Heat exchanger

Abstract

The utility model discloses a heat exchanger which comprises a shell and a heat exchange tube located in the shell, a support is arranged in a containing space and comprises partition plates, the partition plates are distributed at intervals so as to divide the containing space into a plurality of heat exchange areas, and the heat exchange areas are communicated with a shell pass liquid inlet and a shell pass liquid outlet. The heat exchange tube comprises a plurality of tube sets, each tube set is composed of at least one tube body, and a flow channel allowing tube pass liquid to flow is formed in each tube body. Wherein each pipe group comprises a circumferential extension section and an axial extension section, and the circumferential extension section of each pipe group corresponds to one heat exchange area and extends for at least one circle in the heat exchange area; and the axial extension section extends from the tube pass liquid inlet to the heat exchange area corresponding to the tube stack and extends from the corresponding heat exchange area to the tube pass liquid outlet. Each pipe group is provided with a corresponding heat exchange area, and the temperature difference of shell pass liquid in contact with each pipe group is not too large; the length of the pipe body in a single heat exchange area and the contact area with shell pass liquid are greatly increased, and the heat exchange efficiency is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to heat exchange technical field, especially a kind of heat exchanger. BACKGROUND

[0002] Heat exchanger is the key equipment for heat transfer between fluids in industrial production, and its performance directly affects the efficiency and safety of system. As shown in the tangential double-liquid inlet heat exchanger in the prior Chinese utility model patent CN201320079036.4, including shell side, tube side, cooling liquid inlet and cooling liquid outlet, the tube side 3 is installed in the cavity of shell side 2, a first cooling liquid inlet 1 is arranged on the upper side of shell side 2 and is tangent to shell side 2, and a second cooling liquid inlet 5 is arranged on the other side of the upper side of shell side 2 and is opposite to the first cooling liquid inlet 1, the first and second cooling liquid inlets are used for injecting cooling liquid or connecting the outlet of cooling liquid pipeline, and a cooling liquid outlet 4 is arranged at the bottom of shell side 2 for discharging cooling liquid or connecting the inlet of cooling liquid pipeline to form a circulating flow.

[0003] In semiconductor applications, heat exchanger is used for heating or cooling wet chemicals, wherein the tube side liquid fluid is acid, alkali or ultrapure water, etc., and the shell side liquid fluid is oil or water respectively according to the need of heating or cooling. However, in the above-mentioned patent, the shell side is an integral whole without reasonable spatial layout, which leads to a significant decrease in heat exchange efficiency when the volume of heat exchanger and the shell side increase, and further leads to the inability of the shell side liquid to efficiently heat or cool the tube side liquid.

[0004] Therefore, it is necessary to improve the heat exchanger, on the one hand, to enable the shell side to accommodate more tube sides, and on the other hand, to enable each tube side in the shell side to obtain good heat exchange efficiency. UTILITY MODEL CONTENTS

[0005] In view of the deficiencies in the prior art, the purpose of the utility model is to provide a heat exchanger, which solves the problem of low heat exchange efficiency of the existing heat exchanger.

[0006] In order to achieve the above-mentioned purpose, the utility model adopts the following technical solutions:

[0007] A heat exchanger, comprising a shell and a heat exchange tube located in the shell, the shell comprising a containing space, a shell side liquid inlet and a shell side liquid outlet communicating with the containing space, and a tube side liquid inlet and a tube side liquid outlet,

[0008] The containing space is provided with a support, the support comprising a plurality of partitions, the partitions being distributed at intervals to separate the containing space into a plurality of heat exchange regions, and each heat exchange region being in communication with the shell side liquid inlet and the shell side liquid outlet;

[0009] The heat exchange tube comprises a plurality of tube groups, each tube group being composed of at least one tube body, and the tube body having a flow channel for the flow of tube side liquid;

[0010] The tube body comprises a circumferential extension section and an axial extension section, the circumferential extension section of the tube body in each tube group corresponds to a heat exchange region and extends at least one turn in the heat exchange region; the axial extension section extends from the tube-side liquid inlet to the heat exchange region corresponding to the tube group, and extends from the heat exchange region to the tube-side liquid outlet.

[0011] The heat exchanger of the utility model, setting support in the containing space of shell, divides the containing space into several heat exchange regions, each heat exchange region communicates with the shell-side liquid inlet and the shell-side liquid outlet, so that the shell-side liquid can flow into each heat exchange region from the shell-side liquid inlet and fill the containing space, and then flow out from the shell-side liquid outlet, realizing the flow and renewal of the shell-side liquid; the circumferential extension section of the tube body in each tube group corresponds to a heat exchange region, on the one hand, the heat exchange tube is divided into several tube groups, on the other hand, the containing space is separated by the partition plate to form several heat exchange regions not less than the number of tube groups, so that the circumferential extension section of a tube group extends in the corresponding heat exchange region and exchanges heat, and the circumferential extension section of each tube group has its independent heat exchange region; in this way, the problem of poor heat exchange efficiency caused by the influence of a large bundle of tube bodies on each other can be avoided as much as possible, thereby improving the heat exchange efficiency of the heat exchanger; compared with the crowded arrangement of multiple tube groups in one containing space, the scheme of the application can make the fluid flow more uniformly in the region, which can also reduce the pressure drop of the shell-side liquid to a certain extent, promote the orderly flow of the shell-side liquid in the containing space, and thereby increase the heat exchange efficiency; at the same time, due to the presence of the support, the position of the heat exchange region can be kept stable, so that the tube group has a stable heat exchange region, thereby ensuring that each tube group can stably and effectively exchange heat.

[0012] Preferably, the partition plate is arranged vertically to the axial direction in the containing space, at least part of the partition plate is provided with an inlet hole and an outlet hole, the tube group enters the corresponding heat exchange region through the inlet hole, and the tube group exits the corresponding heat exchange region through the outlet hole.

[0013] In this way, the partition plate is arranged to make the heat exchange regions distributed in the axial direction of the containing space, and the tube-side liquid in the tube body will continue to exchange heat with the shell-side liquid of other heat exchange regions before and after the axial extension section of the heat exchange tube enters and exits the corresponding heat exchange region, so as to further improve the heat exchange efficiency by utilizing the axial space; at the same time, the inlet hole and the outlet hole can position the heat exchange tube, so that the heat exchange tube is fixed in position and uniformly distributed in the heat exchange region, thereby ensuring the installation stability of the heat exchange tube and reducing the contact area with the shell-side liquid by stacking the tube bodies on each other.

[0014] Preferably, the inlet hole and the outlet hole are tangentially arranged on the partition plate.

[0015] When the number of rows of the inlet tube holes is ≥2, each row of the inlet tube holes is parallel and spaced apart from each other, and / or when the number of rows of the outlet tube holes is ≥2, each row of the outlet tube holes is parallel and spaced apart from each other.

