DESC:FORM 2
The Patent Act 1970
(39 of 1970)
&
The Patent Rules, 2003

COMPLETE SPECIFICATION
(See Section 10 and Rule 13)

“SELF-ALIGNING CLUTCH RELEASE BEARING”

TEXSPIN Bearings Limited,
A Company Incorporated under the Indian Companies Act
having address at B-804,
Shapath-4 Opp. Karnavati Club,
S.G.Highway, Ahmedabad, Gujarat, India

The following specification particularly describes the nature of this invention and the manner in which it is to be performed.
FIELD OF INVENTION:

The present invention relates to the self-aligning clutch release bearing. More particularly, the present invention relates to the self-aligning clutch release bearing wherein said clutch release bearing have both self-aligning and self-centering feature in a single mechanism.

BACKGROUND OF THE INVENTION:

Majority of automotive vehicles are equipped with manual or automatic manual transmission system for providing control of speed and torque to the vehicle for different driving conditions. Said control of speed and torque is achieved by altering the gear of transmission. This alteration of gear changes the speed and torque of the vehicle but the engine output remains unchanged. To compensate this change of speed and torque between engine and vehicle a clutch is used to facilitate smooth alteration of gear in transmission systems. Depending on the type of the vehicle, said clutch can be of following types:
• Friction Clutch
• Centrifugal Clutch
• Hydraulic Clutch
• Dog Clutch

Centrifugal clutch mostly used in moped or mini-bike, Hydraulic clutch used in vehicle which is equipped with automatic transmission and dog clutches are very old type of clutch which is obsoleted because of its low life and wearing problem.

When passenger vehicles and goods careers are considered, the type of clutch used is Friction Clutch. There were two types of friction clutch i) Push type and ii) Pull type. The main difference between these two types of clutch is direction of clutch release force. Selection of push and pull type is according clutch design and its packaging dimension. Present invention is related to push type of friction clutch. An illustrative line diagram of typical push type of friction clutch assembly is shown in Fig. 1.

As shown in Fig. 1, typical push type of friction clutch assembly 100 comprises of flywheel 60, engine output shaft 70, clutch 40, clutch bearing 20, fork 30 and driven shaft 50. Said flywheel 60 is rigidly connected to engine output shaft 70 to store the energy of engine in terms of inertia. Said clutch 40 is concentrically mounted on the flywheel 60, to provide disengagement and engagement of output shaft 70 and driven shaft 50 for smooth gear shifting. Said driven shaft 50 is placed concentric with clutch 40. Said clutch bearing 20 is placed between clutch 40 and fork 30 and is concentrically and slide-ably mounted on driven shaft 50.

Said clutch 40 comprises of preloaded diaphragm spring 41 or spring loaded levers (not shown), clutch cover 42, clutch plate 43 and pressure plate 44. Said preloaded spring 41 is connected with clutch cover 42 through pivot point 45, holding said pressure plate 44 through point 46. Said pressure plate 44 is frictionally in contact with clutch plate 43, which is further frictionally in contact with flywheel 60. Said clutch plate 43 is connected with the driven shaft 50 by means of spline 51. Said spline 51 allows relative axial movement of clutch plate 43 and driven shaft 50.

Fig. 1 shows engage condition of engine output shaft 70 and driven shaft 50 wherein the preloaded diaphragm spring 41 applies force on clutch plate 43 by pushing the pressure plate 44 against it. During gear shifting it is require to disengage the driven shaft 50 from output shaft 70 which is done by releasing pressure from clutch plate 43. To release said pressure from clutch plate 43, some axial force must be applied on diaphragm spring 41. The axial force required for releasing clutch plate 43 is known as clutch release force. Applying force on diaphragm spring deflects it from pivot point 45 as shown in Fig. 1 and pull the pressure plate 44 through point 46 to release the clutch plate 43, thereby disengaging driven shaft 50 from engine output shaft 70.

