Special high-speed bearing for textile machinery

Abstract

The utility model relates to a special high-speed bearing for textile machinery in the technical field of bearings, which comprises an outer ring, an inner ring, a retainer, a rolling body and a sealing structure, the sealing structure comprises a sealing element, a mounting part of the sealing element is embedded in a non-bearing area of the inner ring surface of the outer ring, and a lip part is in non-contact sealing fit with the middle part of the non-bearing area of the outer ring surface of the inner ring; the dirt discharge groove is spirally or axially obliquely formed in the non-bearing area of the outer ring surface of the inner ring and located on the axial outer side of the sealing piece, the outlet direction of the dirt discharge groove is opposite to the rotating direction of the inner ring, and the dirt discharge groove is used for guiding away sundries through centrifugal force; according to the utility model, the inner lip and the outer lip of the lip part of the sealing piece and the outer ring surface of the inner ring form two sealing structures in micro clearance fit; and the dirt discharge groove is designed to reversely guide impurities such as fiber chippings away from the bearing cavity through centrifugal force, so that the sealing effect is improved.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and in particular to a high-speed bearing for textile machinery. Background Technology

[0002] As a core transmission component of textile machinery, the operational stability of high-speed bearings directly determines the production efficiency and service life of the equipment. However, textile machinery operates under harsh conditions of high speed, high fiber lint, and drastic temperature and humidity fluctuations, posing the following challenges to the sealing performance of bearings:

[0003] Contamination prevention requirements: Traditional contact seals have the following defects when operating at high speeds: the seals are prone to overheating and aging due to continuous friction; fiber debris enters the sealing interface, exacerbating friction and heating, accelerating lip hardening and cracking, and ultimately leading to seal failure.

[0004] Lubrication control challenges: Traditional non-contact seals have the drawback of easy lubricant leakage due to high-speed centrifugal force during high-speed operation.

[0005] To address this, we designed a high-speed bearing specifically for textile machinery. Utility Model Content

[0006] In order to overcome the shortcomings of the prior art, this utility model discloses a high-speed bearing for textile machinery.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A high-speed bearing for textile machinery includes an outer ring, an inner ring, a cage, rolling elements, and a sealing structure, wherein the sealing structure includes:

[0009] The sealing element has its mounting part embedded in the non-load-bearing area of ​​the inner ring surface of the outer ring, and the lip part forms a non-contact sealing fit with the middle of the non-load-bearing area of ​​the outer ring surface of the inner ring.

[0010] The drain trough is spirally or axially inclined in the non-load-bearing area of ​​the outer ring surface of the inner ring and located on the axial outside of the seal. The outlet direction of the drain trough is opposite to the rotation direction of the inner ring and is used to guide away debris by centrifugal force.

[0011] The guide groove is spirally or axially inclined in the non-load-bearing area of ​​the outer ring surface of the inner ring and located on the axial inner side of the seal. The outlet direction of the guide groove is opposite to the rotation direction of the inner ring and is used to guide the lubricant away by centrifugal force.

[0012] Furthermore, each of the two ends of the outer ring is provided with at least one annular groove and / or annular protrusion, which is used to cooperate with the bearing seat or bearing cover to form a labyrinth seal structure.

[0013] Furthermore, each end face of the inner ring is provided with at least one annular groove and / or annular protrusion, which are used to cooperate with the bearing cap to form a non-contact labyrinth seal structure.

[0014] Furthermore, the lip portion of the seal includes a radially extending inner lip and a radially extending outer lip that is axially outwardly skewed.

[0015] Furthermore, the skew angle of the outer lip is 30-50°.

[0016] Furthermore, a stepped surface is provided in the middle of the non-load-bearing area of ​​the outer ring of the inner ring, and the stepped surface forms a non-contact sealing fit with the inner side of the outer lip.

[0017] Furthermore, the inclination angle of the sewage trough and the guide trough is in the range of 10-15°.

[0018] Furthermore, the depth of the sewage trough and the guide trough is 0.2-0.8 mm, and the width of the trough is 1-3 mm.

[0019] Compared with the prior art, the beneficial effects of this utility model are:

[0020] 1. The sealing structure is formed by the inner and outer lips of the sealing element and the outer ring surface of the inner ring through two micro-gap fits; the design of the drain groove uses centrifugal force to guide impurities such as fiber debris away from the bearing cavity, thereby improving the sealing effect.

