Damper assembly

Abstract

The invention relates to a damper assembly comprising a radially outer ring gear unit (2), which comprises a ring gear (3) and two side discs (5) provided on the end face thereof, and a radially inner output hub (7), wherein the ring gear unit (2) and the output hub (7) can be rotated with respect to one another in the circumferential direction and are braced against one another in the circumferential direction via a plurality of spring elements (14), and the output hub (7) engages between the two side discs (5). A plurality of rolling bodies (11) which are held in a common cage are provided, in each case, between a hub-side bearing surface (13) of the output hub (7) and a disc-side bearing surface (12) of the respective adjacent side disc (5), the rolling bodies rolling on the hub-side and the disc-side bearing surfaces (12, 13).

Description

[0001] Damper arrangement

[0002] The invention relates to a damper arrangement comprising a radially outer gear ring assembly comprising a gear ring and two side discs arranged on its end face, and a radially inner output hub, wherein the gear ring assembly and the output hub are rotatable relative to each other in the circumferential direction and are clamped relative to each other in the circumferential direction by several spring elements, and wherein the output hub engages between the two side discs.

[0003] In transmissions, regardless of whether they are used with an internal combustion engine or another drive system, noise is generated by the backlash between meshing gears under alternating torque. To counteract this, it is known to integrate one or more damper arrangements. Such a damper arrangement comprises a radially outer gear ring assembly with a gear ring and two axially, i.e., end-face, side discs arranged on it, which are firmly connected to the gear ring, for example, by welding or riveting.The damper assembly further comprises a radially inner output hub, wherein the gear assembly and the output hub are rotatable relative to each other in the circumferential direction and are preloaded in both circumferential directions by several spring elements arranged between the gear assembly and the output hub, so that they are in a neutral position relative to each other when no torque is applied, from which they can be rotated. The output hub engages radially between the two side discs, so that the two side discs overlap the output hub axially. Due to the integrated springs and the preload, a certain degree of damping can be achieved when a torque is introduced via the gear assembly and transmitted via the output hub.

[0004] The invention is based on the problem of improving such a damper arrangement. To solve this problem, in a damper arrangement of the type mentioned above, the invention provides that several rolling elements held in a common cage are arranged between a hub-side bearing surface of the output hub and a disc-side bearing surface of the respective adjacent side disc, and these rolling elements roll on the hub-side and disc-side bearing surfaces.

[0005] In the damper arrangement according to the invention, axial bearing means are integrated, wherein the output hub with two hub-side bearing surfaces and each side disc with one disc-side bearing surface function as direct elements of the bearing means. According to the invention, several, but at least three, rolling elements are arranged between each axial hub-side bearing surface of the output hub and each axial disc-side bearing surface of the respective adjacent side disc, and these rolling elements are held in a common cage. This is possible because the output hub engages radially between the two side discs, i.e., a side disc is always arranged axially adjacent to the output hub, thus creating an axial overlap area in which the rolling elements can be arranged. The rolling elements run on the hub-side and disc-side bearing surfaces, i.e., they roll on these surfaces.The inventive design allows these hub-side and disc-side bearing surfaces to directly form the running surfaces for the rolling elements. This is possible because, as described, the side discs axially overlap the output hub, so that only the rolling element cage with the rolling elements arranged thereon needs to be integrated between the output hub and the respective disc surface. This integration is also possible in very narrow installation spaces. According to the invention, separate bearing rings are not required and therefore do not need to be integrated, which would again require a corresponding amount of installation space. The inventive design therefore allows for a simplified, direct mounting of the gear ring assembly against the output hub, with the mounting being a rolling bearing, which is correspondingly stable and wear-resistant. Furthermore, the rolling bearing increases the axial stiffness of the damper assembly.

[0006] In a further development of the invention, the output hub can be provided with a T-shaped cross-section comprising a radial leg and an axial leg having internal teeth, wherein the bearing surfaces are formed on both sides of the radial leg. This radial leg can be designed to be correspondingly narrow, i.e., with a small axial width, so that a sufficient distance to the side discs can be formed to accommodate the rolling elements.

[0007] In a first variant, the design can be such that the hub-side bearing surfaces and the disc-side bearing surfaces are configured as axial bearing surfaces. This means that the hub-side bearing surfaces and the disc-side bearing surfaces are purely axial bearing surfaces on which the rolling elements are axially supported or run. Thus, only opposing axial raceways are realized.

