DE102019117157A1 - Torsional vibration damper with a centrifugal pendulum - Google Patents

Abstract

The invention relates to a torsional vibration damper (10) for reducing torsional vibrations, comprising a damper housing (24) which at least partially delimits an interior space (25), at least one spring element (28), a damper input (12) which rotates about an axis of rotation (A) is rotatable and a damper output (30) which is rotatable to a limited extent against the action of the at least one spring element (28) relative to the damper input (12), and a centrifugal pendulum (44) with a pendulum mass carrier (46) and at least one pendulum mass (48), which is received on the pendulum mass carrier (46) along a pendulum track so that it can be deflected to a limited extent, the spring element (28) and the pendulum mass (48) being arranged in the interior (25) and the pendulum mass (48) radially by a radial dimension (L) and by a Axial dimension (B) is arranged axially overlapping to the spring element (28).

Description

The invention relates to a torsional vibration damper with a centrifugal pendulum according to the preamble of claim 1.

A torsional vibration damper is off, for example DE 10 2014 225 663 A1 known. It describes a torsional vibration damper which is designed as a two-mass flywheel. The twin-mass flywheel has a housing which delimits an interior space in which a hub flange is arranged, on which a centrifugal pendulum is attached with a plurality of pendulum masses distributed over the circumference. The twin-mass flywheel comprises a primary flywheel and a secondary flywheel, which can be rotated relative to one another against the force of several arc springs. The bow springs are arranged in the same interior space as the pendulum masses. The pendulum masses are arranged radially inward of the bow springs. With this arrangement of the pendulum masses, the moment of inertia of the pendulum masses can be insufficient.

The object of the present invention is to improve a torsional vibration damper. If the installation space is available, the moment of inertia of the pendulum mass and the spring capacity of the spring element should be increased as much as possible.

At least one of these objects is achieved by a torsional vibration damper with the features according to claim 1. As a result, the spring capacity of the spring element and the moment of inertia of the pendulum mass can be increased with a reduced installation space. The torsional vibrations can be reduced better.

The torsional vibration damper can be arranged in a vehicle. The torsional vibration damper can be arranged in a drive train. The torsional vibration damper can be a two-mass flywheel.

The damper housing can include a primary flywheel. The damper housing can be made in one piece with the damper inlet. The damper input can have a primary flywheel and a cover disk, which can be connected to one another radially outside of the spring element. This connection can be arranged axially spaced from the pendulum mass. The primary flywheel can have, in particular, one-piece first spring engagement means, and the cover plate, in particular one-piece, further first spring engagement means, each for the force-transmitting connection with the spring element.

The spring element can be a helical spring, preferably an arc spring. Several spring elements can be arranged offset from one another on the circumferential side.

The damper output can be an arc spring flange. The damper output can have, in particular one-piece, second spring engagement means for the force-transmitting connection with the spring element.

The centrifugal pendulum can be a bifilar centrifugal pendulum. The pendulum mass can be received in a deflectable manner via at least two bearing points on the pendulum mass carrier.

The pendulum mass carrier can be permanently connected to the damper inlet or damper outlet. The pendulum mass carrier can be made in one piece with the damper inlet or damper outlet. The pendulum mass carrier can be firmly connected to an output hub, in particular riveted or made in one piece.

The first and / or second pendulum mass element can axially have a maximum pendulum mass element width. The axial dimension can be less than or equal to 80%, preferably less than or equal to 50% of the maximum pendulum mass element width. The radial dimension can be greater than or equal to 50%, preferably greater than or equal to 80% of the maximum pendulum mass element width.

The spring element can have a maximum spring element length radially. The radial dimension can be less than or equal to 50%, preferably less than or equal to 20% of the maximum spring element length. The axial dimension can be less than or equal to 50%, preferably less than or equal to 20% of the maximum spring element length.

