Novel two-way stress tapered roller bearing

Abstract

The utility model relates to the technical field of tapered roller bearings, in particular to a novel two-way stressed tapered roller bearing. Comprising an outer ring, an inner ring arranged in the outer ring and a plurality of rollers arranged between the outer ring and the inner ring, and further comprises a retainer used for separating the rollers, a check ring arranged on one side of the inner ring in an abutting mode and a spring ring arranged between the check ring and the inner ring. One end of the spring ring abuts against the inner wall of the check ring, and the other end of the spring ring abuts against the inner wall of the inner ring. The novel two-way stressed tapered roller bearing provided by the utility model has the advantages of high positioning precision, good stability and firmness, simplicity in operation, convenience in disassembly and assembly and the like.

Description

Technical Field

[0001] This utility model relates to the field of tapered roller bearing technology, and in particular to a novel bidirectional tapered roller bearing. Background Technology

[0002] Tapered roller bearings are separable bearings that can withstand both radial and axial loads during operation, and are widely used in industries such as automotive, mining, and metallurgy. Conventional tapered roller bearings can only withstand unidirectional axial loads. In applications requiring bidirectional forces, double-row or multi-row tapered roller bearings are often used, resulting in a larger assembly space requirement and failing to meet lightweight design requirements.

[0003] Chinese patent CN201908949U discloses a tapered roller bearing with a cage guided at the large end and a bottomless small end, suitable for high-power, high-speed, and certain impact load applications. This invention comprises an outer ring, an inner ring, a cage, rolling elements, and a locking ring. Its key features are: the inner ring eliminates the small flange and uses a movable locking ring; the inner diameter of the cage's large end is guided by the diameter of the inner ring's large flange, and an appropriate number of R-shaped lubrication grooves are formed on the inner diameter of the cage's large end; the small end of the cage is designed to remove the flange portion from the bottom surface of the conventional cage inner diameter.

[0004] However, this technical solution does not have a flange on the outer ring of the tapered roller bearing, which means that the entire bearing can only be subjected to force in one direction. The rollers may wobble or slip out of the raceway, affecting the positioning accuracy. In addition, the locking ring and the inner ring of this tapered roller bearing are simply snapped together, and there are no additional fixing structures inside. After long-term use, the locking ring may fall off, affecting the use of the bearing and reducing the interchangeability and utilization rate of the bearing parts. Utility Model Content

[0005] The purpose of this invention is to address the shortcomings of existing technologies by providing a novel bidirectional tapered roller bearing. By fixing the inner ring and retaining ring with a spring ring, the bearing inner ring and rollers are sufficiently stable, ensuring the stability of the bearing during operation, improving the interchangeability and utilization rate of bearing parts, and avoiding damage to parts due to loose assembly of internal bearing components.

[0006] To achieve the above objectives, this utility model provides the following technical solution:

[0007] A novel bidirectional tapered roller bearing includes: an outer ring, an inner ring disposed inside the outer ring, and a plurality of rollers disposed between the outer ring and the inner ring; and further includes: a cage for separating the rollers, a retaining ring disposed close to one side of the inner ring, and a spring ring disposed between the retaining ring and the inner ring, wherein one end of the spring ring abuts against the inner wall of the retaining ring, and the other end abuts against the inner wall of the inner ring.

[0008] Preferably, the spring ring is embedded in the mounting groove formed by the retaining ring and the inner ring.

[0009] Preferably, the mounting groove includes: a first groove disposed on the inner ring and a second groove disposed on the retaining ring and symmetrically disposed with respect to the first groove, wherein the spring ring is installed inside the first groove and the second groove.

[0010] Preferably, a retaining edge is provided on the side of the outer ring opposite to the spring ring.

[0011] Preferably, the outer diameter surface of the retaining ring exceeds the minimum outer diameter surface of the inner ring and is disposed close to the cage, and the outer diameter surface of the retaining ring does not contact the cage.

[0012] Preferably, a groove is provided on the outer diameter surface of the spring coil.

[0013] Preferably, the protrusions are adapted to the first groove and the second groove, respectively.

[0014] Preferably, the slot is adapted to the protrusions on the inner diameter surfaces of both the retaining ring and the inner ring.

[0015] Preferably, the spring coil has a notch.

[0016] Preferably, the slot is provided with a plurality of disassembly and assembly holes that completely penetrate the spring coil.

[0017] The beneficial effects of this utility model are as follows:

[0018] (1) This utility model improves the interchangeability and utilization of bearing parts by splitting the integrated inner ring into an inner ring and a retaining ring, and fixing the inner ring and the retaining ring together by a spring ring installed in the slot. It avoids the damage to parts caused by the loose parts when assembling the inner components. When replacing parts, only the spring ring needs to be removed. The spring ring is provided with a disassembly and assembly hole, which is convenient to disassemble and assemble and has low operation difficulty.

[0019] (2) This utility model achieves bidirectional axial force by setting a retaining edge at the small end of the outer ring, which makes the roller more stable, ensures the positioning accuracy of the bearing, and saves assembly space in the bidirectional force scenario, thus meeting the requirements of lightweight design.

