Outer ring split type double-row asymmetric self-lubricating conical bearing

Abstract

The utility model provides an outer ring split type double-row asymmetric self-lubricating conical bearing. The outer ring split type double-row asymmetric self-lubricating conical bearing comprises an inner ring, a first outer ring and a second outer ring, the inner ring is arranged, and the outer side faces of the two ends of the inner ring are the first conical part and the second conical part respectively. And an inner hole of the inner ring is a full-length cylindrical hole. The taper of the outer side face of the first conical part is larger than that of the outer side face of the second conical part, in the field installation process, the first conical part can be installed at the end with large axial force, and large bearing force can be borne through the first conical part. According to the bearing, the second conical part is installed at the end with small axial force, by increasing the inclination angle of the first conical part, when the first conical part is sleeved with the first outer ring, large axial force can be borne, the service life of the end, with large force, of the bearing can be prolonged, and the service life of the bearing can be effectively prolonged in an effective installation space.

Description

Technical Field

[0001] This utility model belongs to the field of split bearing technology, specifically relating to a split outer ring double-row asymmetric self-lubricating tapered bearing. Background Technology

[0002] Split-ring self-lubricating bearings typically consist of an inner ring and two outer rings, with a spacer installed between the two outer rings to adjust the clearance between them. To ensure the bearing's ability to withstand axial forces, the mating area between the inner and outer rings is usually designed with a tapered structure to improve the bearing's axial and radial load capacity. The inclination angle of the tapered contact surface determines the bearing's axial load capacity. However, during use, bearings are often subjected to a larger axial force on one side, which can easily lead to unilateral bearing failure and affect the bearing's normal service life. Utility Model Content

[0003] This utility model provides a split-ring double-row asymmetric self-lubricating tapered roller bearing, which aims to solve the problem of low service life of split bearings in the prior art due to the influence of unilateral axial force.

[0004] To achieve the above objectives, the technical solution adopted by this utility model is: to provide an outer ring split type double row asymmetric self-lubricating tapered roller bearing, comprising:

[0005] The inner ring has a first tapered portion and a second tapered portion at both ends, and the angle between the first tapered portion and the axis of the inner ring is greater than the angle between the second tapered portion and the axis of the inner ring.

[0006] The first outer ring is fitted onto the outside of the first conical part and is rotatably disposed on the outside of the first conical part. The inner hole of the first outer ring is a conical hole with the same angle as the outer shape of the first conical part.

[0007] The second outer ring is fitted onto the outside of the second conical part and is rotatably disposed on the outside of the second conical part. The inner hole of the second outer ring is a conical hole with the same angle as the outer shape of the second conical part.

[0008] In one possible implementation, a spacer is fitted in the middle of the inner ring, and the ends of the first outer ring and the second outer ring abut against the two ends of the spacer, respectively.

[0009] In one possible implementation, the inner ring has a connecting portion at its center for connecting the first tapered portion and the second tapered portion, and the spacer ring is rotatably disposed outside the connecting portion.

[0010] In one possible implementation, the connecting portion is an annular column coaxially disposed with the first tapered portion and the second tapered portion.

[0011] In one possible implementation, the spacer is fitted onto the outside of the connecting portion, and the inner diameter of the spacer is larger than the outer diameter of the connecting portion.

[0012] In one possible implementation, the outer sides of the first outer ring and the second outer ring are cylindrical surfaces coaxially arranged with the first tapered portion and the second tapered portion.

[0013] In one possible implementation, the outer diameters of the first outer ring and the second outer ring are larger than the outer diameter of the spacer ring.

[0014] In one possible implementation, a first conical gasket is slidably connected between the first outer ring and the first conical portion, and a second conical gasket is slidably connected between the second outer ring and the second conical portion.

[0015] The solution shown in this application, compared with the prior art, features an inner ring with a first tapered portion and a second tapered portion on its outer sides at both ends. The inner ring has a continuous cylindrical bore, coaxially aligned with the first and second tapered portions. Furthermore, the taper of the outer surface of the first tapered portion is greater than that of the outer surface of the second tapered portion. During on-site installation, the first tapered portion can be installed at the end subjected to greater axial force, allowing it to withstand a larger load. The second tapered portion is installed at the end subjected to less axial force. By increasing the tilt angle of the first tapered portion, it can withstand a larger axial force when the first outer ring is fitted onto the outside of the first tapered portion, thus extending the service life of the bearing at the end subjected to greater force. Within the effective installation space, this significantly improves the bearing's service life. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the structure of the outer ring split double-row asymmetric self-lubricating tapered bearing provided in an embodiment of the present invention.

