High-speed compact nested shafting structure with clutch function

Abstract

The invention discloses a high-speed compact nested shafting structure with a clutch function, and relates to the technical field of mechanical transmission. The problems that an existing high-speed power transmission system is long in structure, low in space utilization rate, complex in supporting structure and poor in lubrication, and consequently stability is poor during high-speed operation are solved. A fifth supporting bearing is embedded in an input port of the clutch assembly, the end of the input gear ring hollow shaft is inserted into the middle of an inner ring of the fifth supporting bearing, one end of the input gear ring hollow shaft is sleeved with a sixth supporting bearing, and a fourth supporting bearing is embedded in an output port of the clutch assembly. One end of the transmission output shaft is inserted into the middle of an inner ring of the fourth supporting bearing and sleeved with the third supporting bearing, the other end of the transmission output shaft is sequentially sleeved with the first supporting bearing and the second supporting bearing in the axis direction, and a counter bore is machined in the center of the end face of the other end of the transmission output shaft in the axis direction. And a clutch oil distributing pipe is arranged in the counter bore. The invention is applicable to the field of machinery.

Description

Technical Field

[0001] This invention relates to the field of mechanical transmission technology, and specifically to a high-speed, compact, nested shaft system structure with a clutch function. Background Technology

[0002] In high-speed powertrain systems, integrating clutch functionality within a limited space, ensuring shaft support rigidity, and achieving reliable lubrication and cooling remains a persistent technical challenge. Traditional solutions typically treat the clutch as a separate component external to the shaft system, or implement clutch engagement through complex synchronizer structures. This leads to the following problems:

[0003] (1) Long structure and low space utilization: The external clutch increases the axial length of the transmission chain, making the entire transmission device less compact and difficult to meet the application scenarios with strict limitations on installation space.

[0004] (2) Complex support and poor high-speed stability: For nested dual-shaft systems, traditional support schemes often require a large number of bearings, which are scattered and affect the overall stiffness and critical speed of the shaft system, making it prone to vibration during high-speed operation.

[0005] (3) Difficulty in lubrication and oil supply: The oil supply of the clutch usually requires additional external oil pipes and rotary joints, which not only increases the complexity of the structure, but also poses a potential risk of leakage. Furthermore, the external oil pipes may cause dynamic balance problems under high-speed rotation.

[0006] (4) Low functional integration: Traditional shaft system design separates the functional modules such as power transmission, clutch, support, and lubrication, failing to achieve integrated integration, which limits the power density and reliability of the entire transmission system.

[0007] In summary, existing high-speed power transmission systems have a lengthy structure, low space utilization, complex support structure, and inadequate lubrication, resulting in poor stability during high-speed operation. Summary of the Invention

[0008] To address the problems of existing high-speed power transmission systems, such as lengthy structures, low space utilization, complex support structures, and inadequate lubrication leading to poor stability during high-speed operation, this invention proposes a high-speed compact nested shaft system structure with clutch function.

[0009] The present invention provides a high-speed compact nested shaft system structure with clutch function, which comprises a transmission output shaft 1, a clutch oil distribution pipe 2, a clutch assembly 3, an input gear ring hollow shaft 4, a first support bearing 5, a second support bearing 6, a third support bearing 7, a fourth support bearing 8, a fifth support bearing 9, and a sixth support bearing 10.

[0010] The input port of the clutch assembly 3 is fitted with a No. 5 support bearing 9, and the end of the input gear ring hollow shaft 4 is inserted into the middle of the inner ring of the No. 5 support bearing 9. A No. 6 support bearing 10 is fitted on one end of the input gear ring hollow shaft 4. The output port of the clutch assembly 3 is fitted with a No. 4 support bearing 8. One end of the transmission output shaft 1 is inserted into the middle of the inner ring of the No. 4 support bearing 8. A No. 3 support bearing 7 is fitted on one end of the transmission output shaft 1. A No. 1 support bearing 5 and a No. 2 support bearing 6 are fitted sequentially along the axial direction on the other end of the transmission output shaft 1. A countersunk hole is machined at the center of the end face of the other end of the transmission output shaft 1 along the axial direction. The clutch oil distribution pipe 2 is provided inside the countersunk hole.

