Torsional vibration damper with centrifugal force pendulum

Abstract

The invention relates to a torsional vibration damper (10) for reducing torsional vibrations, comprising a damper housing (24) at least partially defining an interior space (25), at least one spring element (28), a damper input (12) rotatable about an axis of rotation (A), and a damper output (30), the damper output being capable of limited rotation relative to the damper input (12) against the action of the at least one spring element (28), and a centrifugal pendulum (44) having a pendulum mass support (46) and at least one pendulum mass (48), the pendulum mass being mounted on the pendulum mass support (46) and being capable of limited deflection along a pendulum path, wherein the spring element (28) and the pendulum mass (48) are arranged in the interior space (25), the pendulum mass (48) being arranged overlapping the spring element (28) in the radial direction by a radial dimension (L) and in the axial direction by an axial dimension (B).

Description

Technical Field

[0001] The invention relates to a torsional vibration damper with a centrifugal force pendulum according to the general concept of claim 1. Background Art

[0002] For example, a torsional vibration damper is known from DE 10 2014 225 663 A1. It describes a torsional vibration damper designed as a dual-mass flywheel. The dual-mass flywheel has a housing that defines an interior space, in which a hub flange is arranged, and on which a centrifugal pendulum having a plurality of pendulum masses distributed over the circumference is fixed. The dual-mass flywheel comprises a primary flywheel mass and a secondary flywheel mass, which can be twisted relative to each other against the forces of a plurality of arc-shaped damping springs. The arc-shaped damping springs are arranged in the same interior space as the pendulum masses. The pendulum masses are arranged radially within the arc-shaped damping springs. In such a pendulum mass arrangement, the moment of inertia of the pendulum masses may be insufficient. Summary of the invention

[0003] The object of the present invention is to improve a torsional vibration damper. In the existing structural space, the moment of inertia of the pendulum mass and the spring load of the spring element should be increased as much as possible.

[0004] At least one of these objects is achieved by a torsional vibration damper having the features of claim 1. With such a damper, the spring load of the spring element and the moment of inertia of the pendulum mass can be increased while reducing the installation space. Torsional vibrations can be better damped.

[0005] The torsional vibration damper can be arranged in the automobile. The torsional vibration damper can be arranged in the powertrain system. The torsional vibration damper can be a dual mass flywheel.

[0006] The damper housing can include a primary flywheel. The damper housing can be designed as an integral structure with the damper input. The damper input can have a primary flywheel and a cover plate, which can be connected to each other radially outside the spring element. The connection can be arranged at a certain distance axially from the pendulum mass. The primary flywheel can have a first spring engagement device, which is particularly of integral design, and the cover plate can have a further first spring engagement device, which is particularly of integral design, for a force-transmitting connection with the spring element.

[0007] The spring element can be a helical spring, preferably an arc-shaped damping spring. A plurality of spring elements can be arranged staggered relative to one another on the periphery.

[0008] The damper output end can be an arc-shaped damping spring flange. The damper output end can be a second spring engagement device of an integral structure, which is used for force transmission connection with a spring element.

[0009] The centrifugal pendulum can be a double-line centrifugal pendulum. The pendulum mass can be supported pivotably by at least two bearing locations on the pendulum mass support.

[0010] The pendulum mass support can be fixedly connected to the damper input end or the damper output end. The pendulum mass support can form an integral structure with the damper input end or the damper output end. The pendulum mass support can be fixedly connected to the driven hub, in particular, riveted or formed into an integral structure.

[0011] The first and / or second pendulum mass element may have a maximum pendulum mass element width in the axial direction. The axial dimension may be less than or equal to 80% of the maximum pendulum mass element width, preferably less than or equal to 50%. The radial dimension may be greater than or equal to 50% of the maximum pendulum mass element width, preferably greater than or equal to 80%.

[0012] The spring element may have a maximum spring element length in the radial direction. The radial dimension may be less than or equal to 50% of the maximum spring element length, preferably less than or equal to 20%. The axial dimension may be less than or equal to 50% of the maximum spring element length, preferably less than or equal to 20%.

[0013] The spring element may have a maximum spring element width in the axial direction. The radial dimension may be less than or equal to 50% of the maximum spring element width, preferably less than or equal to 20%. The axial dimension may be less than or equal to 50% of the maximum spring element width, preferably less than or equal to 20%.