[0020] (3) By embedding the spring ring into the mounting groove formed by the retaining ring and the inner ring, this utility model can effectively limit the radial or axial displacement of the spring ring, prevent the spring ring from centrifugal deformation or misalignment during high-speed rotation, ensure that the preload is always transmitted axially, and thus ensure the stability of the bearing during operation.

[0021] In summary, this utility model has the advantages of high positioning accuracy, good stability and firmness, simple operation and convenient assembly and disassembly. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the overall structure of this utility model;

[0023] Figure 2 for Figure 1 Enlarged view of point A;

[0024] Figure 3 This is a schematic diagram of the overall structure of the spring coil of this utility model;

[0025] Figure 4 This is a partial cross-sectional view of the spring coil of this utility model;

[0026] Figure 5 for Figure 4 Enlarged view of point B;

[0027] Figure 6 This is a partial sectional view of the assembly of the inner ring and the retaining ring of this utility model;

[0028] Figure 7 for Figure 6 Enlarged view of point C. Detailed Implementation

[0029] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0030] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or component referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0031] Example

[0032] like Figures 1-7 As shown, this embodiment provides a novel bidirectional tapered roller bearing, comprising: an outer ring 1, an inner ring 2 disposed inside the outer ring 1, and a plurality of rollers 3 disposed between the outer ring 1 and the inner ring 2. It also includes: a cage 4 for separating the rollers 3, a retaining ring 5 disposed close to one side of the inner ring 2, and a spring ring 6 disposed between the retaining ring 5 and the inner ring 2. One end of the spring ring 6 abuts against the inner wall of the retaining ring 5, and the other end abuts against the inner wall of the inner ring 2. The spring ring 6 fixes the inner ring 2 and the retaining ring 5, improving the interchangeability and usability of bearing parts and preventing damage to parts during assembly. The retaining ring 5 serves as a rigid support base for the spring ring 6, transmitting the spring preload to the inner ring 2. The spring ring 6 provides continuous elastic compensation; when the axial clearance of the bearing increases due to temperature rise or wear, the spring ring 6 automatically extends to fill the clearance, maintaining a constant bidirectional preload.

[0033] Meanwhile, the inner ring 2 and the retaining ring 5 are used together and fixed together with the spring ring 6, which improves the interchangeability and utilization of bearing parts, avoids damage to parts when assembling internal components, and only the spring ring 6 needs to be removed when replacing parts. They can be replaced independently without disassembling the entire bearing. The disassembly and assembly are convenient, the operation is simple, and the use is convenient.

[0034] In this embodiment, the spring ring 6 is embedded in the mounting groove 21 formed by the retaining ring 5 and the inner ring 2. The mounting groove 21 restricts the radial or axial displacement of the spring ring 6, preventing the spring ring 6 from centrifugal deformation or misalignment during high-speed rotation, and ensuring that the preload is always transmitted axially.

[0035] In this embodiment, the mounting groove 21 includes: a first groove 211 disposed on the inner ring 2 and a second groove 51 disposed on the retaining ring 5 and symmetrically disposed with respect to the first groove 211. The spring ring 6 is installed inside the first groove 211 and the second groove 51 to ensure that the spring ring 6 can tightly fix the retaining ring 5 and the inner ring 2 together.

[0036] In this embodiment, a retaining edge 11 is provided on the side of the outer ring 1 opposite to the spring ring 6 to achieve bidirectional force, so that the bearing has the ability to withstand bidirectional axial loads. The retaining edge 11 can also prevent the roller 3 from moving axially.

[0037] In this embodiment, the outer diameter surface of the retaining ring 5 exceeds the minimum outer diameter surface of the inner ring 2 and is located close to the retainer 4. The outer diameter surface of the retaining ring 5 and the retainer 4 do not contact each other, that is, they are separated by a certain distance and do not interfere with each other.

[0038] In this embodiment, the cross-section of the spring coil 6 is U-shaped, forming an elastic arch structure to ensure the structural strength of the spring coil 6; two protrusions 61 are provided on the outer diameter surface of the spring coil 6, and a groove 62 is provided in the middle of the two protrusions 61. The protrusions 61 serve as radial positioning keys and are interference-fitted with the first groove 211 and the second groove 51 to prevent the spring coil 6 from moving radially due to centrifugal force when rotating at high speed.

[0039] In this embodiment, the protrusion 61 is adapted to the first groove 211 and the second groove 51 respectively, ensuring that the spring ring 6 can be smoothly installed into the mounting groove 21.

[0040] In this embodiment, the inner diameters of the first groove 211 of the inner ring 2 and the second groove 51 of the retaining ring 5 are larger than the outer diameter of the protrusion 61 of the spring ring 6. More preferably, the inner diameters of the first groove 211 and the second groove 51 are designed to be 69.4 mm, and the outer diameter of the spring ring 6 is designed to be 68.5 mm, forming a gap between them to facilitate the installation of the spring ring 6.

