US20020185002A1

US20020185002A1 - Sliding ring for a radial piston pump, and device for the installation thereof

Info

Publication number: US20020185002A1
Application number: US10/155,635
Authority: US
Inventors: Michael Herrmann
Original assignee: ZF Batavia LLC
Current assignee: ZF Transmission Technologies LLC
Priority date: 2001-05-30
Filing date: 2002-05-23
Publication date: 2002-12-12
Also published as: DE10126151A1

Abstract

The sliding ring (1) for a radial piston pump has an inner ring (2) and a coaxial outer ring (3) between which a spring/damping element (5) is arranged. The spring/damping element (5) is in one piece and comprises on both sides an annular rim bead (8). The rim beads rest at the side rim of the inner ring (2) against the latter's outer circumference and at the rim of the outer ring (3) against the latter's inner circumference. Provided between the rim beads (8) is a connecting structure (9) that is constituted, for example, by at least one further damping ring (10) that is connected via webs (11) to the rim beads (8). By way of a corresponding configuration of the spring/damping element (5), chambers (32) into which a liquid can be introduced can additionally be formed between the inner ring (2) and outer ring (3) so that the stiffness of the sliding ring (1) can be variably configured.

Description

The invention refers to a sliding ring for a radial piston pump as defined in the preamble of claim 1, and to a device for the installation thereof.

Sliding rings of this kind comprise an inner ring and a coaxial outer ring, between which a spring/damping element is arranged. The sliding ring fits around an eccentric and a sliding bushing placed thereon, and acts with its external surface on spring-braced pistons arranged in star-shaped fashion in a pump housing, the piston chambers being connected to a consumption point via outlet valves. Radial piston pumps of this kind are used, for example, as fuel pumps in diesel trucks.

As existing art, reference may be made to DE-C2-43 36 673, which describes a radial piston pump in which the sliding ring is equipped with a spring/damping element, e.g., in the form of a slotted spring washer, that can additionally be embedded in plastic; this document also mentions the use, as the spring/damping element, of a rubber ring vulcanized on either side onto the inner ring and outer ring.

The operating noise of a radial piston pump can be reduced by way of an elastic spring/damping element of this kind.

In order to reduce this noise further, it has been proposed to arrange several rubber rings, e.g., conventional O-rings, next to one another between the inner and outer ring. Usually three to four O-rings are placed onto the inner ring between two lateral shoulders. Both the manufacture and the installation of these separate O-rings are relatively complex.

The spring/damping properties can be improved with these known elements, but cannot be optimally adapted to the operation of the sliding ring.

In addition, fundamental problems exist in radial piston pumps having elastic sliding rings of this kind when taking in very cold oil, e.g., at temperatures of about −20° C. This has to do with the increase in the oil's viscosity at lower temperatures, and the associated greater difficulty in taking in said oil. In order to improve the intake behavior of the radial piston pump, it has therefore been proposed to lengthen the piston stroke in order to give the oil more time to flow into the piston chamber. This is made possible by a greater eccentricity of the pump eccentric, but this action changes the volume flow characteristic curve of the pump. This is not additionally prejudicial during the cold oil intake phase—since what is most important then is that the pump simply operate—but in normal operation such a change in the volume flow characteristic curve cannot be accepted.

In the context of the aforementioned elastic sliding rings having either several separate O-rings or other spring/damping elements, it has been found that the elasticity of the sliding ring causes a decrease in piston stroke and thus also volume flow. In the operating phase during intake of cold oil, it would thus be desirable to reduce the elasticity of the sliding ring and make it, so to speak, harder. This is not possible, however, with the aforementioned conventional sliding rings.

It is the object of the invention to describe a sliding ring having a spring/damping element which is relatively simple to manufacture and install; whose damping properties can be optimally adapted, by way of the geometry of the spring/damping element, to the particular function of the radial piston pump; and in which, by way of a modification, the elasticity properties of the sliding ring also can be modified, in particular the damping ring can be set for harder elasticity, in order also to optimize the intake behavior of the pump when the liquid to be taken in is at a low temperature.

These objects are achieved, according to the invention, by the features of claim 1.

The spring damping element accordingly is of one-piece configuration and comprises on both circumferential sides a respective annular bead that rests at the rim of the inner ring against the latter's outer circumference and at the rim of the outer ring against the latter's inner circumference, a connecting structure being provided between said rim beads.

