Elastic pre-tightening roller bearing

Abstract

The utility model discloses an elastic pre-tightening roller bearing which comprises a bearing inner ring and a bearing outer ring, a roller is arranged between the bearing inner ring and the bearing outer ring in a rolling manner, and the bearing outer ring rotates relative to the bearing inner ring; the two end faces of the bearing inner ring are each provided with a disc, the discs can elastically deform, fulcrums are formed between the discs and the bearing inner ring, and the fulcrums are located between the inner edges of the discs and the outer edges of the discs and used for axially supporting the discs, so that when the discs are installed on the bearing inner ring, the inner edges of the discs get close to the end faces of the bearing inner ring and are fixedly connected with the bearing inner ring. The outer edge of the disc is matched with the end face of the bearing outer ring, and the roller is axially limited. By means of the matching relation formed between the disc and the bearing outer ring, the roller can be axially limited and cannot abut against the bearing outer ring, friction between the disc and the bearing outer ring is effectively reduced, abrasion is reduced, and meanwhile lubrication of lubricating oil on the roller is prevented from being affected.

Description

Technical Field

[0001] This utility model relates to the technical field of bearings, and in particular to an elastic preloaded roller bearing. Background Technology

[0002] The textile cam multi-arm mechanism consists of a cam drive mechanism, a disc bearing, and a heddle arm. The cam drive mechanism drives the disc bearing to move up and down through a transmission connection, which in turn drives the heddle arm to move up and down. The disc bearing includes an inner ring, an outer ring, and a disc. The cam drive mechanism is connected to the outer ring of the bearing, causing it to rotate relative to the inner ring. One end of the disc is fixed to the inner ring, and the other end engages with the outer ring. Due to the unique motion of the cam multi-arm mechanism, coupled with the limited installation space, the large impact it experiences, and the harsh working environment, some existing technologies use steel ball disc bearings. This design has the problem of excessively tight fit between the disc and the outer ring of the bearing, resulting in excessive friction and affecting the entry of lubricating oil into the rollers. Utility Model Content

[0003] The purpose of this utility model is to provide an elastic preloaded roller bearing, and the technical problem to be solved is to reduce the friction between the disc and the outer ring of the bearing.

[0004] To achieve the above objectives, the solution of this utility model is: an elastic preloaded roller bearing, including an inner bearing ring and an outer bearing ring, with rollers rolling between the inner and outer bearing rings, and the outer bearing ring rotating relative to the inner bearing ring;

[0005] The bearing inner ring has discs on both ends. The discs are elastically deformable and form a fulcrum between the discs and the bearing inner ring. The fulcrum is located between the inner edge and the outer edge of the disc and is used to axially support the discs. When the discs are installed on the bearing inner ring, the inner edge of the discs moves towards the end face of the bearing inner ring and is connected and fixed to the bearing inner ring. The outer edge of the discs fits on the end face of the bearing outer ring and axially limits the rollers.

[0006] Furthermore, an inclined section is formed on the disc, which extends radially from the inner ring of the bearing to the outer ring of the bearing and gradually tilts inward toward the end face of the outer ring of the bearing. The fulcrum is located in the middle of the inclined section, so that when the disc is installed on the inner ring of the bearing, the inner edge of the disc moves toward the end face of the inner ring of the bearing, and the outer edge of the disc tilts toward the direction away from the end face of the outer ring of the bearing.

[0007] Furthermore, the fulcrum is formed on the inner ring of the bearing, and mating parts are formed on both ends of the outer ring of the bearing. The disc mates with the mating parts, and the fulcrum protrudes from the surface of the mating parts.

[0008] Furthermore, along the axial direction of the inner ring of the bearing, the height difference between the fulcrum and the mating part is less than the axial deformation of the disc.

[0009] Furthermore, the mating part is an annular groove, which is formed by the indentation of the end face of the outer ring of the bearing and connects to the inner ring and outer ring of the bearing. The inner diameter of the annular groove is larger than the outer diameter of the disc, so that after the disc is installed on the outer ring of the bearing, a gap is formed between the disc and the inner wall of the annular groove.

[0010] Furthermore, the tilt angle of the tilted section of the disk is 1 to 1.5°.

[0011] Furthermore, the disc is disc-shaped, with one end of the inclined section extending horizontally in the radial direction toward the inner ring of the bearing to form a first horizontal section. A fixing part is formed on the inner ring of the bearing, which corresponds to the position of the first horizontal section and is parallel to the first horizontal section, for riveting and fixing with the first horizontal section.

