JPS5848780B2 - clutch release assembly - Google Patents

Description

[Detailed description of the invention] Background of the invention The present invention relates to a clutch release device.

Various types of clutch releases. In other words, there is only one expulsion device so far.
BACKGROUND OF THE INVENTION Drives such as motor vehicles 1 equipped with manual transmissions are used or proposed to be used.

The relatively harsh operating conditions to which the clutch release bearing assembly is subjected during operation are: It encourages continued development of improved designs for aggressive and quiet operation over a long operating life.

The operating conditions to which the clutch release bearing is subjected are relatively harsh. Intermittent loads that these are subjected to. When the clutch assembly is actuated and released, the load and rotational force are applied relatively suddenly. These are the critical lubrication conditions to which they are subjected during operation. Vibration effects due to wear of operating elements. Furthermore, the effect of misalignment of the axis of the clutch release bearing and the axis of rotation of the rotary clutch assembly, which imposes loads on the assembly 1 unequally, is at least partially due.

As a result of continuing development work. Clutch release assembly operating efficiency. The length and lifespan have been significantly improved. Some of these are the axis of the release assembly. A device is provided to provide automatic adjustment for misalignment between the axis of rotation of the clutch and the release member thereon.

In some cases of prior art design. The self-regulatory matching effect is. After the clutch is re-engaged. This happens every time the clutch system operates on the release bearing assembly and returns to the neutral position.

This repeated self-adjustment action and relative movement between elements to correct misalignment conditions increases wear. This correspondingly reduces the effective operating life of the release bearing assembly.

In other prior art structures. At least some of the autoregulatory effects are retained. Some of the shortcomings of other prior art self-aligning clutch release assemblies are overcome.

Unfortunately, clutch release assemblies that incorporate self-aligning features by prior art practice are relatively complex, making them somewhat expensive to manufacture and assemble.

A typical example of these prior art structures is U.S. Patent No.
No. 416637. No. 3815715. No. 387755
No. 7. Third. ．． ．． 9 0 0 0 9 1, No. 402
9186 No. 1 is described.

The clutch release bearing assembly f described in Japanese Patent Application Laid-Open No. 49-125753, etc., includes a component for maintaining the clutch release bearing in the correct position in the radial direction. It has two separate parts, one for maintaining the clutch release bearing in a fixed longitudinal position with respect to the bearing carrier. Therefore, the entire device has a complicated structure.

Therefore, the main purpose of the present invention is. Overcomes many of the problems and drawbacks associated with prior art constructions. Easy to design. Durable and works. It has automatic matching ability. It is an object of the present invention to provide an improved self-aligning clutch release bearing assembly that is economical to make.

SUMMARY OF THE INVENTION The benefits and advantages of the present invention are for automotive power transmission systems, etc.
It was placed approximately coaxially with the rotational axis of the clutch and clutch actuating device. This is accomplished by a self-aligning clutch release bearing assembly 1 of the type that is mounted reciprocally on a guide member such as a transmission support tube.

Clutch release assembly. The clutch pedal of a vehicle equipped with a manual transfer transmission device is connected. A suitable actuating device 1, such as an actuating fork, allows reciprocation along the guide member 1.

The clutch release bearing assembly according to the present invention is as follows. A tubular bearing carrier. and a bearing device supported by this bearing carrier. This bearing device.
Stationary race member. Rotatable race member. It has a plurality of rolling elements inserted between these race members.

This bearing device is mounted with an inner circumferential surface spaced apart from the outer circumferential surface of the bearing carrier by a distance f in the radial direction.

Stationary race members. It has an annular groove extending in a radial direction and having a pair of side walls and an end wall.

and. In this groove E, a spring washer is inserted. One edge of the spring washer is biased and preloaded in the axial direction of the side wall of the groove, and is spaced from the end wall. It thus allows a limited radial movement between the bearing carrier and the bearing arrangement and a limited angular displacement of the axis of said bearing with respect to the axis of the bearing carrier. It's straining.

Furthermore. 1 bearing carrier. A retention device, such as a groove, is provided for receiving a locking connection on the other edge of the spring washer to maintain the spring washer in a fixed longitudinal position.

Therefore. The spring washer has 1 degree flexibility in the axial direction and has a suitable 1 degree biasing ability. Because of that. As soon as the bearing arrangement is able to tilt to a certain extent, it can be held in a fixed position with respect to the axis of the bearing carrier in both the radial and axial directions. Become.