[0016] When a plurality of tube bodies are included in each tube group, the corresponding inlet tube holes and outlet tube holes form a row and are tangentially arranged on the baffle plate. In this way, the interference between the tube bodies in the circumferential extension can be reduced, and the radial gap between the adjacent tube bodies is reserved, so that the tube bodies can be in full contact with the shell side liquid. When the number of tube groups is ≥2, the number of rows of the inlet tube holes and outlet tube holes on some baffle plates is also ≥2, each row of the inlet tube holes is parallel and spaced apart from each other, and each row of the outlet tube holes is parallel and spaced apart from each other, which ensures that the tube bodies in different groups of tube groups do not interfere with each other and maintain appropriate spacing, facilitating the flow of shell side liquid and full contact with the tube bodies for heat exchange.

[0017] Preferably, the tube side liquid inlet and the tube side liquid outlet are located at the same end of the shell, the number of rows of the inlet tube holes and outlet tube holes of the baffle plates closest to the tube side liquid inlet and the tube side liquid outlet is equal to the number of tube groups, and the number of rows of the inlet tube holes and outlet tube holes of the baffle plates away from the tube side liquid inlet and the tube side liquid outlet decreases by one row in turn, and the baffle plate farthest from the tube side liquid inlet and the tube side liquid outlet is not provided with the inlet tube hole.

[0018] In this way, the tube bodies in all tube groups need to pass through the inlet tube holes of the baffle plate closest to the tube side liquid inlet, and then the tube bodies of the next group enter the corresponding heat exchange area, and the tube bodies of the remaining tube groups pass through the next layer of baffle plates, and a group of tube bodies enters the corresponding heat exchange area, and the number of tube groups is reduced layer by layer, until the last group of tube bodies passes through the second-to-last layer of baffle plates, enters the corresponding heat exchange area, and then extends circumferentially, and then passes out of the outlet tube holes of the second-to-last layer of baffle plates, and then passes out of the tube groups in the heat exchange area of the upper layer, until all the tube bodies in the tube groups pass out of the outlet tube holes of the baffle plate closest to the tube side liquid inlet. Thus, the farther the distance from the tube side liquid inlet and the tube side liquid outlet, the longer the length of the tube bodies of the tube groups, and the longer the contact time with the shell side liquid, which compensates for the temperature change of the shell side liquid during the flow to the farther heat exchange area, and ensures the heat exchange effect of the tube bodies in each heat exchange area.

[0019] Preferably, the inlet tube holes and outlet tube holes on the same baffle plate are symmetrically arranged about the center of the baffle plate, so that the positions of the tube bodies passing into the heat exchange area and passing out of the heat exchange area are far apart, avoiding interference and facilitating tube insertion.

[0020] Preferably, the partition plate comprises first partition plates and second partition plates alternately arranged along the axial direction of the shell, the center of the first partition plate has a first channel penetrating through the upper and lower surfaces of the first partition plate, the center of the second partition plate is a solid structure, and the outer sidewall of the second partition plate is arranged apart from the inner wall of the shell to form a second channel; the first channel, the second channel and each heat exchange region are communicated to form a heat exchange flow channel communicated with the shell-side liquid inlet and the shell-side liquid outlet.

[0021] In this way, the first channel and the second channel are respectively communicated with each heat exchange region, and the shell-side liquid is prolonged in the flow path, so that the shell-side liquid can contact more heat exchange tubes in a limited space, and has a larger heat exchange surface area, so that the shell-side liquid and the tube-side liquid are fully heat exchanged, and the heat exchange efficiency is improved; and because the positions of the first channel and the second channel are different, the shell-side liquid can be evenly distributed in the entire containing space, so that the heat exchange tubes in different regions can be heat exchanged with the shell-side liquid, and the shell-side liquid flows in a direction according to the flow channel, so that the shell-side liquid flows quickly and is updated, and the situation that part of the shell-side liquid leaves the heat exchanger without being fully heat exchanged is avoided. In addition, when the shell-side liquid flows through each turn, eddy current and velocity gradient are generated at the corner due to inertia, which helps to break the boundary layer, promotes the mixing of the fluid inside, and enhances the heat transfer effect.

[0022] Preferably, the partition plate comprises a second partition plate and a plurality of first partition plates arranged axially above the second partition plate.

[0023] The center of the first partition plate has a first channel penetrating through the upper and lower surfaces of the first partition plate, and part of the outer sidewall of the first partition plate is arranged apart from the inner wall of the shell to form a liquid collecting channel.

[0024] The center of the second partition plate is a solid structure, and the outer sidewall of the second partition plate is arranged apart from the inner wall of the shell to form a second channel.

[0025] At least part of the shell-side liquid in the first channel enters the liquid collecting channel after the heat exchange region, and enters the shell-side liquid outlet through the second channel.

[0026] In this way, the shell-side liquid can quickly reach each heat exchange region after entering the containing space from the shell-side liquid inlet, especially the heat exchange region farthest from the shell-side liquid inlet, further improving the uniformity of the temperature of the shell-side liquid in each heat exchange region, so that the temperature difference between the heat exchange region closest to the shell-side liquid inlet and the heat exchange region farthest from the shell-side liquid inlet is smaller, which is beneficial to improve the heat exchange effect of the tube body in each heat exchange region; and the purpose of arranging the liquid collecting channel is to promote the flow of the shell-side liquid in the heat exchange region and avoid the formation of dead zones. The shell-side liquid entering the heat exchange region flows to the liquid collecting channel, and then flows to the second channel and the shell-side liquid outlet.

[0027] Preferably, the support further includes a third partition extending along the axial direction, and a plurality of the third partitions are circumferentially spaced to divide each heat exchange area into a plurality of fan-shaped flow channels. The third partition is provided with a through hole, and the tube is sequentially inserted into the through hole on each of the third partitions and extends circumferentially at least one circle.

[0028] The fan-shaped flow channels allow the shell-side liquid to diffuse or converge, further guiding its flow and mixing. This promotes a more uniform temperature distribution across the channels, reducing the likelihood of insufficient heat exchange before the shell-side liquid leaves the heat exchanger and minimizing dead zones. This ensures adequate flow of the shell-side liquid throughout the entire container. Furthermore, the guiding effect of the fan-shaped flow channels helps maintain sufficient heat exchange efficiency while keeping the overall pressure drop within a reasonable range, reducing energy consumption. The heat exchange tubes have circumferential extensions within the heat exchange area, and the third baffle has several through-holes through which the tubes pass and extend circumferentially around the center of the first and second baffles. This configuration ensures uniform distribution of the heat exchange tubes within the heat exchange area and maximizes contact with the shell-side liquid in each fan-shaped flow channel, improving heat exchange efficiency. The third baffle also secures the heat exchange tubes, maintaining their stability and axial spacing within the heat exchange area.

