Torsional vibration damper with an axial spring fall protection formed by a flange

Abstract

Torsional vibration damper (1) for a drive train of a motor vehicle, comprising a flange (6), two discs (8a, 8b), and a spring element (10) resiliently supporting the flange (6) relative to the discs (8a, 8b) over a limited range of rotational angles, wherein the flange (6) has both a support region (12) arranged axially between the two discs (8a, 8b) and supported on the spring element (10) in a circumferential direction, and a stop region (14) projecting at least partially radially beyond the spring element (10) from an axial side (13b), wherein, in addition to a first spring damper unit (4) comprising the flange (6), the two discs (8a, 8b), and the spring element (10), a further second spring damper unit (5) is provided, wherein the two spring damper units (4, 5) are inserted to act in series or in parallel between an input (2) and an output (3),and wherein a further second stop region (22) is formed on the flange (6) of the first spring damper unit (4), which at least partially radially projects beyond a spring element (11) of the second spring damper unit (5) from an axial side (23a), wherein the second stop region (22) is formed by a reveal region (24) of a passage (25) penetrating the flange (6) of the first spring damper unit (4), wherein a spring element (11) of the second spring damper unit (5) projects at least partially into the passage (25) of the flange (6) of the first spring damper unit (4).

Description

[0001] The invention relates to a torsional vibration damper which is preferably used in a hybrid / hybridized drive train of a motor vehicle.

[0002] In the field of hybridized powertrains, increasingly stringent demands are being placed on compact powertrain designs. In particular, the modules used should have an axially compact design, while at the same time avoiding unnecessary complexity.

[0003] As state of the art, reference is made, for example, to DE 10 2018 115 904 A1, DE 198 81 099 B3, DE 10 2017 109 855 A1, DE 10 2010 054 550 A1, DE 10 2008 029 685 A1, US 2001 / 0 018 367 A1, FR 3 057 927 A1 and CN 1 11 503 172 A.

[0004] It is therefore an object of the present invention to provide a torsional vibration damper which can be integrated into motor vehicle drive trains in a space-saving manner and at the same time has the simplest possible structure.

[0005] This is achieved according to a first inventive concept by the wording of claim 1. Accordingly, a torsional vibration damper for a (preferably hybridized) drive train of a motor vehicle is claimed, wherein the torsional vibration damper comprises a flange, two discs, and a spring element that resiliently supports the flange relative to the discs over a limited rotation angle range. The flange further comprises both a support region arranged axially between the two discs and supported on the spring element in a circumferential direction, as well as a stop region that at least partially radially projects beyond / covers the spring element from one axial side.

[0006] The design of the flange provides lateral / axial fall protection for the spring element. This, in turn, allows for a simpler design of a torsional vibration damper disc positioned on the axial side of the stop area. This, in turn, enables more compact axial nesting of the torsional vibration damper components and other drivetrain components in the torsional vibration damper's ultimate application area.

[0007] Further advantageous embodiments are claimed in the subclaims and explained in more detail below.

[0008] Accordingly, it is also advantageous if the flange's stop area extends axially beyond a radially inner half of the spring element, and at the same time, a projection area formed on a (second) disc extends axially beyond / covers the spring element on the same axial side of the spring element as the stop area, but toward a radially outer half of the spring element. This ensures the most reliable fall-out protection for the spring element.

[0009] If the (second) disc has a receiving pocket that is open radially inwards and within which the spring element is accommodated, the (second) disc can be manufactured as simply as possible.

[0010] Furthermore, it is advantageous if an additional (first) disc has two radially spaced projections on an axial side facing away from the stop area, partially projecting axially beyond or covering the spring element. This provides a simple and reliable fall-out protection for the spring element on an axial side opposite the stop area of ​​the flange. This allows for the simplest possible design of the torsional vibration damper.

[0011] The production of the flange is further simplified if the stop area is formed by the end face of a sheet metal tab that protrudes or folds over (directly) from the flange. The flange is therefore preferably formed as a sheet metal part, more preferably from a steel sheet.