The bearing carrier according to the first preferred embodiment of the invention. Furthermore, a flange protruding in the radial direction is provided at the rear end. The flange is shaped with a radially extending notch for engaging the clutch actuator or fork. This prevents relative rotation of the clutch release assembly after the first clutch actuation cycle. The radial adjustment of the bearing thereby correcting the eccentric misalignment is maintained during the next clutch actuation cycle.

The bearing carrier is shaped like a rolled tubular plate. Preferably, the flange is, for example, folded back and one end thereof is rounded.

The inner surface of the bearing carrier. One or more recesses adapted to receive and retain a reservoir of lubricant are preferably provided to facilitate reciprocating movement of the clutch release assembly along the guide member i.

Another Embodiment 1 of the present invention. The inner race member rotates. The outer race member is stationary.

This is based on type 1 of this example. One area around the outer surface of the outer stationary race member. A groove is formed that extends one inch inward. Inside this groove, the inside of the spring washer is placed. Bearing carrier E limits the relative translational movement of the bearing assembly. Misalignment conditions can be corrected.

The bearing carrier. To hold and support the surrounding area of the Hanewatzscher. An annular housing is provided surrounding the periphery of the stationary race member and placed in spaced apart spaced relation thereto.

Other benefits and advantages of the invention will become apparent from the description of the preferred embodiments, taken in conjunction with the accompanying drawings.

Referring to Figure 1. A clutch release bearing assembly constructed in accordance with one embodiment of the present invention is shown. It has a tubular bearing carrier 6 which is slidably mounted on a guide member 8 shown in phantom lines. This guide member is representative. It has a tubular support that is fixed to the front of a transmission device (not shown) through which a transmission shaft extends and projects forward.

The guide member is arranged such that its axis 10 is substantially coaxial with the axis of rotation of a rotary clutch (not shown). The clutch is shown in Figure 1 f.
It has a clutch release device such as a release finger 12 shown in chain lines.

The automatic alignment of the clutch release bearing assembly will be discussed later. It is intended to compensate for unavoidable misalignments resulting from manufacturing tolerances and assembly techniques. Here, the axis 10 is parallel to the rotational axis of the rotary clutch, but is eccentric. In other words, it is lopsided. The release finger 12 then provides an eccentric misalignment condition. Moreover, the axis 10 is here inclined angularly with respect to the axis of rotation I of the rotary clutch. Release finger 12 is in angular misalignment.

Referring to Figure 1 again. Reduced friction bearing assembly 14
is 1 inch around the tubular bearing carrier 6. The rotating race member 16 is supported in an encircling, radially spaced relationship. This member is formed with a flange 18 extending radially inwardly f at its front end, i.e., to the left in FIG. Its annular outer surface 20 is . It defines a locking surface for cooperating with the end of the clutch release finger 12 during actuation of the clutch device.

The bearing assembly 14 includes a ball 2 inserted between a rotating race member 16 and an inner stationary race member 24.
It has a plurality of rolling elements such as 2.

The bearing assembly 14 is preferably of the inclined contact type in order to withstand an additional thrust force.

The stationary race member 24 is . An axially rearward extension 26 is provided which terminates in a generally radial annular surface 28. This surface 28 is the first
As shown in FIG. 1, it is bent into bearing contact with the end of a clutch actuating device such as an actuating fork 30.

The bearing assembly 14 is . As shown in FIG. 1E, the spring washers 32 are supported or suspended in radially spaced apart and generally concentric relationship about the periphery of the bearing carrier 6. The washer sits with its inner edge in a groove 34 extending around the periphery of the bearing carrier. Relative axial movement between the bearing carrier and the spring washer is prevented.

The width of the groove 34 is approximately one inch larger than the thickness of the spring washer to facilitate assembly.

The inner diameter of the spring washer is. This is only one size smaller than the diameter of the base of the groove 34 in the free stress-free state shown in FIG. As a result, when the spring washer sits in the groove 34, it is in a state where it is pressed once in the peripheral direction. The inner edge grips and engages the bearing carrier to limit relative movement therebetween.

The outer periphery of the spring washer 32 is. An annular groove 3 extending radially inward one circle of a circular hole 38 passing through the stationary race member 24
6 in axially pressed mutually fixed relation.

