A heat exchanger

Abstract

The utility model provides a kind of heat exchanger, comprising: heat exchanger body, the heat exchanger body includes inner shell and outer shell, the outer shell is sleeved in the inner shell, the outer shell and the inner shell are connected and enclosed, form heat exchange cavity;Flow guide structure, the flow guide structure is arranged in the heat exchange cavity, the flow guide structure is connected with the outer shell;Wherein, along the circumference of the heat exchanger body, the flow guide structure includes opposite flow face and back flow face, the flow face and the outer shell between there is first inclination alpha, 45 ° ≤ alpha ≤ 80 °.Can improve heat exchange effect.

Description

Technical Field

[0001] This utility model relates to the field of photovoltaic technology, and in particular to a heat exchanger. Background Technology

[0002] With the development of new energy technologies, competition in the photovoltaic industry is becoming increasingly fierce. Reducing the cost of monocrystalline silicon production in crystal pulling furnaces and improving production efficiency are the current goals of the photovoltaic industry. Against this backdrop, the heat exchanger inside the crystal pulling furnace plays a crucial role. The core function of the heat exchanger is to precisely and efficiently control the cooling process of the crystal after solidification, optimizing the cooling rate as much as possible while ensuring crystal quality, thus creating conditions for safely and stably increasing the pulling speed.

[0003] Current heat exchangers mainly enhance heat exchange by designing multiple flow channels to increase the internal medium flow rate. However, the heat exchange efficiency of a heat exchanger does not increase linearly with the increase of the medium flow rate. After the medium flow rate reaches a certain level, the gain on heat exchange efficiency decreases sharply, making it impossible to further improve the heat exchange efficiency of the heat exchanger. Utility Model Content

[0004] In view of the above problems, the present invention provides a heat exchanger that overcomes or at least partially solves the above problems.

[0005] To address the aforementioned problems, this utility model discloses a heat exchanger, comprising: A heat exchanger body, the heat exchanger body including an inner shell and an outer shell, the outer shell being sleeved outside the inner shell, the outer shell and the inner shell being connected and enclosing to form a heat exchange cavity; A flow guiding structure is disposed within the heat exchange cavity and is connected to the outer shell; Along the circumference of the heat exchanger body, the flow guiding structure includes a frontal surface and a backal surface connected together, and the frontal surface and the outer shell have a first inclination angle α, 45°≤α≤80°.

[0006] The embodiments of this utility model have the following advantages: In this embodiment of the invention, a flow guiding structure is provided within the heat exchange cavity. Furthermore, along the circumference of the heat exchanger body, the flow guiding structure includes a frontal surface and a backal surface, allowing the cooling medium to flow from the frontal surface to the backal surface. By setting a suitable angle for the frontal surface, the vortex intensity within the flow channel is improved, and the flow resistance is reduced, thereby enhancing the heat exchange effect. Attached Figure Description

[0007] Figure 1 This is a schematic diagram of the structure of a heat exchanger according to this utility model; Figure 2 This is a cross-sectional schematic diagram of a heat exchanger according to this utility model; Figure 3 This is a cross-sectional schematic diagram of another heat exchanger according to this utility model; Figure 4 This is a schematic diagram of a flow guiding structure provided in the first sub-heat exchange cavity according to this utility model; Figure 5 This is a schematic diagram of the cooperation between the first flow guiding structure and the second flow guiding structure of this utility model; Figure 6 This is a top view of a flow guiding structure according to this utility model; Figure 7 This is a schematic diagram of a heat exchanger arrangement and flow guiding structure according to this utility model.

[0008] Explanation of reference numerals in the attached figures: 10. Heat exchanger body; 11. Heat exchange cavity; 111. First sub-heat exchange cavity; 112. Second sub-heat exchange cavity; 12. Conical section; 13. Straight section; 14. Inner shell; 15. Outer shell; 20. Flow guiding structure; 21. First flow guiding structure; 22. Second flow guiding structure; 23. Frontal surface; 24. Backal surface; 30. Water inlet pipe; 40. Water outlet pipe. Detailed Implementation

[0009] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, the utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0010] The terms "first" and "second" in the specification and claims of this application may explicitly or implicitly include one or more of the features. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0011] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", 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 are not intended to 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.

[0012] 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.

[0013] This utility model embodiment provides a heat exchanger that can be used in a single crystal furnace. Specifically, during crystal growth, the heat exchanger is fitted around the single crystal silicon rod. The heat exchanger absorbs the heat radiated by the single crystal silicon rod during crystallization and transfers the absorbed heat to the outside of the furnace, thereby increasing the longitudinal temperature gradient of the single crystal silicon rod and improving the crystal growth rate. The heat exchanger can be any of a water-cooled heat exchanger or a heat exchanger using other cooling media. This embodiment only uses a water-cooled heat exchanger as an example for illustration; the same principle applies to heat exchangers using other cooling media.