[0012] Alternatively, in order to further reduce wear and / or further simplify the reworking of the flange, it is also beneficial if the stop area is directly formed by a convex surface area of ​​a sheet metal tab that is extended / folded / bent from the flange.

[0013] Furthermore, it is expedient if the torsional vibration damper is implemented as a so-called double damper with two spring damper units. According to one embodiment of the invention, the torsional vibration damper thus has, in addition to a first spring damper unit comprising the flange, the two discs, and the spring element, a further, second spring damper unit. The two spring damper units are inserted in series or in parallel between an input and an output, and a further (second) stop region is formed on the flange of the first spring damper unit, which at least partially radially projects over / covers a spring element of the second spring damper unit from one axial side. This allows the two spring damper units to be axially nested with one another in a space-saving manner.

[0014] In this regard, it has also proven useful if the additional (second) stop area is formed by a reveal area of ​​a passage penetrating the flange of the first spring damper unit (axially and / or radially). This also provides reliable fall-out protection for the second spring damper unit directly through the flange of the first spring damper unit.

[0015] If a spring element of the second spring damper unit protrudes at least partially into the passage of the flange of the first spring damper unit, the axial installation space requirement is further reduced.

[0016] Furthermore, the torsional vibration damper is implemented as a double spring damper / double damper. This design provides a torsional vibration damper for a (preferably hybridized) drivetrain of a motor vehicle, comprising two spring damper units arranged in series or parallel between an input and an output, each spring damper unit having a flange acting as a primary component, at least one disc acting as a secondary component, and a spring element resiliently supporting the flange relative to the at least one disc over a limited angle of rotation. The flange of a first spring damper unit projects beyond / covers the spring element of the first spring damper unit and / or the spring element of a second spring damper unit at least partially radially from an axial side with a (first and / or second) stop region formed thereby.

[0017] It has also proven advantageous if the flange of the first spring damper unit is directly connected, preferably riveted, to a (first) disc of the second spring damper unit.

[0018] In other words, the invention directly implements axial spring fallout protection via a flange. The flange is designed to limit the springs (spring elements) from moving out of the spring windows (receiving pockets of the discs). In this case, one of the two discs has no interfering contours in the inner area that could prevent the springs from doing so.

[0019] In the case of a double damper, the flange connecting the two dampers is designed to limit the springs from moving out of the spring apertures. Depending on the design, the flange can be used as a limit for both dampers or just for one of the two dampers. The inner discs then have no interfering contours at the points where the flange acts as a limit (especially on the inside of the spring apertures).

[0020] The invention will now be explained in more detail below with reference to figures, in which context various embodiments are also shown.

[0021] They show: Fig. 1 is a longitudinal sectional view of a torsional vibration damper according to the invention according to a first embodiment, wherein the detailed structure of the torsional vibration damper designed as a double damper can be clearly seen, Fig. 2 a perspective view of a spring damper unit of the torsional vibration damper of the Fig. 1 inserted (first) flange together with the spring elements of this first spring damper unit, wherein the interaction of these spring elements with a (first) stop area formed on the flange can be seen, Fig. 3 a perspective view of the Fig. 1 inserted first spring damper unit, wherein the formation of a (second) disc and its interaction via a (first) projection area with the (first) stop area of ​​the flange becomes clear, Fig. 4 a perspective view of the Fig. 3 already shown first spring damper unit from a side showing a (first) disc, wherein this (first) disc forms two radially spaced projection areas, Fig. 5 a longitudinal section of a part of the torsional vibration damper according to Fig. 1, whereby, among other things, the two discs and the spring element of the first spring damper unit are omitted, so that the position and shape of the (first) stop area can be seen more clearly, Fig. 6 a perspective view of the partial assembly of the Fig. 5, whereby several (first) stop areas of the flange distributed in the circumferential direction can be seen, Fig. 7 a perspective view of the partial assembly of the Fig. 5, which shows a side of the second spring damper unit axially facing away from the (first) stop areas of the flange, Fig. 8 is a perspective view of the second spring damper unit as shown in the Fig. 1 and 5 to 7, from an axial side facing the flange of the first spring damper unit in the fully assembled state of the torsional vibration damper, Fig. 9 a longitudinal sectional view of a torsional vibration damper according to the invention according to a second embodiment, wherein that (first) stop region of the flange is now formed by a convex surface region of a correspondingly bent sheet metal tab, and Fig. 10 a perspective view of the Fig. 9 inserted (first) flange together with the spring elements of the first spring damper unit.

