A duct, thermal management system and vehicle

Abstract

The embodiment of the present application relates to the technical field of heat management, and discloses a flow guide pipe, a heat management system and a vehicle, which comprise a pipe body and a flow disturbing piece, the pipe body is provided with a through cavity and a liquid inlet, the liquid inlet is communicated with the through cavity, the flow disturbing piece is accommodated in the through cavity, the flow disturbing piece comprises a main body part and at least three flow disturbing pieces, along the axial direction of the main body part, the at least three flow disturbing pieces are spirally and staggered around the outer side wall of the main body part, the at least three flow disturbing pieces are arranged at intervals and have a flow guide channel between any two adjacent flow disturbing pieces, and the flow guide channel is used for guiding the flow of liquid. Through the above manner, the fluid entering the through cavity through the liquid inlet flows along the spiral flow guide channel, the flow path and flow time of the liquid in the through cavity are prolonged, so that when the flow guide pipe is applied to the heat management system, the liquid in the flow guide pipe can continuously change the speed and direction of the fluid, generate secondary flow and turbulent flow, effectively destroy the laminar bottom layer, and improve the heat exchange capacity of the flow guide pipe.

Description

Technical Field

[0001] The present invention relates to the field of thermal management technology, and in particular to a flow guide pipe, a thermal management system, and a vehicle. Background Technology

[0002] As a key component in the thermal management system of new energy vehicles, the heating tube includes a tube body, an inner tube sleeved inside the tube body, a heating film attached to the outer wall of the tube body, and a flow-dispersing element disposed on the outer wall of the inner tube. Fluid flows between the tube body and the inner tube. When energized, the heating film can generate heat and transfer the heat to the fluid inside the tube body. The flow-dispersing element is used to disrupt the laminar flow of the fluid inside the tube body, thereby facilitating the even transfer of heat from the heating film to the fluid.

[0003] In the process of developing this invention, the inventors discovered that currently, only one or two flow-disrupting elements are typically installed inside the heating tube. Although a spiral flow-guiding channel can be formed between adjacent flow-disrupting elements, the insufficient number results in inadequate radial disturbance capability of the fluid. This significantly limits the mixing degree between the cold fluid in the central region and the hot fluid near the inner tube wall, leading to obvious temperature stratification in the flow channel cross-section, limiting the overall heat exchange efficiency, and easily causing local overheating, thus affecting the safety and power density improvement of the heater. Summary of the Invention

[0004] This invention provides a flow guide pipe, a thermal management system, and a vehicle. The main technical problem it solves is that the existing flow guide pipes have a limited number of flow disturbance components, which are insufficient in their ability to radially disturb the fluid. This limits the mixing degree between the cold fluid in the central region and the hot fluid near the inner pipe wall, resulting in obvious temperature stratification in the flow channel cross-section, limiting the overall heat exchange efficiency, and easily causing local overheating, which affects the safety of the heater and the improvement of power density.

[0005] To solve the above-mentioned technical problems, the present invention provides a flow guide tube, comprising: a tube body and a flow disruptor; the tube body is provided with a cavity and a liquid inlet, the liquid inlet being connected to the cavity; the flow disruptor is housed in the cavity, the flow disruptor comprising a main body and at least three flow disruptors; along the axial direction of the main body, the three flow disruptors are spirally interlaced around the outer wall of the main body, the three flow disruptors are spaced apart and a flow guide channel is provided between any two adjacent flow disruptors, the flow guide channel being used to guide the flow of liquid.

[0006] In some embodiments, the pitch of each of the baffles is greater than or equal to 20 mm.

[0007] In some embodiments, the ratio of the pitch of each of the baffles to the diameter of the main body is greater than or equal to 3.

[0008] In some embodiments, a gap is provided between the outer wall of the spoiler and the inner wall of the cavity, the gap being 0 mm to 1 mm.

[0009] In some embodiments, the distance between the outer wall of the main body and the inner wall of the cavity is less than or equal to 5 mm.

[0010] In some embodiments, the outer surface of the main body is provided with a protrusion, which is located within the flow channel.

[0011] In some embodiments, the baffle is provided with a clearance hole, and two adjacent flow channels are connected through the clearance hole.

[0012] In some embodiments, the spoiler includes a plurality of spoiler segments, which are arranged sequentially at intervals along the rotation direction of the spoiler.

