Torque limiter with a spacer rivet and torsional vibration damper

Abstract

The invention relates to a torque limiter (24) for limiting a maximum transmissible torque, comprising a torque limiter input (26) with at least one input flange (28), a friction area (30), a torque limiter output (34) frictionally connected to the input flange (28) via the friction area (30) by an axial preload force (32) for transmitting the torque, and comprising at least one support disc (36), wherein the axial preload force (32) is supported axially on a first support area (38) of the support disc (36) and on a second support area (42) axially opposite the first support area (38) with respect to the input flange (28), wherein at least one spacer rivet (44) is rotationally fixed to the support disc (36), on which the second support area (42) is formed. The invention further relates to a torsional vibration damper (10).

Description

[0001] The invention relates to a torque limiter according to the preamble of claim 1. Furthermore, the invention relates to a torsional vibration damper.

[0002] DE 10 2014 211 603 A1 describes a torque limiter for a torsional vibration damper, comprising a torque limiter input with an input flange, a friction region, and a torque limiter output that is preloaded and frictionally connected to the input flange via the friction region. The torque limiter output comprises a support disc forming a first support region and a further support disc arranged axially spaced therefrom and forming a second support region. The input flange is arranged axially between the support disc and the further support disc.

[0003] The object of the present invention is to make the torque limiter more cost-effective, space-saving and simpler.

[0004] At least one of these objects is achieved by a torque limiter having the features of claim 1. This allows the torque limiter to be designed more cost-effectively and in a more compact manner. The number of components of the torque limiter is reduced. The torque limiter can be manufactured more easily.

[0005] The torque limiter can be installed in a vehicle. The torque limiter can be installed in a drivetrain of the vehicle. The torque transmitted via the torque limiter can be a drive torque for propelling the vehicle.

[0006] The torque limiter can be designed as a slip clutch. The torque limiter output can be connected to the input flange, preloaded by the axial force of a disc spring. The torque limiter input can be axially clamped between the first and second support areas by the axial force of the disc spring. The axial force can form the axial preload force.

[0007] The torque limiter input and torque limiter output can be rotated in parallel when the torque applied to the torque limiter reaches a limit torque and can be rotated against each other when the limit torque is exceeded.

[0008] The friction area can be designed to run dry or wet.

[0009] The torque that can be transmitted from the torque limiter input to the torque limiter output can depend on the axial preload force that frictionally connects the torque limiter output to the torque limiter input. The friction torque provided for transmitting the torque can depend on the axial preload force. The first and second support areas can axially support the axial preload force in both axial directions.

[0010] The second support area can be formed by several spacer rivets arranged distributed around the circumference.

[0011] The spacer rivet can be directly riveted to the support washer. The spacer rivet can be a stepped rivet. The stepped rivet can have a larger diameter in the spacer area between the rivet head and the locking head than in the rivet area that passes through the support washer.

[0012] In a preferred embodiment of the invention, it is advantageous if the input flange is designed as a disc spring flange. This allows the input flange itself to provide the axial preload force for the axial preload between the first and second support areas.

[0013] A preferred embodiment of the invention is advantageous in which the disc spring flange directly abuts the second support region. The disc spring flange can directly abut a rivet head of the spacer rivet having the second support region. The input flange and the spacer rivet can be made of steel. The friction point between the input flange and the second support region can be a steel-to-steel contact.

[0014] In an advantageous embodiment of the invention, the input flange is axially supported on the second support region via a friction lining arranged axially between the second support region and the input flange. This allows the coefficient of friction between the input flange and the second support region to be specifically adjusted. The coefficient of friction can be more constant and consistent. The friction lining can be connected to the spacer rivet in a rotationally fixed manner, in particular, fixedly. The friction lining is made of a material other than steel.

[0015] A preferred embodiment of the invention is advantageous in which the input flange bears directly against the first support area. The input flange can bear directly against the support disc. The input flange and the support disc can be made of steel. The friction point between the input flange and the first support area can be a steel-to-steel contact.

[0016] In a preferred embodiment of the invention, it is advantageous if the input flange is axially supported on the first support region via a friction lining arranged axially between the first support region and the input flange. This allows the coefficient of friction between the input flange and the second support region to be specifically adjusted. The coefficient of friction can be more constant and consistent. The friction lining can be connected to the support disk in a rotationally fixed manner, in particular fixedly. The friction lining is made of a material other than steel.