[0014] Specifically, this invention designs a new heat exchanger that can achieve higher heat exchange efficiency and stronger heat exchange capacity, and can accurately and efficiently control the cooling process of the crystal after solidification and forming, ensuring the crystal pulling quality of the single crystal silicon rod and reducing the production cost of the single crystal silicon rod.

[0015] like Figures 1 to 5 As shown, the heat exchanger includes a heat exchanger body 10, which includes an inner shell 14 and an outer shell 15. The outer shell 15 is fitted over the inner shell 14, and the outer shell 15 and the inner shell 14 are connected and enclosed to form a heat exchange cavity 11. The heat exchanger also includes a flow guiding structure 20, which is disposed within the heat exchange cavity 11 and connected to the outer shell 15. In this embodiment, by providing the flow guiding structure 20, the heat exchange capacity of the heat exchanger can be improved.

[0016] In this invention, the heat exchanger may include a heat exchanger body 10, an inlet pipe 30, and an outlet pipe 40. A heat exchange chamber 11 may be provided inside the heat exchanger body 10. The inlet pipe 30 and the outlet pipe 40 may be connected to the top of the heat exchanger body 10; in actual use, the bottom of the heat exchanger body 10 is close to the silicon liquid surface. The inlet pipe 30 may communicate with the inlet of the heat exchange chamber 11, allowing the cooling medium to be introduced into the heat exchange chamber 11. The outlet pipe 40 may communicate with the outlet of the heat exchange chamber 11, allowing the cooling medium to be discharged from the heat exchange chamber 11.

[0017] Specifically, the heat exchange cavity 11 may include multiple sub-heat exchange cavities distributed along the axial direction of the heat exchanger body 10. Adjacent sub-heat exchange cavities are connected, so that the cooling medium can flow in each sub-heat exchange cavity to carry away heat and achieve heat exchange.

[0018] Specifically, the heat exchanger body 10 includes an inner shell 14 and an outer shell 15. The outer shell 15 is fitted onto the inner shell 14, and the outer shell 15 and the inner shell 14 are connected and enclosed to form a heat exchange cavity 11. The inlet pipe 30 and the outlet pipe 40 can be connected to the top of the inner shell 14. In this embodiment of the invention, the inner shell 14 and the outer shell 15 are the inner and outer layers of the heat exchanger body 10. During the crystal pulling process, the inner shell 14 is closer to the single-crystal silicon rod, and the inner shell 14 can conduct the latent heat of crystallization generated during the single-crystal silicon rod pulling process to the cooling medium.

[0019] Specifically, both the inner shell 14 and the outer shell 15 can be annular structures. The inner periphery of the inner shell 14 forms a crystal pulling channel for inserting a single crystal silicon rod. A heat exchange cavity 11 is formed between the outer periphery of the inner shell 14 and the inner periphery of the outer shell 15.

[0020] Furthermore, the heat exchanger also includes a flow guiding structure 20, which can be disposed inside the heat exchange cavity 11. The flow guiding structure 20 is connected to the outer shell 15 and can be spaced apart from the inner shell 14. In this way, when the cooling medium flows through the flow guiding structure 20, the flow guiding structure 20 can squeeze the cooling medium toward the inner shell 14 to increase the flow velocity of the cooling medium on the side near the inner shell 14, thereby increasing the scouring effect of the cooling medium on the inner shell 14, so as to remove the heat absorbed by the inner shell 14 and improve the heat exchange efficiency.

[0021] In some embodiments, along the circumference of the heat exchanger body 10, the flow guiding structure 20 includes an opposing frontal surface 23 and a backal surface 24. In this embodiment, the frontal surface 23 and the backal surface 24 are merely distinctions between two opposing surfaces of the flow guiding structure 20. The frontal surface 23 and the outer shell 15 have a first inclination angle α, 45°≤α≤80°. In this embodiment, the first inclination angle α is the tilt angle of the frontal surface 23 relative to the outer shell 15. Specifically, the first inclination angle α refers to the angle between the line connecting the end of the frontal surface 23 away from the outer shell 15 and the end closer to the outer shell 15 along the direction from the outer shell 15 to the inner shell 14, and the tangent line passing through the outer shell 15 and tangent to the junction of the frontal surface 23 and the outer shell 15. Figure 5 As shown, the outer shell 15 has a first tangent at the position where it intersects with the frontal surface 23, and the first tilt angle α is the angle between the first tangent and the frontal surface 23.