[0013] In some embodiments, the included angle between any two adjacent spoilers is equal along the circumference of the main body.

[0014] To solve the above-mentioned technical problems, another technical solution adopted by the present invention is to provide a thermal management system, including a compressor and the above-mentioned guide pipe, wherein the compressor is connected to the liquid outlet of the guide pipe.

[0015] To solve the above-mentioned technical problems, another technical solution adopted by the present invention is to provide a means of transportation, which includes a vehicle body and the above-mentioned thermal management system, wherein the thermal management system is disposed in the vehicle body.

[0016] The beneficial effects of this invention are as follows: Unlike existing technologies, this invention provides a flow guide pipe comprising a pipe body and a flow disruptor. The pipe body has a cavity and an inlet, the inlet communicating with the cavity. The flow disruptor is housed within the cavity and includes a main body and at least three flow disruptors. Along the axial direction of the main body, the three flow disruptors are spirally arranged around the outer wall of the main body. The three flow disruptors are spaced apart, and a flow guide channel is formed between any two adjacent flow disruptors, the flow guide channel being used to guide the flow of liquid. Through this structure, this invention can effectively disrupt the laminar flow phenomenon of the fluid within the flow guide pipe by relying on the arrangement of at least three flow disruptors. Furthermore, the flow guide channel formed by the spirally arranged flow disruptors forces the fluid to continuously change its velocity and direction, generating secondary flow and turbulence, effectively disrupting the laminar sublayer and improving the heat exchange capacity of the flow guide pipe. Attached Figure Description

[0017] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the embodiments of this application will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the exploded structure of a flow guide tube provided in an embodiment of the present invention; Figure 2 This is a cross-sectional schematic diagram of a flow guide provided in an embodiment of the present invention; Figure 3 This is another enlarged cross-sectional view of a guide tube provided in an embodiment of the present invention; Figure 4 This is a schematic diagram of the structure of another flow guide tube with a flow disturbance element provided in an embodiment of the present invention; Figure 5 This is a schematic diagram of the structure of a flow-disrupting component of another flow guide provided in an embodiment of the present invention; Figure 6 This is a schematic diagram of the structure of a flow-disrupting element in another type of flow guide provided in an embodiment of the present invention; Figure 7 yes Figure 1 A magnified view of part A in the middle; Figure 8 This is a schematic diagram of the structure provided in an embodiment of the present invention, in which two guide tubes are connected by a 180° bend. Figure 9 This is a schematic diagram of the temperature parameter simulation results for a flow guide tube with a pitch of 35 mm provided in an embodiment of the present invention; Figure 10 This is a schematic diagram of the temperature parameter simulation results for a flow guide tube with a pitch of 40 mm provided in an embodiment of the present invention; Figure 11 This is a schematic diagram of the temperature parameter simulation results for a flow guide tube with a gap of 0 mm between the outer wall of the flow deflector and the inner wall of the cavity, according to an embodiment of the present invention. Figure 12 This is a schematic diagram of the temperature parameter simulation results for a flow guide tube with a gap of 0.5 mm between the outer wall of the flow deflector and the inner wall of the cavity, according to an embodiment of the present invention.

[0019] Icon labels: 100. Drainage tube; 1. Pipe body; 11. Through cavity; 12. Liquid inlet; 13. Liquid outlet; 1a. Port section; 1b. Main body section; 2. Spoiler; 21. Main body; 211. Protrusion; 22. Spoiler vane; 221. Clearance hole; 22a. Spoiler section; 222. First sidewall; 223. Second sidewall; 224. Inclined surface; 3. Flow diversion channel; 4. Heating layer; 5. Filter screen; 6. Detection probe. Detailed Implementation

[0020] To facilitate understanding of the present invention, 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 being "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 being "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 "vertical," "horizontal," "left," "right," and similar expressions used in this specification are for illustrative purposes only.

