Heating tube and heating device

Abstract

The application relates to the technical field of heating equipment, and discloses a heating pipe and a heating device. The heating pipe comprises an outer shell, a shaft core, a partition plate and a protrusion. The shaft core is arranged in the outer shell, the partition plate is arranged on the surface of the shaft core, the space between the shaft core and the outer shell is divided into a plurality of flow channels by the partition plate, and the protrusion is arranged on the surface of the shaft core and located in the flow channels. The flow channels are formed by arranging the partition plate on the surface of the shaft core, and the protrusion is arranged on the surface of the shaft core in the flow channels. When the fluid flows in the flow channels, the fluid is disturbed by the partition plate and the protrusion at the same time, the effect of the disturbance and the turbulence is significantly enhanced, the fluid and the inner wall of the outer shell are fully exchanged, and the heating efficiency is greatly improved.

Description

Technical Field

[0001] This application relates to the field of heating equipment technology, and in particular to a heating tube and a heating device. Background Technology

[0002] With the rapid development of the new energy vehicle industry, automotive thermal management systems are playing an increasingly important role in vehicle energy management and passenger cabin comfort adjustment. As a core component of the thermal management system, the automotive thermal management all-in-one compressor integrates multiple functions such as compression, heating, and control. It typically contains heating pipes to heat the flowing liquid, meeting the heating needs of the battery, passenger cabin, and other components in low-temperature environments.

[0003] However, the structure of the baffles in current heating pipes is relatively simple. For example, a single or double-headed spiral baffle is only installed inside the pipe. The fluid flows smoothly along a relatively fixed path in the spiral channel. The baffle only plays a simple guiding role for the fluid and it is difficult to form effective turbulence in the flow channel. The boundary layer between the fluid and the pipe wall is not easily broken, resulting in low heat exchange efficiency between the fluid and the pipe wall and the liquid cannot be fully heated. Summary of the Invention

[0004] This application provides a heating tube and heating device that can enhance the turbulence and flow effects of fluid in the flow channel, so that the fluid is fully heated and the heating efficiency is improved.

[0005] In a first aspect, this application provides a heating tube, which includes a shell, a core, a partition, and a protrusion. The core is disposed within the shell, and the partition is disposed on the surface of the core, dividing the space between the core and the shell into several flow channels. The protrusion is disposed on the surface of the core and located within the flow channels. By providing a partition on the surface of the core to form flow channels, and providing a protrusion on the surface of the core within the flow channels, the fluid flowing within the flow channels is simultaneously subjected to dual disturbances from the partition and the protrusion. This significantly enhances the turbulence and flow effects, allowing for sufficient heat exchange between the fluid and the inner wall of the shell, thereby greatly improving the heating efficiency.

[0006] In some embodiments, the partition is spiral-shaped and extends axially along the shaft core.

[0007] In some embodiments, the number of partitions is multiple, and the partitions are integral helical structures that extend continuously along the axial direction of the shaft core; and / or, the partitions include multiple helical segments arranged at intervals along the axial direction of the shaft core.

[0008] In some embodiments, along the flow direction of the fluid, the starting end of the downstream spiral segment is correspondingly disposed between the flow channels formed by two adjacent upstream spiral segments.

[0009] In some embodiments, the total rotation angle of the partition along the circumference of the shaft is less than or equal to 180°.

[0010] In some embodiments, the total rotation angle is 70° to 110°.

[0011] In some embodiments, the upstream end of the partition has a radially increasing bevel, the bevel connecting the surface of the shaft core and the edge of the partition radially away from the shaft core.

[0012] In some embodiments, the partition has a gap of 0 mm to 1 mm between its radially away edge from the shaft and the inner wall of the housing; and / or, the radial distance between the surface of the shaft and the inner wall of the housing is 2.5 mm to 5 mm along the radial direction of the shaft.

[0013] In some embodiments, the partition has an opening that connects to flow channels on both sides of the partition.

[0014] In some embodiments, the opening includes a notch or groove disposed on the edge of the partition, and / or the opening includes a closed through hole disposed on the plate body of the partition.

[0015] In some embodiments, the protrusion includes a plurality of circumferentially extending annular protrusions, which are spaced apart along the axial direction of the shaft core, with openings located axially between adjacent annular protrusions.

[0016] In some embodiments, the edge of the opening is provided with a deflection portion, which is deflected relative to the side of the partition plate facing the plate surface. The deflection direction of the deflection portion is the same as or opposite to the spiral direction of the partition plate.