Said disengaging process of driven shaft 50 from engine output shaft 70 is achieved by clutch bearing 20 and fork 30 or hydraulically operated actuation mechanism (not shown). Said fork 30 is actuated by slave cylinder (not shown) or mechanical linkages which further operated by pedal effort to apply clutch release force on clutch bearing 20 which further transfer the axial force to the clutch finger 41 in order to disengage clutch plate 43 from flywheel 60, thereby disengaging the driven shaft 50 from engine output shaft 70 and providing smooth gear shifting.

Said typical clutch 40 suffers from geometrical inaccuracy as result of manufacturing tolerance of its components. Because of manufacturing tolerance there is eccentricity between clutch rotation axis 47 and driven shaft axis 52. To compensate this eccentricity self-centering feature is provided in conventional clutch bearing 20. To provide this self-centering feature static ring 212 of bearing is preloaded by spring 23 and there is a gap c between static ring 212 and sleeve 22 of clutch bearing 20 as shown in Fig. 2. Because of this gap c bearing 21 has tendency to shift under application of radial forces and get in centered with clutch axis 47.

Furthermore, there are two more geometrical inaccuracies in clutch assembly 100,
i. One of the geometrical inaccuracy run-out r of clutch finger 41 is shown in Fig.1 and Fig. 2. This inaccuracy caused by inaccurate fitment of diaphragm spring 41 with clutch cover 42 and cumulative tolerance of all components which are connected with it.

ii. Also because of mounting inaccuracy of clutch 40 and flywheel 60 there is misalignment ? between clutch rotation axis 47 and driven shaft axis 52 as shown in Fig. 1 and Fig. 2.

As mentioned above the clutch bearing 20 suffers from total three geometrical inaccuracies,
1. Eccentricity of rotational axis of clutch and driven shaft 47,57
2. Run-out r of spring 41
3. Misalignment ? of rotational axis of clutch and driven shaft
from which the inaccuracy of eccentricity is compensated in conventional clutch bearing 20 by self-centering feature. Because of remaining two inaccuracies, clutch bearing 20 suffers from unbalanced forces of diaphragm spring 41. Said unbalanced forces create vibrations in clutch bearing, which transferred to the clutch pedal by fork and its actuation mechanism. Said vibration reduces the driver comfort while clutching. Furthermore, said unbalanced forces create noise, wearing of rotating ring and wearing of rolling elements, which results in excessive temperature rise and premature failure of clutch bearing 20.

PRIOR ARTS AND ITS DISADVANTAGES:

To compensate said misalignment ? and run-out r many attempts has been carried out, like:

• German patent DE 102009055659A1 describes a method of manufacturing clutch release bearing which has both self-centering and self-aligning feature in single mechanism by providing spherical face on ring and on support structure. However, this device requires a modified bearing ring which includes extra material and complex machining, thereby increases packaging size d, cost and weight of Clutch release bearing 20.

• German patent DE 102007053180A1 describes a method of manufacturing clutch release bearing which has self-aligning feature by providing spherical rings. However this device comprises of loose spherical ring which leads to noise, vibration and wear of bearing ring.

Therefore, an available prior art teaches about the clutch release bearing that suffers from the disadvantages of loose parts, extra material and extra machining.

OBJECTS OF THE PRESENT INVENTION:

The main object of present invention is to provide a self-aligning clutch release bearing; which compensate the inaccuracy of run-out of diaphragm spring and misalignment of driven shaft in clutch assembly by self-aligning feature.

Another object of present invention is to provide a self-aligning clutch release bearing; which has both self-centering and self-aligning feature in single mechanism.

Another object of present invention is to provide a self-aligning clutch release bearing; wherein said clutch release bearing has more life and temperature rise of which is less, as there were no wearing of its components.

Another object of present invention is to provide a self-aligning clutch release bearing; wherein present self-aligning clutch bearing has same packaging size as conventional clutch bearing.

Another object of present invention is to provide a self-aligning clutch release bearing; wherein present self-aligning clutch bearing do not tilt the sleeve, as a result of which harsh sliding of clutch bearing on driven shaft is eliminated, which reduces the clutch pedal effort and wearing of bearing sleeve.