[0022] The figures are merely schematic in nature and serve exclusively to understand the invention. The same elements are provided with the same reference numerals. Furthermore, it should be noted that the various features of the different embodiments can, in principle, be freely combined with one another.

[0023] A torsional vibration damper 1 according to the invention according to a first embodiment is provided with the Fig. 1 to 8. The torsional vibration damper 1 is intended for use in a hybridized drive train of a (hybrid) motor vehicle. The torsional vibration damper 1 is further preferably installed between an output shaft of an internal combustion engine and a transmission. Further preferably, an input 2 of the torsional vibration damper 1 is directly and non-rotatably connected to a rotor of an electric motor (not shown for the sake of clarity).

[0024] It should be noted that the directional terms used herein, axial / axial direction, radial / radial direction, and circumferential direction, are to be understood with reference to a central axis of rotation 27 of the torsional vibration damper 1. Consequently, axial / axial direction is to be understood as a direction along / parallel to the axis of rotation 27, radial / radial direction is to be understood as a direction perpendicular to the axis of rotation 27, and circumferential direction is to be understood as a direction along a circular line concentric with the axis of rotation 27.

[0025] In addition to the input 2, the torsional vibration damper 1 has an output 3. However, it should be noted that - contrary to the predominant operating mode (input 2 as torque input and output as torque output) - the input 2 can also serve as a torque output and the output 3 as a torque input, depending on the operating mode of the motor vehicle.

[0026] The torsional vibration damper 1 is in the first embodiment of the Fig. 1 to 8 is implemented as a double damper / double spring damper and accordingly has two spring dampers, designated as the first spring damper unit 4 and the second spring damper unit 5. Both spring damper units 4, 5 are thus designed as spring dampers. In further embodiments according to the invention, however, the torsional vibration damper 1 can also be designed as a simple spring damper with only one spring damper unit, in which case preferably with only the first spring damper unit 4.

[0027] The first spring damper unit 4 is inserted between the input 2 and the second spring damper unit 5. The second spring damper unit 5, in turn, is inserted between the first spring damper unit 4 and the output 3. The two spring damper units 4, 5 are therefore connected / arranged in series with each other. According to further embodiments, it is also possible, in principle, to arrange the two spring damper units 4, 5 in parallel.

[0028] The first spring damper unit 4 is designed here as a bow spring damper. The first spring damper unit 4 essentially has a first flange 6, two disks 8a, 8b and a plurality of first spring elements 10 arranged distributed in the circumferential direction. The first spring elements 10 are arranged such that the first flange 6 is resiliently supported relative to the two disks 8a, 8b within a limited rotation angle range (in the circumferential direction). The two disks 8a, 8b, which are more precisely referred to as the first disk 8a and second disk 8b of the first spring damper unit 4, form in a typical manner, as can be seen from the Fig. 1, Fig. 3 and Fig. 4, a housing, wherein the first flange 6 with its respective support area 12 supported on a first spring element 10 ( Fig. 3) is arranged axially between the two discs 8a, 8b. Each first spring element 10 is supported on the first flange 6 on a first circumferential side (as seen in the circumferential direction) and on the two discs 8a, 8b on a second circumferential side opposite the first circumferential side in the circumferential direction.

