Heat exchanger

Abstract

The application relates to the technical field of heat exchange equipment, in particular to a heat exchanger. The heat exchanger comprises a shell, a separation assembly and a heat exchange assembly. The shell has a cavity, a fluid inlet and a fluid outlet which are communicated with the cavity respectively; the separation assembly is arranged in the cavity and separates the cavity into a serpentine flow channel for fluid flow, the flow channel reciprocates and returns in a first direction; the heat exchange assembly is arranged in the shell, the heat exchange assembly comprises a plurality of heat exchange coils which are arranged at intervals in the first direction, each heat exchange coil reciprocates and returns in a second direction and is arranged in an interlaced mode with the serpentine flow channel; wherein the angle between the first direction and the second direction is between 30 DEG and 150 DEG. The heat exchanger optimizes the structure, and the heat exchange efficiency of the fluid is improved.

Description

Technical Field

[0001] This application relates to the field of heat exchange equipment, and more specifically, to a heat exchanger. Background Technology

[0002] A heat exchanger is a device used to transfer heat between two or more fluids. It is widely used in industries such as industrial, energy, chemical, refrigeration, air conditioning, and food processing. The working principle of a heat exchanger is based on the second law of thermodynamics, which states that heat transfers from a high-temperature object to a low-temperature object. Its core principle is to separate the two fluids through solid walls such as heat exchange plates or tubes, preventing direct contact, while allowing heat to be transferred from the high-temperature fluid to the low-temperature fluid through the walls.

[0003] In related technologies, heat exchangers generally include a shell and heat exchange coils disposed within the shell. The heat exchange coils are used to flow the heat exchange medium, and the fluid comes into contact with the heat exchange coils as it flows through the shell, thereby exchanging heat. However, the heat exchange efficiency of heat exchangers in related technologies is low. Utility Model Content

[0004] The purpose of this application is to overcome the shortcomings of the above-mentioned related technologies and to provide a heat exchanger with high heat exchange efficiency.

[0005] To achieve the above objectives, this application adopts the following technical solution: The heat exchanger provided in this application includes a shell, a partition assembly, and a heat exchange assembly. The shell has a chamber and a fluid inlet and a fluid outlet respectively communicating with the chamber. The partition assembly is disposed within the chamber and divides the chamber into a serpentine flow channel for fluid flow, the flow channel reciprocating in a first direction. The heat exchange assembly is disposed within the shell and includes a plurality of heat exchange coils spaced apart in the first direction, each heat exchange coil reciprocating in a second direction and staggered with the serpentine flow channel; wherein the angle between the first direction and the second direction is between 30° and 150°. This heat exchanger improves the heat exchange efficiency of the fluid by optimizing its structure. The angle between the first direction and the second direction is 90°.

[0006] According to one embodiment of this application, the housing includes a first side plate and a second side plate disposed opposite to each other in a first direction, and a first end plate and a second end plate respectively fixed to opposite sides of the first side plate and the second side plate; the flow channel reciprocates between the first side plate and the second side plate, and the heat exchange coil reciprocates between the first end plate and the second end plate.

[0007] According to one embodiment of this application, the partition assembly includes a plurality of partition plates spaced apart along a third direction. The partition plates extend along the first direction, and one end of each partition plate is alternately fixed to a first side plate and a second side plate. A notch is formed between the other end of the partition plate fixed to the first side plate and the second side plate, and a notch is formed between the other end of the partition plate fixed to the second side plate and the first side plate. The plurality of notches communicate with the space between adjacent partition plates to form the flow channel, wherein the third direction is perpendicular to the first direction and the second direction.

[0008] According to one embodiment of this application, the flow area of ​​the gap gradually decreases along the fluid path from the fluid inlet to the fluid outlet.

[0009] According to one embodiment of this application, the end of the partition plate near the notch is provided with a flow-dispersing portion.

[0010] According to one embodiment of this application, the turbulence portion is a turbulence hole penetrating the partition plate.

[0011] According to one embodiment of this application, multiple turbulence holes are provided, and the flow areas of the multiple turbulence holes are different.

[0012] According to one embodiment of this application, a plurality of turbulence holes are provided, and the plurality of turbulence holes are uniformly arranged along the second direction. The sum of the flow areas of all turbulence holes on each partition plate is S1, and the flow area of ​​the notch at the end of the partition plate is S2. S1 and S2 satisfy: 0.07≤S1:S2≤0.15.

[0013] According to one embodiment of this application, the distance between the centerlines of two adjacent heat exchange coils in the first direction is L1, and the size of the turbulence hole in the first direction is L2; ​​L1 and L2 satisfy: 1≤L1:L2≤2.5.

