GB2304859A

GB2304859A - Projection snap connecting in recess for mounting bearing rings in components.

Info

Publication number: GB2304859A
Application number: GB9618239A
Authority: GB
Inventors: Albert Albers; Hartmut Mende
Original assignee: LuK Lamellen und Kupplungsbau GmbH
Current assignee: LuK Lamellen und Kupplungsbau GmbH
Priority date: 1995-09-02
Filing date: 1996-08-30
Publication date: 1997-03-26
Anticipated expiration: 2016-08-30
Also published as: FR2738305B1; GB2304859B; DE19631725A1; FR2738305A1; GB9618239D0; DE19631725B4

Abstract

A connection between two components 10, 13 which are slidable axially one on the other. The two components slide together and are centred through radially opposing support faces 24, 22 formed on the parts. One of the components has a radial projection 29 directed towards the second component and the second component has a radial recess 36. The projection and the recess overlap one another by deforming the axial support element 33 along ramped part 38 of projection 29 so that after sliding the components together the radial projection is snapped into the radial recess.

Description

MECHANICAL CONNECTION FOR COMPONENTS The invention relates to a connection between two components which can be fitted or slid axially on each other to form assemblies.

Connections of this kind are known in connection with rolling bearings, such as for example through DE-GM 69 45 830 wherein the inner ring of a bearing has for axially securing on a stud-like attachment an area rolled into a groove of the attachment. To this end the inner ring must however consist of a plastically deformable material and be made from sheet metal. Bearings of this kind are however only able to be used in special cases. Furthermore owing to the material which can be used the tracks can only have a low hardness. This method is furthermore relatively expensive.

Through DE-GM 74 20 237 a connection is known wherein a rolling bearing is secured on a seat of a shaft in that at the end of the seat there is a collar which is enlarged compared to the inner diameter of the inner ring and the inner ring is pushed over same. For the assembly a temperature difference between the components is thereby utilized in order to push the ring over the collar and shrink fit it onto the seat. This is a relatively expensive process and cannot be used generally particularly as the bearing must be heated which causes difficulties in view of the grease contained therein.

The object of the present invention is to provide securing means for a rolling bearing which act mainly with keyed locking engagement in the axial direction, which take up little space and which require no additional components.

The securing means according to the invention should furthermore allow the assembly of the complete rolling bearing and furthermore be able to be manufactured in a simple cost-effective manner. Furthermore the work or assembly steps required to assemble or fix the rolling bearing are to be carried out in a simple economic way.

According to the invention this is achieved in that in order to secure two components which can be slid or fitted axially one on the other, such as in particular an at least ringtype component on or in a similarly shaped seat of another component, the components after sliding on each other are centred through radially opposing support areas moulded on same wherein at least one of the components, namely the ring-shaped component and the other component, has at least one radial projection directed towards the second component and the second component has at least one radial recess wherein the projection and recess radially overlap or coincide so that after sliding the two components one over the other the radial projection snaps or engages in the radial recess.It can be particularly expedient if the projection prior to sliding or fitting the ring-shaped component on or in the seat of the second component is already moulded on the corresponding component, namely is preferably formed integral with this component. The radial projection can thereby be formed by a ring-shaped bead. The radial recess however can be formed as a ring-shaped groove.

The support areas can be formed by associated cylindrical sleeve faces of the two components. Thus for example one sleeve face can be formed by the inner face of a bore or sleeve or the outer face of a stud and the other sleeve face can be formed by the outer face of a bearing outside ring or sleeve or the inner face of a bearing inside ring.

The connections designed according to the invention are however suitable quite generally for connecting two components which have areas which fit axially inside each other and are positioned through support areas.

The invention further relates to a method for securing two components which can be pushed or mounted axially one on the other such as an at least approximately ring-shaped component on or in a ring-shaped seat on another component wherein after sliding one on the other the two components are centred through their radially opposing support areas moulded on same, which are preferably at least approximately cylindrical, wherein furthermore at least one of the components has at least one radial projection directed towards the other component and the other component has at least one radial recess which radially overlap one another, wherein only over a partial area of the entire axial sliding path forming the detent path the radial projection of one component as well as where applicable areas adjoining the projection, and a leading area during assembly - seen in the sliding direction of the components - of the other component radially covering the projection as well as where applicable areas adjoining this area are deformed at least mainly elastically whereby at the end of the engagement path the projection snaps or engages in the recess.