[0021] 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 invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0022] This application provides a flow guide tube 100; please refer to [link / reference]. Figure 1The guide pipe 100 includes a pipe body 1 and a flow-turbulent element 2. The pipe body 1 is provided with a through cavity 11 and a liquid inlet 12. The liquid inlet 12 is connected to the through cavity 11 and is used to connect with an external pipeline (such as a pipeline connected to the evaporator in the thermal management system) so that external fluid can enter the through cavity 11 through the liquid inlet 12. Furthermore, the pipe body 1 is also provided with a liquid outlet 13 along the fluid flow direction. The liquid outlet 13 is connected to the through cavity 11 and is located downstream of the liquid inlet 12. After the fluid flows in the through cavity 11 and is turbulent, it flows out through the liquid outlet 13 and then flows to the next level equipment (such as a compressor). The flow-deflecting element 2 is housed in the cavity 11. The flow-deflecting element 2 includes a main body 21 and at least three flow-deflecting vanes 22. Along the axial direction of the main body 21, the three flow-deflecting vanes 22 are spirally interlaced around the outer wall of the main body 21. The three flow-deflecting vanes 22 are spaced apart, and a flow-guiding channel 3 is provided between any two adjacent flow-deflecting vanes 22. The flow-guiding channel 3 is used to guide the flow of liquid. Through this structure, the fluid entering the cavity 11 from the inlet 12 flows spirally along the corresponding flow-guiding channel 3, thus spiraling forward around the outer wall of the main body 21. Compared to straight-line flow, the flow path and flow time of the fluid are extended, which is beneficial for continuously changing velocity and direction, generating secondary flow and turbulence, effectively disrupting the laminar sublayer, and improving the heat exchange capacity of the guide pipe 100.

[0023] The direction of rotation of the baffle 22 can be left-handed or right-handed. This application does not limit the specific direction of rotation of the baffle 22, and the direction of rotation of each baffle 22 in the same guide tube 100 is the same. The baffle 22 and the main body 21 can be integrally injection molded or integrally extruded, or they can be separately fixed to the outer wall of the main body 21 by welding, bonding or other methods.

[0024] It is understandable that the connection (or limiting) methods between the baffle 2 and the tube body 1 include, but are not limited to, interference fit, snap-fit, welding, bonding, and spacing between the baffle 2 and the tube body 1 by means of the bayonet located at both ends of the tube body 1. These will not be listed here.

[0025] It should be noted that "at least three" means that the number of baffles 22 can be three, four, five, or more. The specific number of baffles 22 can be selected and set according to factors such as the diameter of the pipe body 1 and the desired baffle effect. For example, in this embodiment, the number of baffles 22 is three.

[0026] The pitch P directly determines the helix angle. The smaller the pitch P, the larger the helix angle, resulting in more rotations of the fluid within the same axial distance and stronger centrifugal force. This enhanced centrifugal force induces a more intense radial pressure gradient, thereby generating a stronger secondary flow (such as Dean's vortex). The secondary flow continuously transports the fluid in the mainstream region to the vicinity of the wall and brings the fluid near the wall back to the mainstream, enhancing macroscopic mixing of the fluid, effectively thinning or even disrupting the laminar sublayer, and thus improving convective heat transfer capacity.

[0027] In some embodiments, please refer to Figure 2 Each baffle 22 has a pitch P greater than or equal to 20 mm. It can be understood that the pitch P of the baffle 22 refers to the distance the baffle 22 travels along the axial direction of the main body 21 during one revolution. A pitch P that is too small can easily lead to the guide channels 3 becoming too narrow and dense, increasing the flow resistance when the liquid flows through the guide channels 3; a pitch P that is too large may weaken the spiral turbulence effect when the liquid flows along the guide channels 3, resulting in a state close to straight flow. Therefore, setting the pitch P to be greater than or equal to 20 mm can ensure the turbulence effect while also considering the flow resistance. In this application, when the number of baffles 22 is three, the preferred pitch P is 35 mm.

[0028] It should be noted that the pitch P of each turbulence vane 22 is fixed along the axial direction of the main body 21 to ensure that the turbulence intensity of the flow guide channel 3 is consistent from the liquid inlet 12 to the liquid outlet 13, the flow field structure is stable, the heat transfer performance is uniform along the flow path, and the flow resistance is predictable.

[0029] In some embodiments, the ratio of the pitch P of each baffle 22 to the diameter D of the main body 21 is greater than or equal to 3. It should be noted that a larger ratio indicates a gentler helical angle of the baffle 22 relative to the axial direction of the main body 21, resulting in less flow resistance to the fluid flowing along the guide channel 3; a smaller ratio indicates a steeper helical angle of the baffle 22, resulting in a stronger disturbance effect on the fluid, but also a corresponding increase in flow resistance. By limiting this ratio to greater than or equal to 3, it is possible to ensure the turbulence effect while avoiding excessive flow resistance that could affect the overall flow efficiency of the fluid. In this application, the ratio of the pitch P of the baffle 22 to the diameter of the main body 21 is preferably 5.47.