[0014] According to one embodiment of this application, each heat exchange coil includes a plurality of extension tube segments and a plurality of U-shaped tube segments. The extension tube segments extend along the second direction, and the plurality of extension tube segments are spaced apart in the third direction. The plurality of U-shaped tube segments are respectively connected to the ends of adjacent extension tube segments. In the third direction, at least two layers of extension tube segments are provided between adjacent partition plates, and the at least two layers of extension tube segments are staggered in the third direction, wherein the third direction is perpendicular to the first direction and the second direction.

[0015] According to one embodiment of this application, the distance between two adjacent partition plates is D1; ​​the distance between the centerlines of the two extended pipe sections located between the two adjacent partition plates is D2; D1 and D2 satisfy: 1≤D1: D2≤2.5.

[0016] According to one embodiment of this application, the two ends of the extension tube section of the heat exchange coil are respectively inserted through the first end plate and the second end plate, and the U-shaped tube section is disposed outside the shell.

[0017] According to one embodiment of this application, the heat exchange assembly further includes an outlet manifold and a plurality of L-shaped outlet connecting pipes, one end of each of the plurality of outlet connecting pipes being connected to a plurality of the extended pipe segments respectively, and the other end of each being connected to the outlet manifold, which is located outside the housing; and / or

[0018] The heat exchange assembly also includes an inlet manifold and multiple L-shaped inlet connecting pipes. One end of each of the multiple inlet connecting pipes is connected to one of the multiple extension pipe sections, and the other end of each is connected to the inlet manifold. The inlet manifold is located outside the housing.

[0019] According to one embodiment of this application, each partition plate has at least one turbulence protrusion at each end along the second direction.

[0020] According to one embodiment of this application, at least a portion of the at least one turbulence protrusion is provided with a through hole; and / or

[0021] Each partition plate has a plurality of uniformly arranged turbulence protrusions at both ends along the second direction, and an arc-shaped groove is formed between two adjacent protrusions. The heat exchange coil is disposed in the groove and maintains a gap with the groove.

[0022] An embodiment of the above application has at least the following advantages or beneficial effects: The heat exchanger of this application uses a partition component to divide the chambers of the shell into serpentine flow channels, with the serpentine flow channels zigzagging back and forth in the first direction. Simultaneously, multiple heat exchange coils constituting the heat exchange assembly zigzag back and forth in the second direction, interleaving with the serpentine flow channels. The angle between the first and second directions ranges from 30° to 150°. This causes the fluid to impact the heat exchange coils multiple times during flow, enhancing fluid turbulence and increasing the contact time and contact area between the fluid and the heat exchange assembly, resulting in more thorough heat exchange and significantly improving the heat exchanger's efficiency. Due to the improved heat exchange efficiency, compared to traditional heat exchangers, it is not necessary to increase the number of heat exchangers to achieve the same heat exchange effect, thereby reducing equipment procurement costs, installation costs, and subsequent operation and maintenance costs. Furthermore, the heat exchanger of this application achieves highly efficient heat exchange within the shell chamber, eliminating the need for a large external structure to meet heat exchange requirements. Therefore, the overall structure of the heat exchanger of this application is more compact, occupying less space, and is suitable for various applications with high space requirements. Attached Figure Description

[0023] Figure 1 This is a three-dimensional structural diagram of the heat exchanger according to an embodiment of the present utility model; Figure 2 yes Figure 1 Exploded view of the heat exchanger in the image; Figure 3 This is a three-dimensional structural diagram of part of the heat exchanger's shell and partition components; Figure 4 yes Figure 1 A three-dimensional structural diagram of the heat exchanger after removing the manifold; Figure 5 yes Figure 4 Top view; Figure 6 yes Figure 5 Sectional view along line AA; Figure 7 yes Figure 6 Enlarged structural diagram at point B; Figure 8 yes Figure 1 A schematic diagram of the heat exchanger coil in the heat exchanger; Figure 9 yes Figure 1 A schematic diagram of the structure of the first side plate, the second side plate, and the partition assembly of the heat exchanger in the diagram; Figure 10 yes Figure 9 Enlarged structural diagram at point C; Figure 11 yes Figure 9 A cross-sectional view along line DD.

[0024] The annotations in the attached figures are explained as follows: 10. Heat exchanger; 100. Shell; 101. Chamber; 102. Fluid inlet; 103. Fluid outlet; 110. First side plate; 120. Second side plate; 130. First end plate; 140. Second end plate; 150. Top plate; 160. Bottom plate; 170. First rectangular frame; 180. Second rectangular frame; 200. Separation assembly; 210. Separation plate; 211. Turbulence protrusion; 2110. Through hole; 2112. Groove; 220. Flow channel; 221. Notch; 230. Turbulence hole; 300. Heat exchange assembly; 310. Heat exchange coil; 311. Extension pipe section; 312. U-shaped pipe section; 313. Inlet connecting pipe; 314. Outlet connecting pipe; 320. Inlet manifold; 330. Outlet manifold; X, First direction; Y, Second direction; Z, Third direction. Detailed Implementation

[0025] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, they are provided so that this application will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore their detailed description will be omitted.