For the design and functioning of the connection it can be particularly expedient if the radially overlapping areas of the projection and recess extend axially only over a fraction of the entire axial assembly or slide-on path of the parts. It can thereby be ensured that the increased assembly force required for the projection to engage in the recess is only necessary over a short period in time.

Furthermore it is thereby guaranteed that a comparatively large radial overlap of the components only occurs over a short partial stretch of the total axial assembly path whereby the elastic deformation of at least one of the components required to produce the connection is favoured.

It can be particularly advantageous if the radial projection and radial recess are provided on the axial extension of the seat and/or of the ring-shaped component so that the radially overlapping areas are pushed past each other only over a short part of the entire axial slide-on path of the parts relative to each other - the engagement path -. It can be particularly expedient if the projection and recess are provided in the axial end areas of the axial areas of the parts which can slide on or in each other since the elastic deformability of the parts required in most cases can thereby be improved, particularly because the areas of the parts sliding on or in each other can thereby be elastically deformed over a greater axial length than the extension length of the projection.It can be particularly expedient if the recess is provided in the area of one of the components which leads during the assembly or sliding-on process and the projection is provided in the trailing area of the other of the components. By leading area is meant the area of a component which during assembly of the two components first interacts with the second component. By trailing area of a component is meant the area of this component which during assembly with a second component interacts with an area of the second component only in the final phase of the sliding process.

A connection designed according to the invention can be used in a particularly advantageous way in cases where the ring is a constituent part of a rolling bearing which consists at least of an inner and outer ring with rolling paths for the rolling bodies wherein at least one of the rings has a projection and/or a recess which viewed in the axial direction is provided outside of the extension of the corresponding rolling paths.

According to a varied embodiment of a connection according to the invention the inner ring of a rolling bearing which supports two components rotatable relative to each other can be secured on a seat of one component formed by a stud-like attachment wherein the radial projection - seen in the assembly or sliding direction of the two parts relative to each other - can be provided in the area of the attachment or seat which trails during assembly and the recess can be provided in the area of the ring which leads during assembly.

According to another design possibility or use of a connection according to the invention the inner ring of a rolling bearing which supports two relatively rotatable components can be secured on a seat of a component formed by a stud-like or sleeve-like attachment wherein the radial recess - seen in the sliding direction of the two parts relative to each other - can be provided in the area of the attachment or seat which leads during assembly and the recess can be provided in the area of the inner ring which trails during assembly.

With an embodiment where an outer ring of a rolling bearing which supports two relatively rotatable components is secured in a seat formed by a component it can be advantageous if the radial projection - seen in the slide-in direction of the two parts relative to each other - is provided in the trailing area of one component and the recess is provided in the leading area of the outer ring.

In devices where an outer ring of a rolling bearing which supports two relatively rotatable components is secured in a seat formed by a component, such as a sleeve-type component, the connection according to the invention can be arranged and designed so that the radial projection - seen in the push-in direction of the two parts relative to each other - is mounted in the area of the outer ring which trails during assembly and the recess is provided in the area of the one component or seat which leads.

In designs where an outer ring of a rolling bearing which supports two relatively rotatable components is set in a component such as a sleeve-like part, for the common insertion of the bearing and sleeve-like component in a seat of another component it can be particularly expedient to design the connection so that the radial recess - seen in the push-in direction of the parts relative to each other is provided in the area of the sleeve-like component which leads during assembly and the projection is provided in the trailing area of the seat.

In cases where an outer ring of a rolling bearing which supports two relatively rotatable components is set in one component such as a sleeve-like component, for the common insertion of the bearing and sleeve-like component in a seat of another component the connection can be designed and arranged so that the radial projection - seen in the insert direction of the two parts relative to each other - is provided in the trailing area of the sleeve-like component and the recess is provided in the leading area of the seat of the other component.

In order to facilitate assembly and more particularly to reduce the maximum force required to overcome the projection during assembly, it can be particularly expedient if the projection - seen in the sliding direction of the component provided with same onto or into the corresponding seat - is formed wedged at least over a partial section of its extension and is enlarged relative to the seat in the radial direction in the assembly direction of the component having the projection so that the radial overlap between the seat and projection increases. The pitch of the wedge-shaped areas of a projection can be in the order of between 40 and 150, preferably between 5 and 100.

