A cooling ring structure

Abstract

The utility model discloses a cooling pressure ring structure, include: pressure ring matrix, cooling unit has a plurality of first cooling part, and first cooling part is along radial or spiral shape and is arranged on the pressure ring matrix, first cooling part includes first end and second end, and first cooling part's first end is located the inner wall surface of pressure ring matrix, and first cooling part's second end is located the outer periphery of pressure ring matrix, and the size of first cooling part is linearly increased from first cooling part's first end to first cooling part's second end, the utility model discloses cooling pressure ring structure, sets up a plurality of first cooling part on the inner wall surface of pressure ring matrix, and the centrifugal force that first cooling part's first end receives is less than the centrifugal force that first cooling part's second end receives, and the size of each first cooling part is linearly increased from first cooling part's first end to first cooling part's second end, forms the stepped heat exchange path, to adapt the gradient change of centrifugal force, makes cooling medium can evenly cover high heat area to improve the cooling efficiency.

Description

Technical Field

[0001] This utility model relates to the field of rotor assembly technology, and in particular to a cooling pressure ring structure. Background Technology

[0002] In high-power-density motors such as those used in electric vehicles, high-speed compressors, and aircraft starter generators, the rotor typically uses clamping rings to axially secure the magnets, core laminations, or winding ends. With the rotor rotating at high speed and electromagnetic losses concentrated, the clamping ring-magnet-core interface becomes the primary heat source.

[0003] Currently, external cooling or opening channels inside the pressure ring is mainly used to cool the pressure ring. However, the cooling medium of external cooling cannot directly reach the core heat-generating area of ​​the rotor, resulting in low cooling efficiency. Furthermore, the layout of the channels mostly uses a single straight line or a single radial hole, which means that the cooling medium cannot cover the high-heat area, thus still resulting in local hot spots. Utility Model Content

[0004] The purpose of this invention is to provide a cooling pressure ring structure to solve the problem that the cooling medium can only cover part of the high-heat area, thereby improving cooling efficiency.

[0005] This utility model provides a cooling pressure ring structure, including: A compression ring substrate, wherein the compression ring substrate is annular in shape; A cooling unit having a plurality of first cooling sections spaced apart on the pressure ring base, wherein the first cooling sections are arranged radially or spirally on the pressure ring base; in: The first cooling section includes a first end and a second end. The first end of the first cooling section is disposed on the inner wall surface of the pressure ring base, and the second end of the first cooling section is disposed on the outer peripheral surface of the pressure ring base. The size of the first cooling section increases linearly from the first end of the first cooling section to the second end of the first cooling section.

[0006] In the cooling ring structure described above, preferably, the first cooling section includes at least two cooling holes that penetrate the wall of the ring base. The cooling holes form liquid inlets on the inner wall of the ring base and liquid outlets on the outer peripheral surface of the ring base. The diameter of the cooling holes increases linearly from the liquid inlet to the liquid outlet.

[0007] In the cooling ring structure described above, preferably, the diameter of the liquid inlet is ≤2mm and the diameter of the liquid outlet is ≤3mm.

[0008] In the cooling ring structure described above, preferably, the cooling holes are spirally arranged on the ring base, and the spiral angle of the cooling holes is 30-60°.

[0009] In the cooling ring structure described above, preferably, at least two of the cooling holes are staggered along the axial direction of the ring base.

[0010] In the cooling ring structure described above, preferably, the cooling unit further includes a plurality of second cooling sections, which are spaced apart on the inner wall surface of the ring base. The plurality of second cooling sections are arranged in a one-to-one correspondence with the plurality of first cooling sections, and each second cooling section is connected to the corresponding first cooling section.

[0011] In the cooling ring structure described above, preferably, the second cooling section includes a cooling groove formed by a recess in the inner wall of the ring base facing the outer peripheral surface of the ring base, and the cooling groove communicates with the first cooling section.

[0012] In the cooling ring structure described above, preferably, the spacing between adjacent first cooling portions is 3-8 mm along the circumferential direction of the ring base.

[0013] In the cooling ring structure described above, preferably, the cooling ring structure further includes reinforcing ribs, which are disposed circumferentially on the inner wall surface of the ring base.

[0014] In the cooling ring structure described above, preferably, the ring matrix is ​​made of titanium alloy or carbon fiber composite material.

