Source: https://patents.google.com/patent/DE102010054297A1/en
Timestamp: 2020-07-14 04:26:07
Document Index: 652119848

Matched Legal Cases: ['art 4', 'art 6', 'art 6', 'art 4', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 9', 'art 45', 'arts 9', 'art 6', 'art 4', 'art 49', 'art 48', 'art 48', 'art 45', 'art 4', 'art 6', 'art 4', 'art 6', 'art 49']

DE102010054297A1 - Compensation device for torsional vibrations, particularly in drive train of motor vehicle, has centrifugal pendulum with pendulum masses, which roll off tracks provided in segments of flange part and pendulum masses by cylinder rollers - Google Patents
Compensation device for torsional vibrations, particularly in drive train of motor vehicle, has centrifugal pendulum with pendulum masses, which roll off tracks provided in segments of flange part and pendulum masses by cylinder rollers
DE102010054297A1
DE102010054297A1 DE201010054297 DE102010054297A DE102010054297A1 DE 102010054297 A1 DE102010054297 A1 DE 102010054297A1 DE 201010054297 DE201010054297 DE 201010054297 DE 102010054297 A DE102010054297 A DE 102010054297A DE 102010054297 A1 DE102010054297 A1 DE 102010054297A1
DE201010054297
Uwe 77815 Grahl
Eugen 77815 Kombowski
Jonathan Laigo
Parviz Dr.-Ing. 76437 Movlazada
Reinhold 76185 Reder
Stefanie 77830 Straub
2009-12-22 Priority to DE102009059920 priority Critical
2009-12-22 Priority to DE102009059920.7 priority
2010-12-13 Priority to DE201010054297 priority patent/DE102010054297A1/en
2011-06-30 Publication of DE102010054297A1 publication Critical patent/DE102010054297A1/en
F16F15/13157—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses with a kinematic mechanism or gear system, e.g. planetary
The invention relates to a compensation device for torsional vibrations in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum with distributed over the circumference, recorded on a flange, on both sides relative to the flange limited radially and circumferentially pivotally received on the flange part pendulum masses, the by means of cylindrical rollers rolling in recesses of the flange and the pendulum masses provided raceways. To further develop such devices means for noise reduction, stop limit, captive locking of the cylindrical rollers and sealing of at least partially filled with lubricant annular spaces are proposed.
The invention relates to a compensation device for torsional vibrations in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum with distributed over the circumference, recorded on a flange, bounded on both sides relative to the flange radially and circumferentially pivotally received on the flange pendulum masses, the roll off the rollers by means of cylindrical rollers in cut-outs of the flange part and the pendulum masses.
Generic compensation devices are for example from the DE 10 2009 021 355 A1 known. Here, a plurality of distributed over the circumference, limited relative to the flange radially and circumferentially displaceable pendulum masses are arranged on a flange. The displacement of the pendulum masses relative to the flange takes place by means of cylindrical rollers which roll on tracks of cutouts in the flange and in the pendulum masses. In this case, distributed on both sides of the flange over the circumference pendulum masses are provided, of which in each case the axially opposite pendulum masses are connected to each other by means of the flange to corresponding cutouts thorough rivets to a pendulum mass pair.
The cylindrical rollers are neither fixedly arranged on the flange or on the pendulum masses and can fall out under appropriate conditions from the cutouts or be displaced in relation to these harmful for the function of the centrifugal pendulum pendulum.
When abutting the pendulum masses to the flange and / or by means of their circumferentially adjacent end faces or rivets in the corresponding cutouts of the flange malfunction and noise may occur. Furthermore, by accommodating the pendulum masses with a corresponding safety distance of the pendulum masses in the circumferential direction to a reduction of the pendulum masses and / or limiting the swing angle lead to a loss of the effectiveness of the centrifugal pendulum.
Furthermore, it has been found that in combination with other compensation elements such as a torsional vibration damper such as dual mass flywheel corresponding friction devices are provided and possibly leaking spaces with lubricants, such as an annulus for lubricated recording of bow springs of a dual mass flywheel, can affect the effect of the centrifugal pendulum by leaking lubricant.
