Cooling device and pulping tank

Abstract

The utility model provides a cooling device and slurrying tank wherein the cooling device comprises: a tank body, the tank body is internally provided with a cylindrical accommodating cavity and a cooling channel suitable for accommodating a refrigerant, the cooling channel is arranged along the circumferential direction of the accommodating cavity, the cooling channel extends along the axial direction of the accommodating cavity, the tank body is provided with an inlet and an outlet, the inlet and the outlet are spaced in the axial direction of the containing cavity and communicate with the cooling channel, and the inlet is lower than the outlet. According to the cooling device disclosed by the utility model, the cooling channel is arranged in the circumferential direction of the accommodating cavity of the tank body, so that the inlet is lower than the outlet, and the slurry is cooled by adopting the refrigerant, so that not only can the refrigerant be utilized to obtain lower cooling temperature and increase heat transfer temperature difference, but also the refrigerant can be uniformly distributed around the accommodating cavity at the bottom of the cooling channel; and a gas-liquid mixture formed after heat absorption can uniformly move upwards, so that the slurry is cooled more uniformly.

Description

Technical Field

[0001] The utility model relates to the technical field of battery manufacturing, and more specifically, to a cooling device and a pulping tank. Background Art

[0002] The pulping tank is an important equipment in the lithium battery manufacturing process. It is mainly used to mix and pulp active materials, conductive agents, dispersants, binders and other raw materials. A large amount of heat will be generated during the pulping process, and a cooling device is required to cool it. In the prior art, a jacket is usually set on the outer layer of the pulping tank, and cooling water is passed through the jacket to dissipate heat. However, the minimum temperature of the cooling water is not lower than 0°C, the amount of heat that can be taken away is limited, and the uniformity of the cooling water flow in the jacket is difficult to control, which will lead to large differences in cooling effects at different positions, greatly restricting the pulping efficiency. Utility Model Content

[0003] The utility model provides a new technical solution for a cooling device, which can at least solve the problems of insufficient cooling capacity and uneven cooling of cooling devices in the prior art.

[0004] The utility model also provides a pulping tank, comprising the above cooling device.

[0005] According to a first aspect of the utility model, a cooling device is provided, comprising: a tank body, wherein a cylindrical accommodating cavity and a cooling channel suitable for accommodating a refrigerant are provided in the tank body, wherein the cooling channel is arranged along the circumference of the accommodating cavity and is separated from the accommodating cavity, wherein the cooling channel extends along the axial direction of the accommodating cavity, wherein an inlet and an outlet are provided on the tank body, wherein the inlet and the outlet are spaced apart in the axial direction of the accommodating cavity and are respectively connected to the cooling channel, wherein the inlet is lower than the outlet.

[0006] Optionally, the cooling channel is annular and arranged around the outer circumference of the accommodating cavity.

[0007] Optionally, the axis of the accommodating cavity extends in a vertical direction.

[0008] Optionally, the tank body includes: a bottom wall; an inner wall, which is annular, connected to the bottom wall and defines the accommodating cavity with the bottom wall; an outer wall, which is connected to the bottom wall and arranged around the outer circumference of the inner wall, and the outer wall is spaced apart from the inner wall; a top wall, which is arranged opposite to the bottom wall, connects the inner wall and the outer wall, and the bottom wall, the inner wall, the outer wall and the top wall define the cooling channel.

[0009] Optionally, a rib is provided on one side of the inner wall facing the outer wall, the rib protrudes toward the outer wall, and the rib is higher than the inlet and lower than the outlet.

[0010] Optionally, the rib is a conical rib, and a diameter / equivalent diameter of the conical rib gradually decreases in a direction from the inner wall toward the outer wall.

[0011] Optionally, a through hole is provided on the conical rib, and the through hole passes through the side surface of the conical rib in a horizontal direction.

[0012] Optionally, at least one row of heat dissipation components is provided on the inner wall, and each row of the heat dissipation components includes a plurality of the ribs arranged along the circumference of the inner wall.

[0013] Optionally, a plurality of rows of heat dissipation components are provided on the inner wall, the plurality of rows of heat dissipation components are arranged in a vertical direction, and the ribs in two adjacent rows of heat dissipation components are staggered in the axial direction of the cooling channel.

[0014] Optionally, in the vertical direction, the distance between the bottommost heat dissipation component and the bottom wall is L1, the distance between two adjacent rows of heat dissipation components is L2, and L1 is greater than L2.

[0015] Optionally, in the vertical direction, the distance between the topmost heat dissipation component and the top wall is L3, the distance between two adjacent rows of heat dissipation components is L2, and L3 is greater than L2.

[0016] Optionally, a groove is provided on a side surface of the inner wall away from the outer wall, and the groove is recessed toward the outer wall.

[0017] Optionally, the groove and the rib are opposite to each other in the thickness direction of the inner wall.