The annular grooves 36 are a pair of substantially parallel grooves spaced apart in the axial direction.
It is defined by a side wall 40 extending in the radial direction E. The groove terminates at an end wall 42 that defines the depth of the groove.

As you can see in Figure 1, 1. The outer diameter of the spring washer 32 is only 1 IF smaller than the diameter of the end wall 42 of the annular groove 36. A radial gap is provided between them. Its purpose will be discussed later.

Referring to Figure 4. PREFERRED EMBODIMENT 1 OF THE INVENTION The spring washer 32 is as follows. It consists of a spirally wound band of elastic material such as spring steel of approximately constant diameter. This forms multiple fruit layers.

1 piece as shown. The spiral obi.

It has a roughly rectangular cross section. It is then deformed into a waveform having a set of repeating wave crests 44 and wave troughs 46 projecting in the axial direction.

If the spring washer has several overlapping layers according to the arrangement 1 shown in FIG. The arrangement of wave crests and wave troughs in the peripheral direction is. When this is placed in mutually fixed relationship within the annular groove 36 of the stationary race member (FIG. 1). Axial direction 1 Elastic 1
In order to be compressed into an elastic preloaded state. The first layer is offset by one layer from the next layer.

The spring washer 32 in Fig. 4 has one additional length. Installation of release bearing. This is required when assembling. The corrugated layers are allowed to slide relative to each other once from their stress-free state as shown in Figure 4. It is characterized by being able to be elastically deformed to reduce its outer diameter and increase its inner diameter.

Due to the specific arrangement shown in FIG. 1, the spring washer 32
First of all. The spring shear is deformed radially inward to reduce its outer diameter. It is installed in the annular groove 36 of the stationary race member by one stroke so that it can be inserted into the hole through the stationary race member.

The spring washer is next. It is moved along the inside of the hole until it radially expands once and fits within the annular groove 36.

The width of the annular groove is smaller than the axial width of the spring washer. Therefore, during initial assembly, the spring washer E is preloaded somewhat in the axial direction.

Then there's the spring washer. The gap between its periphery and the end wall 42 of the groove causes it to expand in the radial direction. The unflangeed end of the tubular bearing carrier can be inserted.
The spring washers can then be advanced until they fit into the peripheral groove 34 around the bearing carrier in mutually fixed relation.

Wave crest in the wave band that defines the spring wave shear. Adjust the wave bottom appropriately
By placing this. Relative cam cooperation between them occurs during assembly work. This assembly work is performed by preloading the spring washer in the axial direction. The plane in the axial direction. It also includes supporting at high pressure one side of both sides of the side wall 40 defining the groove.

With this preload. What is the axial bearing cooperation between the spring washer and the side wall of the annular groove 36? Bearing assembly 14
are suspended around the bearing carrier 6 in such a way as to limit the relative radial movement between them. In addition to correcting eccentric misalignment conditions. Maintaining the axial position of the rotating race member 16. and also the angular displacement of the bearing assembly with respect to the axis of the bearing carrier. In other words, the diagonal movement is 1 hour. Angular misalignment conditions can be corrected.

Regarding this matter, let us consider the structural characteristics of the spring washer shown in Figure 4. The limit of the axial displacement of the spring washer is obtained in a plane tilted angularly by 1 with respect to the plane perpendicular to the axis of the bearing carrier (E), so that the angle between the axis of the bearing carrier and the axis of rotation of the clutch device is adjustment of the misalignment is obtained.

Due to the above-mentioned elastic suspension device 1. Bearing carrier 61
The radial movement of the bearing assembly 14 in this regard is. From a neutral or concentric position, shown in solid lines, in FIG. Automatically adjusts for eccentricity and angular misalignment.

The axial pressing force applied by the spring washer 32 is.
A bearing assembly and a carrier. During the clutch actuation cycle f. The radially offset position I is maintained so that the adjusted alignment remains as long as it remains valid.

The radial transition force that causes self-adjustment is. This results from the force l exerted on the rotating race member 16J as a result of the engagement of the clutch release finger 12 against its engagement surface 20.

The elasticity of the spring washer is. Quickly corrects any angular misalignment conditions that occur at the beginning of each clutch actuation cycle. And the bearing assembly. After the clutch is re-engaged and the release finger is separated. The axis of rotation is returned to a neutral position E parallel to that of the bearing carrier.

The radial displacement of the bearing assembly 14 with respect to the bearing carrier E is limited by the cooperation between the periphery of the spring washer 32 and the end wall 42 of the annular groove.

