A new combined double-limiting one-way bearing
By using a combination of double-row rollers with double inclined surfaces and a limiting ring, the problem of locking failure, large axial movement, and high vibration and noise of one-way bearings under high-speed conditions is solved, resulting in more stable operation and a longer service life.
Patent Information
- Application Number
- CN202521470667.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-07-15
- Publication Date
- 2026-08-25
- Estimated Expiration
- 2035-07-15
AI Technical Summary
Existing one-way bearings are prone to locking failure due to temperature rise under high-speed operating conditions, and traditional combination solutions have problems such as large axial movement, high vibration and noise, and difficult assembly.
It adopts a combination of double-row rollers with double inclined surfaces and limit rings, combined with ball bearings, and is designed as a combined double-limit one-way bearing. The roller tilting and deflection realizes quick locking and unlocking, reducing axial movement and amplitude.
It improves the locking effect, reduces axial movement and amplitude, extends the service life of the bearing, and reduces structural wear and noise.
Smart Images
Figure CN224679903U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to a novel combined double-limit one-way bearing, and belongs to the field of one-way bearing equipment technology. Background Technology
[0002] One-way bearings, as key components in mechanical transmission systems, are mainly used to achieve power transmission in one direction and reverse idling, and are widely used in gearboxes, starters, conveying equipment, and other scenarios. Traditional one-way bearings are mainly divided into two types: wedge type and roller type. Although the wedge type structure has a high load capacity (≥500Nm), its speed limit is generally lower than 3000rpm, and it is prone to lock-up failure due to temperature rise under high-speed conditions. Although the roller type structure can achieve a high speed of 8000rpm, it cannot provide a reliable one-way lock-up function and requires an additional clutch system. Existing improvement solutions attempt to combine the two types of bearings, but due to the split series design, axial movement is ≥0.3mm, vibration and noise are as high as 70dB, and assembly is difficult in narrow spaces. These defects seriously restrict the improvement of reliability of heavy-duty high-speed equipment. Therefore, a new type of combined double-limit one-way bearing is proposed to solve the problems existing in the current technology. Utility Model Content
[0003] The purpose of this invention is to address the defects or deficiencies in the existing technology by providing a novel combined double-limit one-way bearing. By using double-row rollers with double inclined surfaces in conjunction with limit rings and ball bearings, the locking effect can be effectively improved, axial movement and amplitude can be reduced, structural wear can be dispersed, and the service life of the bearing can be extended.
[0004] To achieve the above objectives, the present invention adopts the following technical solution: It includes an outer shell 1 and an inner shell 4. A deep groove ball bearing 3 is provided at the front end of the inner shell 4 and is interference-fitted with the outer shell 1. A one-way roller assembly 5 is provided in the middle of the inner shell 4 and is radially constrained by the outer shell 1. The one-way roller assembly 5 includes a plurality of first rollers 51 and a plurality of second rollers 52. The first rollers 51 and second rollers 52 are arranged side by side. The first rollers 51 and second rollers 52 have the same structure, but the thickness of the second rollers 52 is greater than that of the first rollers 51. The first rollers 51 include a first mating surface 511, a second mating surface 512, and a friction surface 515. The first mating surfaces 511 and second mating surfaces 512 are adjacent and located above the friction surface 515. Limiting rings are provided on both the first rollers 51 and the second rollers 52 for radial constraint.
[0005] Furthermore, the first roller 51 and the second roller 52 are respectively provided with an inclined first limiting groove 514 and a second limiting groove 521 in the middle part of the upper part. The limiting rings include a first limiting ring 53 and a second limiting ring 54. The first limiting ring 53 is disposed in the first limiting groove 514 and the second limiting ring 54 is disposed in the second limiting groove 521.
[0006] Furthermore, the first limiting groove 514 starts below the transition position between the first mating surface 511 and the friction surface 515, and ends below the transition position between the second mating surface 512 and the friction surface 515.
[0007] Furthermore, the length of the first mating surface 511 is greater than the length of the second mating surface 512, and both are planar structures. The angle between the first mating surface 511 and the first limiting groove 514 is 25°±1°, and the angle between the second mating surface 512 and the first limiting groove 514 is 45°±1°.