[0011] Furthermore, the left end of the input gear ring hollow shaft 4 is machined with an internal spline;

[0012] Furthermore, the inner wall of the input port of the clutch assembly 3 is machined with external splines along the circumferential direction;

[0013] Furthermore, the internal spline at the left end of the input gear ring hollow shaft 4 is connected to the external spline at the input port of the clutch assembly 3.

[0014] Furthermore, the left end of the transmission output shaft 1 is machined with an external spline;

[0015] Furthermore, the friction plate seat in the clutch assembly 3 is connected to the external spline at the left end of the transmission output shaft 1 via an internal spline.

[0016] Furthermore, the No. 4 support bearing 8 and the No. 6 support bearing 10 are a combination of deep groove ball bearings and cylindrical roller bearings.

[0017] Furthermore, the No. 1 support bearing 5, the No. 2 support bearing 6, and the No. 3 support bearing 7 are four-point contact ball bearings or cylindrical roller bearings.

[0018] Furthermore, one end of the clutch oil distribution pipe 2 is connected to the main shaft oil supply channel; the outer surface of the other end of the clutch oil distribution pipe 2 is provided with radial oil holes, through which oil is sprayed into the working area of ​​the clutch assembly 3 to lubricate and cool the friction plates.

[0019] Furthermore, the outer surface of the input gear ring hollow shaft 4 is provided with an oil return hole along the circumferential direction;

[0020] Furthermore, during operation, power is introduced from the hollow shaft of the input gear ring, which is connected to the power input via a spline at the end of the input gear ring. The hollow shaft 4 of the input gear ring serves as the primary transmission shaft, supported on the housing by bearings 8 and 10. The output shaft 1 serves as the secondary transmission shaft, nested inside the hollow shaft 4 of the input gear ring, and supported on the housing by bearings 5, 6, and 7, thus achieving coaxial nesting and relatively independent rotation of the two shafts.

[0021] The clutch function is achieved through a splined interface. An internal spline is machined on the left end of the input gear ring hollow shaft 4. The clutch assembly 3 engages with this internal spline via an external spline. An external spline is machined on the left end of the transmission output shaft 1. The clutch friction plate seat 3 engages with this external spline via an internal spline. The friction plate assembly is mounted between the clutch hub and the clutch carrier. When the friction plate assembly is pressed together, power is transmitted from the input gear ring hollow shaft 4 to the transmission output shaft 1; when disengaged, the two shafts separate.

[0022] The bearing assembly employs a six-bearing arrangement. Support bearings 8 (number four) and 10 (number six) are located at the input end, typically using a combination of deep groove ball bearings and cylindrical roller bearings to withstand radial and axial forces. Support bearings 5 ​​(number one), 6 (number two), and 7 (number three) are located at the output end, using four-point contact ball bearings and cylindrical roller bearings to withstand the radial and axial forces of the helical gear meshing. Support bearing 9 (number five) is located at the end of the clutch assembly, providing auxiliary support in the middle of the hollow shaft of the input gear ring, distributing the weight of the output shaft system, increasing the rigidity of the entire output shaft system, and providing additional intermediate support. When the clutch is engaged, the inner and outer rings of support bearings 8 (number four) and 9 (number five) are in a relatively stationary, non-working state. The entire shaft system is supported by four bearings, preventing over-coupling and ensuring the stability and reliability of the overall shaft system under high-speed operation. Furthermore, these two bearings provide reliable support to the clutch assembly, ensuring smooth clutch operation.