[0017] In some embodiments, the shaft core has a constant diameter structure; or, the shaft core has a non-constant diameter structure, and along the axial direction of the shaft core, the shaft core is provided with at least one step with a drop.

[0018] In some embodiments, the housing is an integral tubular structure; and / or, a heating film assembly is provided on the outer wall of the housing.

[0019] Secondly, this application provides a heating device, which includes at least one bent tube and at least two heating tubes. The bent tube is connected between the two heating tubes. The heating tube at one end of the heating device is provided with an inlet for fluid to enter, and the heating tube at the other end of the heating device is provided with an outlet for fluid to flow out.

[0020] In some embodiments, the baffles within at least two heating tubes have the same or opposite spiral directions.

[0021] The beneficial effects of this application embodiment are as follows: The heating tube of this application sets a core inside the shell, sets a baffle on the surface of the core to divide the space between the core and the shell into several flow channels, and sets a protrusion on the surface of the core in the flow channels. When the fluid flows in the flow channels, it is simultaneously subjected to the dual disturbance effect of the baffle and the protrusion, thereby generating sufficient turbulence in the flow channels. This effectively breaks the boundary layer between the fluid and the inner wall of the shell, enhances the heat exchange effect between the fluid and the inner wall of the shell, and allows the liquid to be fully heated, significantly improving the heating efficiency. At the same time, it avoids the situation of local overheating of the heating film assembly on the outer wall of the shell, and extends the service life of the heating tube. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the specific embodiments of this application, the accompanying drawings used in the description of the specific embodiments will be briefly introduced below. In all the drawings, similar elements or parts are generally identified by similar reference numerals. In the drawings, the elements or parts are not necessarily drawn to scale.

[0023] Figure 1 This is a schematic diagram of the heating device according to an embodiment of this application; Figure 2 This is an exploded view of the heating device according to an embodiment of this application; Figure 3 This is a partial structural schematic diagram of the heating tube in an embodiment of this application; Figure 4 This is a partial structural schematic diagram of the heating tube according to another embodiment of this application; Figure 5 The heating element in the embodiment of this application is Figure 4 A magnified view of part B in the middle; Figure 6 In another embodiment of this application, the heating element is... Figure 4 A magnified view of part B in the middle; Figure 7 The heating device in the embodiments of this application is Figure 1 A sectional view along the middle AA; Figure 8 The heating device in the embodiments of this application is Figure 7 A magnified view of part C in the middle.

[0024] The attached icons are numbered as follows: 100. Heating element; 10. Outer shell; 11. Bracket; 20. Shaft core; 21. Gap; 22. Drop step; 30. Partition; 31. Spiral section; 32. Bevel; 33. Opening; 331. Notch / groove; 34. Deflection section; 40. Protrusion; 41. Annular protrusion; 50. Flow channel; 60. Heating film assembly; 200. Heating device; 201. Bent pipe; 202. Inlet; 203. Outlet. Detailed Implementation

[0025] To facilitate understanding of this application, a more detailed description is provided below with reference to the accompanying drawings and specific embodiments. It should be noted that when an element is described as "fixed to" another element, it can be directly on the other element, or one or more intermediate elements may exist between them. When an element is described as "connected" to another element, it can be directly connected to the other element, or one or more intermediate elements may exist between them. The terms "upper," "lower," "inner," "outer," "vertical," "horizontal," etc., used in this specification indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0026] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of the application. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0027] Furthermore, the technical features involved in the different embodiments of this application described below can be combined with each other as long as they do not conflict with each other.

[0028] In existing heating pipes, a single type of spiral baffle is typically installed inside the pipe to guide the flowing fluid. As the fluid flows along the spiral channel, it is guided to contact the pipe wall for heat exchange. However, in this type of structure, the fluid flow path is relatively fixed, and the baffle only plays a simple guiding role, making it difficult to form effective turbulence within the pipe. The boundary layer between the fluid and the pipe wall is not easily disrupted, resulting in low heat exchange efficiency between the fluid and the pipe wall, and the liquid cannot be fully heated. At the same time, due to the uneven heat exchange between the fluid and the pipe wall, localized overheating of the heating film assembly outside the heating pipe can easily occur, thereby affecting the service life of the heating pipe and even posing a risk of localized burnout.