[0026] The features, structures, or characteristics described below can be combined in any suitable manner in one or more embodiments. Numerous specific details are provided in the following description to give a full understanding of embodiments of this application. However, those skilled in the art will recognize that the technical solutions of this application can be practiced without one or more of the specific details, or other methods, components, materials, etc., can be employed. In other instances, well-known structures, materials, or operations are not shown or described in detail to avoid obscuring various aspects of this application.

[0027] like Figure 1 and Figure 2 As shown, the heat exchanger 10 provided in this embodiment includes: a shell 100, a partition assembly 200 and a heat exchange assembly 300, wherein the shell 100 has a chamber 101 inside.

[0028] The partition component 200 is disposed in the chamber 101 and divides the chamber 101 into a serpentine flow channel 220 for fluid flow, so that the fluid can flow along the flow channel 220, avoiding the fluid from flowing randomly in the chamber, and helping to improve the orderliness and controllability of the fluid flow.

[0029] The heat exchange component 300 is disposed in the housing 100 and extends into the flow channel 220. A heat exchange medium, such as hot water or steam, flows inside the heat exchange component 300. When the fluid flows in the flow channel 220, it comes into contact with the heat exchange component 300 and exchanges heat through heat conduction, heat radiation, etc., thereby changing the temperature of the fluid.

[0030] like Figure 1 , Figure 2 and Figure 3As shown, the housing 100 includes a first side plate 110 and a second side plate 120 disposed opposite each other in a first direction X, a first end plate 130 and a second end plate 140 disposed opposite each other in a second direction Y, a top plate 150 and a bottom plate 160 disposed opposite each other in a third direction Z, and a first rectangular frame 170 and a second rectangular frame 180. The first side plate 110 is fixed to the first rectangular frame 170, and the second side plate 120 is fixed to the second rectangular frame 180. The first end plate 130 and the second end plate 140 are respectively fixed to both sides of the first rectangular frame 170 and the second rectangular frame 180 along the second direction Y. The top plate 150 and the bottom plate 160 are respectively fixed to both sides of the first rectangular frame 170 and the second rectangular frame 180 along the third direction Z. In this embodiment, the first direction X, the second direction Y, and the third direction Z are all perpendicular to each other. In other embodiments, the first direction X and the second direction Y may not be perpendicular, for example, the angle between them may be between 30° and 150°, and the third direction Z is perpendicular to the first direction X and the second direction Y.

[0031] The first side plate 110, the second side plate 120, the first end plate 130, the second end plate 140, the top plate 150, and the bottom plate 160 together form a closed chamber 101. The housing 100 is provided with a fluid inlet 102 and a fluid outlet 103 communicating with the chamber 101. The fluid inlet 102 and the fluid outlet 103 are spaced apart in the third direction (Z). In this embodiment, the fluid inlet 102 is located on the top plate 150 near the first side plate 110, and the fluid outlet 103 is located at the bottom of the first side plate 110. In other embodiments, the fluid outlet 103 may also be located on the first side plate 110, the second side plate 120, or the bottom plate 160.

[0032] like Figure 3 , Figure 4 and Figure 6 As shown, the partition assembly 200 includes a plurality of partition plates 210 parallel to each other in a third direction Z, extending along a first direction X. In a plane perpendicular to the third direction Z, the orthographic projections of two adjacent partition plates 210 partially overlap. One end of each partition plate 210 is alternately fixed to a first side plate 110 and a second side plate 120, with a notch 221 formed between the other end of the partition plate 210 fixed to the first side plate 110 and the second side plate 120, and a notch 221 also formed between the other end of the partition plate 210 fixed to the second side plate 120 and the first side plate 110. The notches 221 communicate with the spaces between adjacent partition plates 210, thereby forming flow channels 220. This arrangement forces the fluid to continuously change direction during flow.

[0033] In detail, such as Figure 3 and Figure 6As shown, in the first direction X, the partition plate 210 has two opposite ends; in the third direction Z, one end of the first partition plate 210 from top to bottom is fixed to the first side plate 110, and a notch 221 is formed between the other end of the first partition plate 210 and the second side plate 120; one end of the second partition plate 210 from top to bottom is fixed to the second side plate 120, and a notch 221 is formed between the other end of the second partition plate 210 and the first side plate 110; this arrangement is repeated until the bottom partition plate 210, thereby forming a serpentine flow channel 220 in the chamber 101. Fluid enters through the fluid inlet 102, passes through the guiding action of multiple partition plates 210 in sequence, and then flows out from the fluid outlet 103.

