Damper arrangement

Abstract

Damper arrangement, comprising a radially outer gear ring assembly (2) comprising a gear ring (3) and two side plates (5) arranged on the end face thereof, as well as a radially inner output hub (7), wherein the gear ring assembly (2) and the output hub (7) are rotatable relative to one another in the circumferential direction and are clamped relative to one another in the circumferential direction by means of several spring elements (14), and wherein the output hub (7) engages between the two side plates (5), wherein a plurality of rolling elements (11) are arranged between a respective axial hub-side bearing surface (13) of the output hub (7) and an axial disc-side bearing surface (12) of the respective adjacent side plate (5), wherein each rolling element (11) is arranged in a receptacle (21, 25) provided on the hub-side or disc-side bearing surface (12, 13), which has a ramp structure (22, 26) on both sides in the circumferential direction. has been recorded.

Description

[0001] 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.

[0002] 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.

[0003] The invention is based on the problem of improving such a damper arrangement.

[0004] To solve the problem, in a damper arrangement of the type mentioned above, it is provided according to the invention 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, wherein each rolling element is 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.If the gear 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. Simultaneously, this preload generates a restoring force, which ensures that when the rotation is reversed, the side discs return to their original position, while the rolling elements move from the ramp structure back to their neutral position.This means that when the two elements are twisted relative to each other, the ramp structures exert an axial force on the side discs, pushing them axially away and thereby creating axial tension. Since this tension varies with the degree of twist, a damping characteristic is 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.

[0006] 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.

[0007] 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.

[0008] 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.

[0009] 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 allows the damping characteristic to be influenced.

[0010] As described, during rotation, the rolling elements, depending on the direction of rotation, run onto the circumferentially following ramp structure, 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 receptacle can be formed by two ramp surfaces running in opposite directions with a constant slope in the circumferential direction. The ramp structure, or rather the ramp surfaces, thus change their slope linearly. In one embodiment, it can be provided that the two ramp surfaces extend from a common center, which forms the lowest point of the receptacle, to both sides, with the two ramp surfaces adjoining each other in the center. The two ramp surfaces thus run directly against each other in the center and form an obtuse angle. Alternatively, it is conceivable that the two ramp surfaces merge into each other in the center via a rounded section, i.e.,, that a radius is given in 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, on both sides with a radius that changes along the ramp's 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 on 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.

[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: Fig. 1 a schematic representation of a damper arrangement of a first embodiment according to the invention in section, Fig. 2 a perspective view of the damper arrangement from Fig. 1, cut, in a second cutting plane, Fig. 3 a perspective view of the damper arrangement from Fig. 1, cut, in a third cutting plane, Fig. 4 a representation of a side window, Fig. 5 a representation of the output hub, Fig. 6 an enlarged partial view of the area of ​​the output hub with the formed receptacle, Fig. 7 a perspective view of the damper arrangement Fig. 1, cut, Fig. 8 A schematic diagram to explain the operating principle of axial clamping, shown in the unrotated position, Fig. 9 a view corresponding Fig. 8 in a slightly twisted position, Fig. 10 a sectional view through a second variant of the damper arrangement with mountings provided on both the output hub and the side discs, Fig. 11 a perspective view of a side window with planned photographs, Fig. 12-15 different possible profiles of the recesses, and Fig. 16 An enlarged partial view of a side window to show spring sections with corresponding images.

[0015] Fig. Figure 1 shows a cutaway partial view of a damper arrangement 1 according to the invention, comprising a radially outwardly arranged gear ring assembly 2 comprising a gear ring 3 and riveted connections 4 on both sides thereof (see Fig. 3) Attached side discs 5. The toothed 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.

[0016] Furthermore, a driven hub 7 is provided, which, see the Fig. 2 and Fig. 3, has a T-shaped cross-section, wherein 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, which 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, 13 simultaneously form running surfaces for the rolling elements 11, meaning that they can roll on these bearing surfaces 12, 13.

[0017] How Fig. Figure 1 further shows that 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. Both are spring-loaded against each other via these supports, 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.

[0018] Fig. 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 discs 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.

[0019] In the section view according to Fig. Figure 3 shows the rivet connections 4 in detail. As described, the gear ring 3 has a T-shaped cross-section, with a transverse leg 15 that carries the external teeth 16, and a radial leg 17. The rivet connections 4 engage through this radial leg 17, thereby firmly connecting the side plates 5 to the gear ring 3.

[0020] The Fig. 4 and Fig. Figure 5 shows a side plate 5 and the output hub 7. The side plate 5 has, on its side facing the output hub 7, the previously described circumferential bearing surface 12, i.e., a circumferential raceway on which each rolling element 11 is supported and rolls. Figure 5 also shows several bores 18, which serve to accommodate the rivet connections 4.

[0021] 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, on corresponding projections formed on the gear ring, which engage radially into the projection structure of the output hub 7.

[0022] 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 described in detail in Fig. Figure 6 shows that 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 circumferential 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.

[0023] Fig. 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 assembly position two rolling elements 11 are always opposite each other.