[0029] For the above issues, please refer to Figures 1 to 3This application provides a heating tube 100, which includes a housing 10, a core 20, a partition 30, and a protrusion 40. The core 20 is disposed within the housing 10, and the core 20 and the housing 10 are spaced apart along the radial direction of the core 20 to have space. The partition 30 is disposed on the surface of the core 20, and the partition 30 divides the space between the core 20 and the housing 10 to form a plurality of flow channels 50 for fluid flow. The protrusion 40 is disposed on the surface of the core 20 and located within the flow channels 50, and the protrusion 40 is used to turbulentize the fluid within the flow channels 50 to increase the turbulence and flow effect of the fluid.

[0030] When the fluid flows in the flow channel 50, it is guided by the baffle 30 to form a flow along the extension direction of the baffle 30. On the other hand, it is blocked and disturbed by the protrusion 40 on the surface of the shaft core 20, causing the fluid to generate multi-directional turbulence in the flow channel 50.

[0031] In this application, the baffle 30 and the protrusion 40 in the heating tube 100 work together to create a double disturbance to the fluid, which can effectively break the boundary layer between the fluid and the inner wall of the outer shell 10, enhance the heat exchange effect between the fluid and the inner wall of the outer shell 10, thereby fully heating the liquid and improving the heating efficiency of the heating tube 100. At the same time, since the heat exchange of the fluid in the flow channel 50 is more uniform, it also avoids the local temperature on the outer wall of the outer shell 10 from being too high, which is conducive to extending the service life of the heating tube 100.

[0032] In some embodiments, please refer to Figure 2 and Figure 7 The outer casing 10 is a hollow tubular structure, with its two ends used to connect to external pipelines for fluid inflow and outflow. In some embodiments, the outer casing 10 is a one-piece tubular structure. By making the outer casing 10 a one-piece tubular structure, it avoids the need for separate sealing structures, thereby eliminating the need for sealing rings in traditional solutions, eliminating the risk of leakage due to sealing ring aging, and improving the reliability and service life of the heating element 100.

[0033] Furthermore, the outer casing 10 is preferably made of a metal material with good thermal conductivity and corrosion resistance, such as stainless steel. The outer casing 10 and other components of the heating tube 100 (such as the end cap of the heating tube 100, the support structure of the shaft core 20, etc.) can be connected and fixed by welding to further ensure the sealing and structural reliability of the heating tube 100.

[0034] In some embodiments, please refer to Figure 2 and Figure 7 A heating film assembly 11 is provided on the outer wall of the outer casing 10. The heating film assembly 11 is disposed on the outer wall of the outer casing 10. When the heating film assembly 11 is powered on, it generates heat, which is transferred through the outer casing 10 to the fluid in the flow channel 50, thereby heating the fluid.

[0035] The heating film assembly 11 can take various forms, such as a thick film heating assembly or a thin film heating assembly. Specifically, the heating film assembly 11 can be directly printed on the outer wall of the housing 10 to form an integral structure with the housing 10, so that the heat generated by the heating film assembly 11 can be efficiently transferred to the inner wall of the housing 10 and the fluid in the flow channel 50, reducing heat loss and improving heating efficiency.

[0036] In a further embodiment, the heating film assembly 11 is multiple and arranged in sections along the axial direction of the shaft core 20, and the multiple heating film assemblies 11 can be independently controlled by a controller. The heating film assemblies 11 in different regions can be set with the same heating power or different heating power. For example, the heating film assembly 11 located in the upstream region of the flow channel 50 has a large heating power, and the heating film assembly 11 located in the downstream region of the flow channel 50 has a small heating power.

[0037] In a further embodiment, the heating tube 100 may also have an axially elongated heating rod disposed at the inner center of the shaft core 20. The heating rod is used to heat the shaft core 20, thereby exchanging heat with the fluid through the surface of the shaft core 20. This allows the heating tube 100 to heat the fluid on both the inner and outer radial sides, resulting in a faster heating speed.

[0038] In some embodiments, please refer to Figure 2 and Figure 3 The shaft core 20 is a columnar structure and is located at the center of the outer shell 10. The two ends of the shaft core 20 can be supported in the outer shell 10 by structures such as brackets 11, or can be fixedly connected to the end caps of the outer shell 10. The specific fixing method between the shaft core 20 and the outer shell 10 is not limited in this embodiment.