[0029] Preferably, the tube assembly consists of multiple tubes; the number of rows and columns of the through holes on the third partition is greater than 1 to form a matrix, and this matrix is ​​arranged circumferentially in the same heat exchange area; the circumferential extension method of the tube assembly includes:

[0030] Multiple tubes pass circumferentially through the same row of through holes on several third partitions and then enter through holes in an adjacent row of a third partition; or,

[0031] Multiple tubes pass circumferentially through the same column of through holes on several third partitions and then enter the adjacent column of through holes in one of the third partitions.

[0032] There are various ways to extend the multiple tubes in a tube bundle circumferentially. Regardless of the method, it ensures that the tubes maintain circumferential and axial clearances with themselves or adjacent tubes in the heat exchange area. This allows the tubes to have sufficient length within the heat exchange area while maintaining adequate contact with the shell-side liquid, resulting in high heat exchange efficiency. Furthermore, each tube is spirally arranged in a planar or vertical manner within the heat exchange area. The tube bundle formed by multiple tubes extends in an orderly, three-dimensional manner within the heat exchange area, further increasing the space utilization of the heat exchange area and thus increasing heat exchange efficiency.

[0033] Preferably, in the liquid inlet direction, the angle between the tube body and the third partition is between 30° and 60°; and / or, in the liquid outlet direction, the angle between the tube body and the third partition is between 130° and 160°.

[0034] This tube design serves two purposes. First, it ensures a more stable flow path within the tube. Since the circumferential and axial extensions of the tube connect at the third baffle, the fluid flowing through the tube changes from axial to circumferential. Large angle changes can cause excessive pressure loss and increased turbulence. Therefore, setting the angle between the tube and the third baffle to 30–60°, or 130–160°, can appropriately buffer the fluid, improve flow quality, and reduce pressure loss and turbulence. Second, this angle range also prevents the heat exchange tube from swaying in the heat exchange area during use, avoiding friction between the tube and the inlet, outlet, or through-hole, and even causing wear.

[0035] Preferably, the gap between adjacent tubes is D1, and the diameter of the tube is D2; 1.4 ≤ D1 / D2 ≤ 2.3. On the one hand, controlling the size of the gap D1 avoids an excessively large gap, which would result in a small total tube length within a single heat exchange area, leading to a smaller amount of tube-side liquid flowing within the tubes per unit time and low heat exchange efficiency. Conversely, an excessively small gap would hinder the flow of shell-side liquid between adjacent tubes and prevent sufficient contact with the tubes. On the other hand, controlling the tube diameter also avoids an excessively small diameter, which would increase the flow resistance of the tube-side liquid, while an excessively large diameter would prevent sufficient heat exchange between the central tube-side liquid and the shell-side liquid, resulting in an excessively large temperature gradient within the tubes and reduced heat exchange efficiency. By controlling the ratio of these two factors within the aforementioned range, the total tube length within a single heat exchange area and the total amount of tube-side liquid exchanging heat per unit time are ensured, as well as the rapid flow of shell-side liquid and sufficient contact with the tubes for heat exchange, thus guaranteeing heat exchange efficiency.

[0036] In summary, compared with the prior art, the present invention has at least the following beneficial effects:

[0037] The heat exchanger of this invention features a support frame within the housing space of the shell, dividing the space into several heat exchange zones. Each heat exchange zone is connected to the shell-side liquid inlet and outlet, allowing the shell-side liquid to rapidly flow from the inlet into each heat exchange zone, filling the housing space, and then flowing out from the outlet. This achieves rapid flow and renewal of the shell-side liquid. Simultaneously, due to the presence of the support frame, eddies and velocity gradients are generated as the shell-side liquid flows between the heat exchange zones. This helps break down the boundary layer, promotes internal mixing of the fluid, and results in a smaller temperature gradient between the heat exchange zones, leading to a more uniform overall temperature. Thus, each tube assembly has a corresponding heat exchange zone, and each… The temperature difference of the shell-side liquid in contact with the tube bundle will not be too large; more preferably, the tube body extends circumferentially within the heat exchange region, which greatly increases the length of the tube body in a single heat exchange region and the contact area with the shell-side liquid, so that the tube-side liquid and the shell-side liquid in the tube body can fully exchange heat, thereby improving the heat exchange efficiency; in addition, the axial extension section of the tube body extends from the tube-side liquid inlet to the heat exchange region corresponding to the tube bundle, and from the corresponding heat exchange region to the tube-side liquid outlet. During this process, the axial extension section can always be within the corresponding heat exchange region, and may also pass through other heat exchange regions. The tube-side liquid in the tube body will also be continuously heated by the shell-side liquid in the corresponding heat exchange region or other heat exchange regions, and the heat exchange efficiency can be further improved by utilizing the axial space. Attached Figure Description

[0038] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0039] Figure 1 This is a schematic diagram of the heat exchanger according to Embodiment 1 of this utility model.

[0040] Figure 2 This is a schematic diagram of the internal structure of the heat exchanger according to Embodiment 1 of this utility model.

[0041] Figure 3 This is a schematic diagram of the internal cross-section of the heat exchanger according to Embodiment 1 of this utility model.

[0042] Figure 4 This is a schematic diagram of the assembly of the bracket and part of the heat exchange tubes in Embodiment 1 of this utility model.

[0043] Figure 5 This is a schematic diagram of the circumferential extension of the tube body in Embodiment 1 of this utility model.

[0044] Figure 6This is a schematic diagram of the support structure according to Embodiment 1 of this utility model.

[0045] Figure 7 This is a schematic diagram of the assembly of the bracket and part of the heat exchange tubes in Embodiment 2 of this utility model.

[0046] Figure 8 This is a schematic diagram of the circumferential extension of the tube body in Embodiment 2 of this utility model.

[0047] Figure 9 This is a schematic diagram of the internal cross-section of the heat exchanger in Embodiment 3 of this utility model.

[0048] Figure 10 This is a schematic diagram of the support structure of Embodiment 3 of this utility model.

[0049] Figure 11 This is a schematic diagram of the structure of the first partition and the second partition in Embodiment 3 of this utility model.