[0022] In this embodiment, by adjusting the first tilt angle α, the turbulence of the water flow when passing the frontal surface 23 can be improved. Increasing the turbulence helps to break the laminar flow when the flow guiding structure 20 is not set, thereby improving the heat exchange effect of the fluid.

[0023] In this embodiment, if the first tilt angle α is too small, the slope of the frontal surface 23 will be too small, resulting in an insignificant improvement in the turbulence of the cooling medium flow. If the first tilt angle α is too large, the slope of the frontal surface 23 will be too large, increasing the resistance to the cooling medium flow. Therefore, in this embodiment, the angle is controlled to be 45°≤α≤80°, making the first tilt angle α appropriately designed. This ensures that the turbulence of the cooling medium flow is improved through the frontal surface 23, thereby increasing the heat exchange efficiency of the heat exchanger, and also results in relatively low flow resistance.

[0024] For example, the first tilt angle α can be 45°, 50°, 55°, 56°, 60°, 66°, 70°, 75° or 80°, etc.

[0025] In some embodiments, the frontal surface 23 and the backal surface 24 can be directly and smoothly connected to improve the transition effect of the cooling medium from the frontal surface 23 to the backal surface 24. Moreover, the frontal surface 23 and the backal surface 24 are set at an angle, which can improve the vortex intensity of the cooling medium after it flows through the frontal surface 23 and reduce the flow loss caused by the vortex.

[0026] In some embodiments, the front surface 23 and the back surface 24 can be indirectly connected by a transition surface, which can be disposed opposite to the inner shell 14 and can extend circumferentially along the heat exchanger body 10.

[0027] In some embodiments, along the circumference of the heat exchanger body 10, the flow guiding structure 20 includes a frontal surface 23 and a backal surface 24 facing away from each other. The frontal surface 23 and the outer shell 15 have a first inclination angle α, and the backal surface 24 and the outer shell 15 have a second inclination angle β, where 10° ≤ β ≤ 40°. In this embodiment, the second inclination angle β is the inclination angle of the backal surface 24 relative to the outer shell 15. Specifically, the second inclination angle β refers to the angle between the line connecting the end of the backal surface 24 away from the outer shell 15 and the end closest to the outer shell 15 along the direction from the outer shell 15 to the inner shell 14, and the tangent line passing through the outer shell 15 and tangent to the point where the backal surface 24 and the outer shell 15 meet. Figure 5 As shown, the outer shell 15 has a second tangent at the position where it intersects with the backflow surface 24, and the second inclination angle β is the angle between the second tangent and the backflow surface 24.

[0028] In this embodiment, by adjusting the second tilt angle β, the intensity of the vortex after the water flows through the guide structure 20 can be adjusted, thereby reducing resistance.

[0029] In this embodiment, if the second tilt angle β is too small, the slope of the backflow surface 24 will be too small, resulting in a large flow resistance. If the second tilt angle β is too large, the slope of the backflow surface 24 will be too large, and the effect of improving the vortex intensity of the cooling medium through the backflow surface 24 will not be significant. Therefore, in this embodiment of the invention, the angle is controlled to be 10°≤β≤40°, so that the second tilt angle β is designed to be more moderate, which can ensure that the cooling substrate can improve the vortex intensity and reduce the flow resistance after flowing from the frontflow surface 23 to the backflow surface 24.

[0030] For example, the second tilt angle β can be 10°, 15°, 20°, 25°, 28°, 30°, 35°, 37° or 40°, etc.

[0031] In some embodiments, along the circumference of the heat exchanger body 10, the flow guiding structure 20 includes a frontal surface 23 and a backal surface 24 facing away from each other. The frontal surface 23 and the outer shell 15 have a first tilt angle α, and the backal surface 24 and the outer shell 15 have a second tilt angle β. The first tilt angle α is greater than the second tilt angle β.

[0032] In this embodiment of the invention, a flow guiding structure 20 is provided within the heat exchange cavity 11. Furthermore, along the circumference of the heat exchanger body 10, the flow guiding structure 20 includes a frontal flow surface 23 and a backal flow surface 24 facing opposite directions. The cooling medium can flow from the frontal flow surface 23 to the backal flow surface 24. Due to the large first inclination angle α between the frontal flow surface 23 and the outer shell 15, the liquid level of the cooling medium changes drastically after flowing through the frontal flow surface 23, increasing turbulence and thus improving the heat exchange effect. Because the small second inclination angle β between the backal flow surface 24 and the outer shell 15 results in a gentler slope on the backal flow surface 24, the eddy current intensity of the cooling medium after flowing through the flow guiding structure 20 is reduced, thereby reducing the flow resistance of the cooling matrix, alleviating the pressure on the water supply system of the heat exchanger, and helping to reduce the power of the water pump and save costs.