Connections designed according to the invention can be used quite generally in mechanical engineering. They can however be used with particular advantage in so-called twin-mass flywheels whose two masses are mounted to rotate relative to each other through a rolling bearing.

A design according to the invention of the connection for axially fixing and holding a rolling bearing, for example a rolling bearing centring the two masses of a so-called twin mass flywheel is shown in the drawings in which: Figure 1 is a sectional view of the twin-mass flywheel; Figure 2 shows an enlarged section of the rolling bearing; Figure 3 shows a further enlarged section of an area of the rolling bearing; Figure 4 shows a press-on force diagram; Figure 5 shows a press-off force diagram; Figure 6 shows a further embodiment according to the invention and Figure 7 shows possibilities for arranging the connections designed according to the invention.

The twin-mass flywheel 1 illustrated in Figure 1 is divided into two flywheel elements 2 and 3. The flywheel element 2 can be fixed on an output shaft (not shown in further detail) of an internal combustion engine through the holes or bores 4 by means of fixing screws 4a. The second flywheel element 3 can be coupled to and uncoupled from a gearbox (not shown in further detail) by a switchable friction clutch 6. Between the two flywheel elements 2 and 3 there is a device for damping torsion vibrations which allows a relative rotation between the two elements 2 and 3 wherein these are positioned rotatable coaxially relative to each other through a bearing 5.

The flywheel element 2 which forms the input part of the damping device 7 forms a housing which defines a circumferentially ring-shaped chamber 8 in which is housed at least one part of the damping device 7, namely at least the coil springs 9 extending arcuate over the circumference.

For further structural and functional features reference is made to DE-OS 44 14 584, DE-OS 41 17 579 and DE-OS 4331 454.

With embodiments of twin-mass flywheels according to the prior art it is also possible to use bearings likewise designed according to the invention. The content of this prior art should thus serve to explain the present invention and should be considered as integrated in same.

The flywheel element 2 on the engine side has a component 10, made in the illustrated embodiment of sheet metal, which can be screwed onto the output shaft of an engine through the radial area 11. The component 10 forms an axially extending ring-shaped area 12 which in the illustrated embodiment is mounted radially inside the bores 4 or the fixing screws 4a set therein.

The inner ring 13 of the bearing 5 is fixed onto the sleeve or ring-shaped area 12 by pressing onto same. The outer ring 1 & of the bearing 5 is set in a cylindrical socket or bore 15 of the flywheel element 3 wherein a force-fit seat is likewise provided between the bore 15 and bearing 5.

As can be seen from Figure 2 the rolling bearing 5 formed by a single-row ball bearing is designed regarding the seal, thermal insulation and measures for forming a reserve of bearing lubricant, in the same way as that proposed by DE-OS 41 14 655 for which therefore reference is made to this specification. The disclosures made in this specification should therefore be considered as integrated into the present application. It can be seen from Figure 2 that the outer bearing ring 14 holds a cap 16 which forms between the sleeve face 15a of the receiving bore 15 and the outer sleeve face 14a of the bearing ring 14 an intermediate layer 17 which can serve as thermal insulation for reducing the temperature of the rolling bearing 5. Furthermore the cap 16 forms - at the side of the bearing 5 - an additional lubricant chamber 18 to hold a reserve supply of bearing grease.Radially inside the cap 16 has an axial area 19 which axially overlaps or engages underneath an area 20 of the inner bearing ring 13 and forms a sealing spot with same. The axial area 19 rotatable relative to the bearing ring 13 forms with the radially opposing areas 20 of the ring 13 at least one gap seal. Preferably however at least in the new state the axial area 19 of the preferably plastics-made cap 16 adjoins with a certain radial pretension the area 20 which can be formed by a nose-like moulded area 20. On the side of the bearing 5 remote from the hollow cavity 18 there is a sealing ring 21 which is supported by the outer bearing ring 14 and radially inwards sealing adjoins the inner bearing ring 13 through sealing lips.Further functional and design features which can be or are used advantageously with the bearing 5 can be drawn from the aforesaid DE-OS 42 14 655.

The inner ring 13 has an inner sleeve face 22 which is set with force and/or shrink fit on the outer sleeve face 24 of the seat 25 formed by the sleeve-like area 12. To assemble the bearing 5 this is pushed onto the seat 25 in the direction of arrow 26.