[0030] In some embodiments, please refer to Figure 3There is a gap L1 between the outer wall of the spoiler 2 and the inner wall of the cavity 11, and the distance of the gap L1 is 0 mm to 1 mm. When the gap L1 is 0 mm, it indicates that the outer wall of the baffle 2 is in close contact with the inner wall of the cavity 11 (e.g., assembled by interference fit). In this case, the liquid can only flow along the guide channel 3 and cannot bypass the baffle 2 by passing directly through the gap L1 between the baffle 2 and the inner wall of the cavity 11. This ensures the guiding and baffle effect of the guide channel 3 on the liquid. However, the corresponding flow resistance will increase compared to the method with gap L1. When the gap L1 is greater than 0 mm and less than or equal to 1 mm, it facilitates the assembly between the baffle 2 and the pipe body 1, allowing for certain assembly tolerances. Furthermore, the smaller gap L1 range does not significantly affect the overall baffle effect of the liquid along the guide channel 3 and reduces the flow resistance. Moreover, when the gap L1 is greater than 0 mm, the fluid can promptly remove heat from the area after passing through, thus preventing localized dry burning of the guide pipe 100 when applied to a thermal management system. Preferably, the gap L1 ranges from 0 mm to 0.3 mm. For example, in this application, the gap L1 is 0 mm.

[0031] In some embodiments, please refer to Figure 3 The distance L2 between the outer wall of the main body 21 and the inner wall of the cavity 11 is less than or equal to 5 mm. This distance is the radial width of the guide channel 3. By limiting this distance to within 5 mm, sufficient flow velocity and disturbance intensity can be ensured when the fluid flows in the guide channel 3, allowing the fluid to form a thin liquid layer within the narrow annular guide channel 3. This greatly shortens the distance heat is transferred from the wall of the tube 1 to the center of the fluid, eliminating the low-temperature (or high-temperature) ineffective fluid zone far from the wall. For example, in this application, the distance between the outer wall of the main body 21 and the inner wall of the cavity 11 is 4.5 mm.

[0032] In some embodiments, please refer to Figure 4 The outer surface of the main body 21 is provided with a protrusion 211, which is located inside the flow channel 3. The protrusion 211 can cause secondary turbulence to the fluid along the flow channel 3, further disrupting the laminar flow state of the liquid. This promotes thorough mixing of the liquid during flow, so that when the flow pipe 100 is used in a thermal management system, the heat transferred to the flow pipe 100 can be carried more efficiently from the pipe wall through the fluid into the main flow and finally carried away by the fluid, thereby significantly improving the overall heat transfer coefficient.

[0033] Understandably, the shape of the protrusion 211 includes, but is not limited to, at least one of the following: convex hull, convex strip, and convex dot. The number of protrusions 211 can be one or more, and the multiple protrusions 211 can be arranged at intervals along the extension direction of the guide channel 3.

[0034] In some embodiments, please refer to Figure 5 The baffle 22 is provided with a clearance hole 221, through which two adjacent flow channels 3 are connected. The clearance hole 221 enables fluid exchange between two adjacent flow channels 3. The clearance hole 221 causes radial flow between adjacent flow channels 3, forcibly mixing fluids of different temperature layers and different channels. It can quickly flatten the temperature distribution on the pipe cross section, prevent local overheating of the pipe wall, and make the overall heat exchange more uniform and efficient. In addition, the clearance hole 221 can also balance the pressure in adjacent flow channels 3, avoiding the phenomenon of pressure concentration in local areas. In particular, when a pressure difference is generated in two adjacent flow channels 3, the fluid will form a jet when passing through the clearance hole 221, rushing into the main spiral flow of the adjacent channel at a near-vertical or large angle. This jet will form a strong shearing effect with the mainstream fluid, inducing multi-scale additional vortices (such as horseshoe vortices and hairpin vortices) downstream of the orifice. These vortex structures can directly impact the flow boundary layer and thermal boundary layer on the surface of the turbulence plate 22 and the main body 21, causing the boundary layer to separate and reattach periodically, effectively reducing local thermal resistance.