[0018] Optionally, the inlet and the outlet are respectively arranged on the outer wall, the number of the outlets is multiple, the multiple outlets are arranged along the circumference of the outer wall, and the multiple outlets and the inlet are respectively connected to the refrigerator.

[0019] Optionally, the cooling device further comprises: a throttle valve, wherein the throttle valve is arranged at the inlet.

[0020] According to a second aspect of the utility model, a pulping tank is provided, comprising the cooling device described in any one of the above embodiments.

[0021] According to the cooling device of the utility model, the cooling channel is arranged along the circumference of the accommodating cavity of the tank body, and the inlet is lower than the outlet, and the slurry is cooled by a refrigerant, which can not only obtain a lower cooling temperature by using the refrigerant and increase the heat transfer temperature difference, but also make the refrigerant evenly distributed around the accommodating cavity at the bottom of the cooling channel, and the gas-liquid mixture formed after absorbing heat can also move upward evenly, so that the cooling of the slurry is more uniform. In addition, since the refrigerant is a single working fluid, the temperature of its gas-liquid mixture is fixed, therefore, the refrigerant can evenly absorb heat in the cooling channel, making the cooling effect more uniform and consistent.

[0022] Other features and advantages of the present invention will become apparent from the following detailed description of exemplary embodiments of the present invention with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate embodiments of the present invention and, together with the description, serve to explain the principles of the present invention.

[0024] Figure 1 is a cross-sectional view of a cooling device according to an embodiment of the utility model;

[0025] Figure 2 yes Figure 1 An enlarged view of the circled portion at A in the middle;

[0026] Figure 3 It is a schematic diagram of the arrangement of heat dissipation components in a cooling device according to an embodiment of the utility model;

[0027] Figure 4 It is a schematic diagram of the flow direction of the refrigerant in a cooling device according to an embodiment of the utility model;

[0028] Figure 5 It is a top view of a cooling device according to an embodiment of the utility model.

[0029] Reference numerals

[0030] Cooling device 100;

[0031] Tank body 10; accommodating cavity 11; cooling channel 12; inlet 13; outlet 14; bottom wall 15; inner wall 16; outer wall 17; top wall 18; heat dissipation assembly 20; first row heat dissipation assembly 20a; second row heat dissipation assembly 20b; rib 21; through hole 22; groove 30; throttle valve 40; connecting pipe 50; total outlet 60;

[0032] Slurry 200. DETAILED DESCRIPTION

[0033] Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. It should be noted that unless otherwise specifically stated, the relative arrangements of components and steps, numerical expressions and numerical values ​​set forth in these embodiments do not limit the scope of the present invention.

[0034] The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the present invention, its application, or uses.

[0035] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered as part of the specification.

[0036] In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not limiting. Therefore, other examples of the exemplary embodiments may have different values.

[0037] It should be noted that like reference numerals and letters refer to similar items in the following figures, and therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0038] The cooling device 100 according to the embodiment of the present utility model is first described in detail below with reference to the accompanying drawings.

[0039] like Figures 1 to 5 As shown, the cooling device 100 according to the embodiment of the utility model includes: a tank body 10.

[0040] Specifically, a cylindrical accommodating cavity 11 and a cooling channel 12 suitable for accommodating refrigerant are provided in the tank body 10. The cooling channel 12 is arranged along the circumference of the accommodating cavity 11 and is separated from the accommodating cavity 11. The cooling channel 12 extends along the axial direction of the accommodating cavity 11. An inlet 13 and an outlet 14 are provided on the tank body 10. The inlet 13 and the outlet 14 are spaced apart in the axial direction of the accommodating cavity 11 and are respectively connected to the cooling channel 12. The inlet 13 is lower than the outlet 14.

[0041] In other words, the cooling device 100 according to the embodiment of the utility model is mainly composed of a tank body 10. The tank body 10 is provided with a receiving chamber 11 and a cooling channel 12. The receiving chamber 11 may be cylindrical and used to receive the slurry 200. The slurry 200 generates a lot of heat when being stirred in the receiving chamber 11. The columnar shape may include but is not limited to a cylindrical shape and a polygonal column shape.

[0042] The cooling channel 12 can be separated from the accommodating chamber 11 by a physical structure. The cooling channel 12 is arranged around the outer periphery of the accommodating chamber 11, and the cooling channel 12 can extend along the axial direction of the accommodating chamber 11. The tank body 10 can be a columnar member, and the cooling channel 12 can be an interlayer of the tank body 10. The refrigerant can flow in the cooling channel 12 to dissipate heat from the slurry 200 in the accommodating chamber 11.

[0043] In addition, the cooling channel 12 has an inlet 13 and an outlet 14, which are respectively arranged on the tank body 10. The refrigerant can flow in from the inlet 13, take away the heat generated by the slurry 200 when flowing in the cooling channel 12, and then flow out through the outlet 14.