By means of the two rim beads, this basic structure of the spring damping element forms, so to speak, the basis for numerous modifications of the sliding ring, which can be adapted and optimized for the particular function of the sliding ring and of the radial piston pump by way of the connecting structure located between the rim beads.

Since the spring damping element is in one piece, its manufacture and of course its installation as well are less complex than the manufacture and installation of multiple separate O-rings; manufacture is also less complex than in the case of the aforementioned composite designs.

Spring and damping properties as good as or even better than with separate O-rings can be achieved if the connecting structure comprises at least one further bead, resting against the outer circumference of the inner ring and the inner circumference of the outer ring, that is connected to the rim beads. The shape of the spring/damping elements can preferably be selected in such a way that said element is substantially an arrangement made up of multiple parallel beads located next to one another, connected to one another e.g., by webs.

The individual beads can have multifarious configurations in a basic structure of this kind, for example can be circular or oval in cross section. Also conceivable is a structure made up of a basic body and sealing lips that protrude out from it on both sides and rest against the inner and outer ring. This multifariously modifiable geometry of the spring/damping element according to the invention makes possible an optimization in terms of the function of the sliding ring and of the respective radial piston pump.

The aforementioned webs for connecting the rim beads and optional beads located therebetween extend substantially along the entire lateral circumference of the beads, but can also extend only along a portion of the lateral circumference. The latter possibility, in particular, can advantageously be used if it should be necessary to use individual beads or O-rings on the sliding ring. In this case the webs between the beads can be configured as preset breaking points that break during operation of the radial piston pump. Since the spring/damping element is nevertheless initially in one piece, the aforementioned advantages in the context of manufacture and installation are retained.

By appropriate configuration of the connecting structure, the elasticity of a sliding ring according to the invention can also be made variable. For that purpose, provision is made for the rim beads to rest in liquid-tight fashion against the inner and outer ring, and to be connected to one another via transverse webs that rest against the inner and/or outer ring, so that along the outer circumference of the spring/damping element between the rim beads, a plurality of chambers separated by the transverse webs are created between the inner and outer ring. The individual chambers each have at least one inflow opening for the liquid to be taken in (e.g., oil), at least some of said inflow openings being provided in the circumferential wall of the inner ring; when the pump is in operation, they open into a groove of the eccentric through which the chambers can be filled with liquid.

When at oil at low temperature needs to be taken in, the elasticity of the sliding ring can thus be decreased by filling its chambers, so that the piston stroke determined by the eccentricity of the eccentric is no longer influenced, or is influenced to only a small degree, by the elasticity of the sliding ring.

If no oil is introduced into the chambers of the sliding ring, the sliding ring then functions as before as a spring/damping element, with the deformation correspondingly adapted to the operation of the radial piston pump and with the reduction in piston stroke associated therewith. If the chambers are filled with oil, however, there will not be much change if the oil is warm; this change in function of course depends on the oil pressure, since the relatively low-viscosity oil can escape very easily from the orifices in the chambers. If the oil is cold and therefore viscous, however, this can no longer occur so quickly because the inflow openings are designed as throttle orifices, and the elasticity of the sliding ring is thus reduced. The piston stroke is thereby increased and the pump can deliver more volume, which means better intake behavior with cold oil.

It is possible to modify the piston stroke, with no change in the eccentricity of the eccentric, by specifically controlling the oil pressure at which the chambers are filled and by allowing oil to flow in controlled fashion into and out of the chambers. If the oil pressure is increased, for example, the sliding ring becomes stiffer, so that at maximum sliding ring stiffness the piston stroke largely corresponds to the eccentricity of the eccentric. Operating at low oil pressure, on the other hand, makes the sliding ring softer, so that the piston stroke correspondingly becomes less than the eccentricity of the eccentric. The volume flow characteristic curve of the radial piston pump can, in this fashion, be influenced during operation.

This kind of control of the volume flow can also be utilized to improve pump functioning at high pump pressures. The reason is that conventional radial piston pumps exhibit a sharp dip in volume flow at high pump pressures, because the large forces acting on the sliding ring at the high pump pressures deform it correspondingly severely, and the piston stroke and thus also the volume flow of the pump decrease accordingly.

With a controllable sliding ring according to the invention, i.e., when the oil pressure in the chambers of the sliding ring and the inflow and outflow of the oil present in the chambers are controlled, the aforementioned effect can be counteracted. At a high pump pressure the oil pressure in the sliding ring should thus be elevated so that the sliding ring becomes stiffer and there is little or no decrease in the piston stroke. The volume flow thus remains the same even at high pump pressures.

