KR100627498B1 - Disengagement bearing - Google Patents

Abstract

The present invention relates to a separation bearing for a separation system of a switch separation clutch for use in a vehicle, wherein the bearing ring of the separation bearing surrounds a bearing shell which is formed in two parts and in which a flange is maintained.

Description

Separation Bearings {DISENGAGEMENT BEARING}

The invention will be described in detail with reference to FIGS. 1 to 5:

1 shows a separating bearing according to the invention in a half section with a split outer ring;

2 shows a separate bearing having a split outer ring, in which the bearing shell is integral to the flange;

3 shows a separating bearing according to another embodiment of the invention, wherein the inner ring is divided into two parts along the circumference of the separating bearing;

4 shows an outer ring consisting of two parts with a retaining member fixed to a bearing shell;

5 is an enlarged precision of the separation bearing shown in FIG.

* Sign Description

1a, 1b, 1c, 1d ... separate bearing 2 ... operating member

3 ... bearing ring 4 ... axis of symmetry

5 ... flange 6 ... retaining prosecution

7 ... leaf spring 8 ... end face

9 ... cross-section 10 ... snap-fit nose

11 ... recessed 12a, 12b ... bearing ring

13a, 13b ... flange 14a, 14b ... bearing shell

15 ... spring tongue 16,17 ... arm

18 ... ends 19 ... contacts

20 ... bends 21 ... rolls

22 ... ball face segment 23 ... pressure line

24 ... cylindrical part 25 ... retaining member

26 ... end 27 ... gap

28 ... sealing disc 29,30 ... arm

31 ... sealing gap 32 ... bearing ring

33 ... flange 34 ... bearing shell

35,36 ... Stop 37 ... Positioner

38 ... bearing ring 39 ... retaining prosecution

40 ... ends 41 ... contacts

42,46 ... retaining member 43 ... pressure line

44,49 ... sealing disc 45,50 ... sealing gap

47 ... edge 48 ... spring clip

51,52 ... contact point α ... pressure angle

β ... angle of rotation

R ... radius of ball face segment

The invention relates in particular to a separate bearing for a clutch in an automobile. The device having this structural form is made of one or more bearing rings, bearing shells that rotate at the speed of the clutch, which are firmly mounted to rotate in the sliding sleeve, the roll being received between the two structures and rotating around the same axis of rotation. This displacement of the separation bearing causes deflection of the leaf spring and deflection of the leaf spring controls the connection and disconnection of the clutch. This disconnection action takes place via a manually actuated clutch pedal or an automatic actuation system and in the case of manual actuation the movement of the pedal can be transmitted to the guide tube of the detachable bearing via the Bowden cable and the release lever. Other manual and automatic actuation systems are hydraulically actuated. It consists of a main cylinder and a longitudinal cylinder connected by hydraulic leads. When operating the main cylinder, the equally arranged pressurized fluid is transferred to the longitudinal cylinder via the hydraulic lead, causing the axial movement of the separation bearing.

The structure of the split bearing is almost identical to that of the axial bearing or the inclined ball bearing, each bearing ring comprising an angled flange portion mounted perpendicular to the axis of symmetry of the split bearing. The bearing ring is rotatably connected with the actuating member that can move axially through the flange portion. The leaf spring tongue or release lever of the clutch is supported at the flange portion of the circumferential bearing ring aligned with the clutch.

The bearings have seals to prevent dust and impurities from entering the separation bearings, which prevent lubricants from escaping from the separation bearings.

When installed, the separation bearings may be subjected to tongue shocks, ie axial shocks of the leaf springs, which increase wear on the separation bearings and thus reduce their service life. One condition of the production method and the axial impact caused by the clutch leaf springs causes a problem in sealing and deteriorates comfort in the case of the separation system described above.

Since the separate bearings can wear more and the vibrations reduce their comfort, the two drive components separated by the clutch between the force-transfer axes that must be compensated by the self-centering function of the separate bearings are parallel in the axial direction. It includes a stagger.

Several proposals have been made to compensate for the shortcomings of the axial stagger of the tongue impact and force-transfer axes.

