DE102016223127A1 - centrifugal pendulum - Google Patents

Abstract

It is a centrifugal pendulum (10) for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine provided with a about an axis of rotation (12) rotatable and with the drive shaft directly or indirectly connectable support flange (14) and one relative to the support flange (14), in particular via pendulum tracks, pendulum pendulum mass (16) for generating a rotational irregularity opposing return torque, wherein the pendulum mass (16) has a first part of mass (20) and a first partial mass (20) relatively movable second part mass (22), wherein the first part mass (20) and the second sub-mass (22) are elastically and / or friction-damped coupled together. By coupled together sub-masses (20, 22) of the multi-part pendulum mass (16) it is possible for a stop of the pendulum mass (16) to dissipate part of the impact energy within the pendulum mass (16) and at a contact point of the pendulum mass (16) to reduce an impact energy other effective component, so that impact noises are reduced and a low-noise drive train of a motor vehicle is possible.

Description

The invention relates to a centrifugal pendulum, by means of which a rotational irregularity directed against a rotational speed introduced via a drive shaft of a motor vehicle engine can be generated to dampen rotational nonuniformity.

For example DE 10 2008 059 297 A1 a centrifugal pendulum pendulum is known in which a guided over in corresponding raceways rollers relative to a support flange displaceable pendulum mass is provided, which can generate at a speed fluctuation of the rotational speed fluctuation directed opposite restoring torque for damping the speed fluctuation. The support flange has two interconnected via spacer bolts flange parts between which the pendulum mass can oscillate. The pendulum mass has at its pointing in the tangential direction end sides in each case a buffer element made of an elastic rubber material which can strike upon reaching a maximum oscillation angle of the pendulum mass to the respectively assigned spacer bolt of the support flange.

There is a constant need to reduce noise emissions in a drive train of a motor vehicle.

It is the object of the invention to show measures that allow a low-noise drive train of a motor vehicle.

The object is achieved by a centrifugal pendulum with the features of claim 1. Preferred embodiments of the invention are set forth in the dependent claims and the description below, each of which individually or in combination may constitute an aspect of the invention.

According to the invention, a centrifugal pendulum for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine is provided with a support flange rotatable about an axis of rotation and directly or indirectly connectable with the drive shaft and a pendulum mass pendulum-like pendulum mass for generating a rotational non-uniformity relative to the support flange, in particular via pendulum tracks Restoring moments, wherein the pendulum mass has a first partial mass and a first partial mass relatively movable second partial mass, wherein the first partial mass and the second partial mass are coupled elastically and / or friction-damped with each other.

Instead of one-piece pendulum masses the pendulum masses are replaced by two or more movable masses. These sub-masses are preferably connected so that they are effective for the basic function (absorber mass) largely as a unit. In particular, the partial masses may each have proportionally about the same inertial mass. In the direction of the stop action, when the pendulum mass strikes against another component when the maximum oscillation angle is reached, the partial masses can be coupled with elastic and / or (friction) damping effective points and preferably tend to be held in a central position relative to one another. For this purpose, for example prestressed spring elements and / or friction devices can be used. Upon impingement of the pendulum mass it is possible, for example by an offset of the partial masses in the circumferential direction, that not all partial masses simultaneously come into direct contact with the opposing part (for example support flange or further pendulum mass). Optionally, the sub-masses in succession or not all sub-masses come into direct contact. Due to the proportionate mass of the striking part of the mass, which has a lower inertial mass compared to the total mass of the pendulum mass, only the corresponding proportion of the total movement energy is directly effective. The kinetic energy of the other sub-mass is only indirectly, in particular via a spring / damper system, effective. As a result, at least part of the impact energy can be dissipated within the pendulum mass. The maximum force occurring at the contact point can be effectively reduced. By coupled together sub-masses of the multi-piece pendulum mass, it is possible at a stop of the pendulum mass to dissipate part of the impact energy within the pendulum mass and reduce effective at a contact point of the pendulum mass to another component impact energy, so that impact noises are reduced and a low-noise drive train a motor vehicle is possible.

The at least one pendulum mass of the centrifugal pendulum, under the influence of centrifugal force, endeavors to assume a position as far away as possible from the center of rotation. The "zero position" is thus the radially furthest from the center of rotation remote position, which can take the pendulum mass in the radially outer position. At a constant input speed and constant drive torque, the pendulum mass will assume this radially outer position. In the case of speed fluctuations, the pendulum mass deflects along its pendulum track due to its inertia. The pendulum mass can be moved in the direction of the center of rotation. The centrifugal force acting on the pendulum mass is thereby divided into one component tangentially and another component normal to the pendulum track. The tangential force component represents the Restoring force ready, which wants to bring the pendulum mass back to its "zero position", while the normal force component on a speed fluctuations inducing force introduction element, in particular a connected to the drive shaft of the motor vehicle flywheel, acting and generates a counter-torque, which counteracts the speed fluctuation and the introduced speed fluctuations attenuates. For particularly high speed fluctuations, the pendulum mass can thus be maximally swung and assume the radially innermost position. For this purpose, the paths provided in the carrier flange and / or in the pendulum mass have suitable curvatures. In particular, more than one pendulum mass is provided. In particular, several pendulum masses can be distributed uniformly in the circumferential direction. The inert mass of the pendulum mass and / or the relative movement of the pendulum mass to the support flange is designed in particular for damping a specific frequency range of rotational irregularities, in particular an engine order of the motor vehicle engine. In particular, more than one pendulum mass and / or more than one support flange is provided. For example, the support flange is arranged between two pendulum masses. Alternatively, the pendulum mass can be accommodated between two flange parts of the support flange, wherein the flange parts are connected to each other in a Y-shape, for example.