[0015] Compared with the prior art, the cooling ring structure of this utility model has multiple radial or spiral first cooling sections on the inner wall of the ring base. The multiple first cooling sections form a cooling array in the circumferential direction of the ring base to improve the heat exchange effect. The centrifugal force on the first end of the first cooling section is less than that on the second end of the first cooling section. Under the action of centrifugal force, the cooling medium can be thrown from the first end of the first cooling section to the second end of the first cooling section. The size of each first cooling section increases linearly from the first end to the second end of the first cooling section to form a stepped heat exchange path to adapt to the gradient change of centrifugal force, so that the cooling medium can uniformly cover the high heat area, thereby improving the cooling efficiency. Attached Figure Description

[0016] Figure 1 This is a first-view perspective perspective view of the cooling ring structure provided in an embodiment of this utility model; Figure 2This is a second-view perspective perspective view of the cooling ring structure provided in an embodiment of this utility model; Figure 3 This is a side view of the cooling ring structure provided in an embodiment of the present invention; Figure 4 yes Figure 3 Cross-sectional view along the AA direction; Figure 5 yes Figure 3 Cross-sectional view along the BB direction.

[0017] Explanation of reference numerals in the attached figures: 10-Pressing ring matrix; 20-Cooling unit, 21-First cooling section, 211-Cooling hole, 212-Liquid inlet, 213-Liquid outlet, 22-Second cooling section, 221-Cooling tank; 30 - Reinforcing ribs; Z - The axis of the compression ring matrix. Detailed Implementation

[0018] The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0019] Reference Figure 1 and Figure 2 As shown, this utility model provides a cooling pressure ring structure, including a pressure ring base 10 and a cooling unit 20, wherein: The pressure ring base 10 is circular and can be fitted onto the motor shaft. The inner diameter of the pressure ring base 10 must match the motor shaft, and the outer circumferential surface of the pressure ring base 10 is in contact with the stator seal.

[0020] The cooling unit 20 has multiple first cooling sections 21, which are spaced apart on the pressure ring base 10. The first cooling sections 21 are arranged radially or spirally on the pressure ring base 10. After the pressure ring base 10 is fitted to the motor shaft, on the one hand, the multiple first cooling sections 21 contact the motor shaft, thereby allowing the first cooling sections 21 to directly contact the core heat-generating area to improve heat dissipation efficiency; on the other hand, the multiple first cooling sections 21 can uniformly cover the outer peripheral surface of the motor shaft, avoiding the situation where local hot spots cannot be cooled, further improving heat dissipation efficiency.

[0021] In the embodiments provided in this application, the first cooling section 21 includes a first end and a second end. The first end of the first cooling section 21 is disposed on the inner wall surface of the pressure ring base 10, and the second end of the first cooling section 21 is disposed on the outer peripheral surface of the pressure ring base 10. Compared with the second end of the first cooling section 21, the first end of the first cooling section 21 is closer to the motor shaft. Therefore, when the motor shaft rotates at high speed, the centrifugal force at the first end of the first cooling section 21 is less than the centrifugal force at the second end of the first cooling section 21. Under the action of centrifugal force, the cooling medium is "thrown" from the first end of the first cooling section 21 to the second end of the first cooling section 21. As the centrifugal force increases, the flow rate of the cooling medium "thrown" from the first end of the first cooling section 21 to the second end of the first cooling section 21 increases accordingly.

[0022] To ensure uniform flow of the cooling medium during the "throwing" process and thus guarantee the cooling effect, the size of the first cooling section 21 is designed to increase linearly from the first end to the second end. As the centrifugal force increases, the first cooling section 21 forms a stepped heat exchange path. The flow rate of the cooling medium through the first end of the first cooling section 21 is relatively small, which is adapted to the smaller size of the first end of the first cooling section 21. The flow rate of the cooling medium through the second end of the first cooling section 21 is relatively large, which is adapted to the larger size of the second end of the first cooling section 21. Thus, under the action of centrifugal force, the flow rate of the cooling medium through each section of the first cooling section 21 can remain uniform, ensuring the uniformity and stability of cooling for the motor shaft. In the embodiments provided in this application, reference is made to Figure 2 As shown, the first cooling section 21 includes at least two cooling holes 211. The cooling holes 211 penetrate the wall of the pressure ring base 10. The cooling holes 211 form liquid inlets 212 on the inner wall of the pressure ring base 10 and liquid outlets 213 on the outer peripheral surface of the pressure ring base 10. The diameter of the cooling holes 211 increases linearly from the liquid inlet 212 to the liquid outlet 213.