[0017] Explanation of reference numerals in the attached figures:

[0018] 1. Inner ring; 11. First conical part; 12. Second conical part; 13. Connecting part; 2. First outer ring; 3. Second outer ring; 4. Spacer; 5. First conical gasket; 6. Second conical gasket. Detailed Implementation

[0019] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0020] Please see Figure 1The present invention provides a split-outer-ring double-row asymmetric self-lubricating tapered bearing. The split-outer-ring double-row asymmetric self-lubricating tapered bearing includes an inner ring 1, a first outer ring 2, and a second outer ring 3. The inner ring 1 has a first tapered portion 11 and a second tapered portion 12 at both ends. The angle between the first tapered portion 11 and the axis of the inner ring 1 is greater than the angle between the second tapered portion 12 and the axis of the inner ring 1. The first outer ring 2 is fitted onto the outside of the first tapered portion 11 and is rotatably disposed on the outside of the first tapered portion 11. The inner hole of the first outer ring 2 is a tapered hole with the same external angle as the first tapered portion 11. The second outer ring 3 is fitted onto the outside of the second tapered portion 12 and is rotatably disposed on the outside of the second tapered portion 12. The inner hole of the second outer ring 3 is a tapered hole with the same external angle as the second tapered portion 12.

[0021] The outer ring split-type double-row asymmetric self-lubricating tapered bearing provided in this embodiment, compared with the prior art, features an inner ring 1 with a first tapered portion 11 and a second tapered portion 12 on its outer surfaces at both ends. The inner ring 1 has a continuous cylindrical bore, coaxially aligned with the first tapered portion 11 and the second tapered portion 12. Furthermore, the taper of the outer surface of the first tapered portion 11 is greater than that of the outer surface of the second tapered portion 12. During on-site installation, the first tapered portion 11 can be installed at the end subjected to greater axial force, allowing it to withstand a larger load. The second tapered portion 12 is installed at the end subjected to less axial force. By increasing the tilt angle of the first tapered portion 11, when the first outer ring 2 is fitted onto the outside of the first tapered portion 11, it can withstand a larger axial force, improving the service life of the bearing at the end subjected to greater force. Within the effective installation space, this significantly extends the bearing's service life.

[0022] Specifically, in this embodiment, the inner ring 1, the first outer ring 2, and the second outer ring 3 are separate assembled bearings, which can be used in working conditions where the precision requirements are not high. At the same time, if one outer ring is damaged, the outer ring can be replaced separately, saving on later maintenance costs.

[0023] Specifically, in this embodiment, the first conical part 11 and the second conical part 12 are coaxially arranged and are integrally formed.

[0024] In some embodiments, the inner ring 1 described above can be as follows: Figure 1 The structure shown. See also Figure 1A spacer 4 is fitted into the middle of the inner ring 1, and the ends of the first outer ring 2 and the second outer ring 3 abut against the two ends of the spacer 4, respectively. The spacer 4 is slidably positioned on the outer side of the inner ring 1 along its axial direction. The spacer 4 allows adjustment of the gap between the first outer ring 2 and the second outer ring 3. When the first outer ring 2 and the second outer ring 3 are subjected to force in a relatively close direction, it helps to limit their relative position. The thickness of the spacer 4 allows for free adjustment of the bearing clearance, enabling adjustment of the spacer 4 thickness according to the requirements of the on-site operating conditions, facilitating on-site installation and use.

[0025] In some embodiments, the inner ring 1 described above can be as follows: Figure 1 The structure shown. See also Figure 1 The inner ring 1 has a connecting portion 13 in its center for connecting the first conical portion 11 and the second conical portion 12. The spacer ring 4 is rotatably disposed outside the connecting portion 13. The inner ring 1 is a one-piece molded structure, including the first conical portion 11, the second conical portion 12, and the connecting portion 13 located between the first conical portion 11 and the second conical portion 12. The connecting portion 13 separates the first conical portion 11 and the second conical portion 12, creating an adjustment gap between the first outer ring 2 and the second outer ring 3, thus facilitating the adjustment of the distance between the first outer ring 2 and the second outer ring 3. It also facilitates the positioning of the spacer ring 4, making on-site installation convenient.

[0026] In some embodiments, the connecting portion 13 may adopt the following form: Figure 1 The structure shown. See also Figure 1 The connecting portion 13 is an annular cylinder coaxially arranged with the first conical portion 11 and the second conical portion 12. The connection point between the outer surface of the connecting portion 13 and the first conical portion 11 and the second conical portion 12 is a rounded chamfer. Furthermore, the projection of the outer surface of the connecting portion 13 along the axis of the inner ring 1 is a circle centered on the axis of the inner ring 1. The two ends of the connecting portion 13 are respectively curved with the first conical portion 11 and the second conical portion 12, facilitating the installation of the spacer 4. Simultaneously, it avoids affecting the adjustment of the relative positions of the first outer ring 2 and the second outer ring 3 during installation, providing sufficient installation space for the first outer ring 2 and the second outer ring 3.

[0027] In some embodiments, the spacer 4 described above can be as follows: Figure 1 The structure shown. See also Figure 1Spacer 4 is fitted onto the outer side of connecting part 13, and the inner diameter of spacer 4 is larger than the outer diameter of connecting part 13. The end of spacer 4 abuts against the middle of the end faces of the first outer ring 2 and the second outer ring 3, and the inner hole of spacer 4 is spaced apart from the outer side of connecting part 13, thereby facilitating on-site assembly of the bearing and adjusting the bearing clearance. When the first outer ring 2 and the second outer ring 3 rotate relative to the inner ring 1, spacer 4 rotates with the first outer ring 2 and the second outer ring 3. The spacer 4 is fitted onto the outer side of connecting part 13, and there is a gap between spacer 4 and the outer wall of connecting part 13, which reduces friction and improves the smoothness of rotation.

