A double lip oil seal and bearing

Abstract

The utility model discloses a double -lipped oil seal and bearing, double -lipped oil seal includes: framework, rubber piece is connected in framework, and rubber piece includes main body and the main lip and the secondary lip that set in the main body radial inboard end in proper order, and there is the inter -lip transition area that recesses to radial outside side between main lip and secondary lip, pumping piece is located on the inner peripheral surface of inter -lip transition area, and pumping piece is used to provide an acting force to transport at least partial medium in inter -lip transition area out of inter -lip transition area. Compared with prior art, the utility model discloses that the pumping piece is additionally arranged in the double -lipped oil seal, and the pumping piece rotates with the bearing outer ring in the bearing working process, when the gear box oil permeates from the secondary lip to the inter -lip transition area, the pumping piece can pump the oil back to the gear box cavity, avoids a large amount of gear box oil gathering in the inter -lip transition area and being extruded to the outside by pressure and causes the leakage problem.

Description

Technical Field

[0001] This utility model relates to the field of bearing sealing technology, and in particular to a double-lip oil seal and a bearing. Background Technology

[0002] In related technologies, a bearing is provided at the truck axle. The bearing is used to bear weight and provide precise guidance for the rotation of the wheel hub. The bearing is equipped with a double-lip oil seal. The existing double-lip oil seal has a sealing lip including a main lip and a secondary lip and an interlip transition area located between the main lip and the secondary lip to seal the gearbox oil and keep the grease inside the bearing.

[0003] In existing technology, the secondary lip is not spring-loaded. Gearbox oil can easily seep from the secondary lip into the interlip transition zone between the two lips. When the gearbox oil accumulates to a certain amount in the cavity, under pressure, the gearbox oil collected in the interlip transition zone between the main and secondary lips can be squeezed outward through the main lip, causing leakage. Utility Model Content

[0004] The purpose of this invention is to provide a double-lip oil seal and bearing to solve the technical problems in the prior art. It can drain the gearbox oil collected in the interlip transition area between the main lip and the secondary lip back into the gearbox cavity to reduce leakage.

[0005] In a first aspect, this utility model provides a double-lip oil seal, comprising:

[0006] skeleton;

[0007] A rubber component connected to the skeleton, the rubber component including a main body and a main lip and a secondary lip sequentially disposed at the radially inner end of the main body, the main lip and the secondary lip having a lip transition area recessed radially outward;

[0008] A pumping element is disposed on the inner circumferential surface of the interlip transition zone, the pumping element being used to provide a force to transport at least a portion of the medium within the interlip transition zone out of the interlip transition zone.

[0009] In the double-lip oil seal described above, preferably, the pumping component includes a first part and a second part, the first part and the second part being spaced apart on the inner circumferential surface of the lip transition area, the first part and the second part each having a first end and a second end in the axial direction, a first preset gap in the circumferential direction between the first end of the first part and the first end of the second part, and a second preset gap in the circumferential direction between the second end of the first part and the second end of the second part, the second preset gap being larger than the first preset gap.

[0010] In the double-lip seal described above, preferably, the first part is a block structure extending along a first direction, the second part is a block structure extending along a second direction, the first ends of the first part and the second part are closer to the main lip than the second ends, and there is a preset angle between the first direction and the second direction.

[0011] In the double-lip seal described above, preferably, the preset included angle is 20°-90°.

[0012] In the double-lip seal described above, preferably, the inner circumferential surface of the interlip transition area includes an intersecting first surface and a second surface, wherein the first surface is adjacent to the main lip opening and the second surface is adjacent to the secondary lip opening.

[0013] In the double-lip seal described above, preferably, the first surface and the second surface are inclined in opposite directions and form an angle between 60° and 120°.

[0014] In the double-lip oil seal described above, preferably, the pumping component is disposed on the first surface, the first ends of the first split and the second split are both farther away from the second surface than the second ends, and the second ends of the first split and the second split are both connected to the second surface.

[0015] In the double-lip seal described above, preferably, in its natural state, the diameter of the secondary lip opening is smaller than that of the primary lip opening, and a narrowed interlip waist is formed in the cross-section of the area where the second surface is located, the interlip waist allowing the secondary lip to deform upward when subjected to radially outward pressure.

[0016] In the double-lip oil seal described above, preferably, multiple pumping elements are provided, and the multiple pumping elements are arranged in a ring at intervals.