[0029] The first disc 8a of the first spring damper unit 4 is directly attached to a support 29 of the input 2, which is further connected to a shaft section 28. The shaft section 28 is therefore also referred to as the input shaft. The first flange 6 extends radially inward from the first spring elements 10 arranged on a common circumference. The first flange 6 is essentially cup-shaped and also extends axially toward the second spring damper unit 5.

[0030] The second spring damper unit 5 is constructed in a similar manner to the first spring damper unit 4. The second spring damper unit 5 is arranged axially next to the first spring damper unit 4. The second spring damper unit 5, which is used in conjunction with the Fig. 5 to 8, has a (second) flange 7 and two discs 9a, 9b forming a housing. The second flange 7 is resiliently supported relative to the two discs 9a, 9b of the second spring-damper unit 5 by means of a plurality of second spring elements 11 distributed in the circumferential direction within a limited rotational angle range. The second flange 7 is located (at least in sections) axially between the two discs 9a, 9b of the second spring-damper unit 5.

[0031] With regard to the second spring damper unit 5, it can be seen that the second flange 7 is attached directly to the output 3 designed as a hub body.

[0032] It can also be seen that the first flange 6 is connected to the first disc 9a of the second spring damper unit 5 (radially inside the first and second spring elements 10, 11) via a rivet connection.

[0033] Furthermore, it should be noted that the first flange 6 according to the invention has a (first) axial stop region 14 for the respective first spring element 10. As described in this regard in Fig. As can be seen in Figure 2, a first stop region 14 is formed directly by the first flange 6 for each first spring element 10. Therefore, several (here four) first stop regions 14 are formed on the first flange 6, evenly distributed in the circumferential direction.

[0034] As can be seen from the Fig. 1 to 6, each first stop region 14 in the first exemplary embodiment is formed by an end face 19 of a sheet metal tab 20 formed / extended directly from the (sheet metal) material of the first flange 6. The sheet metal tab 20 is preferably formed by stamping and bending. This end face 19 is essentially oriented in both the axial direction and the radial direction. The end face 19 / the first stop region 14 is located at the level of the lower radial / radially inner half 16 of the first spring element 10, viewed in the radial direction. Viewed in the axial direction, the end face 19 / the first stop region 14 is arranged directly next to the first spring element 10.The first stop region 14 thus serves as an axial fall-out protection / stop for the first spring element 10, seen in the radial direction, towards the inner half 16 of the first spring element 10 and prevents the first spring element 10 from axially falling out of the two first and second discs 8a, 8b of the first spring damper unit 4 towards a (second) axial side 13b.

[0035] To implement the fall-out protection towards the (second) axial side 13b, the first stop region 14 interacts with a first projection region 15a of the second disc 8b of the first spring damper unit 4, which also prevents the first spring element 10 from axially falling out of the two discs 8a, 8b of the first spring damper unit 4. The first projection region 15a is located, viewed in the radial direction, at the level of the upper radial / radially outer half 17 of the first spring element 10. Viewed in the axial direction, the first projection region 15a is also arranged directly next to the first spring element 10.

[0036] With Fig. In this regard, Figure 3 illustrates that the second disc 8b is open radially within the first projection region 15a due to the design of the first flange 6 and thus has no further interfering contour. A receiving pocket 18 formed by the second disc 8b for receiving the first spring element 10 is thus open radially inward.

[0037] With Fig. 4 shows that the first disc 8a of the first spring damper unit 4, which is arranged on a (first) axial side 13a of the first spring element 10 facing away from the (second) axial side 13b, has two radially spaced projection regions 15a, 15c. A (second) projection region 15b of the first disc 8a covers the radially inner half 16 of the first spring element 10 towards its first axial side 13a. A (third) projection region 15c of the first disc 8a covers the radially outer half 17 of the first spring element 10 towards the first axial side 13a. Thus, the respective first spring element 10 is secured against axially falling out of the two discs 8a, 8b of the first spring damper unit 4 by two projection regions 15b, 15c of the first disc 8a towards the first axial side 13a. A region of the first pane 8a receiving a first spring element 10 is implemented as a window 26.