The object of the invention is therefore to improve a compression device with a centrifugal pendulum in an advantageous manner, in particular against the background of improved reliability, improved performance and / or reduced noise.
At least a partial aspect of the object is defined by a compensation device for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum with circumferentially distributed, received on a flange, bounded on both sides relative to the flange radially and circumferentially pivotable on the flange recorded pendulum masses, roll off by means of cylindrical rollers in sections such as recesses of the flange and the pendulum masses provided loosened, with two axially opposite pendulum masses are interconnected and the cylindrical rollers are captively received in the flange by be provided on the pendulum masses embossments such as axial stops for the cylindrical rollers , which at least partially radially overlap the track of the pendulum mass.
The embossments in the form of the axial stops can be introduced in a preferred manner in the pendulum mass by the provided with the tracks for the pendulum masses cutouts are limited by this over an entire surface area of the cutouts to a diameter smaller than a diameter of the end faces of the cylindrical rollers. In this way, cover plates can be avoided, which are riveted to the pendulum masses and cover the cutouts with the raceways. These cause possibly in addition to an increased manufacturing and parts costs vibration-related noise. The one-piece design of a captive protection by stamping on the pendulum masses avoids these disadvantages in an advantageous manner.
At least one aspect is also recorded by a compensation device for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a gearbox with a centrifugal pendulum with circumferentially distributed, recorded on a flange, on both sides limited relative to the flange radially and circumferentially pivotally received on the flange Pendulum masses, roll off by means of cylindrical rollers provided in recesses of the flange and the pendulum masses raceways, solved, being formed in the circumferential direction end faces of the Pendulum masses form radially outside a circular contour and radially within the circular contour with a smaller circumference than the circular contour a stop surface for a flange part arranged in the circumferential direction adjacent pendulum masses a stop forming stop element is formed.
By forming a circumferentially beyond the abutment surface on the stopper out addition area in the form of circular contour pendulum masses can overlap in the circumferential direction, so that they are provided with a larger mass and thus the insulation behavior of the centrifugal pendulum can be increased. Depending on the pivoting, the circular contours of two circumferentially adjacent pendulum masses radially overlap and strike against the preferably soft stop element. By a circular design of the stop surface and the stop element with similar radii and large stop surface thereby striking the pendulum masses is elastically and softly damped on the stop elements, so that impact noises are largely reduced. The stop elements can be provided with an elastically deformable surface.
The stop element is preferably arranged on a pitch axis, each defining an angular segment for a pendulum mass or pendulum mass pair of axially spaced, both sides of the flange arranged and interconnected pendulum masses with a circumferentially adjacent pitch between two pendulum masses, the pendulum masses in the context of the invention by means of the circular contour overlap the stop elements in the circumferential direction and radially.
The contours and the predetermined by the shape of the raceways of the provided in the flange and in the pendulum masses swing angles such as maximum pivot angle of the pendulum masses are designed so that the circular contour at maximum pivot angle does not exit from the outer diameter of the flange, the circular contour and an outer periphery of the flange So at maximum pivot angle of the pendulum masses are preferably arranged on the same diameter. Due to the overlap of the pendulum mass at maximum pivot angle in the circumferential direction, a larger maximum pivot angle can be provided in addition to a higher mass.
The radii of the circular contour, the stop elements and stop surfaces, the swing angle and swing radii and the division of the pendulum masses, ie the number of pendulum masses arranged around the circumference, are designed to optimize the tuning of the centrifugal pendulum and the torsional vibrations to be compensated. For example, the sum of a radius of a circular stop element and a radius of the circular contour substantially correspond to a vibrating radius of the pendulum masses or be slightly smaller while maintaining appropriate tolerances.