The spring element can axially have a maximum spring element width. The radial dimension can be less than or equal to 50%, preferably less than or equal to 20% of the maximum spring element width. The axial dimension can be less than or equal to 50%, preferably less than or equal to 20% of the maximum spring element width.

The radial dimension can be larger or smaller than the axial dimension. The radial dimension and the axial dimension can be the same.

In a preferred embodiment of the invention, a radially innermost section of the pendulum mass is arranged radially inward of a radially innermost section of the spring element.

In a special embodiment of the invention, a radially outermost section of the pendulum mass is arranged radially inside of a radially outermost section of the spring element.

In a preferred embodiment of the invention, the damper input can be connected to the spring element in a force-transmitting manner via a first spring engagement means and the first spring engagement means is arranged axially overlapping with the pendulum mass.

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 means, and the second spring engagement means is arranged so as to overlap the pendulum mass radially.

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

In a special embodiment of the invention, the damper output is arranged so that it overlaps radially and axially with respect to the pendulum mass.

In a further special embodiment of the invention, the damper output is arranged axially spaced from the pendulum mass carrier.

In a special embodiment of the invention, the pendulum mass has a pendulum mass element arranged on one side of the pendulum mass carrier and a further pendulum mass element spaced apart from this and on the opposite side of the pendulum mass carrier, the pendulum mass elements being firmly connected to one another. The pendulum mass can have a further pendulum mass element, which is axially received within a recess in the pendulum mass carrier and is firmly connected to the pendulum mass elements.

In a preferred embodiment of the invention, the torsional vibration damper is designed as a two-mass flywheel, the spring element is an arc spring, the damper housing is a primary flywheel and is made in one piece with the damper input, the damper output is an arc spring flange and the pendulum mass carrier is riveted to the arc spring flange and an output hub.

Further advantages and advantageous embodiments of the invention emerge from the description of the figures and the illustrations.

Figure list

• 1: Einen Halbschnitt durch einen Drehschwingungsdämpfer in einer speziellen Ausführungsform der Erfindung.
• 2: Einen Ausschnitt aus 1 in vergrößerter Ansicht.

The invention is described in detail below with reference to the figures. They show in detail:

• 1 : A half section through a torsional vibration damper in a special embodiment of the invention.
• 2 : An excerpt from 1 in enlarged view.

1 shows a half section through a torsional vibration damper 10 in a special embodiment of the invention. The torsional vibration damper 10 is designed as a two-mass flywheel, which is installed in a drive train of a vehicle to reduce torsional vibrations. The torsional vibration damper 10 includes one about an axis of rotation A. rotatable damper inlet 12 that has a screw connection 14th can be connected to a drive element, for example an internal combustion engine.

The damper input 12 includes a primary flywheel 16 that on an outer circumference 18th a starter ring gear 20th and a primary flywheel 22nd and one with the primary flywheel 16 connected cover disk 23 . The damper input 12 is in one piece with a damper housing 24 executed by the primary flywheel 16 and the cover disk 23 is formed and that an interior 25th at least partially limited. The interior 25th is preferably filled with a lubricating fluid, for example a lubricating oil or a lubricating grease.

The damper input 12 can be force-transmitting with one in the interior 25th arranged spring element 26th are in operative connection. The damper input includes for this purpose 12 first spring engagement means formed integrally thereon 26th on the primary flywheel 16 and on the cover plate 23 that a power transmission between the spring element 28 and the damper inlet 12 cause. The torsional vibration damper 10 comprises at least one further spring element arranged at a distance from the circumference. The spring elements 28 are designed as bow springs and in one by the primary flywheel 16 and the cover disk 23 formed spring guide channel 29 axially and radially fixed.

The spring element 28 is on the output side with a damper output 30th connectable in a force-transmitting manner. The damper output 30th is in the area of the spring element 28 in particular arranged centrally to this and has second spring engagement means 32 for operative connection with the spring element 28 on. The damper output 30th is as a bow spring flange 34 executed and extends from the spring element 28 starting radially inwards, where this with a disc spring diaphragm 36 via a rivet element 38 is firmly connected.