[0034] Specifically, as the fluid travels along the flow channel 220, it turns at the notch 221 to change direction. This turning flow effectively increases the fluid's travel distance within the chamber 101, allowing it to have more contact opportunities with the heat exchange coil 310 within the limited internal space, thus extending the heat exchange path and facilitating more thorough heat exchange.

[0035] Furthermore, each time the fluid turns through the notch 221, the flow state changes drastically, generating strong disturbances. These disturbances disrupt the fluid boundary layer, allowing for more thorough mixing within the fluid and increasing the heat transfer coefficient between the fluid and the surface of the heat exchange component 300. The disruption of the boundary layer means reduced resistance to heat transfer, enabling faster and more efficient heat transfer from the heat exchange component 300 to the fluid, and vice versa, significantly improving the heat transfer effect.

[0036] Along the fluid path from fluid inlet 102 to fluid outlet 103, the flow area of ​​gap 221 gradually decreases, causing the fluid velocity from fluid inlet 102 to fluid outlet 103 to gradually increase. In the early stage, sufficient heat exchange occurs, and in the later stage, the flow velocity increases, thereby improving heat exchange efficiency.

[0037] To improve the connection stability between the partition plate 210 and the first side plate 110 or the second side plate 120, a flange structure can be provided at the end of the partition plate 210 to achieve fixation with the first side plate 110 or the second side plate 120. The flange structure can be fixed to the shell 100 by welding, screwing, riveting, or other connection methods, which are not limited in this embodiment.

[0038] like Figure 4 , Figure 5 and Figure 6As shown, the heat exchange assembly 300 includes a plurality of heat exchange coils 310 spaced apart in the first direction X, each heat exchange coil 310 reciprocating in the second direction Y; the flow channel 220 reciprocates in the first direction X, and the heat exchange coils 310 and the serpentine flow channel 220 are arranged alternately. The reciprocating arrangement of the flow channel 220, forming a serpentine shape, can extend the flow path of the fluid, thereby extending the contact time between the fluid and the heat exchange assembly 300 during the flow process, which is conducive to more fully absorbing or releasing heat and improving the heat exchange efficiency of the heat exchanger 10.

[0039] The angle between the first direction X and the second direction Y is between 30° and 150°. This means that the heat exchange coil 310 and the serpentine flow channel 220 are spatially intersecting, meaning the fluid flow direction along the partition plate 210 is not parallel to the heat exchange coil 310, allowing the heat exchange coil 310 to turbulentize the fluid. Specifically, as the fluid flows along the flow channel 220, it impacts the heat exchange component 300, thereby changing the fluid's flow direction and velocity, resulting in a complex flow pattern within the flow channel 220. This disturbance disrupts the stability of the boundary layer, promotes internal mixing of the fluid, increases the heat transfer coefficient, and further enhances heat exchange efficiency.

[0040] Furthermore, the angle between the heat exchange coil 310 and the serpentine flow channel 220 can be 30°, 50°, 70°, 90°, 110°, 120°, 150°, or any value between any two adjacent values ​​mentioned above. In this embodiment, the angle between the heat exchange assembly 300 and the flow channel 220 can be 90°.

[0041] The angle between the heat exchange coil 310 and the serpentine flow channel 220 is 90°. Compared with other angle settings, it can more effectively utilize the surface area of ​​the heat exchange component 300 for heat exchange, further improving the heat exchange efficiency per unit area and ensuring that more heat is transferred in a limited space; at the same time, it is more convenient to manufacture and assemble.

[0042] Furthermore, the heat exchange coil 310 is perpendicular to the serpentine flow channel 220, causing the fluid to form a strong turbulent state as it flows through the heat exchange component 300. The vertical flow resistance and change in direction break up the laminar boundary layer, resulting in a more uniform temperature distribution within the fluid and reduced thermal resistance. This turbulent state effectively enhances the heat transfer coefficient between the fluid and the surface of the heat exchange component 300, thereby significantly improving the overall heat exchange performance.

[0043] It should also be noted that the heat exchange medium flowing within the heat exchange coil 310 can be either gas or liquid. The fluid flowing within the shell 100 can also be either gas or liquid. Furthermore, the shell 100 needs to have a certain degree of sealing to prevent fluid leakage. The sealing method of the shell 100 can be set with reference to conventional sealing methods in the art, and this embodiment does not impose any limitations on this.

[0044] This embodiment uses the fluid flowing within chamber 101 as a liquid for description.

[0045] The serpentine flow channel 220 zigs back and forth between the first side plate 110 and the second side plate 120, and the heat exchange coil 310 zigs back and forth between the first end plate 130 and the second end plate 140. This arrangement allows the heat exchange coil 310 and the serpentine flow channel 220 to be spatially angled, enabling the fluid to come into contact with the heat exchange coil 310 multiple times during flow, increasing the heat exchange area, improving the fluid turbulence effect, and thus improving the heat exchanger's heat exchange efficiency.