[0039] In some embodiments, the partition 30 is in the form of a thin sheet, one side of the partition 30 is fixed to the outer surface of the shaft core 20, and the other side of the partition 30 extends outward along the radial direction of the shaft core 20 to form a baffle structure, which cooperates with the inner wall of the housing 10 to form a plurality of separated flow channels 50.

[0040] The protrusion 40 protrudes from the outer surface of the shaft core 20 toward the outer casing 10 and is located within the flow channel 50. The protrusion 40 can be in various shapes such as ring-shaped, block-shaped, or strip-shaped. The specific shape of the protrusion 40 is not limited in this embodiment. In some embodiments, the surface of the protrusion 40 is arc-shaped, which increases the turbulence effect without excessively increasing the flow resistance of the fluid in the flow channel 50.

[0041] In some embodiments, the baffle 30 is a flat plate extending axially along the shaft core 20, making all flow channels 50 flat. A plurality of spaced protrusions 40 are provided in the flow channels 50, which can increase the turbulence and flow of the fluid. In a further embodiment, the baffle 30 can be a single flat plate extending from one end of the shaft core 20 to the other end, which facilitates processing and manufacturing. In other embodiments, between the two ends of the shaft core 20, the baffle 30 can include a plurality of flat plates spaced axially, allowing fluid in adjacent flow channels to flow across the cross-section of the flat plates, thus increasing the turbulence effect.

[0042] Please continue reading. Figure 2 and Figure 3 In some embodiments, the baffle 30 is helical and extends axially along the core 20. Setting the baffle 30 in a helical shape serves two purposes: firstly, it extends the flow path of the fluid within the outer casing 10, increasing the heat exchange time between the fluid and the inner wall of the outer casing 10; secondly, the helical baffle 30 guides the fluid to flow in a helical direction, causing the fluid to generate a circumferential velocity around the core 20 during flow, which, combined with the fluid's own axial flow, forms a helical flow state, further enhancing the contact effect between the fluid and the inner wall of the outer casing 10 and improving heat exchange efficiency.

[0043] Please see Figure 3 and Figure 4 In some embodiments, there are multiple partitions 30, which are spaced apart in the circumferential direction of the core 20 to divide the space between the core 20 and the housing 10 into multiple side-by-side flow channels.

[0044] Furthermore, the partition 30 may be an integral helical structure that extends continuously along the axial direction of the core 20; and / or, the partition 30 may include multiple helical segments 31 arranged at intervals along the axial direction of the core 20.

[0045] like Figure 3 As shown, when the baffle 30 adopts an integrated spiral structure, the fluid flows along the continuous spiral flow channel 50, resulting in good flow stability; Figure 4 As shown, when the baffle 30 is arranged in the form of multiple spiral segments 31, the fluid will diffuse and converge in the two adjacent flow channels 50 when it flows through the interval area between two adjacent spiral segments 31, forming additional disturbances and further improving the turbulence effect.

[0046] It is understood that the two structures of the partition 30 of this application can be selected according to actual heating needs, or combined and arranged in the same heating tube 100, so as to stabilize the flow of fluid while taking into account the effect of enhancing turbulence.

[0047] In an embodiment where the partition 30 includes multiple axially spaced spiral segments 31, please refer to... Figure 4 Along the flow direction of the fluid, the starting end of the downstream spiral segment 31 is correspondingly positioned between the flow channels 50 formed by the two adjacent upstream spiral segments 31.

[0048] With the above structural configuration, when the fluid flows through the upstream spiral section 31, it will flow along the corresponding flow channel 50. When this part of the fluid reaches the downstream spiral section 31, since the starting end of the downstream spiral section 31 is located in the area of ​​the upstream flow channel 50, the fluid flowing out of the upstream flow channel 50 will be divided into two by the starting end of the downstream spiral section 31, so that they enter the downstream flow channels 50 on both sides of the downstream spiral section 31 respectively, forming a redistribution and mixing of the fluid, thereby generating a significant turbulence effect in the downstream flow channel 50, further promoting the heat exchange between the fluid and the inner wall of the outer shell 10.

[0049] In some embodiments, the total rotation angle of the baffle 30 along the circumference of the shaft core 20 is less than or equal to 180°. If the total rotation angle of the baffle 30 is too large, the spiral density of the flow channel 50 will be too high, and the resistance experienced by the fluid during flow will be too great, requiring a water pump with a higher head to maintain normal flow rate and velocity. Therefore, this application controls the total rotation angle of the baffle 30 along the circumference of the shaft core 20 to within 180°, which can reduce the flow resistance of the flow channel 50 to the fluid while ensuring the turbulence effect, so that the heating tube 100 can be matched with a water pump with a conventional head, reducing the overall system cost.