[0012] Furthermore, one end of the inclined section extends horizontally in the radial direction toward the outer ring of the bearing to form a second horizontal section, so that when the disc is installed on the inner ring of the bearing, the second horizontal section can tilt away from the end face of the outer ring of the bearing, forming a trumpet-shaped gap with the end face of the outer ring of the bearing.

[0013] The beneficial effects of this utility model after adopting the above solution are as follows: the disc can be elastically deformed, and a fulcrum is formed between the disc and the inner ring of the bearing. The fulcrum is located between the inner edge and the outer edge of the disc. When the disc is installed on the inner ring of the bearing, the inner edge of the disc moves towards the end face of the inner ring of the bearing and is connected and fixed to the inner ring of the bearing, so that the outer edge of the disc fits on the end face of the outer ring of the bearing. Through the setting of the fulcrum, the outer edge of the disc has a tendency to move away from the end face of the outer ring of the bearing. The fit relationship formed between the disc and the outer ring of the bearing can both limit the axial movement of the roller and prevent it from pressing against the outer ring of the bearing. When the outer ring of the bearing rotates relative to the inner ring of the bearing, the friction between the disc and the outer ring of the bearing is effectively reduced, reducing wear. At the same time, it avoids the disc and the outer ring of the bearing from being in too tight contact, which would affect the lubrication of the roller by the lubricating oil. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the combined structure of this utility model.

[0015] Figure 2 This is an exploded structural diagram of the present invention. Figure 1 .

[0016] Figure 3 This is an exploded structural diagram of the present invention. Figure 2 .

[0017] Figure 4 This is a cross-sectional structural diagram of the present invention before assembly.

[0018] Figure 5 yes Figure 4 A magnified view of a portion of the image.

[0019] Label Explanation:

[0020] 1-Bearing inner ring, 2-Bearing outer ring, 3-Roller, 4-Disc, 5-Pivot point, 6-Roller mounting groove, 11-Fixing part, 12-Supporting part, 13-Inner ring annular groove, 21-Mating part, 22-Mounting hole, 41-Inclined section, 42-First horizontal section, 43-Second horizontal section. Detailed Implementation

[0021] The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

[0022] Unless otherwise expressly defined, the use of directional terms such as "center," "lateral," "longitudinal," "horizontal," "vertical," "top," "bottom," "inner," "outer," "upper," "lower," "front," "rear," "left," "right," "clockwise," and "counterclockwise" in the claims, description, and accompanying drawings of this invention is merely for the convenience of describing the invention and simplifying the description, and is not intended to indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the specific scope of protection of this invention.

[0023] like Figure 1 As shown in Figure 5, this utility model provides an elastic preloaded roller bearing, including an inner ring 1 and an outer ring 2. Rollers 3 are rolled between the inner ring 1 and the outer ring 2, and the outer ring 2 rotates relative to the inner ring 1. Two discs 4 are respectively provided on the two end faces of the inner ring 1. The two discs 4 are fixedly mounted on the end faces of the inner ring 1 from both end faces. The discs 4 are elastically deformable, and a fulcrum 5 is formed between the discs 4 and the inner ring 1. The fulcrum 5 is located between the inner edge and the outer edge of the discs 4 and is used to axially support the discs 4. When the discs 4 are mounted on the inner ring 1, the inner edge of the discs 4 moves closer to the end face of the inner ring 1 and is connected and fixed to the inner ring 1, so that the outer edge of the discs 4 fits on the end face of the outer ring 2, axially limiting the rollers 3. Specifically, the fulcrum 5 can be formed on the inner ring 1 or on the discs 4; there is no specific limitation. Those skilled in the art can design according to specific circumstances.

[0024] Key points combined Figure 1 As shown, the disc 4 is disc-shaped, specifically a ring structure. The disc 4 has an inner edge and an outer edge. The inner edge of the disc 4 is used to fix and connect with the inner ring 1 of the bearing, and the outer edge of the disc 4 is used to mate with the outer ring 2 of the bearing. The disc 4 has a first horizontal section 42, an inclined section 41 and a second horizontal section 43 formed in the radial direction. The first horizontal section 42 corresponds to the inner edge of the disc 4 and the second horizontal section 43 corresponds to the outer edge of the disc 4.