[0044] Compared with the cooling water cooling method in the conventional technology, the cooling temperature of the refrigerant cooling method is lower, and the temperature difference between the refrigerant and the slurry 200 is greater. The liquid refrigerant can be vaporized after entering the cooling channel 12, and the vaporization process will absorb a large amount of heat and the temperature can remain unchanged, thereby increasing the heat transfer temperature difference and thus increasing the heat transfer amount.

[0045] In addition, the inlet 13 and the outlet 14 can be spaced apart in the axial direction of the accommodating chamber 11, and the inlet 13 can be lower than the outlet 14, so that after the liquid refrigerant enters the cooling channel 12 from the inlet 13, it enters the bottom of the cooling channel 12 under the action of gravity and is opposite to the bottom of the accommodating chamber 11. In other words, the liquid refrigerant can be concentrated and stay at the bottom of the cooling channel 12, and the liquid level can be kept basically horizontal, and at this time, the liquid refrigerant can be evenly distributed in the circumferential direction of the accommodating chamber 11.

[0046] Since the temperature of the liquid refrigerant is relatively low, the heat of the slurry 200 in the receiving chamber 11 will be transferred to the liquid refrigerant through the tank body 10. After the liquid refrigerant absorbs heat, part of the liquid refrigerant will gasify and expand, increase in volume, and form a gas-liquid mixture, which will flow upward. Due to the effect of gravity and the uniform distribution of the original liquid refrigerant, the gas-liquid mixture surrounding the outer periphery of the receiving chamber 11 can move upward roughly uniformly, that is, at any height, the gas-liquid mixture can be evenly distributed in the circumference of the receiving chamber 11.

[0047] As the gas-liquid mixture moves upward, the liquid in the gas-liquid mixture absorbs a large amount of heat and vaporizes after contacting the surface of the tank body 10, cooling the slurry 200. More liquid refrigerant vaporizes into gas, the gas-liquid ratio of the gas-liquid mixture becomes smaller, and the gas-liquid mixture continues to move upward uniformly in the circumferential direction.

[0048] As the height increases, the gas-liquid mixture absorbs more heat, more liquid vaporizes into gas, and the gas-liquid ratio becomes smaller. Due to gravity, all the refrigerant reaching the top of the cooling channel 12 vaporizes into gas, and the gas eventually flows out from the outlet 14.

[0049] In addition, since the refrigerant is a single working fluid, the temperature remains unchanged during the vaporization process. Therefore, the temperature of the gas-liquid mixture is fixed, and the heat transfer temperature difference remains unchanged during the refrigerant flowing from the inlet 13 to the outlet 14 in the cooling channel 12 to absorb heat, the heat transfer amount is consistent, and the cooling effect is uniform.

[0050] Therefore, according to the cooling device 100 of the embodiment of the utility model, the cooling channel 12 is arranged along the circumference of the accommodating chamber 11 of the tank body 10, and the inlet 13 is lower than the outlet 14, and the refrigerant is used to cool the slurry 200. Not only can the refrigerant be used to obtain a lower cooling temperature and increase the heat transfer temperature difference, but the refrigerant can also be evenly distributed around the accommodating chamber 11 at the bottom of the cooling channel 12, and the gas-liquid mixture formed after absorbing heat can also move upward evenly, so that the cooling of the slurry 200 is more uniform. In addition, since the refrigerant is a single working fluid, the temperature of its gas-liquid mixture is fixed, so the refrigerant can evenly absorb heat in the cooling channel 12, making the cooling effect more uniform and consistent.

[0051] In some specific embodiments, a negative pressure environment can be maintained in the cooling channel 12. In other words, a necessary vacuum degree can be maintained in the cooling channel 12, so that the refrigerant can flow from the inlet 13 to the outlet 14 in the negative pressure environment. In addition, since the cooling channel 12 maintains a negative pressure environment, the structure used to form the cooling channel 12 in the tank body 10 needs to have sufficient strength to withstand the pressure. The strength can be designed according to the vacuum degree in the cooling channel 12. The greater the vacuum degree, the greater the strength requirement.

[0052] In some optional embodiments, the cross-sectional areas of the inlet 13 and the outlet 14 are respectively smaller than the cross-sectional area of ​​the cooling channel 12. The cross-sectional area of ​​the cooling channel 12 may be a cross-sectional area obtained by cutting the cooling channel 12 with a plane perpendicular to the axis B of the accommodating chamber 11. The cross-sectional areas of the inlet 13 and the outlet 14 are smaller, and the cross-sectional area of ​​the cooling channel 12 is larger. The volume of the liquid refrigerant increases after vaporization, and the gas-liquid mixture can fill the cooling channel 12. The gas-liquid mixture exchanges heat with the slurry 200 through the tank body 10, and the refrigerant will continue to vaporize, taking away a large amount of heat. As the liquid vaporization ratio in the gas-liquid mixture increases, the volume of the refrigerant increases, and the flow speed increases, thereby ensuring that the refrigerant in the cooling channel 12 flows evenly in the vertical direction.