At least one further aspect of the object is defined by a compensating device for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum with circumferentially distributed, received on a flange, both sides relative to the flange limited radially and circumferentially pivotable on the Flange part recorded pendulum masses, roll off the rollers provided by means of cylindrical rollers in recesses of the flange and the pendulum masses, solved, wherein from radially inside and / or radially outside at least one plastic clip is engaged in the pendulum masses and / or in the flange. Such plastic clips can be used to reduce noise, for example, in a striking the pendulum masses on the flange. The plastic brackets are formed from a corresponding vibration damping material. It can advantageously be arranged to limit the number of parts on a pendulum mass one or two plastic clips. On the flange part in the peripheral region of a pendulum mass also one or two clipped plastic clips may be advantageous. Particularly advantageous is the arrangement of the plastic clamps in such a way that a mutual contact of the plastic clamps is achieved during expected contact of the pendulum mass and the flange. It has proved to be particularly advantageous if such plastic clips are provided only in the flange part.
Furthermore, it has proven to be advantageous if the at least one plastic clip is arranged flush with an outer circumference or inner circumference of the pendulum masses or of the flange part. For this purpose, corresponding incisions may be provided in the outer circumference of the flange part and radially spaced apart therefrom or the inner and / or outer circumference of the pendulum masses, in which on the one hand the undercuts for fixing hook hook and on the other hand the staple back in the space of the flange or the pendulum masses can be integrated. The plastic brackets can be attached from radially inward to radially outward and vice versa. For example, the staple spine may be housed radially outward in an incision and the hooks are suspended in a radially inwardly introduced to this incision.
At least a partial aspect of the object is limited by a compensation device for torsional vibrations in particular in a drive train of a motor vehicle with an internal combustion engine and a gear containing a torsional vibration damper with an input part and against the action of energy absorbed in an annular space formed by the input part against the input part rotatable output part with an engaging in the annular space flange and a parallel to the torsional vibration damper centrifugal pendulum with an axially spaced flange portion to the flange with limited on both sides relative to the flange radially and circumferentially pivotally received pendulum masses dissolved, wherein between the flange of the centrifugal pendulum and the input part of the torsional vibration damper is a plate spring clamped.
Such a diaphragm spring can on the one hand provide a friction device with a basic friction in a rotation of input part and output part of the torsional vibration damper and / or on the other as a membrane seal the annulus of the input part for receiving the energy storage as bow springs to the outside. The plate spring can be clamped axially against an axial stop formed on the outer circumference of the flange part.
The invention is based on the in 1 to 12 illustrated embodiments explained in more detail. Showing:
1 a partial section through a compensation device,
2 a partial view of the compensation device of 1 .
3 a detail of a on the flange portion of the compensation device of 1 absorbed pendulum mass,
4 a partial view of a compensation device with end face equipped with a circular contour pendulum masses,
5 a detailed view of the compensation device of 4 with maximum pendulum masses twisted against each other,
6 to 9 Various embodiments of a stop element of the compensation device of 4 .
10 a detailed view of a compensation device with plastic clips,
11 one opposite the 11 changed detailed view of the compensation device of 10
12 a partial section through a compensation device with a torsional vibration damper and a centrifugal pendulum.
The 1 shows the around the rotation axis 2 arranged compensating device for the compensation of rotational shocks and torsional vibrations, which are registered in a drive train, for example, from an internal combustion engine, in partial section. The compensation device 1 contains the torsional vibration damper 3 with the entrance part 4 and the contrary to the effect of designed as a bow springs energy storage 5 limited rotatable output part 6 , The starting part 6 Contains that with the flywheel 7 and the internally toothed hub 8th connected as riveted flange 9 that is from radially inside to that of the front part 4 formed annulus 51 engages and stored in this energy storage 5 applied.
The flange part 9 forms with the both sides of this in the radial direction and in the circumferential direction limited pivotable and distributed over the circumference arranged pendulum masses 11 a speed-adaptive torsional vibration damper in the form of centrifugal pendulum 10 , The pendulum masses 11 are radially inside the energy storage 5 arranged. The axially opposite pendulum masses 11 are in pairs with each other by means of the step rivet 12 connected, which at the same time the way of the pendulum masses 11 opposite the flange part 9 limit. These are the step rivets 12 with an elastic sheath 13 provided after exhaustion of the maximum pivot angle of the pendulum masses 11 at the in the flange 9 corresponding excluded recesses 14 strikes.