[0008] According to a second variant, the hub-side bearing surfaces can have an axial and a radial section, with each bearing surface extending from the radial leg via a rounded transition to the outer circumference of the axial leg. In this variant, the hub-side bearing surface, or running surface, has an axial and a radial component; that is, the running surface is not only formed on the radial leg but also extends onto the axial leg, i.e., the dome of the output hub. The run-out of the raceway is preferably tangential on both the radial leg and the axial leg, i.e., at the dome.

[0009] Furthermore, another embodiment provides for the possibility that each side disk has a Z-shaped cross-section with a radially outer first leg, an adjoining axial second leg, and an adjoining radial inner third leg. This design of the two side disks with a cup or offset makes it possible to increase the axial distance between the axially opposing third legs accordingly, so that sufficient space is provided both for the engagement of the radial leg of the output hub and for the integration of the rolling elements between the respective third legs and the output hub.A further development of this variant provides that the disc-side bearing surfaces have an axial and a radial section, with each bearing surface extending from the second leg via a rounded transition to the third leg. In this variant, the disc-side bearing surface, or running surface, is therefore designed with an axial and a radial component; that is, the running surfaces are not only formed on the radial third leg but also extend onto the axial second leg, i.e., they are located in the cup or offset. Here, too, the run-out of the raceway on the axial second leg and on the third leg is preferably tangential.

[0010] It is conceivable that only the hub-side raceways, only the disc-side raceways, or both the disc-side and hub-side raceways each have an axial and a radial component, so that the rolling elements, i.e., the balls, are guided on the disc side in the hub with axial and radial running components, just as they are guided in the disc-side groove at the transition from the radial leg to the axial leg with axial and radial running components. This design is ultimately the most compact variant.

[0011] As described, the rolling elements are held by the cage or fixed to it. To facilitate this, several pockets are advantageously formed on the cage to accommodate the rolling elements. Naturally, the number of pockets corresponds to the number of rolling elements to be integrated, meaning at least three pockets for every three rolling elements. The cage, similar to the side plates, is a sheet metal component, preferably manufactured in a stamping-forming process. During this process, the pockets can be formed by appropriate shaping. The pockets are preferably designed such that the rolling elements are held captive within them. The rolling elements, i.e., the balls, are essentially clipped into their respective pockets, ensuring they are securely and permanently fixed while still allowing them to roll freely.

[0012] As described, the side discs are also expediently designed as sheet metal components, manufactured using a stamping and forming process. This process allows the bearing surface on each side disc to be machined simultaneously, meaning the raceway is directly integrated into the tooling. On the output hub, the raceway can be machined, for example, or formed during the hub's manufacturing process.

[0013] As described, the side discs are firmly connected to the toothed ring. This can be done by welding, or, preferably, by riveting.

[0014] The invention is explained below with reference to exemplary embodiments and the drawings. The drawings are schematic representations and show:

[0015] Figure 1 shows a schematic representation of a damper arrangement of a first embodiment according to the invention in section,

[0016] Figure 2 shows a perspective view of the damper arrangement from Figure 1, cut in a second sectioning plane.

[0017] Figure 3 shows a perspective view of the damper arrangement from Figure 1, cut in a third sectioning plane.

[0018] Figure 4 shows a perspective view of a side window of the damper assembly from Figure 1.

[0019] Figure 5 shows a perspective view of the output hub of the damper assembly from Figure 1.

[0020] Figure 6 shows a perspective view of a cage including the rolling elements of the damper assembly from Figure 1.

[0021] Figure 7 shows a cutaway perspective view of the damper arrangement from Figure 1, Figure 8 shows a schematic representation of a damper arrangement of a second embodiment according to the invention in section,

[0022] Figure 9 shows a perspective view of the output hub of the damper assembly from Figure 8.

[0023] Figure 10 shows a schematic representation of a damper arrangement of a third embodiment according to the invention in section, and

[0024] Figure 11 shows a perspective view of a side window of the damper assembly from Figure 10.

[0025] Figure 1 shows a sectional view of a damper assembly 1 according to the invention, comprising a radially outwardly arranged gear ring assembly 2 comprising a gear ring 3 and side discs 5 attached to it on both sides by means of rivet connections 4 (see Figure 3). The gear ring 3 has a T-shaped cross-section, i.e., it has two annular recesses 6 at its ends, into which the side discs 5 are inserted. The side discs 5 have a Z-shaped cross-section, i.e., they have a cupped or offset and widen towards their radial inner end at a distance.