[0053] According to an embodiment of the present invention, the cooling channel 12 is annular and is disposed around the outer circumference of the accommodating cavity 11 .

[0054] Specifically, the cross section of the cooling channel 12 may be annular. It should be noted that the cross section of the cooling channel 12 may be a cross section obtained by cutting the cooling channel 12 with a plane perpendicular to the axis B of the accommodating cavity 11, and the annular shape may include but is not limited to a circular ring, an elliptical ring, and a square ring, which are not limited here.

[0055] The annular shape may be adapted to the cross-sectional shape of the accommodating cavity 11 . For example, when the cross-sectional shape of the accommodating cavity 11 is circular, the cooling channel 12 may be in the shape of an annular ring.

[0056] In this embodiment, the cooling channel 12 is arranged in an annular shape, which is beneficial to the uniform distribution of the refrigerant in the circumferential direction of the accommodating cavity 11, and is beneficial to uniform heat dissipation, so that the cooling effect around the slurry 200 remains consistent, thereby ensuring the cooling effect of the slurry 200 and improving production efficiency.

[0057] According to some other embodiments of the utility model, the axis B of the accommodating chamber 11 extends in the vertical direction. Since the cooling channel 12 is arranged along the circumference of the accommodating chamber 11, the axis B of the cooling channel 12 can coincide with the axis B of the accommodating chamber 11. For the liquid refrigerant, the liquid level is basically kept horizontal in the cooling channel 12, and the axis B of the accommodating chamber 11 is perpendicular to the liquid level of the liquid refrigerant. The refrigerant can move vertically upward in the cooling channel 12 and gradually vaporize and absorb heat. The formed gas-liquid mixture can be roughly evenly distributed in any horizontal plane, that is, the refrigerant can be evenly distributed at any height of the cooling channel 12. Therefore, the refrigerant can evenly absorb heat, so that the cooling effect of the slurry 200 at each height remains consistent, thereby improving the cooling effect of the slurry 200.

[0058] In some specific embodiments of the present invention, the tank body 10 includes: a bottom wall 15 , an inner wall 16 , an outer wall 17 and a top wall 18 .

[0059] The inner wall 16 is annular, connected to the bottom wall 15 and defines an accommodating chamber 11 with the bottom wall 15. The outer wall 17 is connected to the bottom wall 15 and arranged around the outer circumference of the inner wall 16, and the outer wall 17 is spaced apart from the inner wall 16. The top wall 18 is arranged opposite to the bottom wall 15, and the top wall 18 connects the inner wall 16 and the outer wall 17, and the bottom wall 15, the inner wall 16, the outer wall 17 and the top wall 18 define a cooling channel 12.

[0060] That is to say, the tank body 10 of the present embodiment may be mainly composed of a bottom wall 15, an inner wall 16, an outer wall 17 and a top wall 18. The bottom wall 15 and the top wall 18 may be spaced apart in the vertical direction, the top wall 18 is located above the bottom wall 15, the inner wall 16 and the outer wall 17 may be annular, the inner wall 16 and the outer wall 17 may be nested, and the outer wall 17 may be sleeved on the outer peripheral side of the inner wall 16.

[0061] For the sake of convenience, the direction from the inner wall 16 toward the outer wall 17 may be defined as the outward direction, and the direction from the outer wall 17 toward the inner wall 16 may be defined as the inward direction.

[0062] The bottom of the inner wall 16 may be connected to the bottom wall 15 , and the inner side surface of the inner wall 16 and the top surface of the bottom wall 15 together enclose the accommodating cavity 11 .

[0063] The bottom of the outer wall 17 can be connected to the bottom wall 15, and the top of the outer wall 17 and the top of the inner wall 16 can be connected to the top wall 18 respectively. The inner side surface of the outer wall 17, the outer side surface of the inner wall 16, the top surface of the bottom wall 15 and the bottom surface of the top wall 18 can enclose the cooling channel 12. In other words, the outer wall 17 and the inner wall 16 are spaced apart to form an annular interlayer, which is the cooling channel 12. When the refrigerant moves in the cooling channel 12, the heat of the slurry 200 can be transferred to the refrigerant through the inner wall 16.

[0064] In this embodiment, the tank body 10 includes a bottom wall 15, an inner wall 16, an outer wall 17 and a top wall 18. A sandwich structure surrounding the accommodating cavity 11 can be formed on the tank body 10. The sandwich structure is used as a cooling channel 12, so that the refrigerant can be evenly distributed around the slurry 200 in the accommodating cavity 11 and move upward evenly, so that the cooling effect around the slurry 200 is consistent, which is beneficial to uniform heat dissipation of the slurry 200, ensures the cooling effect of the slurry 200, and improves production efficiency.

