, which would significantly increase the flow resistance.

[0057] In some embodiments, such as Figure 9 and Figure 11 As shown, in the same flow channel 2-1, the inclination angle of each of the turbulence ribs 2-2 is the same along the extension direction.

[0058] In the same flow channel 2-1, the inclination angles of each turbulence rib 2-2 relative to the extension direction are the same, such as... Figure 9 As shown, for the straight flow channel 2-1, the inclination direction of each turbulence rib 2-2 is the same, such as... Figure 11 As shown, for the Z-shaped flow channel 2-1, the inclination direction of each bleeder 2-2 is the same within the region of each segment of the Z-shape.

[0059] In some embodiments, such as Figure 7 As shown, the thickness of the turbulence rib 2-2 is H1, and the depth of the flow channel groove 2-1 is H0, satisfying 0.4H0≤H1≤H0.

[0060] like Figure 7 As shown, the thickness of the turbulence rib 2-2 is H1, the depth of the flow channel 2-1 is H0, and the total height of the heat exchange channel 3 is 2H0. Setting 0.4H0≤H1≤H0 avoids the turbulence rib 2-2 being too thin, resulting in an insignificant disturbance effect and insufficient improvement in heat transfer performance; it also avoids the turbulence rib 2-2 being too thick, resulting in a larger low-velocity region behind the turbulence rib 2-2, which would also significantly increase resistance and lead to insufficient overall performance.

[0061] In some embodiments, in the same flow channel 2-1, the distance between two adjacent turbulence ribs 2-2 is L1; in the same heat exchange flow channel 3, the distance between the turbulence ribs 2-2 of two cooperating flow channel 2-1 along the extension direction is L2, satisfying L2=0.5L1.

[0062] like Figure 9As shown, L1 is the distance between two adjacent turbulence ribs 2-2 in the flow channel 2-1, and L2 is the distance between the upper turbulence rib 2-2 and the lower turbulence rib 2-2 in the heat exchange flow channel 3. Setting L2=0.5L1 ensures uniform fluid disturbance, relatively small increase in resistance, and better overall heat exchange performance.

[0063] In some embodiments, the length of the turbulence rib 2-2 is L3, satisfying 2L3≤L1≤10L3.

[0064] like Figure 9 As shown, setting 2L3≤L1≤10L3 avoids the situation where the spacing between the turbulence ribs 2-2 is too small, causing the increase in pressure drop to exceed the improvement in heat transfer performance, which would lead to a decrease in its overall performance index; it also avoids the situation where the spacing between the turbulence ribs 2-2 is too large, which would cause the turbulence state of the heat exchange fluid to be discontinuous, and the enhancement of heat transfer performance would be reduced.

[0065] In some embodiments, on the same heat exchange plate 2, the flow channel 2-1 on one side is a straight structure, and the flow channel 2-1 on the other side is a Z-shaped structure.

[0066] like Figure 3 As shown, the flow channel groove 2-1 on the first surface of the first type of heat exchange plate 2 can be configured as a Z-shaped structure for the flow of heat exchange fluid on the cold side. The inlet and outlet of the flow channel groove 2-1 are located on both sides of the long side of the heat exchange plate 2; as shown Figure 4 As shown, the flow channel groove 2-1 on the second surface of the first type of heat exchange plate 2 can be set as a straight structure for the flow of heat exchange fluid on the hot side. The inlet and outlet of the flow channel groove 2-1 are located on both sides of the short side of the heat exchange plate 2, which is convenient to set and ensures the heat exchange effect.

[0067] In some embodiments, on the same side of the heat exchange plate 2, the turbulence ribs 2-2 in adjacent flow channel grooves 2-1 are arranged alternately or in an array, and the inclination directions of the turbulence ribs 2-2 in adjacent flow channel grooves 2-1 are opposite or the same.

