Clutch release bearing

Abstract

The clutch release bearing comprises a bearing sleeve, and the bearing sleeve is sequentially sleeved with a trapezoidal inner ring and an L-shaped outer ring backwards in the axial direction; a polygonal cavity is axially formed between the trapezoidal inner ring and the L-shaped outer ring; a first retainer is arranged in the polygonal cavity, and a tapered roller is arranged in the first retainer; the L-shaped outer ring, the trapezoidal inner ring, the tapered roller, the first retainer, the first sealing ring and the bearing sleeve form a rotating module of the release bearing, and a traditional radial ball bearing is converted into a thrust tapered roller bearing, so that the bearing capacity is improved by 312% compared with that of the traditional radial ball bearing, and the thrust tapered roller bearing can be used in an extremely heavy load scene; meanwhile, the thrust tapered roller bearing can bear a certain radial load, and the radial load must be smaller than 55% of the axial load; the technical problem that in the prior art, a traditional clutch release bearing is insufficient in load bearing capacity is solved.

Description

Technical Field

[0001] The invention belongs to the field of clutches and relates to a clutch release bearing, in particular to a clutch release bearing. Background Art

[0002] Friction loss: The separation sleeve and guide shaft sleeve are in a state of dry friction or boundary lubrication for a long time. Especially under frequent gear shifting conditions, the contact surface is prone to high temperatures, leading to carbonization of the grease and increased wear of the sliding pair. Test data shows that when the operating temperature exceeds 120°C, the lubrication efficiency of conventional grease decreases by more than 60%.

[0003] Limitations of the lubrication system: Traditional grease-filled lubrication relies on periodic manual maintenance. The friction pair in the inner hole of the sliding sleeve is prone to increased wear due to grease drying. Especially under high temperature or heavy load conditions, the grease is prone to carbonization and failure. The oil filling hole still cannot achieve full coverage lubrication of the ball area.

[0004] Insufficient load-bearing capacity: The axial load-bearing capacity of radial ball bearings is weak. In the frequent clutch operations of commercial vehicles or high-load scenarios of construction machinery, bearing raceway spalling failure is prone to occur, resulting in an average lifespan of only 300,000 to 500,000 cycles.

[0005] Lubrication technology innovation:

[0006] Active lubrication system: An oil storage tank and a controllable valve group are designed to achieve dynamic supply of lubricating fluid, but it relies on rotational centrifugal force to drive and cannot be adapted to non-rotating sleeve scenarios.

[0007] Application of self-lubricating materials: The PEEK self-lubricating material bearings developed by Chongde Technology (2025) reduce grease dependence through the material's self-lubricating properties, but the cost is relatively high and has not yet been widely used in the clutch release bearing field.

[0008] Structural design innovation:

[0009] Split load-bearing module: International manufacturers SKF and Valeo use a removable bearing ring design to improve axial load capacity through preload adjustment, but the complex structure increases maintenance costs by more than 20%.

[0010] Sealing system upgrade: Jishang Automobile uses casting molding technology to reduce the gap between components, but it does not solve the problem of dynamic sealing of reciprocating parts.

[0011] Material surface treatment: Plasma nitriding, DLC coating and other processes are gradually being used in high-end bearings, which can reduce the friction coefficient to below 0.1. However, due to processing costs, the penetration rate is less than 15%.

[0012] Long life demand: The commercial vehicle and construction machinery sectors require that the life of release bearings be increased from the current 500,000 times to more than 1 million times, while traditional technologies only achieve limited improvements (life increase of approximately 30%) through material replacement (such as ceramic rollers).

[0013] Heavy-load adaptability: The increase in torque density of new energy commercial vehicles has led to a 30%-50% increase in axial load, and the existing ball bearing structure urgently needs to break through the load-bearing limit.

[0014] Maintenance-free trend: End users have a strong demand for extended lubrication cycles (>5000 hours), but the oil storage capacity of existing self-lubricating solutions (such as porous oil-containing bushings) is significantly reduced at high temperatures. Summary of the Invention

[0015] In view of the deficiencies in the prior art, the object of the present invention is to provide a clutch release bearing to solve the technical problems of insufficient service life and insufficient load bearing capacity of traditional clutch release bearings in the prior art.

