KR101655597B1 - Apparatus for reducing vibration for vehicle - Google Patents

Apparatus for reducing vibration for vehicle Download PDF

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Publication number
KR101655597B1
KR101655597B1 KR1020140175528A KR20140175528A KR101655597B1 KR 101655597 B1 KR101655597 B1 KR 101655597B1 KR 1020140175528 A KR1020140175528 A KR 1020140175528A KR 20140175528 A KR20140175528 A KR 20140175528A KR 101655597 B1 KR101655597 B1 KR 101655597B1
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KR
South Korea
Prior art keywords
base plate
formed
bearing
contact
mass
Prior art date
Application number
KR1020140175528A
Other languages
Korean (ko)
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KR20160070201A (en
Inventor
오완수
이장원
황재웅
진용욱
Original Assignee
현대자동차주식회사
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Priority to KR1020140175528A priority Critical patent/KR101655597B1/en
Publication of KR20160070201A publication Critical patent/KR20160070201A/en
Application granted granted Critical
Publication of KR101655597B1 publication Critical patent/KR101655597B1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/021Decoupling of vibrations by means of point-of-contact supports, e.g. ball bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/022Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression 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
    • F16F15/121Suppression 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 using springs as elastic members, e.g. metallic springs
    • F16F15/123Wound springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers

Abstract

A base plate coupled to the rotating shaft and rotating together, the at least one elongated hole being formed; A pair of mass bodies provided on the front and rear sides of the base plate and coupled to each other through an engaging portion penetrating the elongated hole; And a bearing which is provided between the engaging portion and the inner peripheral portion of the long hole to reduce the frictional force of the engaging portion moving along the long hole.

Description

 [0001] APPARATUS FOR REDUCING VIBRATION FOR VEHICLE [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a vehicle vibration reduction device, and more particularly, to a vehicle vibration reduction device that reduces driving vibration generated when a vehicle is driven.

Recently, eco-friendly vehicles have emerged as an important element of vehicle design, and technologies are being developed to improve the fuel efficiency of the vehicle while reducing fuel consumption as much as possible.

In order to achieve this, in recent years, technologies have been applied to increase the compression ratio and improve the combustion efficiency of the vehicle by installing turbocharger, twin turbo, and two-stage turbocharger to supercharge the air to the combustion chamber.

In the case of an engine using such a turbocharger, since the exhaust amount can generate at least a greater output than the output from the same conventional exhaust amount, the application of the high-power downsizing engine in which the number of cylinders and the amount of exhaust of the engine are reduced while generating the same output as the conventional engine .

However, such a downsized engine can increase the torsional excitation force of the engine as the output relative to the engine displacement and the number of cylinders increases, which can affect the transmission and cause a vibration amount due to the twist of the transmission shaft to also increase .

As the amount of vibration increases, noise and vibration due to vibrations such as a rattle and a boom may be generated, which may lead to inconvenience to a vehicle user, which may lead to a problem of deteriorating the commerciality of the vehicle.

In order to solve this problem, a conventional KR10-2000-0025389 A vehicle vibration reduction apparatus and method thereof includes an accelerometer for detecting a vibration of a vehicle and generating a vibration signal corresponding thereto, A tracking filter for filtering a vibration signal synchronized with the engine rotation signal and outputting a filtering signal from the vibration signal; and a phase shifter for shifting the phase of the filtered signal by 180 degrees, Phase signal generator for generating a vibration signal and an unbalanced mass for vibration generation, and generates a vibration corresponding to the drive signal by inputting the anti-phase signal as a drive signal.

However, such a conventional technology has a complicated structure and is controlled by an electronic method, which may cause a breakdown, and various parts have been included to cause difficulties in production and installation.

It should be understood that the foregoing description of the background art is merely for the purpose of promoting an understanding of the background of the present invention and is not to be construed as an admission that the prior art is known to those skilled in the art.

KR 10-2000-0025389 A

SUMMARY OF THE INVENTION The present invention has been proposed in order to solve such a problem, and provides a vibration reduction device for a vehicle that reduces vibration generation due to rotation of an engine in cooperation with rotation of an engine and simplifies a structure, thereby improving vibration reduction performance and productivity. There is a purpose.

According to an aspect of the present invention, there is provided a vibration reduction device for a vehicle, comprising: a base plate rotatably coupled to a rotation shaft and having at least one elongated hole; A pair of mass bodies provided on the front and rear sides of the base plate and coupled to each other through an engaging portion penetrating the elongated hole; And a bearing which is provided between the engaging portion and the inner peripheral portion of the long hole to reduce the frictional force of the engaging portion moving along the long hole.

The elongated holes may be formed only on the base plate and not on the mass body.

The elongated holes are arc-shaped, and the imaginary tangent lines at both ends may be formed so as to be perpendicular to each other.

The pair of mass bodies each having both ends extending to both side ends of the base plate so that both ends of the pair of mass bodies are coupled to each other via the coupling portion, And may be provided at the upper end and the lower end of the base plate, respectively.