[0050] Furthermore, in some embodiments, the total rotation angle of the baffle 30 is 70° to 110°, for example, it can be 70°, 75°, 80°, 85°, 90°, 95°, 100°, 105° or 110°, preferably 90°. When the total rotation angle is within the above range or value, the helical density of the baffle 30 can ensure that the fluid generates sufficient helical flow to promote heat transfer, while controlling the flow resistance at a low level, achieving the best balance between turbulence effect and flow resistance.

[0051] Please see Figure 3 , Figure 4 and Figure 7 In some embodiments, along the flow direction of the fluid, the upstream end of the baffle 30 is provided with a radially enlarging bevel 32, the bevel 32 connecting the surface of the core 20 and the edge of the baffle 30 radially away from the core 20.

[0052] The upstream end of the baffle 30 in this application does not have a stepped abrupt change in the radial direction, but rather a gentle transition through the inclined edge 32. In this way, the fluid entering the heating tube 100 from the outside can be buffered in the area corresponding to the inclined edge 32, avoiding abrupt entry into one of the flow channels 50. When the fluid flows into the flow channel 50, it can be smoothly distributed along the inclined edge 32 to the flow channels 50 on both sides of the baffle 30, avoiding severe impact and eddy current losses at the end of the baffle 30, which helps to reduce the flow resistance of the fluid. At the same time, the inclined edge 32 can make the distribution of fluid among the flow channels 50 more balanced, avoiding the situation where the flow rate of one flow channel 50 is too large while the flow rate of other flow channels 50 is insufficient, thereby making the overall heat exchange effect of the heating tube 100 more uniform.

[0053] Furthermore, the shape of the upstream end of the partition 30 can be a wedge-shaped triangle or a trapezoidal shape that is close to a wedge.

[0054] In some embodiments, the partition 30 is disposed in abutment between its edge radially away from the core 20 and the inner wall of the housing 10, which can enhance the connection stability between the partition 30 and the housing 10.

[0055] Please see Figure 7 In other embodiments, a gap 21 is provided between the edge of the partition 30 radially away from the core 20 and the inner wall of the housing 10, and the radial dimension L1 of the gap 21 is 0 mm to 1 mm. Controlling the gap 21 between the partition 30 and the inner wall of the housing 10 between 0 mm and 1 mm can, on the one hand, prevent direct contact between the partition 30 and the inner wall of the housing 10, preventing the partition 30 from directly abutting against the inner wall of the housing 10 during assembly or thermal expansion and contraction, thus avoiding the risk of localized dry burning of the heating film assembly 11 in this area; on the other hand, the gap 21 allows for a small amount of circumferential permeation and exchange of fluid between adjacent flow channels 50, forming additional microscopic disturbances and further enhancing the turbulence effect. In a further embodiment, the radial dimension L1 of the gap 21 is 0.3 mm to 0.6 mm.

[0056] Please see Figure 7 In some embodiments, the radial distance L2 between the surface of the shaft core 20 and the inner wall of the housing 10 is 2.5 mm to 5 mm along the radial direction of the shaft core 20. Controlling the radial distance between the surface of the shaft core 20 and the inner wall of the housing 10 to between 2.5 mm and 5 mm can ensure that the flow channel 50 has a sufficient flow cross-section while avoiding the flow channel 50 being too large and reducing the heat exchange efficiency between the fluid and the inner wall of the housing 10, thus balancing flow rate and heat exchange performance.

[0057] Please see Figure 3 and Figure 4 , Figure 5 and Figure 6In some embodiments, the baffle 30 is provided with an opening 33, which connects the adjacent flow channels 50a and 50b on both sides of the baffle 30. Traditional spiral turbulence devices typically separate each flow channel 50 independently, and the fluid flows smoothly in the spiral direction within each flow channel 50. The fluid between adjacent flow channels 50 cannot be exchanged, resulting in limited turbulence effect.