[0023] The lubrication and oil supply system is integrated within the shaft. Pressurized oil is injected into the main shaft oil supply channel from the right end of the clutch oil distribution pipe 2, and then sprayed into the clutch working area through radial oil holes to lubricate and cool the friction plates. After use, the oil is thrown out through the return oil hole on the hollow shaft 4 of the input gear ring under centrifugal force, flowing back to the bottom of the housing to complete the cycle. This shaft system structure highly integrates transmission, clutch, support, and lubrication, achieving stable, compact, and efficient transmission and clutch functions under high-speed operating conditions.

[0024] Compared with the prior art, the present invention has the following advantages:

[0025] 1. This invention overcomes the shortcomings of the prior art by using a hollow shaft nested with a solid shaft design and integrating the clutch between the two shafts in the form of a built-in spline, which greatly shortens the axial dimension of the transmission chain, achieves extremely high power density, and thus improves the compactness of the structure.

[0026] 2. This invention overcomes the shortcomings of the prior art by adopting an optimized layout of six bearings and providing multiple supports at the input end, output end and middle, which greatly improves the bending stiffness and torsional stiffness of the entire shaft system (especially the nested structure), increases the critical speed of the shaft system, ensures the stability and reliability under high-speed operation, and also effectively improves the support rigidity.

[0027] 3. This invention overcomes the shortcomings of the prior art by using the central through hole of the clutch oil distribution pipe assembled inside the output shaft as the main oil supply channel to directly deliver pressurized oil to the clutch working chamber, eliminating the need for complex external oil pipes and rotary sealing joints. It has a simple structure, reliable sealing, high oil supply efficiency, and is beneficial to dynamic balance.

[0028] 4. This invention overcomes the shortcomings of existing technologies by dynamically connecting the input gear ring hollow shaft, clutch, and transmission output shaft through a spline connection, thus realizing the interface function for power on / off switching. This structure transmits large torque, engages smoothly, and responds quickly.

[0029] 5. This invention overcomes the shortcomings of the prior art. This shaft system structure perfectly integrates four major functions—power transmission, clutch operation, multi-point support, and internal lubrication—into a compact unit, simplifying the design of the external system and improving the reliability and service life of the overall transmission system. Attached Figure Description

[0030] Figure 1 This is a main sectional view of a high-speed compact nested shaft system structure with clutch function as described in this invention;

[0031] Figure 2 This is a transmission principle diagram of a high-speed, compact nested shaft system structure with clutch function as described in this invention. Detailed Implementation

[0032] Specific implementation method one: Combining Figure 1 and Figure 2 This embodiment describes a high-speed, compact, nested shaft system structure with clutch function, which includes a transmission output shaft 1, a clutch oil distribution pipe 2, a clutch assembly 3, an input gear ring hollow shaft 4, a first support bearing 5, a second support bearing 6, a third support bearing 7, a fourth support bearing 8, a fifth support bearing 9, and a sixth support bearing 10.

[0033] The input port of the clutch assembly 3 is fitted with a No. 5 support bearing 9, and the end of the input gear ring hollow shaft 4 is inserted into the middle of the inner ring of the No. 5 support bearing 9. A No. 6 support bearing 10 is fitted on one end of the input gear ring hollow shaft 4. The output port of the clutch assembly 3 is fitted with a No. 4 support bearing 8. One end of the transmission output shaft 1 is inserted into the middle of the inner ring of the No. 4 support bearing 8. A No. 3 support bearing 7 is fitted on one end of the transmission output shaft 1. A No. 1 support bearing 5 and a No. 2 support bearing 6 are fitted sequentially along the axial direction on the other end of the transmission output shaft 1. A countersunk hole is machined at the center of the end face of the other end of the transmission output shaft 1 along the axial direction. The clutch oil distribution pipe 2 is provided inside the countersunk hole.