2 shows the centrifugal pendulum 10 the compensation device 1 of the 1 in partial view with the flange part 9 , the radially extended arms 15 for charging the energy storage 5 ( 1 ) having. The axially opposite pendulum masses 11 are by means of the cutouts 14 of the flange part 9 sweeping step rivets 12 connected with each other. The pendulum masses 11 are opposite the flange part 9 for specifying a swing angle on raceways 16 . 17 guided by appropriate cutouts 18 . 19 in the pendulum masses 11 and in the flange part 9 are formed. In the embodiment shown, two circumferentially spaced cutouts are provided for this purpose 18 in the pendulum masses 11 and this complementary cutouts 19 provided in the flange part.
On the careers 16 . 17 each rolls a cylindrical roller 20 off, so due to the design of the raceways 16 . 17 the pendulum masses 11 describe a given orbit about a pendulum point, which is provided radially within the pendulum masses.
The cylindrical rollers 20 are neither in the flange part 9 still in the pendulum masses 11 attached and can under unfavorable conditions, especially during transport of the compensation device 1 before being installed in the drive train from the centrifugal pendulum 10 fall out. To form a captive protection for the cylindrical rollers 20 without the use of additional parts, which also by their attachment to other moving parts such as the pendulum masses 11 can be noisy, the cross section of the cutouts 18 so narrows that a circumferential diameter of the cutouts 18 at least partially smaller than the diameter of the end faces of the cylindrical rollers 20 is. These are the pendulum masses 11 in the field of cutouts 18 radially inward, the raceway 17 radially overlapping embossings 21 intended. The markings 21 may fall off the pendulum masses produced by means of a stamping / embossing process 11 be provided.
The 3 shows a detail of 2 on average in the neckline 19 intended career 16 of the flange part 9 rolling cylindrical roller 20 , The cylindrical roller 20 has radially expanded ring rims 22 for guiding the cylindrical roller 20 on the track 16 on. The career 17 the pendulum mass 11 is through the neckline 18 formed from the pendulum mass 11 is punched out. Then the embossing 21 formed, for example, from the originally existing, dashed against the cutout 18 delimited mass accumulation 23 Material radially inward to form the impression 21 is displaced. The material displacement takes place from a radially outer part of the cutout 18 on which the cylindrical roller 20 usually does not roll because the pendulum mass 11 is displaced radially outward under centrifugal force and only at the radially inside of the cutout 18 intended career 17 rolls. The surface of the clipping 18 radially outward remains so far that the optionally over the axis of rotation 2 ( 1 ) placed and at standstill of the centrifugal pendulum 10 ( 1 ) radially inwardly falling pendulum mass 11 radially outside of the cylindrical roller 20 can support.
4 shows a schematically illustrated partial view of one opposite the compensation device 1 of the 1 to 3 changed to the axis of rotation 2 arranged compensation device 1a , of which only the centrifugal pendulum 10a is shown. Opposite the pendulum masses 11 of the 1 to 3 are the pendulum masses 11a with changed front sides 24 formed in the circumferential direction. The pivotable mounting of the pendulum masses 11a by means of corresponding in sections of the pendulum masses 11a and the flange part 9a intended tracks corresponds essentially to the designs of 1 to 3 , The representation of this is omitted here for the sake of clarity.
The front ends 24 have radially outwardly the circular segment-shaped circumferentially expanded circle contour 25 with the radius r S , to the radially inward of the stop surface 26 followed by the radius r 2 . At the stop surface 26 beats at maximum swing angle β max that on the flange 9a on the division axis 28 between two pendulum masses arranged at twice the distance of the pitch angle γ 11a arranged stop element 27 with the radius r 1 on. The radius r 2 is the stop surface 26 greater than or equal to the radius r 1 of the stop element 27 plus a tolerance quantity c arranged around the circular contour. The stop surfaces 26 of each adjacent end faces in the circumferential direction 24 the pendulum masses 11a and the stopper member disposed therebetween 27 form a soft stop with each other, so that provided for connecting two axially spaced pendulum mass stage rivets relative to the corresponding in the flange 9a recessed cutouts form no stop and thus have a corresponding clearance angle to the maximum swing angle β max by extending the cutouts in the circumferential direction. The outer circumference including the tolerance size c of the circular contour 25 is arranged tangentially to the division axis.