[0065] Optionally, the bottom wall 15 and the top wall 18 may be parallel to the horizontal plane, and the inner wall 16 and the outer wall 17 may extend in the vertical direction.

[0066] According to some optional embodiments of the present invention, a rib 21 is provided on one side of the inner wall 16 facing the outer wall 17 . The rib 21 protrudes toward the outer wall 17 . The rib 21 is higher than the inlet 13 and lower than the outlet 14 .

[0067] Specifically, the outer side surface of the inner wall 16 may be provided with a rib 21, and the rib 21 may be a protruding structure, and the protruding structure may protrude toward the outer wall 17, thereby increasing the contact area between the inner wall 16 and the refrigerant and enhancing the heat dissipation effect.

[0068] In addition, in the vertical direction, the height of the rib 21 can be higher than the inlet 13 and lower than the outlet 14, so that the refrigerant can pass through the rib 21 when flowing from the inlet 13 to the outlet 14. When the gas-liquid mixture passes through the rib 21, a bypass flow occurs, the contact area with the inner wall 16 increases, the flow changes dramatically, and the heat transfer between the gas-liquid mixture and the inner wall 16 is enhanced.

[0069] Optionally, the rib 21 may be integrally formed on the outer wall 17 .

[0070] According to some other embodiments of the present invention, Figures 1 to 4 As shown, the rib 21 is a tapered rib, and the diameter / equivalent diameter of the tapered rib gradually decreases in the direction from the inner wall 16 to the outer wall 17 .

[0071] Specifically, the bottom of the tapered rib may be connected to the outer side of the inner wall 16, and the tip of the tapered rib may face the outer wall 17. In the direction from the inner wall 16 to the outer wall 17, any cross section of the tapered rib may be circular, and the diameter / equivalent diameter of the tapered rib gradually decreases from the bottom and finally forms a tip.

[0072] In some optional embodiments, the cross section of the tapered rib may be circular or irregular, which is not limited here. The irregular shape may include but is not limited to elliptical, polygonal and irregular shapes.

[0073] The cross section of the tapered rib may be a cross section obtained by cutting the tapered rib with a plane perpendicular to the axis of the tapered rib. In other words, the area of ​​the cross section of the tapered rib may gradually decrease from the bottom.

[0074] It should be noted that the equivalent diameter may refer to the diameter of a circular cross section having the same cross-sectional area as the special-shaped cross section.

[0075] In this embodiment, the rib 21 is configured as a conical rib, which can increase the contact area between the refrigerant and the inner wall 16 and reduce the volume of the rib 21, thereby reducing the thermal resistance of the solid heat transfer part and enhancing the heat exchange effect.

[0076] In some other embodiments, the rib 21 may be a columnar member, a frustum, or other special-shaped protruding structures, which are not limited here.

[0077] In some specific embodiments of the present invention, a through hole 22 is provided on the conical rib, and the through hole 22 passes through the side surface of the conical rib in the horizontal direction. The through hole 22 is provided on the conical rib, and the inner wall surface of the through hole 22 can contact with the refrigerant for heat exchange, thereby increasing the contact area between the refrigerant and the inner wall 16, increasing the heat exchange amount, and reducing the weight of the tank body 10.

[0078] In addition, the through hole 22 is provided to penetrate the side surface of the conical rib in the horizontal direction, so as to intensify the flow change of the gas-liquid mixture and enhance the heat transfer between the gas-liquid mixture and the inner wall 16 .

[0079] According to some optional embodiments of the utility model, at least one row of heat dissipation components 20 is provided on the inner wall 16, and each row of heat dissipation components 20 includes a plurality of ribs 21 arranged along the circumference of the inner wall 16, thereby increasing the number of ribs 21, which is conducive to increasing the contact area between the refrigerant and the inner wall 16, and strengthening the heat transfer between the refrigerant and the inner wall 16. In addition, the flow of the refrigerant at each row of heat dissipation components 20 changes dramatically, and can change roughly uniformly in the circumference of the inner wall 16, which can better uniformly dissipate heat for the slurry 200 and improve the consistency of cooling.

[0080] Preferably, the multiple ribs 21 of each row of heat dissipation components 20 are evenly arranged along the circumference of the inner wall 16, which can make the gas-liquid mixture more evenly distributed in the circumference of the inner wall 16, which is more conducive to uniform heat dissipation of the slurry 200 and improves the cooling consistency of the slurry 200.

[0081] According to some other embodiments of the present invention, multiple rows of heat dissipation components 20 are provided on the inner wall 16 , and the multiple rows of heat dissipation components 20 are arranged in a vertical direction, and the ribs 21 in two adjacent rows of heat dissipation components 20 are staggered in the axial direction of the cooling channel 12 .