According to a preferred embodiment of the invention, each chamber of a controllable sliding ring of this kind is sealed off in liquid-tight fashion with respect to the adjacent chambers, an inflow opening through the wall of the inner ring then being provided for each chamber.

Alternatively, it is possible to connect adjacent chambers with one another through an opening; that opening extends, for example, through the webs separating the chambers. It is also possible to provide, in the outer circumference of the inner ring or in the inner circumference of the outer ring, a groove by way of which the chambers are then connected to one another. It would also be possible to decrease the depth of the webs so that they no longer rest against the inner and/or outer ring; as a result, a gap remains there, through which oil can flow between the chambers. With a design of this kind, an opening through the wall of the inner ring does not need to be provided for each chamber; instead, just a few inflow openings are sufficient here.

This kind of configuration of the sliding ring is advantageous particularly for the intake of cold oil, since as a result of the connection of the individual chambers, the oil can be displaced internally in the sliding ring. The sliding ring thus essentially retains its favorable damping properties. When the oil is cold, the viscous oil can no longer distribute itself so easily in the sliding ring, since it can no longer flow substantially without significant resistance through the connections (configured as throttles) between the chambers, resulting in an overall stiffening of the sliding ring. The stiffness of the sliding ring therefore depends on the viscosity of the oil and thus also on its temperature.

If operation always occurs with a filled sliding ring, the inflow openings through the wall of the inner ring essentially serve to compensate for oil leakage and, if applicable, to control the oil pressure in the sliding ring. In this context, it would be conceivable to incorporate a check valve into the oil inlet, e.g., in a central conduit of the eccentric, so that oil can flow only into the ring but not out of it. If the oil pressure in the sliding ring is to be controlled, a modified valve must then of course be provided in the delivery line.

In order to control the oil pressure in the sliding ring and the oil flow between the individual chambers, it is conceivable to provide webs, functioning as bulkheads, between the chambers, as a result of which the sliding ring automatically becomes stiffer at a higher oil viscosity. These bulkheads can be configured, for example, as fixed webs on the inner and outer ring or, for example, as movable webs that are mounted on the inner wall of the inner ring and can be retracted and extended by means of a corresponding oil flow between the individual chambers.