[0021] 2. The inclined design of the guide groove generates a centripetal pump effect during high-speed operation, which forces the grease near the lip of the seal to flow back to the raceway, enhancing the lubricant retention rate and reducing the frequency of grease replenishment compared to conventional bearings.

[0022] 3. The design of the annular groove and annular protrusion, when used in conjunction with the bearing seat or bearing cover, provides bidirectional protection against external moisture and other impurities, further improving the sealing effect. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the structure of this utility model;

[0024] Figure 2 for Figure 1 Enlarged view of part I in the image;

[0025] Figure 3 This is a schematic diagram of the inner ring structure in this utility model;

[0026] Figure 4 This is a structural diagram of the present invention in its assembled state.

[0027] In the diagram: 1. Outer ring; 2. Inner ring; 21. Stepped surface; 3. Cage; 4. Rolling element; 5. Sealing structure; 51. Seal; 511. Inner lip; 512. Outer lip; 52. Drain groove; 53. Guide groove; 6. Annular groove; 7. Annular protrusion. Detailed Implementation

[0028] The present invention will be explained in detail through the following embodiments. The purpose of disclosing the present invention is to protect all technical improvements within the scope of the present invention. In the description of the present invention, it should be understood that if terms such as "upper", "lower", "front", "rear", "left", "right" indicate orientation or positional relationship, they are only corresponding to the drawings of this application for the convenience of describing the present invention. It should be understood that if terms such as "end", "side", "end portion", "side part", "lateral", "longitudinal", etc. indicate orientation or positional relationship, they are only corresponding to the length and width of the corresponding component. That is, "end" indicates the head and tail area in the length direction of the corresponding component, and "side part" indicates the head and tail area in the width direction of the corresponding component. They are used for the convenience of describing the present invention and do not indicate or imply that the device or element referred to must have a specific orientation.

[0029] Example 1, in conjunction with Appendix Figure 1-3 A high-speed bearing for textile machinery includes: an outer ring 1, an inner ring 2, a cage 3, rolling elements 4, and a sealing structure 5. The sealing structure 5 is composed of three parts working together:

[0030] The seal 51 has a mounting portion embedded in the non-load-bearing area of ​​the inner ring surface of the outer ring 1; the lip portion includes a radially extending inner lip 511 and a radially extending outer lip 512 that is axially deflected outward (e.g., deflection angle of 30-50°). In this embodiment, the outer lip 512 is deflected at an angle of 45°.

[0031] The outer lip 512 forms a non-contact seal with the stepped surface 23 in the middle of the non-load-bearing area of ​​the outer ring 2 (e.g., a gap of 0.08-0.12mm); the inner lip 511 forms a non-contact seal with the outer ring 2 (e.g., a gap of 0.08-0.12mm). In this embodiment, a gap of 0.1mm is used.

[0032] The drain groove 52 has a spiral groove machined on the non-load-bearing area of ​​the outer ring surface of the inner ring 2 (e.g., an inclination angle of 10-15°, a groove depth of 0.2-0.8 mm, and a groove width of 1-3 mm). It is located axially outside the seal 51, and its outlet direction is opposite to the rotation direction of the inner ring. In this embodiment, the drain groove 52 has an inclination angle of 12°, a groove depth of 0.5 mm, and a groove width of 2 mm. During high-speed operation of the bearing, centrifugal force throws fiber debris and other impurities out along the groove.

[0033] The guide groove 53 has an axially inclined groove (e.g., an inclination angle of 10-15°, a groove depth of 0.2-0.8 mm, and a groove width of 1-3 mm) in the non-load-bearing area of ​​the outer ring surface of the inner ring 2. It is located axially inside the seal 51, and its outlet direction is opposite to the rotation direction. In this embodiment, the guide groove 53 has an inclination angle of 10°, a groove depth of 0.5 mm, and a groove width of 2 mm. During high-speed operation of the bearing, centrifugal force drives the grease near the seal 51 to flow back towards the raceway, preventing grease overflow.

[0034] Example 2, in conjunction with Appendix Figure 1 and 4 A high-speed bearing for textile machinery, based on the technology of Embodiment 1, optimizes the outer ring 1 and inner ring 2 so that only the outer ring 1 is reinforced with a labyrinth seal against the bearing cap or bearing housing.