The coupling portion may be riveted.

The bearing has an inner circumferential surface contacting the outer circumferential surface of the engaging portion, and a flange protruding toward the circumferential portion of the elongated hole on the outer circumferential surface of the bearing to partially surround the circumferential portion of the elongated hole.

And hemispherical contact protrusions protruding toward the pair of mass bodies may be provided on the front and rear surfaces of the long hole-side base plate.

The end of the contact projection may be formed to be higher than the end of the bearing in the projecting direction so as to be in contact with the mass.

And gear teeth that are engaged with each other may be formed on the inner peripheral surface of the long hole and the outer peripheral surface of the bearing.

A stopper may be provided on the base plate on both end sides of the mass body so as to be in contact with an end of the mass body so that the engaging portion does not contact the end of the long hole.

According to the vibration reduction device for a vehicle having the above-described structure, it is possible to reduce the occurrence of vibration due to twisting as the mass moves relative to the rotation of the engine and to provide a bearing and a stopper at a position where friction can be generated, It is possible to prevent the occurrence of residual vibration and noise due to the impact.

In addition, it can be designed to operate mechanically and simplify the structure to improve productivity and reduce costs.

1 is a front view of a vehicle vibration reduction device according to a first embodiment of the present invention;
Fig. 2 is a cross-sectional view taken along line AA in Fig. 1; Fig.
3 is a view showing a mass of a vibration reduction device for a vehicle according to a first embodiment of the present invention.
4 is a front view of a vehicle vibration reduction device according to a second embodiment of the present invention;

Hereinafter, a vehicle vibration reduction device according to a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

FIG. 1 is a front view of a vibration reduction device for a vehicle according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line AA of FIG. 1, which is rotated together with an engine or a transmission rotation shaft, 110) is formed; A pair of mass bodies 200 provided in front of and behind the base plate 100 and coupled to each other through a coupling portion 300 passing through the elongated hole 110; And a bearing 310 provided between the coupling portion 300 and the inner peripheral portion of the elongated hole 110. [

The central portion of the base plate 100 may be coupled to a rotation shaft of an engine or a transmission to rotate together with the engine or the transmission. When the base plate 100 rotates, The pair of mass bodies 200 connected to the coupling portion 300 are moved by sliding the long holes 110. The mass body 200 may be in the form of a panel. When the mass of the mass body 200 functions as an inertia damper to change the rotational force of the rotating shaft due to the fluctuation of the piston gas pressure, instantaneous torque is prevented from being applied to the rotating shaft. The driving vibration due to the fluctuation of the piston gas pressure and thus the occurrence of the rattling and the booming can be suppressed.

It is preferable that the elongated holes 110 are formed only in the base plate 100 and not formed in the mass body 200. When the elongated holes are formed in the mass body 200, Since three movement paths are formed and different motions can be displayed according to the respective movement paths, the design becomes complicated and the control becomes unstable. In addition, when the mass 200 is small, the size and shape of the long holes that can be formed in the mass body 200 may be limited. Accordingly, the size and shape of the long holes 110 formed in the base plate 100 may be limited The overall travel path is limited and the degree of freedom of path design can be limited. The point of contact with the coupling portion 300 or the bearing 310 is increased and the total frictional force with the coupling portion 300 or the bearing 310 can be increased and the load applied to the coupling portion 300 can be increased Thereby reducing the durability of the coupling portion 300, or generating frictional noise.

Therefore, in this embodiment, the elongated holes 110 are formed only on the base plate 100, so that the design and control are facilitated and the possible area for forming the elongated holes 110 is increased, And the maximum bending angle at which the elongated holes 110 can be formed can be increased. In addition, since there is only one friction point with the coupling portion 300 or the bearing 310, there is an advantage that the slip occurrence is reduced and the durability of the coupling portion 300 or the occurrence of friction noise due to slip can be reduced will be.

It is preferable that the elongated holes 110 are formed symmetrically on both ends of the upper and lower ends of the base plate 100. The pair of mass bodies 200 are formed such that both ends of the elongated holes 110 are extended to both ends of the base plate 100 A pair of mass bodies 200 coupled to each other via both coupling portions 300 may be provided at the upper and lower ends of the base plate 100, respectively. At this time, the mass bodies 200 on the upper and lower ends of the base plate 100 are preferably arranged symmetrically with respect to the center of the base plate 100.

For example, a plurality of mass bodies 200 may be arranged on one surface of the base plate 100 at various intervals such as 180 degrees, 120 degrees, or 90 degrees, for example. And the elongated holes 110 can be formed at various positions in accordance with the arrangement interval of the mass bodies 200. [

In addition, the elongated holes 110 may be formed to be arc-shaped and bent at both ends so that imaginary tangential lines a and b are perpendicular to each other. Accordingly, the range in which the engaging portion 300 can move along the long hole 110 is limited to a range of 90 degrees. Accordingly, the range in which the mass body 200 can move is also limited to allow excessive movement of the mass body 200 So that it is possible to prevent the engine output from being excessively absorbed by the inertia damping of the mass body 200. When the center of gravity of the mass body 200 is positioned at the center of both sides of the base plate 100, the coupling unit 300 is positioned at the center of the long hole 110, Clockwise or counterclockwise to move in the counterclockwise or clockwise direction of the mass body 200 by inertia so that the inertia damper function can be performed with respect to the full rotation direction.

