DE102015205500A1 - torsional vibration dampers - Google Patents

Abstract

It is a torsional vibration damper (10) for damping torsional vibrations of a drive shaft of an automotive engine provided with a dual mass flywheel (14) for torsional vibration damping, wherein the dual mass flywheel (14) coupled to the drive shaft a primary mass (12) for introducing a torque, relative to the primary mass (12) rotatable secondary mass (18) for discharging the torque and one with the primary mass (12) and the secondary mass (18) coupled energy storage element (16), in particular bow spring, for torque transmission between the primary mass (12) and the secondary mass (18) and a centrifugal pendulum (22) for damping rotational irregularities introduced via the drive shaft of the motor vehicle engine, the centrifugal pendulum (22) having a support flange (20) connected to the secondary mass (18) of the dual mass flywheel (14) and at least one relative to the support flange (20 ), in particular via aerial tramway en, pendulable pendulum mass (24) for generating a rotational irregularity oppositely directed restoring torque, wherein the support flange (20) of the centrifugal pendulum (22) through a passage opening (32) of the primary mass (12) of the dual mass flywheel (14) is passed. By the through the passage opening (32) of the primary mass (12) passed through carrier flange (20) can still be achieved in a failure of the energy storage element (16) on the abutting carrier flange (20) torque transmission between the primary mass (12) and the secondary mass (18) be so that a torsional vibration damper (10) is made possible with a low-cost emergency running property.

Description

The invention relates to a torsional vibration damper, with the help of which torsional vibrations of a drive shaft of a motor vehicle engine can be damped.

For example DE 10 2014 203 788 A1 a dual mass flywheel is known in which a primary mass is coupled via a bow spring with a relative to the primary mass rotatable secondary mass for the torsional vibration damping of a crankshaft of a motor vehicle internal combustion engine. With the secondary mass, a centrifugal pendulum for further torsional vibration damping is attached to a in the installed state by a motor vehicle engine facing away and to a motor vehicle facing side, wherein the centrifugal pendulum is positioned in the axial direction between the secondary mass of the dual mass flywheel and a pressure plate of a friction clutch.

There is a continuing need to provide a low cost runflat property for a torsional vibration damper.

It is the object of the invention to show measures that allow a torsional vibration damper with a low-cost emergency running.

The object is achieved by a torsional vibration damper with the features of claim 1. Preferred embodiments of the invention are set forth in the subclaims and the following description, each of which individually or in combination may constitute an aspect of the invention.

According to the invention, a torsional vibration damper for damping torsional vibrations of a drive shaft of an automotive engine is provided with a dual mass flywheel for torsional vibration damping, wherein the dual mass flywheel coupled to the drive shaft primary mass for introducing a torque, a rotatable relative to the primary mass secondary mass for discharging the torque and one with the primary mass and the secondary mass coupled energy storage element, in particular bow spring, for torque transmission between the primary mass and the secondary mass, and a centrifugal pendulum for damping introduced via the drive shaft of the motor vehicle rotational irregularities, wherein the centrifugal pendulum connected to the secondary mass of the dual mass flywheel and at least one flange relative to the Trägerflansch , In particular via pendulum tracks, pendulum pendulum mass for generating a rotationally uniform having oppositely directed return torque, wherein the support flange of the centrifugal pendulum is passed through a passage opening of the primary mass of the dual mass flywheel.