[0033] In this embodiment of the invention, the first tilt angle α and the second tilt angle β are different, which makes the tilt angles of the frontal surface 23 and the backal surface 24 relative to the outer shell 15 different. The two have different shapes and slopes. The frontal surface 23 and the backal surface 24 can play different roles. For example, the frontal surface 23 can improve the turbulence of the cooling medium and improve the heat exchange efficiency, while the backal surface 24 can improve the flow resistance of the cooling medium.

[0034] Optionally, the frontal surface 23 can be a flat surface or a concave surface that is recessed towards the backal surface 24. This can ensure the reliability of improving the turbulence of the cooling medium flow through the frontal surface 23, and can also increase the design versatility of the frontal surface 23.

[0035] Optionally, the backflow surface 24 can be a flat surface or a concave surface that is recessed towards the frontflow surface 23. This can ensure the reliability of improving the vortex intensity of the cooling medium through the backflow surface 24, and can also increase the design versatility of the backflow surface 24.

[0036] In some embodiments, along the direction perpendicular to the outer casing 15, the maximum height of the flow guiding structure 20 protruding from the outer casing 15 is H2; the backflow surface 24 is a concave surface facing the frontflow surface 23, and the maximum concavity depth of the backflow surface 24 is D. In this embodiment, the maximum concavity depth D of the backflow surface 24 specifically refers to the straight-line distance between the line connecting the end of the backflow surface 24 away from the outer casing 15 and the end closer to the outer casing 15, and the deepest point of the concavity.

[0037] In this embodiment, if the value of D is too small, the backflow surface 24 will be close to a plane, resulting in a slow contraction of the flow channel and low heat exchange efficiency. If the value of D is too large, the backflow surface 24 will be too concave, resulting in a larger flow channel, a significantly enhanced tail flow, intensified eddies, increased flow resistance, and higher pressure in the water supply system. Therefore, in this embodiment, the value of D is controlled to be 0.1H2≤D≤0.4H2, so that the maximum concavity depth of the backflow surface 24 is designed appropriately, which facilitates the formation of a gentler slope on the backflow surface 24, making it easier to reduce the intensity of eddies through the backflow surface 24, thereby reducing flow resistance.

[0038] For example, the maximum indentation depth D of the backflow surface 24 can be 0.1H2, 0.11H2, 0.14H2, 0.2H2, 0.25H2, 0.3H2, 0.36H2, 0.39H2 or 0.4H2.

[0039] In some embodiments, the extension length of the flow guiding structure 20 along the circumference of the heat exchanger body 10 is B; the maximum height of the flow guiding structure 20 protruding from the outer shell 15 along the direction perpendicular to the outer shell 15 is H2. If the value of B is too small, the extension lengths of the front flow surface 23 and the back flow surface 24 will be too short, which is not conducive to influencing the flow velocity of the cooling medium through the flow guiding structure 20. If the value of B is too large, the extension lengths of the front flow surface 23 and the back flow surface 24 will be too long, resulting in excessive resistance to the cooling medium and a low flow velocity of the cooling medium through the flow guiding structure 20. Therefore, in this embodiment of the invention, controlling 12mm≤B≤20mm and H2=3.3B makes the size design of the flow guiding structure 20 more suitable, which can improve the flow velocity of the cooling medium and enhance the heat exchange efficiency of the heat exchanger.

[0040] Specifically, the extended length and width B of the flow guide structure 20 can be determined by the maximum height H2 of the flow guide structure 20 protruding from the outer shell 15, the first tilt angle α, and the second tilt angle β. An optimal value can be selected based on H2, the first tilt angle α, and the second tilt angle β. For example, the extended length and width B of the flow guide structure 20 can be designed to be 12mm, 13mm, 14mm, 15mm, 16mm, 17mm, 18mm, 19mm, or 20mm.

[0041] In some embodiments, the shortest distance between the outer shell 15 and the inner shell 14 along the direction perpendicular to the outer shell 15 is H1, and the maximum height of the flow guiding structure 20 protruding from the outer shell 15 is H2.