Referring to Figure 3 in detail. A tubular bearing carrier 6 is shown constructed in accordance with a preferred embodiment of the invention.

With the specific arrangement shown. The bearing carrier is shaped as a roll insert that can be economically manufactured from a flat metal sheet using a series of stamping operations according to techniques known in the art.

The plate material is preferably steel, but other shapes may be used for this purpose.
It is thought that j2QT function plate material can also be used.

For example, the plate material may be made by laminating two types of metal plates together. Composite structures with bearing material coated along the inner surface f are also contemplated.

This is due to ordinary forming techniques. First of all, the steel plate. Use material of appropriate dimensions. During this time, one E-groove 34 is machined on one side of the plate.

Additionally, suitable grooves or recesses, such as groove 48, are also machined on the opposite side of the plate. The inner surface of the bearing carrier. A lubricant such as grease is held in the form of a film between the guide member and the periphery of the guide member that is mounted on the top. It is also possible to use it as a reservoir for distribution.

Material processing in progress. The opposing edges 50, 52 are each formed with one or more longitudinally spaced droplet-shaped tabs 54 and corresponding droplet-shaped holes 56, which tabs and holes are formed during the next winding operation. One piece is mutually fixed and one piece is wound. This forms a so-called hook butt joint.

Although the material and wrapping structure shown in Figure 3i constitute a preferred embodiment. The tubular bearing carrier is assembled from a single piece of tubular material. It is understood that it can also be machined from a solid bar material.

After the winding operation, the tubular bearing carrier. Final processing work to secure the tab and hole to each other and hook them. Furthermore, it undergoes a folding operation to form a radially projecting flange 58 at one end of the bearing carrier.

When doing turnaround work. A notch or groove 60 shaped like a letter radially and opening outward one corner is formed on the flange. Its sides are defined by the opening of the edges 50, 52 of the initial blank.

■The letter-shaped notch. Clutch actuating device, that is, mutually fixed with the fork. Bearing carrier. This provides the important function of acting as a stop or joint device to prevent relative rotation of the guide member with the suspended stationary race member.

Referring again to FIG. 1, the actuation fork 30 has a rearwardly extending cantilevered spring member 62. This is usually according to the prior art structure. Preload the working fork against the working surface 28 of the bearing assembly. This prevents rattling and noise as a result of vibration.

In the case of the present invention, ■. Cantilever spring 62 is used to install the shape notch.
Fix it with the hanging part. This prevents relative rotation between the bearing carrier and the guide member.

When assembling the clutch release assembly. There is no need to place a diagonal 1-shaped notch in order to fix it to the cantilever spring. The torque applied to the bearing assembly during the first clutch actuation rotates the bearing carrier until the square notch aligns with the spring 62. The clutch release bearing assembly is then held in a fixed position on the guide member.

Figure 1: The arrangement shown in Figure 1. The axial thrust of the actuating fork 30 is not passed through the bearing carrier 6. It is noted that the bearing assembly 141 is directly transmitted.

Referring to FIG. 2, another embodiment of the clutch release bearing assembly is shown. Similar parts are designated here with the same reference numerals as used in FIG.

1 piece as shown. The assembly has a tubular bearing carrier 6'. A bearing assembly 14' is suspended above it. The bearing assembly. It is formed with an outwardly projecting radial flange 18' that defines an engaging surface 20' which is adapted to cooperate with the clutch release device of the rotary clutch assembly.

A plurality of rolling elements, such as balls 22', are inserted between the rotating and stationary race members. Stationary race member 1 is at the rear end. That is, the right end in FIG. 2 has a radial annular surface 28' oriented toward a stabilizing collar or washer 64.

The actuating fork 30' is placed in bearing contact against one opposite side of the stabilizing collar 64. The fork has a cantilever spring 62' which is placed in fixed relationship with one another within a V-shaped groove formed in the radial flange 58'I of the bearing carrier.

The same applies to the embodiment shown in Figure 1. The arrangement in Figure 2 is. Groove 34'
One piece around the bearing carrier 6' is fixed to the other. It also has a spring washer 32' whose peripheral portion presses into contact with the axial surface I of the annular groove 36' in the axial direction E with a preload. Groove 36' is a circular hole 38' passing through stationary race member 24'.
It extends one inch inward.