The passage opening for the support flange may have an extension in the circumferential direction that does not abut the support flange in an intended rotation angle range in which the secondary mass can be relatively rotated relative to the primary mass. If, for example, a component failure of the energy storage element, a maximum intended rotation angle range is exceeded, the support flange can strike in the through hole on the primary mass and thereby block too large a rotation of the secondary mass relative to the primary mass. As a result, unintended excessive loading of the energy storage element and other components of the dual mass flywheel can be avoided, so that a long service life of the torsional vibration damper can be achieved. In particular, it is possible even with a total failure of the energy storage element via the abutting on the primary mass carrier flange to transmit a torque. In this case, the primary mass would abut against the support flange and transmit the torque introduced by the drive shaft to the support flange, while the support flange attached to the secondary mass can transmit the torque past the energy storage element past the secondary mass, from where the torque is transmitted via, for example, a friction clutch can be transmitted to a motor vehicle transmission. As a result, even with a failure of the torsional vibration damping function of the dual mass flywheel in the nature of a runflat property a torque transmission with limited torsional vibration damping function done, which allows a driver of a motor vehicle with such a torsional vibration damper to reach from his own strength a workshop ("limp home function"). For this limp home function anyway built-in components can be used in a cost effective manner, without the need for additional components must be provided for this purpose. By passed through the passage opening of the primary mass carrier flange can still be achieved in a failure of the energy storage element on the abutting support flange torque transmission between the primary mass and the secondary mass, so that a torsional vibration damper is made possible with a low-cost emergency running.

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 farthest from the center of rotation radially 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 provides the restoring force which the pendulum mass wants to return to its "zero position", while the normal force component acts on a force introduction element introducing the speed fluctuations, in particular a flywheel connected to the drive shaft of the motor vehicle engine, for example a primary mass or secondary mass of a dual mass flywheel, and there generates a counter-torque, which counteracts the speed fluctuation and dampens the introduced speed fluctuations. 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 and / or between two mass elements of a pendulum mass. 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, the passage opening of the primary mass is configured as an arcuate slot. Thereby, the volume of the through hole can be minimized and easily limited to the area swept by the support flange during the regular operation of the dual mass flywheel. A reduction of the moment of inertia of the primary mass through the passage opening can be kept low, so that a detuning of the dual mass flywheel is rather not to be feared.

Preferably, the through-opening of the primary mass has a first emergency stop pointing in a first circumferential direction for striking the carrier flange and a second emergency stop for striking the carrier flange facing in a second circumferential direction opposite to the first circumferential direction, the carrier flange between the first emergency stop and the second Emergency stop is rotatable by an Notdrehwinkelbetrag φ _N , wherein for the Notdrehwinkelbetrag φ _N relative to a planned maximum rotational angle amount φ _{max of} the secondary mass relative to the primary mass 1.00 ≤ φ _N / φ _max ≤ 1.20, in particular 1.01 ≤ φ _N / φ _max ≤ 1.15, preferably 1.02 ≤ φ _N / φ _max ≤ 1.10, and more preferably 1.03 ≤ φ _N / φ _max ≤ 1.05. It can thus be ensured that, taking into account the extent of the part of the support flange passing through the passage opening in the circumferential direction, striking of the support flange during normal operation of the dual mass flywheel can be avoided. If the intended maximum angle of rotation amount φ _{max is} exceeded, it can be assumed that the dual-mass flywheel is no longer functioning properly. In this situation, after a comparatively small angle amount, a striking of the carrier flange can take place, so that unnecessary component loads, in particular of the energy storage element, can be avoided. As a result, repair costs can be saved if necessary.

Particularly preferably, the support flange has at least two fastening webs fastened to the secondary mass, wherein the fastening webs are guided through respectively different through openings of the primary mass. This makes it possible that the support flange can be configured radially outwardly to the through hole as a closed ring on which the pendulum masses are guided. In particular, the support flange is designed in several parts, preferably each attachment web is part of a separate flange. The individual flange parts can be connected to one another radially outwardly of the through openings of the primary mass to form a ring closed in the circumferential direction, after the fastening web of the respective flange part has been threaded in the associated through-opening and optionally secured to the secondary mass. Additionally or alternatively, it is possible that the passage opening for the respective associated attachment web has a radially inwardly projecting recess through which the attachment web can be passed during assembly in the axial direction, in particular when the support flange relative to the primary mass coaxially centered in the radial direction is. In this case, the support flange can be designed in one piece.