[0025] In this specific embodiment, the inclined section 41 extends radially from the inner ring 1 of the bearing to the outer ring 2 of the bearing, and gradually tilts inward toward the end face of the outer ring 2 of the bearing. The fulcrum 5 is located in the middle of the inclined section 41, so that when the disc 4 is installed on the inner ring 1 of the bearing, the inner edge of the disc 4 moves toward the end face of the inner ring 1 of the bearing, and the outer edge of the disc 4 extends outward and tilts toward the direction away from the end face of the outer ring 2 of the bearing, so that the disc 4 and the outer ring 2 of the bearing are kept in a non-tight state, in a critical state of contact and non-contact, which effectively reduces the friction between the disc 4 and the outer ring 2 of the bearing, reduces wear, and improves the service life of the bearing.

[0026] Preferably, the tilt angle of the tilted segment 41 of the disk 4 is α, where α is 1 to 1.5° (e.g., Figure 5 As shown in the figure, this angle can effectively control the axial deformation of the disc 4, especially the amount of warping of the outer edge of the disc 4, so that the contact between the outer edge of the disc 1 and the end face of the bearing outer ring 2 can reach a light contact state, that is, the two are in a critical state of contact and non-contact.

[0027] Key points combined Figure 1-3 As shown, the fulcrum 5 is formed on the inner ring 1 of the bearing, and a support portion 12 is formed on the inner ring 1. The support portion 12 is located on the outer edge of the inner ring 1, close to the roller 3. The support portion 12 corresponds to the inclined section 41 of the disc 4. After the disc 4 is installed on the inner ring 1, it can provide axial support for the disc 4. The two end faces of the outer ring 2 of the bearing are respectively formed with mating portions 21. The outer edge of the disc 4 is mated on the mating portion 21. Along the axial direction of the inner ring 1 of the bearing, the height of the support portion 12 is greater than the height of the mating portion 21. The fulcrum 5 is specifically formed on the support portion 12, so that the fulcrum 5 protrudes from the surface of the mating portion 21. Preferably, the height difference between the fulcrum 5 and the mating portion is less than the axial deformation of the disc 4, controlling the size of the gap between the disc 4 and the mating portion 21, and avoiding an excessively large height difference, so that the gap between the outer edge of the disc 4 and the mating portion 21 is too large.

[0028] Key points combined Figure 4-5 As shown, the first horizontal segment 42 is formed by extending horizontally in the radial direction towards the inner ring 1 of the bearing from one end of the inclined segment 41. Since it is fixedly connected to the inner ring 1 of the bearing, a fixing part 11 is formed on the inner ring 1 of the bearing. The fixing part 11 is positioned corresponding to the first horizontal segment 42. Preferably, the fixing part 11 is parallel to the first horizontal segment 42. When the disc 4 is installed on the inner ring 1 of the bearing, the first horizontal segment 42 is riveted and fixed to the fixing part 11 in parallel, making the connection more stable.

[0029] Furthermore, the inner ring 1 of the bearing has an inner ring annular groove 13 formed by the concave inner faces of both ends. The inner ring annular groove 13 is located between the fixed part 11 and the support part 12, which can provide deformation space for the deformation of the disc 4.

[0030] In this specific embodiment, an axially penetrating mounting hole 22 is formed on the outer ring 2 of the bearing. The inner ring 1 of the bearing falls into the mounting hole 22, forming a roller mounting groove 6 between it and the outer ring 2. Rollers 3 are rolled and installed in the roller mounting groove 6, rolling and fitting against the inner wall of the roller mounting groove 3. There are several rollers 3, and two adjacent rollers 3 roll and fit against each other, so that several rollers 3 are fully distributed in the mounting groove 6. The mating part 21 is an annular groove, which is formed by the indentation of the end face of the outer ring 2 of the bearing and connects to the inner ring 1 and the outer ring 2 of the bearing. That is, the annular groove is connected to the roller mounting groove 6. The inner diameter of the annular groove is larger than the outer diameter of the disc 4, so that after the disc 4 is installed on the outer ring 2 of the bearing, a gap is formed between the disc 4 and the inner wall of the annular groove, and the lubricating oil can enter the roller mounting groove 6 through the gap.

[0031] The second horizontal section 43 is formed by extending radially horizontally towards the outer ring 2 of the bearing from the other end of the inclined section 41. It is used to mate with the end face of the outer ring 2 of the bearing. Specifically, the radial dimension of the part of the disc 4 that mates with the outer ring 2 of the bearing is greater than the radial dimension of the second horizontal section 43. When the disc 4 is installed on the inner ring 1 of the bearing, the second horizontal section 43 can be tilted away from the end face of the outer ring 2 of the bearing, and the gap between it and the outer ring 2 gradually expands radially outward to form a trumpet-shaped lubricating oil inlet, which facilitates the flow of lubricating oil into the roller mounting groove 6.