[0050] Explanation of reference numerals in the attached figures

[0051] 10. Shell; 11. Housing space; 12. Shell-side liquid inlet; 13. Shell-side liquid outlet; 14. Tube-side liquid inlet; 15. Tube-side liquid outlet; 16. Heat exchange zone; 161. Fan-shaped flow channel; 17. Sum plate;

[0052] 20. Heat exchanger tube; 21. Tube assembly; 211. Tube body; 212. Axial extension section; 213. Circumferential extension section;

[0053] 30. Support; 31. Partition; 32. Inlet port; 33. Outlet port; 34. First partition; 35. First channel; 36. Liquid collection channel; 37. Second partition; 38. Second channel; 39. Third partition; 391. Through-hole. Detailed Implementation

[0054] The technical solution of this utility model will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0055] In the description of this utility model, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0056] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0057] like Figures 1 to 6 The illustrated embodiment provides a heat exchanger including a shell 10 and heat exchange tubes 20 located within the shell 10. The shell 10 includes a receiving space 11, a shell-side liquid inlet 12 and a shell-side liquid outlet 13 communicating with the receiving space 11, and a tube-side liquid inlet 14 and a tube-side liquid outlet 15. The receiving space 11 is used to receive the heat exchange tubes 20 and the shell-side liquid. The heat exchange tubes 20 are connected to the tube-side liquid inlet 14 and the tube-side liquid outlet 15. The receiving space 11 is connected to the shell-side liquid inlet 12 and the shell-side liquid outlet 13. When the heat exchanger is working, the tube-side liquid enters the heat exchange tubes 20 through the tube-side liquid inlet 14, and the shell-side liquid enters the receiving space 11 through the shell-side liquid inlet 12. There is a temperature difference between the shell-side liquid and the tube-side liquid. The heat exchange tubes 20 are made of a thermally conductive material. Therefore, when the shell-side liquid comes into contact with the heat exchange tubes 20, it can exchange heat with the tube-side liquid therein. The specific heat exchange process can be that the tube-side liquid heats up and the shell-side liquid cools down, or the tube-side liquid cools down and the shell-side liquid heats up.

[0058] like Figure 2As shown, a support 30 is provided in the containing space 11. The support 30 includes partitions 31. Several partitions 31 are spaced apart to divide the containing space 11 into several heat exchange zones 16. Each heat exchange zone 16 is connected to the shell-side liquid inlet 12 and the shell-side liquid outlet 13, so that the shell-side liquid can quickly flow from the shell-side liquid inlet 12 into each heat exchange zone 16 and fill the containing space 11, and then flow out from the shell-side liquid outlet 13, realizing the rapid flow and renewal of the shell-side liquid. At the same time, due to the presence of the support 30, eddies and velocity gradients are generated when the shell-side liquid flows between the heat exchange zones 16. This helps to break the boundary layer, promote the mixing inside the fluid, and make the temperature gradient of the shell-side liquid between the heat exchange zones 16 smaller and the overall temperature more uniform.

[0059] The heat exchange tube 20 includes several tube groups 21, each tube group 21 consisting of at least one tube body 211. The tube body 211 has a flow channel for the flow of the tube-side liquid. The tube body 211 includes a circumferential extension section 213 and an axial extension section 212. The circumferential extension section 213 of the tube body 211 in each tube group 21 corresponds to a heat exchange region 16 and extends at least one full circle within that heat exchange region 16. The axial extension section 212 extends from the tube-side liquid inlet 14 to the corresponding heat exchange region 16 of the tube group 21, and from the corresponding heat exchange region 16 to the tube-side liquid outlet 15. Based on the small temperature difference within each heat exchange region 16, the circumferential extension of the tube body 211 within the heat exchange region 16 greatly increases the efficiency of heat exchange. The length of the tube body 211 within a single heat exchange zone 16 and its contact area with the shell-side liquid are adjusted to ensure sufficient heat exchange between the tube-side liquid and the shell-side liquid, thereby improving heat exchange efficiency. Simultaneously, the axial extension section 212 of the tube body 211 extends from the tube-side liquid inlet 14 to the corresponding heat exchange zone 16 of the tube assembly 21, and from the corresponding heat exchange zone 16 to the tube-side liquid outlet 15. During this process, the axial extension section 212 may always be within the corresponding heat exchange zone 16, or it may pass through other heat exchange zones 16. The tube-side liquid within the tube body 211 will also be continuously heated by the shell-side liquid of the corresponding heat exchange zone 16 or other heat exchange zones 16, further improving heat exchange efficiency by utilizing the axial space. It should be noted that this application aims to artificially divide a large bundle of heat exchange tubes 20 into multiple tube groups 21, and allow the main heat exchange portion of each tube group 21, namely the circumferential extension section 213, to exchange heat in the corresponding heat exchange region 16, so as to avoid mutual interference between adjacent tubes 211 of the large bundle of heat exchange tubes 20, thereby affecting the heat exchange uniformity and heat exchange efficiency. Furthermore, those skilled in the art should know that the tubes 211 in the heat exchanger are made of a material that is flexible to a certain extent; therefore, the axial extension section 212 is generally arranged in an axial direction.

[0060] There are many ways to set the baffle 31. In some embodiments, the baffle 31 extends axially, and both ends of the axial direction of each heat exchange region 16 are connected to the shell liquid inlet 12 and the shell liquid outlet 13. This ensures that the shell liquid flowing in from the shell liquid inlet 12 is evenly distributed into each heat exchange region 16, and keeps the shell liquid temperature in each heat exchange region 16 basically the same or with a small temperature difference. The axial extension section 212 and the circumferential extension section 213 of the tube assembly 21 are both located in the corresponding heat exchange region 16. The circumferential extension section 213 does not extend circumferentially around the center of the accommodating area, but instead circles around itself to be evenly distributed in the heat exchange region 16. The total length of the tube body 211 is relatively long.

[0061] And Benru Figure 2 In the first embodiment shown, multiple baffles 31 are arranged perpendicular to the axial direction in the receiving space 11, such that the heat exchange regions 16 are spaced apart in the axial direction of the receiving space 11. In non-corresponding heat exchange regions 16, the axial extension section 212 of the tube body 211 passes through at least one baffle 31. In the corresponding heat exchange region 16, the circumferential extension section 213 of the tube body 211 extends circumferentially in the heat exchange region 16. Before the axial extension section 212 of the heat pipe enters the corresponding heat exchange region 16 and after it exits the corresponding heat exchange region 16, the tube-side liquid in the tube body 211 will continue to be heated by the shell-side liquid in other heat exchange regions 16, utilizing the axial space to further improve the heat exchange efficiency; at least some of the partition plates 31 are provided with inlet holes 32 and outlet holes 33. The tube group 21 enters the corresponding heat exchange region 16 through the inlet hole 32 and exits the corresponding heat exchange region 16 through the outlet hole 33. The inlet hole 32 and outlet hole 33 can position the heat exchange tube 20, so that the position of the heat exchange tube 20 is fixed and evenly distributed in the heat exchange region 16, ensuring the installation stability of the heat exchange tube 20 and avoiding the tube bodies 211 from stacking on each other and reducing the contact area with the shell-side liquid.