[0046] In the aforementioned "reciprocating turnaround," "turnaround" refers to the process of going from the first side to the second side, turning around on the second side, and then returning to the first side. "Reciprocating" means that the "turnaround" is performed multiple times in the third direction Z.

[0047] For example, consider the example of "a serpentine flow channel 220 repeatedly zigzagging between the first side plate 110 and the second side plate 120": "Flow channel zigzagging" means that the flow channel 220 extends from the first side plate 110 to the second side plate 120, then turns back from the second side plate 120 to the first side plate 110. "The reciprocating motion of the flow channel 220" means that the "zigzag" process of the flow channel 220 is performed multiple times in the third direction Z. Figure 9 Taking the flow channel 220 shown as an example, the flow channel 220 undergoes three reversals in the third direction Z.

[0048] For example, taking "the heat exchange coil 310 folding back and forth between the first end plate 130 and the second end plate 140" as an example: "The folding back of the heat exchange coil 310" means that the heat exchange coil 310 extends from the first end plate 130 to the second end plate 140, then turns back from the second end plate 140 to the first end plate 130. "The folding back and forth of the heat exchange coil 310" means that the folding back of the heat exchange coil 310 is performed multiple times in the third direction Z. Figure 8 Taking the heat exchange coil 310 shown as an example, the heat exchange coil 310 has undergone 6 turns in the third direction Z.

[0049] like Figure 6As shown, the fluid flows from the first partition plate 210 to the second side plate 120. Blocked by the second side plate 120, the fluid changes direction through the gap 221 between the end of the first partition plate 210 and the second side plate 120, then flows from the second partition plate 210 to the first side plate 110. After passing through the gap 221 at the end of the second partition plate 210 again, it changes direction again and flows from the third partition plate 210 to the second side plate 120, until it passes through all the partition plates 210 and exits from the fluid outlet 103. This arrangement of the partition plates 210 divides the chamber 101 into a zigzag flow channel 220, thereby extending the fluid's flow time within the casing 100 and improving heat exchange efficiency.

[0050] like Figure 7 , Figure 10 and Figure 11 As shown, the partition plate 210 is provided with a turbulence section. The turbulence section is close to the notch 221 at the end of the partition plate 210. Under the action of the turbulence section, the fluid forms a complex flow state, such as vortex and turbulent mass, thereby increasing the degree of mixing inside the fluid, enhancing molecular diffusion and heat transfer, thereby improving the heat transfer rate and enhancing the heat exchange efficiency.

[0051] like Figure 11 As shown, the turbulence-inducing section includes a plurality of turbulence-inducing holes 230 penetrating the partition plate 210, which are uniformly arranged along the second direction Y. The uniformly distributed turbulence-inducing holes 230 can form a row of uniform disturbance sources near the ends of the partition plate 210. When fluid flows through the turbulence-inducing holes 230, vortices or turbulent masses are formed (see...). Figure 10 These disturbances superimpose and influence each other, resulting in relatively uniform disturbance across the entire cross-section of the flow channel 220. This ensures that the fluid across the entire cross-section of the flow channel 220 can fully participate in mixing and heat exchange, improving the uniformity and efficiency of heat transfer. The multiple turbulence holes 210 at the ends of each partition plate 210 have different flow areas, thereby increasing the turbulence effect and further improving heat transfer efficiency.

[0052] Furthermore, continue to refer to Figure 11 The sum of the areas of all the turbulence holes 230 on each partition plate 210 is S1, and the opening area of ​​the notch 221 at the end of the partition plate 210 is S2. S1 and S2 satisfy: 0.07≤S1:S2≤0.15. The ratio of S1 to S2 is between 0.07 and 0.15, which helps to balance the degree of fluid disturbance and the mainstream flow state.

[0053] Specifically, if the ratio of S1 to S2 is too small, the amount of fluid passing through the turbulence orifice 230 will be insufficient, resulting in a weak turbulence effect and hindering effective heat exchange. Conversely, if the ratio of S1 to S2 is too large, excessive fluid passing through the turbulence orifice 230 may cause excessive disturbance to the mainstream flow, affecting overall flow efficiency. The aforementioned range of S1 to S2 ensures a balance between the turbulence and the mainstream flow, allowing the fluid to receive sufficient turbulence to enhance heat transfer while maintaining orderly flow.