[0058] In this embodiment, by providing an opening 33 on the partition 30, the fluid between adjacent flow channels 50a and 50b can flow and exchange circumferentially through the opening 33, breaking the independence of the flow in the spiral flow channel 50. While the fluid flows in the spiral direction, the circumferential flow across the flow channel 50 is superimposed, forming a significant turbulence effect, thereby greatly improving the heat exchange efficiency between the fluid and the inner wall of the outer shell 10, and ensuring that the liquid is fully heated.

[0059] Please see Figure 3 and Figure 4 In some embodiments, the opening 33 includes a notch 331 disposed on the edge of the partition 30. The notch 331 is recessed inward from the edge of the partition 30 away from the shaft core 20. Fluid can flow through the notch 331 between adjacent flow channels 50a and 50b. At the same time, the notch 331 is relatively simple to manufacture and easy to process.

[0060] In some embodiments, the opening 33 includes a closed through hole disposed on the plate body of the partition 30. The closed through hole penetrates the plate body of the partition 30, and fluid can flow between adjacent flow channels 50a and 50b through the closed through hole. Compared with the notch groove 331, the closed through hole can maintain the integrity and rigidity of the partition 30 structure.

[0061] It is understandable that the structure of the partition 30 can include either a notch 331 or a through hole, or both, to achieve a richer streaming effect.

[0062] Please see Figure 3 and Figure 4 In some embodiments, the protrusion 40 includes a plurality of circumferentially extending annular protrusions 41, and the plurality of annular protrusions 41 are spaced apart along the axial direction of the core 20, and the opening 33 is located axially between two adjacent annular protrusions 41.

[0063] In this application, the protrusion 40 is configured as a circumferentially extending annular protrusion 41, which can form a circumferential surrounding obstruction of the fluid, causing the fluid to generate violent contraction, expansion and vortex before and after the annular protrusion 41, forming a first-level disturbance; at the same time, by arranging multiple annular protrusions 41 at intervals along the axial direction of the shaft core 20, a multi-level series disturbance can be formed in the flow channel 50, further enhancing the turbulence effect.

[0064] By placing the opening 33 in the region between two adjacent annular protrusions 41, on the one hand, the fluid can be disturbed by the annular protrusions 41 and then flow across the flow channel 50 through the opening 33, forming a combined turbulent effect of protrusion disturbance and opening flow; on the other hand, the region between two adjacent annular protrusions 41 is a location where the fluid turbulence is more intense. Placing the opening 33 between the two annular protrusions 41 can make full use of the turbulent characteristics of this region and maximize the effect of flow across the flow channel 50.

[0065] In some embodiments, please refer to Figure 4 Along the axial direction of the shaft core 20, the opening 33 is located at the midpoint of two adjacent annular protrusions 41.

[0066] Please see Figure 5 and Figure 6 In some embodiments, the edge of the opening 33 is provided with a deflection portion 34, which is deflected relative to the side of the partition 30 facing the plate surface. The deflection direction of the deflection portion 34 is the same as or opposite to the spiral direction of the partition 30, so as to further enhance the effect of guiding and disturbing the fluid.

[0067] As an example, such as Figure 5 As shown, when the deflection direction of the deflection part 34 is the same as the spiral direction of the partition 30, for example, when the partition 30 is right-handed and the deflection part 34 deflects to the right beyond the surface of the partition 30, the fluid flowing toward the deflection part 34 will be blocked to the right by the deflection part 34 so as to collide with the fluid that directly passes through the opening 33, thereby increasing turbulence.

[0068] As another example, such as Figure 6 As shown, when the deflection direction of the deflection part 34 is opposite to the spiral direction of the partition 30, for example, when the partition 30 is right-handed, the deflection part 34 deflects to the left beyond the surface of the partition 30. This can guide more fluid in one flow channel 50b to the adjacent flow channel 50a. The flow direction of this part of the fluid passing through the opening 33 is opposite to the direction of the mainstream fluid in the merged flow channel. For example, the mainstream fluid flows right-handed, and the small stream of fluid passing through flows to the left. This further aggravates the turbulence and flow across the flow channel 50.

[0069] Furthermore, in some embodiments, the deflection directions of multiple deflection portions 34 on the same partition 30 may be the same or different, or the deflection portions 34 at different axial positions may adopt different deflection directions, so as to form turbulence effects with different characteristics in different sections of the heating tube 100, thereby adapting to the heating requirements of different sections within the heating tube 100.

[0070] In some instances, the deflector 34 is positioned on the upstream side of the opening 33, near the direction of fluid flow.