The arrangement of Figure 2 is similar to that described above with respect to Figure 1. of the axis of the guide member with respect to the axis of rotation of the rotary clutch and the release device thereon. Similar self-alignment adjustments are obtained for eccentric and angular misalignment conditions.

The main difference is the relative placement of the rotating and stationary race members.
A clutch release bearing assembly for heavy loads and high rotational speeds has been obtained. It has a long life under heavy loads.

Installation of the safety collar 64 is optional. It is preferably constructed with a simple steel washer. The washer is placed in an oversized configuration around the periphery of the bearing carrier 6'.

Stabilizing collar 64 is removed after separation of stationary race member 24'. Give support. The arrangement E shown in FIG. 3 thus supports the hook butt joint of the bearing carrier.

Figure 5. Referring to Figure 6. Yet another clutch release bearing assembly is shown. At this point, the outer race member comes to rest. On the other hand, the inner race member is made of conveyor belt. And here is the stationary race member. Unlike the embodiment of FIG. 2 in which the wave spring engages a groove on the inner surface of the stationary race member. It is supported by a wave spring that engages around its periphery.

Figure 5. As shown in Figure 6.1. Clutch release bearing assembly. Tubular member 66. As shown in FIG. 5, an oblong flange 68 is fixed at the rear or right end of the tubular member.
．． It has a bearing carrier consisting of an axially projecting annular housing γ0 containing a bearing assembly γ2.

The inner surface of the tubular member 66 is. Groove 14 and. A plurality of recesses T2 are formed to hold a lubricant such as grease. The recess facilitates the reciprocation of the tubular member along a guide tube (not shown), such as a guide member 8 shown in phantom in FIGS.

The oval flange 68 is press-fitted into a groove at the right end of the tubular member 66 in FIG. 5, and is tightly mounted on the tubular member 66.

The tubular member is provided with a radial annular flange 77 for mounting the plate assembly thereon.

The ends of the flange 68 are bent to form a pair of rearwardly extending tabs or ears 18. Tab 1 is provided with a hole 80 for mounting the bearing carrier on an actuating fork (not shown).

The annular housing 70 is. They extend substantially concentrically and spaced apart about the periphery of the tubular member 66. It is then attached to the flange 68 with a curved tab 82. The knobs 82 are positioned in fixed engagement with each other within recesses 84 shaped along the edges of the flange as shown in FIG.

It is convenient to make flange 6B by punching. It is then shaped to provide two arcuate recesses 86. This recess extends forward of the flange surface. It is adapted to contact the inner edge of stationary race member 88 of bearing assembly 12 to maintain it in proper axial spacing.

The periphery or outer surface of the stationary race member. The inner surface of the annular housing is placed in a radially spaced relationship with respect to the inner surface f of the annular housing. The joint bearing carrier 1 limits radial movement of the bearing assembly.

For this purpose. The outer surface of the stationary race member 88 is formed with an annular groove 90 extending inwardly. In this waveform spring 92
The inner edge of Figure 1. The seating engagement is similar to that described above with respect to FIG.

The inner edge of the wave spring 92 is placed in a clearance relationship with respect to the base of the annular groove 90 to limit radial movement of the bearing assembly with respect to the bearing carrier and to correct eccentric misalignment.

Similarly, a single wave spring can be deformed to allow angular tilting of the bearing assembly. Angular misalignment conditions can be corrected as described above.

The outer edge of the wave spring 92 is placed in a locking and supporting relationship against the inner annular surface 1 of the housing γ0.

As seen in Fig. 5, the outer end, that is, the left end of the housing γ0 is
It has a flange 94 facing inward. This prevents the bearing assembly from accidentally falling out of the housing.

Bearing assembly T2 may be of any type previously described and has a rotating inner race member 96 of a length extending axially f beyond the end of tubular member 66 to define an annular contact surface 98. Surface 98 is adapted to engage the clutch release finger as described above.

The inner surface of the inner race member 96 is spaced apart in radial clearance relationship with respect to the periphery of the tubular member. Radial movement and angular tilting movement of the bearing assembly is compensated for to correct misalignment conditions.

1 as shown in Figure 5. A plurality of rolling elements or balls 1
00 are inserted into stationary and rotationally spaced relationship by cage 1021.

A resilient annular seal 104 is mounted along the forward inner edge of stationary race member 88. It extends radially inwardly in sealing engagement with the periphery of the rotating race member.