In particular, it is provided that a pointing in a first circumferential direction first right end side of the first partial mass is arranged offset to a pointing in the first circumferential direction second right end side of the second partial mass in the circumferential direction and / or pointing in a direction of the first circumferential direction second circumferential direction first left end face of the first sub-mass is arranged offset in the circumferential direction to a pointing in the second circumferential direction second left end side of the second partial mass. If the maximum oscillation angle of the pendulum mass is reached, only a partial mass or a part of the intended multiple partial masses strikes, so that at least one partial mass does not impact or at least does not impinge simultaneously with the at least one other partial mass. The striking inertial mass and the associated impact energy can be reduced, so that the associated impact noises are reduced.

Preferably, a stop damper which can be hit against the first part mass and / or the second part mass, in particular for limiting a maximum swing angle of the pendulum mass, is provided, wherein the stop damper is connected to the support flange or a further pendulum mass following in the circumferential direction. The stop damper may in particular comprise a damper material which can dissipate impact energy and dampen impact noise. By the stop damper also a defined location for limiting the maximum swing angle of the pendulum mass can be specified so that the pendulum masses does not strike against another component that may not be designed for such loads and / or dampen bad impact noises.

Particularly preferably, the first partial mass and the second partial mass are held together by a holding force that can be overcome by tangential striking, in particular by friction. This makes it possible that the pendulum mass behaves like a common solid, as long as the pendulum mass does not abut a component and the holding force is overcome by the sudden impact. A detuning of the centrifugal pendulum by a change in the mass moment of inertia due to a relative movement of the masses relative to each other can be avoided.

• 1: eine schematische Prinzipdarstellung eines Fliehkraftpendels in einer ersten Ausführungsform,
• 2: eine schematische Prinzipdarstellung eines Fliehkraftpendels in einer zweiten Ausführungsform,
• 3: eine schematische Prinzipdarstellung eines Fliehkraftpendels in einer dritten Ausführungsform,
• 4a: eine schematische Draufsicht und Radialansicht eines konkreten ersten Ausführungsbeispiels eines Fliehkraftpendels in einer Neutrallage,
• 4b: eine schematische Draufsicht und Radialansicht des Fliehkraftpendels aus
• 4a in einer Extremlage,
• 5: eine schematische Schnittansicht des Fliehkraftpendels aus 4a,
• 6a: eine schematische Draufsicht und Radialansicht eines konkreten zweiten Ausführungsbeispiels eines Fliehkraftpendels in einer Neutrallage,
• 6b: eine schematische Draufsicht und Radialansicht des Fliehkraftpendels aus
• 6a in einer Extremlage und
• 7: eine schematische Schnittansicht des Fliehkraftpendels aus 6a.

The invention will now be described by way of example with reference to the accompanying drawings with reference to preferred embodiments, wherein the features shown below, both individually and in combination may represent an aspect of the invention. Show it:

• 1 FIG. 2 is a schematic diagram of a centrifugal pendulum in a first embodiment, FIG.
• 2 FIG. 2 is a schematic diagram of a centrifugal pendulum in a second embodiment, FIG.
• 3 FIG. 2 is a schematic diagram of a centrifugal pendulum in a third embodiment, FIG.
• 4a FIG. 2 is a schematic plan view and radial view of a concrete first exemplary embodiment of a centrifugal pendulum in a neutral position, FIG.
• 4b : A schematic plan view and radial view of the centrifugal pendulum
• 4a in an extreme situation,
• 5 : A schematic sectional view of the centrifugal pendulum 4a .
• 6a FIG. 2 is a schematic top view and radial view of a concrete second embodiment of a centrifugal pendulum in a neutral position. FIG.
• 6b : A schematic plan view and radial view of the centrifugal pendulum
• 6a in an extreme position and
• 7 : A schematic sectional view of the centrifugal pendulum 6a ,

This in 1 shown centrifugal pendulum 10 has one about a rotation axis 12 rotatable support flange 14 on, which may be provided in a drive train of a motor vehicle and in particular is coupled to a drive shaft of an automotive engine in order to dampen occurring with the frequency of the engine orders rotational irregularities can. With the carrier flange 14 is a pendulum mass 16 and another pendulum mass 18 coupled pendelbar. The pendulum masses 16 . 18 each have a first partial mass 20 and a second submass 22 on that via a spring / damper system 24 are coupled. The spring / damper system 24 For example, a preloaded spring 26 and a friction device 28 exhibit. The maximum swing angle of the pendulum masses 16 . 18 is by stopper connected to the support flange 30 limited. If the respective pendulum mass 16 . 18 on the stop damper 30 with the one part mass 20 . 22 strikes, the other submass 22 . 20 against the spring force of the spring 26 and the friction force of the friction device 28 a relative movement on the on the stop damper 30 damaged part mass 20 . 22 to perform and this part of the other part of the mass 22 . 20 Applicable impact energy in the friction device 28 dissipate and / or in the spring 26 caching, so that the other part mass 22 . 20 if at all, can only strike with a lower impact energy. When the pendulum mass 16 . 18 from the stop damper 30 Moving away, the spring can 26 the other pendulum mass 22 . 20 push back in the direction of their previous starting position.