As a result of the drop in temperature which can occur during the operation of the device or twin-mass flywheel 1 as well as the axial forces which arise, more particularly between the ring 13 and attachment 12, it can happen that the force and/or shrink fit seat provided between the ring 13 and attachment 12 is not sufficient to prevent the bearing 5 and thus the flywheel element 3 from slipping off.

In order to avoid this, additional securing means 27 are provided according to the invention which will be described in further detail in connection with Figure 3.

The securing means 27 comprise an area 28 which is widened in diameter compared to the outer cylindrical sleeve face 24 of the attachment 12 and forms a ring-shaped projection 29.

In the illustrated embodiment the projection 29 - viewed in the slide-on direction 26 of the ring 13 onto the attachment 12 - is provided in the end area or at the end of the outer sleeve face 24 of the attachment 12. Axially adjoining the ledge formed by the ring-shaped projection 29 is a rear-cut section or recess 30 which is formed here by a ring-shaped groove 30. Adjoining the recess 30 the component 10 has a radially aligned shoulder 31 which serves as a stop for defining the axial movement of the ring 13 in the direction of arrow 26. The ring 13 can be supported by its end face 32 on this shoulder 31.

The securing means 27 further comprise an axially supporting area 33 which interacts with the axial counter supporting area 34 formed by the projection 29 in order to prevent through a mainly positive-locking connection or support the ring 13 slipping axially off from the attachment 12. The inner diameter 35 defining the axial supporting area 33 has in the illustrated embodiment substantially the same diameter as the diameter of the ring sleeve face 22. These two diameters should be at least approximately the same wherein it can be advantageous depending on the type of use if the inner diameter 35 defining the axial supporting area 33 is slightly smaller or larger than the outer diameter of the sleeve face 24 of the attachment 12. If such a difference in diameter exists this can be in the order of between 0.01 and 0.05 mm.

The axial supporting area 33 is formed by introducing a rear cut section or recess 36 in the area of the inner originally continuous cylindrical sleeve face 24 of the ring 13. The rear cut section 36 is provided in the section 37 of the ring 13 which first comes into contact with the attachment 12 when the ring 13 is pushed onto the attachment 12.

Through the arrangement of the rear cut section 36 and projection 29 engaging radially in same according to the invention the axially keyed positive locking between the components 10 and the ring 13 only takes place in the end phase of the sliding process of the ring 13 onto the attachment 12 so that damage to the interacting supporting areas 33 and 34 is avoided.

In order to reduce the assembly or press-on forces the projection 29 is formed at least over a partial'section of its axial extension so that it gradually changes in height in the direction of arrow 26. To this end, as marked by 38, the projection 29 - viewed in cross-section - can expand wedge-shaped in the direction of arrow 26. The pitch 30 of the conically expanding surface 38 of the projection 29 can thereby be in the order of between 40 and 15 , preferably in the order of between 50 and 100. In the illustrated embodiment the pitch 29 is about 80.

With a diameter of the sleeve faces 22, 24 in the order of between 30 mm and 40 mm it is expedient if the radial overlap 40 between the faces formed by the supporting areas 33 and 34 is in the order of between 0.03 and 0.08 mm. This overlap can however also be greater. In practice where the sleeve faces 22,24 have a diameter of about 34 mm an overlap 40 in the order of about 0.04 mm has proved suitable.

As can be seen from the drawings, with the illustrated embodiment the securing means 27 - viewed axially - are provided outside of the axial extension of the rolling path 41 for the balls 42 of the bearing 5. It is thereby guaranteed that during assembly of the bearing 5 on the attachment 12 the bearing inner ring 13 in the area of the balls 42 or the rolling path 41 is not or is only slightly elastically radially widened whereby damage to the bearing can be avoided. The balls 42 and/or at least the rolling path 41 need not therefore be pushed axially over the projection 29.

In order to make it easier to slide the ring 13 onto the attachment 12 the ring 13 has on its end area facing the shoulder 31 a chamfer 43 which practically directly adjoins the axial supporting area 33.

When fitting the bearing 5 or ring 13 onto the attachment 12 at least the corresponding components 10,13 have the same temperature. It can however also be expedient if during assembly there is a negative temperature difference at least between the attachment 12 and ring 13, this means that the attachment 12 can have a slightly lower temperature than the ring 13. This can be achieved by the area 12 or component 10 cooling down and/or by the ring 13 or bearing 5 or bearing unit heating up. Through such a difference in temperature the forces required to push the ring 13 onto the attachment 12 can be reduced since the radial overlap between the corresponding diameters is reduced.