[0042] Specifically, such as Figure 5 As shown, along the direction from the outer shell 15 to the inner shell 14, the shortest distance between the outer shell 15 and the inner shell 14 is H1, making the width of the heat exchange cavity 11 H1. Without the flow guide structure 20, the width of the flow channel through which the cooling medium can flow is H1. By providing the flow guide structure 20 on the outer shell 15, the width of the flow channel through which the cooling medium can flow is reduced. The width of the flow channel through which the cooling medium can flow is the width of the gap between the flow guide structure 20 and the inner shell 14, meaning the cooling medium flows through the gap between the flow guide structure 20 and the inner shell 14. For example, as the cooling medium flows through the front flow surface 23, the flow channel width gradually decreases, causing a drastic change in the liquid level of the cooling medium, increasing turbulence, and improving the heat exchange effect; as the cooling medium flows through the back flow surface 24, the flow channel width gradually increases.

[0043] In this embodiment, if the difference between H1 and H2 is too small, the flow guide structure is too close to the inner shell 14, which is not conducive to the flow of the cooling medium. If the difference between H1 and H2 is too large, the flow guide structure is too far from the inner shell 14, making it difficult for the flow guide structure 20 to squeeze the cooling matrix into the inner shell 14 when the cooling medium flows through the flow guide structure. Therefore, in this embodiment of the present invention, the distance between the flow guide structure and the inner shell 14 is controlled to be more appropriate. This can increase the flow velocity of the cooling medium when it flows through the flow guide structure, increase the scouring effect of the cooling medium in the inner shell 14, so as to remove more heat and improve the heat exchange efficiency.

[0044] For example, the difference between H1 and H2 can be 2mm, 2.1mm, 2.5mm, 3mm, 3.3mm, 4mm, 4.5mm, 5mm or 6mm.

[0045] In some alternative embodiments, the number of flow guiding structures 20 includes a plurality of flow guiding structures 20, which are arranged at circumferential intervals along the heat exchanger body 10.

[0046] In this embodiment of the present invention, multiple flow guiding structures 20 are arranged at intervals along the circumference of the heat exchanger body 10, so that the cooling medium can flow through multiple flow guiding structures 20 during the flow process, which can further improve the turbulence of the cooling medium and further improve the heat exchange efficiency of the heat exchanger.

[0047] Optionally, the plurality of flow guiding structures 20 include a plurality of first flow guiding structures 21 and a plurality of second flow guiding structures 22, wherein the first flow guiding structures 21 and the second flow guiding structures 22 are arranged along the axial direction of the heat exchanger body 10; the plurality of first flow guiding structures 21 are arranged at intervals along the circumferential direction of the heat exchanger body 10, and the plurality of second flow guiding structures 22 are arranged at intervals along the circumferential direction of the heat exchanger body 10.

[0048] In this embodiment of the present invention, the first flow guiding structure 21 and the second flow guiding structure 22 are arranged along the axial direction of the heat exchanger body 10. The first flow guiding structure 21 and the second flow guiding structure 22 can respectively shield the heat exchange cavity 11 along the axial direction of the heat exchanger body 10, so that the cooling medium can flow through the first flow guiding structure 21 and the second flow guiding structure 22 respectively, which can further improve the turbulence during the flow of the cooling medium.

[0049] Specifically, the first flow guiding structure 21 and the second flow guiding structure 22 are arranged in the same direction, that is, the front flow surface 23 and the back flow surface 24 of the first flow guiding structure 21 and the second flow guiding structure 22 are arranged sequentially along the flow direction of the cooling medium, so that the cooling medium flows through the front flow surface 23 first and then through the back flow surface 24 during the flow process.

[0050] Optionally, the first flow guiding structure 21 and the second flow guiding structure 22 are staggered along the axial direction of the heat exchanger body 10.

[0051] In this embodiment, the first flow guiding structure 21 and the second flow guiding structure 22 are staggered, so that the flow guiding structure 20 can come into contact with more cooling medium to improve the turbulence during the flow of the cooling medium.

[0052] Optionally, along the axial direction of the heat exchanger body 10, the heat exchanger body 10 includes a conical portion 12 and a straight cylindrical portion 13, and the heat exchange cavity 11 includes at least one first sub-heat exchange cavity 111 and a plurality of second sub-heat exchange cavities 112 that are sequentially connected. The first sub-heat exchange cavity 111 is disposed in the straight cylindrical portion 13, and the second sub-heat exchange cavities 112 are disposed in the conical portion 12.

[0053] In some embodiments, a flow guiding structure 20 may be provided in the first sub-heat exchange cavity 111. In other embodiments, a flow guiding structure 20 may be provided in the second sub-heat exchange cavity 112. In still other embodiments, flow guiding structures 20 may be provided in both the first sub-heat exchange cavity 111 and the second sub-heat exchange cavity 112.