[0082] Specifically, multiple rows of heat dissipation components 20 can be arranged at intervals in the vertical direction. When the gas-liquid mixture formed by the refrigerant absorbing heat and vaporizing moves upward in the vertical direction, it can pass through multiple rows of heat dissipation components 20 in sequence and flow around the ribs 21 of each row of heat dissipation components 20, which is beneficial to increase the contact area between the gas-liquid mixture and the inner wall 16 and enhance heat transfer.

[0083] For the sake of convenience, any two adjacent rows of heat dissipation components 20 may be defined as comprising a first row of heat dissipation components 20a and a second row of heat dissipation components 20b. The first row of heat dissipation components 20a may be located at the bottom of the second row of heat dissipation components 20b. Figure 3 As shown, any rib 21 in the first row of heat dissipation components 20a and any rib 21 in the second row of heat dissipation components 20b may be staggered in the vertical direction.

[0084] When the gas-liquid mixture flows from bottom to top, it first passes through the first row of heat dissipation components 20a. The contact area at the place where the ribs 21 are provided on the inner wall 16 is large, the heat exchange is large, the vaporized liquid is large, and the gas-liquid ratio changes greatly. The contact area between two adjacent ribs 21 is small, the heat exchange is small, the vaporized liquid is small, and the gas-liquid ratio changes less than the place where the ribs 21 are provided. When the gas-liquid mixture moves upward to the second row of heat dissipation components 20b, the place where the gas-liquid ratio changed less before can pass through the ribs 21 in the second row of heat dissipation components 20b. At this time, the contact area here is large, the heat exchange is large, the vaporized liquid is large, and the gas-liquid ratio changes greatly. This can improve the uniformity of the gas-liquid ratio in the circumferential direction of the cooling channel 12, so that the gas-liquid mixture in the circumferential direction flows upward uniformly, thereby ensuring the uniformity of the circumferential heat exchange.

[0085] In some optional embodiments, in three adjacent rows of heat dissipation components 20, the ribs 21 in the top heat dissipation component 20 and the ribs 21 in the bottom heat dissipation component 20 are arranged one by one opposite to each other in the vertical direction, which is beneficial to further improve the uniformity of the gas-liquid ratio in the circumferential direction of the cooling channel 12.

[0086] According to some optional embodiments of the present invention, in the vertical direction, the distance between the bottommost heat dissipation assembly 20 and the bottom wall 15 is L1, and the distance between two adjacent rows of heat dissipation assemblies 20 is L2, where L1 is greater than L2.

[0087] like Figure 1 As shown, the distance L1 between the bottom heat dissipation assembly 20 and the bottom wall 15 may be the distance between the center point of any rib 21 in the bottom row of heat dissipation assemblies 20 in the vertical direction and the top surface of the bottom wall 15 in the vertical direction.

[0088] The distance L2 between two adjacent rows of heat dissipation components 20 may be the distance in the vertical direction between the center point of any rib 21 in the first row of heat dissipation components 20a and the center point of any rib 21 in the second row of heat dissipation components 20b.

[0089] When the rib 21 is a tapered rib, the height of the center point of any one of the ribs 21 in the vertical direction may be the height of the tip of the tapered rib.

[0090] Since the heat exchange effect of the gaseous refrigerant is much smaller than the heat exchange effect of the liquid refrigerant, setting L1 greater than L2 can leave a larger space at the bottom of the cooling channel 12 for accommodating the liquid refrigerant, increase the contact area between the liquid refrigerant and the inner wall 16, and enhance the heat exchange effect.

[0091] According to some other embodiments of the present invention, in the vertical direction, the distance between the topmost heat dissipation assembly 20 and the top wall 18 is L3, and the distance between two adjacent rows of heat dissipation assemblies 20 is L2, and L3 is greater than L2.

[0092] like Figure 1 As shown, the distance L3 between the top heat dissipation assembly 20 and the top wall 18 may be the distance between the center point of any rib 21 in the top row of heat dissipation assemblies 20 in the vertical direction and the bottom surface of the top wall 18 in the vertical direction.

[0093] By setting L3 larger than L2, a larger space can be reserved at the top of the cooling channel 12 for the gaseous refrigerant to flow out. Figure 4 As shown, during slurrying, a certain distance is left between the liquid level of the slurry 200 in the tank 10 and the top wall 18, and the height of the top row of heat dissipation components 20 can be lower than the liquid level of the slurry 200. The heat transfer coefficient of the gaseous refrigerant is small, and the gaseous refrigerant can be discharged from the top of the cooling channel 12 without affecting the cooling of the slurry 200.