Seal 104 serves to retain a suitable lubricant, such as grease, within the bearing assembly.

An annular disk 106 limits contaminants from the inner or right end of the race member from entering the bearing assembly, as shown in FIG.

Figure 5. As can be seen from the arrangement of the bearing assembly shown in FIG. 6, the radial and angular movement of the bearing assembly is... Figure 1. As mentioned above, this is a town Noh performance.

The axial thrust from the working fork coupled to the joint bearing carrier is . It is conveyed directly to the inner end of the stationary race member through an arcuate recess 86 in the flange.

As described above with respect to Embodiment 1 shown in FIG. Spring washer 32. The inner diameter when there is no free stress is. It is only one size smaller than the diameter of the base of the groove 34 of the bearing carrier. So. The spring washer is in a condition in which it is pressed circumferentially when it grips and engages its inner edge around the bearing carrier and is seated in the groove. Limit relative movement between them.

Similarly, Fig. 5. Regarding the embodiment of FIG. 6, the spring washer. The outer diameter in a free and stress-free state is only one size larger than the inner diameter of the annular housing. So. The spring washer is. When this is placed in the housing according to arrangement 1 shown in FIG. This results in a state where the peripheral direction is suppressed. The outer edge then grips into engagement with the housing to limit relative rotational movement therebetween.

Figure 1. According to the arrangement shown in Figure 2.1. spring washer
32 and the bearing carrier 6,6b groove 34 by one more. The end of the wave spring 108 can be provided with an inwardly directed protrusion or serration 110, as shown in FIG. This serration bites into the soft metal surface of the bearing carrier in groove 34.34'M. In other words, it was made to sink. Thus forming a mechanical mutual fixation between them.

The bases of the grooves 34, 34'. In addition to the butt joint coupling tab 54 as seen in Figure 3E, a rough or irregular surface may be provided. Further increases the frictional and mechanical gripping or mutual locking between the wave spring and the bearing carrier. Relative peripheral movement during that time can be prevented.

When the waveform spring 108 of Fig. γ is used in the arrangement of Fig. 5.
A protrusion 110 projects radially outward from the periphery of the spring so as to be recessed into the surface of the annular housing 10 and mechanically secured to each other.

Forming a protrusion on the end of a wave spring is... Before rubbing the wave spring strip material by 1 coil. It is convenient to shape the pieces when cutting them into individual lengths.

γ In place of the protrusion 110 in the embodiment shown in FIG. The wave spring 112 is as shown in FIG. Reduce the radius at the end. Therefore, its sharp inward facing edge 114. It is also possible to design the grooves 34, 34' of the bearing carrier in such a way that the soft metal bases are sunk and mechanically fixed to each other.

An alternative wave spring 116 is shown in FIG. Here the end of the spring has an increased radius. Therefore, its sharp terminal edge 118 protrudes outward by one inch. In the embodiment shown in FIG. 5f, the inner surface E of the annular housing γ0 is bent so that it can be sunk.

Yet another embodiment of a wave spring 120 is shown in FIG. Here, its inner and/or outer edges are provided with a stamped ■-shaped notch. A plurality of inwardly directed protrusions 122 and outwardly directed protrusions 124 are provided circumferentially spaced around the wave spring, thereby providing the structure shown in FIG. Embodiment 1 of FIG. 2 shows the relationship between the groove base of the bearing carrier and the groove base. Alternatively, the respective mechanical gripping action with the inner surface of the annular housing according to the embodiment of FIG. 5 is strengthened.

As above. Spring washer 32, 32', 92, 100
, 88, the bearing device is the bearing carrier 6, 6',
661 As shown by the dashed line in the first interval, the inclination is 1 incline. The bearing arrangement can be fixed not only radially but also longitudinally with respect to the axis of the bearing carrier.