The front ends 24 the pendulum masses 11a swing opposite the center M of the circle contour 25 around the swing angle β s . The pendulum masses swing 11a around the opposite of the axis of rotation 2 Pendulum point P displaced radially outward about the pendulum length l. For the radius r S of the circular contour 25 this results in an advantageous relationship with r S = lsinγ. The sum r 1 + r 2 of the stop surface 26 and the stop element 27 preferably corresponds to the pendulum length l.
Like from the 5 which shows a partial view of the centrifugal pendulum 10a of the 4 shows overlap upon reaching a stop of the stop element 27 at the stop surface 26 at maximum swing angle the pendulum masses 11a radially and circumferentially by means of their circular contours 25 , By matching the circle contours 25 , the radii of the stop surface 26 and of stop element 27 , the swing angle, the pendulum length and the pendulum mass, the centrifugal pendulum 10a optionally adjusted to a vibration damping in conjunction with a torsional vibration damper.
The 7 to 9 show advantageous embodiments of stop elements 27a . 27b . 27c . 27d for use as a stop element 27 of the 4 and 5 in 3-D view. In detail, the shows 6 the stop element 27a in stick form with the axial extension 29 which enters a corresponding opening of the flange part 9a ( 4 ) is introduced and optionally riveted. To the approach 29 is the stop ring 30 , which may be formed for example of elastic material such as plastic or rubber, laid.
7 shows the cup-shaped stop element 27b with one in the bottom of the pot 35 provided opening 31 at the stop element 27b for example, on one of the flange 9a ( 4 ) exhibited Nietwarze can be recorded and riveted. The stop element 27b can be thermoformed from sheet metal and at correspondingly set wall thickness of the wall 32 an elastic contact with the stop surface 26 ( 5 ) form.
8th shows that against the stop element 27b of the 7 slightly modified stop element 27c with opposite the opening 31 additionally in the bottom of the pot 35 radially outside of these recessed openings 33 that the wall 32a except for the bars 34 from the bottom of the pot 35 crop, leaving the wall 32a is designed radially elastic.
9 shows in a further development of the stop element 27c of the 8th the stop element 27d with innterruptions 36 the wall 32b under formation unilaterally with the bottom of the pot 35 connected, circumferentially extended tabs 37 to further increase the radial elasticity of the stop element 27d ,
10 shows a partial view of one opposite the compensation device 1 of the 1 to 3 amended arranged compensation device 1b , of which only the centrifugal pendulum 10b is shown. At the flange part 9b are the arms 15 formed to act on energy storage of a torsional vibration damper, not shown. Radial within these are the pendulum masses 11b for the formation of the centrifugal pendulum 10b pivotally arranged, wherein in the view in front of the flange 9b arranged pendulum masses are omitted.
In particular, for damping of impact noises are in the embodiment shown from radially outside plastic brackets 38 with the flange part 9b locked. The plastic clamp 38a is not yet in the flange part 9b locked and gives the view of one of the outer circumference of the flange 9b incisions distributed over the circumference 39 and the radially arranged inside this recesses 40 free, on each of which a plastic clip 38 . 38a is included. This is the clip back 41 with the outer periphery of the flange part 9b flush in the incision 39 inserted and each on the cheeks 42 the plastic clamp 38 . 38a inward pointing hook 42 with the recess 40 locked. The cheeks 42 form for the pendulum masses arranged on both sides of the flange 11b a contact surface, so that noisy metal / metal contacts between the pendulum masses 11b and the flange part 9b excluded are. For this purpose, the circumference per pendulum mass 11b two plastic clips 38 each in the circumferential direction between the cutouts 14 . 18 for the cylindrical rollers 20 or level rents 12 arranged.
