Damper assembly

Abstract

The invention relates to a damper assembly, comprising a radially outer rim gear unit (2) having a rim gear (3) and two side plates (5) arranged on the end face thereof, and comprising a radially inner output hub (7), wherein: the rim gear unit (2) and the output hub (7) are rotatable with respect to one another in the circumferential direction and are braced with respect to one another in the circumferential direction via a plurality of spring elements (14); the output hub (7) engages between the two side plates (5); and a plurality of rolling bodies (11) are arranged between in each case an axial hub-side bearing surface (13) of the output hub (7) and an axial plate-side bearing surface (12) of the particular adjacent side plate (5), each rolling body (11) being received in a receptacle (21, 25) which is provided on the hub-side or the plate-side bearing surface (12, 13) and has a ramp structure (22, 26) on both sides in the circumferential direction.

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 are arranged between each axial hub-side bearing surface of the output hub and an axial disk-side bearing surface of the respective adjacent side disk, with each rolling element being received in a receptacle provided on the hub-side or disk-side bearing surface, which has a ramp structure on both sides in the circumferential direction.

[0005] The damper arrangement according to the invention is characterized by an integrated clamping unit by means of which, depending on the degree of rotation of the gear ring assembly and the output hub relative to each other, axial clamping of the gear ring assembly and the output hub against each other is possible, thus axially stiffening the damper arrangement in the event of rotation. This clamping unit is integrated in the area where the two side discs, which, as described, are a fixed part of the gear ring assembly, axially overlap or are adjacent to the output hub. It is implemented by means of several rolling elements arranged between an axial end face or face of the output hub and the adjacent surface of a side disc. Advantageously, at least three, preferably four, rolling elements are provided, which are distributed equidistantly around the circumference.The corresponding surfaces on the output hub and the side plate form bearing surfaces on which the rolling elements are supported and on which they also roll; that is, each bearing surface simultaneously serves as a running surface for the rolling elements. On the hub-side bearing surface or the plate-side bearing surface, a number of receptacles are provided, corresponding to the number of rolling elements, each holding one rolling element. Each receptacle features a ramp structure extending circumferentially to both sides, i.e., inclined surfaces that are not parallel to the respective bearing surface. If the gear assembly and the output hub are not rotated relative to each other, the rolling elements in the respective receptacle are in their lowest position, so that the output hub and the side plate or the gear assembly, respectively, are not axially preloaded or only negligibly preloaded.However, if the gear ring assembly and its side discs rotate relative to the output hub, the rolling elements run from their neutral position onto the respective ramp structure, depending on the direction of rotation. This causes the side discs to be pushed axially away from the output hub, with this axial displacement increasing as they run onto the ramp. Consequently, each side disc is axially preloaded relative to the output hub, thus increasing the component stiffness.

[0006] Simultaneously, this tension creates a restoring force, which ensures that when the rotation is reversed, the side discs also return to their initial position, while the rolling elements return from the ramp structure to their neutral position. This means that when the two elements are rotated relative to each other, the ramp structures exert an axial force on the side discs, pushing them axially away and thereby creating the axial tension. Since this tension varies with the degree of rotation, a damping characteristic is thus defined; that is, the corresponding damping characteristic can be defined by the ramp structures. As a result of the axial tension and damping, there is advantageously no or only negligible noise generation during alternating torques.

[0007] As described, corresponding side discs are provided on both sides of the output hub, and corresponding rolling elements are arranged on both sides of the output hub. Therefore, a uniform axial preload occurs on both sides, meaning that the side discs are axially offset symmetrically and thus preloaded.

[0008] Such a damping function or damping characteristic can be integrated and implemented simply by providing corresponding receptacles only on the hub-side bearing surface or only on the disc-side bearing surface, meaning that each rolling element is held in only one receptacle and runs onto only one ramp structure. A further development provides receptacles on both the hub-side and disc-side bearing surfaces, with each rolling element being held in both a hub-side and a disc-side receptacle. The hub-side and disc-side receptacles are axially congruent, so that each rolling element is held in two receptacles.Since each mounting has corresponding ramp structures, each rolling element consequently runs simultaneously on two ramp structures during a rotation, which results in the axial displacement movement of the side discs being almost twice as large compared to running on only one ramp structure, i.e., the degree of axial preload can be further varied, as well as a variation of the damper characteristic by appropriate design of the ramp structures.