[0071] Please see Figure 7 In some embodiments, the shaft core 20 has a constant diameter structure, which makes the processing technology simpler and the production cost lower.

[0072] Please see Figure 8 In other embodiments, the shaft core 20 is a non-uniform diameter structure, that is, along the axial direction of the shaft core 20, the shaft core 20 is provided with at least one drop step 22, the diameter of the shaft core 20 changes abruptly at the drop step 22, and the flow cross section of the flow channel 50 also changes accordingly. When the fluid flows through the drop step 22, it will undergo violent expansion or contraction due to the abrupt change in the flow cross section, thereby generating additional turbulence effect in the flow channel 50, further promoting heat exchange between the fluid and the inner wall of the outer casing 10.

[0073] As an example, a drop step 22 is provided at the downstream edge of the protrusion 40 along the flow direction of the fluid, which increases the radial space at the downstream edge of the protrusion 40. After the fluid flows through the protrusion 40, it has a leaping and tumbling posture. At the drop step 22, the fluid has a deceleration effect, and some of the fluid forms a vortex at the drop step 22, which can significantly improve the disturbance effect on the fluid.

[0074] Furthermore, along the direction of fluid flow, the diameter of the core 20 can gradually increase, making the bottom surface of the drop step 22 a sloping structure. On the one hand, the sloping structure guides the fluid flow, preparing it for the fluid to flow to the next protrusion 40. On the other hand, the sloping structure guides the fluid toward the inner wall of the outer shell, allowing the turbulent fluid to approach the outer shell to obtain heat and ensure its heating effect. Moreover, the gradually increasing diameter of the sloping structure can gradually reduce the space between the drop step 22 and the inner wall of the outer shell 10, thus compressing the fluid and increasing its flow velocity.

[0075] In some embodiments, the radial depth of the drop step 22 can be from 0.5 mm to 1.5 mm. Preferably, the radial depth of the drop step 22 can be from 0.8 mm to 1.2 mm. Further, the radial depth of the drop step 22 can be 1 mm. In some embodiments, the number of drop steps 22 can be one or more, and multiple drop steps 22 can be continuously arranged along the axial direction of the shaft core 20 to form a stepped shaft core 20 structure.

[0076] Please see Figure 1 and Figure 2This application also provides a heating device 200, which includes at least one bent tube 201 and at least two heating tubes 100 in any of the foregoing embodiments. The bent tube 201 is connected between the two heating tubes 100. The heating tube 100 at one end of the heating device 200 is provided with an inlet 202 for fluid to enter, and the heating tube 100 at the other end of the heating device 200 is provided with an outlet 203 for fluid to flow out.

[0077] This application connects at least two heating tubes 100 in series via a bent tube 201, enabling the arrangement of a longer effective heating flow channel within a limited space, increasing the overall heating stroke of the fluid, and enhancing the total heating capacity of the heating device 200. At the same time, the connection via the bent tube 201 allows the heating device 200 to take on a U-shaped, S-shaped, or other similar form, facilitating its integration into equipment with strict space requirements, such as automotive thermal management multi-function compressors, thereby improving the overall integration and space utilization of the device.

[0078] Furthermore, compared to the solution of using a single heating tube 100 to achieve the same heating capacity, using multiple heating tubes 100 in series can reduce the total rotation angle of the spiral section of each heating tube 100, thereby effectively reducing the overall flow resistance and avoiding the problem of needing to match a high-lift water pump due to excessive flow resistance of a single heating tube 100.

[0079] In some embodiments, the helical directions of the baffles 30 within at least two heating tubes 100 are the same or opposite. When the helical directions of the baffles 30 within at least two heating tubes 100 are opposite, the fluid forms a helical flow in one direction after flowing through the upstream heating tube 100, and needs to be converted to a helical flow in the opposite direction after entering the downstream heating tube 100. This generates severe turbulence in the inlet region of the curved tube 201 and the downstream heating tube 100, further enhancing the turbulence effect and improving the overall heating efficiency.

[0080] Specifically, the spiral direction of the inner baffle 30 of the two heating tubes 100 can be a combination of left-handed and right-handed spirals, thereby forming a distinct turbulent boundary region before and after the curved tube 201.