[0062] For a single baffle 31, when each tube group 21 includes multiple tubes 211, the number of inlet holes 32 and outlet holes 33 of the baffle 31 is also multiple. The inlet holes 32 and outlet holes 33 corresponding to a group of tubes 211 form a row and are arranged tangentially on the baffle 31. This arrangement can reduce the interference between the tubes 211 when they extend circumferentially, and maintain the radial clearance between adjacent tubes 211, so that the tubes 211 can fully contact the shell-side liquid. When the number of tube groups 21 is ≥2, the number of rows of inlet holes 32 and outlet holes 33 on some baffles 31 will also be ≥2. Each row of inlet holes 32 is parallel and spaced apart, and each row of outlet holes 33 is parallel and spaced apart, ensuring that the tubes 211 in different groups of tube groups 21 do not interfere with each other and maintain an appropriate distance to facilitate the flow of shell-side liquid.

[0063] As a preferred option, such as Figure 2In the first embodiment shown, a tube sheet 17 is used to connect the inlet end of all heat exchange tubes 20, and another tube sheet 17 is used to connect the outlet end of all heat exchange tubes 20. This ensures that the tube-side liquid flowing into and out of the heat exchanger meets the requirements. In particular, the tube-side liquid flowing out of the heat exchanger can be collected by summing the tube-side liquids in different tube bodies 211 to obtain the required temperature.

[0064] like Figure 2 and Figure 3 As shown, in this embodiment, the tube fluid inlet 14 and the tube fluid outlet 15 are located at the same end of the housing 10. The number of rows of inlet holes 32 and outlet holes 33 on the partition plate 31 closest to the tube fluid inlet 14 and the tube fluid outlet 15 is equal to that of the tube group 21, and decreases by one row in sequence in the direction away from the tube fluid inlet 14 and the tube fluid outlet 15. No inlet holes 32 are provided on the partition plate 31 furthest from the tube fluid inlet 14 and the tube fluid outlet 15.

[0065] With this configuration, all tubes 211 in the tube bundle 21 must pass through the inlet hole 32 of the partition 31 closest to the tube-side liquid inlet 14. Then, one group of tubes 211 enters the corresponding heat exchange zone 16. The remaining tubes 211 of the tube bundle 21 then pass through the next layer of partition 31, and another group of tubes 211 enters the corresponding heat exchange zone 16. This process is repeated to gradually reduce the number of tube bundles 21 until the last group of tubes 211 passes through the second-to-last partition 31, enters the corresponding heat exchange zone 16, and extends circumferentially. The tubes extend out through the outlet hole 33 and together with the tube bundles 21 of the heat exchange zone 16 above, they extend upwards until the tube bodies 211 of all tube bundles 21 extend out through the outlet hole 33 of the partition 31 closest to the tube-side liquid inlet 14. Thus, as the distance from the tube-side liquid inlet 14 and the tube-side liquid outlet 15 increases, the length of the tube body 211 of the tube bundle 21 also increases, and the contact time with the shell-side liquid also increases. This compensates for the temperature change of the shell-side liquid during the process of flowing to the distant heat exchange zone 16, and ensures the heat exchange effect of the tube bodies 211 in each heat exchange zone 16.

[0066] Specifically, such as Figure 4In the first embodiment shown, there are four partitions 31, forming three axially distributed heat exchange zones 16. There are also three sets of corresponding tube assemblies 21. Therefore, the uppermost partition 31 has three rows of inlet holes 32 and three rows of outlet holes 33. The tubes 211 of the three sets of tube assemblies 21 connected to the tube-side liquid inlet 14 enter the first-layer heat exchange zone 16 through the corresponding row of inlet holes 32. One set of tubes 21 extends circumferentially in the first-layer heat exchange zone 16 and then exits through the outlet hole 33 on the uppermost partition 31. The remaining two sets of tubes 211 continue through the corresponding row of inlet holes 32 on the second partition 31 to enter the second-layer heat exchange zone. In zone 16, the tube body 211 of a group of tubes 21 extends circumferentially in the heat exchange zone 16 of the second layer, and then passes through the outlet hole 33 on the second partition 31 to enter the heat exchange zone 16 of the first layer, and then continues to extend axially until it passes through a row of outlet holes 33 on the uppermost partition 31; the tube body 211 of the last group of tubes 21 continues to extend axially, passes through a row of inlet holes 32 on the third partition 31, enters the heat exchange zone 16 of the third layer, and after circumferential extension, it axially passes through a row of outlet holes 33 on the third partition 31, the second partition 31 and the first partition 31 in sequence. Thus, the tube body 211 of the three groups of tubes 21 is connected to the tube-side liquid outlet 15.

[0067] In other embodiments, the tube-side liquid inlet 14 and the tube-side liquid outlet 15 are located at the axial ends of the shell 10. In this case, the inlet hole 32 and the outlet hole 33 are the same hole. The total number of rows of inlet holes 32 and outlet holes 33 on each partition 31 is the same as the number of tube groups 21. Taking four partitions 31 and three tube groups 21 as an example, the tube bodies 211 of the three tube groups 21 connected to the tube-side liquid inlet 14 enter the heat exchange area 16 of the first layer through the corresponding row of inlet holes 32. The tube body 211 of one tube group 21 extends circumferentially in the heat exchange area 16 of the first layer, and then exits through the corresponding row of outlet holes 33 on the second partition 31, the third partition 31 and the fourth partition 31, and connects with the tube-side liquid outlet 15. The tube bodies 211 of the other two tube groups 21 extend axially directly through the corresponding row of inlet holes 32 on the second partition 37 and enter the second layer. In the heat exchange zone 16, the tubes 211 of one group of tubes 21 extend circumferentially in the heat exchange zone 16 of the second layer, and then pass through the corresponding row of outlet holes 33 on the third and fourth partitions 31, communicating with the tube-side liquid outlet 15; the tubes 211 of the remaining group of tubes 21 continue to extend axially directly through the corresponding row of inlet holes 32 on the third partition 39, enter the heat exchange zone 16 of the third layer, and extend circumferentially, and then pass through the corresponding row of outlet holes 33 on the fourth partition 31, communicating with the tube-side liquid outlet 15; thus, the total length of the tubes 211 in each group of tubes 21 is equivalent, and the heat exchange time of the tube-side liquid in the tube body 211 within the containment space 11 is also equivalent, but since there is still a temperature difference between the shell-side liquid in the heat exchange zone 16 farthest from the shell-side liquid inlet 12, the heat exchange effect of the tubes 21 in the heat exchange zone 16 is not optimal.

[0068] In Example 1, as Figure 6 As shown, on the same partition 31, the inlet hole 32 and the outlet hole 33 are symmetrically arranged about the center of the partition 31, so that the distance between the part of the tube body 211 that enters the heat exchange area 16 and the part that exits the heat exchange area 16 is large, avoiding interference and facilitating tube insertion.