The invention described herein provides the aforementioned benefits. Although it is clear that it is adapted to achieve its advantages. The present invention is. Modifications that do not depart from that spirit. It is recognized that changes can be made.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a self-aligning clutch release bearing assembly constructed in accordance with the present invention, showing a fragmentary view of the operating fork. FIG. 2 is a longitudinal sectional view of a clutch release bearing assembly constructed in accordance with another embodiment of the present invention. Figure 3 is similar to Figure 1. FIG. 2E is a partially cut away perspective view of the bearing carrier of the clutch release assembly shown. Figure 4 is similar to Figure 1. A perspective view of a spring washer that cannot be used in the clutch release assembly of Figure 2. FIG. 5 is a cross-sectional view taken along line 5--5 of FIG. 6 of a clutch release assembly constructed in accordance with another embodiment of the present invention. FIG. 6 is an end view of the clutch release bearing assembly of FIG. 5. Figures γ-10 are front views of a spring washer configured to increase the mutual locking engagement with the bearing carrier. 6...Bearing carrier. 8...Guiding member. 10・
...Axis line. 12...Release finger. 14...Bearing assembly. 16...Rotating race member. 18...flange. 20...External surface. 22... Ball, 24... Stationary race member. 26...Extension part. 28... side. 30・
··fork. 32... Spring washer 34, 36
···groove. 38... hole. 40...Side wall. 42...
End wall. 44... wave crest. 46... Wave bottom. 48... groove, 50, 52... edge. 54...Tab. 56... hole. 58...flange. 60...Groove. 62...Spring. 64...Color 66...Component. 68...flange. γ0...Housing. 72...Bearing assembly. γ4...Groove. 16... recess. TI...
Flange. 18...tab, 80...hole. 82...
tab. 84, 86... recess. 88... Lace member.
90...Groove. 92...Spring. 94...flange.
96... Lace member. 98... sides. 100...ball. 102...Cage. 104...Seal. 10
6...Disk. 108...Spring. 110...Protrusion.
112...Spring. 114... edge. 116...Spring. 118... edge. 120...Spring. 122, 124
···protrusion.

Claims (1)

[Claims] 1. A tubular bearing carrier; and a bearing device supported by this bearing carrier. The bearing device is. Stationary race member. Rotating town Noh lace parts.
A clutch release bearing assembly having a plurality of rolling elements inserted between these race members.
The bearing device is mounted with an inner circumferential surface spaced apart from the outer circumferential surface of the bearing carrier in a radial direction.
The stationary race member has a radially extending annular groove having a pair of side walls and an end wall. An annular spring washer is inserted into the groove. One edge of the spring washer is axially biased and preloaded against the side wall of the groove and spaced apart from the end wall. This allows a limited radial movement between the bearing carrier and the bearing arrangement and a limited angular displacement of the axis of the bearing arrangement with respect to the axis of the bearing carrier. This makes it possible. Furthermore. A retaining device for receiving the other edge of the spring washer in locking relation is provided on the bearing carrier to longitudinally fix the spring washer at a position 1.
The clutch release bearing assembly is designed to maintain this condition. 2 The spring washer. 2. A clutch release bearing assembly as claimed in claim 1 including an anti-rotation device for preventing rotation between said spring washer and said bearing carrier. 3. The rotation prevention device. 2. A clutch release bearing assembly according to claim 2, further comprising at least one protrusion flexibly biased to engage said bearing carrier. 4. A clutch release bearing assembly according to claim 3, wherein said projection is provided at one end of said spring washer. 5. According to claim 2, the anti-rotation device includes a plurality of protrusions spaced apart from one another in the circumferential direction along the other edge of the spring washer facing one side of the bearing carrier. Clutch release bearing assembly as shown. 6 The rotation prevention device. A clutch according to claim 2, characterized in that the corner edge of one end of said spring washer is radially biased from its normal position so as to engage said corner edge with said bearing carrier. Release bearing assembly. γ A retaining device on the bearing carrier. 2. A clutch release bearing assembly as claimed in claim 1 including a groove formed around the outer periphery of the bearing carrier for receiving the other edge of the spring washer in locking relationship. 8 The tubular bearing carrier is... It has a radial flange with a notch extending in the radial direction. The notch is. Claim 1: 1. A clutch release bearing assembly according to claim 1, wherein said clutch release bearing assembly forms a cooperating device for locking engagement with a clutch actuation device to prevent relative rotation of said bearing carrier. . 9. A clutch release bearing assembly according to claim 8, wherein said radial flange is integrally formed with a bearing carrier. 10. The clutch release bearing assembly of claim 8, wherein said notch is generally outwardly V-shaped. 11 The spring washer. It has a corrugated multi-layered band of spirally wound elastic material formed of repeating axially projecting tops and seats. 2. A clutch release bearing assembly as claimed in claim 1, wherein the top of said layer abuts a corresponding seat of an adjacent layer. 12. The clutch release bearing assembly of claim 1, wherein said spring washer is made of spring steel.