DE U 72 45 141 describes a separate bearing assembly with a center ring mounted between the spring tongue of the leaf spring and the inner ring of the separating bearing. This contact bearing face is made in the form of a sphere between the inner ring and the center ring, which center ring is aligned by sliding movement against the inner ring of the separating bearing. The disadvantage of this method is the lack of radial compensation parallel to the axial direction in the form of radial auto-center so that the force-transfer axis cannot be compensated. And the above-described type of separate bearing may fall around the ball center of the ball-shaped center ring. This is because the separating bearing is mounted along the axial height by means of an elastic ring so that irregular running and hence vibration can be expected. The structure of a separate bearing in the form of a solid structural part made by the stock-removal method requires large space and increased intrinsic weight.

The arrangement of the self-centering separate bearing is shown in US 4 555 007. The outer bearing ring of the separable bearing, which is firmly rotatably mounted, is rotatably fixed to the separable bearing and supported radially movable in the connected housing. The housing is fully engaged outside of the perimeter of the separation bearing and extends axially parallel along the axis of symmetry of the separation bearing, and the outer arm of the housing has a sealing seal at its free end with a radially inward sealing seal in two parts. It forms a labyrinth seal with an inner ring of the configured rolling bearing. This arrangement does not allow displacement and rotational movement of the separating bearing portion to compensate for tongue shock of the leaf spring tongue.

The object of the invention is that the separating bearing can compensate for the tongue impact of the leaf spring tongue and the staggers parallel in the axial direction of the power-transfer axis and the other influences that can contribute to the stagger between the two axes. To make a separate bearing. Separate bearings also take up less space and can be manufactured at lower cost compared to the prior art.

This is achieved by a separate bearing according to the invention, which is guided between the two components as well as between the bearing ring and the rotating bearing shell, which is rigidly mounted on the sliding sleeve, as a roll which rotates around the same axis of rotation. And a region having complementary ball surface segments provided between the leaf spring and the separating bearing included in the clutch, the first region having the ball surface segment being provided directly or indirectly on the leaf spring and having the ball surface segment The two zones are provided directly or indirectly on the separation bearing and the ball surface segment radius of curvature intersects the common axis of rotation provided by the roll of the separation bearing and the separation bearing is centered parallel to the axis of rotation.

It is also advantageous if the components with the ball surface segment can rotate relative to one another without the activation of the resetting forces that can be generated in the turning area via stops.

The structure of the separating bearing according to the invention provides a bearing ring formed in two parts, in which the clutch leaf spring or leaf spring tongue of the friction clutch is supported. The circumferential bearing ring has a bearing shell for guiding the roll and a flange supported on the bearing shell and interacting with the spring tongue, the flange and the bearing shell forming complementary ball surface segments. The bearing ring portion forming the support flange is separated from the component to which the roll is guided. With the bearing ring divided according to the invention, a single adjustment of the divided bearing ring, ie the movement of the flange relative to the bearing shell, takes place in the installed state with the axial impact of the clutch leaf spring, which is a production method condition. The forcing accompanying by the axial impact is kept away from the separate bearing, thus achieving optimal round running of the rolling bearing.                         

The self-adjusting rotary bearing ring of the separation bearing according to the invention effectively prevents the undesirable separation of the clutch accompanying from axial impact. The structure of the bearing ring made of two parts according to the invention can be used for the pulling and pressing action of the friction clutch.

The present invention includes a closed separate bearing, i.e. a closed piece arranged on each side of the roll. This prevents impurities from entering the interior of the separating bearing, ie the guide track of the rolling bearing. At the same time, the closed charge prevents the lubricant from flowing out of the separation bearing.

Other improvements are provided so that the free end of the sealing disc can be guided to the flange while maintaining the sealing gap so that the sealing disc can be mounted to the bearing ring to seal the interior of the separating bearing.

The sealing disc can be made without cutting into sheet metal and has an L-shaped cross section so that the short arms can be aligned on the cylindrical arms under pretension while keeping the ring gap radial in the direction of the bearing ring.