[0026] Furthermore, an output hub 7 is provided, which, as shown in Figures 2 and 3, has a T-shaped cross-section. A toothed section 9 with a central oil groove and radially extending oil bores is formed on the inner circumference of the transverse leg 8, while a radial leg 10 engages between the two side discs 5 in their extended area. Several, at least three, and optionally more, rolling elements 11 in the form of balls are arranged between the output hub 7 and the two side discs 5. These rolling elements are supported on bearing surfaces 12 of the side discs 5 and bearing surfaces 13 of the output hub 7 and the radial leg 10, respectively. The bearing surfaces 12 and 13 simultaneously form running surfaces for the rolling elements 11, meaning that they can roll on these bearing surfaces 12 and 13. The rolling elements 11 are held and guided in a cage, which will be described below.As further shown in Figure 1, several spring elements 14 are provided, which are supported circumferentially on one side by a support surface of the gear ring 3 and on the other side by a support surface of the output hub 7. These support surfaces provide mutual spring contact, thereby enabling damping of any rotational movement of the gear ring assembly 2 relative to the output hub 7 from a neutral position in both circumferential directions.

[0027] Figure 2 shows a sectional view in another section plane. The output hub 7 can be seen engaging with its radial leg 10 between the two side disks 5, with the section plane shown here also revealing a stop projecting radially from the output hub 7, against which a spring element 14 is supported on each side.

[0028] The riveted connections 4 are shown in detail in the sectional view according to Figure 3. As described, the gear ring 3 has a T-shaped cross-section, with a transverse leg 15, which carries the external teeth 16, and a radial leg 17. The riveted connections 4 engage through this radial leg 17, thereby firmly connecting the side plates 5 to the gear ring 3.

[0029] Figure 4 shows a perspective view of one of the two side disks 5. This, or rather each side disk 5, has a Z-shaped cross-section, meaning it has a radially outer first leg 18, to which an axial second leg 19 is attached, and to which a radially inner third leg 20 is attached. Each side disk is thus designed with a cup or offset. In the embodiment shown in Figure 1, the respective bearing surface 12 is located exclusively on the radially inner third leg 20, i.e., the rolling elements 11 are supported purely axially by the side disks 5. Figure 4 also shows several bores 25, which serve to receive the rivet connections 4.

[0030] Similarly, a purely axial circumferential bearing surface 13 is formed on the radial leg 10 of the output hub 7 (see Figure 5), so that the rolling elements 11 are also supported purely axially on the output hub 7 (see Figure 1). As already described, the output hub 7 has the radial leg 10, on which, as also shown in Figure 5, two radially projecting projections 21 are formed. These projections have corresponding stops 22 on both sides for a spring element 14, a simple helical spring. The other ends of the spring elements 14 are supported, as described, on corresponding projections formed on the gear ring that engage radially into the projection structure of the output hub 7.

[0031] Figure 6 further shows a perspective view of the aforementioned cage 23, which has a number of pockets 24 corresponding to the number of rolling elements, here four, each pocket holding a rolling element 11. The pockets are designed such that the respective rolling element, here the ball, can be easily clipped in and is held rotatably but securely in the pocket.

[0032] Figure 7 shows, in a perspective, sectional view, the damper arrangement 1 according to the first embodiment of Figure 1. Two rolling elements 11 are shown, which are mounted between the output hub 7 or the radial leg 10 and the two side disks 5 or the respective third leg 20, and which roll on both the disk-side raceways 12 and the hub-side raceways 13. Also shown are the two cages 23 in which the rolling elements 11 are mounted. The cages are arranged such that the rolling elements 11 are axially opposed to each other.

[0033] Figure 8 shows a second embodiment of a damper arrangement 1 according to the invention, where the same reference numerals are used for identical components. The construction of the damper arrangement 1 essentially corresponds to that described for the first variant shown in Figure 1. The only difference here is the mounting of the rolling elements 11 on the hub 7. In this embodiment, the respective hub-side bearing surface 13 extends not only along the radial leg 10, but also onto the transverse leg 8, i.e., onto the outside of the dome. The bearing surface 13, i.e., the running surface, has both an axial and a radial component, so that each spherical rolling element 11 is supported and guided both axially and radially. A radial gap, as exists in the embodiment according to Figure 1 between the respective rolling element 11 and the transverse leg 8, is no longer present here, so that this damper arrangement is somewhat more compact in the radial direction.

[0034] While the side discs 5 in the variant shown in Figure 8 are identical to the side discs 5 in the variant shown in Figure 1, since the rolling elements are only axially supported or mounted on them, the geometric design of the output hub 7 is somewhat different compared to the example in Figure 1, as shown in Figure 9. In this design, the respective bearing surface 13 is designed as a rounded rebate, with the bearing surface 13 extending tangentially in both the radial and axial directions. This is clearly illustrated in Figure 9.