[0016] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0017] A clutch release bearing comprises a bearing sleeve, wherein a trapezoidal inner ring and an L-shaped outer ring are sequentially sleeved on the bearing sleeve in an axially rearward direction; a polygonal cavity is formed between the trapezoidal inner ring and the L-shaped outer ring in an axial direction;

[0018] A first retaining frame is provided in the polygonal cavity, and a tapered roller is provided in the first retaining frame;

[0019] A first sealing ring is provided between the axial front inner wall of the L-shaped outer ring and the axial front outer wall of the trapezoidal inner ring;

[0020] A porous bronze bushing is provided on the inner wall of the bearing sleeve, a second retainer is provided on the inner wall of the porous bronze bushing, and a ball is provided in the second retainer;

[0021] A pair of symmetrically distributed first elastic oil scraping compensation rings and a pair of symmetrically distributed second elastic oil scraping compensation rings are provided at both axial ends of the second retainer; the inner walls of the pair of first elastic oil scraping compensation rings are in contact with the external core shaft, and the outer walls of the pair of second elastic oil scraping compensation rings are in contact with the inner wall of the porous bronze bushing;

[0022] The present invention also includes the following technical features:

[0023] The first elastic oil scraping compensation ring comprises a first polygonal metal ring, the outer edge of the first polygonal metal ring is provided with a first rubber protective sleeve, and the inner wall of the first rubber protective sleeve is sequentially provided with a plurality of first inclined scrapers and first scraper rings distributed at equal intervals;

[0024] The second elastic oil scraping compensation ring includes a No. 2 polygonal metal ring, the outer edge of which is provided with a No. 2 rubber protective sleeve, and the outer wall of the No. 2 rubber protective sleeve is sequentially provided with a plurality of second inclined scrapers and second scraper rings distributed at equal intervals.

[0025] The angles between the first inclined scraper plate and the second inclined scraper plate and the axial direction are both in the range of 60° to 75°.

[0026] The first inclined scraper plate and the second inclined scraper plate are both trapezoidal in shape.

[0027] The included angles between the first scraper ring and the second scraper ring and the axial direction are both 45°.

[0028] The bearing sleeve and the porous bronze bushing are in interference fit.

[0029] A retaining ring is provided on the outer wall of the bearing sleeve, and one end of the retaining ring contacts the inner wall of the L-shaped outer ring; a retaining ring is provided on the bearing sleeve, and the retaining ring contacts the other end of the retaining ring.

[0030] A gradient annular groove is provided on the inner wall of the L-shaped outer ring. The first sealing ring is provided in the gradient annular groove, and an interference fit is formed between the gradient annular groove and the first sealing ring.

[0031] Second sealing rings are provided on the inner walls of both ends of the bearing sleeve.

[0032] The distance c1 between adjacent first inclined scrapers and the distance c2 between adjacent second inclined scrapers are calculated according to the following formula;

[0033]

[0034] in:

[0035] θ is the angle formed by the center of the cross-section circle of the ball and the two ends of the diameter perpendicular to the line connecting the center of the cross-section circle of the external core shaft and the center of the ball in the same plane;

[0036] a is the cross-sectional radius of the external mandrel;

[0037] b is the radius of the ball;

[0038] C1 is the circumference of the circle formed by the connection between the first inclined scraper and the first scraper ring;

[0039] C1 is the circumference of the circle formed by the connection between the second inclined scraper and the second scraper ring.

[0040] Compared with the prior art, the present invention has the following beneficial technical effects:

[0041] (I) The present invention comprises an L-shaped outer ring, a trapezoidal inner ring, a tapered roller, a first retaining frame, a first sealing ring and a bearing sleeve, forming a rotating module of a release bearing, which transforms a traditional radial ball bearing into a thrust tapered roller bearing, thereby increasing the load-bearing capacity by 312% compared with the traditional radial ball bearing and enabling it to be used under extremely heavy load scenarios. At the same time, the thrust tapered roller bearing can also withstand a certain radial load, which must be less than 55% of the axial load. This solves the technical problem in the prior art that the load-bearing capacity of the traditional clutch release bearing is insufficient.