When fitting the bearing 5 onto the component 10 the ring 13 first comes to adjoin the free end 44 (Figure 2) of the attachment 12. The free end 44 is thereby designed with a sharp edge whereby the effective contact face between the sleeve faces 22 and 24 is enlarged. With an increasing axial overlap between the sleeve faces 22 and 24 the presson force required gradually increases, but this increase is however slight compared with the increase which is required for the supporting area 33 to axially overcome the projection 29.As soon as the chamfer 43 comes to adjoin the conically widening face 38 the axial supporting area 33 moves along the surface 38 whereby as a result of the inherent elasticity of the components 13 and 10 or attachment 12 a change in diameter takes place at the parts so that the supporting area 33 can axially overcome the ring-shaped projection 29 whereby this projection 29 comes to lie in the recess or rear-cut section 36. When the supporting area 33 oversteps the projection 29 the elastically deformed areas of the parts 13 and 10 spring back again so that the supporting area 33 and the counter supporting area 34 formed by the projection 29 radially overlap by a small amount so that an axially active locking occurs which is predominantly formed as a positive lock.

The supporting area 33 thus snaps in behind the projection 29 or the projection 29 snaps into the rear cut section 36 whereby an axial lock is formed between the components 10,13.

A typical path of the press-on force required for the ring 13 or bearing 5 is shown in Figure 4. It can be seen from this figure that the press-on force required increases comparatively little over the first area part 44 which lasts substantially until the chamber 43 adjoins the conical shaped surface 38. A considerably higher press-on force is only required to overcome the projection 29 whereby the increase lasts up to point 45. On exceeding point 45 which corresponds to the snap-in point, thus the point at which the supporting areas 33 and 34 radially overlap or engage axially behind each other by springing back, the press-on force decreases suddenly again wherein on continuing to press the ring 13 in the direction of arrow 26 (Figure 3) a sudden increase in force takes place again which is caused by the end face 32 of the bearing ring 13 stopping against the shoulder 31.The press-on process is ended from this point.

As can be seen from Figure 3 as a result of the manufacturing tolerances required it is advantageous if when the end face 32 stops against the shoulder 31 there is a slight play 46 between the axially opposing supporting areas 33,34.

From the diagram illustrated in Figure 5 it can be seen that the maximum force 45a required to press the bearing 5 or ring 13 off from the axial attachment 12 amounts as a result of the securing means 27 to a multiple of that axial force which is required to overcome the press or shrink fit connection existing between the sleeve faces 22'and 24.

With the illustrated embodiment the securing means 27 viewed in the push-on direction 26 of the bearing ring 13 are provided at the end or in the end area of the sleeve faces 22, 24 or of the attachment 12 and ring 13. Securing means of this kind can however also be provided at any point on the axial extension of the attachment 12 or ring 13. As can be seen however in connection with the diagram according to Figure 4, when the securing means 27 in Figure 3 are moved to the right the area of the press-on path over which a high press-on force occurs corresponding to point 45 according to Figure 4 is then correspondingly longer which can be disadvantageous for many cases.

Furthermore viewed over the length of the attachment 12 or ring 13 several places can be provided with corresponding securing means 27.

A projection equivalent to the projection 29 can also be provided on the bearing ring 13 wherein then the attachment 12 has a rear cut section equivalent in terms of function to the rear cut section 36. With an arrangement or design of the securing means of this kind it is then expedient if these are provided in the area of the free end 44 (Figure 2) of the attachment 12 or sleeve face 24, since then it can likewise be guaranteed that the increased press-on force corresponding to point 45 of Figure 4 only occurs in the end phase of the press-on process of the ring 13 onto the attachment 12. A design of the securing means of this kind can also be combined with one such according to the figures.

Furthermore securing means 46 can be seen from Figure 3 for axially securing the outer bearing ring 14 relative to the flywheel element 3. As can be seen - viewed in the axial direction - the bore 15 or its sleeve face 1Sa is divided in areas with different diameters. The smaller diameter 47 is thereby provided in the area of the open end section of the bore 15. The larger diameter 48 of the bore 15 axially adjoins the smaller diameter 47 viewed in the press-in direction 49 of the bearing 5 in the bore 15 whereby in the illustrated embodiment a transitional area 50 is provided which widens conically in the direction of arrow 49.