The component part of the circumferential bearing made of two parts is supported at the bent contact area. When a tilting force is applied from the clutch leaf spring to the flange of the bearing ring, a constant movement occurs with respect to the bearing ring. Curved contact areas should be made of a material suitable for the amount of force generated and the materials used should be considered, which reduces wear and extends service life.

The compensating function according to the invention of the divided circumferential bearing ring enables the optimal transmission of the force, which has a positive effect on the service life of the separate bearing. This action is achieved by dividing the bearing ring into a bearing shell to guide the roll and by dividing the bearing ring into the flange portion where the spring tongue of the clutch leaf spring is guided. The bearing shell includes a contact area on a face spaced from the track of the roll, the flange being supported at the contact area. In addition to the flanges, the bearing shells are made complementary to the ball segments in the contact area and are arranged concentrically with each other so that in the installed position the flanges can slide along the curvature in the bearing shells. Since the bearing shell and flange portion each form a ball segment of the contact area, the self-adjustment of the two-part circumferential bearing ring is improved. This configuration allows the flange to slide more easily as required along the curved contact bearing face on the bearing shell when axial or spring tongue impact occurs.

Another form of the present invention provides a bearing shell having a thin wall made of steel without cutting and inserted into a flange portion surrounding the bearing shell. The flange portion has a positioning portion that is adapted to the outer curvature of the bearing shell and forms a contact area that allows the flange to slide along the curvature of the bearing shell.

A rotation angle β of ± 10 degrees, preferably ± 1.5 degrees, is sufficient as the angle by which the flange can rotate relative to the bearing shell in the case of a circumferential bearing ring divided according to the invention. The present invention includes a contact area treated with anti-friction means as a support means that allows the flange to slide in the bearing shell with reduced friction.                         

According to the invention the inner bearing ring or the outer bearing ring is formed as a divided circumferential bearing ring. The invention does not affect the placement of the area with the ball surface segment and the installation position of the bearing ring of the separating bearing. For example, an area with a second ball face segment may be formed from a bearing shell, and an area forming the ball face segment may be disposed radially inward or outward along the circumference formed by the roll and the first ball face segment The region with can be formed out of the flange or directly in the leaf spring.

The present invention relates to the position of the contact between the bearing shell and the flange portion. It is arranged in accordance with the invention in the projection of the pressure line and the projection of the pressure line connects the bearing spring securely mounted so as to rotate with the two contact points of the roll on the bearing shell and extends through the center point of the roll so that the radius of curvature is Intersect the axis of rotation defined by the roll. This bearing transfers the force from the flange portion to the separate bearing.

As a preferred embodiment the invention comprises a bearing shell which surrounds the ball-shaped roll at an angle of less than 100 degrees. The flange, in turn, completely surrounds the bearing shell. A stop is provided in the locator of the flange spaced from the end of the bearing shell to limit the rotational movement of the flange portion with respect to the bearing shell with a thin wall.

The present invention includes a method of making a pre-assembled separate bearing. A retaining member is used for this purpose, the retaining member being fixed to the bearing ring, which can be easily moved and engaged around the bearing ring so as to be connected by a key. It is possible to obtain a separate bearing unit which cannot be lost with the retaining member according to the invention, through which the assembly can be simplified and cost-effectively stored.

According to the invention the separate bearing comprises a bearing ring which can be made of sheet metal without cutting, for example by a deep drawing process, can be mass produced in a cost effective and reliable process. The same prerequisites apply to making and using all the remaining components, for example retaining members.

According to a preferred embodiment of the invention it is proposed to fix the retaining member or retaining ring to the rotatably fixed bearing ring of the separate bearing. The free end of the retaining member surrounds the cross section of the circumferential bearing ring while maintaining a constant ring gap. The free end of the retaining member is radially spaced and follows the outer contour of the radial stepped cross section of the bearing ring, so that the two bearing rings are firmly fixed in order to make a pre-assembled unit of the totally separated bearing. The retaining member serves to seal the gap between the bearing rings, effectively preventing all kinds of dust and impurities from entering the separation bearing.