[0042] (II) In the thrust tapered roller bearing of the present invention, which is composed of an L-shaped outer ring, a trapezoidal inner ring, tapered rollers, a first retaining frame and a first sealing ring, the change of the tapered roller 3 is changed from the original elliptical contact to a rectangular contact, which disperses the load on a line (the actual contact area is rectangular), makes the roller contact stress distribution more uniform, and improves the impact load resistance under extreme working conditions; compared with the radial ball bearing that concentrates the load on one point (the actual contact area is elliptical), the maximum contact stress generated by line contact under the same load is much lower than that of point contact, so the thrust tapered roller bearing has lower contact stress and longer life, which solves the technical problem of insufficient life of traditional clutch release bearings in the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Figure 1 It is a cross-sectional schematic diagram of the present invention;

[0044] Figure 2 for Figure 1 A magnified schematic diagram of point A in the middle;

[0045] Figure 3 Schematic diagram of the three-dimensional structure of the first elastic oil scraping compensation ring;

[0046] Figure 4 is a schematic cross-sectional view of the first elastic oil scraping compensation ring;

[0047] Figure 5 Schematic diagram of the three-dimensional structure of the second elastic oil scraper compensation ring;

[0048] Figure 6 is a schematic cross-sectional view of the second elastic oil scraping compensation ring;

[0049] Figure 7 It is a three-dimensional schematic diagram of the present invention.

[0050] The meanings of the various numbers in the figure are: L-shaped outer ring 1, trapezoidal inner ring 2, tapered roller 3, first cage 4, first sealing ring 5, bearing sleeve 6, circlip 7, retaining ring 8, second cage 9, ball 10, first elastic oil scraping compensation ring 11, second sealing ring 12, porous bronze bushing 13, second elastic oil scraping compensation ring 14;

[0051] A first polygonal metal ring 1101, a first rubber protective cover 1102, a first inclined scraper 1103, and a first scraper ring 1104;

[0052] The second polygonal metal ring 1401 , the second rubber protective cover 1402 , the second inclined scraper 1403 , and the second scraper ring 1404 .

[0053] The specific contents of the present invention are further explained in detail below with reference to the embodiments. DETAILED DESCRIPTION

[0054] It should be noted that, unless otherwise specified, all components in the present invention are components known in the art.

[0055] Specific embodiments of the present invention are given below. It should be noted that the present invention is not limited to the following specific embodiments, and all equivalent modifications made on the basis of the technical solution of this application fall within the protection scope of the present invention.

[0056] The present invention discloses a clutch release bearing, comprising a bearing sleeve 6, on which a trapezoidal inner ring 2 and an L-shaped outer ring 1 are sequentially sleeved in an axially rearward direction; a polygonal cavity is formed between the trapezoidal inner ring 2 and the L-shaped outer ring 1 in an axial direction;

[0057] A first cage 4 is provided in the polygonal cavity, and a tapered roller 3 is provided in the first cage 4;

[0058] A first sealing ring 5 is provided between the axial front inner wall of the L-shaped outer ring 1 and the axial front outer wall of the trapezoidal inner ring 2;

[0059] A porous bronze bushing 13 is provided on the inner wall of the bearing sleeve 6, a second retainer 9 is provided on the inner wall of the porous bronze bushing 13, and a ball 10 is provided in the second retainer 9;

[0060] A pair of symmetrically distributed first elastic oil scraping compensation rings 11 and a pair of symmetrically distributed second elastic oil scraping compensation rings 14 are provided at both axial ends of the second retainer 9; the inner walls of the pair of first elastic oil scraping compensation rings 11 are in contact with the external core shaft, and the outer walls of the pair of second elastic oil scraping compensation rings 14 are in contact with the inner wall of the porous bronze bushing 13;

[0061] In the above technical solution, the rotating module of the release bearing is composed of an L-shaped outer ring 1, a trapezoidal inner ring 2, a tapered roller 3, a first retaining frame 4, a first sealing ring 5, and a bearing sleeve 6. The traditional radial ball bearing is converted into a thrust tapered roller bearing, which increases the load-bearing capacity by 312% compared with the traditional radial ball bearing and can be used under extremely heavy load scenarios. At the same time, the thrust tapered roller bearing can also withstand a certain radial load, and the radial load must be less than 55% of the axial load; it solves the technical problem of insufficient load-bearing capacity of the traditional clutch release bearing in the existing technology.