[0094] In some specific embodiments of the utility model, a groove 30 is provided on one side of the inner wall 16 away from the outer wall 17, and the groove 30 is recessed toward the outer wall 17. When the slurry 200 flows in the accommodating chamber 11, the slurry 200 flows violently at the groove 30, forming a vigorous turbulence, and there is a strong mass exchange inside the slurry 200. At the same time, the relative speed between the slurry 200 and the inner wall 16 is greater, which enhances the heat exchange effect between the slurry 200 and the inner wall 16. In addition, the groove 30 is also conducive to increasing the contact area between the slurry 200 and the inner wall surface, thereby increasing the heat exchange amount and improving the heat exchange efficiency.

[0095] The groove 30 may be any shape as long as it can increase the contact area between the inner wall 16 and the slurry 200. It is not limited here. Preferably, the groove 30 may be a spherical groove, and the inner wall surface of the spherical groove may be an arc surface, which is conducive to the formation of vigorous turbulence of the slurry 200 in the spherical groove, further enhancing the mass exchange inside the slurry 200, thereby improving the heat exchange effect.

[0096] According to some optional embodiments of the present invention, the groove 30 and the rib 21 are arranged opposite to each other in the thickness direction of the inner wall 16 , which may specifically include but are not limited to the following situations.

[0097] In case 1, the plurality of grooves 30 and the plurality of ribs 21 correspond one to one in the thickness direction of the inner wall 16;

[0098] In case 2, a portion of the plurality of grooves 30 may be opposite to the plurality of ribs 21 in the thickness direction of the inner wall 16, and another portion of the plurality of grooves 30 may be staggered from the plurality of ribs 21 in the thickness direction of the inner wall 16;

[0099] In case three, a portion of the plurality of ribs 21 may be opposite to the plurality of grooves 30 in the thickness direction of the inner wall 16 , and another portion of the plurality of ribs 21 may be staggered from the grooves 30 in the thickness direction of the inner wall 16 .

[0100] That is, at least one groove 30 and at least one rib 21 are arranged opposite to each other in the thickness direction of the inner wall 16.

[0101] Thus, the thickness of the inner wall 16 at the position where the groove 30 and the rib 21 are opposite to each other can be reduced, thereby reducing the thermal resistance of the solid part and further enhancing the heat exchange effect.

[0102] In some optional embodiments, the center line of the groove 30 may coincide with the axis of the conical rib, so that the thickness of the conical rib at various locations in its circumference is roughly equal, which is beneficial to improving the consistency and uniformity of heat exchange.

[0103] Preferably, the grooves 30 and the ribs 21 can be arranged in a one-to-one correspondence in the thickness direction of the inner wall 16, that is, on the inner wall 16, the number of grooves 30 and ribs 21 is equal, and a groove 30 is provided at the position corresponding to each rib 21. This is not only beneficial to increase the number of grooves 30 and further increase the contact area between the slurry 200 and the inner wall 16, but also can further reduce the wall thickness of the ribs 21, reduce the thermal resistance of the solid part, and better enhance heat exchange.

[0104] According to some other embodiments of the utility model, the inlet 13 and the outlet 14 are respectively arranged on the outer wall 17, the number of the outlets 14 is multiple, and the multiple outlets 14 are arranged along the circumference of the outer wall 17, and the multiple outlets 14 and the inlet 13 are respectively connected to a refrigerator (not shown in the figure).

[0105] Specifically, the inlet 13 and the outlet 14 are arranged on the outer wall 17, so that the external cooling circuit can be connected to the inlet 13 and the outlet 14 respectively through the connecting pipe 50. Since the volume of the refrigerant expands after gasification, the multiple outlets 14 can be provided to discharge the gaseous refrigerant in time, so as to avoid the accumulation of the gaseous refrigerant in the cooling channel 12 and affect the heat exchange effect.

[0106] Optionally, the plurality of outlets 14 may be evenly spaced and arranged along the circumference of the outer wall 17, thereby making the gaseous refrigerant at the top of the cooling channel 12 more evenly distributed, thereby preventing the gaseous refrigerant from being locally accumulated and affecting the cooling effect. Figure 5 As shown, five outlets 14 may be provided on the outer wall 17 , and the five outlets 14 are evenly spaced and arranged along the circumference of the outer wall 17 .

[0107] In addition, multiple outlets 14 can be connected to a total outlet 60 through a connecting pipe 50, and then the total outlet 60 can be connected to the refrigerator, and the inlet 13 can also be connected to the refrigerator. The refrigerator can receive gaseous refrigerant from the total outlet 60, liquefy the gaseous refrigerant, and then transport liquid refrigerant to the inlet 13. When the refrigerator is working, it will draw air, thereby forming a vacuum in the cooling channel 12 to drive the refrigerant to flow from the inlet 13 to the outlet 14.