In particular, the primary mass of the dual mass flywheel is in the axial direction between arranged the pendulum mass of the centrifugal pendulum and the energy storage element of the dual mass flywheel, in particular, the primary mass considered in the axial direction completely covers the pendulum mass. The pendulum mass can thereby be positioned on the motor side to the dual mass flywheel. The centrifugal pendulum can thereby be positioned at least with the pendulum mass in a space that allows the arrangement of the pendulum mass on a relatively large radius, which at a low weight of the pendulum mass and a correspondingly low space requirement, a high torsional vibration damping capacity is possible. At the same time it is avoided that the centrifugal pendulum is positioned in a transmission-side space in which the secondary mass can form a pressure plate of a friction clutch. For example, it is not necessary to connect the secondary mass via a drive ring on a transmission side positioned centrifugal pendulum past with a pressure plate of a friction clutch. Instead, the secondary mass itself can form the pressure plate of the friction clutch, so that the axial space requirement of the torsional vibration damper can be kept low.

Preferably, the primary mass of the dual mass flywheel in the radial direction covers the pendulum mass of the centrifugal pendulum at least to a large extent, in particular completely. The primary mass can form, for example, a recess or a receiving pocket for receiving the pendulum mass of the centrifugal pendulum. This avoids that the centrifugal pendulum with a part in the axial direction to a contact plane, in which the primary mass on the drive shaft of the motor vehicle engine or another component contacting axially protrudes, protrudes. As a result, tight space requirements can be met.

Particularly preferably, the primary mass has a substantially axially extending radially outward to the centrifugal pendulum arranged burst protection for the centrifugal pendulum, the burst protection viewed in the radial direction, the pendulum mass of the centrifugal pendulum at least to a large extent, in particular completely covers. The primary mass can form a receiving pocket for receiving the pendulum mass, so that automatically results in the radially outside of the pendulum mass arranged rupture protection. The bursting protection superior to the pendulum mass can prevent throwing the pendulum mass radially outward in a component failure of the centrifugal pendulum and thereby prevent unnecessary damage.

In particular, with the bursting protection, a starter ring for initiating a starting torque generated by a starter generator for starting the motor vehicle engine mounted, wherein in particular the starter ring viewed in the radial direction, the pendulum mass at least partially, preferably completely covered. The starter ring can form an additional accumulation of material, which allows a particularly robust burst protection. In addition, the starter ring can stiffen the substantially axially extending burst protection, whereby the protective effect of the burst protection can be improved.

It is preferably provided that the secondary mass is connected to a pressure plate of a friction clutch or the secondary mass forms a pressure plate of a friction clutch. By the motor-side positioning of the pendulum mass of the centrifugal pendulum, the axial extent of the torsional vibration damper can be kept low in order to effect a torque transmission to the pressure plate of the friction clutch.

The invention further relates to a drive train for a motor vehicle having a drive shaft having motor vehicle engine and a torsional vibration damper, which may be as described above and further educated, the primary mass of the dual mass flywheel is directly or indirectly coupled to the drive shaft and the pendulum mass of the centrifugal pendulum in axial Direction between the motor vehicle engine and the primary mass is arranged. By passed through the passage opening of the primary mass carrier flange can still be achieved in a failure of the energy storage element on the abutting support flange torque transmission between the primary mass and the secondary mass, so that a torsional vibration damper is made possible with a low-cost emergency running.