Another example of the invention provides a retaining member fixed to a flange or bearing shell of a divided bearing ring and the free end engages the connected components of the divided bearing ring. This type of retaining member has radially aligned edges which engage radially with respect to the free end of the bearing ring to provide a preassembly unit.

Suitable retaining members are preferably components made of sheet metal without cutting by the deep drawing process. For fixing, this structural part can be fixed by press fit or welding. In the installed state the retaining member has sufficient elasticity so that the radial stepped section can be radially discharged and positively secure each component during assembly of the bearing ring.

The present invention includes a sealing piece mounted on the face of the roll away from the retaining member to provide a seal on both sides of the separate bearing interior space. Sealing discs are suitable for this, which are rigidly mounted to allow the bearing to rotate and are guided to the opposite bearing ring while maintaining a constant ring clearance. This type of sealing disc is a component made of sheet metal without cutting and having an L-shaped cross section. The short arm of the sealing disc is supported in a bearing ring firmly mounted to be able to rotate under pretension. The long arm of the sealing disc connects the distance between the two bearing rings. In order to obtain a labyrinth such as a sealing gap between the sealing disc and the rotating bearing ring, the free end of the sealing disc is mounted parallel to the vertically aligned cross section of the rotating bearing ring. This form extends into the sealing gap, increasing the sealing efficiency.

According to another idea of the invention, a separate bearing is proposed in which the bearing shell and the flange are linearly contacted and shaped into components supported against each other. The displacement and rotational movement of the flange relative to the bearing ring is on the curvature of the bearing ring forming a linear guide.

1 shows a separating bearing 1a fixed to an actuating member 2 which can be moved axially. This separating bearing 1a consists of an inner bearing ring 3 which is rigidly connected to the actuating member so as to be rotatable. The bearing ring 3 comprises a flange which is vertically aligned, ie extending at right angles to the axis of rotation 4 and supported in a retaining inlet 6 formed of sheet metal. The leaf spring 7 sandwiched between the flange 5 and the inner cylindrical section of the retaining prosthesis 6 is used to make a force-fixed bearing of the flange 5 with respect to the retaining prosthesis 6. The retaining element 6 adjacent the end face 8 of the actuating element 2 is engaged with the outer cylindrical cross section 9 around the end of the actuating element 2 and positively fixed to engage the actuating element 2. Is engaged with the snap-fitting nose 10 with the radial recess 11. The circumferential outer bearing ring 12a consists of two components: the flange 13a and the bearing shell 14a.

This flange 13a forms two arms 16, 17 arranged at right angles to each other. The vertically arranged arm 16 serves to support the spring tongue 15, which is connected with a friction clutch, not shown in FIG. 1. The arm 17 angled against the spring tongue 15 has a radially outwardly rounded end 18 and is supported therein on the bearing shell 14a through the contact surface 19. This contact surface 19 is arranged outward in the region 20 of the bearing shell 14a having the ball surface segment so that the radius R of the ball surface segment intersects the axis of rotation 4. Because of the inner shape of the end 18 formed complementary to the curvature 20, the flange 13a and the bearing shell 14a form a ball segment 22. The contact surface 19 and the pressure line 23 of the separation bearing 1a are suitably positioned in place to apply a direct force and prevent the forcing. This pressure line 23 is determined by the pressure angle α of the separating bearing 1a. Because of the divided arrangement of the bent contact region 19 and the bearing ring 12a according to the invention, the flange 13a has a certain degree of freedom so that it can be aligned when there is an axial impact of the spring tongue 15. And the bearing shell 14a can achieve a specific displacement corresponding to the swing area β, which can be characterized by a double arrow.