Further embodiments of the invention are evident from the dependent claims. The invention is explained in further detail, in several exemplary embodiments, with reference to the drawings in which: [0028]
FIG. 1 is a side view of a sliding ring for a radial piston pump with a spring/damping element according to the invention; [0029]
FIGS. [0030] 2 to 4 are sections through the sliding ring in 1 along line A-A, to explain different configurations of the spring/damping element;
FIG. 5 is a plan view of a sliding ring having a spring/damping element made up of three damping rings arranged next to one another and connected to one another by webs; [0031]
FIG. 6 shows a partially sectioned device for installing a spring/damping element on the inner ring of the sliding ring; [0032]
FIG. 7 is a sectioned depiction of a sliding ring with a spring/damping element according to the invention whose elasticity is adjustable; [0033]
FIG. 8 is a plan view of the spring/damping element of FIG. 7; [0034]
FIG. 9 shows a modified embodiment of a spring/damping element according to the invention with adjustable stiffness; [0035]
FIG. 10 shows a further modified embodiment of a spring/damping element according to the invention, indicating the oil flow in the context of the forces of the eccentric and the piston of the radial piston pump acting in opposite directions on the upper side of the element; and [0036]
FIG. 11 shows the spring/damping element of FIG. 10, indicating the oil flow in the context of the forces of the eccentric and the piston of the radial piston pump acting in opposite directions on the lower side of the element.[0037]
FIG. 1 depicts a sliding [0038] ring 1 for a radial piston pump 1 that has an inner ring 2 and an outer ring 3. The inner ring has on both sides shoulders 4 that face toward the outer ring and hold a spring/damping element 5 in place between the inner and outer ring. Sliding ring 1 is slid in precisely fitting fashion onto an eccentric 6 that rests flush against the inner circumference of inner ring 2. The eccentric is driven by an eccentrically mounted drive shaft 7. A sliding bushing (not depicted here) can also be provided, if applicable, between eccentric 6 and inner ring 2.
As [0039] drive shaft 7 turns and eccentric 6 rotates, spring-braced pistons arranged in star-shaped fashion in a housing of the radial piston pump are displaced, so that oil is correspondingly taken in and delivered to a consumption point. Regarding function, the reader is referred to the aforementioned German Patent DE-C2-43 36 673.
As shown in FIG. 2, spring/damping [0040] element 5 comprises two elastic rim beads 8 that are configured, for example, as O-rings and rest against the outer circumference of the inner ring and the inner circumference of outer ring 3. The two rim beads 8 are connected to one another via a connecting structure 9 that in this case is constituted by a further damping ring 10 located in the center of spring/damping element 5 and by webs 11 projecting out on either side of said damping ring 10. Webs 11 thus each connect a rim bead 8 to the central damping ring 10, so that a one-piece spring/damping element 5 is present. Webs 11 extend around the entire lateral circumference of beads 8 and damping ring 10.
In the present case, damping [0041] ring 10 also touches the outer circumference of inner ring 2 and the inner circumference of outer ring 3, so that the elastic properties of the spring/damping element are determined substantially by the material properties of all three rings and by the geometry of the spring/damping element.
FIG. 3 depicts a spring/damping element that again comprises two [0042] rim beads 8 and a central damping ring 10, which in this case are identically configured and have a cross section in the form of a square set on its vertices, resting with oppositely located vertices against the outer circumference of inner ring 2 and the inner circumference of outer ring 3. Beads 8 and damping ring 10 are once again connected to each other via webs 11, yielding a one-piece spring/damping element.
Spring/damping [0043] element 5 shown in FIG. 4 again comprises two rim beads 8 in the form of damping rings with an oval or circular cross section, and a central damping ring 10 that in this case takes the form of a rectangle and rests with the two narrow sides of the rectangle against inner ring 2 and outer ring 3. Webs 11 are once again provided in order to connect the individual rings.
FIG. 5 shows a spring/damping [0044] element 5 in plan view, the upper half of outer ring 3 being omitted. This spring/damping element comprises three damping rings arranged next to one another, i.e., two rings 8 located at the rims and a central damping ring 10, which are connected to one another via small webs 11. Webs 11 are, for example, arranged at angular spacings of 90° and are configured such that upon operation of the radial piston pump, these webs 11 act as preset breaking points. The spring/damping element manufactured in one piece thus breaks apart, upon operation of the pump, into three damping rings separated from and lying next to one another.
FIG. 6 depicts a [0045] device 21 for installation of an annular spring/damping element 5 as described above, i.e., for placing the one-piece spring/damping element onto the outer circumference of inner ring 2 between its shoulders 4. This device 21 comprises a cylindrical tube 22 which has a diameter such that spring/damping element 5 can easily be slid on. The diameter of this cylindrical tube 22 is slightly smaller than the diameter of inner ring 2. Continuous with this cylindrical tube is an installation taper 23 that widens conically and can be placed onto a shoulder 4 of inner ring 2, and has at its enlarged end a thin circumferential flange 24 that is slid onto the outer circumference of a shoulder 4. Device 21 furthermore has a separate pusher tube 25 that can be mounted flush onto cylindrical tube 22. At its end facing toward the cylindrical tube, the pusher tube has multiple slots in the longitudinal direction over at least a portion of its length and over the entire circumference, thus creating here a plurality of leaves 27 separated by slots 26. These leaves 27 can be elastically deflected and are each equipped at their front, free end with a radially outwardly directed flange 28. At the opposite, closed end, pusher tube 25 is equipped with a handle 29.