[0009] In a further development of the invention, each receptacle can be designed as a groove-like recess that guides the respective rolling element circumferentially and radially, thus forming the local bearing or running surface. Each rolling element is received in the groove-like recess and its movement is limited radially outwards and inwards by this recess. In the circumferential direction, it can move accordingly so that it can run onto the respective ramp structure. These grooves can be formed directly during the manufacture of the respective side disc, particularly on the side discs. Such a side disc, made from a sheet metal part, can be produced in a stamping-forming process in which the receptacles, which ultimately form the bearing surfaces for the rolling elements and thus the running surfaces for the rolling elements, are simultaneously formed; that is, the raceway is directly incorporated into the tooling.The recesses or groove-shaped depressions in the axial end faces of the output hub can be created, for example, by machining or pressing.

[0010] A further advantageous embodiment of the invention provides that the bearing surfaces or receptacles on the disc side are formed on disc sections which are designed as spring sections via radial slots. Each disc side is provided with several radial slots extending from the inner circumference towards the outer circumference of the side disc, so that a spring section is formed between any two adjacent slots. This makes it possible to vary the axial stiffness of the respective side disc in the area of ​​the disc-side bearing surface or receptacle, which in turn influences the damping characteristic. As described, during rotation, the rolling elements run onto the circumferentially following ramp structure, depending on the direction of rotation, which leads to axial displacement or tensioning of the side discs relative to the output hub.According to a first embodiment of the invention, the ramp structure of each recess can be formed by two ramp surfaces running in opposite directions with a constant gradient in the circumferential direction. The ramp structure, or rather the ramp surfaces, thus change their gradient linearly. In one embodiment, the two ramp surfaces can extend from a common center point, which forms the lowest point of the recess, to both sides, with the two ramp surfaces meeting at the center. The two ramp surfaces thus meet directly at the center and form an obtuse angle. Alternatively, it is conceivable that the two ramp surfaces merge into each other at the center via a rounded section, i.e., that a radius is defined at the transition.

[0011] In a second embodiment of the invention, the ramp structure of each mounting can be formed by two ramp surfaces running in opposite directions with varying slopes in the circumferential direction. Here, the ramp surfaces do not run linearly, but rather increase progressively in their slope, which means that, as the respective rolling element runs further onto the ramp, the axial offset also increases progressively, compared to linearly rising ramp surfaces.

[0012] In one embodiment, the two ramp surfaces can extend from a common center, which forms the lowest point of the recess, to both sides with a radius that changes along the ramp length. In this variant, the radius of each ramp surface is variable along its length, changing symmetrically on both ramp surfaces. Alternatively, the two ramp surfaces can extend from the center to both sides with the same radius. In this variant, the recess is essentially designed as a rounded depression with a constant radius. Both variants, however, are characterized by a progressive slope. As described, the side plates are rigidly connected to the toothed ring. This can be done by welding or, preferably, by riveting.

[0013] The invention is explained below with reference to exemplary embodiments and the drawings. The drawings are schematic representations and show:

[0014] Figure 1 shows a schematic representation of a damper arrangement of a first embodiment according to the invention in section,

[0015] Figure 2 shows a perspective view of the damper arrangement from Figure 1, cut in a second sectioning plane.

[0016] Figure 3 shows a perspective view of the damper arrangement from Figure 1, cut in a third sectioning plane.

[0017] Figure 4 shows a side window,

[0018] Figure 5 shows a representation of the output hub,

[0019] Figure 6 shows an enlarged partial view of the area of ​​the output hub with the formed receptacle.

[0020] Figure 7 shows a perspective view of the damper arrangement from Figure 1, cut away.

[0021] Figure 8 shows a schematic diagram to illustrate the operating principle of axial clamping, shown in the unrotated position.

[0022] Figure 9 shows a view corresponding to Figure 8 in a slightly rotated position; Figure 10 shows a sectional view through a second variant of the damper arrangement with mountings provided on both the output hub and the side discs.

[0023] Figure 11 shows a perspective view of a side window with mounting points provided on it,

[0024] Figures 12-15 show different possible profiles of the recesses, and

[0025] Figure 16 shows an enlarged partial view of a side panel to illustrate spring sections with corresponding images.

[0026] 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.

[0027] 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.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.

[0028] 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 showing a stop projecting radially on the output hub 7, against which a spring element 14 is supported on each side.

[0029] 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.

[0030] Figures 4 and 5 show a side disk 5 and the output hub 7. The side disk 5 has, on its side facing the output hub 7, the previously described rotating bearing surface 12, i.e., a rotating raceway on which each rolling element 11 is supported and rolls. Several bores 18, which serve to accommodate the rivet connections 4, are also shown.