[0034] In this specific embodiment, during use, power is introduced from the hollow shaft of the input gear ring, which is connected to the power input via a spline at the end of the input gear ring. The hollow shaft 4 of the input gear ring serves as the primary transmission shaft and is supported on the housing by bearings 8 and 10. The output shaft 1 serves as the secondary transmission shaft, nested inside the hollow shaft 4 of the input gear ring, and is supported on the housing by bearings 5, 6, and 7, thus achieving coaxial nesting and relatively independent rotation of the two shafts.

[0035] The clutch function is achieved through a splined interface. An internal spline is machined on the left end of the input gear ring hollow shaft 4. The clutch assembly 3 engages with this internal spline via an external spline. An external spline is machined on the left end of the transmission output shaft 1. The clutch friction plate seat 3 engages with this external spline via an internal spline. The friction plate assembly is mounted between the clutch hub and the clutch carrier. When the friction plate assembly is pressed together, power is transmitted from the input gear ring hollow shaft 4 to the transmission output shaft 1; when disengaged, the two shafts separate.

[0036] The bearing assembly employs a six-bearing arrangement. Support bearings 8 (number four) and 10 (number six) are located at the input end, typically using a combination of deep groove ball bearings and cylindrical roller bearings to withstand radial and axial forces. Support bearings 5 ​​(number one), 6 (number two), and 7 (number three) are located at the output end, using four-point contact ball bearings and cylindrical roller bearings to withstand the radial and axial forces of the helical gear meshing. Support bearing 9 (number five) is located at the end of the clutch assembly, providing auxiliary support in the middle of the hollow shaft of the input gear ring, distributing the weight of the output shaft system, increasing the rigidity of the entire output shaft system, and providing additional intermediate support. When the clutch is engaged, the inner and outer rings of support bearings 8 (number four) and 9 (number five) are in a relatively stationary, non-working state. The entire shaft system is supported by four bearings, preventing over-coupling and ensuring the stability and reliability of the overall shaft system under high-speed operation. Furthermore, these two bearings provide reliable support to the clutch assembly, ensuring smooth clutch operation.

[0037] The lubrication and oil supply system is integrated within the shaft. Pressurized oil is injected into the main shaft oil supply channel from the right end of the clutch oil distribution pipe 2, and then sprayed into the clutch working area through radial oil holes to lubricate and cool the friction plates. After use, the oil is thrown out through the return oil hole on the hollow shaft 4 of the input gear ring under centrifugal force, flowing back to the bottom of the housing to complete the cycle. This shaft system structure highly integrates transmission, clutch, support, and lubrication, achieving stable, compact, and efficient transmission and clutch functions under high-speed operating conditions.

[0038] Specific Implementation Method Two: Combining Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 1. This embodiment describes a high-speed, compact, nested shaft system structure with a clutch function, wherein the left end of the input gear ring hollow shaft 4 is machined with an internal spline.

[0039] Specific implementation method three: Combining Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment Two. The high-speed compact nested shaft system structure with clutch function described in this embodiment has an external spline machined along the circumferential direction on the inner wall of the input port of the clutch assembly 3.

[0040] Specific implementation method four: Combination Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 3. The high-speed compact nested shaft system structure with clutch function described in this embodiment is such that the internal spline at the left end of the input gear ring hollow shaft 4 is connected to the external spline of the input port of the clutch assembly 3.

[0041] In this specific embodiment, the input gear ring hollow shaft 4, clutch assembly 3, and transmission output shaft 1 are dynamically connected via a spline connection, realizing the interface function for power on / off switching. This structure transmits large torque, engages smoothly, and responds quickly.

[0042] Specific Implementation Method Five: Combining Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 1. This embodiment describes a high-speed, compact, nested shaft system structure with a clutch function, wherein the left end of the transmission output shaft 1 is machined with an external spline.

[0043] Specific Implementation Method Six: Combination Figure 1 and Figure 2This embodiment further defines the shaft system structure described in Specific Embodiment Five. This embodiment describes a high-speed, compact, nested shaft system structure with clutch function. In this embodiment, the friction plate seat in the clutch assembly 3 is connected to the external spline at the left end of the transmission output shaft 1 via an internal spline.