[0062] In addition, the thrust tapered roller bearing composed of an L-shaped outer ring, a trapezoidal inner ring, tapered rollers, a first retaining ring and a first sealing ring, the change of the tapered roller 3 is from the original elliptical contact to a rectangular contact, which disperses the load on a line (the actual contact area is rectangular), makes the roller contact stress distribution more uniform, and improves the impact load resistance under extreme working conditions; compared with the radial ball bearing that concentrates the load on one point (the actual contact area is elliptical), the maximum contact stress generated by the line contact under the same load is much lower than that of the point contact, so the tapered roller bearing has lower contact stress and longer life, which solves the technical problem of insufficient life of the traditional clutch release bearing in the existing technology.

[0063] The first elastic oil scraping compensation ring 11 comprises a first polygonal metal ring 1101, the outer edge of which is provided with a first rubber protective cover 1102, and the inner wall of the first rubber protective cover 1102 is provided with a plurality of first inclined scrapers 1103 and a first scraper ring 1104 distributed at equal intervals.

[0064] The second elastic oil scraper compensation ring 14 includes a second polygonal metal ring 1401, the outer edge of which is provided with a second rubber protective sleeve 1402, and the outer wall of the second rubber protective sleeve 1402 is sequentially provided with a plurality of second inclined scrapers 1403 and a second scraper ring 1404 distributed at equal intervals.

[0065] In the above technical solution, when the first scraper ring 1104 and the second scraper ring 1404 perform oil scraping work, the first inclined scraper 1103 and the second inclined scraper 1403 use the elastic deformation during movement rebound to evenly spread the accumulated grease on the raceway and the porous bronze bushing 13 to prevent fatigue caused by uneven lubrication.

[0066] The included angles between the first inclined scraper 1103 and the second inclined scraper 1403 and the axial direction are both in the range of 60° to 75°.

[0067] In the above technical solution, the axial direction of the inclined scraper can effectively disperse stress to avoid local stress concentration when it is subjected to vertical load or lateral force. When the angle is greater than 75°, it may cause insufficient side stiffness and easy bending and deformation. When the angle is less than 45°, it may cause the bottom to bear excessive tensile stress and easy cracking.

[0068] The first inclined scraper 1103 and the second inclined scraper 1403 are both trapezoidal in shape.

[0069] In the above scheme, the ratio of the upper base to the lower base of the first inclined scraper 1103 and the second inclined scraper 1403 is approximately between 1:2 and 2:3. The trapezoid can transfer the load to the support point more evenly when under pressure, while optimizing the material distribution and thickening the bottom edge so that it can withstand greater bending moment.

[0070] The included angles between the first scraper ring 1104 and the second scraper ring 1404 and the axial direction are both 45°.

[0071] In the above-mentioned technical solution, a 45° bevel design is adopted, and a one-way valve effect is formed through the rigid support of the skeleton. (Due to the high viscosity of the lubricating oil, the opening of the first elastic scraper compensation ring 11 will form a negative pressure when it contacts the shaft surface. This negative pressure will help form a tight seal, scraping the lubricating oil from the shaft surface and preventing it from leaking outward, forming a one-way valve effect.) During axial movement, the first scraper ring 1104 and the core shaft produce slight deformations due to contact and friction, squeezing the grease on the shaft surface, scraping the grease from the raceway surface into the contact area of ​​the ball 10, ensuring that the rolling area is always fully lubricated, improving grease usage efficiency and reducing maintenance frequency. Similarly, the second scraper ring 1404 guides the grease into the small holes of the porous bronze bushing 13.

[0072] The bearing sleeve 6 and the porous bronze bushing 13 are in interference fit.

[0073] A retaining ring 8 is provided on the bearing sleeve 6 , and the retaining ring 8 is in contact with the other end of the retaining ring 7 .

[0074] In the above technical solution, the retaining ring 7 is used to limit the L-shaped outer ring 1 to prevent it from axial displacement; the retaining ring 8 is used to limit and fix the retaining ring 7.

[0075] A gradient annular groove is provided on the inner wall of the L-shaped outer ring 1 , in which a first sealing ring 5 is provided, and an interference fit is formed between the gradient annular groove and the first sealing ring 5 .