[0017] In a preferred embodiment of the invention, it is advantageous if the support disc is designed as a single piece with an output hub. The support disc and the output hub can also be designed as separate components that are connected to each other in a rotationally fixed manner, in particular rigidly. The support disc and the output hub can be connected to each other in a form-fitting, force-fitting, and / or material-fitting manner.

[0018] In an advantageous embodiment of the invention, the second support region is formed on a rivet head of the spacer rivet. The rivet head can have a larger diameter than the spacer region of the spacer rivet arranged axially between the rivet head and a closing head. The second support region can be formed on the axial side surface of the rivet head facing the input flange.

[0019] Furthermore, within the scope of the invention, a torsional vibration damper with the features of claim 9 is proposed to achieve at least one of the aforementioned objects. The torsional vibration damper can be designed as a dual-mass flywheel. The torsional vibration damper can be designed to be wet or dry-running.

[0020] The damper output can be connected to the input flange in a form-fitting, force-fitting and / or material-locking manner, in particular in one piece.

[0021] In a preferred embodiment of the invention, it is advantageous if the torque limiter is effectively connected in series downstream of the damper output with respect to torque transmission. The torque limiter can be arranged inside or outside a damper interior that accommodates the spring element. The damper interior can accommodate a lubricant, in particular a lubricating oil or grease.

[0022] Further advantages and advantageous embodiments of the invention emerge from the description of the figures and the illustrations. Character description

[0023] The invention is described in detail below with reference to the figures. They show in detail: Fig. 1: A torsional vibration damper with a torque limiter in a special embodiment of the invention. Fig. 2 to 4: A torsional vibration damper with a torque limiter in a respective further specific embodiment of the invention.

[0024] Fig. 1 shows a torsional vibration damper with a torque limiter in a specific embodiment of the invention. The torsional vibration damper 10 is arranged to reduce torsional vibrations in a vehicle drivetrain. The torsional vibration damper 10 is designed, in particular, as a dual-mass flywheel 12 and comprises a damper input 16 rotatable about a rotational axis 14, a plurality of spring elements 18, in particular arc springs, and a damper output 20 rotatable about the rotational axis 14 and rotatable to a limited extent relative to the damper input 16 against the spring force of the spring elements 18. The damper output 20 is preferably a arc spring flange 22.

[0025] A torque limiter 24 is connected in series downstream of the damper output 20 for torque transmission. The torque limiter 24 comprises a torque limiter input 26 with at least one input flange 28, which is integrally formed with the damper output 20, a friction region 30, and a torque limiter output 34, which is frictionally connected to the input flange 28 via the friction region 30 by an axial preload force 32 for transmitting the torque. The torque limiter output 34 comprises a support disk 36, which forms a first support region 38 and is integrally formed with an output hub 40.

[0026] The input flange 28 is axially clamped between the first support region 38 and a second support region 42 axially opposite the first support region 38 with respect to the input flange 28. The first and second support regions 38, 42 support the axial preload force 32. The second support region 42 is formed by a plurality of spacer rivets 44, which are distributed circumferentially and are each rotationally fixedly coupled to the support disk 36.

[0027] The input flange 28 is designed as a disc spring flange 46, which provides the axial preload force between the first and second support regions 38, 42. The disc spring flange 46 is axially supported on the second support region 42 by a friction lining 48 arranged axially between the second support region 42 and the disc spring flange 46, and by a further friction lining 50 arranged axially between the disc spring flange 46 and the first support region 38. The friction points 56, 58 forming the frictional connection between the torque limiter input 26 and the torque limiter output 34 are thus surface contacts between the disc spring flange 46 and the friction linings 48, 50, thereby reducing the fluctuations in the total friction coefficient between the torque limiter input 26 and the torque limiter output 34.

[0028] The second support region 42 is preferably formed on a rivet head 52 of the spacer rivet 44. A closing head 54 secures the spacer rivet 44 to the support disc 36. The spacer rivet 44 is designed as a stepped rivet and has a larger diameter in the spacer region 60 arranged between the rivet head 52 and the closing head 54 than in the rivet region 62 penetrating the support disc 36.