[0035] Understandably, the shape of the clearance hole 221 includes, but is not limited to, a circular hole, an oblong hole, or a strip-shaped hole. The number of clearance holes 221 can be one or more. Multiple clearance holes 221 can be distributed at intervals along the spiral extension direction of the baffle 22; or multiple clearance holes 221 can be arranged sequentially along the axial direction of the main body 21.

[0036] In some embodiments, please refer to Figure 6 The spoiler 22 includes multiple spoiler sections 22a, which are arranged at intervals along the spiral direction of the spoiler 22. That is, the spoiler 22 does not extend continuously along the entire spiral path, but is composed of multiple spoiler sections 22a arranged sequentially along the spiral extension direction, with a gap between adjacent spoiler sections 22a. This gap is similar to the aforementioned clearance hole 221, and also serves to connect adjacent flow channels 3, balance pressure, and extend the disturbance path.

[0037] It is understandable that the lengths of multiple spoiler sections 22a may be equal or unequal; the width of the gap between two adjacent spoiler sections 22a may be equal or unequal, and there is no restriction here.

[0038] In some embodiments, please refer to Figure 3 Along the circumference of the main body 21, the included angle between any two adjacent baffles 22 is equal. By making the included angle between adjacent baffles 22 equal, it can be ensured that the liquid is uniformly turbulent along the circumference within the cavity 11, avoiding the phenomenon of excessively large differences in the turbulence effect in local areas.

[0039] It should be noted that this spacing can also be understood as the distance between two adjacent spoilers 22 along the width of the guide channel 3. When the number of spoilers 22 is N and they are evenly distributed along the circumference of the main body 21, the spacing angle between any two adjacent spoilers 22 is 360° / N. For example, in this embodiment, the number of spoilers 22 is three, and the spacing angle between any two adjacent spoilers 22 is 120°.

[0040] In other embodiments, the angle between any two adjacent baffles 22 may not be exactly equal, so that when there are three baffles 22 in the guide tube 100, there can be guide channels 3 with different widths, and the spacing between adjacent baffles 22 can be adjusted according to the actual required baffle effect.

[0041] In some embodiments, along the axial direction of the main body 21, the end of the baffle 22 facing the inlet 12 is provided with a chamfer. The chamfer is used to reduce the body resistance and eddy current loss at the inlet, reduce the overall pressure drop, and also reduce large-scale eddies and pressure fluctuations at the inlet, which helps to reduce the mid-to-high frequency noise caused by fluid excitation and the resulting vibration of the tube 1.

[0042] In some embodiments, please refer to Figure 7 The baffle 22 has adjacent first sidewalls 222 and second sidewalls 223. An inclined surface 224 is provided at the connection position of the first sidewalls 222 and the second sidewalls 223. The inclined surface 224 is used to guide fluid flow, reduce fluid flow resistance, and reduce pressure loss during fluid flow.

[0043] In some embodiments, please refer to Figure 1 The flow guide 100 includes a heating layer 4, which is attached to the outer surface of the tube body 1. The heating layer 4 is used to generate heat when energized and transfer it to the fluid inside the tube body 1 through the tube body 1, so that the flow guide 100 can act as a heater when applied to a thermal management system.

[0044] In some embodiments, please refer to Figure 1 The tube body 1 includes a port segment 1a and a main body segment 1b, both of which are tubular. The end of the port segment 1a furthest from the main body segment 1b defines the aforementioned liquid inlet 12. The port segment 1a is fixed to the flow-dispersing element 2 and is connected to the main body segment 1b. It is understood that the connection between the port segment 1a and the main body segment 1b can be, but is not limited to, snap-fit, screw-fit, or welding. When there is a gap L1 between the outer wall of the flow-dispersing element 22 and the inner wall of the cavity 11, the flow-dispersing element 2, when fixed to the port segment 1a, is housed in a cantilever-like shape inside the main body segment 1b, thereby forming the required gap L1 between the outer wall of the flow-dispersing element 2 and the inner wall of the cavity 11.

[0045] In some embodiments, please refer to Figure 1 A filter screen 5 is provided at the liquid inlet 12. The filter screen 5 is used to intercept solid particles or impurities carried in the fluid entering the passage cavity 11, preventing them from clogging the guide channel 3, scratching the surface of the baffle plate 22, or entering downstream equipment (such as the compressor), thereby protecting the reliability and service life of the guide pipe 100 and the entire thermal management system.