In order to install spring/damping [0046] element 5, the latter is placed onto cylindrical tube 22; the pusher tube is then slipped over the cylindrical tube until flange 28 is resting against the back side of spring/damping element 5. The pusher tube is then pushed toward the inner ring, thus pushing the spring/damping element over installation taper 23 and elastically deflecting leaves 27. As a result, the spring/damping element travels from the first position (labeled A) on the cylindrical tube to the end of installation taper 25, labeled as position B. As pusher tube 25 is advanced further, spring/damping element 5 slides into the space between shoulders 4 of inner ring 2. The entire device is then pulled off shoulder 4 of inner ring 2.
FIG. 7 depicts a modified sliding [0047] ring 1. It too has an inner ring 2 and an outer ring 3, between which is placed a spring/damping element 5 that is held in place by shoulders 4 of inner ring 2. The annular one-piece spring/damping element has two rim beads 8 and a connecting structure 9 between the rim beads 8 that is constituted in this case by transverse webs 31.
[0048] Rim beads 8 are again made of elastic material, and rest in liquid-tight fashion against the outer circumference of inner ring 2 and the inner circumference of outer ring 3. Transverse webs 31 also rest in more or less liquid-tight fashion in inner ring 2 and on outer ring 3. The result is that a chamber 32 is formed between each two webs. An inflow opening 33, penetrating through the wall of inner ring 2 and configured as a throttle opening, is provided for each chamber. Eccentric 6 has a central groove 34, running around the entire circumference, that communicates with inflow openings 33. Provided in drive shaft 7 is a central inflow orifice 35 at whose end a transverse orifice 36, which opens into groove 34 of the eccentric, branches off. A valve 37 (merely indicated here), e.g., a check valve, can additionally be inserted into inflow opening 25.
[0049] Inflow orifice 35 is connected to a source (not depicted here) of a hydraulic fluid, e.g., oil. Each chamber 32 of the sliding ring can thereby be filled with oil through inflow orifice 35, transverse orifice 36, groove 34, and inflow openings 33.
During normal operation of sliding [0050] ring 1, the latter can be operated without oil in the individual chambers 32, so that the elasticity and stiffness of sliding ring 1 are determined substantially by the material properties and dimensions of spring/damping element 5. If oil is introduced into chambers 32 and held at a specific pressure, sliding ring 1 is thus made “stiffer,” so that the elasticity of sliding ring 1 is determined additionally or substantially by the oil pressure. As explained above, the piston stroke of the individual pistons of the radial piston pump can thereby be increased, which is advantageous in particular when taking in cold oil.
FIG. 9 depicts a modification of the sliding ring shown in FIGS. 7 and 8. The configuration of spring/damping [0051] element 5 is similar to that in FIG. 8, but transverse webs 31 are each penetrated by passthrough openings 38 that are configured as throttle openings and each connect two adjacent chambers 32 to one another. As a result, it is possible to provide only a smaller number of inflow openings 33 in the wall of the inner ring; in the example depicted, there are two inflow openings that once again communicate with groove 34 in the eccentric (not depicted here). This kind of configuration of the sliding ring allows the oil in the respective chambers 32 to flow to adjacent chambers, specifically from the region in which inner ring 2 lies close to outer ring 3 into a region in which that distance is greater. A modified sliding ring as shown in FIGS. 7 and 9 can also be slid onto the inner ring using the installation device described above.
In another embodiment of a sliding [0052] ring 1 according to the present invention, it is proposed to arrange transverse webs 31 on inner ring 2 and on outer ring 3 so that they act as bulkheads and in that way influence the flow of oil in sliding ring 1. The stiffness of sliding ring 1 is thereby increased, especially when the oil's viscosity is higher. An embodiment of this kind, and its manner of operation, are depicted in FIGS. 10 and 11, transverse webs 31 between inner ring 2 and the outer ring being arranged alternatingly on the inner ring and outer ring. Transverse webs 31 do not extend all the way to the respective opposite ring, so that passthrough openings 38 are created here between adjacent chambers 32.
In FIG. 10, force K_e of the eccentric and force K_k of the piston of the radial pump act in opposite directions on the upper side of the spring/damping element. The sliding ring is then compressed at the upper side so that oil is displaced there. The indicated oil flow F then flows from the upper side in two opposite directions toward the lower side of the sliding ring. [0053]
In FIG. 11, the two forces K_e and K_k act in opposite directions on the lower side of sliding [0054] ring 1, so that it is compressed there. The indicated oil flow F then flows from this lower side in both directions toward the upper side of the sliding ring.
As a further embodiment, provision can also be made to mount these bulkheads movably, for example, in the inner ring, in such a way that they are retracted and extended as a function of the oil flow between the individual chambers. [0055]