The disc spring membrane 36 is axially preloaded on the cover plate 23 on, being effective between the disc spring diaphragm 36 and the cover disk 23 a sliding member 37 for reducing a coefficient of friction is arranged. The disc spring membrane 36 represents a further limitation of the interior space 25th represent.

The damper output 30th is about the rivet element 38 with an output hub 40 directly connected. The output hub 40 has a toothing on an inner circumference 42 for engagement in an output shaft. Furthermore is the damper output 30th with a bifilar centrifugal pendulum 44 firmly connected. The damper output is used for this 30th through the rivet element 38 with a pendulum mass carrier 46 firmly connected. The damper output 30th is axially spaced from the pendulum mass carrier 46 arranged. The centrifugal pendulum 44 comprises several pendulum masses arranged offset to one another on the circumference 48 , each on the pendulum mass carrier 46 are added to a limited extent deflectable along an aerial tramway.

The pendulum mass 48 has one on one side of the pendulum mass carrier 46 arranged pendulum mass element 50 and one at a distance from this and on the opposite side of the pendulum mass carrier 46 arranged further pendulum mass element 50 on. The pendulum mass elements 50 are firmly connected to each other. The pendulum mass 48 is about a self-aligning bearing 54 , here at least one pendulum roller, on the pendulum mass carrier 46 movably recorded.

The spring element 28 and the pendulum mass 48 are in the interior 25th arranged, whereby a lubrication of the contact points of the centrifugal pendulum 44 and the spring elements 28 is effected. The pendulum mass 48 is radial by a radial dimension and axially overlapping by an axial dimension to the spring element 28 arranged. As a result, the moment of inertia of the pendulum mass and at the same time the spring capacity of the spring element can be increased.

The damper output 30th is completely radially and partially axially overlapping to the pendulum mass 48 arranged. A radially innermost section 56 the pendulum mass 48 is radially inward of a radially innermost section 58 of the spring element 28 arranged. Furthermore, there is a radially outermost section 60 the pendulum mass 48 radially inward of a radially outermost portion 62 of the spring element 28 arranged.

The first spring engagement means 26th , here the primary flywheel 16 associated first spring engagement means 26th , is axially overlapping to the pendulum mass 48 and the second spring engagement means 32 is radially overlapping to the pendulum mass 48 arranged. The pendulum mass 48 has a center of gravity of the pendulum mass 64 on, which is radially inward and spaced from the spring element 28 is arranged.

The spring element 28 has a maximum spring element length radially FI and axially a maximum spring element width Fb on. The spring element 28 has a circular cross-section. The maximum spring element length Fl and the maximum spring element width Fb are the same. The respective pendulum mass element 50 axially has a maximum pendulum mass element width Mb on. The maximum pendulum mass element width Mb is smaller than the maximum spring element width Fb and smaller than the maximum spring element length Fl.

In 2 is an excerpt from 1 shown in an enlarged view. The pendulum mass 48 is about a radial dimension L. radially and by an axial dimension B. axially overlapping to the spring element 28 arranged. The pendulum mass element 50 is on one of the spring element 28 facing side of the pendulum mass carrier 46 arranged.

The radial dimension L. is larger than the axial dimension B. . Furthermore is the axial dimension B. less than or equal to 80%, here less than or equal to 50% of the maximum pendulum mass element width Mb . The radial dimension L. is greater than or equal to 50%, here greater than or equal to 80% of the maximum pendulum mass element width Mb . The radial dimension L. and the axial dimension B. is less than or equal to 50%, here less than or equal to 20% of the maximum spring element length. The radial dimension L. and the axial dimension B. is in each case less than or equal to 50%, here less than or equal to 20% of the maximum spring element width. This allows a sufficiently large moment of inertia for the pendulum mass 48 and a large spring capacity of the spring element 28 be provided with the smallest possible installation space.