[0076] In the above technical solution, the first sealing ring 5 is used to seal the polygonal cavity to prevent lubrication failure and impurities from entering due to oil leakage, thereby extending the life of the bearing.

[0077] Second sealing rings 12 are provided on the inner walls of both ends of the bearing sleeve 6 .

[0078] In the above technical solution, the second sealing rings 12 at both ends of the bearing sleeve 6 are used to achieve sealing between the bearing and the core shaft.

[0079] The spacing c1 between adjacent first oblique scrapers 1103 and the spacing c2 between adjacent second oblique scrapers 1403 are calculated according to the following formula:

[0080]

[0081] in:

[0082] θ is the angle formed by the center of the cross-sectional circle of the ball 10 and the two ends of the diameter perpendicular to the line connecting the center of the cross-sectional circle of the external core shaft and the center of the ball 10 in the same plane;

[0083] a is the cross-sectional radius of the external mandrel;

[0084] b is the radius of the ball 10;

[0085] C1 is the circumference of the circle formed by the connection between the first inclined scraper 1103 and the first scraper ring 1104;

[0086] C1 is the circumference of the circle formed by the connection between the second inclined scraper 1403 and the second scraper ring 1404.

[0087] In the above technical solution, based on the above calculation, the spacing c1 between adjacent first inclined scrapers 1103 and the spacing c2 between adjacent second inclined scrapers 1403 can be determined, ensuring that the spacing matches the ball 10, thereby achieving the purpose of uniform lubrication of the first inclined scraper 1103 and the second inclined scraper 1403.

[0088] See attached Figure 4 Point M is the connection point between the first inclined scraper 1103 and the first scraper ring 1104, and the connection point between the second inclined scraper 1403 and the second scraper ring 1404 can be obtained similarly.

[0089] Example:

[0090] In this embodiment, the deep groove ball bearing is model 6205, and the tapered roller bearing is model 30205. The two have similar dimensions and are typical replacement models of the same specification and have the same application scenarios.

[0091] Inner diameterd(mm) Outer diameter D(mm) Width B (mm) Deep groove ball bearing 6205 25 52 15 Tapered roller bearing 30205 25 52 16.25

[0092] Set radial load F r =10000N, material parameters: equivalent elastic modulus E′=220×10 3 MPa (bearing steel);

[0093] Deep groove ball bearing parameters: number of balls Z b =8; contact angle α b ≈0° (pure radial); ball diameter d b =12mm, ball radius R b =6mm; inner raceway curvature radius R ib =0.52d b =6.24mm (typical value).

[0094] Tapered roller bearing parameters: number of rollers Z r =12; contact angle α r =15°; Roller effective length L = 15mm; Roller average diameter d r =10mm, roller radius R r =5mm; inner ring raceway curvature radius R ir =5.2mm (assumption)

[0095] Single rolling element load (deep groove ball bearing)

[0096]

[0097] Single rolling element load (tapered roller bearings)

[0098]

[0099] Contact stress (deep groove ball bearings):

[0100] Equivalent radius of curvature:

[0101]

[0102] R eq ≈3.06mm

[0103] Maximum contact stress (simplified formula):

[0104]

[0105] Contact stress (tapered roller bearings)

[0106] Equivalent radius of curvature:

[0107]

[0108] R≈2.55mm

[0109] Contact half-width:

[0110]

[0111] Maximum contact stress:

[0112]

[0113] Results comparison:

[0114] parameter Deep groove ball bearings tapered roller bearings Single rolling element load Q 6250N 862N Contact area characteristics Ellipse (point contact) Rectangular strip (line contact) <![CDATA[Maximum contact stress σ max > 1236MPa 890MPa Stress and load relationship <![CDATA[σ∝Q 1 / 3 ]]> <![CDATA[σ∝Q 1 / 2 ]]>

[0115] Under the same load, although the stress of line contact increases faster with load (Q 1 / 2 VSQ 1 / 3 ), but in fact Q r The reduction in stress (only 13.8% of deep groove ball bearings) far exceeds the stress growth effect. Therefore, under the same load, tapered roller bearings have lower contact stress and longer life, making them suitable for heavy load conditions.