[0014] The radial dimension may be larger or smaller than the axial dimension. The radial dimension and the axial dimension may be the same.

[0015] In a preferred embodiment of the invention, the radially innermost portion of the pendulum mass is arranged radially in the radially innermost portion of the spring element.

[0016] In a special embodiment of the invention, the radially outermost part of the pendulum mass is arranged radially in the radially outermost part of the spring element.

[0017] In a preferred embodiment of the present invention, the input end of the shock absorber can be connected to the spring element in force transmission via a first spring engagement device, and the first spring engagement device is arranged to overlap with the pendulum mass in the axial direction.

[0018] In an advantageous embodiment of the invention, the damper output can be connected to the spring element in a force-transmitting manner via a second spring engagement device, and the second spring engagement device is arranged overlapping with the pendulum mass in the radial direction.

[0019] In a preferred embodiment of the invention, the pendulum mass has a pendulum mass center of gravity which is arranged radially in the spring element and at a distance from the spring element.

[0020] In a special embodiment of the invention, the damper output is arranged overlapping the pendulum mass in radial and axial directions.

[0021] In another special embodiment of the present invention, the output end of the vibration absorber is arranged at a certain distance from the pendulum mass support in the axial direction.

[0022] In a special embodiment of the invention, the pendulum mass has a pendulum mass element arranged on one side of the pendulum mass support and a further pendulum mass element arranged at a distance from the pendulum mass element on the opposite side of the pendulum mass support, wherein the two pendulum mass elements are fixedly connected to each other. The pendulum mass can have a further pendulum mass element, which is fixed in the axial direction in a recess of the pendulum mass support and is fixedly connected to the pendulum mass element.

[0023] In a preferred embodiment of the present invention, the torsional vibration damper is designed as a dual-mass flywheel, the spring element is an arc-shaped vibration damping spring, the vibration damper housing is a primary flywheel and is integrated with the vibration damper input end, the vibration damper output end is an arc-shaped vibration damping spring flange, and the pendulum mass bracket is riveted to the arc-shaped vibration damping spring flange and a driven wheel hub.

[0024] Further advantages and advantageous embodiments of the invention are apparent from the description of the figures and the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The present invention is described in detail below with reference to the accompanying drawings.

[0026] Figure 1 : Half section of a torsional vibration damper in a special embodiment of the invention.

[0027] Figure 2 : Figure 1 Magnified view of the cross section. DETAILED DESCRIPTION

[0028] Figure 1 1 is a half-section of a torsional vibration damper 10 in a special embodiment of the present invention. The torsional vibration damper 10 is a dual mass flywheel, which is installed in a vehicle powertrain system for reducing torsional vibrations. The torsional vibration damper 10 comprises a damper input 12 rotatable about a rotation axis A, which can be connected to a drive element, such as an internal combustion engine, via a threaded connection 14.

[0029] The damper input 12 comprises a primary flywheel 16 having a flywheel ring 20 and a primary flywheel mass 22 on an outer circumference 18, and a cover plate 23 connected to the primary flywheel 16. The damper input 12 is a one-piece structure with a damper housing 24, which is formed by the primary flywheel 16 and the cover plate 23 and at least partially defines an inner space 25. The inner space 25 is preferably filled with a lubricating fluid, such as lubricating oil or grease.

[0030] The damper input 12 can be effectively connected to a spring element 26 arranged in the inner space 25 in a force-transmitting manner. To this end, the damper input 12 includes a first spring engagement device 26 formed integrally thereon and located on the primary flywheel 16 and the cover disk 23, which transmits force between the spring element 28 and the damper input 12. The torsional vibration damper 10 includes at least one further spring element arranged at a certain distance on the circumferential side. The spring element 28 has an arc-shaped damping spring structure and is arranged and fixed in the axial and radial directions in a spring guide channel 29 formed by the primary flywheel 16 and the cover disk 23.

[0031] The spring element 28 can be connected to the damper output 30 on the output side in a force-transmitting manner. The damper output 30 is arranged in the region of the spring element 28, in particular in the center of the spring element, and has a second spring engagement device 32 for being effectively connected to the spring element 28. The damper output 30 is designed as an arc-shaped damping spring flange 34 and extends radially inward from the spring element 28, where the damper output is fixedly connected to the disc spring diaphragm 36 by a rivet element 38.