[0024] The operating principle of axial clamping is described in the Fig. 8 and Fig. 9 shown. Fig. 8 are the gear ring assembly 2, of which the two side discs 5 are shown here, and the output hub 7 are not rotated relative to each other, i.e., the rolling elements 11 are in the neutral position, in which they are each located at the center 23 of their respective receptacle 21. They are visibly 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.

[0025] 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 inevitably also slightly axially displaced, i.e., pushed outwards, as indicated by arrows P2. This results in the gear assembly 2, the part of which comprises the side discs 5, being axially clamped to the output hub 7, thus stiffening the entire damper assembly 1. The greater the twisting, the further the rolling elements 11 run on the ramp surfaces 24, and the more the side discs are pushed to the side, and the greater the axial tension.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.

[0026] Fig. 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 is shown in Figure 10. Fig. 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 here by corresponding receptacles 25.

[0027] 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.

[0028] Since in this embodiment both the output hub 7 and the side discs 5 (see also Fig. 11) Since corresponding receptacles 21 and 25 are formed, which are axially adjacent or congruent, 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 consequently run on two ramp surfaces, namely a ramp surface 24 and a ramp surface 27, so that, as far as the side disk 5 is concerned, there is a virtually double axial offset in each case, 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.

[0029] The Fig. 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.

[0030] In the example according to Fig. 12 The two ramp surfaces 24 extend with a constant, linear slope from the center 23 in opposite directions. They meet at an obtuse angle at the center 23.

[0031] In the exemplary embodiment according to Fig. 13 The ramp surfaces 24 again have a constant, linear slope, but they merge into each other via a rounding 29 in the center 23.

[0032] In the initial example according to Fig. Figure 14 shows a recording with a progressive increase. The two ramp surfaces 24 have a varying slope; the slope becomes increasingly steep with increasing distance from the center 23, thus forming a progressive spherical ramp with a variable radius.

[0033] Fig. Figure 15 finally shows a variant in which the ramp surfaces 24 are part of a common, spherical recording 21, which is defined by a common radius.

[0034] Fig. Figure 16 shows a further embodiment of a side disc 5, in which corresponding spring sections 31 are formed via several slots 30 provided on the inner circumference, with a receptacle 25 being formed on each spring section 31. The axial stiffness of the respective side disc 5 can be additionally adjusted by means of the design of these spring sections 31, which in turn can influence the damper characteristic. Although in the example according to Fig. 15 a receptacle 25 is formed on each spring section 31, i.e. according to the second embodiment according to Fig. 9, it is equally conceivable to form such spring sections 31 in the first variant as well. In this case, the spring sections 31 would not have separate receptacles 25, but only the bearing surfaces 12, which form the raceways for the rolling elements 11. Reference symbol list 1 Damper arrangement 2 Gear ring assembly 3 sprocket 4 rivet connection 5 side windows 6. Further Study 7 Output hub 8 crossbars 9 gear teeth 10 thighs 11 rolling elements 12 storage areas 13 storage areas 14 spring element 15 transverse legs 16 External teeth 17 thighs 18 bore 19 lead 20 attacks 21 recording 22 Ramp structure 23 Center 24 ramp area 25 recording 26 ramp structure 27 ramp area 28 Center 29 rounding 30 slots 31 Spring section P1, P2 Arrow

Claims

[1] Damper assembly comprising a radially outer gear ring assembly (2) comprising a gear ring (3) and two side disks (5) arranged at 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 by , that 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) several rolling elements (11) are arranged, wherein each rolling element (11) is received in a receptacle (21, 25) provided on the hub-side or disk-side bearing surface (12, 13), which has a ramp structure (22, 26) in the circumferential direction on both sides. [2] Damper arrangement according to claim 1, characterized by , that both on the hub-side bearing surface and on the disc-side bearing surface (12, 13) receptacles (21, 25) are provided, 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 by , that the receptacles (21, 25) are designed as groove-like recesses that guide the respective rolling element (11) circumferentially and radially. [4] Damper arrangement according to one of the preceding claims, characterized by , 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 by, that the ramp structure (22, 26) of each recording (21, 25) is formed via two ramp surfaces (24, 27) running in opposite directions with a constant gradient in the circumferential direction. [6] Damper arrangement according to claim 5, characterized by , that the two ramp surfaces (24, 27) extend from a common center (23, 28) which forms the lowest point of the recordings (21, 25) to both sides, with the two ramp surfaces (24, 27) joining each other in the center (23, 28) or with the two ramp surfaces (22, 27) merging 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 by , that the ramp structure (22, 26) of each recording (21, 25) is formed via two ramp surfaces (24, 27) running in opposite directions with varying gradients in the circumferential direction. [8] Damper arrangement according to claim 7, characterized by, that the two ramp surfaces (22, 27) extend from a common center (23, 28) which forms the lowest point of the recording (21, 25) on 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) on both sides with the same radius. [9] Damper arrangement according to one of the preceding claims, characterized by , that the two side discs (5) are connected to the toothed ring (3) via rivet connections (4).

Images