Claims

1. A clutch release bearing, characterized in that: The invention comprises a bearing sleeve (6), wherein a trapezoidal inner ring (2) and an L-shaped outer ring (1) are sequentially sleeved on the bearing sleeve (6) in the axial direction and in the rear direction; a polygonal cavity is formed between the trapezoidal inner ring (2) and the L-shaped outer ring (1) in the axial direction; A first retaining frame (4) is provided in the polygonal cavity, and a tapered roller (3) is provided in the first retaining frame (4); A first sealing ring (5) is provided between the axial front inner wall of the L-shaped outer ring (1) and the axial front outer wall of the trapezoidal inner ring (2); A porous bronze bushing (13) is provided on the inner wall of the bearing sleeve (6), a second retainer (9) is provided on the inner wall of the porous bronze bushing (13), and a ball (10) is provided in the second retainer (9); A pair of symmetrically distributed first elastic oil scraping compensation rings (11) and a pair of symmetrically distributed second elastic oil scraping compensation rings (14) are provided at both axial ends of the second retainer (9); the inner walls of the pair of first elastic oil scraping compensation rings (11) are in contact with the external core shaft, and the outer walls of the pair of second elastic oil scraping compensation rings (14) are in contact with the inner wall of the porous bronze bushing (13).

2. The clutch release bearing according to claim 1, characterized in that: The first elastic oil scraping compensation ring (11) comprises a first polygonal metal ring (1101), the outer edge of the first polygonal metal ring (1101) is provided with a first rubber protective sleeve (1102), and the inner wall of the first rubber protective sleeve (1102) is sequentially provided with a plurality of first inclined scrapers (1103) and first scraper rings (1104) distributed at equal intervals. The second elastic oil scraping compensation ring (14) comprises a second polygonal metal ring (1401), the outer edge of the second polygonal metal ring (1401) is provided with a second rubber protective sleeve (1402), and the outer wall of the second rubber protective sleeve (1402) is provided with a plurality of second inclined scrapers (1403) and a second scraper ring (1404) distributed at equal intervals.

3. The clutch release bearing according to claim 2, characterized in that: The angles between the first inclined scraper (1103) and the second inclined scraper (1403) and the axial direction are both in the range of 60° to 75°.

4. The clutch release bearing according to claim 2, characterized in that: The first inclined scraper (1103) and the second inclined scraper (1403) are both trapezoidal in shape.

5. The clutch release bearing according to claim 2, characterized in that: The angles between the first scraper ring (1104) and the second scraper ring (1404) and the axial direction are both 45°.

6. The clutch release bearing according to claim 1, characterized in that: The bearing sleeve (6) and the porous bronze bushing (13) are in interference fit.

7. The clutch release bearing according to claim 1, characterized in that: A retaining ring (7) is provided on the outer wall of the bearing sleeve (6), and one end of the retaining ring (7) contacts the inner wall of the L-shaped outer ring (1); a retaining ring (8) is provided on the bearing sleeve (6), and the retaining ring (8) contacts the other end of the retaining ring (7).

8. The clutch release bearing according to claim 1, characterized in that: A gradient annular groove is provided on the inner wall of the L-shaped outer ring (1), the first sealing ring (5) is arranged in the gradient annular groove, and an interference fit is formed between the gradient annular groove and the first sealing ring (5).

9. The clutch release bearing according to claim 1, characterized in that: Second sealing rings (12) are provided on the inner walls of both ends of the bearing sleeve (6).

10. The clutch release bearing according to claim 1, characterized in that: The spacing c1 between adjacent first inclined scrapers (1103) and the spacing c2 between adjacent second inclined scrapers (1403) are calculated according to the following formula; in: θ is the angle formed by the center of the cross-sectional circle of the ball (10) and the two ends of the diameter perpendicular to the line connecting the center of the cross-sectional circle of the external core shaft and the center of the ball (10) in the same plane; a is the cross-sectional radius of the external mandrel; b is the radius of the ball (10); C1 is the circumference of the circle formed by the connection between the first inclined scraper (1103) and the first scraper ring (1104); C1 is the circumference of the circle formed by the connection between the second inclined scraper (1403) and the second scraper ring (1404).

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