[0031] As previously described, the output hub 7 has a radial leg 10 on which two radially projecting projections 19 are formed. These projections have corresponding stops 20 on both sides for a spring element 14, a simple helical spring. The other ends of the spring elements 14 are supported, as described, by corresponding projections formed on the gear ring that engage radially into the projection structure of the output hub 7. As described, the output hub 7 also has corresponding bearing surfaces 13, which are designed in the form of receptacles 21. Each receptacle 21 is designed as a recess in the form of an elongated groove, with a rolling element 11 being received in each receptacle 21. Each receptacle 21 has a ramp structure 22, which is shown in detail in Figure 6.The ramp structure in the initial example shown has two ramp surfaces 24 extending laterally from a center 23 in opposite directions, rising, for example, with a constant gradient. The ramp surfaces 24 lie on or extend along a pitch circle that has a common center point with the axis of the output hub 7. A rolling element 14 held in the respective receptacle 21 is therefore axially displaced when it moves from the center 23, which occurs in the case of a rotation of the gear ring assembly 2 relative to the output hub 7 from its neutral position. As described, each rolling element is supported and mounted on the two bearing surfaces 12, 13, i.e., on the one hand on the rotating bearing surface 12, which forms the first raceway, and on the other hand in the respective receptacle 21, which forms the second bearing surface 13 or the second raceway.If a relative rotation occurs, the rolling elements roll on both bearing surfaces 12, 13, each running onto a ramp surface 24 depending on the direction of rotation. This causes the elastic side disk 5 to be axially displaced, generating axial tension of the respective side disk 5 towards the output hub 7. The degree of tension increases with the rotation, i.e., the further the rolling elements 11 run onto the respective, linearly rising ramp surface 24.

[0032] Figure 7 shows a sectional view illustrating the arrangement of the two rolling elements 11 between the output hub 7 and the two side disks 5. The receptacles 21 formed on both sides of the output hub 7 are axially opposite each other, so that in the assembled position two rolling elements 11 are always opposite each other.

[0033] The operating principle of the axial clamping is shown in Figures 8 and 9. In Figure 8, the gear ring assembly 2, of which the two side discs 5 are shown, and the output hub 7 are not rotated relative to each other, i.e., the rolling elements 11 are in their neutral position, in which they are each located at the center 23 of their respective receptacle 21. They are clearly supported on the two bearing surfaces 12 of the two side discs 5, as well as on the two bearing surfaces 13 formed by the respective receptacles 21.

[0034] If the gear assembly 2 is now rotated relative to the output hub 7, the rolling elements 11 roll from their neutral position onto the two bearing surfaces 12, 13, as indicated by arrows P1. In doing so, the rolling elements 11 run onto the two ramp surfaces 24 of the two receptacles 21, thus being axially displaced laterally. Since the side discs 5 are supported by the rolling elements 11, the two side discs 5 are also inevitably slightly axially displaced, i.e., pushed outwards, as indicated by arrows P2. This results in the gear assembly 2, which includes the side discs 5, being axially preloaded with the output hub 7, thus stiffening the entire damper assembly 1. The greater the rotation, the further the rolling elements 11 run onto the ramp surfaces 24, the greater the side discs are pushed laterally, and the greater the axial preload.As a result of this tension, the side discs 5, which are only elastically deformed, build up a restoring force, so that when they rotate back, they automatically return to their original position. Therefore, by selecting the slope and the slope geometry, a corresponding damper characteristic curve can be created or defined.

[0035] Figure 10 shows an embodiment of a damper arrangement 1 according to the invention, wherein the same reference numerals are used for identical components. The basic structure of the damper arrangement 1 from Figure 10 is identical to that of the preceding embodiment. The only difference here is that both on the output hub 7, receptacles 21 are formed on both sides (as already provided in the previously discussed example), and corresponding receptacles 25 are formed on the two side discs 5, which are also designed in the form of recesses and each have ramp structures 26, again formed by two ramp surfaces 27 running in opposite directions laterally and circumferentially, which, as assumed in the example shown, also rise linearly from a center 28. The bearing surfaces 12 of the side discs 5 are thus also formed by corresponding receptacles 25 here.

[0036] The cutaway detail view shows the corresponding images 25, with their respective centers 28 from which the ramp surfaces 27 extend on both sides. Preferably, the geometry of the images 25 is identical to the geometry of the images 21, both in terms of length and the shape of the ramp surfaces and their slope; however, the geometries can also vary.

[0037] Since, in this embodiment, corresponding receptacles 21 and 25 are formed on both the output hub 7 and the side disks 5 (see also Figure 11), which are positioned adjacent or congruently in axial terms, each rolling element 11 is consequently received in two receptacles, namely a receptacle 21 and a receptacle 25. When the gear ring assembly 2 is rotated relative to the output hub 7, the rolling elements 11 therefore run onto two ramp surfaces, namely a ramp surface 24 and a ramp surface 27, so that, with regard to the side disk 5, there is a virtually double axial offset, and the side disks are bent or pushed away more axially, and consequently the preload is greater compared to the variant according to the preceding figures at the same angle of rotation.