[0023] When the motor shaft rotates at high speed, refer to Figure 5 As shown, the cooling medium is "thrown" from the smaller inlet 212 to the larger outlet 213, where the centrifugal force gradually increases and the diameter of the orifice increases linearly. As a result, the cooling medium flows from the inlet 212 to the outlet 213 along a stepped path. The flow rate of the cooling medium is uniform during the flow process, thus achieving uniform cooling of the motor shaft.

[0024] Specifically, the diameter of the liquid inlet 212 is ≤2mm, and the diameter of the liquid outlet 213 is ≤3mm. The diameter range of the liquid inlet 212 and the liquid outlet 213 can ensure the structural strength of the cooling pressure ring structure while also ensuring a uniform cooling effect.

[0025] To further improve the cooling effect, in the embodiments provided in this application, the cooling holes 211 are spirally arranged on the pressure ring base 10, and the spiral angle of the cooling holes 211 is 30-60°. Compared with radial openings, within the same axial length range, the spiral holes can form a longer heat dissipation path, allowing the cooling medium to flow through the cooling holes 211 for a longer time, thereby achieving a better cooling effect.

[0026] Furthermore, if the spiral angle of the cooling hole 211 is too small, the cooling hole 211 will be close to a radial hole. When the cooling medium is subjected to centrifugal force, the axial force generated by the centrifugal force decomposition will be small, making it easy for the cooling medium to be blocked at the inlet 212. If the spiral angle of the cooling hole 211 is too large, the cooling hole 211 will be close to a circumferential hole. On the one hand, the cooling medium will be easy to be blocked at the outlet 213 and difficult to discharge. On the other hand, the cooling hole 211 with an excessively large spiral angle is more difficult to process.

[0027] Therefore, the spiral angle of the cooling hole 211 is set to 30-60°, which can ensure that the cooling medium can smoothly enter from the inlet 212 and exit from the outlet 213, and also facilitates processing.

[0028] In one feasible embodiment, at least two cooling holes 211 are staggered along the Z-axis of the pressure ring base, and the positions and angles of the two liquid outlets 213 on the outer peripheral surface of the pressure ring base 10 are different, so that the cooling medium can be discharged through the two liquid outlets 213 at different angles. The cooling medium discharged from the two liquid outlets 213 forms a wide-angle spray pattern, which can expand the spray range of the cooling medium and improve the heat dissipation efficiency.

[0029] Reference Figure 1 As shown, the cooling unit 20 also includes a plurality of second cooling sections 22, which are spaced apart on the inner wall surface of the pressure ring base 10. Each second cooling section 22 corresponds to one of the first cooling sections 21, and each second cooling section 22 communicates with its corresponding first cooling section 21. Because the second cooling sections 22 are located on the inner wall surface of the pressure ring base 10, they can directly contact the high-temperature areas, thereby directly dissipating heat from the high-temperature areas and improving heat dissipation efficiency.

[0030] In one feasible implementation, refer to Figure 2 and Figure 4As shown, the second cooling section 22 includes a cooling groove 221, which is formed by a recess in the inner wall of the pressure ring base 10 toward the outer peripheral surface of the pressure ring base 10. The cooling groove 221 communicates with the first cooling section 21. The cooling groove 221 forms a cooling channel inside the pressure ring base 10. When the cooling medium flows through the cooling groove 221, it directly dissipates heat to the high-temperature area, and then flows from the cooling groove 221 to the first cooling section 21, carrying away the heat. Under the combined action of the first cooling section 21 and the second cooling section 22, the heat dissipation effect is improved.

[0031] The number of first cooling sections 21 and second cooling sections 22 can be set according to the heat density of the part to be cooled. Since the spacing between adjacent first cooling sections 21 determines the number of first cooling sections 21, when cooling high-temperature areas (such as the contact area of ​​a bearing contactor) requires a larger flow rate of cooling medium, a smaller spacing can be selected to increase the number of first cooling sections 21; when cooling low-temperature areas requires a smaller flow rate of cooling medium, a larger spacing can be selected to set a relatively smaller number of first cooling sections 21. In the embodiment provided in this application, along the circumferential direction of the pressure ring base 10, the spacing between adjacent first cooling sections 21 is 3-8 mm. The spacing between adjacent first cooling sections 21 is the distance between adjacent cooling holes 211 located on the same circumference of the pressure ring base 10. The spacing range of 3-8 mm can meet the heat dissipation requirements and save processing costs. Since both the first cooling section 21 and the second cooling section 22 need to be formed on the pressure ring base 10, multiple cooling holes 211 and multiple cooling grooves 221 need to be formed by multiple processing on the pressure ring base 10. However, multiple processing will have a certain impact on the structural strength of the pressure ring base 10.