Another object of present invention is to provide a self-aligning clutch release bearing; wherein present self-aligning clutch bearing absorbs the vibrations caused by the unbalanced forces of diaphragm spring and increases the comfort of driver while clutching

Another object of present invention is to provide a self-aligning clutch release bearing; which does not have any loose parts, thereby reducing wear and vibration of bearing.

Still another object of present invention is to provide a self-aligning clutch release bearing; wherein no major modification required in bearing rings, thereby reduces requirement of extra material and the complexity of machining.

Yet the object of the present invention is to provide a self-aligning clutch release bearing; which has self-aligning and self-centering feature, without providing any major modification in bearing ring, thereby eliminating wear and premature failure bearing.

BRIEF DESCRIPTION OF THE DRAWINGS:

Fig. 1 shows the sectional view of clutch assembly with conventional clutch release bearing

Fig. 2 shows enlarged sectional view of conventional clutch release bearing with inaccuracies of run-out and misalignment

Fig. 3 shows enlarged sectional view of present self-aligning clutch release bearing which compensate inaccuracies of run-out and misalignment

Fig. 4 shows the sectional view of present self-aligning clutch release bearing showing its self-aligning feature

Fig. 5 shows the sectional view of present self-aligning clutch release bearing showing its self-centering feature

Fig. 6 discloses the sectional view of second embodiment of present self-aligning clutch release bearing showing setup to convert conventional clutch release bearing into present self-aligning clutch release bearing

Fig. 7 discloses the sectional view of third embodiment of present self-aligning clutch release bearing showing setup to convert conventional clutch bearing of hydraulically operated actuation mechanism into present self-aligning clutch bearing

Reference numerals used for various parts of the invention:

1 : Present self-aligning clutch release bearing
1A : Second embodiment of self-aligning clutch release bearing
1B : Third embodiment self-aligning clutch release bearing
100 : Clutch assembly
10 : Center point of bearing
11 : Bearing
11A : Bearing for second embodiment
11B : Bearing for third embodiment
111 : Rotation axis of Bearing
112 : Static ring of Bearing
113 : Spherical face of Static ring
114 : Rotating ring of bearing
115 : Rolling element of bearing`
116 : Inner spherical face of static ring
12 : Sleeve
12A : Sleeve of second embodiment
12B : Sleeve of third embodiment
121 : Bush of sleeve
122 : Bracket support
123 : Bracket
124 : Spring stopper
13 : Spherical cup
131 : Spherical face of cup
14 : Spherical ring
141 : Spherical face of ring
15 : Spring
16 : Cover
161 : Outer spherical face of cover
162 : Inner spherical face of cover
17 : Cover for third embodiment
171 : Spherical face of cover
20 : Conventional clutch bearing
21 : Conventional bearing
211 : Rotation axis of Conventional bearing
212 : Static ring of conventional bearing
22 : Conventional sleeve
23 : Spring of conventional clutch bearing
30 : Fork
40 : Clutch
41 : Diaphragm spring
42 : Clutch cover
43 : Clutch plate
44 : Pressure plate
45 : Pivot point on cover
46 : Pivot point on pressure plate
47 : Rotation axis of clutch
50 : Driven shaft
51 : Spline of driven shaft
52 : Rotation axis of driven shaft
60 : Flywheel
70 : Engine output shaft

DETAILED DESCRIPTION OF THE PRESENT INVENTION:

The present invention provides a self-aligning clutch release bearing 1, wherein said self-aligning clutch release bearing further provides both self-centering and self-aligning feature in single mechanism.

Referring to Fig. 3, 4 and 5; which shows main embodiment of the present invention provides a self-aligning clutch release bearing wherein said self-aligning clutch release bearing 1 mainly comprises of:
• Bearing 11
• Sleeve 12
• Spherical cup 13
• Spherical ring 14
• Spring 15

Said bearing 11 comprises of one rotating ring 114 and other static ring 112, between the tracks of which balls 115 is accommodated and allowed to roll between them 114 and 112. Rotating ring 114 and static ring 112 is preferably made from bearing steel and is hardened.