[0069] In Example 1, as Figure 3 As shown, the partition 31 includes a first partition 34 and a second partition 37 alternately arranged along the axial direction of the shell 10. The center of the first partition 34 has a first channel 35 that penetrates the upper and lower surfaces of the first partition 34. The center of the second partition 37 is a solid structure, and the outer side wall of the second partition 37 is spaced apart from the inner wall of the shell 10 to form a second channel 38. The first channel 35, the second channel 38 and each heat exchange area 16 are connected to form a heat exchange channel that is connected to the shell liquid inlet 12 and the shell liquid outlet 13.

[0070] Several first baffles 34 and second baffles 37 are fixed in the receiving space 11 in an alternating manner. This allows the shell-side liquid to flow from one heat exchange region 16 to another in a radial flow pattern, then turn to axial movement, and then turn back to radial flow, repeating this process until it exits the shell-side liquid outlet 13. This forms a "string"-shaped flow channel, extending the flow path and allowing the liquid to contact more heat exchange tubes 20 within a limited space. This results in a larger heat exchange surface area, ensuring sufficient heat exchange between the shell-side liquid and the tube-side liquid, and improving heat exchange efficiency. Thermal efficiency: Due to the different positions of the first channel 35 and the second channel 38, the shell-side liquid can be guided to fully fill the entire containment space 11, so that the heat exchange tubes 20 in different areas can exchange heat with the shell-side liquid. Moreover, the shell-side liquid flows in a directional manner according to the flow channel, realizing rapid flow and renewal of the shell-side liquid. This avoids the situation where some shell-side liquid leaves the heat exchanger without sufficient heat exchange. In addition, when the shell-side liquid flows through each bend, due to inertia, eddies and velocity gradients will be generated at the corners. This helps to break the boundary layer, promote the mixing inside the fluid, and enhance the heat transfer effect.

[0071] In this first embodiment, the outer wall of the first partition 34 is adapted to the inner wall of the shell 10 to prevent the shell liquid entering from the shell liquid inlet 12 from flowing directly to the shell liquid outlet 13 through the second channel 38 without entering the heat exchange area 16.

[0072] It should be noted that the outer wall of the first partition 34 is adapted to the inner wall of the shell 10. This means that the outer diameter of the outer wall of the first partition 34 is basically the same as the inner diameter of the inner wall of the shell 10. The outer wall of the first partition 34 can be tightly attached to the inner wall of the shell 10, or there can be installation tolerances. Even if there are tiny gaps, it is generally impossible for the shell-side fluid to flow through the gaps in large quantities. At most, there will be a small amount of seepage, which will not affect the flow direction of most of the shell-side fluid.

[0073] In this first embodiment, the support 30 also includes a third partition 39 extending along the axial direction. Several third partitions 39 are distributed circumferentially to divide each heat exchange area 16 into several fan-shaped flow channels 161. The third partition 39 is provided with a through hole 391. The tube body 211 is inserted into the through hole 391 on each third partition 39 in sequence and extends circumferentially at least one circle.

[0074] The first baffle 34 and the second baffle 37 are respectively installed at different heights of the third baffle 39; a plurality of third baffles 39 are circumferentially distributed around the first baffle 34 and the second baffle 37 to divide each heat exchange zone 16 into multiple fan-shaped flow channels 161. Each fan-shaped flow channel 161 is connected to the first flow channel and the second flow channel. The shell-side liquid can diffuse or converge along the fan-shaped flow channel 161, further guiding the flow direction of the shell-side liquid, making the shell-side liquid more evenly distributed in each fan-shaped flow channel 161, reducing the situation where some shell-side liquid leaves the heat exchanger without sufficient heat exchange, and reducing fluid dead zones, ensuring that the shell-side liquid flows fully in the entire containment space 11; in addition, due to the guiding effect of the fan-shaped flow channel 161, the overall pressure drop can be controlled within a reasonable range while ensuring sufficient heat exchange efficiency, reducing transport energy consumption.

[0075] Preferably, it is necessary to ensure that each fan-shaped flow channel 161 is relatively independent in the circumferential direction. That is, the shell-side fluid should be controlled to have as little circumferential flow as possible near the inner wall of the shell 10 in the fan-shaped flow channel 161, and should move axially through the second flow channel as much as possible. Therefore, in some embodiments, the outer wall of the third partition 39 is adapted to the inner wall of the shell 10, that is, the outer diameter of the outer wall of the third partition 39 is basically equivalent to the inner diameter of the inner wall of the shell 10. The outer wall of the third partition 39 can be in close contact with the inner wall of the shell 10, or there can be installation tolerances. Even if there are small gaps, it is generally impossible for a large amount of shell-side fluid to flow through the gaps. At most, a small amount of seepage will occur, which will not affect the flow direction of most of the shell-side fluid. The outer wall of the third partition 39 can be flush with the outer wall of the first partition 34. Of course, in the actual installation process, due to processing errors or installation errors, the outer wall of the third partition 39 cannot be flush with the outer wall of the first partition 34, and errors within a reasonable range are allowed. This configuration allows the shell-side liquid within the same sector flow channel 161 to move axially directly to the next sector flow channel 161, preventing the shell-side liquid in adjacent sector flow channels 161 of the same heat exchange region 16 from exchanging with each other near the inner wall of the shell 10. This reduces turbulence and flow. On the other hand, if the shell-side liquid in adjacent sector flow channels 161 of the same heat exchange region 16 were to exchange with each other near the inner wall of the shell 10, some of the shell-side liquid would flow circumferentially near the inner wall of the shell 10, potentially interfering with the axial flow in the second shell-side liquid channel 38. This would affect the rapid flow and renewal of the shell-side liquid in the receiving space 11, thus preventing some of the shell-side liquid from remaining in the receiving space 11 for a long time.

[0076] There are various ways in which the multiple tubes 211 in the tube assembly 21 extend circumferentially. In embodiment one, for example... Figure 4As shown, the tube assembly 21 is composed of multiple tubes 211; the number of rows and columns of the through holes 391 on the third partition 39 is greater than 1 to form a matrix. This matrix is ​​arranged circumferentially in the same heat exchange area 16. For a heat exchange area 16, the circumferential extension of the tube assembly 21 is such that multiple tubes 211 pass through the through holes 391 in the same row on several third partitions 39 from the circumferential direction and then enter the through holes 391 in the adjacent row of a third partition 39. Specifically, in this embodiment, the multiple through holes 391 arranged in a matrix on each third partition 39 have essentially the same axial height in each row and essentially the same radial distance from each column to the axis of the shell 10. After the tube group 21 enters the corresponding heat exchange area 16 from the first partition 34 or the second partition 37, multiple tubes 211 pass through the first row of through holes 391 on the same third partition 39, and then through the first row of through holes 391 on the next third partition 39, until they pass through the first row of through holes 391 on all third partitions 39, and then sequentially through the second row of through holes 391 on all third partitions 39, and so on, until they exit through the outlet hole 33 on the first partition 34 or the second partition 37. The circumferential extension method of a single tube 211 is as follows: Figure 5 As shown. Using the above method, all third baffles 39 can have the same structure and the same installation height. The structure is simple and easy to assemble, which is beneficial to improving the heat exchange efficiency of the heat exchanger and reducing the pressure drop of the shell-side liquid.