[0035] The outer ring 1 has at least one annular groove 6 or an annular protrusion 7 on each of its two ends, forming a labyrinth seal with the bearing housing or bearing cover;

[0036] The inner ring 2 has at least one annular groove 6 or annular protrusion 7 on each end face, forming a labyrinth seal with the bearing housing.

[0037] Preferably, each end face of the outer ring 1 and the inner ring 2 is provided with an annular groove 6 and an annular protrusion 7.

[0038] Preferably, the number of annular protrusions 7 on one end face of the outer ring 1 and the inner ring 2 is greater than the number of annular protrusions 7 on the other end face. This allows the assembly direction of the outer ring 1 and the inner ring 2, as well as the installation direction of the bearing, to be quickly identified by the position of the annular protrusions 7.

[0039] Example 3, in conjunction with Appendix Figure 3 A high-speed bearing for textile machinery is described, differing from Embodiment 1 in that both the drain trough 52 and the guide trough 53 are replaced with spiral grooves (e.g., with an inclination angle of 10-15°). In this embodiment, the inclination angle of the drain trough 52 and the guide trough 53 is 15°.

[0040] The parts of this utility model not described in detail are prior art. It is obvious to those skilled in the art that this utility model is not limited to the details of the above exemplary embodiments, and that this utility model can be implemented in other specific forms without departing from the spirit or basic characteristics of this utility model. Therefore, the above embodiments should be regarded as exemplary and non-limiting in all respects. The scope of this utility model is defined by the appended claims rather than the foregoing description. Therefore, it is intended to include all changes that fall within the meaning and scope of the equivalents of the claims in this utility model, and no reference numerals in the claims should be regarded as limiting the content of the claims.

Claims

1. A high-speed bearing for textile machinery, comprising an outer ring (1), an inner ring (2), a cage (3), rolling elements (4), and a sealing structure (5), characterized in that: The sealing structure (5) includes: The sealing element (51) has its mounting part embedded in the non-load-bearing area of ​​the inner ring (1), and its lip part forms a non-contact sealing fit with the middle of the non-load-bearing area of ​​the outer ring (2); The drain trough (52) is spirally or axially inclined in the non-load-bearing area of ​​the outer ring surface of the inner ring (2) and located on the axial outside of the seal (51). The outlet direction of the drain trough (52) is opposite to the rotation direction of the inner ring (2) and is used to guide away debris by centrifugal force. The guide groove (53) is spirally or axially inclined in the non-load-bearing area of ​​the outer ring surface of the inner ring (2) and located on the axial inner side of the seal (51). The outlet direction of the guide groove (53) is opposite to the rotation direction of the inner ring (2) and is used to guide the lubricant away by centrifugal force.

2. The high-speed bearing for textile machinery according to claim 1, characterized in that: The outer ring (1) has at least one annular groove (6) and / or annular protrusion (7) on both ends, which are used to cooperate with the bearing seat or bearing cover to form a labyrinth seal structure.

3. The high-speed bearing for textile machinery according to claim 1, characterized in that: The inner ring (2) has at least one annular groove (6) and / or annular protrusion (7) on both ends, which are used to cooperate with the bearing cover to form a non-contact labyrinth seal structure.

4. The high-speed bearing for textile machinery according to claim 1, characterized in that: The lip portion of the seal (51) includes a radially extending inner lip (511) and a radially extending outer lip (512) that is axially outwardly skewed.

5. A high-speed bearing for textile machinery according to claim 4, characterized in that: The skew angle of the outer lip (512) is 30-50°.

6. A high-speed bearing for textile machinery according to claim 4 or 5, characterized in that: The inner ring (2) has a stepped surface (21) in the middle of the non-load-bearing area of ​​the outer ring surface, which forms a non-contact sealing fit with the inner side of the outer lip (512).

7. A high-speed bearing for textile machinery according to claim 1, characterized in that: The inclination angle of the drain (52) and the guide channel (53) is in the range of 10-15°.

8. A high-speed bearing for textile machinery according to claim 1, characterized in that: The depth of the drain trough (52) and the guide trough (53) is 0.2-0.8 mm, and the width of the trough is 1-3 mm.

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