Said sleeve 12 is placed between actuating fork 30 or piston of hydraulic actuation mechanism (not shown) and bearing 11 to provide seating face for fork 30 or piston of hydraulic actuation mechanism.

Said static ring 112 further comprises of spherical face 113 at the bottom side, unlike of prior art without any spherical face. It is very reliable to provide said spherical face 113. Said spherical ring 14 is heat treated. Further said spherical ring 14 is comprises of spherical face 141 to match with spherical face 113 of static ring 112. Both said spherical face 113 and 141 have same spherical radius R2 to allow the tilting of bearing 11 on action of unbalanced forces due to misalignment. The center point 10 of said spherical radius is on the rotational axis 111 of bearing 11. Said spring 15 is placed between stopper 124 of sleeve 12 and spherical ring 14 and is in preloaded condition, thereby applying force on spherical ring 14. As shown in Fig. 4 and 5 there is gap c between spherical ring 13 and bush 121 to provide means of self-centering while working.

Said bearing 11 is placed in spherical cup 13 which is placed on said sleeve 12 having spherical face 131 with radius of R1. Said spherical cup 13 is heat treated. This spherical face 131 also has the same center point 10 as spherical face 141 of spherical ring 14.

There were three components:
i) spherical ring 14,
ii) static ring 112 and
iii) spherical cup 13
are preloaded between spring 15 and sleeve 12, which serves the mechanism self-centering by allowing the bearing 11 to shift as shown in Fig. 5.

Further, these three components have spherical faces 113, 131 and 141 with same center point 10, which allows bearing 11 to tilt about center point 10 by an angle of a. As shown in Fig. 3 this mechanism compensate the run-out r of diaphragm spring 41 and misalignment ? of shaft 50 and matches the rotation axis (47 and 111) of clutch 40 and clutch bearing 1, as shown in Fig. 3, on action of unbalanced forces, yet equally distribute the forces on bearing 11, thereby reduces the wearing of ring, vibrations, noise and premature failure of clutch release bearing 1.

As shown in Fig. 3 said bearing 11 gets tilted by an angle ß, which is cumulative of run-out r and misalignment ? on application of unbalanced forces. This tilting match the clutch rotation axis 47 and bearing rotation axis 111, which aligns the bearing 11 with diaphragm spring 41 and equally distribute the release force on bearing 11.

As shown in Fig. 4 said bearing 11 is allowed to tilt by an angle a as result of self-aligning feature constituted by preloaded spring 15, bearing 11 and spherical cup 13. Said bearing 11 is tilted by unbalanced forces from diaphragm spring as a result of geometrical in accuracies of run-out r and misalignment ?. Tilting of bearing 11 equally distributes release force on bearing ring which helps to reduce wear and rise in temperature.

As shown in Fig. 5 said bearing 11 is allowed to shift on sleeve 12. This shifting requires some amount of radial force on bearing ring 114 as bearing 11 is preloaded under spring 15. The amount of required radial force on bearing ring 114 to shift the bearing 11 is called shifting force. Said shifting force comes from diaphragm spring 41 as a result of geometrical inaccuracy of eccentricity.

OTHER EMBODIMENTS OF PRESENT INVENTION:

i) Second embodiment of present invention:

Second embodiment of the present invention provides present self-aligning clutch release bearing 1A as an improvement of the conventional bearing 11A.

As shown in Fig. 6, said improvement comprises of cover 16. Said bearing 11A is press fitted in cover 16. Said cover 16 comprises of outer spherical face 161 and inner spherical face 162. Said spherical face 161 has radius of R1 which is same as radius of spherical cup 13. Further said spherical face 162 has radius of R2 which is same as radius of spherical ring 14. Said cover 16 is preloaded between spherical cup 13 and spherical ring 14 by spring 15. The center points of said spherical faces are at the same position on point 10. In this embodiment the cover 16 and bearing 11A can tilt about point 10 and compensate the run-out r and misalignment ?. Hence present invention allows one to convert conventional clutch bearing in present Self-aligning clutch bearing 1.

ii) Third embodiment of present invention:

Third embodiment of the present invention provides present self-aligning clutch release bearing 1B as an improvement of the conventional bearing 11B of hydraulic actuation mechanism.