[0077] In other embodiments, within a heat exchange zone 16, the tube 211 extends circumferentially in a cylindrical spiral manner, thereby appropriately varying the height of the through-hole 391 on each third partition 39.

[0078] like Figure 7 and Figure 8The difference between Embodiment 2 and Embodiment 1 lies in the way the heat exchange tubes 20 are inserted into the support 30. Specifically, the arrangement of the inlet holes 32 and outlet holes 33 on the first partition 34 and the second partition 37 is different. In this embodiment, the inlet holes 32 and outlet holes 33 corresponding to a group of tubes 21 are circumferentially spaced, and the inlet holes 32 and outlet holes 33 of each group are radially spaced. The through holes 391 on the third partition 39 are also matrix-distributed. For the tube groups 21 in the same heat exchange area 16, the tube body 211 extends from the first partition 34 or the second partition 37. The inlet holes 32 on the second partition 37 enter the corresponding heat exchange area 16. In a group of tubes 21, the number of tubes 211 is the same as the number of through holes 391 in the same column. Several tubes 211 in the tube group 21 are inserted into through holes 391 with the same center distance on the same third partition 39. When passing through adjacent third partitions 39, the center distance of the through holes 391 is the same. When the number of columns is greater than 1, after the tubes 211 pass through through holes 391 of the same height on all third partitions 39, they are inserted into through holes 391 in adjacent columns in sequence until they exit the corresponding heat exchange area 16. For example, multiple tubes 211 pass through the first row of through holes 391 with the farthest center-to-center distance on the same third partition 39, then through the first row of through holes 391 on the next third partition 39, and so on, until they pass through the first row of through holes 391 on all third partitions 39. Then they pass through the second row of through holes 391 on all third partitions 39, and so on, until they exit through the outlet hole 33 on the inner side of the first partition 34 or the second partition 37. Alternatively, the tube 211 can first pass through the row with the smallest center-to-center distance, and then sequentially pass through the corresponding row of through holes 391 outwards. The circumferential extension method of a single tube 211 is as follows: Figure 8 As shown. Using the above method, all third partitions 39 can have the same structure and installation height, resulting in a simple structure, convenient assembly, and improved heat exchanger production efficiency. Other structures in Embodiment 2 can be referred to Embodiment 1, and will not be repeated here.

[0079] In other embodiments, within a heat exchange zone 16, the tube 211 extends circumferentially in a spiral pattern, thereby appropriately varying the center distance of the through holes 391 on each third partition 39 to meet the through requirements of the tube 211.

[0080] Both of the above embodiments ensure that the tube 211 maintains circumferential and axial clearances with itself or adjacent tubes 211 within the heat exchange region 16. This ensures that the tube 211 has sufficient length within the heat exchange region 16 while maintaining adequate contact with the shell-side liquid, resulting in high heat exchange efficiency. Furthermore, each tube 211 is spirally arranged in a planar or vertical manner within the heat exchange region 16, and multiple tubes 211 forming a tube group 21 extend in an orderly manner within the heat exchange region 16, creating a three-dimensional arrangement. This further increases the space utilization of the heat exchange region 16, thereby increasing heat exchange efficiency.

[0081] Preferably, in both embodiments, the angle A between the tube body 211 and the third baffle 39 in the liquid inlet direction is between 30° and 60°. With the tube body 211 positioned in this way, supported by the through-hole 391, the angle ensures a more stable flow path within the tube body 211. Furthermore, since the circumferential extension 213 and the axial extension 212 of the tube body 211 connect at the third baffle 39, the tube-side liquid changes from axial to circumferential flow. A large angle change would cause excessive pressure loss and increased turbulence intensity. Additionally, setting the angle between the tube body 211 and the third baffle 39 to between 130° and 160° allows the tube-side liquid to change angle slowly during outlet, preventing the heat exchange tube 20 from swaying in the heat exchange zone 16 during use and avoiding friction between the tube body 211 and the inlet hole 32, outlet hole 33, or through-hole 391, which could even cause wear to the tube body 211.

[0082] Preferably, in both embodiments, the gap between adjacent tubes 211 is D1, and the diameter of the tube 211 is D2; 1.4 ≤ D1 / D2 ≤ 2.3. On the one hand, controlling the size of the gap D1 avoids an excessively large gap, which would result in a small total length of the tubes 211 within a single heat exchange region 16, leading to a smaller amount of tube-side liquid flowing in the tubes 211 within the heat exchange region 16 per unit time and lower heat exchange efficiency. Conversely, an excessively small gap would hinder the flow of shell-side liquid between adjacent tubes 211 and prevent sufficient contact with the tubes 211. On the other hand, it is also necessary to control... The diameter of tube 211 is carefully controlled to avoid both excessively small diameters, which would increase the flow resistance of the tube-side liquid, and excessively large diameters, which would prevent sufficient heat exchange between the tube-side liquid and the shell-side liquid, resulting in an excessively large temperature gradient within tube 211 and reduced heat exchange efficiency. By controlling the ratio of these two factors within the specified range, the total length of tube 211 within a single heat exchange zone 16 and the total amount of tube-side liquid undergoing heat exchange per unit time are ensured, as well as the rapid flow of the shell-side liquid and its sufficient contact with tube 211 for heat exchange, thus guaranteeing heat exchange efficiency.

[0083] like Figure 9 The difference between Embodiment 3 shown in the figure and Embodiments 1 and 2 is that the partition 31 includes a second partition 37 and multiple first partitions 34 located axially above the second partition 37; the center of the first partition 34 has a first channel 35 penetrating the upper and lower surfaces of the first partition 34, and a portion of the outer wall of the first partition 34 is spaced apart from the inner wall of the shell 10 to form a liquid collection channel 36; the center of the second partition 37 is a solid structure, and the outer wall of the second partition 37 is spaced apart from the inner wall of the shell 10 to form a second channel 38; wherein, at least a portion of the shell-side liquid in the first channel 35 enters the liquid collection channel 36 after passing through the heat exchange area 16, and enters the shell-side liquid outlet 13 through the second channel 38.

