Torsional vibration damper

Abstract

The invention relates to a torsional vibration damper (1) which is designed as a dual-mass flywheel, comprising a primary part (3) and a secondary part (4), which are rotatable about a common axis of rotation (5) and are limitedly rotatable relative to one another, wherein a spring damper device (2) acts between the primary part (3) and the secondary part (4), an arc spring (6) of the spring damper device, which is inserted in a spring channel (7), is supported by one end at a stop of the primary part (3) and by the other end at a carrier flange (11), which is associated with the secondary part (4) together with a driven hub (12), and a disc spring diaphragm (13), which is arranged between the carrier flange (11) and a cover element (8) of the primary part (3), seals an interior space, and a cover disk (16), which is fixed at the primary part (3) and forms an axial path stop for the secondary part (4), limits the carrier flange (11) in a clearance-fitting manner, wherein the carrier flange (11) is fixed relative to the cover disk (16) by means of a bayonet connection (20).

Description

Technical Field

[0001] The present invention relates to a torsional vibration damper configured as a dual-mass flywheel, comprising a primary portion and a secondary portion, the primary portion and the secondary portion being rotatable about a common axis of rotation and being rotatable relative to each other in a limited manner, wherein a spring damper device functions between the primary portion and the secondary portion. Background Technology

[0002] Dual-mass flywheels are used to dampen torsional vibrations in the powertrain of motor vehicles. Torsional vibrations are caused by the periodic combustion process of a reciprocating piston internal combustion engine. The firing order of this engine causes rotational inhomogeneity, which is transmitted to the powertrain via the crankshaft. Therefore, in motor vehicles, due to the operating mode of the internal combustion engine, discontinuous torque is transmitted to the powertrain via its crankshaft. This results in torsional vibrations, also known as torsional vibration dampers (ZMS). To dampen these vibrations, a torsional vibration damper is used.

[0003] To dampen torsional vibrations, torsional vibration dampers configured as dual-mass flywheels are known in the prior art. For example, such torsional vibration dampers for aggravation or attenuation are known from DE10 2012 202 255 A1 and DE 10 2016 214 712 A1, which can be inserted in a powertrain between the crankshaft of an internal combustion engine and, for example, a shift disengagement clutch located upstream of a shift transmission. The torsional vibration damper includes a primary portion and a secondary portion, which are rotatable and can rotate limitedly relative to each other, wherein a spring damping device acts between the primary and secondary portions.

[0004] Torsional vibration dampers typically include a disc spring diaphragm that protects the internal space, also known as the spring channel, from grease leaving the damper assembly and from dirt entering the internal space. This configuration is shown in DE10 2017 117 976 A1. Summary of the Invention

[0005] The present invention aims to provide a torsional vibration damper that is structurally and / or functionally improved, wherein assembly is simplified by means of simple, technologically advantageous and cost-effective measures.

[0006] Therefore, the cover plate, which is fixed at the primary section and forms an axial path blocking element for the secondary section, surrounds the bearing flange with a limited gap, wherein the bearing flange is fixed relative to the cover plate by a bayonet-type connector.

[0007] The bayonet-type connector forms a functional fixing structure, via which the main components of the torsional vibration damper are secured in a pre-installed state during assembly. The bayonet connection offers the advantage of simple installation, easily guiding the secondary and primary components together. Here, the bearing flange is shaped-fitted and fixed to the cover plate associated with the primary component via a thrust-rotation connection. Furthermore, the bayonet-type connector decisively simplifies the installation of the disc spring diaphragm, thus avoiding the previously complex installation sequence of the diaphragm protector.

[0008] Furthermore, this solution ensures ample free space in the primary section, also known as the primary flywheel, particularly regarding the screw joint and main riveting at the crankshaft, through which the main components of the torsional vibration damper are assembled. Therefore, a simply constructed primary section can be used, whereby by eliminating the holes in the primary flywheel, a primary section with reduced component thickness can be achieved while maintaining strength and advantageously reducing weight.

[0009] The bayonet-type connectors provide a technologically advantageous, cost-effective, and functionally improved fixation for the various components of the torsional vibration damper. Advantageously, through the disclosed concept, the primary and secondary parts can be easily connected to each other and disassembled without damage.

[0010] According to a preferred embodiment, to form a bayonet connector, the load-bearing flange preferably includes a plurality of radially inwardly oriented fingers, also referred to as noses, distributed circumferentially. These fingers are form-fitted into mating recesses of the cover plate. Alternatively, the bayonet connector is formed by radially outwardly oriented fingers of the cover plate, which are form-fitted into corresponding, equally constructed recesses of the load-bearing flange. The load-bearing flange can be easily, reliably, and permanently secured at the primary portion via the cover plate using a thrust-rotation connection device referred to as the bayonet connector. Regardless of the bayonet connector configuration, the cooperating fingers and recesses are arranged such that the bayonet connector ensures the secure structure even at the maximum rotation angle between the primary and secondary portions.