[0032] To ensure the structural strength of the compression ring matrix 10, refer to Figure 1 , Figure 2 and Figure 4 As shown, the cooling ring structure also includes reinforcing ribs 30, which are arranged circumferentially on the inner wall surface of the ring base 10. On the inner wall surface of the ring base 10, the solid portion between adjacent cooling grooves 221 forms the reinforcing ribs 30. The inner wall surface of the ring base 10 becomes thinner due to the opening of the cooling grooves 221. When the motor shaft rotates at high speed, the solid portion of the reinforcing ribs 30 and the solid portion of the grooves together form a continuous annular reinforcing band, thereby improving the overall rigidity of the ring base 10 and ensuring that the ring base 10 remains stable even under high-speed rotation.

[0033] To improve the structural strength of the cooling ring matrix 10 while ensuring the cooling efficiency of the cooling ring structure, in the embodiments provided in this application, the cooling ring matrix 10 is made of titanium alloy or carbon fiber composite material. Both titanium alloy and carbon fiber composite materials have the advantages of being lightweight, high-strength, having excellent heat resistance, and corrosion resistance. Using titanium alloy or carbon fiber composite materials to make the cooling ring matrix 10 is beneficial for improving the structural strength of the cooling ring structure and extending its service life.

[0034] The above description, based on the embodiments shown in the drawings, details the structure, features, and effects of this utility model. The above description is only a preferred embodiment of this utility model, but the scope of implementation of this utility model is not limited to what is shown in the drawings. Any changes made in accordance with the concept of this utility model, or modifications to equivalent embodiments, that do not exceed the spirit covered by the specification and drawings, shall be within the protection scope of this utility model.

Claims

1. A cooling ring structure, characterized in that, include: A compression ring substrate, wherein the compression ring substrate is annular; A cooling unit having a plurality of first cooling sections spaced apart on the pressure ring base, wherein the first cooling sections are arranged radially or spirally on the pressure ring base; in: The first cooling section includes a first end and a second end. The first end of the first cooling section is disposed on the inner wall surface of the pressure ring base, and the second end of the first cooling section is disposed on the outer peripheral surface of the pressure ring base. The size of the first cooling section increases linearly from the first end of the first cooling section to the second end of the first cooling section.

2. The cooling ring structure according to claim 1, characterized in that, The first cooling section includes at least two cooling holes that penetrate the wall of the pressure ring base. The cooling holes form liquid inlets on the inner wall of the pressure ring base and liquid outlets on the outer peripheral surface of the pressure ring base. The diameter of the cooling holes increases linearly from the liquid inlet to the liquid outlet.

3. The cooling ring structure according to claim 2, characterized in that, The diameter of the liquid inlet is ≤2mm, and the diameter of the liquid outlet is ≤3mm.

4. The cooling ring structure according to claim 2, characterized in that, The cooling holes are spirally arranged on the pressure ring base, and the spiral angle of the cooling holes is 30-60°.

5. The cooling ring structure according to claim 2, characterized in that, At least two of the cooling holes are staggered along the axial direction of the pressure ring base.

6. The cooling ring structure according to claim 1, characterized in that, The cooling unit further includes a plurality of second cooling sections, which are spaced apart on the inner wall surface of the pressure ring base. The plurality of second cooling sections are arranged in a one-to-one correspondence with the plurality of first cooling sections, and each second cooling section is connected to the corresponding first cooling section.

7. The cooling ring structure according to claim 6, characterized in that, The second cooling section includes a cooling groove, which is formed by a recess in the inner wall of the pressure ring base facing the outer peripheral surface of the pressure ring base, and the cooling groove is in communication with the first cooling section.

8. The cooling ring structure according to claim 1, characterized in that, Along the circumferential direction of the pressure ring base, the spacing between adjacent first cooling sections is 3-8 mm.

9. The cooling ring structure according to claim 1, characterized in that, The cooling ring structure also includes reinforcing ribs, which are disposed on the inner wall surface of the ring base along the circumference of the ring base.

10. The cooling ring structure according to claim 1, characterized in that, The pressure ring matrix is ​​made of titanium alloy or carbon fiber composite material.

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