[0035] The geometry of the cage 23 does not change compared to that shown in Figure 1; only the diameter of the cage is marginally different, as the rolling elements 11 now run slightly further radially inside on the transverse leg 10, as described.

[0036] Figure 10 shows a third embodiment of a damper arrangement 1 according to the invention, in which the same components and reference memorandum are used. The embodiment is almost identical to the embodiment according to Figure 8. The only difference compared to the embodiment according to Figure 8 is that the side discs 5 are geometrically slightly different. The respective radially inner third leg 20 is slightly shorter, so that the respective bearing surface 12 now also has both an axial component on the radially inner third leg and a radial component on the axial second leg 19. Each rolling element 11 is visibly received in the cup, i.e., the rounded transition from leg 19 to leg 20, and guided thereon by both an axial and a radial bearing component. Since the bearing arrangement is alsoSince the guide on the output hub 7 has an axial and radial component, as described for the embodiment according to Figure 8, each rolling element is therefore supported and guided both axially and radially on both the hub-side and the disc-side. This embodiment is the most compact of all variants. While the output hub 7 in this variant is identical to the embodiment according to Figure 9, the design of the respective side disc 5 is somewhat different. Here, the running surface 12 is now designed to be quasi-rounded and extends directly into the hub; here, too, the running surface 13 extends tangentially both axially and radially. Compared to the embodiment according to the two variants described above, the radial length of the inner third leg is somewhat shorter.

[0037] The design of the cage 23 again corresponds essentially to that described in Figure 6, with only possible adjustments to the diameter if necessary.

[0038] It should be noted that a variant is also conceivable in which the rolling elements on the radial leg 10 of the hub 7 are supported or roll exclusively axially, while on the side discs 5 they are supported or guided with both axial and radial components, as described in the initial example according to Figure 10. (List of reference symbols)

[0039] Damper assembly, gear ring assembly

[0040] Sprocket

[0041] riveted joint

[0042] side window

[0043] in-depth

[0044] Output hub

[0045] transverse leg

[0046] Interlocking

[0047] leg

[0048] rolling elements

[0049] Storage area

[0050] Storage area

[0051] spring element

[0052] transverse leg

[0053] External gearing

[0054] leg

[0055] first thigh

[0056] second thigh

[0057] third thigh

[0058] projection

[0059] stop

[0060] cage

[0061] Bag

[0062] Drilling

Claims

Patent claims 1. Damper assembly comprising a radially outer gear ring assembly (2) comprising a gear ring (3) and two side disks (5) arranged on its end face, and a radially inner output hub (7), wherein the gear ring assembly (2) and the output hub (7) are rotatable relative to each other in the circumferential direction and are clamped relative to each other in the circumferential direction by several spring elements (14), and wherein the output hub (7) engages between the two side disks (5), characterized in that several rolling elements (11) held in a common cage are arranged between a hub-side bearing surface (13) of the output hub (7) and a disk-side bearing surface (12) of the respective adjacent side disk (5), which roll on the hub-side and disk-side bearing surfaces (12, 13).

2. Damper arrangement according to claim 1, characterized in that the output hub (7) has a T-shaped cross-section with a radial leg (10) and an axial leg (8) having internal teeth (9), wherein the bearing surfaces (13) are formed on both sides of the radial leg (10).

3. Damper arrangement according to claim 2, characterized in that the hub-side bearing surfaces (13) and the disk-side bearing surfaces (12) are designed as axial bearing surfaces (12, 13).

4. Damper arrangement according to claim 2, characterized in that the hub-side bearing surfaces (13) have an axial and a radial section, wherein the respective bearing surface (13) extends from the radial leg (10) via a rounded transition to the outer circumference of the axial leg (8).

5. Damper arrangement according to one of the preceding claims, characterized in that each side disc (5) has a Z-shaped cross-section with a radially outer first leg (18), an axially adjoining second leg (19) and a subsequent radial inner third leg (20).

6. Damper arrangement according to claim 5, characterized in that the disk-side bearing surfaces (12) have an axial and a radial section, wherein the respective bearing surface (12) extends from the second leg (19) via a rounded transition to the third leg (20).

7. Damper arrangement according to one of the preceding claims, characterized in that several pockets (24) are formed on the cage (23) in which the rolling elements (11) are received.

8. Damper arrangement according to claim 7, characterized in that the pockets (24) are designed such that the rolling elements (11) are irretrievably received therein.

9. Damper arrangement according to one of the preceding claims, characterized in that the two side discs (5) are connected to the toothed ring (3) via rivet connections (4).

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