[0011] The bayonet-type connector enables the assembly of secondary-side sub-assemblies, where the driven hub, disc spring diaphragm, and load-bearing flange are assembled together by means of a riveting connection. In the pre-installation state, the structural unit is axially guided towards the primary section, where the elements forming the bayonet-type connector, acting in conjunction with the load-bearing flange and cover plate, are precisely oriented. Subsequently, the arcuate spring and sliding housing of the spring damper assembly are installed before the final cover element is welded to the primary section. The bayonet-type connector offers a simplified and more cost-effective installation sequence compared to previous solutions.

[0012] Furthermore, it is proposed that during installation, after the finger-shaped piece engages with the corresponding mating gap of the bayonet connector, it rotates ≥90° between the bearing flange and the cover plate. This measure ensures that, in operation, the components of the torsional vibration damper—the bearing flange and the cover plate—remain fixed to prevent axial displacement even when the arc spring of the spring damper device is in its maximum rotational angle of the blocking position.

[0013] Advantageously, a disc spring diaphragm is provided, wherein the disc spring diaphragm is indirectly force-supported on the inner side of the primary portion at the cover element via a friction ring on the radially outer side. By means of the friction ring, wear-optimized and simultaneously sealing support of the disc spring diaphragm at the cover element of the primary portion is achieved.

[0014] A preferred embodiment includes a can-shaped cover plate having a Z-shaped cross-section. The cover plate is supported at the primary portion and positioned such that its bores are aligned to receive a fixing screw, by means of which the torsional vibration damper is tightened to the crankshaft of the internal combustion engine. The cover plate's additional radially outward-pointing flanges include circumferentially projecting fingers, protrusions, or openings that, together with the corresponding mating profile of the supporting flange, form a bayonet-type connection.

[0015] The components secured by bayonet-type connectors, namely the load-bearing flange and the cover plate, are preferably manufactured from metal without cutting, wherein the cover plate is configured, for example, as a sheet metal component and the load-bearing flange is configured as a stamped component. Advantageously, the radially oriented fingers associated with one component and the mating gaps of the corresponding other components are already formed during the manufacturing process of the respective components.

[0016] The bayonet-type connector can also be used in torsional vibration dampers, the secondary part of which does not include the flywheel, also known as the secondary mass.

[0017] According to a preferred embodiment, a centrifugal pendulum associated with a secondary component is integrated into the torsional vibration damper. Advantageously, a bayonet-type connector enables the balancing of the internally located centrifugal pendulum. Attached Figure Description

[0018] The solution is described in detail below with reference to two embodiments and eleven accompanying drawings. However, the solution is not limited to the embodiments shown in the drawings. The drawings show:

[0019] Figure 1 A half-section of a torsional vibration damper configured as a dual-mass flywheel is shown, with a bayonet-type connector of a first variant.

[0020] Figure 2 The basis for showing the absence of a driven hub is shown. Figure 1 A view of a torsional vibration damper;

[0021] Figure 3 Enlarged views of the components secured by bayonet connectors, the cover plate, and the load-bearing flange of the torsional vibration damper are shown.

[0022] Figure 4 A three-dimensional view of the cover plate as a single component is shown;

[0023] Figure 5 A three-dimensional view of the load-bearing flange as a single component is shown;

[0024] Figure 6 Showing according to Figure 1 A view of a torsional vibration damper without a driven hub and an inserted load-bearing flange;

[0025] Figure 7 A diagram illustrating a portion of the first step in installing a torsional vibration damper for mounting a load-bearing flange;

[0026] Figure 8 A diagram illustrating a portion of the second step in installing the load-bearing flange of a torsional vibration damper;

[0027] Figure 9 A diagram illustrating a portion of the third step in installing the load-bearing flange of a torsional vibration damper;

[0028] Figure 10 A half-section of a torsional vibration damper configured as a dual-mass flywheel is shown, with a bayonet-type connector of a second variant.