[0017] Secondly, this utility model provides a bearing, including the aforementioned double-lip oil seal.

[0018] Compared with the prior art, this utility model adds a pumping component inside the double-lip oil seal. During the operation of the bearing, the pumping component rotates together with the outer ring of the bearing. When gearbox oil permeates from the secondary lip into the lip transition area, the pumping component can pump the oil back to the gearbox cavity, thus avoiding the problem of a large amount of gearbox oil accumulating in the lip transition area and being squeezed out by pressure, which would cause leakage. Attached Figure Description

[0019] Figure 1 This is a perspective view of the double-lip oil seal provided in one direction according to an embodiment of the present invention;

[0020] Figure 2This is a perspective view of the double-lip oil seal provided in an embodiment of this utility model from another direction.

[0021] Explanation of reference numerals in the attached figures:

[0022] 10-Skeleton;

[0023] 20-Rubber part, 21-Main body, 22-Main lip, 23-Secondary lip, 24-Interlip transition area, 25-First surface, 26-Second surface, 27-Annular groove, 28-Spring;

[0024] 30 - Pumping component, 31 - First part, 32 - Second part. Detailed Implementation

[0025] The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0026] Reference Figure 1 as well as Figure 2 As shown, an embodiment of this utility model provides a double-lip oil seal, including a skeleton 10, a rubber component 20, and a pumping component 30, wherein:

[0027] The skeleton 10 is fitted inside the outer ring of the bearing. The skeleton 10 provides support and positioning, offering a fixed base structure for the entire double-lip oil seal. It can withstand the forces and pressures from the rubber component 20, friction components, and other components, ensuring the double-lip oil seal can be stably mounted on the bearing's outer ring. The shape and dimensions of the skeleton 10 match the inner surface of the bearing's outer ring to achieve a tight fit. The skeleton 10 is typically designed as a ring or other structure suitable for the bearing's outer ring to ensure uniform support for the entire double-lip oil seal.

[0028] The skeleton 10 is preferably made of metal, such as steel, aluminum alloy or other high-strength metal materials. Metal materials have high strength and rigidity to withstand various forces and vibrations generated during bearing operation, ensuring the stability and reliability of the double-lip oil seal.

[0029] The skeleton 10 and the outer ring of the bearing are statically fitted. After installation, there is no relative movement between the skeleton 10 and the outer ring of the bearing, or only a very small relative movement within a very small range. This avoids the generation of frictional torque, which may cause wear, loosening or damage to the double-lip oil seal, thus affecting the sealing performance. By adopting a static fit, this risk can be effectively reduced, preventing lubricating oil leakage and external impurities from entering the bearing, and extending the service life of the double-lip oil seal.

[0030] The rubber component 20 is connected to the skeleton 10, preferably by a vulcanized connection. The rubber component 20 provides elasticity and sealing performance to accommodate the minor deformations and vibrations generated during the operation of the bearing, while preventing gearbox oil leakage and the entry of external impurities.

[0031] The rubber component 20 includes a main body 21 and a main lip 22 and a secondary lip 23 sequentially arranged at the radially inner end of the main body 21. A radially outward recessed interlip transition zone 24 exists between the main lip 22 and the secondary lip 23. The interlip transition zone 24 can accommodate gearbox oil permeating from the secondary lip 23. The presence of the interlip transition zone 24 also enhances the resistance of the double-lip oil seal to pressure changes or minor leaks. Even if a minor leak occurs between the main lip 22 and the secondary lip 23, pressure changes within the interlip transition zone 24 will slow down the leakage rate.

[0032] The pumping element 30 is disposed on the inner circumferential surface of the lip transition zone 24. The pumping element 30 is used to provide a force to transport at least a portion of the medium (such as gearbox oil) in the lip transition zone 24 out of the lip transition zone 24, thereby effectively reducing the accumulation of gearbox oil in the lip transition zone 24 and preventing seal failure due to excessive gearbox oil.

[0033] In the embodiments provided by this utility model, reference is made to Figure 1 as well as Figure 2 As shown, the pumping component 30 includes a first part 31 and a second part 32. The first part 31 and the second part 32 are spaced apart on the inner circumferential surface of the lip transition area 24. The first part 31 and the second part 32 are arranged in a ring with the axis of the bearing as the center. The first part 31 and the second part 32 have the same shape and size. The first part 31 and the second part 32 both have a first end and a second end in the axial direction. The first end of the first part 31 and the second part 32 are closer to the main lip 22 than the second end.