[0068] like Figure 3 As shown, for the heat exchange fluid on the cold side, turbulence ribs 2-2 in adjacent flow channel slots 2-1 can be arranged in an alternating pattern to improve fluid turbulence and thus enhance heat transfer. Figure 4 As shown, for the heat exchange fluid on the hot side, the baffles 2-2 in adjacent flow channel slots 2-1 can be arranged in an array for easy configuration. Furthermore, the baffles 2-2 in adjacent flow channel slots 2-1 can have the same inclination direction for easy configuration; alternatively, the baffles 2-2 in adjacent flow channel slots 2-1 can have opposite inclination directions, which can be selected according to requirements.

[0069] Comparative Example 1

[0070] The core plate bundle comprises multiple stacked heat exchange plates, forming a straight heat exchange channel between them. No turbulence ribs are provided within this heat exchange channel. A 1 m / s velocity distribution simulation was performed on this heat exchange channel, and the simulation results are as follows: Figure 12 and Figure 13 As shown, the disturbance of the heat exchange fluid is very small, and the field cooperation angle of the heat exchange fluid (the angle between the heat exchange fluid streamline and the heat exchange channel wall) is almost 90°, resulting in poor heat transfer effect.

[0071] Comparative Example 2

[0072] The core plate bundle comprises multiple stacked heat exchange plates, forming a wave-shaped heat exchange channel between them. No turbulence ribs are provided within this heat exchange channel. A 1 m / s velocity distribution simulation was performed on this heat exchange channel, and the simulation results are as follows: Figure 14 and Figure 15 As shown, the heat transfer fluid experiences significant turbulence and high velocity in the central region of the channel, resulting in a marked increase in resistance. However, in the region behind the inflection point of the wavy channel, the velocity is very low, and the low-velocity area is quite large, with minimal turbulence and poor heat transfer.

[0073] Comparative Example 3

[0074] The core plate bundle comprises multiple stacked heat exchange plates, forming a straight heat exchange channel between them. Fluctuation ribs are alternately arranged on the sidewalls of this heat exchange channel perpendicular to the heat exchange plates. A 1 m / s velocity distribution simulation was performed on this heat exchange channel, and the simulation results are as follows: Figure 16 and Figure 17 As shown, there is a clear low-velocity region, and the size of the low-velocity region is positively correlated with the rib size.

[0075] Comparative Example 4

[0076] The core plate bundle comprises multiple stacked heat exchange plates, forming a straight heat exchange channel between them. Fluctuation ribs are alternately arranged parallel to the bottom and top walls of the heat exchange plates within this channel, and these ribs are perpendicular to the extension direction of the heat exchange channel. A 1 m / s velocity distribution simulation was performed on this heat exchange channel, and the simulation results are as follows: Figure 18 and Figure 19 As shown, a low velocity zone also exists in the area behind the turbulence ribs, but it is better than the velocity distribution effect of Comparative Example 3.

[0077] Example 1

[0078] The core plate bundle comprises multiple stacked heat exchange plates, forming a straight heat exchange channel between them. Fluctuation ribs are alternately arranged parallel to the bottom and top walls of the heat exchange plates within this channel. These ribs are inclined towards the extension direction of the heat exchange channel. A 1 m / s velocity distribution simulation was performed on this heat exchange channel, and the simulation results are as follows: Figure 20 and Figure 21 As shown, Figure 20It can be seen that the heat exchange fluid exhibits significant upward and downward turbulence, and a low-velocity region exists, but its area is very small. Figure 21 It can be seen that the disturbance in the horizontal section is also significant, while the low-velocity region is almost negligible. Compared with Comparative Example 2, the disturbance in Example 1 is more uniform in the three-dimensional space of the flow channel, and the area of ​​the low-velocity region is smaller, resulting in higher overall performance. Compared with Comparative Example 4, the area of ​​the low-velocity region in the structure of Example 1 is greatly reduced.