[0008] Furthermore, the transition between the first mating surface 511 and the second mating surface 512 is an arc-shaped locking apex angle 513, the included angle between the first mating surface 511 and the second mating surface 512 is 110°±1°, and the maximum distance from the locking apex angle 513 to the friction surface 515 is greater than the distance between the inner wall of the outer shell 1 and the outer wall of the inner shell 4.
[0009] Furthermore, the inner shell 4 includes a first fixing layer 41, a second fixing layer 42, and a third fixing layer 43. The first fixing layer 41 is interference-fitted with the deep groove ball bearing 3, the second fixing layer 42 is fitted with the one-way roller assembly 5, and the third fixing layer 43 is provided with a roller constraint plate 6.
[0010] Furthermore, the inner shell 4 is provided with an axial second fixing groove 44 inside, and the outer shell 1 is provided with an axial first fixing groove 11 on the outside.
[0011] Furthermore, the inner wall of the outer shell 1 is provided with two mounting grooves, one located on the outside of the deep groove ball bearing 3 and the other located on the outside of the roller constraint plate 6. A first open retaining ring 2 is provided in the mounting groove on the outside of the deep groove ball bearing 3, and a second open retaining ring 7 is provided in the mounting groove on the outside of the roller constraint plate 6. The openings of the first open retaining ring 2 and the second open retaining ring 7 are not on the same vertical plane.
[0012] The working principle of this utility model is as follows: During the use of the bearing, the inner housing 4 is the driving component. When it rotates counterclockwise, it is in normal rotation. At this time, under the constraint of the limiting ring, the friction surfaces of the first roller 51 and the second roller 52 contact and rub against the outer wall of the second fixed layer 42 of the inner housing 4, resulting in clockwise tilting and deflection. The first mating surface 511 rises, and the second mating surface 512 falls. The friction surfaces are not in close contact with the second fixed layer 42, and the locking apex 513 is not in close contact with the inner wall of the outer housing 1, only maintaining a supporting contact. The deep groove ball bearing 3 at the front end plays the main rotational support role. When it is necessary to lock the bearing, the inner housing 4 is rotated clockwise. At this time, under the action of the massage force, the first roller... 51. The second roller 52 tilts counterclockwise, the first mating surface 511 descends, the second mating surface 512 rises, and the limiting groove pushes the limiting ring outward on one side of the second mating surface 512. The locking apex 513 presses against the inner wall of the outer shell 1. The limiting ring generates a reaction force during the pushing process, so that the friction surface is in close contact with the outer wall of the second fixed layer 42. At this time, the greater the tilting angle, the greater the reaction force generated by the limiting ring. Therefore, the locking force of the first roller 51 and the second roller 52 on the outer shell 1 and the inner shell 4 is greater. Moreover, since the double-layer roller and deep groove ball bearing 3 are used, and under the constraint of the first open hole spring 3 and the second open retaining spring 7 at both ends, the amount of movement and amplitude can be effectively reduced.
[0013] After adopting the above technical solution, the beneficial effects of this utility model are as follows: by using double-row rollers with double inclined surfaces in combination with the limiting ring, and then combining them with ball bearings, the locking effect can be effectively improved, axial movement and amplitude can be reduced, structural wear can be dispersed, and the service life of the bearing can be extended. Attached Figure Description
[0014] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0015] Figure 1 This is a schematic diagram of the structure of this utility model; Figure 2 yes Figure 1 The second angle view; Figure 3 This is a schematic diagram of the inner shell 4 in this utility model; Figure 4 This is a schematic diagram of the structure of the first roller 51 in this utility model; Figure 5 This is a schematic diagram of the structure of the second roller 52 in this utility model; Figure 6 yes Figure 1 Sectional view along the AA direction; Figure 7 This is an exploded structural diagram of the present invention; Figure 8 yes Figure 7 Sectional view along the BB direction.