The 11 shows the centrifugal pendulum 10b of the 10 in a modified partial view with indicated pendulum masses 11b from which the positioning of the cutouts 40 radially within the inner circumference of the pendulum masses 11b shows, so that caused by this weakening of the flange 9b in the radial band with the cutouts 14 . 18 on the one hand and the radial band with the openings 44 is avoided, for example, for riveting the flange with other components. It is understood that the the plastic clips 38 can also be suspended from radially inward to radially outward by these after appropriate adjustment of the incisions 39 and cutouts 40 threaded through a cutout and locked by means arranged on the cheeks hook with the incision. With such plastic brackets, a particularly good resistance to detachment under centrifugal force can be achieved.
12 shows the around the rotation axis 2 arranged compensation device 1c with the trained as a dual mass flywheel torsional vibration damper 3c and the parallel to this effective centrifugal pendulum 10c , In contrast to the compensation device 1 of the 1 is the flange part 45 for acting as trained in nested bow springs energy storage 5c as a separate component to the flange 9c of the centrifugal pendulum 10c , the pendulum masses on both sides 11c pivotally receives, trained. The flange parts 9c . 45 are by means of the rivet 46 with the secondary flywheel 7c of the starting part 6c the compensation device 1c riveted.
The entrance part 4c the compensation device 1c is from the primary flywheel 47 formed with the side panel 48 and with this firmly connected ring member 49 the primary flywheel 50 of the torsional vibration damper 3c forms. It is understood that side panel 48 and ring part 49 can also be formed in one piece.
The primary flywheel 47 and the side part 48 form the optionally partially filled with lubricant annulus 51 in which the energy store 5c are housed and input side of the indents 52 . 53 the primary flywheel 47 or the side part 48 and on the output side of the radially expanded arms 15c of the flange part 45 be charged.
For sealing the annulus 51 to the outside or to provide a friction device 54 , For example, without play a basic friction between the input part 4c and the output part 6c when twisting this forms against each other, is the diaphragm spring 55 between the entrance part 4c and the output part 6c axially braced. These are on the flange 9c for the formation of the centrifugal pendulum 10c radially outside of the radially outwardly directed ring board 56 with the secondary flywheel 7c facing contact surface 57 and on the ring part 49 the energy stores 5c facing contact surface 58 provided, opposite which the diaphragm spring 55 axially braced.
Swing angle end face
Radius circle contour
Radius stop surface
Radius stop element
DE 102009021355 A1 [0002]
Compensation device ( 1 ) for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum ( 10 ) distributed over the circumference, on a flange ( 9 ), on both sides opposite the flange ( 9 ) limited radially and circumferentially pivotable on the flange ( 9 ) received pendulum masses ( 11 ), which by means of cylindrical rollers ( 20 ) in excerpts ( 18 . 19 ) of the flange part ( 9 ) and the pendulum masses ( 11 ) ( 16 . 17 ), wherein two axially opposite pendulum masses ( 11 ) and the cylindrical rollers ( 20 ) captive in the flange part ( 9 ), characterized in that on the pendulum masses ( 11 ) Stampings ( 21 ), which mark the tracks ( 17 ) of the pendulum masses ( 11 ) at least partially radially overlap.
Compensation device ( 1 ) according to claim 1, characterized in that in the pendulum mass ( 11 ) introduced sections ( 19 ) by embossing ( 21 ) over an entire area of the cutouts ( 19 ) to a diameter smaller than a diameter of the end faces of the cylindrical rollers ( 20 ) are limited.
Compensation device ( 1a ) for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum ( 10a ) distributed over the circumference, on a flange ( 9a ), on both sides opposite the flange ( 9a ) limited radially and circumferentially pivotable on the flange ( 9a ) received pendulum masses ( 11a ), which by means of cylindrical rollers in sections of the flange ( 9a ) and the pendulum masses ( 11a ) provided raceways, characterized in that formed in the circumferential direction end faces ( 24 ) of the pendulum masses ( 11a ) radially outside a circular contour ( 25 ) and radially within the circular contour ( 25 ) at a smaller circumference than the circle contour ( 25 ) a stop surface ( 26 ) for a in the flange ( 9a ) arranged for two circumferentially adjacent pendulum masses ( 11a ) a stop-forming stop element ( 27 . 27a . 27b . 27c . 27d ) is formed.