[0054] Optionally, along the axial direction of the heat exchanger body 10, the height of the first sub-heat exchange chamber 111 is L1, the height of the first flow guiding structure 21 is L2, and the height of the second flow guiding structure 22 is L3.

[0055] In this embodiment, by adjusting the height of the first guide structure 21 and the second guide structure 22 along the axial direction of the heat exchanger body 10, the width of the flow channel of the guide structure 20 for the cooling medium can be adjusted, thereby improving the flow cross-sectional area of ​​the cooling medium. If the ratio of L2 and L3 to L1 is too small, the obstruction area of ​​the guide structure 20 on the flow channel will be small, resulting in lower turbulence and correspondingly lower heat exchange efficiency. If the ratio of L2 and L3 to L1 is too large, the obstruction area of ​​the guide structure 20 on the flow channel will be large, which will easily increase the flow resistance during the flow of the cooling medium, putting pressure on the water supply system of the heat exchanger and easily increasing the heat exchange cost. Therefore, in this embodiment of the invention, controlling 0.5L1≤L2≤0.8L1 and 0.5L1≤L3≤0.8L1 makes the ratio of L2 and L3 to L1 more appropriate, which can both meet the turbulence requirements during the flow of the cooling medium and improve the heat exchange efficiency, while reducing the flow resistance during the flow of the cooling medium.

[0056] For example, the ratio of L2 to L1, i.e., L2 / L1, can take values ​​of 0.5, 0.55, 0.58, 0.6, 0.66, 0.7, 0.72, 0.75, or 0.8.

[0057] Specifically, the dimensions of the first flow guiding structure 21 and the second flow guiding structure 22 may be the same or different, and this embodiment of the present invention does not impose specific limitations on this.

[0058] In some embodiments, along the axial direction of the heat exchanger body 10, the first flow guiding structure 21 is spaced apart from the top and bottom of the first sub-heat exchange chamber 111, and the second flow guiding structure 22 is spaced apart from the top and bottom of the first sub-heat exchange chamber 111, respectively.

[0059] In other embodiments, a flow guiding structure 20 is provided in the first sub-heat exchange cavity 111; along the axial direction of the heat exchanger body 10, the first flow guiding structure 21 abuts against the top of the first sub-heat exchange cavity 111, and the second flow guiding structure 22 abuts against the bottom of the first sub-heat exchange cavity 111.

[0060] In the embodiment, the first flow guiding structure 21 and the second flow guiding structure 22 can be along the axial direction of the heat exchanger body 10, and can fill the first sub-heat exchange cavity 111, which can improve the sufficiency of contact between the cooling medium and the flow guiding structure 20, so as to further improve the turbulence of the heat exchange medium.

[0061] Specifically, such as Figure 6 As shown, dashed line S1 represents the upper boundary where the top of the first sub-heat exchange cavity 111 is located, and dashed line S2 represents the lower boundary where the bottom of the first sub-heat exchange cavity 111 is located. The straight-line distance between dashed lines S1 and S2 represents the height L1 of the first sub-heat exchange cavity 111 extending along the axial direction of the heat exchanger body 10. The first flow guiding structure 21 extends from the top to the bottom of the first sub-heat exchange cavity 111, and the second flow guiding structure 22 extends from the bottom to the top of the first sub-heat exchange cavity 111. The first flow guiding structure 21 and the second flow guiding structure 22 are staggered along the axial direction of the heat exchanger body 10.

[0062] In this embodiment of the invention, the straight cylindrical portion 13 is located at the bottom end of the heat exchanger body 10. During the crystal pulling process, the straight cylindrical portion 13 is closer to the molten silicon surface than the conical portion 12, and the straight cylindrical portion 13 has a stronger demand for heat exchange. The first sub-heat exchange chamber 111 is located in the straight cylindrical portion 13, closer to the molten silicon surface. By arranging a flow guiding structure 20 within the first sub-heat exchange chamber 111, the heat exchange efficiency of the cooling medium within the first sub-heat exchange chamber 111 can be enhanced.

[0063] In some alternative embodiments, the first flow guiding structure 21 and the second flow guiding structure 22 are alternately arranged along the circumference of the heat exchanger body 10, so that the first flow guiding structure 21 and the second flow guiding structure 22 are distributed more evenly, so that the cooling medium can flow through the first flow guiding structure 21 and the second flow guiding structure 22 in sequence, which can better improve the turbulence during the flow of the cooling medium.