[0054] like Figure 3 and Figure 7 As shown, each partition plate 210 has multiple turbulence protrusions 211 at both ends along the second direction Y. When fluid flows along the serpentine flow channel 220, a small portion of the fluid located on both sides of the flow channel 220 overflows to both sides through the turbulence protrusions 211, which help generate turbulent flow masses. Some or all of the multiple turbulence protrusions 211 have through holes 2110, which further enhance the turbulence effect. An arc-shaped groove 2112 is formed between two adjacent turbulence protrusions 211. Figure 7 As shown, multiple heat exchange coils 310 are arranged in multiple grooves 2112 in a one-to-one correspondence. The heat exchange coils 310 and the grooves 2112 do not contact each other, and there is a gap between them, so that the fluid in the flow channel 220 can have sufficient contact with the heat exchange coils 310, which is beneficial to heat exchange.

[0055] like Figure 1 and Figure 6 As shown, multiple heat exchange coils 310 are spaced apart in the first direction X. This increases the contact area between the fluid and the heat exchange component 300, allowing for more thorough contact. Furthermore, when the fluid encounters the spaced-apart heat exchange coils 310, its flow direction and velocity are further altered, resulting in a more complex flow pattern. This complex flow pattern effectively disrupts the laminar boundary layer formed on the surface of the heat exchange coils 310, increasing the turbulence within the fluid, enhancing molecular diffusion for heat transfer, and improving the heat transfer coefficient, thereby increasing heat exchange efficiency.

[0056] Specifically, such as Figure 6 , Figure 7 and Figure 8 As shown, each heat exchange coil 310 includes multiple extension tube sections 311 and multiple U-shaped tube sections 312. The extension tube sections 311 extend along the second direction Y, and the multiple extension tube sections 311 are arranged in parallel along the third direction Z. The multiple U-shaped tube sections 312 are staggered at both ends of the extension tube sections 311 to connect the multiple extension tube sections 311.

[0057] In this embodiment, the two ends of the extension section 311 of the heat exchange coil 310 are respectively inserted into the first end plate 130 and the second end plate 140, while the U-shaped section 312 is located outside the shell 100. This arrangement ensures that only the extension section 311 exists within the flow channel 220, preventing the fluid from contacting the U-shaped section 312 and allowing the U-shaped section 312 to guide the fluid flow, thus reducing turbulence. Furthermore, the U-shaped section 312's location within the shell 100 also facilitates the inspection and maintenance of the heat exchange coil 310.

[0058] In other embodiments, the extension tube segment 311 may be located within the chamber 101, and the U-shaped tube segment 312 may extend through the first end plate 130 toward the second end plate 140, or extend through the second end plate 140 toward the first end plate 130. A connecting sleeve for the U-shaped tube segment 312 to pass through may be provided on the first end plate 130 and / or the second end plate 140 to increase the connection area between the extension tube segment 311 and the first end plate 130 and / or the second end plate 140.

[0059] like Figure 6 As shown, in order to further improve the heat exchange efficiency, two layers of extension pipe sections 311 can be provided between adjacent partition plates 210 in the third direction Z. Each layer can include multiple extension pipe sections 311 spaced apart along the first direction X. In the third direction Z, the upper layer extension pipe section 311 and the lower layer extension pipe section 311 are staggered. For example, the center lines of the two upper layer extension pipe sections 311 and the center line of one adjacent lower layer extension pipe section 311 are arranged in a triangle. Also, the center line of one upper layer extension pipe section 311 and the center lines of two adjacent lower layer extension pipe sections 311 are arranged in a triangle. This arrangement helps to increase the number of times the fluid impacts the heat exchange coil 310 and changes the flow direction during the flow process, effectively destroying the laminar boundary layer formed on the surface of the heat exchange coil 310, increasing the degree of turbulence inside the fluid, thereby improving the heat exchange efficiency of the heat exchanger.

[0060] In some other embodiments, 2-4 layers of extension pipe sections 311 may also be provided between adjacent partition plates 210 on the third direction Z.

[0061] like Figure 6 and Figure 7As shown, in the third direction Z, the distance between two adjacent partition plates 210 is D1; ​​the distance between the centerlines of the two layers of extension pipe sections 311 located between these two adjacent partition plates 210 is D2. D1 and D2 satisfy: 1 ​​≤ D1 : D2 ≤ 2.5. If the ratio of D1 to D2 is too small, the distance between the two adjacent layers of extension pipe sections 311 is too close, and the distance between the extension pipe sections 311 and the partition plates 210 is too small, affecting the uniformity of fluid heating. Conversely, if the ratio of D1 to D2 is too large, the fluid will not contact the extension pipe sections 311 frequently enough, which is not conducive to heat transfer. Therefore, the ratio of D1 to D2 should be between 1 and 2.5 to allow the fluid to flow smoothly between adjacent partition plates 210 and to make sufficient contact with the extension pipe sections 311, resulting in the best heat exchange effect. For example, the ratio of D1 to D2 can be 1, 1.5, 2, 2.5, or any value between the two adjacent values ​​mentioned above. For example, the value of D1 can be between 22mm and 33mm.