Compensation device ( 1a ) according to claim 3, characterized in that the stop element ( 27 . 27a . 27b . 27c . 27d ) on a division axis ( 28 ) between two pendulum masses ( 11a ) is arranged.
Compensation device ( 1a ) according to claim 3 or 4, characterized in that at a maximum oscillation angle (β max ) of the pendulum masses ( 11a ) relative to the flange part ( 9a ) the circular contour ( 25 ) and an outer periphery of the flange part ( 9a ) are arranged on the same diameter.
Compensation device ( 1a ) according to one of claims 3 to 5, characterized in that the sum of a radius (r 2 ) of a circular stop element ( 27 . 27a . 27b . 27c . 27d ) and a radius (r 1 ) of the stop surface ( 26 ) substantially a pendulum length (l) of the pendulum masses ( 11a ) corresponds.
Compensation device ( 1b ) for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum ( 10b ) distributed over the circumference, on a flange ( 9b ), on both sides opposite the flange ( 9b ) limited radially and circumferentially pivotable on the flange ( 9b ) received pendulum masses ( 11b ), which by means of cylindrical rollers ( 20 ) in excerpts ( 18 . 19 ) of the flange part ( 9b ) and the pendulum masses ( 11b Rolling provided trajectories, characterized in that from radially inside and / or radially outside at least one plastic clip ( 38 . 38a ) in the pendulum masses and / or in the flange ( 9b ) is engaged.
Compensation device ( 1b ) according to claim 7, characterized in that the at least one plastic clip ( 38 . 38a ) flush with an outer circumference or inner circumference of the pendulum masses or of the flange part ( 9b ) is arranged.
Compensation device ( 1c ) for torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine and a transmission comprising a torsional vibration damper (US Pat. 3c ) with an input part ( 4c ) and one against the action of in one of the input part ( 4c ) formed annular space ( 51 ) recorded energy stores ( 5c ) opposite the entrance part ( 4c ) limited rotatable output part ( 6c ) with one in the annulus ( 51 ) engaging flange part ( 45 ) and a parallel to the torsional vibration damper ( 3c ) switched centrifugal pendulum ( 10c ) with an axial to the flange ( 45 ) spaced flange part ( 9c ) with at this on both sides relative to the flange ( 9c ) limited radially and circumferentially pivotally received pendulum masses ( 11c ), characterized in that between the flange ( 9c ) of the centrifugal pendulum ( 10c ) and the input part ( 4c ) of the torsional vibration damper ( 3c ) a plate spring ( 55 ) is braced.
Compensation device ( 1c ) according to claim 9, characterized in that the disc spring ( 55 ) axially against a on the outer circumference of the flange ( 9c ) trained ring board ( 56 ) is braced.
DE201010054297 2009-12-22 2010-12-13 Compensation device for torsional vibrations, particularly in drive train of motor vehicle, has centrifugal pendulum with pendulum masses, which roll off tracks provided in segments of flange part and pendulum masses by cylinder rollers Ceased DE102010054297A1 (en)
DE102009059920 2009-12-22
DE102009059920.7 2009-12-22
DE201010054297 DE102010054297A1 (en) 2009-12-22 2010-12-13 Compensation device for torsional vibrations, particularly in drive train of motor vehicle, has centrifugal pendulum with pendulum masses, which roll off tracks provided in segments of flange part and pendulum masses by cylinder rollers
DE102010054297A1 true DE102010054297A1 (en) 2011-06-30
ID=44311965