[0029] Figure 11 The basis for showing the absence of a driven hub is shown. Figure 10 A view of a torsional vibration damper. Detailed Implementation

[0030] Figure 1 and Figure 2 The diagram illustrates the basic structure of a torsional vibration damper 1, which has an integrated spring damper device 2 associated with the powertrain of a motor vehicle (not shown) running on an internal combustion engine. Figure 2 A half-section of the torsional vibration damper 1 is shown in the figure. Figure 2The diagram shows a view without a driven hub. The torsional vibration damper 1, also known as a dual-mass flywheel (ZMS), includes, on the drive side, a primary portion 3 connected to the crankshaft (not shown) of an internal combustion engine and a secondary portion 4 connected to an output device, such as a shift disengagement clutch, and a downstream transmission (not shown). The primary and secondary portions are rotatable about a rotation axis 5 and are rotatable relative to each other with limited capacity. Here, the primary portion 3 is connected to the secondary portion 4 via an arcuate spring 6 of a spring damper assembly 2. The arcuate spring 6 is arranged circumferentially in a spring channel 7 filled with a lubricating material, particularly grease, which is limited by the primary portion 3 and a cover element 8 that is material-fitted to the primary portion 3. Here, the arcuate spring 6 is guided on its outer side at a sliding housing 9 fixed in position within the spring channel 7.

[0031] Furthermore, each arcuate spring 6 is supported by one end at a stop (not shown) in the primary portion 3 and by the other end at a flange wing 10 of the supporting flange 11, which together with the driven hub 12 forms the secondary portion 4. On the radially inner side, away from the primary portion 3, the spring channel 7, and thus the internal space of the torsional vibration damper 1, is sealed by a disc spring diaphragm 13, which, in the pre-installed state of the torsional vibration damper 1, is assembled together with the supporting flange 11 and the driven hub 12 via a riveting connection 14 in the secondary-side sub-assembly to form a structural unit. The disc spring diaphragm 13, also referred to as a disc spring sealing diaphragm, is pre-tightened and supported on the radially outer side via a friction ring 15 at the inner side at the cover element 8, and is elastically deformable in the axial direction to compensate for the limited axial displacement of the secondary portion 4 relative to the primary portion 3. During operation, in the case of relative rotation between the primary portion 3 and the secondary portion 4, the disc spring diaphragm 13 generates frictional force, thus producing a substantial hysteresis.

[0032] Furthermore, the torsional vibration damper 1 includes a cover plate 16, also referred to as a retaining element, which further forms an axial path barrier and restricts relative axial displacement or adjustment between the primary portion 3 and the secondary portion 4. The canister-shaped cover plate 16, having a Z-shaped cross-section, is screwed together with the primary portion 3 at the crankshaft of the internal combustion engine in the installed state via a radially inwardly oriented flange 18. Reciprocally, the cover plate 16 engages in the central opening 21 of the support flange 11 and surrounds the central opening by means of a radially outwardly oriented flange 17, which engages with a gap in an annular gap 19 axially limited by the support flange 11 and the driven hub 12. Here, a bayonet-type connector 20 is provided between the support flange 11 and the cover plate 16, via which the support flange 11, together with the disc spring diaphragm 13 and the driven hub 12, is securely fixed in a form-fitting manner at the cover plate 16 associated with the primary portion 3 by a thrust-rotation connection. The bayonet-type connector 20 simplifies the installation of the disc spring diaphragm 13 and avoids the complex installation sequence of the diaphragm protector. As proposed, the bayonet-type connector 20 includes radially inwardly oriented fingers 22 in the area of ​​the opening 21 of the bearing flange 11, which, during installation, form-fittingly engage with the corresponding recess 23 of the cover plate 16.

[0033] Figure 3 Showing according to Figure 2 A partial enlarged view of the torsional vibration damper 1, and details of the construction of the bayonet connector 20, are shown, illustrating the combined action of the bearing flange 11 and the cover plate 12. The bearing flange 11 includes two radially inwardly oriented fingers 22 offset from each other by 180° in the area of ​​the opening 21. These fingers, during installation, form-fit into the corresponding opening 23 of the cover plate 16. Subsequently, rotation is performed, thereby fixing the components to resist axial movement. Simultaneously, the bayonet connector 20 ensures effective protection during the operation of the torsional vibration damper 1, even at the maximum rotational angle between the bearing flange 11 and the cover plate 12.

[0034] exist Figure 4 In the middle, cover disk 12 and in Figure 5 The load-bearing flange 11 is drawn as a single piece in the three-dimensional drawing. These views illustrate the design of the recess 23 in the cover plate 12 and the finger-shaped member 22 of the load-bearing flange 11, which forms the bayonet connector 20.

[0035] Figure 6 The load-bearing flange 11 is shown in its final position after successful installation. Figures 7 to 9 The installation steps are shown in the diagram. First, the load-bearing flange 11 is installed as follows: Figure 7 As shown, it is conveyed axially in the direction of the arrow. After the fingers 22 of the bearing flange 11 engage with the corresponding recess 23 of the cover plate 12, as in Figure 8 As shown, the bearing flange 11 is rotated clockwise. According to... Figure 9 The bearing flange 11 is in its final position, which is the same as in... Figure 6 The position shown is consistent with that in which the finger 22 is rotated 90° relative to the empty portion 23 by an angle α, which is achieved by the flange wing 10 of the bearing flange 11. Figure 6 The location is illustrated in the diagram.