[0032] The butterfly spring diaphragm 36 is axially preloaded against the cover disk 23 , wherein a sliding element 37 is effectively arranged between the butterfly spring diaphragm 36 and the cover disk 23 for reducing the friction coefficient. The butterfly spring diaphragm 36 further limits the inner space 25 .

[0033] The damper output 30 is directly fixedly connected to the driven hub 40 via a rivet element 38. The driven hub 40 has a gear train 42 on the inner circumference for meshing into the output shaft. In addition, the damper output 30 is fixedly connected to a dual-line centrifugal pendulum 44. To this end, the damper output 30 is fixedly connected to a pendulum mass support 46 via a rivet element 38. The damper output 30 and the pendulum mass support 46 are arranged at a certain distance in the axial direction. The centrifugal pendulum 44 includes a plurality of pendulum masses 48 arranged staggered on the circumferential side, and the pendulum masses are mounted on the pendulum mass support 46 and can be deflected limitedly along a pendulum track.

[0034] The pendulum mass 48 has a pendulum mass element 50 arranged on one side of the pendulum mass support 46 and another pendulum mass element 50 arranged at a distance from the pendulum mass element on the opposite side of the pendulum mass support 46. The pendulum mass elements 50 are fixedly connected to each other. The pendulum mass 48 is supported movably on the pendulum mass support 46 via a swivel bearing 54, here at least via a swivel roller.

[0035] The spring element 28 and the pendulum mass 48 are arranged in the interior space 25, thereby lubricating the contact points of the centrifugal pendulum 44 and the spring element 28. The pendulum mass 48 is arranged to overlap the spring element 28 in the radial direction with a certain radial dimension and in the axial direction with a certain axial dimension. This can increase the moment of inertia of the pendulum mass and at the same time increase the spring load of the spring element.

[0036] The damper output 30 is arranged completely in the radial direction and partially in the axial direction overlapping the pendulum mass 48. The radially innermost portion 56 of the pendulum mass 48 is arranged radially in the radially innermost portion 58 of the spring element 28. Furthermore, the radially outermost portion 60 of the pendulum mass 48 is arranged radially in the radially outermost portion 62 of the spring element 28.

[0037] The first spring engagement device 26, here the first spring engagement device 26 assigned to the primary flywheel 16, is arranged in the axial direction overlapping the pendulum mass 48, and the second spring engagement device 32 is arranged in the radial direction overlapping the pendulum mass 48. The pendulum mass 48 has a pendulum mass center of gravity 64, which is arranged in the radial direction in the spring element 28 and at a distance therefrom.

[0038] The spring element 28 has a maximum spring element length F1 in the radial direction and a maximum spring element width Fb in the axial direction. The spring element 28 has a circular cross section. The maximum spring element length F1 and the maximum spring element width Fb are identical. The corresponding pendulum mass element 50 has a maximum pendulum mass element width Mb in the axial direction. The maximum pendulum mass element width Mb is smaller than the maximum spring element width Fb and smaller than the maximum spring element length F1.

[0039] Figure 2 yes Figure 1 Enlarged view of a cross section. The pendulum mass 48 is arranged overlapping the spring element 28 in the radial direction by a radial dimension L and in the axial direction by an axial dimension B. The pendulum mass element 50 is arranged on the spring element 28 on the side facing the pendulum mass support 46 .

[0040] The radial dimension L is greater than the axial dimension B. In addition, the axial dimension B is less than or equal to 80% of the maximum pendulum mass element width Mb, and is less than or equal to 50% here. The radial dimension L is greater than or equal to 50% of the maximum pendulum mass element width, and is greater than or equal to 80% here. The radial dimension L and the axial dimension B are each less than or equal to 50% of the maximum spring element length, and are less than or equal to 20% here. The radial dimension L and the axial dimension B are each less than or equal to 50% of the maximum spring element width, and are less than or equal to 20% here. As a result, a sufficiently large moment of inertia of the pendulum mass 48 and a large spring load of the spring element 28 can be provided while occupying as little structural space as possible.