[0029] Fig. 2 to 4 show a torsional vibration damper with a torque limiter in a respective further specific embodiment of the invention. The structure of the torsional vibration damper in Fig. 2 to Fig. 4 compensates for this Fig. 1 except for the following differences.

[0030] In Fig. Figure 2 shows a torsional vibration damper 10 in which the disc spring flange 46 bears directly against the second support area 42, which is formed on the rivet head 52. If the disc spring flange 46 and the spacer rivet 44 are made of steel, the friction point 56 between the disc spring flange 46 and the second support area 42 is formed by a steel-to-steel contact. The rivet head 52 is preferably hardened to reduce wear on the second support area 42.

[0031] In Fig. Figure 3 shows a torsional vibration damper 10 in which the disc spring flange 46 bears directly against the first support area 38, i.e., the support disc 36. If the disc spring flange 46 and the support disc 36 are made of steel, the friction point 58 between the disc spring flange 46 and the first support area 38 is formed by a steel-to-steel contact.

[0032] Fig.Figure 4 shows a torsional vibration damper 10 in which the disc spring flange 46 bears directly against the first support area 38 and directly against the second support area 42. This creates a steel-to-steel friction on both sides axially, eliminating the need for friction linings, which results in the torque limiter 24 having the narrowest axial dimension. List of reference symbols 10 torsional vibration dampers 12 Dual-mass flywheel 14 axis of rotation 16 Damper input 18 spring element 20 Damper output 22 Bow spring flange 24 torque limiters 26 Torque limiter input 28 Inlet flange 30 friction area 32 axial preload force 34 Torque limiter output 36 support disc 38 first support area 40 Output hub 42 second support area 44 spacer rivet 46 Disc spring flange 48 Friction lining 50 additional friction lining 52 rivet head 54 locking head 56 friction point 58 friction point 60 distance range 62 riveting area QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2014 211 603 A1

[0002]

Claims

[1] Torque limiter (24) for limiting a maximum transmittable torque, comprising a torque limiter input (26) with at least one input flange (28), a friction area (30), a torque limiter output (34) which is frictionally connected to the input flange (28) via the friction region (30) by an axial preload force (32) for transmitting the torque and has at least one support disc (36), where the axial preload force (32) is supported axially on a first support region (38) of the support disc (36) and on a second support region (42) axially opposite the first support region (38) with respect to the input flange (28), characterized by , that at least one spacer rivet (44) is coupled in a rotationally fixed manner to the support disc (36), on which the second support region (42) is formed. [2] Torque limiter (24) according to claim 1, characterized bythat the input flange (28) is designed as a disc spring flange (46). [3] Torque limiter (24) according to claim 1 or 2, characterized by that the disc spring flange (46) lies directly against the second support area (42). [4] Torque limiter (24) according to claim 1 or 2, characterized by that the input flange (28) is axially supported on the second support region (42) via a friction lining (48) arranged axially between the second support region (42) and the input flange (28). [5] Torque limiter (24) according to one of claims 1 to 4, characterized by that the input flange (28) lies directly against the first support area (38). [6] Torque limiter (24) according to one of claims 1 to 4, characterized by that the input flange (28) is axially supported on the first support region (38) via a friction lining (48) arranged axially between the first support region (38) and the input flange (28). [7] Torque limiter (24) according to one of the preceding claims, characterized by that the support disc (36) is designed as a single piece with an output hub (40). [8] Torque limiter (24) according to one of the preceding claims, characterized by that the second support region (42) is formed on a rivet head (52) of the spacer rivet (44). [9] Torsional vibration damper (10) for reducing torsional vibrations, comprising a damper input (16) rotatable about a rotation axis (14), at least one spring element (18), a rotatable about the axis of rotation (14) and counter to the spring force of the at least a spring element (18) with a damper output (20) which can be rotated to a limited extent relative to the damper input (16) and a torque limiter (24) according to one of the preceding claims. [10] Torsional vibration damper (10) according to claim 9, characterized bythat the torque limiter (24) is effectively connected in series downstream of the damper output (20) with respect to a transmission of the torque.

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