[0084] Preferably, the first partition 34 closest to the shell-side liquid inlet 12 is adapted to the interior of the shell 10, that is, the outer diameter of the outer side wall of the first partition 34 is basically the same as the inner diameter of the inner wall of the shell 10. The outer side wall of the first partition 34 can be tightly attached to the inner wall of the shell 10, or there can be installation tolerance. Even if there are small gaps, it is generally impossible for the shell-side liquid to flow through the gaps in large quantities. At most, there will be a small amount of seepage, which will not affect the flow direction of most of the shell-side liquid.

[0085] With this configuration, the shell-side liquid can quickly reach each heat exchange zone 16 after entering the containment space 11 from the shell-side liquid inlet 12, especially the heat exchange zone 16 furthest from the shell-side liquid inlet 12. This further improves the temperature uniformity of the shell-side liquid in each heat exchange zone 16, making the temperature difference between the heat exchange zone 16 closest to the shell-side liquid inlet 12 and the heat exchange zone 16 furthest from the shell-side liquid inlet 12 smaller, which is beneficial to improving the heat exchange effect of the tube 211 in each heat exchange zone 16. The purpose of setting up the liquid collection channel 36 is to promote the flow of shell-side liquid in the heat exchange zone 16 and avoid the formation of dead zones. The shell-side liquid entering the heat exchange zone 16 flows to the liquid collection channel 36, and then flows to the second channel 38 and the shell-side liquid outlet 13.

[0086] like Figure 11 As shown, the aperture of the first channel 35 on the first partition 34 gradually decreases along the axial direction. That is, the aperture of the first channel 35 near the shell liquid inlet 12 is larger, and the aperture of the first channel 35 near the shell liquid outlet 13 is smaller. This is because the shell liquid gradually flows towards the liquid collection channel 36 during the flow process. Gradually reducing the aperture of the first channel 35 can keep the hydraulic pressure of each heat exchange zone 16 basically consistent, and ensure that the shell liquid flows smoothly in the containment space 11.

[0087] The above embodiments are merely preferred embodiments of this utility model and should not be construed as limiting the scope of protection of this utility model. Any non-substantial changes and substitutions made by those skilled in the art based on this utility model shall fall within the scope of protection claimed by this utility model.

Claims

1. A heat exchanger, comprising a shell and heat exchange tubes located within the shell, the shell including a receiving space, a shell-side liquid inlet and a shell-side liquid outlet communicating with the receiving space, and a tube-side liquid inlet and a tube-side liquid outlet, characterized in that, The containment space is provided with a support, the support includes partitions, and a plurality of partitions are spaced apart to divide the containment space into a plurality of heat exchange zones, each heat exchange zone being connected to the shell-side liquid inlet and the shell-side liquid outlet. The heat exchange tubes include several tube groups, each tube group consisting of at least one tube body, and the tube body has a flow channel for the flow of the tube-side liquid. The tube body includes a circumferential extension section and an axial extension section. In the same tube group, the circumferential extension section of the tube body corresponds to a heat exchange region and extends at least one circumference in the heat exchange region. The axial extension section extends from the tube-side liquid inlet to the heat exchange region corresponding to the tube group, and extends from the corresponding heat exchange region to the tube-side liquid outlet.

2. The heat exchanger as described in claim 1, characterized in that, The partition is arranged perpendicular to the axial direction within the accommodating space. At least a portion of the partition is provided with inlet and outlet pipe holes. The pipe group enters the corresponding heat exchange area through the inlet pipe hole and exits the corresponding heat exchange area through the outlet pipe hole.

3. The heat exchanger as described in claim 2, characterized in that, The inlet and outlet pipes are tangentially arranged on the partition plate; When the number of rows of inlet holes is ≥2, the inlet holes in each row are parallel to each other and spaced apart, and / or, when the number of rows of outlet holes is ≥2, the outlet holes in each row are parallel to each other and spaced apart.

4. The heat exchanger as described in claim 3, characterized in that, The inlet and outlet of the tube fluid are located at the same end of the housing. The number of rows of inlet and outlet holes on the partition closest to the inlet and outlet of the tube fluid is equal to that of the tube assembly, and decreases by one row in sequence towards the direction away from the inlet and outlet of the tube fluid. No inlet hole is provided on the partition furthest from the inlet and outlet of the tube fluid.

5. The heat exchanger as described in claim 2, characterized in that, On the same partition plate, the inlet and outlet pipes are symmetrically arranged about the center of the partition plate.

6. The heat exchanger as described in claim 1, characterized in that, The partition includes a first partition and a second partition that are alternately spaced along the axial direction of the shell. The center of the first partition has a first channel that penetrates the upper and lower surfaces of the first partition. The center of the second partition is a solid structure, and the outer side wall of the second partition is spaced apart from the inner wall of the shell to form a second channel. The first channel, the second channel, and each of the heat exchange areas are connected to form a heat exchange channel that is connected to the shell liquid inlet and the shell liquid outlet.

7. The heat exchanger as claimed in claim 1, characterized in that, The partition includes a second partition and multiple first partitions located axially above the second partition; The first partition has a first channel through the upper and lower surfaces of the first partition at its center, and a portion of the outer wall of the first partition is spaced apart from the inner wall of the shell to form a liquid collection channel; The center of the second partition is a solid structure, and the outer wall of the second partition is spaced apart from the inner wall of the shell to form a second channel; In this process, at least a portion of the shell-side liquid in the first channel enters the liquid collection channel after passing through the heat exchange area, and then enters the shell-side liquid outlet through the second channel.

8. The heat exchanger according to any one of claims 1 to 7, characterized in that, The support also includes a third partition extending along the axial direction. Several of the third partitions are circumferentially spaced to divide each heat exchange area into several fan-shaped flow channels. The third partitions are provided with through holes, and the tubes are sequentially inserted into the through holes on each of the third partitions and extend circumferentially at least one circle.

9. The heat exchanger as described in claim 8, characterized in that, The tube assembly consists of multiple tubes; the number of rows and columns of the through holes on the third partition plate is greater than 1 to form a matrix, which is arranged circumferentially in the same heat exchange area; The circumferential extension methods of the pipe assembly include: Multiple tubes pass through the same row of through holes on several third partitions in a circumferential direction and then enter the through holes in an adjacent row of a third partition. or, Multiple tubes pass circumferentially through the same column of through holes on several third partitions and then enter the adjacent column of through holes in one of the third partitions.

10. The heat exchanger as claimed in claim 8, characterized in that, In the liquid inlet direction, the angle between the tube body and the third partition is between 30° and 60°; and / or, in the liquid outlet direction, the angle between the tube body and the third partition is between 130° and 160°.

11. The heat exchanger as claimed in claim 1, characterized in that, The gap between adjacent pipes is D1, and the diameter of the pipe is D2; 1.4≤D1 / D2≤2.3.

Images