[0044] Specific implementation method seven: Combination Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 1. The high-speed compact nested shaft system structure with clutch function described in this embodiment uses a combination of deep groove ball bearings and cylindrical roller bearings for the No. 4 support bearing 8 and the No. 6 support bearing 10.

[0045] Specific implementation method eight: Combination Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 1. The high-speed compact nested shaft system structure with clutch function described in this embodiment uses four-point contact ball bearings or cylindrical roller bearings for the first support bearing 5, the second support bearing 6, and the third support bearing 7.

[0046] Specific Implementation Method Nine: Combining Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 1. This embodiment describes a high-speed, compact, nested shaft system structure with clutch function. One end of the clutch oil distribution pipe 2 is connected to the main shaft oil supply channel; the other end of the clutch oil distribution pipe 2 has radial oil holes on its outer surface, through which oil is sprayed into the working area of ​​the clutch assembly 3 to lubricate and cool the friction plates.

[0047] In this specific embodiment, one end of the clutch oil distribution pipe 2 is connected to the main shaft oil supply channel; the other end of the clutch oil distribution pipe 2 has radial oil holes on its outer surface; thus, the lubrication and oil supply system are integrated into the shaft. Pressurized oil is injected into the main shaft oil supply channel from the right end of the clutch oil distribution pipe 2, and sprayed into the clutch working area through the radial oil holes to lubricate and cool the friction plates.

[0048] Specific Implementation Method Ten: Combining Figure 1 and Figure 2 This embodiment further defines the shaft system structure described in Specific Embodiment 1. This embodiment describes a high-speed, compact, nested shaft system structure with a clutch function, wherein the outer surface of the input gear ring hollow shaft 4 is provided with an oil return hole along the circumferential direction.

[0049] Working principle

[0050] In operation, power is introduced from the hollow shaft of the input gear ring, which is connected to the power input via a spline at the end of the input gear ring. The hollow shaft 4 of the input gear ring serves as the primary transmission shaft, supported on the housing by bearings 8 and 10. The output shaft 1 serves as the secondary transmission shaft, nested inside the hollow shaft 4 of the input gear ring, and supported on the housing by bearings 5, 6, and 7, thus achieving coaxial nesting and relatively independent rotation of the two shafts.

[0051] The clutch function is achieved through a splined interface. An internal spline is machined on the left end of the input gear ring hollow shaft 4. The clutch assembly 3 engages with this internal spline via an external spline. An external spline is machined on the left end of the transmission output shaft 1. The clutch friction plate seat 3 engages with this external spline via an internal spline. The friction plate assembly is mounted between the clutch hub and the clutch carrier. When the friction plate assembly is pressed together, power is transmitted from the input gear ring hollow shaft 4 to the transmission output shaft 1; when disengaged, the two shafts separate.

[0052] The bearing assembly employs a six-bearing arrangement. Support bearings 8 (number four) and 10 (number six) are located at the input end, typically using a combination of deep groove ball bearings and cylindrical roller bearings to withstand radial and axial forces. Support bearings 5 ​​(number one), 6 (number two), and 7 (number three) are located at the output end, using four-point contact ball bearings and cylindrical roller bearings to withstand the radial and axial forces of the helical gear meshing. Support bearing 9 (number five) is located at the end of the clutch assembly, providing auxiliary support in the middle of the hollow shaft of the input gear ring, distributing the weight of the output shaft system, increasing the rigidity of the entire output shaft system, and providing additional intermediate support. When the clutch is engaged, the inner and outer rings of support bearings 8 (number four) and 9 (number five) are in a relatively stationary, non-working state. The entire shaft system is supported by four bearings, preventing over-coupling and ensuring the stability and reliability of the overall shaft system under high-speed operation. Furthermore, these two bearings provide reliable support to the clutch assembly, ensuring smooth clutch operation.