DE201010054297 Ceased DE102010054297A1 (en) 2009-12-22 2010-12-13 Compensation device for torsional vibrations, particularly in drive train of motor vehicle, has centrifugal pendulum with pendulum masses, which roll off tracks provided in segments of flange part and pendulum masses by cylinder rollers
DE (1) DE102010054297A1 (en)
WO2012130203A1 (en) * 2011-03-31 2012-10-04 Schaeffler Technologies AG & Co. KG Centrifugal pendulum device
DE102012212694A1 (en) 2012-07-19 2014-01-23 Zf Friedrichshafen Ag Tail vibration damper and method of providing a Tilgerschwingungsdämpfers
WO2014114280A1 (en) * 2012-12-20 2014-07-31 Schaeffler Technologies AG & Co. KG Centrifugal force pendulum
DE102013217091A1 (en) 2013-08-28 2015-03-05 Zf Friedrichshafen Ag Absorber system
WO2015058757A1 (en) 2013-10-24 2015-04-30 Schaeffler Technologies AG & Co. KG Torsional vibration isolation device
US20150167779A1 (en) * 2012-08-27 2015-06-18 Bayerische Motoren Werke Aktiengesellschaft Centrifugal Pendulum
DE102015201199A1 (en) 2014-02-07 2015-08-13 Schaeffler Technologies AG & Co. KG torsional vibration dampers
DE102015203046A1 (en) 2014-02-26 2015-08-27 Schaeffler Technologies AG & Co. KG centrifugal pendulum
DE102014207961A1 (en) 2014-04-28 2015-10-29 Zf Friedrichshafen Ag Tail vibration damper and method of providing a Tilgerschwingungsdämpfers
WO2016058604A1 (en) * 2014-10-16 2016-04-21 Schaeffler Technologies AG & Co. KG Torsional vibration damper with centrifugal force pendulum
FR3031560A1 (en) * 2015-01-14 2016-07-15 Valeo Embrayages Torsion oscillation damping device
DE102015202021A1 (en) 2015-02-05 2016-08-11 Schaeffler Technologies AG & Co. KG centrifugal pendulum
DE102016201099A1 (en) 2015-02-09 2016-08-11 Schaeffler Technologies AG & Co. KG centrifugal pendulum
ITUA20164639A1 (en) * 2016-06-24 2017-12-24 Moretto Spa Method for the production of a mass damper flywheel
DE102017105902A1 (en) 2017-03-20 2018-09-20 Schaeffler Technologies AG & Co. KG centrifugal pendulum
EP3207278B1 (en) 2014-10-14 2019-04-10 Valeo Embrayages Device for damping torsional oscillations
DE102011086567B4 (en) 2010-12-15 2019-10-17 Schaeffler Technologies AG & Co. KG Device for damping torsional vibrations
DE102009021355A1 (en) 2008-06-02 2009-12-03 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torsional vibration damper with centrifugal pendulum
2010-12-13 DE DE201010054297 patent/DE102010054297A1/en not_active Ceased
US9243681B2 (en) 2011-03-31 2016-01-26 Schaeffler Technologies AG & Co. KG Centrifugal pendulum device
CN104471280B (en) * 2012-07-19 2017-10-31 Zf腓特烈斯哈芬股份公司 Snubber and the method for providing snubber
CN104471280A (en) * 2012-07-19 2015-03-25 Zf腓特烈斯哈芬股份公司 Tuned mass damper and method for providing a tuned mass damper
CN104487737A (en) * 2012-07-19 2015-04-01 Zf腓特烈斯哈芬股份公司 Tuned mass damper and damper assembly
CN104487737B (en) * 2012-07-19 2020-02-28 Zf腓特烈斯哈芬股份公司 Shock absorber and shock absorbing assembly
US9915317B2 (en) * 2012-08-27 2018-03-13 Bayerische Motoren Werke Aktiengesellschaft Centrifugal pendulum
CN104956120A (en) * 2012-12-20 2015-09-30 舍弗勒技术股份两合公司 Centrifugal force pendulum
WO2015165669A1 (en) * 2014-04-28 2015-11-05 Zf Friedrichshafen Ag Tuned mass damper and method for providing a tuned mass damper
EP3260734A1 (en) * 2016-06-24 2017-12-27 Moretto S.P.A. Method for the production of a flywheel mass
EP2718586B1 (en) 2019-03-20 Drive system for a vehicle
DE19909044B4 (en) 2018-06-21 torsional vibration dampers
DE102008053377B4 (en) 2018-09-20 rupftilger
DE102012219799B4 (en) 2017-05-24 Torque transfer device
2016-02-11 R130 Divisional application to
Ref document number: 102010064610
2019-08-28 R002 Refusal decision in examination/registration proceedings
2019-10-01 R003 Refusal decision now final