[0079] For Example 1 and Comparative Examples 1-4, the comprehensive performance index at different flow rates was calculated according to the comprehensive performance index formula described in the relevant patent (CN119022691A). Specifically, the comprehensive performance index PEC = (A / A0) / (P / P0) 1 / 3 Where A0 is the film coefficient of Comparative Example 1, P0 is the pressure drop of Comparative Example 1, A is the film coefficient of Comparative Examples 2-4 and Example 1, and P is the pressure drop of Comparative Examples 2-4 and Example 1. The film coefficient is the convective heat transfer coefficient. The larger the film coefficient, the better the heat transfer performance; the smaller the pressure drop, the less pumping power is lost due to fluid loss, and the higher the energy efficiency. The larger the PEC value, the better the overall performance of the core plate bundle.

[0080] Table 1 Comprehensive Performance Index Test Table

[0081]

[0082] The test results of each comprehensive performance index are shown in Table 1. It can be seen from the table that, under the same equivalent diameter, the comprehensive performance index of different flow velocities is the best of the simulation results of Example 1. It can also be seen that the upper and lower setting of the turbulence ribs is better than the side setting of the turbulence ribs, and the inclined setting of the turbulence ribs is better than the vertical setting of the turbulence ribs.

[0083] In some embodiments of this application, a heat exchanger is provided, such as... Figure 1 As shown, it includes a core plate bundle 1 as described in any of the above embodiments, wherein the top and bottom surfaces of the core plate bundle 1 are respectively provided with pressure plates 4, and the side surfaces of the core plate bundle 1 are provided with tube boxes 5.

[0084] like Figure 1 As shown, the heat exchanger includes a core plate bundle 1, with pressure plates 4 fixing it to the top and bottom surfaces. A tube box 5 is located on the side of the core plate bundle 1 for the heat exchange fluid to enter and exit. This heat exchanger has good heat exchange performance and a long service life.

[0085] 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.

[0086] 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.

[0087] 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.

[0088] 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 core plate bundle, characterized in that, Applied to heat exchangers, the core plate bundle includes multiple stacked heat exchange plates, each heat exchange plate including two opposing sides, each side having multiple flow channel grooves, the flow channel grooves of two adjacent heat exchange plates cooperating to form a closed heat exchange flow channel, the heat exchange flow channel being used to contain heat exchange fluid; Along the extension direction of the flow channel, each flow channel has multiple baffles spaced apart near the bottom of the channel inside the heat exchange plate; along the width direction of the flow channel, the baffles completely cover the bottom of the channel; in each heat exchange channel, the baffles of two mating flow channels are staggered along the extension direction, and the orthographic projections of the baffles of two mating flow channels on the plane of a heat exchange plate do not overlap; the baffles are strip-shaped structures, and the strip-shaped structures are inclined to the extension direction; in the same flow channel, the inclination angle of each baffle is the same along the extension direction; in the same heat exchange channel, the inclination directions of the baffles of two mating flow channels are opposite.

2. The core plate bundle according to claim 1, characterized in that, The angle between the bleed rib and the extending direction is greater than or equal to 30° and less than or equal to 60°.

3. The core plate bundle according to claim 1, characterized in that, The thickness of the turbulence rib is H1, and the depth of the flow channel groove is H0, satisfying 0.4H0≤H1≤H0.

4. The core plate bundle according to claim 1, characterized in that, In the same flow channel, the distance between two adjacent turbulence ribs is L1; in the same heat exchange flow channel, the distance between the turbulence ribs of two cooperating flow channels along the extension direction is L2, satisfying L2=0.5L1.

5. The core plate bundle according to claim 4, characterized in that, The length of the turbulence rib is L3, which satisfies 2L3≤L1≤10L3.

6. The core plate bundle according to claim 1, characterized in that, On the same side of the heat exchange plate, the turbulence ribs in adjacent flow channel grooves are arranged alternately or in an array, and the inclination directions of the turbulence ribs in adjacent flow channel grooves are opposite or the same.

7. The core plate bundle according to claim 1, characterized in that, On the same heat exchange plate, the flow channel groove on one side is a straight structure, and the flow channel groove on the other side is a Z-shaped structure.

8. A heat exchanger, characterized in that, The core plate bundle includes any one of claims 1-7, wherein the top and bottom surfaces of the core plate bundle are respectively provided with pressure plates, and the side surfaces of the core plate bundle are provided with tube boxes.

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