[0016] Explanation of reference numerals in the attached drawings: 1. Outer shell; 2. First open retaining ring; 3. Deep groove ball bearing; 4. Inner shell; 5. One-way roller assembly; 6. Roller constraint plate; 7. Second open retaining ring; 11. First fixing groove; 41. First fixing layer; 42. Second fixing layer; 43. Third fixing layer; 44. Second fixing groove; 51. First roller; 52. Second roller; 53. First limiting ring; 54. Second limiting ring; 511. First mating surface; 512. Second mating surface; 513. Locking apex angle; 514. First limiting groove; 515. Friction surface. Detailed Implementation
[0017] See Figures 1-8As shown, the technical solution adopted in this specific embodiment is as follows: It includes an outer shell 1 and an inner shell 4. A deep groove ball bearing 3 is provided at the front end of the inner shell 4 and is interference-fitted with the outer shell 1. A one-way roller assembly 5 is provided in the middle of the inner shell 4 and is radially constrained by the outer shell 1. The one-way roller assembly 5 includes a plurality of first rollers 51 and a plurality of second rollers 52. The first rollers 51 and second rollers 52 are arranged side by side. The first rollers 51 and second rollers 52 have the same structure, but the thickness of the second rollers 52 is greater than that of the first rollers 51. The first rollers 51 include a first mating surface 511, a second mating surface 512, and a friction surface 515. The first mating surface 511 and the second mating surface 512 are adjacent and located above the friction surface 515. The first rollers 51 and the second rollers 52 are also arranged side by side. Each roller 52 is equipped with a limit ring for radial constraint. In this embodiment, a combined bearing structure is adopted. One type uses a deep groove ball bearing, which serves as the radial load support during normal rotation. The other type is a one-way roller assembly. The deep groove ball bearing has no directional restriction, while the one-way roller assembly has directional limit. During normal rotation, the cooperation of the two sets of bearings not only ensures smooth rotation, but also helps reduce the amplitude and suppress noise when the one-way roller assembly vibrates during rotation or locking. The overall ball movement of the bearing is more stable. The one-way roller assembly uses a combination of rollers arranged in parallel, and the limit rings are used to radially constrain the two sets of rollers. The high efficiency and speed are achieved by the several rollers covering the inner shell and the tightness when locking with the outer shell. Locking, specifically, is achieved by the rollers tilting and deflecting under the constraint of the limiting ring. In this embodiment, the two sets of rollers have the same structure, but the thickness of the second roller is greater than that of the first roller, so that the different roller sets are subjected to different forces, thereby dispersing friction and reducing wear. The roller is a cylindrical structure with two inclined surfaces. The main body is a cylinder, with a long mating surface and a short mating surface on it. The cylindrical surface is the friction surface, which contacts the inner shell and generates a force to drive the rollers to tilt and deflect. The transition position of the long and short mating surfaces forms an arc protrusion. The inner shell rotates counterclockwise for rotation and clockwise for locking. The locking principle is based on the lever principle. The contact point between the friction surface and the inner shell is the force application point, and the contact position with the limiting ring is the fulcrum of the lever. The contact point between the arc-shaped protrusion and the outer shell is the force-bearing point. The distance from the force-bearing point to the fulcrum is greater than the distance from the fulcrum to the force-bearing point. Therefore, it can quickly and effectively allow the roller to instantly open the inner shell and outer shell when tilting and deflecting, thus achieving locking. The clockwise rotation just releases the locking state and restores the rotation state. The vibration and noise during movement are less than those of traditional structures. Traditional structures mostly use the cooperation of rolling and blocking mechanisms to achieve locking, which requires a certain response time. At the same time, the collision between mechanisms will generate greater noise and produce greater amplitude and jerking. In contrast, the enveloping locking structure in this embodiment achieves instantaneous locking and unlocking through its own tilting and deflection, with a faster response speed and no obvious collision noise, thus achieving better operating performance.