The socket or bore 15 has in the area of its open end adjoining the diameter 47 a tr.read-in chamfer 51. The bore 15 with the larger diameter 48 extends at least over the axial area of the outer ring 14 which is in direct contact with the cap 16. One end of this area is marked 52. In Figure 3 the end section 53 of the sleeve-like section 16a of the cap 16 engaging over or round the bearing is shown in the relaxed state. In actual fact in the illustrated assembled state the end area 53 is however forced or swivelled radially inwards through the circular radial projection 54 formed as a result of the smaller diameter 47.

The overlap 55 shown in or apparent from Figure 3 is thus not present. After the assembly of the bearing 5 in the bore 15 the seal 21 is at least elastically deformed by a layer 21 formed of a yielding material. This layer can consist of a plastics material, such as for example an elastomer.

The radial height 56 of the projection 54 is measured so that the bearing unit formed by the rolling bearing 5 and the cap 16 as well as the seal 21 can be pressed into the bore 15 as a result of the elastic deformability of the individual components. The assembly of the bearing 5 or bearing unit into the bore 15 can take place at room temperature or with an at least approximately identical temperatures of the parts but it can also be expedient as has already been described in connection with sliding the ring 13 onto the attachment 12 if the press-in forces required can be reduced by heating or cooling the corresponding parts. Thus for example the part 3 can be heated and/or the bearing unit having the bearing 5 can be cooled.

It is expedient for the assembly of the bearing unit if this is first fitted onto the flywheel element 3 and then pushed together with this onto the component 10 or attachment 12.

By heating up or cooling down the corresponding components during their assembly, thus by utilizing the temperature differences between the components which are to be assembled the radial overlap of the corresponding securing means can be increased whereby an improved axial security can be achieved. Utilizing the temperature differences when fitting the corresponding parts can however also be used to reduce the elastic deformability of at least one of these parts which is required during fitting whereby it can be ensured that at least this part is not damaged during fitting.The latter is particularly advantageous when fitting the bearing unit containing the bearing 5 into the bore 15 since in many cases a comparatively brittle or hard plastics is used to make the cap 16 which as a result of the small thickness in the area of the bore 15 only allows a slight radial internal deformability.

Figure 6 shows a further possible use of a connection according to the invention, namely between the bearing cap 116 and the component 103. The component 103 has similar to that shown in Figures 1 to 3 in connection with the second flywheel element 3 a circular hole or bore 115 to receive the bearing unit 1OSa which contains the bearing 105. The bearing unit 105a is apart from the securing means 146 which are to prevent the bearing unit 105a from sliding out axially from the bearing socket 115, designed similar to the bearing unit according to Figures 1 to 3. The bearing unit 105a can however also have a different shape and arrangement. The securing means 146 are designed similar to and act like the securing means 27 according to Figures 2 and 3.These securing means 146 comprise a radial projection 129 provided on the end section 153, facing the open side of the bore 115, of the sleeve-like section 116a of the cap 116 engaging round the bearing 105 wherein this projection 129 engages radially in a ring-shaped recess 136 of the component 103. The recess 136 or rear cut section 136 is provided in the area of the open end of the bore 115 from which the bearing unit 105a is inserted in this bore 115.In the direction of the open side of the bore 115 the recess 136 is followed by a supporting area 133 which interacts with the axial counter supporting area 134 which is formed by the projection 129 in order to produce a predominantly positive-locking keyed connection between the cap 116 and the component 103, namely in a similar way to that already described in connection with the supporting areas 33, 34 and projection 29 and recess 36.

The size 140 of the radial overlap between the supporting areas 134, 135 can be in the same order as described in connection with the securing means 27 according to Figures 2 and 3. Since however the sleeve-like section 116a of the cap 116 has a comparatively long end area 154 which does not adjoin the outer sleeve face 114a of the outer ring 114 but projects axially over this sleeve face 114a in the direction of the open end of the recess 115 and furthermore an elastomer pliable layer 157 of the seal 121 is present radially inside this end area 154 the overlap 140 can also be selected larger since namely the area 154 of the cap 116 protruding opposite the sleeve face 114a of the outer bearing ring 114 is elastically deformable a certain amount in the radial direction like a bending beam.Thus for example for a diameter 115a of the bore 115 in the order of between 40 and 60 mm the overlap 140 can have a size in the order of between 0.1 and 0.2 mm. As already mentioned, this overlap can however also be smaller. Depending on the type of use this overlap can however also be made larger. This is particularly dependent on the possible radial deformability of the end area 154 which in turn is dependent on the dimensions of this end area.