[0064] Optionally, at least two second flow guiding structures 22 may be provided between every two adjacent first flow guiding structures 21 along the circumference of the heat exchanger. Alternatively, at least two first flow guiding structures 21 may be provided between every two adjacent second flow guiding structures 22 along the circumference of the heat exchanger.

[0065] In some alternative embodiments, such as Figure 7 In a cross-section perpendicular to the axial direction of the heat exchanger, along the circumference of the heat exchanger body 10, there is an arc segment between the first flow guiding structure 21 and the second flow guiding structure 22, with a central angle θ corresponding to the arc segment, where 5°≤θ≤30°. In this embodiment, the arc segment specifically refers to the arc located between the end of the flow-facing surface 23 of the first flow guiding structure 21 away from the outer shell 15 and the end of the flow-facing surface 23 of the second flow guiding structure 22 away from the outer shell 15 in a cross-section perpendicular to the axial direction of the heat exchanger, along the circumference of the heat exchanger body 10.

[0066] In this embodiment, if the central angle θ is too small, the interval between the first guide structure 21 and the second guide structure 22 along the circumference of the heat exchanger body 10 will be too small, resulting in an overly dense arrangement of the guide structures 20 and an increased flow resistance of the cooling medium. Conversely, if the central angle θ is too large, the interval between the first guide structure 21 and the second guide structure 22 along the circumference of the heat exchanger body 10 will be too large, resulting in an overly sparse arrangement of the guide structures 20 and a smaller effect on increasing the turbulence of the cooling medium. Therefore, in some embodiments of this invention, controlling 5°≤θ≤30° ensures a suitable value for the central angle θ and a suitable interval between the first guide structure 21 and the second guide structure 22 along the circumference of the heat exchanger body 10, effectively increasing the turbulence of the cooling medium.

[0067] For example, along the circumference of the heat exchanger body 10, the central angle corresponding to the arc segment between the frontal surface 23 of the first flow guiding structure 21 and the frontal surface 23 of the second flow guiding structure 22 can be 5°, 8°, 10°, 15°, 20°, 25°, 28° or 30°.

[0068] For example, heat exchangers A1 and A2 are provided respectively; wherein, a first flow guiding structure 21 and a second flow guiding structure 22 are arranged in the first sub-heat exchange cavity 111 of heat exchanger A2. The cooling medium introduced into heat exchangers A1 and A2 is the same. The only difference between heat exchangers A1 and A2 is that the first and second flow guiding structures are not arranged in the first sub-heat exchange cavity. In heat exchanger A2, along the axial direction of the heat exchanger body 10, the first flow guiding structure 21 abuts against the top of the first sub-heat exchange cavity 111, and the second flow guiding structure 22 abuts against the bottom of the first sub-heat exchange cavity 111, and the first and second flow guiding structures 21 and 22 are staggered. Through simulation experiments, it was found that the temperature of the cooling medium before entering heat exchanger A1 is 27°C, and the temperature after flowing out of heat exchanger A1 is 32.68°C; the temperature of the cooling medium before entering heat exchanger A2 is 27°C, and the temperature after flowing out of heat exchanger A2 is 31.13°C. Comparative analysis shows that heat exchanger A2 has a stronger heat exchange capacity and higher heat exchange efficiency than heat exchanger A1. Compared with heat exchanger A1, heat exchanger A2's heat exchange power is increased by 37.6%.

[0069] The heat exchanger described in this embodiment of the invention has at least the following advantages: In this embodiment of the invention, a flow guiding structure is provided within the heat exchange cavity. Furthermore, along the circumference of the heat exchanger body, the flow guiding structure includes a frontal surface and a backal surface, allowing the cooling medium to flow from the frontal surface to the backal surface. By setting a suitable angle for the frontal surface, the vortex intensity within the flow channel is improved, and the flow resistance is reduced, thereby enhancing the heat exchange effect.

[0070] Although preferred embodiments of the present invention have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments as well as all changes and modifications falling within the scope of the present invention.

[0071] Finally, it should be noted that in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or terminal device that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or terminal device. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or terminal device that includes said element.

[0072] The present invention provides a detailed description of a heat exchanger. Specific examples have been used to illustrate the principle and implementation of the present invention. The description of the above embodiments is only for the purpose of helping to understand the method and core idea of ​​the present invention. At the same time, for those skilled in the art, there will be changes in the specific implementation and application scope based on the idea of ​​the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A heat exchanger, characterized in that, include: The heat exchanger body (10) includes an inner shell (14) and an outer shell (15). The outer shell (15) is fitted over the inner shell (14). The outer shell (15) and the inner shell (14) are connected and enclosed to form a heat exchange cavity (11). A flow guiding structure (20) is disposed inside the heat exchange cavity (11) and is connected to the outer shell (15); Along the circumference of the heat exchanger body (10), the flow guiding structure (20) includes a front flow surface (23) and a back flow surface (24) facing away from each other. The front flow surface (23) and the outer shell (15) have a first inclination angle α, 45°≤α≤80°.