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 : A schematic sectional view of a torsional vibration damper and

2 : A schematic plan view of the torsional vibration damper 1 ,

The in 1 and 2 illustrated torsional vibration damper 10 has a primary mass connectable to a motor shaft of an automobile engine 12 a dual mass flywheel 14 on, which has a designed as a bow spring energy storage element 16 with a relative to the primary mass 12 limited rotatable secondary mass 18 is coupled. With the secondary mass 18 of the dual mass flywheel 12 is a carrier flange 20 a centrifugal pendulum 22 riveted. With the carrier flange 20 are pendulum masses 24 relatively over in aerial tramways 26 guided rollers 28 coupled pendelbar. In the illustrated embodiment, the support flange 20 in the axial direction between two pendulum masses connected to each other 24 positioned. Alternatively, it is possible the pendulum mass 24 in the axial direction between two, for example, Y-shaped interconnected flange of the support flange 20 to position. Several pendulum masses 24 are evenly distributed in the circumferential direction with the support flange 20 connected.

In the illustrated embodiment, the pendulum masses 24 motor side to the dual mass flywheel 14 arranged, that is the primary mass 12 of the dual mass flywheel 14 is in the axial direction between the pendulum mass 24 and the energy storage element 16 as well as the secondary mass 18 arranged. For this purpose, the support flange 20 for example, two radially inwardly projecting mounting webs 30 in each case by an associated essentially as an arcuate slot associated passage opening 32 passed through to the motor side axial side of the primary mass 12 to the transmission-side axial side of the primary mass 12 to arrive and with the secondary mass 18 to be connected. To the carrier flange 20 by an axial relative movement to the primary mass 12 and the secondary mass 18 with the secondary mass 18 to be able to attach during assembly, has the passage opening 32 for the respective fastening web 30 a radially inwardly projecting recess 34 on, through which the mounting bridge 30 during assembly by the primary mass 12 can be moved through.

The primary mass 12 has radially outward on a cranked course, so that a receiving pocket 36 results, in which the pendulum masses 24 of the centrifugal pendulum 22 can be absorbed sunk in the axial direction. Additionally forms the primary mass 12 a one-piece in the axial direction radially outward to the pendulum masses 24 extending burst protection 38 for the centrifugal pendulum 22 out. At the motor-side axial end of the burst protection 38 is a starter wreath 40 fastened by the burst protection 38 additionally reinforced and stiffened.

As in 2 shown has the passage opening 32 at its peripheral ends a first emergency stop 42 and a second emergency stop 44 on. If by a component failure, in particular the energy storage element 16 , an intended maximum angle of rotation of the secondary mass 18 to the primary mass 12 is exceeded, the fastening bridge 30 the carrier flange 20 on the side of the first emergency stop 42 or at the second emergency stop 44 strike and a torque transmission between the primary mass 12 and the secondary mass 18 cause.

LIST OF REFERENCE NUMBERS

10

 torsional vibration dampers

12

 primary mass

14

 Dual Mass Flywheel

16

 Energy storage element

18

 secondary mass

20

 beam flange

22

 centrifugal pendulum

24

 pendulum mass

26

 aerial tramway

28

 caster

30

 fastening web

32

 Through opening

34

 recess

36

 receiving pocket

38

 Burst protection

40

 starter wreath

42

 first emergency stop

44

 second emergency stop

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 102014203788 A1 [0002]

Claims (10)