[0028] In some embodiments, the first outer ring 2 and the second outer ring 3 may be adopted as follows: Figure 1 The structure shown. See also Figure 1 The outer sides of the first outer ring 2 and the second outer ring 3 are cylindrical surfaces coaxially arranged with the first tapered portion 11 and the second tapered portion 12. The outer surfaces of the first outer ring 2 and the second outer ring 3 are cylindrical structures, and the inner holes of the first outer ring 2 and the second outer ring 3 are tapered holes adapted to the first tapered portion 11 and the second tapered portion 12, respectively. The cylindrical outer surfaces of the first outer ring 2 and the second outer ring 3 facilitate the assembly of the bearings on site.

[0029] In some embodiments, the first outer ring 2 and the second outer ring 3 may be adopted as follows: Figure 1 The structure shown. See also Figure 1 The outer diameters of the first outer ring 2 and the second outer ring 3 are larger than the outer diameter of the spacer 4. This larger outer diameter facilitates the installation of the spacer 4 during on-site assembly and prevents interference between the spacer 4 and the mounting holes of the first outer ring 2 or the second outer ring 3.

[0030] In some embodiments, the first outer ring 2 and the second outer ring 3 may be adopted as follows: Figure 1 The structure shown. See also Figure 1 A first conical gasket 5 is slidably connected between the first outer ring 2 and the first conical portion 11, and a second conical gasket 6 is slidably connected between the second outer ring 3 and the second conical portion 12. The connection between the first outer ring 2 and the second outer ring 3 and their conical portions 12 is achieved using the first conical gasket 5 and the second conical gasket 6. This reduces the overall space occupied by the bearing. Furthermore, the use of gaskets makes on-site installation and use more convenient compared to ball bearing connections. Additionally, the gaskets can be replaced individually after wear, minimizing damage to the outer wall of the inner ring 1 and the inner walls of the first outer ring 2 and the second outer ring 3.

[0031] Specifically, in this embodiment, the first conical gasket 5 and the second conical gasket 6 are made of PTFE material or are processed with copper sleeves.

[0032] Specifically, in this embodiment, the first conical pad 5 is a conical sleeve adapted to the shape of the first conical part 11, and the second conical pad 6 is a conical sleeve adapted to the shape of the second conical part 12.

[0033] 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 double-row asymmetric self-lubricating tapered roller bearing with a split outer ring, characterized in that, include: The inner ring (1) has a first tapered portion (11) and a second tapered portion (12) at both ends. The angle between the first tapered portion (11) and the axis of the inner ring (1) is greater than the angle between the second tapered portion (12) and the axis of the inner ring (1). The first outer ring (2) is fitted on the outside of the first conical part (11) and is rotatably disposed on the outside of the first conical part (11). The inner hole of the first outer ring (2) is a conical hole with the same outer angle as the first conical part (11). The second outer ring (3) is fitted on the outside of the second conical part (12) and is rotatably set on the outside of the second conical part (12). The inner hole of the second outer ring (3) is a conical hole with the same outer angle as the second conical part (12).

2. The outer ring split type double row asymmetric self-lubricating tapered roller bearing as described in claim 1, characterized in that, The inner ring (1) is fitted with a spacer ring (4) in the middle, and the ends of the first outer ring (2) and the second outer ring (3) abut against the two ends of the spacer ring (4).

3. The outer ring split double-row asymmetric self-lubricating tapered roller bearing as described in claim 2, characterized in that, The inner ring (1) has a connecting part (13) in the middle for connecting the first tapered part (11) and the second tapered part (12), and the spacer (4) is rotatably disposed on the outside of the connecting part (13).

4. The outer ring split-type double-row asymmetric self-lubricating tapered roller bearing as described in claim 3, characterized in that, The connecting part (13) is an annular column that is coaxially arranged with the first conical part (11) and the second conical part (12).

5. The outer ring split-type double-row asymmetric self-lubricating tapered roller bearing as described in claim 3, characterized in that, The spacer (4) is fitted on the outside of the connecting part (13), and the inner diameter of the spacer (4) is larger than the outer diameter of the connecting part (13).

6. The outer ring split-type double-row asymmetric self-lubricating tapered roller bearing as described in claim 2, characterized in that, The outer sides of the first outer ring (2) and the second outer ring (3) are cylindrical surfaces coaxially arranged with the first tapered portion (11) and the second tapered portion (12).

7. The outer ring split-type double-row asymmetric self-lubricating tapered roller bearing as described in claim 6, characterized in that, The outer diameters of the first outer ring (2) and the second outer ring (3) are larger than the outer diameter of the spacer (4).

8. The outer ring split-type double-row asymmetric self-lubricating tapered roller bearing as described in claim 1, characterized in that, A first conical pad (5) is slidably connected between the first outer ring (2) and the first conical part (11), and a second conical pad (6) is slidably connected between the second outer ring (3) and the second conical part (12).

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