In another embodiment, provision can also be made to configure sliding

ring

1, having transverse webs 31 acting as bulkheads, as a sealed hydraulic damping element, i.e., without inflow openings. This yields an additional degree of design freedom, since the type of oil in the sealed sliding ring 1 is independent of the type of oil in the pump. For example, silicone oil can be used as the damping oil in the sealed sliding ring 1.



Reference characters

	1	sliding ring
	2	inner ring
	3	outer ring
	4	shoulder
	5	spring/damping element
	6	eccentric
	7	drive shaft
	8	rim bead
	9	connecting structure
	10	damping ring
	11	webs
	21	installation device
	22	cylindrical tube
	23	installation taper
	24	flange
	25	pusher tube
	26	slots
	27	leaves
	28	flange
	29	handle
	31	transverse webs
	32	chambers
	33	inflow openings
	34	groove
	35	inflow orifice
	36	transverse orifice
	37	valve
	38	passthrough openings
	F	oil flow in sliding ring
	K_e	force of eccentric
	K_k	Force of piston

[0057]

Claims

1. A sliding ring (1) for a radial piston pump, having an inner ring (2) and a coaxial outer ring (3) between which a spring/damping element (5) is arranged, wherein the spring/damping element (5) is in one piece and comprises on both sides a respective annular rim bead (8) that rests at the side rim of the inner ring (2) against the latter's outer circumference and at the rim of the outer ring (3) against the latter's inner circumference; and a connecting structure (9) is provided between the rim beads (8).

2. The sliding ring as defined in claim 1, wherein the connecting structure (9) comprises at least one further bead (10), resting against the outer circumference of the inner ring (2) and the inner circumference of the outer ring (3), that is connected to the rim beads (8).

3. The sliding ring as defined in claim 1 or 2, wherein the sliding ring (1) is substantially an arrangement made up of multiple parallel beads (8,10) located next to one another and connected to one another.

4. The sliding ring as defined in one of the foregoing claims, wherein the beads (8,10) are connected to one another by webs (11).

5. The sliding ring as defined in claim 4, wherein the webs (11) extend substantially along the entire lateral circumference of the beads (8,10).

6. The sliding ring as defined in claim 4, wherein the webs (11) extend along only a portion of the lateral circumference of the beads (8,10).

7. The sliding ring as defined in one of claims 4 through 6, wherein the webs (11) are configured as preset breaking points that break during operation of the sliding ring.

8. The sliding ring as defined in one of the foregoing claims, wherein the beads (8,10) are damping rings having a circular cross section.

9. The sliding ring as defined in one of claims 1 through 7, wherein the beads (8,10) comprise a basic body and sealing lips, continuous therewith, that rest against the outer ring (3) and/or inner ring (2).

10. The sliding ring as defined in claim 1, wherein the rim beads (8) rest in liquid-tight fashion against the inner ring (2) and outer ring (3), and are connected to one another via transverse webs (31) that rest against the inner ring (2) and/or outer ring (3), so that along the outer circumference of the spring/damping element (5) between the rim beads (8), a plurality of chambers (32) separated by the transverse webs (31) are created between the inner ring (2) and outer ring (3).

11. The damping ring as defined in claim 10, wherein the chambers (32) each have at least one inflow opening (33,38) for a liquid; and at least one of said inflow openings (33) is provided in the circumferential wall of the inner ring (2).

12. The damping ring as defined in claim 10 or 11, wherein the transverse webs (31) are equipped with passthrough openings (38) so that each two adjacent chambers (32) are thereby connected.

13. The sliding ring as defined in claim 11 or 12, wherein the inflow openings (33) in the wall of the inner ring (2) can be connected to a liquid source.

14. The sliding ring as defined in one of claims 10 through 13, wherein the transverse webs (31) are configured as bulkheads that are arranged on the inner ring (2) and/or outer ring (3).

15. The sliding ring as defined in one of claims 10 through 14, wherein the transverse webs can be retracted into and/or extended out of the inner ring (2) and/or outer ring (3).

16. A device for placing an annular spring/damping element onto an inner ring (2) of a sliding ring, the inner ring having on its side rims circumferential shoulders (4) that hold the spring/damping element (5) in place, characterized by the following features:

a cylindrical tube (22) that has an outside diameter approximately corresponding to that of the inner ring (2) and onto which the spring/damping element (5) can be slid;

an installation taper (23) that is continuous with the cylindrical tube (22), widens conically, and can be placed onto a shoulder (4) of the inner ring (2);

a separate pusher tube (25) that can be slid flush onto the cylindrical tube (22) and that at the end facing toward the cylindrical tube (22) has a plurality of slots in the longitudinal direction over at least a portion of its length over the entire circumference, thus creating a plurality of leaves (27), separated by slots (26), that can be elastically deflected and each have at their front, free end a radially outwardly directed flange (28) that can be brought into contact against the spring/damping element (5) slid onto the cylindrical tube (22) and with which the spring/damping element (5) can be slid, while spreading the leaves (27), over the conical installation taper (23) onto the circumference of the inner ring (2).

17. The device as defined in claim 16, wherein the diameter of the cylindrical tube (22) is smaller than that of the inner ring (2).

18. The device as defined in claim 16 or 17, wherein the pusher tube (25) is equipped, at its end opposite the flange (28), with a handle (29).