Torsional vibration damper for damping torsional vibrations of a drive shaft of a motor vehicle engine, with a dual-mass flywheel (US Pat. 14 ) for torsional vibration damping, wherein the dual mass flywheel ( 14 ) a coupling with the drive shaft primary mass ( 12 ) for introducing a torque, one relative to the primary mass ( 12 ) rotatable secondary mass ( 18 ) for discharging the torque and one with the primary mass ( 12 ) and the secondary mass ( 18 ) couplable energy storage element ( 16 ), in particular bow spring, for torque transmission between the primary mass ( 12 ) and the secondary mass ( 18 ), and a centrifugal pendulum ( 22 ) for damping rotational irregularities introduced via the drive shaft of the motor vehicle engine, the centrifugal pendulum ( 22 ) one with the secondary mass ( 18 ) of the dual mass flywheel ( 14 ) connected carrier flange ( 20 ) and at least one relative to the support flange ( 20 ), in particular over pendulum tracks, pendulum pendulum mass ( 24 ) for generating a rotational irregularity opposing return torque, wherein the support flange ( 20 ) of the centrifugal pendulum ( 22 ) through a passage opening ( 32 ) of the primary mass ( 12 ) of the dual mass flywheel ( 14 ) is passed. Torsional vibration damper according to claim 1, characterized in that the passage opening ( 32 ) of the primary mass ( 12 ) is designed as an arcuate slot. Torsional vibration damper according to claim 1 or 2, characterized in that the passage opening ( 32 ) of the primary mass ( 12 ) a pointing in a first circumferential direction first emergency stop ( 42 ) for striking on the support flange ( 20 ) and a second emergency stop pointing in a second circumferential direction in the first circumferential direction ( 44 ) for striking on the support flange ( 20 ), wherein the support flange ( 20 ) between the first emergency stop ( 42 ) and the second emergency stop ( 44 ) is rotatable about an Notdrehwinkelbetrag φ _N , wherein for the Notdrehwinkelbetrag φ _N relative to a designated maximum rotational angle amount φ _{max of} the secondary mass ( 18 ) relative to the primary mass ( 12 ) 1.00 ≤ φ _N / φ _max ≤ 1.20, in particular 1.01 ≤ φ _N / φ _max ≤ 1.15, preferably 1.02 ≤ φ _N / φ _max ≤ 1.10, and particularly preferably 1.03 ≤ φ _N / φ _max ≤ 1.05 applies. Torsional vibration damper according to one of claims 1 to 3, characterized in that the support flange ( 20 ) at least two with the secondary mass ( 18 ) fastened fastening webs ( 30 ), wherein the fastening webs ( 30 ) by respective different passage openings ( 32 ) of the primary mass ( 12 ) are passed through. Torsional vibration damper according to one of claims 1 to 4, characterized in that the primary mass ( 12 ) of the dual mass flywheel ( 14 ) in the axial direction between the pendulum mass ( 24 ) of the centrifugal pendulum ( 22 ) and the energy storage element ( 16 ) of the dual mass flywheel ( 14 ), in particular the primary mass ( 12 ) viewed in the axial direction of the pendulum mass ( 24 completely covered. Torsional vibration damper according to one of claims 1 to 5, characterized in that the primary mass ( 12 ) of the dual mass flywheel ( 14 ) viewed in the radial direction, the pendulum mass ( 24 ) of the centrifugal pendulum ( 22 ) at least to a large extent, in particular completely, covered. Torsional vibration damper according to one of claims 1 to 6, characterized in that the primary mass ( 12 ) extending substantially in the axial direction radially outward to the centrifugal pendulum ( 22 ) arranged burst protection ( 38 ) for the centrifugal pendulum ( 22 ), wherein the burst protection ( 38 ) viewed in the radial direction, the pendulum mass ( 24 ) of the centrifugal pendulum ( 22 ) at least to a large extent, in particular completely, covered. Torsional vibration damper according to claim 7, characterized in that with the burst protection ( 38 ) a starter ring ( 40 ) is mounted for initiating a starting torque generated by a starter generator for starting the motor vehicle engine, wherein in particular the starter ring ( 40 ) viewed in the radial direction, the pendulum mass ( 24 ) at least partially, preferably completely, covered. Torsional vibration damper according to one of claims 1 to 8, characterized in that the secondary mass ( 18 ) is connected to a pressure plate of a friction clutch or the secondary mass ( 18 ) forms a pressure plate of a friction clutch. Drive train for a motor vehicle with a drive motor shaft having motor vehicle engine and a torsional vibration damper ( 10 ) according to any one of claims 1 to 9, wherein the primary mass ( 12 ) of the dual mass flywheel ( 14 ) is indirectly or directly coupled to the drive shaft and the pendulum mass ( 24 ) of the centrifugal pendulum ( 22 ) in the axial direction between the motor vehicle engine and the primary mass ( 12 ) is arranged.

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