As shown in Fig. 7 bearing 11B comprises of static ring 112 with spherical face 113. The cover 17 for this embodiment is as shown in Fig. 6 comprises of spherical face 171. Said cover 17 is preloaded between spring 15 and spherical ring 14. The center points of said spherical faces 171, 113, 116 and 141 are at the same position on point 10. In this embodiment the bearing 11B can tilt about point 10 and compensate inaccuracies of run-out r and misalignment ?. Hence present invention allows one to convert conventional clutch bearing in present Self-aligning clutch bearing.

The foregoing description of the specific embodiments will so fully reveal the general nature of the embodiments herein that others can, by applying current knowledge, readily modify and/or adapt for various applications such specific embodiments without departing from the generic concept, and, therefore, such adaptations and modifications should and are intended to be comprehended within the meaning and range of equivalents of the disclosed embodiments. It is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation. Therefore, while the embodiments herein have been described in terms of preferred embodiments, those skilled in the art will recognize that the embodiments herein can be practiced with modification within the spirit and scope of the embodiments as described herein.

WORKING OF INVENTION:

1. With the starting of automotive vehicle, the output shaft 70 of engine starts to rotate, which further rotates the flywheel 60 as it is rigidly connected with output shaft 70. The clutch 40 also rotates at same speed of flywheel as they are connected rigidly and concentrically by clutch cover 42. The driven shaft 50 is connected with clutch plate 43 by means of spline 51, which implies that driven shaft also rotates. Further the rotating ring 114 of clutch bearing 1 is in contact with the diaphragm spring 41 of clutch 40 with some preload. Here the rotating ring 114 rotates, while static ring 112 remains stationary as there were balls 115 rolling between them. Said static ring 112 makes the sleeve 12 of clutch bearing 1 to remain stationary as sleeve 12 is connected with static ring 112 by means of preloaded spring 15. The fork 30 is placed on sleeve 12 and is connected with slave cylinder (not shown). So, here fork 30, sleeve 12 and static ring 112 are stationary.

2. At the time of starting of vehicle, the gears are in neutral condition so that gears are not connected with output shaft and vehicle speed is zero. To achieve some speed of vehicle it is requires to change the gears condition from neutral. The driven shaft 50 is connected to the gears.

3. Said assembly of friction clutch 100 has inaccuracies of eccentricity, run-out r and misalignment ?. Because of this inaccuracies said rotating ring 114 of clutch bearing 1 suffers from unbalanced forces from diaphragm spring 41.

4. Applying release force on clutch bearing 1 by fork 30, which is operated by slave cylinder or mechanical linkages (not shown), said diaphragm spring 41 deflects and release clutch plate 43 from flywheel 60.

5. In starting condition of vehicle, clutch 40 and clutch bearing 1 are rotating at speed of engine. So when there is inaccuracy of eccentricity, the clutch 40 applies radial load on rotating ring 114. Through the rotating ring 114, force transmits to the static ring 112 via balls 15. As static ring 112 get the required shifting force, it slides frictionally on sleeve 12 as it is preloaded by spring 115. As the bearing 11 slides on sleeve 12, the rotation axis of bearing and clutch becomes same.

6. To run the vehicle at some speed, driver applies some effort on clutch pedal which is converted to clutch release force by slave cylinder (not shown). Said slave cylinder actuates fork 30 which applies force on clutch release bearing 1. As amount of force increases on clutch bearing 1, the bearing 11 experiences more unbalanced forces as a result of geometrical inaccuracies of run-out r and misalignment ?. Said unbalances forces tilt the bearing 11 about center point 10 as contact faces 131, 113 and 141 has spherical faces.

7. After tilting, the release force equally distributes on bearing ring which reduces noise, vibration, and wear. Further as there were no wear of bearing ring temperature rise is less.