[0041] In this embodiment, the total width of the mounting groove 21 is greater than the width of the spring coil 6. More preferably, the total width of the mounting groove 21 is designed to be 5.6 mm and the width of the spring coil 6 is designed to be 5.2 mm. The width of the mounting groove 21 is less than the width of the spring coil 6 slot 62. More preferably, the width of the mounting groove 21 is designed to be 2.8 mm and the width of the spring coil 6 slot 62 is designed to be 3 mm. The gap between the two facilitates the installation of the spring coil 6.

[0042] In this embodiment, the slot 62 is adapted to the protrusion 22 on the inner diameter surface of both the retaining ring 5 and the inner ring 2. The slot 62 and the protrusion 22 form an axial keyway fit, which suppresses the relative rotation of the spring ring 6 with the retaining ring 5 and the inner ring 2 (especially under vibration conditions) and prevents the preload from being reduced due to fretting wear.

[0043] In this embodiment, the inner diameter of the protrusion 22 inside the inner ring 2 and the retaining ring 5 is smaller than the outer diameter of the slot 62 of the spring ring 6, forming an interference fit. More preferably, the inner diameter of the protrusion 22 inside the inner ring 2 and the retaining ring 5 is designed to be 66.8 mm, the outer diameter of the slot 62 of the spring ring 6 is designed to be 66.9 mm, and the interference is 0.1 mm.

[0044] In this embodiment, the inner diameter of the spring ring 6 is adapted to the inner diameter of the inner ring 2. Preferably, the inner diameter of the inner ring 2 is smaller than the inner diameter of the spring ring 6 to ensure smooth installation of the shaft and not affect the use of the bearing. Preferably, the inner diameters of the inner ring 2 and the retaining ring 5 are designed to be 65mm, and the inner diameter of the spring ring 6 is designed to be 65.3mm to reduce the processing difficulty of the spring ring 6.

[0045] In this embodiment, the spring coil 6 is provided with a notch 63, which is symmetrical along the center line. The notch 63 is similar to an open ring, and the preload can be finely adjusted by adjusting the size of the notch 63, such as to compensate for the clearance difference of different bearings. When the temperature rises, the notch 63 will contract to release the axial stress, preventing the spring coil 6 from seizing the inner ring 2 and causing jamming.

[0046] Of course, the slot 62 is provided with a number of disassembly holes 64 that completely penetrate the spring ring 6. Preferably, two disassembly holes 64 are symmetrically distributed. By inserting a special tool through the disassembly hole 64, the spring ring 6 can be expanded. The spring ring 6 can be replaced or the preload can be adjusted without disassembling other parts on the shaft, thus shortening maintenance downtime.

[0047] In addition, the material of the spring ring 6 is preferably spring steel, and the material grade is generally 65Mn, because spring steel has high structural strength, good wear resistance and corrosion resistance, and long service life, thereby ensuring the service life of the bearing.

[0048] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A novel bidirectional tapered roller bearing, comprising: The outer ring, the inner ring disposed inside the outer ring, and a plurality of rollers disposed between the outer ring and the inner ring are characterized in that they further include: a retainer for separating the rollers, a retainer ring disposed close to one side of the inner ring, and a spring ring disposed between the retainer ring and the inner ring, one end of the spring ring abutting against the inner wall of the retainer ring and the other end abutting against the inner wall of the inner ring.

2. The novel bidirectional tapered roller bearing according to claim 1, characterized in that, The spring ring is embedded in the mounting groove formed by the retaining ring and the inner ring.

3. A novel bidirectional tapered roller bearing according to claim 2, characterized in that, The mounting groove includes: a first groove disposed on the inner ring and a second groove disposed on the retaining ring and symmetrically disposed with respect to the first groove, wherein the spring ring is installed inside the first groove and the second groove.

4. A novel bidirectional tapered roller bearing according to claim 1, characterized in that, A retaining edge is provided on the side of the outer ring opposite to the spring ring.

5. A novel bidirectional tapered roller bearing according to claim 1, characterized in that, The outer diameter of the retaining ring exceeds the minimum outer diameter of the inner ring and is located close to the cage, and the outer diameter of the retaining ring does not contact the cage.

6. A novel bidirectional tapered roller bearing according to claim 3, characterized in that, The cross-section of the spring coil is U-shaped, and two protrusions are provided on its outer diameter surface. A groove is provided in the middle of the two protrusions.

7. A novel bidirectional tapered roller bearing according to claim 6, characterized in that, The protrusions are respectively adapted to the first groove and the second groove.

8. A novel bidirectional tapered roller bearing according to claim 6, characterized in that, The slot is adapted to the protrusions on the inner diameter surfaces of both the retaining ring and the inner ring.

9. A novel bidirectional tapered roller bearing according to claim 1, characterized in that, The spring coil has a notch.

10. A novel bidirectional tapered roller bearing according to claim 6, characterized in that, The slot is provided with several mounting and dismounting holes that completely penetrate the spring coil.

Images