[0038] In the Fig. 1 to 8 of the first exemplary embodiment, it can further be seen that the first flange 6 not only serves as an axial fall-out protection for the first spring elements 10 (through the first stop region 14), but also as an axial fall-out protection for the second spring elements 11. For this purpose, the first flange 6 has a passage 25 in the form of a through-hole penetrating it axially and radially for each second spring element 11. A (hole) reveal region 24 of the passage 25 serves directly as a (second) axial stop region 22 of the second spring element 11 towards a first axial side 23a of the second spring element 11. Since the second spring elements 11, in contrast to the first spring elements 10 implemented as arc springs, run in a straight line, the passage 25 does not extend over the entire length of the second spring elements 11 in the circumferential direction.

[0039] With Fig. 5, for example, it can be seen that the second spring element 11 is arranged axially and radially at least partially in the passage 25 of the first flange 6 assigned to it.

[0040] For the second spring elements 11, further projection regions 15d to 15f are then provided on the two disks 9a, 9b of the second spring damper unit 5. A (fourth) projection region 15d of the first disk 9a is arranged together with the second stop region 22 on the first axial side 23a of the second spring element 11. The two projection regions 15e, 15f formed on the second disk 9b, which serve as fall-out protection on a second axial side 23b of the second spring elements 11, are referred to as the fifth projection region 15e and the sixth projection region 15f. The fifth projection region 15e can, in principle, like the other projection regions 15a to 15d and 15f, be implemented as an axially flared tab region, or, as implemented here, be formed directly by an edge of the second disk 9b.

[0041] In connection with the Fig. 9 and Fig. Finally, Figure 10 illustrates a second embodiment of the torsional vibration damper 1 according to the invention. Since the torsional vibration damper 1 of this second embodiment essentially corresponds in structure and function to the first embodiment, only the differences between these two embodiments will be described below for the sake of brevity.

[0042] Considering the Fig. 9 and Fig.10, it should be noted in particular that the first flange 6 forms its first stop region 14 in a different way. The first stop region 14 is now formed by a sheet metal tab 20 that is also flared, but bent / curved. The sheet metal tab 20 is essentially folded / bent by an angle of 90°. The immediate first axial stop region 14 for the first spring element 10 is therefore no longer the end face 19 of the sheet metal tab 20, but rather the convex surface region 21 of the sheet metal tab 20 facing the first spring element 10. In other words, the sheet metal tab 20, which forms the first stop region 14, is bent in the direction of the second spring damper unit 5, and the first stop region 14 is formed directly by the convex side surface (surface region 21) thus formed.

[0043] In other words, according to the invention, the flange (first flange 6) is designed to limit the movement of the springs (first and second spring elements 10, 11) out of the spring windows (receiving pocket 18). In this case, one of the two discs (here, the second disc 8b) has no interfering contour (in the inner area) that could prevent the springs from moving out.

[0044] In the case of a double damper, the flange connecting the two dampers (spring damper units 4, 5) is designed to limit the movement of the springs out of the spring windows. Depending on the design, the flange can be used as a limit for both dampers or just for one of them. The (axially) inner discs (second disc 8a of the first spring damper unit 4 and first disc 9a of the second spring damper unit 5) then have no interfering contours at the points where the flange provides the limit (on the inside of the spring windows).

[0045] In a preferred variant, the first damper (first spring damper unit 4) is supported by a contour that is cupped, unlike the rest of the flange. This contour supports the springs at the front face 19 (cut edge).

[0046] In a preferred variant, the first damper is again preferably supported via a contour that is cupped, unlike the rest of the flange. This contour supports the springs on the component surface (in the form of a wing; referred to as surface area 21).

[0047] The second damper (second spring damper unit 5) is supported via a recess (passage 25) in the flange. This has the advantage of allowing the spring (second spring element 11) to accommodate a larger installation space.

[0048] In another variant, the second damper is supported via the component surface. This would be the case if the installation space is large enough to accommodate the flange (first flange 6) without a recess under the spring (second spring element 11).