[0062] like Figure 6 and Figure 7 As shown, the centerline distance between two adjacent heat exchange coils 310 in the first direction X is L1; the dimension of the turbulence hole 230 in the first direction X is L2, and L1 and L2 satisfy: 1≤L1:L2≤2.5. This dimension setting allows the liquid flowing out of the turbulence hole 230 to contact the heat exchange coil 310, thereby generating a more complex flow state, which is beneficial to improving heat exchange efficiency. For example, the ratio of L1 to L2 can be 1, 1.5, 2, 2.5, or any value between the two adjacent values ​​mentioned above. Furthermore, the value of L1 can be between 25mm and 40mm.

[0063] like Figure 1 and Figure 2 As shown, the heat exchange assembly 300 also includes a manifold and connecting pipes, and multiple heat exchange coils 310 are all connected to the manifold through the connecting pipes. Specifically, the heat exchange assembly 300 may include an inlet manifold 320 and multiple L-shaped inlet connecting pipes 313. One end of each inlet connecting pipe 313 is connected to a corresponding extension pipe section 311, and the other end is connected to the inlet manifold 320, which is located outside the housing 100. The inlet manifold 320 can evenly distribute the heat exchange medium entering the heat exchange assembly 300 to each heat exchange coil 310.

[0064] The heat exchange assembly 300 may include an outlet manifold 330 and multiple L-shaped outlet connecting pipes 314. One end of each outlet connecting pipe 314 is connected to a corresponding extension pipe section 311, and the other end is connected to the outlet manifold 330, which is located outside the shell 100. The outlet manifold 330 collects the heat exchange medium, allowing it to be recycled. Both the inlet manifold 320 and the outlet manifold 330 are located outside the shell 100, making them easily accessible for inspection and maintenance. If a problem occurs in a heat exchange coil 310, such as blockage or leakage, it can also be troubleshooted through the manifold.

[0065] It should be noted that the flow direction of the heat exchange medium in the heat exchange coil 310 and the flow direction of the fluid in the flow channel 220 can also be opposite to the direction in the previous example.

[0066] In this embodiment, the heat exchanger 10 uses a partition component 200 to divide the chamber 101 of the shell 100 into a serpentine flow channel 220, and the heat exchange component 300 is spatially angled to the flow channel 220. This increases the contact time and contact area between the fluid and the heat exchange component 300, while also enhancing fluid turbulence, resulting in more complete heat exchange and significantly improving the heat exchange efficiency of the heat exchanger 10. Furthermore, the partition plate 210 in this embodiment is also provided with turbulence holes 230, which cooperate with the extension section 311 of the heat exchange tube to further enhance the turbulence effect, contributing to improved heat exchange efficiency of the heat exchanger 10.

[0067] Finally, it should be noted that the various embodiments / implementations provided in this application can be combined with each other without creating contradictions, and will not be described in detail here.

[0068] In the embodiments of this application, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term "multiple" refers to two or more unless otherwise expressly defined. The terms "install," "connect," "link," and "fix" should be interpreted broadly. For example, "connect" can be a fixed connection, a detachable connection, or an integral connection; "link" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.

[0069] In the description of the embodiments of the application, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the application and simplifying the description, and do not indicate or imply that the device or unit referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of the application.

[0070] The above are merely preferred embodiments of the application examples and are not intended to limit the application examples. For those skilled in the art, the application examples can have various modifications and variations. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the application examples should be included within the protection scope of the application examples.

Claims

1. A heat exchanger, characterized in that, include: The housing (100) has a chamber (101) and a fluid inlet (102) and a fluid outlet (103) respectively communicating with the chamber (101). A partition assembly (200) is disposed within the chamber (101) and divides the chamber (101) into a serpentine flow channel (220) for fluid flow, the flow channel (220) reciprocating in a first direction (X); A heat exchange assembly (300) is disposed in the housing (100). The heat exchange assembly (300) includes a plurality of heat exchange coils (310) spaced apart in the first direction (X). Each heat exchange coil (310) folds back and forth in the second direction (Y) and is staggered with the flow channel (220). The angle between the first direction (X) and the second direction (Y) is between 30° and 150°.

2. The heat exchanger according to claim 1, characterized in that, The angle between the first direction (X) and the second direction (Y) is 90°.

3. The heat exchanger according to claim 1, characterized in that, The housing (100) includes a first side plate (110) and a second side plate (120) disposed opposite each other in the first direction (X), and a first end plate (130) and a second end plate (140) respectively fixed to opposite sides of the first side plate (110) and the second side plate (120); the flow channel (220) reciprocates between the first side plate (110) and the second side plate (120), and the heat exchange coil (310) reciprocates between the first end plate (130) and the second end plate (140).