[0041] Reference numerals list

[0042] 10 Torsional vibration damper

[0043] 12 Shock absorber input

[0044] 14 Threaded connector

[0045] 16 Primary Flywheel

[0046] 18 Outer circumference

[0047] 20 Flywheel ring gear

[0048] 22 Primary flywheel mass

[0049] 23 Cover plate

[0050] 24 Shock absorber housing

[0051] 25 Interior Space

[0052] 26 First spring engagement device

[0053] 28 Spring element

[0054] 29 Spring guide channel

[0055] 30 Shock absorber output

[0056] 32 Second spring engagement device

[0057] 34 Arc damping spring flange

[0058] 36 butterfly spring diaphragm

[0059] 38 Riveting elements

[0060] 40 Driven hub

[0061] 42 Gear train

[0062] 44 Centrifugal Pendulum

[0063] 46 Pendulum mass bracket

[0064] 48 Pendulum mass

[0065] 50 Pendulum mass element

[0066] 54 Swing bearing

[0067] 56 Radial innermost part

[0068] 58 radial innermost part

[0069] 60 radial outermost part

[0070] 62 radial outermost part

[0071] 64 Pendulum mass center of gravity

[0072] A Rotation axis

[0073] B Axial dimension

[0074] Fb maximum spring element width

[0075] Fl Maximum spring element length

[0076] Mb Maximum pendulum mass element width

[0077] L Radial size

Claims

1. A torsional vibration damper (10) for reducing torsional vibrations, comprising a damper housing (24) at least partially defining an interior space (25), at least one spring element (28), a damper input (12) rotatable about an axis of rotation (A) and a damper output (30), the damper output being capable of limited rotation relative to the damper input (12) against the action of the at least one spring element (28), and a centrifugal pendulum (44) having a pendulum mass support (46) and at least one pendulum mass (48), the pendulum mass being mounted on the pendulum mass support (46) and being limitedly deflectable along a pendulum path, wherein the spring element (28) and the pendulum mass (48) are arranged in the interior space (25), characterized in that The pendulum mass (48) is arranged overlapping the spring element (28) in the radial direction according to the radial dimension and in the axial direction according to the axial dimension, the damper input end (12) is connected to the spring element (28) in a force-transmitting manner via a first spring coupling device (26), and the first spring coupling device (26) is arranged overlapping the pendulum mass (48) in the axial direction.

2. The torsional vibration damper (10) according to claim 1, characterized in that The radially innermost portion of the pendulum mass (48) is arranged in the radially innermost portion of the spring element (28) in the radial direction.

3. The torsional vibration damper (10) according to claim 1 or 2, characterized in that The radially outermost portion of the pendulum mass (48) is arranged in the radially outermost portion of the spring element (28) in the radial direction.

4. The torsional vibration damper (10) according to claim 1, characterized in that The damper output (30) is connected to the spring element (28) in a force-transmitting manner via a second spring coupling (32), and the second spring coupling (32) is arranged overlapping the pendulum mass (48) in a radial direction.

5. The torsional vibration damper (10) according to claim 1, characterized in that The pendulum mass (48) has a pendulum mass center of gravity (64) which is arranged in the radial direction in the spring element (28) at a distance therefrom.

6. The torsional vibration damper (10) according to claim 1, characterized in that The damper output (30) is arranged overlapping the pendulum mass (48) in radial and axial directions.

7. The torsional vibration damper (10) according to claim 1, characterized in that The damper output end (30) is arranged at a certain distance from the pendulum mass support (46) in the axial direction.

8. The torsional vibration damper (10) according to claim 1, characterized in that The pendulum mass (48) comprises a pendulum mass element arranged on one side of the pendulum mass support (46), and a pendulum mass element spaced apart from the pendulum mass element and arranged on the opposite side of the pendulum mass support (46), wherein the two pendulum mass elements are fixedly connected to each other.

9. The torsional vibration damper (10) according to claim 1 or 2, characterized in that The torsional vibration damper (10) is designed as a dual mass flywheel, the spring element (28) is an arc-shaped damping spring, the damper housing (24) is a primary flywheel (16) and is an integral structure with the damper input end (12), the damper output end (30) is an arc-shaped damping spring flange (34), and the pendulum mass bracket (46) is riveted to the arc-shaped damping spring flange (34) and the driven wheel hub (40).

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