[0036] The second embodiment of the bayonet connector 30 is in Figure 10 Neutralization Figure 11 As depicted in the figure. Accordingly, the bayonet connector 30 is formed by radially outwardly oriented fingers 32 of the cover plate 16, which are form-fitted and locked into the corresponding recess 33 of the support flange 11 during installation.

[0037] List of reference numerals

[0038] 1 Torsional vibration damper

[0039] 2. Spring damper device

[0040] 3. Elementary Section

[0041] 4th secondary part

[0042] 5. Rotation axis

[0043] 6-curved spring

[0044] 7 Spring Channels

[0045] 8 cover components

[0046] 9 Slipper Boots

[0047] 10 Flange Wings

[0048] 11 bearing flange 1

[0049] 12 driven hubs

[0050] 13 disc spring diaphragms

[0051] 14 Riveting Connection Device 1

[0052] 15 Friction Ring

[0053] 16-coverage disk

[0054] 17 flanges

[0055] 18 flanges

[0056] 19 Annular Gap

[0057] 20 bayonet connectors

[0058] 21 openings

[0059] 22-finger component

[0060] 23. Leave blank space

[0061] 30 bayonet connector

[0062] 32-finger component

[0063] 33 Empty Section

[0064] α angle

Claims

1. A torsional vibration damper (1) configured as a dual-mass flywheel, comprising a primary portion (3) and a secondary portion (4), the primary and secondary portions being rotatable about a common axis of rotation (5) and rotatable relative to each other in a limited manner, wherein a spring damper device (2) acts between the primary portion (3) and the secondary portion (4), the spring damper device having an arcuate spring (6) inserted in a spring channel (7) supported by one end at a stop in the primary portion (3) and by the other end at a bearing flange (11), wherein the bearing flange (11) and a driven hub (12) are associated together with the secondary portion (4), and a disc spring diaphragm (13) disposed between the bearing flange (11) and a cover element (8) of the primary portion (3) seals the internal space. Its features are, A cover plate (16) fixed at the primary portion (3) and forming an axial path blocking member for the secondary portion (4) surrounds the bearing flange (11) with a defined gap, wherein the bearing flange (11) is fixed relative to the cover plate (16) by a bayonet connector (20, 30). As a bayonet connector (20), the bearing flange (11) includes radially inwardly oriented fingers (22) that engage in a form-fitting manner with a corresponding recess (23) of the cover plate (16) during installation. In pre-installation, in the sub-assembly on the secondary side, the driven hub (12), the disc spring diaphragm (13), and the bearing flange (11) are assembled together by means of a riveting connection device (14). During installation, after the fingers (22) engage in their respective corresponding recesses (23), the bearing flange (11) rotates ≥90° between the bearing flange (11) and the cover plate (16).

2. The torsional vibration damper (1) according to claim 1. Its features are, As a bayonet connector (30), the cover plate (16) is provided with radially outward oriented fingers (32), which are shaped to lock into the corresponding recess (33) of the bearing flange (11) during installation.

3. The torsional vibration damper (1) according to any one of the preceding claims. Its features are, In the secondary-side subassembly, the driven hub (12), the disc spring diaphragm (13), and the load-bearing flange (11) are assembled together by means of a riveting connection device (14).

4. The torsional vibration damper (1) according to any one of the preceding claims. Its features are, The disc spring diaphragm (13) is indirectly force-supported on the cover element (8) of the primary part (3) via a friction ring (15) on the radially outer side.

5. The torsional vibration damper (1) according to any one of the preceding claims. Its features are, The can-shaped cover plate (16) surrounds the bearing flange (11) in the region of the central opening (21) by means of a radially outer flange (17) and engages with a gap in an annular gap (19) axially limited by the bearing flange (11) and the driven hub (12), and the radially inwardly oriented flange (18) of the cover plate (16) is fixed together with the primary portion (3) at the crankshaft of the internal combustion engine.

6. The torsional vibration damper (1) according to any one of the preceding claims. Its features are, The cover plate (16) and the bearing flange (11) are made of metal material without cutting.

7. The torsional vibration damper (1) according to any one of the preceding claims. Its features are, Use a secondary part that does not have secondary mass or flywheel (4).

8. The torsional vibration damper (1) according to any one of the preceding claims. Its features are, The secondary part (4) is associated with a centrifugal pendulum.

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