There are also further variants with divided pendulum masses 16 . 18 possible. For example, the stop points on the stop damper 30 the carrier flange 14 and / or the outer contact areas of the pendulum masses 16 . 18 with damping elements 32 be provided, as in 2 shown. It is also conceivable that the pendulum masses16, 18 not against a stop damper 30 on the carrier flange 14 collide, but that overlap the ranges of movement of the pendulum masses 16, 18 and the pendulum masses16, 18 can so mutually abut, as in 3 shown.

At the in 4a and 4b shown centrifugal pendulum 10 in which, for reasons of simplified representation, only one of several pendulum masses 16 can be shown, for example, on the support flange 14 the pendulum masses 16 through pivot bearings 34 (preferably with low friction) be connected. The pendulum masses 16 have at least two partial masses 20 . 22 on. These are movable with each other and with a spring / damper system 24 , which is designed, for example, similar to a clutch disc damper equipped. The feather 26 of the spring / damper system 24 can in particular be biased and guaranteed on both sides by the installation in spring windows of the sub-masses 20 . 22 a force effect when striking one of the sub-masses 20 . 22 , Furthermore, but this is also a new neutral position of the sub-masses 20 . 22 guaranteed after the impact process.

In 5 is an arrangement of a spring 26 between the sub-masses 20 . 22 shown. In addition to the illustrated variant further possibilities are given. So can the pivot bearings 34 the sub-masses 20 . 22 be combined, for example, a partial mass 20,22 with low-friction bearing 34 on the carrier flange 14 and the other part mass 22 . 20 coaxial on the first part mass 20 . 22 optionally stored with a higher frictional resistance. Likewise, various types of spring, for example, leg springs, disc springs, elastomer body, etc., and for acting as a damper friction device, such as Reibscheibeneinrichtungen etc., possible.

At the in 6a . 6b and 7 shown centrifugal pendulum 10 is an alternative arrangement to that in 4a and 4b shown centrifugal pendulum 10 shown at the pendulum mass 16 in more than two parts 20 . 22 shared. As a difference to the 4a and 4b shown arrangement can be seen that in both directions of movement in each case the same, for example, centrally arranged part mass 22 at the stop damper 30 has direct contact. Through the two other sub-masses 20 can be realized as an advantageous symmetrical load of all components. Also, in such an arrangement advantageously a friction-minimized mounting of the pendulum mass 16 and a frictional storage of the sub-masses 20 . 22 be realized with each other, whereby an increased energy absorption is possible during the impact process.

LIST OF REFERENCE NUMBERS

10

centrifugal pendulum

12

axis of rotation

14

beam flange

16

pendulum mass

18

further pendulum mass

20

first partial mass

22

second part mass

24

Spring / damper system

26

feather

28

friction device

30

stop damper

32

damping element

34

pivot bearing

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been 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.

Cited patent literature

• DE 102008059297 A1 [0002]

Claims (4)

Centrifugal pendulum for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine, with a carrier flange (14) which can be rotated about an axis of rotation (12) and can be directly or indirectly connected to the drive shaft a pendulum mass (16) which can be oscillated relative to the carrier flange (14), in particular via pendulum tracks, in order to generate a restoring moment directed counter to the rotational irregularity, wherein the pendulum mass (16) has a first partial mass (20) and a first partial mass (20) relatively movable second partial mass (22), wherein the first partial mass (20) and the second partial mass (22) coupled elastically and / or friction damped with each other are. Centrifugal pendulum after Claim 1 characterized in that a pointing in a first circumferential direction first right end side of the first part mass (20) to a pointing in the first circumferential direction second right end side of the second part mass (22) is circumferentially offset and / or opposite in one of the first circumferential direction directed second circumferential direction facing first left end side of the first part of mass (20) is arranged offset to one in the second circumferential direction facing second left end side of the second partial mass (22) in the circumferential direction. Centrifugal pendulum after Claim 1 or 2 characterized in that a on the first part mass (20) and / or on the second part mass (22) abutment stop damper (30), in particular for limiting a maximum swing angle of the pendulum mass (16) is provided, wherein the stop damper (30) the carrier flange (14) or a further downstream in the circumferential direction pendulum mass (18) is connected. Centrifugal pendulum after one of Claims 1 to 3 characterized in that the first partial mass (20) and the second partial mass (22) are held together by a, in particular by friction provided, surmountable in a tangential abutment holding force.

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