[0018] More specifically, the first roller 51 and the second roller 52 are respectively provided with an inclined first limiting groove 514 and a second limiting groove 521 at their upper middle portions. The limiting rings include a first limiting ring 53 and a second limiting ring 54. The first limiting ring 53 is disposed in the first limiting groove 514, and the second limiting ring 54 is disposed in the second limiting groove 521. The first limiting groove 514 starts below the transition position between the first mating surface 511 and the friction surface 515, and ends below the transition position between the second mating surface 512 and the friction surface 515. The first mating surface 512... The length of mating surface 511 is greater than the length of the second mating surface 512. Both are planar structures. The angle between the first mating surface 511 and the first limiting groove 514 is 25°±1°, and the angle between the second mating surface 512 and the first limiting groove 514 is 45°±1°. The transition between the first mating surface 511 and the second mating surface 512 is an arc-shaped locking apex angle 513. The angle between the first mating surface 511 and the second mating surface 512 is 110°±1°, and the maximum distance from the locking apex angle 513 to the friction surface 515 is greater than the distance between the inner wall of the outer shell 1 and the outer wall of the inner shell 4. This is to achieve the purpose of this embodiment. The locking effect requires a combination of three aspects: First, a limiting groove is provided inside the roller to cooperate with the limiting ring, providing a fulcrum when the roller and the limiting ring are engaged. Second, the length of the first mating surface is greater than the length of the second mating surface, so that the protruding locking apex is in an offset position, ensuring that the locking apex can contact and separate from the outer shell when the roller tilts or deflects. Third, the angle between the two mating surfaces and the limiting groove is set so that when the inner shell is rotated counterclockwise, the first mating surface rises, and the contact between the limiting groove corresponding to the first mating surface and the limiting ring separates, turning into... The limiting groove corresponding to the second mating surface contacts the limiting ring to create a fulcrum, while the first mating surface only rises a short distance before being unable to rise further due to the limitation of the limiting ring, thus achieving smooth rotation. Conversely, when rotating clockwise, the locking apex rises upward and presses against the inner wall of the outer shell. Under the action of the lever, a small frictional force can achieve a strong locking effect. However, if the angle between the first mating surface and the limiting groove increases, the locking apex will be too high, resulting in a poor unlocking effect and still significant friction. If the angle decreases, the height of the locking apex will be lower, reducing the locking force and affecting the locking effect.
[0019] More specifically, the inner shell 4 includes a first fixing layer 41, a second fixing layer 42, and a third fixing layer 43. The first fixing layer 41 is interference-fitted with the deep groove ball bearing 3, the second fixing layer 42 is fitted with the one-way roller assembly 5, and the third fixing layer 43 is provided with a roller constraint plate 6. In this embodiment, the outer wall structure of the shell is divided into three sections: one section is used to fix the deep groove ball bearing, one section is used to assemble with the one-way roller assembly, and one section is used to install the roller constraint plate. Thus, the one-way roller assembly is constrained and limited at one end by the deep groove ball bearing and at the other end by the roller constraint plate, ensuring the compactness of the bearing structure and reducing the amplitude and noise during operation.
[0020] More specifically, the inner shell 4 is provided with an axial second fixing groove 44 inside, and the outer shell 1 is provided with an axial first fixing groove 11 on the outside. The two fixing grooves are used to cooperate with disassembly and assembly tools to facilitate assembly operations.
[0021] More specifically, the inner wall of the outer casing 1 is provided with two mounting grooves, one located on the outside of the deep groove ball bearing 3 and the other on the outside of the roller constraint plate 6. A first open retaining ring 2 is provided in the mounting groove on the outside of the deep groove ball bearing 3, and a second open retaining ring 7 is provided in the mounting groove on the outside of the roller constraint plate 6. The openings of the first open retaining ring 2 and the second open retaining ring 7 are not on the same vertical plane. In this embodiment, two open retaining rings are also provided to increase the radial constraint effect on the bearing. Moreover, the use of a sub-opening structure not only facilitates assembly, but also allows the open retaining rings to adapt to deformation and maintain the constraint effect when the bearing structural components undergo slight deformation under changes in operating temperature.
[0022] The working principle of this utility model is as follows: During the use of the bearing, the inner housing 4 is the driving component. When it rotates counterclockwise, it is in normal rotation. At this time, under the constraint of the limiting ring, the friction surfaces of the first roller 51 and the second roller 52 contact and rub against the outer wall of the second fixed layer 42 of the inner housing 4, resulting in clockwise tilting and deflection. The first mating surface 511 rises, and the second mating surface 512 falls. The friction surfaces are not in close contact with the second fixed layer 42, and the locking apex 513 is not in close contact with the inner wall of the outer housing 1, only maintaining a supporting contact. The deep groove ball bearing 3 at the front end plays the main rotational support role. When it is necessary to lock the bearing, the inner housing 4 is rotated clockwise. At this time, under the action of the massage force, the first roller... 51. The second roller 52 tilts counterclockwise, the first mating surface 511 descends, the second mating surface 512 rises, and the limiting groove pushes the limiting ring outward on one side of the second mating surface 512. The locking apex 513 presses against the inner wall of the outer shell 1. The limiting ring generates a reaction force during the pushing process, so that the friction surface is in close contact with the outer wall of the second fixed layer 42. At this time, the greater the tilting angle, the greater the reaction force generated by the limiting ring. Therefore, the locking force of the first roller 51 and the second roller 52 on the outer shell 1 and the inner shell 4 is greater. Moreover, since the double-layer roller and deep groove ball bearing 3 are used, and under the constraint of the first open hole spring 3 and the second open retaining spring 7 at both ends, the amount of movement and amplitude can be effectively reduced.