[0034] There is a first preset gap in the circumferential direction between the first end of the first segment 31 and the first end of the second segment 32, and a second preset gap in the circumferential direction between the second end of the first segment 31 and the second end of the second segment 32. The second preset gap is larger than the first preset gap. When the bearing is working, the rotation of the outer ring of the bearing drives the skeleton 10 and the rubber part 20 to rotate. The pumping part 30 utilizes its structural characteristics and preset gap to generate a pumping effect, thereby delivering the gearbox oil in the lip transition zone 24, preventing the accumulation of the medium, thereby reducing the pressure of the medium on the sealing lip and improving the sealing performance.

[0035] Specifically, the first part 31 is a block structure extending along the first direction, and the second part 32 is a block structure extending along the second direction. Both the first and second directions are inclined relative to the axial extension direction of the bearing. The first end of the first part 31 and the second part 32 are closer to the main lip 22 than the second end. There is a preset angle between the first direction and the second direction.

[0036] The first split body 31 and the second split body 32 are inclined. When the outer ring of the bearing rotates, the first split body 31 and the second split body 32 rotate together. The two opposing surfaces of the first split body 31 and the second split body 32 apply a force to the gearbox oil in the lip transition area 24. This force applies a component force to the gearbox oil towards the secondary lip 23, causing the gearbox oil to move towards the secondary lip 23 side. This pumps the gearbox oil from the sealing surface of the secondary lip 23 back to the gearbox cavity, thereby reducing leakage, preventing the accumulation of gearbox oil in the lip transition area 24, reducing the pressure of gearbox oil on the main lip 22, thereby reducing the wear of the main lip 22, improving the sealing performance, and extending the service life of the double-lip oil seal.

[0037] The preset included angle is 20°-90°, preferably 60°. The first part 31 and the second part 32 have a large included angle so that the first part 31 and the second part 32 have a large projection in the bearing axis direction. The first part 31 and the second part 32 have a large contact surface to push the gearbox oil in the lip transition zone 24. The gearbox oil can be effectively guided and transported, and at the same time, it helps to apply force to the gearbox oil more evenly, avoid local pressure being too high or too low, and further optimize the fluid dynamic performance.

[0038] In one feasible implementation, refer to Figure 1 As shown, the inner circumferential surface of the interlip transition zone 24 includes an intersecting first surface 25 and a second surface 26. The first surface 25 is adjacent to the opening of the main lip 22, and the second surface 26 is adjacent to the opening of the secondary lip 23. The first surface 25 and the second surface 26 are inclined in opposite directions and form an angle between 60° and 120°, preferably 90°. The secondary lip 23 intersects the main lip 22 at an angle. By reducing the contact area of ​​the secondary lip 23, the inclined lip design reduces direct friction, thereby reducing the frictional torque. At the same time, it can automatically compensate for gap changes caused by wear during operation, further enhancing the reliability of the seal.

[0039] The pumping component 30 is located on the first surface 25. The first ends of the first part 31 and the second part 32 are both farther away from the second surface 26 than the second ends. The second ends of the first part 31 and the second part 32 are both connected to the second surface 26. The first part 31 and the second part 32 can thus support the secondary lip 23, prevent the secondary lip 23 from being pressed down by pressure, improve the stability of the secondary lip 23, reduce the risk of leakage caused by deformation of the secondary lip 23, and improve the sealing performance.

[0040] In its natural state, when the double-lip oil seal is not installed on the shaft or subjected to external force, the diameter of the secondary lip 23 is smaller than that of the primary lip 24. This creates a narrowed waist between the lips in the cross-section of the area containing the second surface 26. This waist allows the secondary lip 23 to deform upwards under radially outward pressure. This allows the secondary lip 23 to better adapt to the movement and pressure changes of the shaft during actual operation, thereby improving sealing performance and preventing seal failure due to excessive pressure.

[0041] In the embodiments provided by this utility model, multiple pumping components 30 are provided, and the multiple pumping components 30 are spaced apart in the circumferential direction, so that the pumping components 30 can be evenly distributed in the circumferential direction of the rubber component 20, thereby more effectively applying force to the medium in the interlip transition zone 24.