The inner bearing ring 3, which is securely mounted in rotation, forms a cylindrical portion 24 at the end spaced from the flange 5 to which the retaining member 25, which is shaped from sheet metal, is fixed. This completely surrounds the separation bearing 1a so that the end 26 of the retaining member 25 is inclined radially inward and is secured while keeping the parts of the separation bearing 1a safe from loss. Cover 18 radially. The retaining member 25 is mounted radially spaced apart from the bearing shell 14a and the flange portion 13a in the state where the separate bearing 1a is installed. The retaining member 25 also covers the gap 27 between the bearing shell 14a and the bearing ring 3 and prevents dust and impurities from entering the separation bearing 1a. The bearing ring 3 is provided with an L-shaped sealing disc 28 on the side of the roll body 21 away from the gap 27. The short arm 29 of the sealing disc 28 is held in force bearing engagement under pretension in the bearing ring 3 for fixing. The radially aligned arm 30 is guided to the flange 13a while maintaining a constant gap 31.

2 shows a separating bearing 1b according to the invention. Each component is identical to the component of FIG. 1 where the same components are denoted by the same reference numerals.

The separating bearing 1b is provided with the outer bearing ring 12b shape | molded in the form different from the separating bearing 1a. The flange 13b of the bearing ring surrounds the roll 21 at the same time. A sheet metal dish having a thin wall formed without cutting is used as the bearing shell 14b. This dish is supported on the locator 37 of the flange 13b and the shape of this locator can be adapted to the ball segment face of the bearing shell 14b. The contact 19 is fixed between the bearing shell 14b and the flange 13b as shown in FIG. 1 and coincides with the pressure line 23 of the pressure angle α. The two-piece bearing ring 12b can move between the flange 13b and the bearing shell 14 due to the bearing shell 14b movably mounted in the locator 37. The stops 35, 36 mounted on the flange 13b and spaced apart from the ends of the bearing shell 14b, respectively, determine the adjustment area between the bearing ring 12b and the flange 13b.

The separate bearing 1c in FIG. 3 comprises a divided circumferential inner bearing ring 32 consisting of a flange 33 and a bearing shell 34 in place of the embodiment described above. This outer bearing ring 38 is rotatably fixed to the retaining prong 39 which is fixed to the actuating member (not shown in FIG. 3). The configuration of the flange 33 and the bearing shell 34 and this support is similar to that of the bearing ring 12a shown in FIG. The flange 33 forms a ball surface segment 40 having a radius R, which constitutes the contact 41 together with the outline of the bearing shell 34, which is in contact with a pressure line having a pressure angle. 43) where R intersects the axis of rotation (4). The retaining member 42 elastically fixed to the bearing shell 34 and radially covering the cross-sectional area 40 of the flange 33 serves to safely hold the two parts of the bearing ring 32. The separating bearing 1c comprises a sealing disc 44, which is fixed to the bearing ring 38 at the end facing the spring tongue 15. The sealing disc 44 is directed radially inwards and to the bearing shell 34 while maintaining a constant sealing gap 45.

The separate bearing 1d shown in FIG. 4 surrounds the divided outer ring 12a arranged along the circumference in a form different from that shown in FIG. 1. However, since the basic structure is not different, the components relating to the bearing rings 3, 12a are numbered according to Fig. 1 and are not explained in more detail. Unlike FIG. 1, the bearing shell 14a surrounds the cross-sectional area of the bearing ring 3. A sheet metal sleeve that is rotatably fixed to the bearing shell 14a and covers the free end of the bearing ring 3 with a radially inwardly facing edge 46 is used as the retaining member 46. This retaining member 46 forms a plurality of spring clips 48 at ends spaced apart from the edges 47 which extend outwardly along the circumference and are pretensioned in the flange 13a. The sealing disc 49 fixed to the flange 13a is used as a seal for the separating bearing 1d between the flange 13a and the inner bearing ring 3. The free end of the sealing disc forms a sealing gap 50 which extends in parallel with the vertically aligned flange 5 of the bearing ring 3 and extends as desired.

5 is an enlarged view of the components of the separating bearing 1a in rolling contact. According to FIG. 5 the flange 13a is supported in the bearing shell 14a so that the pressure line 23 of the separating bearing 1a is guided through the contact surface 19. The pressure line 23 connects with the contact points 51 and 52 established between the roll 21 and the bearing ring 3 and the bearing shell 14a, respectively, and extends through the center point of the roll 21. The extension of the pressure line 23 defined by the pressure angle α to the axis of rotation (not shown) shows that the ball radius must intersect the axis of rotation to make the ball segment surface.