[0049] In a further preferred design variant, the torsional vibration damper is simply designed as a single damper. The previously explained fall-out protection via the flange can also be used with single dampers. This may be necessary if the installation space is very tight or sharply curved, and there is no room for the inner edge of one of the two discs (first disc 8a and second disc 8b).

[0050] In the case of a single damper, the first damper is preferably supported by a contoured section, unlike the rest of the flange. This section supports the springs (first spring elements 10) at the front face 19 (cutting edge).

[0051] According to an alternative design, the first damper, even in the case of a single damper, is supported by a contour that is cupped, unlike the rest of the flange. This contour supports the springs on the component surface (in the form of a wing; referred to as surface area 21). List of reference symbols 1 torsional vibration damper 2 entrance 3 Exit 4 first spring damper unit 5 second spring damper unit 6 first flange 7 second flange 8a first disc of the first spring damper unit 8b second disc of the first spring damper unit 9a first disc of the second spring damper unit 9b second disc of the second spring damper unit 10 first spring element 11 second spring element 12 Support area 13a first axial side of the first spring element 13b second axial side of the first spring element 14 first stop area 15a first projection area 15b second projection area 15c third projection area 15d fourth projection area 15e fifth projection area 15f sixth projection area 16 inner half 17 outer half 18 Recording pocket 19 Front side 20 sheet metal tabs 21 Surface area 22 second stop area 23a first axial side of the second spring element 23b second axial side of the second spring element 24 reveal area 25 passage 26 windows 27 axis of rotation 28 wave section 29 carriers

Claims

[1] Torsional vibration damper (1) for a drive train of a motor vehicle, comprising a flange (6), two discs (8a, 8b) and a spring element (10) resiliently supporting the flange (6) relative to the discs (8a, 8b) over a limited range of rotation angles, wherein the flange (6) has both a support region (12) arranged axially between the two discs (8a, 8b) and supported in a circumferential direction on the spring element (10), and a stop region (14) projecting at least partially radially beyond the spring element (10) from an axial side (13b), wherein, in addition to a first spring damper unit (4) comprising the flange (6), the two discs (8a, 8b) and the spring element (10), a further second spring damper unit (5) is provided, wherein the two spring damper units (4, 5) are inserted in series or in parallel between an input (2) and an output (3),and wherein a further second stop region (22) is formed on the flange (6) of the first spring damper unit (4), which at least partially radially projects beyond a spring element (11) of the second spring damper unit (5) from an axial side (23a), wherein the second stop region (22) is formed by a reveal region (24) of a passage (25) penetrating the flange (6) of the first spring damper unit (4), wherein a spring element (11) of the second spring damper unit (5) projects at least partially into the passage (25) of the flange (6) of the first spring damper unit (4). [2] Torsional vibration damper (1) according to claim 1, characterized bythat the stop region (14) of the flange (6) projects axially beyond this spring element (10) to a radially inner half (16) of the spring element (10) and at the same time a projection region (15a) formed on a disc (8b) projects axially beyond the spring element (10) to the same axial side (13b) of the spring element (10) as the stop region (14) to a radially outer half (17) of the spring element (10). [3] Torsional vibration damper (1) according to claim 2, characterized by that the disc (8b) has a radially inwardly open receiving pocket (18) within which the spring element (10) is received. [4] Torsional vibration damper (1) according to one of claims 1 to 3, characterized by that a further disc (8a) has, on an axial side (13a) facing away from the stop region (14), two radially spaced projection regions (15b, 15c) partially projecting axially beyond the spring element (10). [5] Torsional vibration damper (1) according to one of claims 1 to 4, characterized by that the stop area (14) is formed by an end face (19) of a sheet metal tab (20) projecting from the flange (6). [6] Torsional vibration damper (1) according to one of claims 1 to 5, characterized by that the stop area (14) is formed by a convex surface area (21) of a sheet metal tab (20) projecting from the flange (6).

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