COMPARATIVE TABLE:

Feature Present Invention Conventional/
Prior Art
Self-aligning Present invention have self-aligning feature, which equally distributes the unbalanced forces of diaphragm spring. Conventional clutch bearing do not have self-aligning feature, because of which bearing suffers from unbalances forces
Life Because of equal distribution of forces present clutch bearing has 25-30% more life than conventional As conventional bearing suffers from unbalanced forces, its life is short
Clutching Comfort Because of self-aligning feature, present clutch bearing absorbs the vibration caused by unbalanced forces and increases clutching comfort Conventional clutch bearing do not absorbs vibration caused by unbalanced forces, which reduces clutching comfort.
Wear and Temperature Because of equal distribution of forces, wearing of bearing ring reduces as a result of which rise in temperature is less by 10-15%. As conventional bearing suffers from unbalanced forces, wearing of bearing ring is more as result of which rise in temperature is higher.
Packaging Size Present self-aligning clutch bearing has same packaging size d as of the conventional. Packaging size d is more in case of prior art, as there were extra material required for self-aligning feature.
Complexity Very slight and reliable modification required to convert conventional clutch bearing into present invention. Extra material, extra machining or loose parts required to provide self-aligning feature as described in prior arts, which increases complexity of manufacturing.

From the table and description it is seen that by providing spherical faces to the static ring 121, spherical cup 13 and spherical ring 14, said bearing 11 is allowed to tilt by the center point 10. Said tilting equally distributes unbalanced forces of diaphragm spring 41, which increases life of bearing 11 and reduces wearing of bearing rings. Further, as there were no wear of bearing rings, the rise in temperature is less than conventional bearing 20. Furthermore, because of self-aligning feature present bearing 1 absorbs vibration of diaphragm spring 41, which improves the clutching comfort of driver. Further, comparing with the prior art present invention do not include any extra material or complex machining, instead it require very slight modification in conventional bearing 20. Furthermore, present invention has same packaging size d as of the conventional bearing 20, unlike the prior art having larger packaging size of bearing. So that present invention describes the best way to provide self-aligning and self-centering feature to the clutch bearing, which is very reliable and because of which the life and clutching comfort of driver increases.

ADVANTAGES OF THE INVENTION:

The present invention imparts various advantages over the prior art. Said advantages are listed herein below:

i. Present invention provides self-aligning clutch release bearing; wherein both feature of self-centering and self-aligning feature is provided in single mechanism.

ii. Present invention compensates the inaccuracies of run-out r and misalignment ?, which implies that bearing do not suffer from unbalanced forces. That is why there is no risk of premature failure.

iii. Present invention reduces the harsh sliding of clutch bearing on driven shaft 50, thereby reduces the pedal effort.

iv. Further, present invention absorbs unbalanced forces from diaphragm spring, which increases the clutching comfort of driver.

v. Because of self-aligning feature bearing life increases by 25-30% and rise in temperature is reduced by 10-15%.

vi. Present invention provides self-aligning clutch release bearing; which does not have any loose parts.

vii. It reduces noise and vibration in bearing
,CLAIMS:WE CLAIM:

1) A self-aligning clutch release bearing 1, for self-centering and self-aligning feature in single mechanism; wherein said self-aligning clutch release bearing 1 mainly comprises of:
• Bearing 11,
• Sleeve 12,
• Spherical cup 13,
• Spherical ring 14,
• Spring 15,

wherein, said bearing 11 further comprises of a rotating ring 114, a static ring 112, and balls 115; wherein said balls 115 are accommodated between the tracks of said rotating ring 114 and static ring 112 and are allowed to roll between said rotating ring and static ring 114 and 112; wherein further, said rotating ring 114 and static ring 112 is preferably made from bearing steel and is hardened;

said sleeve 12 is placed between actuating fork 30 or piston of hydraulic actuation mechanism (not shown) and bearing 11 to provide seating face for fork 30 or piston of hydraulic actuation mechanism;

further, said static ring 112 in turn comprises of spherical face 113 at the bottom side,

said spherical ring 14 is heat treated ring; further comprising of spherical face 141 to match with spherical face 113 of static ring 112; wherein both said spherical face 113 and 141 have same spherical radius R2; wherein further, the center point 10 of said spherical radius is on the rotational axis 111 of bearing 11;

said spring 15 is placed between stopper 124 of sleeve 12 and spherical ring 14 and is in preloaded condition, thereby applying force on spherical ring 14. Further there is gap c between spherical ring 14 and bush 121 to provide means of self-centering while working;

2) A self-aligning clutch release bearing 1 as claimed in claim 1; wherein said bearing 11 is placed in said spherical cup 13 which is placed on said sleeve 12 having spherical face 131 with radius of R1.