2. The heat exchanger according to claim 1, characterized in that, There is a second tilt angle β between the backflow surface (24) and the outer shell (15), and the first tilt angle α is greater than the second tilt angle β; And / or, 10°≤β≤40°.

3. The heat exchanger according to claim 2, characterized in that, The frontal surface (23) is a plane or a concave surface that is recessed toward the backal surface (24); The backflow surface (24) is a plane or a concave surface that is recessed toward the frontflow surface (23).

4. The heat exchanger according to claim 2, characterized in that, Along the direction perpendicular to the outer shell (15), the maximum height of the flow guiding structure (20) protruding from the outer shell (15) is H2; The backflow surface (24) is a concave surface that is recessed towards the frontflow surface (23), and the maximum recess depth of the backflow surface (24) is D; 0.1H2≤D≤0.4H2.

5. The heat exchanger according to claim 1 or 4, characterized in that, Along the circumference of the heat exchanger body (10), the extension length of the flow guiding structure (20) is B; along the direction perpendicular to the outer shell (15), the maximum height of the flow guiding structure (20) protruding from the outer shell (15) is H2; Where 12mm≤B≤20mm, H2=3.3B.

6. The heat exchanger according to claim 1, characterized in that, Along the direction perpendicular to the outer shell (15), the shortest distance between the outer shell (15) and the inner shell (14) is H1, and the maximum height of the flow guiding structure (20) protruding from the outer shell (15) is H2; 2mm≤H1-H2≤6mm.

7. The heat exchanger according to claim 1, characterized in that, The number of the flow guiding structures (20) includes a plurality of them, and the plurality of flow guiding structures (20) are arranged at circumferential intervals along the heat exchanger body (10).

8. The heat exchanger according to claim 7, characterized in that, The plurality of flow guiding structures (20) include a plurality of first flow guiding structures (21) and a plurality of second flow guiding structures (22); A plurality of first flow guiding structures (21) are arranged at intervals along the circumference of the heat exchanger body (10), and a plurality of second flow guiding structures (22) are arranged at intervals along the circumference of the heat exchanger body (10); Along the axial direction of the heat exchanger body (10), the first flow guiding structure (21) and the second flow guiding structure (22) are staggered.

9. The heat exchanger according to claim 8, characterized in that, Along the axial direction of the heat exchanger body (10), the heat exchanger body (10) includes a conical portion (12) and a straight portion (13). The heat exchange cavity (11) includes at least one first sub-heat exchange cavity (111) and a plurality of second sub-heat exchange cavities (112) that are sequentially connected. The first sub-heat exchange cavity (111) is disposed in the straight cylinder portion (13), and the second sub-heat exchange cavity (112) is disposed in the conical portion (12). Along the axial direction of the heat exchanger body (10), the height of the first sub-heat exchange chamber (111) is L1, the height of the first flow guiding structure (21) is L2, and the height of the second flow guiding structure (22) is L3; wherein, 0.5L1≤L2≤0.8L1, 0.5L1≤L3≤0.8L1.

10. The heat exchanger according to claim 8, characterized in that, Along the axial direction of the heat exchanger body (10), the heat exchanger body (10) includes a conical portion (12) and a straight portion (13). The heat exchange cavity (11) includes at least one first sub-heat exchange cavity (111) and a plurality of second sub-heat exchange cavities (112) that are sequentially connected. The first sub-heat exchange cavity (111) is disposed in the straight cylinder portion (13), and the second sub-heat exchange cavity (112) is disposed in the conical portion (12). Along the axial direction of the heat exchanger body (10), the first flow guiding structure (21) abuts against the top of the first sub-heat exchange chamber (111), and the second flow guiding structure (22) abuts against the bottom of the first sub-heat exchange chamber (111).

11. The heat exchanger according to claim 8, characterized in that, Along the circumference of the heat exchanger body (10), the first flow guiding structure (21) and the second flow guiding structure (22) are alternately arranged.

12. The heat exchanger according to claim 11, characterized in that, Along the circumference of the heat exchanger body (10), the first flow guiding structure (21) and the second flow guiding structure (22) are spaced by an arc segment, and the central angle corresponding to the arc segment is θ, 5°≤θ≤30°.

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