4. The heat exchanger according to claim 3, characterized in that, The partition assembly (200) includes a plurality of partition plates (210) spaced apart along a third direction (Z), the partition plates (210) extending along the first direction (X), and one end of the plurality of partition plates (210) being alternately fixed to the first side plate (110) and the second side plate (120), the other end of the partition plate (210) fixed to the first side plate (110) forming a notch (221) between it and the second side plate (120), and the other end of the partition plate (210) fixed to the second side plate (120) forming a notch (221) between it and the first side plate (110); the plurality of notches (221) communicating with the space between adjacent partition plates (210) thereby forming the flow channel (220), wherein the third direction (Z) is perpendicular to the first direction (X) and the second direction (Y).

5. The heat exchanger according to claim 4, characterized in that, Along the fluid path from the fluid inlet (102) to the fluid outlet (103), the flow area of ​​the gap (221) gradually decreases.

6. The heat exchanger according to claim 4, characterized in that, The separator (210) has a flow-dissipating part at the end near the notch (221).

7. The heat exchanger according to claim 6, characterized in that, The turbulence-disrupting part is a turbulence-disrupting hole (230) that penetrates the partition plate (210).

8. The heat exchanger according to claim 7, characterized in that, Multiple turbulence holes (230) are provided, and the flow areas of the multiple turbulence holes (230) are different.

9. The heat exchanger according to claim 7, characterized in that, The turbulence holes (230) are provided in multiple ways and are evenly arranged along the second direction (Y). The sum of the flow areas of all the turbulence holes (230) on each partition plate (210) is S1, and the flow area of ​​the notch (221) at the end of each partition plate (210) is S2. S1 and S2 satisfy: 0.07≤S1:S2≤0.

15.

10. The heat exchanger according to claim 7, characterized in that, The distance between the centerlines of two adjacent heat exchange coils (310) in the first direction (X) is L1, and the size of the turbulence hole (230) in the first direction (X) is L2; ​​L1 and L2 satisfy: 1≤L1:L2≤2.

5.

11. The heat exchanger according to any one of claims 1-10, characterized in that, Each heat exchange coil (310) includes a plurality of extension tube segments (311) and a plurality of U-shaped tube segments (312). The extension tube segments (311) extend along the second direction (Y). The plurality of extension tube segments (311) are spaced apart in the third direction (Z). The plurality of U-shaped tube segments (312) are respectively connected to the ends of adjacent extension tube segments (311). In the third direction (Z), at least two layers of extension tube segments (311) are arranged between adjacent partition plates (210) of the partition assembly (200), and the at least two layers of extension tube segments (311) are staggered in the third direction (Z), wherein the third direction (Z) is perpendicular to the first direction (X) and the second direction (Y).

12. The heat exchanger according to claim 11, characterized in that, The distance between two adjacent partition plates (210) is D1; ​​the distance between the center lines of the two extended pipe sections (311) located between the two adjacent partition plates (210) is D2; D1 and D2 satisfy: 1≤D1: D2≤2.

5.

13. The heat exchanger according to claim 11, characterized in that, The two ends of the extension tube section (311) of the heat exchange coil (310) are respectively inserted through the first end plate (130) and the second end plate (140) of the shell (100), and the U-shaped tube section (312) is located outside the shell (100).

14. The heat exchanger according to claim 11, characterized in that, The heat exchange assembly (300) further includes an outlet manifold (330) and a plurality of L-shaped outlet connecting pipes (314). One end of each of the plurality of outlet connecting pipes (314) is connected to a plurality of extension pipe sections (311) respectively, and the other end of each is connected to the outlet manifold (330). The outlet manifold (330) is located outside the housing (100); and / or The heat exchange assembly (300) also includes an inlet manifold (320) and a plurality of L-shaped inlet connecting pipes (313). One end of each of the plurality of inlet connecting pipes (313) is connected to a plurality of extension pipe sections (311) respectively, and the other end is connected to the inlet manifold (320). The inlet manifold (320) is located outside the housing (100).

15. The heat exchanger according to any one of claims 1-10, characterized in that, Each partition plate (210) of the partition assembly (200) is provided with at least one turbulence protrusion (211) at each end along the second direction (Y).

16. The heat exchanger according to claim 15, characterized in that, At least a portion of at least one of the at least one of the turbulence protrusions (211) is provided with a through hole (2110); and / or Each of the partition plates (210) has a plurality of uniformly arranged turbulence protrusions (211) at both ends along the second direction (Y), and an arc-shaped groove (2112) is formed between two adjacent protrusions (2111). The heat exchange coil (310) is disposed in the groove (2112) and maintains a gap with the groove (2112).

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