In order to increase the radial spring capacity or elastic deformability of the sleeve-like area 116a at least in its end area 154 axially aligned slits can be introduced viewed over the circumference of the sleeve-like section 116a - at least over a partial area of the extension of the end area 1543 or at least over a partial area of the axial extension of the sleeve-like section 116a wherein it is advantageous if at least two slits are provided. Preferably however even more slits can be introduced, eg three to ten.

Fitting the bearing unit 1OSa into the recess 115 can be carried out in a similar way to that described in connection with Figures 2 and 3 for fitting the inner bearing ring 13 onto the attachment 12 or the bearing unit containing the bearing 5 into the bore 15.

Although it is particularly advantageous if as illustrated in Figure 6 the securing means 146 - viewed in the insert direction of the bearing unit 105a into the opening 115 -are provided at the beginning, thus on the open side of the opening 115 or on the end area 153, facing this open end, of the component to be slid in, such as the cap 116, securing means 146 of this kind can also be provided at another place, as also explained in connection with Figures 2 and 3.

Thus the securing means 146 can also be moved to the right wherein the radial overlap 140 between the corresponding supporting areas must be adapted to the elastic deformation properties of the corresponding components existing there.

The securing means 146 can also be provided at the other end area of the sleeve-shaped section 116a, namely roughly at the point marked 60 in Figure 7 wherein it is then however expedient if a projection functionally equivalent to the projection 129 is provided in the area of the recess 115 of the component 103 and the sleeve-like section 116a or the cap 116 has a recess interacting with this projection and forming or restricting a corresponding supporting area.

Different points 58, 59, 60, 61, 62 are marked in Figure 7 in the area of which a connection designed according to the invention can be provided in a particularly advantageous manner since these points ensure that the securing means only come into operation in the end phase of the slide-on phase between the two corresponding components. It is thereby ensured that an increased slide-in or slide-on force is only required over a short distance of the axial relative movement required between the two corresponding components.

The connection at point 61 is thereby advantageously formed according to claim 11. The connection at point 59 is preferably designed according to claim 12. The connection at point 58 is advantageously formed according to claim 13 wherein this connection is formed function-wise in relation to the axially interfitting components similar to that in Figure 6. The connection at point 60 can advantageously be designed according to claim 14. The arrangement of the projection and recess at point 62 can advantageously be like that at point 60 and this means that the recess is provided on the cap 16 and the projection on the part 3.

The patent claims filed with the application are proposed wordings without prejudice for obtaining further extensive patent protection. The applicant reserves the right to claim further features disclosed up until now only in the description and/or drawings.

The references used in the sub-claims refer to the further development of the subject of the main claim through the features of the relevant sub-claim; they are not to be regarded as dispensing with obtaining an independent subject protection for the features of the sub-claims referred to.

The subjects of these sub-claims also form however independent inventions which have a configuration independent of the subjects of the preceding sub-claims.

The invention is also not restricted to the embodiment of the description. Rather numerous alterations and modifications are possible within the scope of the invention, more particularly those variations, elements and combinations and/or materials which for example are inventive through combination or modification of individual features or elements or method steps described in the general description and embodiments and claims and contained in the drawings and which through combinable features lead to a new subject or new method steps or sequences of method steps, insofar as they relate to manufacturing, testing and work processes.

Claims

PATENT CLAIMS

1. A connection between two components which are slidable axially one on the other, such as an at least approximately ring-shaped component on or in a similarly formed seat of another component, wherein after sliding together the two components are centred through radially opposing support areas formed on the components, at least one of the components having at least one radial projection directed towards the other component and the other component has at least one radial recess and the projection and the recess overlap one another so that after sliding one on the other the radial projection is snapped into the radial recess.