[0032] The assembly process of disc 4 involves first placing disc 4 axially on the inner ring 1 of the bearing (e.g., ...). Figure 4 As shown), the second horizontal section 43 of the disc 4 abuts against the outer ring 2 of the bearing. Since the support part 12 is higher than the mating part 21, and the inclined section 41 of the disc 4 corresponds to the support part 12, before assembly, there is a gap between the inner edge of the disc 4 and the inner ring 1 of the bearing. During assembly, after applying axial force to the disc 4, the inner edge of the disc 4 moves closer to the end face of the inner ring 1 of the bearing. The first horizontal section 42 of the disc 4 is first riveted and fixed to the fixing part 11 of the inner ring 1 of the bearing. The disc 4 abuts against the support part 12. The outer edge of the disc 4 extends outward and tilts away from the end face of the outer ring 2 of the bearing, forming a light contact state with the end face of the outer ring 2 of the bearing. A trumpet-shaped gap is formed between the second horizontal section 43 and the outer ring 2 of the bearing.

[0033] The above description is only a preferred embodiment of this utility model and is not intended to limit the design of this case. All equivalent changes made based on the key design of this case shall fall within the protection scope of this case.

Claims

1. A resilient preload roller bearing, characterized in that: It includes an inner ring (1) and an outer ring (2) of a bearing, with rollers (3) rolling between the inner ring (1) and the outer ring (2), and the outer ring (2) of the bearing rotating relative to the inner ring (1); The inner ring (1) of the bearing is provided with discs (4) on both ends. The discs (4) can be elastically deformed. A fulcrum (5) is formed between the discs (4) and the inner ring (1). The fulcrum (5) is located between the inner edge of the discs (4) and the outer edge of the discs (4) and is used to axially support the discs (4). When the discs (4) are installed on the inner ring (1) of the bearing, the inner edge of the discs (4) moves closer to the end face of the inner ring (1) of the bearing and is connected and fixed to the inner ring (1). The outer edge of the discs (4) fits on the end face of the outer ring (2) of the bearing and axially limits the rollers (3).

2. The elastic preload roller bearing as described in claim 1, characterized in that: An inclined section (41) is formed on the disc (4). The inclined section (41) extends radially from the inner ring (1) of the bearing to the outer ring (2) of the bearing and gradually tilts inward toward the end face of the outer ring (2). The fulcrum (5) is located in the middle of the inclined section (41) so that when the disc (4) is installed on the inner ring (1) of the bearing, the inner edge of the disc (4) moves toward the end face of the inner ring (1) of the bearing, and the outer edge of the disc (4) tilts away from the end face of the outer ring (2) of the bearing.

3. The elastic preload roller bearing as described in claim 1, characterized in that: The fulcrum (5) is formed on the inner ring (1) of the bearing, and the two ends of the outer ring (2) of the bearing are respectively formed with mating parts (21). The disc (4) is mated on the mating parts (21), and the fulcrum (5) protrudes from the surface of the mating parts (21).

4. The elastic preload roller bearing as described in claim 3, characterized in that: Along the axial direction of the inner ring (1) of the bearing, the height difference between the fulcrum (5) and the mating part (21) is less than the axial deformation of the disc (4).

5. The elastic preload roller bearing as described in claim 3, characterized in that: The mating part (21) is an annular groove, which is formed by the concave end face of the bearing outer ring (2) and connects to the bearing inner ring (1) and the bearing outer ring (2). The inner diameter of the annular groove is larger than the outer diameter of the disc (4) so ​​that after the disc (4) is installed on the bearing outer ring (2), a gap is formed between the disc (4) and the inner wall of the annular groove.

6. The elastic preload roller bearing as described in claim 2, characterized in that: The tilt angle of the tilted section (41) of the disk (4) is 1 to 1.5°.

7. The elastic preload roller bearing as described in claim 2, characterized in that: The disc (4) is disc-shaped. One end of the inclined section (41) extends horizontally in the radial direction toward the inner ring (1) of the bearing to form a first horizontal section (42). A fixing part (11) is formed on the inner ring (1) of the bearing. The fixing part (11) corresponds to the position of the first horizontal section (42) and is parallel to the first horizontal section (42), and is used to rivet and fix it to the first horizontal section (42).

8. The elastic preload roller bearing as described in claim 2, characterized in that: One end of the inclined section (41) extends horizontally in the radial direction toward the outer ring (2) of the bearing to form a second horizontal section (43), so that when the disc (4) is installed on the inner ring (1) of the bearing, the second horizontal section (43) can be tilted away from the end face of the outer ring (2) of the bearing to form a trumpet-shaped gap with the end face of the outer ring (2).

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