[0081] Furthermore, the number of bent tubes 201 and heating tubes 100 in the heating device 200 can be flexibly adjusted according to the actual spatial layout and heating power requirements. For example, a U-shaped layout with two heating tubes 100 and one bent tube 201 can be adopted, an S-shaped layout with three heating tubes 100 and two bent tubes 201 can be adopted, or a multi-segment folding layout with more heating tubes 100 and bent tubes 201 alternately connected in series can be adopted. The specific form of the heating device 200 is not limited in the embodiments of this application.

[0082] This application also provides an all-in-one automotive thermal management compressor, including the heating device 200 from the aforementioned embodiments. Integrating the heating device 200 into the all-in-one automotive thermal management compressor enables the compressor to simultaneously perform multiple functions such as cooling and heating, achieving a high degree of integration of the vehicle's thermal management system, reducing the space and number of pipelines occupied by the vehicle's thermal management system, reducing vehicle energy consumption, and improving system reliability. Furthermore, since the heating device 200 of this application embodiment has advantages such as good turbulence effect, high heating efficiency, controllable flow resistance, and high reliability, integrating it into the compressor can significantly improve the overall performance of the compressor, meeting the increasingly higher performance requirements of new energy vehicles for their thermal management systems.

[0083] The above description is merely an embodiment of this application and does not limit the patent scope of this application. Any equivalent structural or procedural transformations made using the content of this application's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this application.

Claims

1. A heating tube, characterized by, include: shell; The shaft is disposed within the housing; A partition is disposed on the surface of the shaft core, and the partition divides the space between the shaft core and the outer shell to form a plurality of flow channels; A protrusion is provided on the surface of the shaft core and located within the flow channel.

2. The heating tube according to claim 1, characterized in that, The partition is spiral-shaped and extends axially along the shaft.

3. The heating tube according to claim 2, characterized in that, The number of partitions is multiple, and the partitions are integral helical structures that extend continuously along the axial direction of the shaft core; and / or, the partitions include multiple helical segments arranged at intervals along the axial direction of the shaft core.

4. The heating tube according to claim 3, characterized in that, Along the flow direction of the fluid, the starting end of the downstream spiral segment is correspondingly located between the flow channels formed by the two adjacent upstream spiral segments.

5. The heating tube according to claim 2, characterized in that, The total rotation angle of the partition along the circumference of the axis is less than or equal to 180°.

6. The heating tube according to claim 5, characterized in that, The total rotation angle is 70° to 110°.

7. The heating tube according to claim 2, characterized in that, The upstream end of the partition has a radially increasing bevel, which connects the surface of the shaft core and the edge of the partition that is radially away from the shaft core.

8. The heating tube according to claim 1, characterized in that, The partition has a gap between its radially away edge from the shaft and the inner wall of the housing, the gap being 0 mm to 1 mm; And / or, Along the radial direction of the shaft, the radial distance between the surface of the shaft and the inner wall of the housing is 2.5 mm to 5 mm.

9. The heating tube according to claim 1, characterized in that, The partition has an opening that connects to the flow channels on both sides of the partition.

10. The heating tube according to claim 9, characterized in that, The opening includes a notch or groove disposed on the edge of the partition, and / or the opening includes a closed through hole disposed on the plate body of the partition.

11. The heating tube according to claim 9, characterized in that, The protrusion includes a plurality of circumferentially extending annular protrusions, which are spaced apart along the axial direction of the shaft core, and the opening is located axially between two adjacent annular protrusions.

12. The heating tube according to claim 9 or 11, characterized in that, The edge of the opening is provided with a deflection portion, which is deflected relative to the side of the partition plate facing the plate surface. The deflection direction of the deflection portion is the same as or opposite to the spiral direction of the partition plate.

13. The heating tube according to claim 1, characterized in that, The shaft core has a constant diameter structure; or, the shaft core has a non-constant diameter structure, and along the axial direction of the shaft core, the shaft core is provided with at least one step with a drop.

14. The heating tube according to claim 1, characterized in that, The outer casing is an integral tubular structure; and / or, a heating film assembly is provided on the outer wall of the outer casing.

15. A heating device, characterized in that, The heating device includes at least one curved tube and at least two heating tubes as described in any one of claims 1 to 14, the curved tube being connected between the two heating tubes, the heating tube at one end of the heating device having an inlet for fluid to enter, and the heating tube at the other end of the heating device having an outlet for fluid to flow out.

16. The heating device according to claim 15, characterized in that, The helical directions of the baffles within at least two of the heating tubes are the same or opposite.

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