[0046] It should be noted that multiple guide pipes 100 can be connected in series to extend the turbulence and heating effects on the fluid. The series connection method can be flexibly selected according to actual pipeline layout requirements. For example, adjacent guide pipes 100 can be connected by straight pipe sections to maintain overall coaxial extension, or connected by bends to adapt to installation scenarios with limited space or requiring detours. If necessary, a combination of straight and bend pipes can be used to construct a series-parallel array. For example, in some embodiments, please refer to... Figure 8 The two guide pipes are arranged side by side in the same direction through a 180° bend.

[0047] In some embodiments, please refer to Figure 1 A detection probe 6 is provided at the inlet 12. The detection probe 6 is used to detect at least one of the following: temperature, flow rate, pressure, and fluid seal of the fluid entering through the inlet 12.

[0048] For easier understanding, please refer to Figures 8 to 10 This application also provides two simulation experiment embodiments of two of the above-mentioned guide pipes 100 connected in series by elbows. In each embodiment, the guide pipe 100 includes a heating layer 4, the pipe body 1 is made of stainless steel, the outer diameter of the pipe body 1 is 23.8 mm, the wall thickness of the pipe body 1 is 1 mm, the spacing between the outer wall of the main body 21 and the inner wall of the cavity 11 is 4.5 mm, the number of baffles 22 is three, and the included angle between any two adjacent baffles 22 along the circumference of the main body 21 is equal.

[0049] The only difference between the following embodiments is that: Embodiments 1-1 and 1-2 only adjust the pitch P of the baffle 22; the performance test results of the guide tube 100 of each embodiment when applied in the thermal management system are shown in Table 1 below.

[0050] Table 1

[0051] The simulation results of the temperature parameters for the pitch P of the spoiler 2 with 35 mm and 40 mm are as follows: Figure 9 and Figure 10As shown in Table 1 above, under the same operating conditions, the flow guide tube 100 with a pitch of 35 mm has a stronger heat exchange capacity, but also a greater flow resistance; increasing the pitch P requires sacrificing some heat exchange performance in exchange for a lower pressure drop.

[0052] For further details, please refer to Figure 8 , Figure 11 and Figure 12 The paper also provides two simulation experimental embodiments of two of the above-mentioned guide pipes 100 connected in series by elbows. In each embodiment, the guide pipe 100 includes a heating layer 4, the pipe body 1 is made of stainless steel, the outer diameter of the pipe body 1 is 23.8 mm, the wall thickness of the pipe body 1 is 1 mm, the spacing between the outer wall of the main body 21 and the inner wall of the cavity 11 is 4.5 mm, the pitch P of the baffle 22 is 35 mm, the number of baffles 22 is three, and the included angle between any two adjacent baffles 22 is equal along the circumference of the main body 21.

[0053] The only difference between the following embodiments is that: Embodiments 2-1 and 2-2 only adjust the gap L1 between the outer wall of the turbulence-disrupting element 2 and the inner wall of the cavity 11; the performance test results of the guide tube 100 of each embodiment when applied in the thermal management system are shown in Table 2 below.

[0054] Table 2

[0055] The simulation results of temperature parameters for the spacing distances of 0 mm and 0.5 mm between the outer wall of the baffle 2 and the inner wall of the cavity 11 are as follows: Figure 11 and Figure 12 As shown in Table 2 above, under the same operating conditions, the heat exchange capacity of the guide tube 100 with zero gap L1 (0mm) is stronger, but the flow resistance is also slightly larger; the presence of gap L1 (0.5mm) will lead to a decrease in heat exchange performance, accompanied by a slight decrease in pressure drop.

[0056] As shown in Table 2, while the gap L1 provides a low-resistance bypass for the fluid, it weakens the heat exchange capacity of the guide tube 100. Specifically, as the gap L1 increases from 0 to 0.5 mm, the highest temperature of the heating layer 4 rises from 249.09℃ to 268.29℃, an increase of 19.2℃; while the pressure difference decreases from 7.46 kPa to 6.90 kPa, a reduction of only 0.56 kPa (a decrease of 7.5%). The gains from the resistance are far outweighed by the heat exchange losses. Therefore, the preferred gap L1 in this application is 0 mm.