[0053] The lubrication and oil supply system is integrated within the shaft. Pressurized oil is injected into the main shaft oil supply channel from the right end of the clutch oil distribution pipe 2, and then sprayed into the clutch working area through radial oil holes to lubricate and cool the friction plates. After use, the oil is thrown out through the return oil hole on the hollow shaft 4 of the input gear ring under centrifugal force, flowing back to the bottom of the housing to complete the cycle. This shaft system structure highly integrates transmission, clutch, support, and lubrication, achieving stable, compact, and efficient transmission and clutch functions under high-speed operating conditions.

Claims

1. A high-speed, compact, nested shaft system structure with clutch function, characterized in that: It includes a transmission output shaft (1), a clutch oil distribution pipe (2), a clutch assembly (3), an input gear ring hollow shaft (4), a first support bearing (5), a second support bearing (6), a third support bearing (7), a fourth support bearing (8), a fifth support bearing (9), and a sixth support bearing (10). The input port of the clutch assembly (3) is fitted with a No. 5 support bearing (9), and the end of the input gear ring hollow shaft (4) is inserted into the middle of the inner ring of the No. 5 support bearing (9). A No. 6 support bearing (10) is fitted on one end of the input gear ring hollow shaft (4). A No. 4 support bearing (8) is fitted inside the output port of the clutch assembly (3). One end of the transmission output shaft (1) is inserted into the middle of the inner ring of the No. 4 support bearing (8). A No. 3 support bearing (7) is fitted on one end of the transmission output shaft (1). A No. 1 support bearing (5) and a No. 2 support bearing (6) are fitted sequentially along the axial direction on the other end of the transmission output shaft (1). A countersunk hole is machined at the center of the other end face of the transmission output shaft (1) along the axial direction. The interior of the countersunk hole is fitted with a clutch oil distribution pipe (2).

2. The high-speed compact nested shaft system structure with clutch function according to claim 1, characterized in that: The left end of the input gear ring hollow shaft (4) is machined with an internal spline.

3. The high-speed compact nested shaft system structure with clutch function according to claim 2, characterized in that: The inner wall of the input port of the clutch assembly (3) is machined with external splines along the circumferential direction.

4. A high-speed compact nested shaft system structure with clutch function according to claim 3, characterized in that: The internal spline at the left end of the input gear ring hollow shaft (4) is connected to the external spline of the input port of the clutch assembly (3).

5. A high-speed compact nested shaft system structure with clutch function according to claim 1, characterized in that: The left end of the transmission output shaft (1) is machined with an external spline.

6. A high-speed, compact, nested shaft system structure with clutch function according to claim 5, characterized in that: The friction plate seat in the clutch assembly (3) is connected to the external spline at the left end of the transmission output shaft (1) via an internal spline.

7. A high-speed, compact, nested shaft system structure with clutch function according to claim 1, characterized in that: The No. 4 support bearing (8) and the No. 6 support bearing (10) are a combination of deep groove ball bearings and cylindrical roller bearings.

8. A high-speed compact nested shaft system structure with clutch function according to claim 1, characterized in that: The No. 1 support bearing (5), No. 2 support bearing (6) and No. 3 support bearing (7) are four-point contact ball bearings or cylindrical roller bearings.

9. A high-speed compact nested shaft system structure with clutch function according to claim 1, characterized in that: One end of the clutch oil distribution pipe (2) is connected to the main shaft oil supply channel; the other end of the clutch oil distribution pipe (2) has a radial oil hole on its outer surface, which sprays oil into the working area of ​​the clutch assembly (3) to lubricate and cool the friction plate.

10. A high-speed compact nested shaft system structure with clutch function according to claim 1, characterized in that: The outer surface of the input gear ring hollow shaft (4) is provided with an oil return hole along the circumferential direction.

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