[0042] Reference Figures 1 to 2 As shown, an annular groove 27 is provided on the side of the main lip 22 away from the interlip transition area 24. A spring 28 is fitted inside the annular groove 27. The design of the annular groove 27 provides a stable installation position for the spring 28, ensuring that the spring 28 will not shift or fall off during operation. The elastic force of the spring 28 is evenly distributed on the main lip 22 through the annular groove 27, making the contact pressure of the main lip 22 more uniform. The additional elastic force provided by the spring 28 compensates for the fatigue loss of the main lip 22, compensates for the wear and deformation of the rubber part 20 during long-term operation, and extends the service life of the double-lip oil seal.

[0043] Based on the double-lip oil seal provided in the above embodiments, the present invention also provides a bearing, which includes an inner ring and an outer ring arranged coaxially. A ball is fixed between the inner ring and the outer ring by a cage. The inner ring and the outer ring are respectively provided with an inner raceway and an outer raceway that cooperate with the outer wall of the ball. The ball rolls between the inner raceway and the outer raceway, so that the outer ring and the inner ring can have relative rotation capability. The aforementioned double-lip oil seal is provided between both ends of the inner ring and the outer ring for sealing.

[0044] By adding a pumping element 30 inside the double-lip oil seal, the pumping element 30 rotates together with the outer ring of the bearing during the bearing operation. When gearbox oil permeates from the secondary lip 23 into the interlip transition zone 24, the pumping element 30 can pump the oil back to the gearbox cavity, thus avoiding a large amount of gearbox oil accumulating in the interlip transition zone 24 and being squeezed out by pressure, which would cause leakage problems.

[0045] The above description, based on the embodiments shown in the drawings, details the structure, features, and effects of this utility model. The above description is only a preferred embodiment of this utility model, but the scope of implementation of this utility model is not limited to what is shown in the drawings. Any changes made in accordance with the concept of this utility model, or modifications to equivalent embodiments, that do not exceed the spirit covered by the specification and drawings, shall be within the protection scope of this utility model.

Claims

1. A double-lip seal, characterized in that, include: skeleton; A rubber component connected to the skeleton, the rubber component including a main body and a main lip and a secondary lip sequentially disposed at the radially inner end of the main body, the main lip and the secondary lip having a lip transition area recessed radially outward; A pumping element is disposed on the inner circumferential surface of the interlip transition zone, the pumping element being used to provide a force to transport at least a portion of the medium within the interlip transition zone out of the interlip transition zone.

2. The double-lip seal according to claim 1, characterized in that, The pumping component includes a first part and a second part, which are spaced apart and sequentially disposed on the inner circumferential surface at the radial inner end of the main body. Both the first part and the second part have a first end and a second end in the axial direction. There is a first preset gap in the circumferential direction between the first end of the first part and the first end of the second part, and there is a second preset gap in the circumferential direction between the second end of the first part and the second end of the second part. The second preset gap is larger than the first preset gap.

3. The double-lip seal according to claim 2, characterized in that, The first segment is a block structure extending along a first direction, and the second segment is a block structure extending along a second direction. The first ends of both the first and second segments are closer to the main lip than the second ends. There is a preset angle between the first direction and the second direction.

4. The double-lip seal according to claim 3, characterized in that, The preset included angle is 20°-90°.

5. The double-lip seal according to claim 2, characterized in that, The inner circumferential surface of the interlip transition area includes an intersecting first surface and a second surface, wherein the first surface is adjacent to the opening of the main lip and the second surface is adjacent to the opening of the secondary lip.

6. The double-lip seal according to claim 5, characterized in that, The first surface and the second surface are tilted in opposite directions and form an angle between 60° and 120°.

7. The double-lip seal according to claim 5, characterized in that, The pumping component is disposed on the first surface, and the first ends of the first part and the second part are both farther away from the second surface than the second ends, while the second ends of the first part and the second part are both connected to the second surface.

8. The double-lip seal according to claim 5, characterized in that, In its natural state, the diameter of the secondary lip is smaller than that of the primary lip. In the cross-section of the area where the second surface is located, a narrowed interlip waist is formed, which allows the secondary lip to deform upward when subjected to radially outward pressure.

9. The double-lip seal according to claim 1, characterized in that, The pumping components are provided in multiple ways, and the multiple pumping components are spaced apart in the circumferential direction.

10. A bearing, characterized in that, Includes the double-lip seal as described in any one of claims 1-9.

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