[0057] The flow guide 100 provided in this application, through the arrangement of at least three baffles 22, fully disturbs the laminar flow phenomenon of the fluid in the flow guide 100, and the flow guide channel 3 formed by the spirally surrounding baffles 22 can force the fluid to continuously change its speed and direction, generate secondary flow and turbulence, effectively destroy the laminar sublayer, and improve the heat exchange capacity of the flow guide 100.

[0058] This application also provides an embodiment of a thermal management system, including a compressor and the aforementioned guide pipe 100. The compressor is connected to the liquid outlet of the guide pipe 100. Specifically, the guide pipe 100 is located upstream of the compressor, and the liquid inlet 12 of the guide pipe 100 is connected to a pipeline upstream of the compressor. Fluid that has been turbulently atomized or vaporized by the guide pipe 100 flows to the compressor, thereby reducing the risk of liquid slugging caused by the compressor drawing in liquid fluid and improving the reliability of compressor operation. Optionally, the thermal management system also includes components such as a condenser, an evaporator, and a throttling device. The guide pipe 100 can be located on the pipeline between the evaporator and the compressor, or it can be located at any other location in the thermal management system where fluid turbulence treatment is required. For the specific structure and function of the guide pipe 100, please refer to the above embodiments; further examples will not be provided here.

[0059] This application also provides an embodiment of a vehicle, which includes a vehicle body and the aforementioned thermal management system, the thermal management system being disposed in the vehicle body. The thermal management system is configured to regulate the temperature of objects such as batteries, motors, or passenger compartments within the vehicle body. It is understood that the vehicle includes, but is not limited to, pure electric vehicles, hybrid electric vehicles, or gasoline-powered vehicles.

[0060] It should be noted that while the preferred embodiments of the present invention are given in the specification and accompanying drawings, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are not intended to impose additional limitations on the content of the present invention; their purpose is to provide a more thorough and comprehensive understanding of the disclosure of the present invention. Furthermore, the above-described technical features can be combined with each other to form various embodiments not listed above, all of which are considered to be within the scope of the present invention specification. Moreover, those skilled in the art can make improvements or modifications based on the above description, and all such improvements and modifications should fall within the protection scope of the appended claims.

Claims

1. A flow guide tube, characterized in that, include: The tube body is provided with a through cavity and a liquid inlet, wherein the liquid inlet is connected to the through cavity; A flow-dispersing element is housed in the cavity. The flow-dispersing element includes a main body and at least three flow-dispersing vanes. Along the axial direction of the main body, the three flow-dispersing vanes are spirally interlaced around the outer wall of the main body. The three flow-dispersing vanes are spaced apart, and a flow-guiding channel is provided between any two adjacent flow-dispersing vanes. The flow-guiding channel is used to guide the flow of liquid.

2. The guide tube according to claim 1, characterized in that, The pitch of each of the aforementioned baffles is greater than or equal to 20 mm.

3. The guide tube according to claim 1, characterized in that, The ratio of the pitch of each of the aforementioned baffles to the diameter of the main body is greater than or equal to 3.

4. The guide tube according to claim 1, characterized in that, There is a gap between the outer wall of the spoiler and the inner wall of the cavity, and the distance of the gap is 0 mm to 1 mm.

5. The guide tube according to claim 1, characterized in that, The distance between the outer wall of the main body and the inner wall of the cavity is less than or equal to 5 mm.

6. The guide tube according to claim 1, characterized in that, The outer surface of the main body is provided with a protrusion, which is located inside the flow channel.

7. The guide tube according to claim 1, characterized in that, The baffle is provided with a clearance hole, and two adjacent flow channels are connected through the clearance hole.

8. The guide tube according to claim 1, characterized in that, The spoiler includes multiple spoiler segments, which are arranged sequentially at intervals along the direction of rotation of the spoiler.

9. The guide tube according to claim 1, characterized in that, Along the circumference of the main body, the included angle between any two adjacent spoilers is equal.

10. A thermal management system, characterized in that, It includes a compressor and a flow guide pipe as described in claim 1, wherein the compressor is connected to the liquid outlet of the flow guide pipe.

11. A means of transportation, characterized in that, It includes a vehicle body and a thermal management system as described in claim 10, wherein the thermal management system is disposed on the vehicle body.

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