The claims herein are described in terms that do not violate for broader protection. Applicants of the present invention have rights to the features described in the detailed description and drawings.

The numbers used in the subclaims refer to different forms according to the subject matter of the main claim through the features of each subclaim concerned; This is not to be considered as an independent protection of the features of the referenced subclaims.

The subject matter of the subclaims may form an independent invention having a form independent of the subject matter of the preceding claims.

The invention is not limited to the embodiments described in the detailed description. Many modifications and variations are possible within the scope of the invention, and such changes, elements, combinations and materials may be combined and modified with each feature, element or process step described in the description and examples and claims and shown in the accompanying drawings. This new combination of features will lead to new themes, stages and series of process steps as far as manufacturing, inspection and work processes are concerned.

Claims (32)

Bearing rings 3,32 firmly mounted to rotate in the sliding sleeve, bearing rings 12a, 12b, 38 rotating in rotation, and bearing rings 3,32 and bearing rings 12a, 12b, 38; In a separate bearing of an automobile clutch comprising a roll body 21 which is guided in between and rotates about a common axis of rotation 4, a) an end 18 and a region 20 with ball face segments of matching shape are provided between the spring tongue 15 of the clutch and the separating bearings 1a, 1b, 1c, 1d, b) an end 18 of the end 18 and region 20 with ball face segments is provided over the spring tongue 15, c) an area 20 of said end 18 and area 20 with ball face segments is provided over the separation bearings 1a, 1b, 1c, 1d, d) the radius of curvature R of the ball surface segments intersects the axis of rotation 4 of the roll 21, e) Separation bearing, characterized in that the separation bearing is arranged in the center parallel to the axis of rotation (4). The bearing as claimed in claim 1, characterized in that the end portion (18) and the area (20) with the ball face segments are rotatable relative to one another. 3. The resetting load as set forth in claim 1, wherein the reset load formed by the stops (35, 36) mounted in the rotational zone of the end (18) and the area (20) is the end (18). Separating bearing from the bearing. Separation bearing according to claim 1 or 2, characterized in that the end (18) and the region (20) forming the ball face segment have a rotational zone (β) of ± 10 degrees or ± 1.5 degrees. 2. The bearing as claimed in claim 1, characterized in that the circumferential bearing ring (12a) comprises an arm (17) and a bearing shell (14a) forming a contact pressure plate for the spring tongue (15). Separation bearing according to claim 1 or 2, characterized in that the region (20) with the ball face segment is formed from the circumferential bearing ring (12b). Separation bearing according to claim 1 or 2, characterized in that the end (18) and the area (20) with ball face segments are configured radially outward from the circumference of the roll (21). Separation bearing according to claim 1 or 2, characterized in that the end (18) and the area (20) with the ball face segments are configured radially inward from the circumference of the roll (21). Separating bearing according to claim 1 or 2, characterized in that the end (18) with a ball face segment is configured in the flange (13a). Separating bearing according to claim 1 or 2, characterized in that the end (18) comprising a ball face segment is formed from the spring tongue (15). The bearing shell (12a) and bearing shell (12) of the end (18) and the area (20) comprising the ball face segments by retaining members (25) fixed to the separating bearing (1a). Separation bearing, characterized in that the 14a have a clearance in the keyed state and are fixed with respect to each other. Separation bearing according to claim 11, characterized in that the retaining member (25) is fixed to the bearing ring (3). Separation bearing according to claim 11, characterized in that the retaining member (25) is fitted or welded to the bearing ring (3) under pressure. 12. The bearing ring (12a) and bearing shell (14a) of the end portion (18) and region (20) comprising ball face segments are surrounded by a retaining member (25) at the circumference. Separating bearings. 12. A separate bearing according to claim 11, characterized in that the flange (33) and bearing shell (34) of the contact portion (41) including ball face segments are surrounded by retaining members (42) at the outer circumference. 