2. Connection according to claim l characterised in that the radial projection is an annular bead.

3. Connection according to claim 1 or 2 characterised in that the radial recess is an annular groove.

4. A method of securing two components which slide axially one on the other, such as an at least approximately ringshaped component on or in a ring-shaped seat of another component wherein after sliding one on the other the two components are centred through radially opposing support areas moulded on same, at least one of the components has at least one radial projection directed towards the other component and the other component has at least one radial recess and these radially overlap each other, wherein the radial projection of the one component as well as where applicable areas adjoining the projection and a leading seen in the sliding direction of the components relative to each other - area of the other component radially covering the projection as well as where applicable areas adjoining this area are elastically deformed only over a partial area of the overall axial sliding path - the engagement path wherein at the end of the engagement path the projection engages in the recess.

5. Connection according to one of claims 1 to 3 as well as for the method according to claim 4 characterised in that the areas of the projection and recess radially covering one another are extended axially only over a fraction of the overall axial sliding path of the parts relative to each other.

6. Connection according to one of claims 1 to 5 characterised in that the radial projection and radial recess are provided on the axial extension of the seat and/or of the ring-type component so that the radially covering areas are pushed past each other only over a short part of the overall axial sliding path of the parts relative to each other - the engagement path

7. Connection according to one of the preceding claims, characterised in that the projection and recess are provided in axial end areas of the axial areas of the components which slide on or in each other.

8. Connection according to one of the preceding claims, characterised in that the recess is provided in the leading area of one of the components and the projection is provided in the trailing area of the other of the components, seen in the sliding direction.

9. Connection according to one of the preceding claims, characterised in that the ring-shaped component is a constituent part of a rolling bearing, consisting of at least an inner and an outer ring with rolling tracks for the rolling bodies and wherein at least one of the rings has a projection and/or a recess which, viewed in the axial direction, is provided outside of the extension of the corresponding rolling path.

10. Connection according to one of the preceding claims, wherein an inner ring of a rolling bearing which supports two relatively rotatable components is secured on a seat formed by a stud wherein the radial projection - seen in the slide-on direction of the two components relative to each other - is provided in the trailing area of the stud and the recess is provided in the leading area of the inner ring.

11. Connection according to one of the preceding claims, wherein an inner ring of a rolling bearing which supports two components rotatable relative to each other, is secured on a seat formed by a stud wherein the radial recess - seen in the slide-on direction of the two components relative to each other - is provided in the leading area of the stud and the projection is provided in the trailing area of the inner ring.

12. Connection according to one of the preceding claims, wherein an outer ring of a rolling bearing which supports two components rotatable relative to each other is secured in a seat formed by a component wherein the radial projection - seen in the push-in direction of the two components relative to each other - is provided in the trailing area of the component and the recess is provided in the leading area of the outer ring.

13. Connection according to one of the preceding claims, wherein an outer ring of a rolling bearing which supports two components rotatable relative to each other is secured in a seat formed by a part such as a sleeve-like part, wherein the radial projection - seen in the push-in direction of the two components relative to each other - is provided in the trailing area of the outer ring and the recess is provided in the leading area of the component.

14. Connection according to one of the preceding claims, wherein an outer ring of a rolling bearing which supports two parts rotatable relative to each other is housed in a part such as a sleeve-like part for the common insertion of the bearing and sleeve-like part in a seat of another component wherein the radial recess - seen in the insert direction of the parts relative to each other - is provided in the leading area of the sleeve-like part and the projection is provided in the trailing area of the seat.

15. Connection according to one of the preceding claims, wherein an outer ring of a rolling bearing which supports two parts rotatable relative to each other is housed in a part such as a sleeve-like part for the common insertion of the bearing and sleeve-like part in a seat of the other component wherein the radial projection - seen in the pushin direction of the parts relative to each other - is provided in the trailing area of the sleeve-like part and the recess is provided in the leading area of the seat of the other component.

16. Connection according to one of the preceding claims, characterised in that the projection - viewed in the slideon direction of the component having same on or in the seat - is formed wedge-shaped at least over a partial section of its extension and is enlarged relative to the seat in the radial direction in the assembly direction of the component having the projection.

17. Connection according to one of the preceding claims, characterised in that the pitch of the wedge-shaped areas of the projection is in the order of between 40 and 15 , preferably between 5 and 100

18. An assembly containing a connection between two components, characterised in that the assembly is a twinmass flywheel whose two masses are mounted rotatable relative to each other through a rolling bearing having a connection according to at least one of the preceding claims.

19. A connection between two components which are slidable axially one on the other, substantially as herein described with reference to the accompanying drawings.

20. A method of securing two components which slide axially one on the other, substantially as herein described with reference to the accompanying drawings.