[0038] Figures 12-15 show four different configurations of the ramp structures. These geometries apply to both the hub-side mounts 21 and the disk-side mounts 25. The different variants are explained above using a mount 21 as an example.

[0039] In the example shown in Figure 12, the two ramp surfaces 24 extend from the center 23 in opposite directions with a constant, linear slope. They meet at an obtuse angle at the center 23. In the embodiment shown in Figure 13, the ramp surfaces 24 again have a constant, linear slope, but they merge into each other via a curve 29 at the center 23.

[0040] In the initial example shown in Figure 14, a recording with a progressive increase is shown. The two ramp surfaces 24 have a varying slope; the slope becomes increasingly steep with increasing distance from the center 23, so that a progressive spherical ramp with a variable radius is formed.

[0041] Finally, Figure 15 shows a variant in which the ramp surfaces 24 are part of a common, spherical receptacle 21, which is defined by a common radius.

[0042] Figure 16 shows a further embodiment of a side disk 5, in which corresponding spring sections 31 are formed via several slots 30 on the inner circumference, with a receptacle 25 being formed on each spring section 31. The axial stiffness of the respective side disk 5 can be additionally adjusted by the design of these spring sections 31, which in turn influences the damper characteristic. Although in the example according to Figure 15 a receptacle 25 is formed on each spring section 31, i.e., corresponding to the second embodiment according to Figure 9, it is equally conceivable to form such spring sections 31 in the first variant as well. In this case, there would be no separate receptacles 25 on the spring sections 31, but only the bearing surfaces 12, which form the raceways for the rolling elements 11. (List of reference symbols)

[0043] Damper assembly, gear ring assembly

[0044] Sprocket

[0045] Riveted joint

[0046] side windows

[0047] in-depth

[0048] Output hub

[0049] transverse leg

[0050] Interlocking

[0051] leg

[0052] rolling elements

[0053] Storage area

[0054] Storage area

[0055] spring element

[0056] transverse leg

[0057] External gearing

[0058] leg

[0059] Drilling

[0060] projection

[0061] stop

[0062] Recording

[0063] Ramp structure

[0064] center

[0065] Ramp area

[0066] Recording

[0067] Ramp structure

[0068] Ramp area

[0069] center

[0070] Rounded 30 slot

[0071] 31 Spring section P1, P2 Arrow

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) are arranged between each axial hub-side bearing surface (13) of the output hub (7) and an axial disk-side bearing surface (12) of the respective adjacent side disk (5), wherein each rolling element (11) is provided in a receptacle (21, 25) on the hub-side or disk-side bearing surface (12, 13), which has a ramp structure (22, 25) on both sides in the circumferential direction. 26) is included.

2. Damper arrangement according to claim 1, characterized in that receptacles (21, 25) are provided both on the hub-side bearing surface and on the disc-side bearing surface (12, 13), wherein each rolling element (11) is received in both a hub-side receptacle (21) and a disc-side receptacle (25).

3. Damper arrangement according to claim 1 or 2, characterized in that the receptacles (21 , 25) are designed as groove-like recesses which guide the respective rolling element (11) circumferentially and radially.

4. Damper arrangement according to one of the preceding claims, characterized in that the disk-side bearing surfaces (12) or receptacles (25) are formed on disk sections which are designed as spring sections (31) via radial slots (30).

5. Damper arrangement according to one of the preceding claims, characterized in that the ramp structure (22, 26) of each receptacle (21, 25) is formed by two ramp surfaces (24, 27) running in opposite directions with a constant slope in the circumferential direction.

6. Damper arrangement according to claim 5, characterized in that the two ramp surfaces (24, 27) extend from a common center (23, 28) which forms the lowest point of the receptacles (21, 25) to both sides, wherein the two ramp surfaces (24, 27) connect to each other in the center (23, 28) or wherein the two ramp surfaces (22, 27) merge into each other in the center (23, 28) via a rounded section (29).

7. Damper arrangement according to one of claims 1 to 4, characterized in that the ramp structure (22, 26) of each receptacle (21, 25) is formed via two ramp surfaces (24, 27) running in opposite directions with varying slopes in the circumferential direction.

8. Damper arrangement according to claim 7, characterized in that the two ramp surfaces (22, 27) extend from a common center (23, 28) which forms the lowest point of the receptacle (21, 25) to both sides with a radius that changes over the length of the ramp, or that the two ramp surfaces (22, 27) extend from the center (23, 28) to both sides with the same radius.

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).

Images