12. The bearing ring (12a) and bearing shell (14a) of the end portion (18) and region (20) comprising ball face segments are surrounded by retaining members (25) at the outer circumference. Separation bearing. 3. The bearing shell (14a) according to claim 1 or 2, wherein the bearing shell (14a) has a region (20) including a ball surface segment at the outer circumferential portion of the bearing shell (14a) connected with the rolling member (21), and the region (20) is In the outer circumferential portion, the contact pressure plate is arranged in close contact with the flange 13a, and in the outer circumferential portion of the flange 13a, the retaining member 46 has a clearance and the bearing shell 14a and the flange ( 13a), a separate bearing characterized in that it surrounds. A bearing as claimed in claim 5, characterized in that the bearing shell (14a) surrounded by the flange (13a) forms an angle β of 100 degrees or less and surrounds the roll body (21). Separation bearing according to claim 4, characterized in that stops (35,36) are provided on the positioner (37) to define the area of rotation of the bearing ring (12b). A retaining member (25) is fixed to a bearing ring of a flange (5) securely mounted so as to be rotatable, and the free end (26) of the retaining member (25) is a radial ring gap. And a gap formed between the bearing ring 12a and the bearing shell 14a is covered by the end 26 so as to be connected to the radially stepped end 18 of the flange 13a. bearing. A retaining member (46) is mounted on a bearing shell (14a), and one end of the retaining member (46) comprises a spring clip (48), by means of the spring clip (48). The flange 13a presses and restrains the bearing shell 14a in a contact state, and the edge 47 of which the end of the retaining member 46 arranged away from the spring clip 48 is arranged radially inward. And a free end of the bearing ring (3) mounted so as to be rotatable and fixedly radially covered by said edge (47). 22. A separate bearing according to claim 20 or 21, characterized in that the retaining member (46) is fitted to the bearing ring (12a) of the flange. The sealing disc 28 is mounted on the bearing ring 3 to seal the inner space of the separation bearings 1a and 1b, and the free end of the sealing disc 28 is a gap 31. Separation bearing, characterized in that guided to the bearing ring (12a, 12b) of the flange while maintaining the). 24. The arm according to claim 23, wherein the sealing disc 28 is made without cutting into sheet metal and comprises an L-shaped cross-section, while maintaining the gap 31 radially toward the bearing rings 12a, 12b of the flange. 29) a pre-tensioned arrangement on the cylindrical arm (30). 2. The sealing disc (50) according to claim 1, wherein the sealing disc (49) is rotatably fixed on the bearing ring (12a) of the flange and parallel to the flange (5) of the bearing ring (3) arranged vertically. Separation bearing, characterized in that the free end of the sealing disc (49) is formed while forming. 2. The bearing as claimed in claim 1, wherein the bearing rings (12a, 12b, 32, 3, 38), bearing shells (14a, 14b) and flanges (13a, 13b) are manufactured without cutting. A retaining member (25, 42, 46) fixed to the bearing ring (3) or the bearing shell (14a, 34) has a clearance in the keyed state with the bearing ring or the flange associated with the bearing ring. Separate bearing characterized in that the connection. Separation bearing according to claim 1, characterized in that the sealing disc (49) is mounted on each side of the roll (21). The bearing shell (14a, 14b, 34) and the flanges (13a, 13b, 33) have portions in which the bearings are supported in a linear contact state, and the flanges (13a, 13b, 33) are mounted in the bearing shells by linear contact. A separate bearing characterized in that it slides along the region 20 of 14a, 14b, 34. 30. A separate bearing according to claim 29, wherein the bearing rings (12a, 12b, 32, 3, 38), bearing shells (14a, 14b) and flanges (13a, 13b) are manufactured by a deep drawing process. 2. The bearing as claimed in claim 1, comprising an inner bearing ring surrounding the bearing shell (34) and the flange (33). The contact portion 41 formed between the bearing shell 34 and the flange 33 is arranged on the pressure line 43 of the separation bearing 1c, and the pressure line 43 is a pressure angle α. And the contact points 51 and 52 of the rolling body 21 formed on the bearing shell 34 and the bearing ring 38 are connected by the pressure line 43, and the pressure line 43 is Separation bearing, characterized in that passing through the center point of the roll (21).

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