List of reference symbols

10

Torsional vibration damper

12th

Damper input

14th

Screw connection

16

Primary flywheel

18th

Outer circumference

20th

Starter ring gear

22nd

Primary flywheel

23

Cover disk

24

Damper housing

25th

inner space

26th

first spring engagement means

28

Spring element

29

Spring guide channel

30th

Damper output

32

second spring engagement means

34

Bow spring flange

36

Disc spring diaphragm

38

Rivet element

40

Output hub

42

Interlocking

44

Centrifugal pendulum

46

Pendulum mass carrier

48

Pendulum mass

50

Pendulum mass element

54

Self-aligning bearings

56

radially innermost section

58

radially innermost section

60

radially outermost section

62

radially outermost section

64

Center of gravity of the pendulum

A.

Axis of rotation

B.

Axial dimension

Fb

maximum spring element width

FI

maximum spring element length

Mb

maximum pendulum mass element width

L.

Radial dimension

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102014225663 A1 [0002]

Claims (10)

Torsional vibration damper (10) for reducing torsional vibrations, having a damper housing (24) which at least partially delimits an interior (25), at least one spring element (28), a damper input (12) which can be rotated about an axis of rotation (A) and a Damper output (30), which can be rotated to a limited extent against the action of the at least one spring element (28) relative to the damper input (12), and a centrifugal pendulum (44) with a pendulum mass carrier (46) and at least one pendulum mass (48) which is attached to the pendulum mass carrier ( 46) is received along a pendulum track so that it can be deflected to a limited extent, the spring element (28) and the pendulum mass (48) being arranged in the interior (25), characterized in that the pendulum mass (48) radially by a radial dimension (L) and by a Axial dimension (B) is arranged axially overlapping to the spring element (28). Torsional vibration damper (10) Claim 1 , characterized in that a radially innermost section (56) of the pendulum mass (48) is arranged radially inward of a radially innermost section (58) of the spring element (28). Torsional vibration damper (10) Claim 1 or 2 , characterized in that a radially outermost section (60) of the pendulum mass (48) is arranged radially inward of a radially outermost section (62) of the spring element (28). Torsional vibration damper (10) according to one of the preceding claims, characterized in that the damper input (12) can be connected to the spring element (28) in a force-transmitting manner via a first spring engagement means (26) and the first spring engagement means (26) axially overlapping with the pendulum mass (48) is arranged. Torsional vibration damper (10) according to one of the preceding claims, characterized in that the damper output (30) can be connected to the spring element (28) in a force-transmitting manner via a second spring engagement means (32) and the second spring engagement means (32) overlap radially to the pendulum mass (48). is arranged. Torsional vibration damper (10) according to one of the preceding claims, characterized in that the pendulum mass (48) has a pendulum mass center of gravity (64) which is arranged radially inside and at a distance from the spring element (28). Torsional vibration damper (10) according to one of the preceding claims, characterized in that the damper outlet (30) is arranged so that it overlaps radially and axially with respect to the pendulum mass (48). Torsional vibration damper (10) according to one of the preceding claims, characterized in that the damper outlet (30) is arranged axially spaced from the pendulum mass carrier (46). Torsional vibration damper (10) according to one of the preceding claims, characterized in that the pendulum mass (48) has a pendulum mass element (50) arranged on one side of the pendulum mass carrier (46) and a further pendulum mass element (50) arranged at a distance from this and on the opposite side of the pendulum mass carrier (46) Has pendulum mass element (50), the pendulum mass elements (50) being firmly connected to one another. Torsional vibration damper (10) according to one of the preceding claims, characterized in that the torsional vibration damper (10) is designed as a dual-mass flywheel, the spring element (28) is an arc spring, the damper housing (24) is a primary flywheel (16) and is integral with the damper input (12) ), the damper output (30) is an arc spring flange (34) and the pendulum mass carrier (46) is riveted to the arc spring flange (34) and an output hub (40).

Images