[0023] The above description is only used to illustrate the technical solution of this utility model and is not intended to limit it. Any other modifications or equivalent substitutions made by those skilled in the art to the technical solution of this utility model, as long as they do not depart from the spirit and scope of the technical solution of this utility model, should be covered within the scope of the claims of this utility model.
Claims
1. A novel combined double-limit unidirectional bearing, characterized in that: It includes an outer shell (1) and an inner shell (4). The inner shell (4) is provided with a deep groove ball bearing (3) at the front end, which is interference-fitted with the outer shell (1). The inner shell (4) is provided with a one-way roller assembly (5) in the middle, which is radially constrained by the outer shell (1). The one-way roller assembly (5) includes a number of first rollers (51) and a number of second rollers (52). The first rollers (51) and second rollers (52) are arranged side by side. The first rollers (51) and second rollers (52) have the same structure, but the thickness of the second rollers (52) is greater than that of the first rollers (51). The first rollers (51) include a first mating surface (511), a second mating surface (512), and a friction surface (515). The first mating surface (511) and the second mating surface (512) are adjacent and located above the friction surface (515). Both the first rollers (51) and the second rollers (52) are provided with limit rings for radial constraint.
2. The novel combined double-limit unidirectional bearing according to claim 1, characterized in that: The first roller (51) and the second roller (52) are respectively provided with an inclined first limiting groove (514) and a second limiting groove (521) in the middle part. The limiting rings include a first limiting ring (53) and a second limiting ring (54). The first limiting ring (53) is disposed in the first limiting groove (514), and the second limiting ring (54) is disposed in the second limiting groove (521).
3. A novel combined double-limit unidirectional bearing according to claim 2, characterized in that: The first limiting groove (514) starts below the transition position between the first mating surface (511) and the friction surface (515) and ends below the transition position between the second mating surface (512) and the friction surface (515).
4. A novel combined double-limit unidirectional bearing according to claim 1, characterized in that: The length of the first mating surface (511) is greater than the length of the second mating surface (512), and both are planar structures. The angle between the first mating surface (511) and the first limiting groove (514) is 25°±1°, and the angle between the second mating surface (512) and the first limiting groove (514) is 45°±1°.
5. A novel combined double-limit unidirectional bearing according to claim 1, characterized in that: The transition between the first mating surface (511) and the second mating surface (512) is an arc-shaped locking apex angle (513). The angle between the first mating surface (511) and the second mating surface (512) is 110°±1°, and the maximum distance from the locking apex angle (513) to the friction surface (515) is greater than the distance between the inner wall of the outer shell (1) and the outer wall of the inner shell (4).
6. A novel combined double-limit unidirectional bearing according to claim 1, characterized in that: The inner shell (4) includes a first fixing layer (41), a second fixing layer (42), and a third fixing layer (43). The first fixing layer (41) is interference-fitted with the deep groove ball bearing (3), the second fixing layer (42) is fitted with the one-way roller assembly (5), and the third fixing layer (43) is provided with a roller constraint plate (6).
7. A novel combined double-limit unidirectional bearing according to claim 1, characterized in that: The inner shell (4) is provided with an axial second fixing groove (44) inside, and the outer shell (1) is provided with an axial first fixing groove (11) on the outside.
8. A novel combined double-limit unidirectional bearing according to claim 1, characterized in that: The inner wall of the outer shell (1) is provided with two mounting grooves, one located on the outside of the deep groove ball bearing (3) and the other located on the outside of the roller constraint plate (6). A first open retaining ring (2) is provided in the mounting groove on the outside of the deep groove ball bearing (3), and a second open retaining ring (7) is provided in the mounting groove on the outside of the roller constraint plate (6). The openings of the first open retaining ring (2) and the second open retaining ring (7) are not on the same vertical plane.