[0108] In some specific embodiments of the present invention, the cooling device 100 further includes a throttle valve 40 , which is disposed at the inlet 13 . The throttle valve 40 can control the refrigerant flow rate at the inlet 13 , thereby adjusting the cooling effect of the cooling device 100 .

[0109] The embodiment of the utility model further provides a pulping tank, which includes a cooling device 100 according to any of the above embodiments. Since the cooling device 100 according to the embodiment of the utility model has the above technical effects, the pulping tank according to the embodiment of the utility model also has corresponding technical effects, that is, the refrigerant can be used to obtain a lower cooling temperature, increase the heat transfer temperature difference, so that the refrigerant is evenly distributed around the accommodating cavity 11 at the bottom of the cooling channel 12, and the gas-liquid mixture formed after absorbing heat can also move upward evenly, so that the cooling of the slurry 200 is more uniform. In addition, since the refrigerant is a single working fluid, the temperature of its gas-liquid mixture is fixed, therefore, the refrigerant can evenly absorb heat in the cooling channel 12, so that the cooling effect is more uniform and consistent.

[0110] Although some specific embodiments of the present invention have been described in detail by way of examples, it should be understood by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the present invention. It should be understood by those skilled in the art that the above embodiments may be modified without departing from the scope and spirit of the present invention. The scope of the present invention is defined by the appended claims.

Claims

1. A cooling device, characterized in that: include: A tank body is provided with a cylindrical accommodating cavity and a cooling channel suitable for accommodating a refrigerant, the cooling channel is arranged along the circumference of the accommodating cavity and is separated from the accommodating cavity, the cooling channel extends along the axial direction of the accommodating cavity, an inlet and an outlet are provided on the tank body, the inlet and the outlet are spaced apart in the axial direction of the accommodating cavity and are respectively connected to the cooling channel, and the inlet is lower than the outlet.

2. The cooling device according to claim 1, characterized in that: The cooling channel is annular and is arranged around the outer circumference of the accommodating cavity.

3. The cooling device according to claim 1, characterized in that: The axis of the accommodating cavity extends in the vertical direction.

4. The cooling device according to any one of claims 1 to 3, characterized in that: The tank body comprises: bottom wall; An inner wall, the inner wall is annular, the inner wall is connected to the bottom wall and defines the accommodating cavity with the bottom wall; an outer wall, the outer wall being connected to the bottom wall and arranged around the outer circumference of the inner wall, the outer wall being spaced apart from the inner wall; A top wall, the top wall is arranged opposite to the bottom wall, the top wall connects the inner wall and the outer wall, and the bottom wall, the inner wall, the outer wall and the top wall define the cooling channel.

5. The cooling device according to claim 4, characterized in that: A rib is provided on one side of the inner wall facing the outer wall. The rib is protruding toward the outer wall. The rib is higher than the inlet and lower than the outlet.

6. The cooling device according to claim 5, characterized in that: The rib is a tapered rib, and a diameter / equivalent diameter of the tapered rib gradually decreases in a direction from the inner wall to the outer wall.

7. The cooling device according to claim 6, characterized in that: The conical rib is provided with a through hole, and the through hole passes through the side surface of the conical rib in a horizontal direction.

8. The cooling device according to claim 5, characterized in that: At least one row of heat dissipation components is disposed on the inner wall, and each row of the heat dissipation components includes a plurality of ribs arranged along the circumference of the inner wall.

9. The cooling device according to claim 8, characterized in that: A plurality of rows of heat dissipation components are arranged on the inner wall, and the plurality of rows of heat dissipation components are arranged in a vertical direction, and the ribs in two adjacent rows of heat dissipation components are staggered in the axial direction of the cooling channel.

10. The cooling device according to claim 9, characterized in that: In the vertical direction, the distance between the bottommost heat dissipation component and the bottom wall is L1, and the distance between two adjacent rows of heat dissipation components is L2, where L1 is greater than L2.

11. The cooling device according to claim 9, characterized in that: In the vertical direction, the distance between the topmost heat dissipation component and the top wall is L3, and the distance between two adjacent rows of heat dissipation components is L2, and L3 is greater than L2.

12. The cooling device according to claim 5, characterized in that: A groove is provided on a side surface of the inner wall away from the outer wall, and the groove is recessed toward the outer wall.

13. The cooling device according to claim 12, characterized in that: The groove and the rib are arranged opposite to each other in the thickness direction of the inner wall.

14. The cooling device according to claim 5, characterized in that The inlet and the outlet are respectively arranged on the outer wall, the number of the outlets is multiple, the multiple outlets are arranged along the circumference of the outer wall, and the multiple outlets and the inlet are respectively connected to the refrigerator.

15. The cooling device according to claim 1, characterized in that Also includes: A throttle valve is arranged at the inlet.

16. A pulping tank, characterized in that: include: The cooling device according to any one of claims 1 to 15.

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