3) A self-aligning clutch release bearing 1 as claimed in claim 1 and 2; wherein said spherical cup 13 is a heat treated spherical cup.

4) A self-aligning clutch release bearing 1 as claimed in claim 1, 2 and 3; wherein said spherical face 131 has the same center point 10 as spherical face 141 of spherical ring 14.

5) A self-aligning clutch release bearing 1 as claimed in claims 1 to 4; said spherical ring 14, static ring 112 and Spherical cup 13 are preloaded between spring 15 and sleeve 12, which serves the mechanism self-centering by allowing the bearing 11 to shift on sleeve 12 on application of radial forces generated because of geometrical inaccuracy of eccentricity.

6) A self-aligning clutch release bearing 1 as claimed in claims 1 to 5; wherein said spherical ring 14, static ring 112 and Spherical cup 13 have spherical faces 113, 131 and 141 with same center point 10, which allows bearing 11 to tilt about center point 10 by an angle of a.

7) A self-aligning clutch release bearing 1 as claimed in claims 1 to 6; wherein the tilting matches the clutch rotation axis 47 and bearing rotation axis 111, which aligns the bearing 11 with diaphragm spring 41 and equally distribute the release force on bearing 11.

8) A self-aligning clutch release bearing 1A wherein a self-aligning clutch release bearing 1 comprises of cover 16 and said bearing 11A is press fitted in said cover 16; wherein further, said cover 16 comprises of outer spherical face 161 and inner spherical face 162; said spherical face 161 has radius of R1. Further the assembly of cover 16 and bearing 12 is placed on spherical cup 13. Said spherical cup 13 is placed on said sleeve 12 having spherical face 131 with radius of R1.

9) A self-aligning clutch release bearing 1A as claimed in claim 8; wherein said spherical face 162 has radius of R2 which is same as radius of spherical ring 14.

10) A self-aligning clutch release bearing 1A as claimed in claim 8 and 9; wherein said cover 16 is preloaded between spherical cup 13 and spherical ring 14 by spring 15.

11) A self-aligning clutch release bearing 1A as claimed in claim 8 to 10; wherein the center points of said spherical faces 161 are at the same position on point 10.

12) A self-aligning clutch release bearing 1A as claimed in claim 8 to 11; wherein the cover 16 and bearing 11A tilts about point 10 and compensate the run-out r and misalignment ?.

13) A self-aligning clutch release bearing 1A as claimed in claim 8 to 12; wherein the tilting matches the clutch rotation axis 47 and bearing rotation axis 111, which aligns the bearing 11A with diaphragm spring 41 and equally distribute the release force on bearing 11A.

14) A self-aligning clutch release bearing 1B of hydraulic actuation mechanism comprises of a static ring 112 with spherical face 113 and a cover 17 having spherical face 171; wherein further said cover 17 is preloaded between spring 15 and spherical ring 14

15) A self-aligning clutch release bearing 1B as claimed in claim 14; wherein the center points of said spherical faces 171, 113, 116 and 141 are at the same position on point 10.

16) A self-aligning clutch release bearing 1B as claimed in claim 14 and 15; wherein the bearing 11B can tilt about point 10 and compensate inaccuracies of run-out r and misalignment ?.

17) A self-aligning clutch release bearing 1B as claimed in claim 14 to 16; wherein the tilting matches the clutch rotation axis 47 and bearing rotation axis 111, which aligns the bearing 11B with diaphragm spring 41 and equally distribute the release force on bearing 11B.

Dated this 19th day of July, 2017

GOPI J. TRIVEDI (Ms)
(Authorized Agent of the Applicant)
To,
The Controller of Patents,
Patent Office,
Mumbai