In this embodiment, the bending angle of the elongated hole 110 is 90 degrees. However, the bending angle of the elongated hole 110 may be variously set according to the designer's intention.

3, the coupling unit 300 may be riveted to couple the pair of mass bodies 200 to each other. In addition, the coupling unit 300 may be a combination member such as a bolt or a pin in addition to the rivet. have.

2, the bearing 310 enhances the mobility of the coupling portion 300 between the inner peripheral portion of the elongated hole 110 and the coupling portion 300. The bearing 310, A flange 311 is formed on the outer circumferential surface of the bearing 310 so as to protrude toward the periphery of the elongated hole 110 and partially surround the circumference of the elongated hole 110 The flange 311 prevents the base plate 100 and the mass body 200 from coming into contact with each other, thereby preventing friction from occurring.

It is preferable that the bearing 310 be a needle bearing so as to secure the stability of the rolling movement. Since the coupling part 300 slips along the long hole 110 due to the bearing 310, The friction resistance can be reduced.

A hemispherical contact protrusion 120 protruding toward the pair of mass bodies 200 may be provided on the front and rear surfaces of the base plate 100 on the long hole 110. The tip of the contact protrusion 120 The bearing 310 may be formed to be higher than the end of the bearing 310 in the protruding direction so as to be in contact with the mass 200.

The contact protrusions 120 may be formed to be directly coupled to the base plate 100. However, the contact protrusions 120 may be formed by forming grooves or holes in the base plate 100, You may. Of course, the groove or the hole may be provided with a lubrication or a separate bearing or the like so that the ball can be rolled, and it should be able to support the ball.

The contact protrusions 120 may contact the mass body 200 more than the bearings 310 and the base plate 100 so that the mass body 200 may contact the base plate 100 while minimizing the contact area with the mass body 200. [ It is possible to prevent friction noise and vibration from occurring by minimizing friction due to contact.

In addition, by making the contact protrusions 120 semi-spherical, it is possible to minimize the contact area and prevent excessive stress concentration at the contact area as compared with a polygonal structure such as a conical shape upon contact with the mass body 200, Can be prevented.

Although the contact protrusions 120 are formed adjacent to the elongated holes 110 in the first embodiment, the positions of the contact protrusions 120 may be variously set, and the number of the contact protrusions 120 may be variously set .

A stopper 400 may be provided on the base plate 100 on both ends of the mass body 200 so as to be in contact with the ends of the mass body 200 so that the coupling portion 300 does not contact the end of the elongated hole 110 .

The mass body 200 can move along the elongated hole 110 in a direction opposite to the rotational direction due to inertia when the base plate 100 rotates clockwise or counterclockwise, So that excessive noise or friction can be generated due to strong collision with the end of the long hole 110 and a considerable impact is generated in the coupling part 300 so that breakage of the coupling part 300 may occur have.

Therefore, the stopper 400 may be installed to contact the outer circumferential surface of the mass body 200 with the stopper 400 in advance before the impact occurs in the joint portion 300, thereby preventing the mass body 200 from moving. So that damage to the unit 300 can be prevented and noise and vibration can be prevented. Of course, it is preferable that an elastic material such as rubber or resin be wrapped around the stopper 400, or the stopper 400 itself may be made of a material capable of absorbing an impact have.

The stopper 400 may be formed one by one between corresponding ends of a plurality of mass bodies 200 disposed on one surface of the base plate 100. The stopper 400 may be formed directly on the front and rear surfaces of the base plate 100, May be formed to be inserted into the base plate 100 so as to protrude from the front and rear surfaces of the base plate 100, respectively. Of course, various other embodiments are possible.

4 is a front view of a vibration reduction device for a vehicle according to a second embodiment of the present invention. In the second embodiment, a gear tooth 500 (see Fig. 4) which meshes with the inner peripheral surface of the long hole 110 and the outer peripheral surface of the bearing 310 ), The rest of them can be configured similarly to the first embodiment.

Specifically, in the second embodiment, the gear teeth 500 formed in the elongated hole 110 may be formed on the entire inner circumferential surface along the circumference of the elongated hole 110, but preferably, the outer diameter of the elongated hole 110 and the outer side It is preferably formed only on the radial side. Since the outer and inner radii have different lengths and bending angles, the number of gear teeth 500 can be different from each other. In order to enable rotation of the bearing 310, the outer side of the inner circumferential surface of the elongated hole 110 It is preferable that it is formed only along the radius. Since the gear teeth 500 are provided and the bearings 310 can move while being engaged with the elongated holes 110, it is possible to prevent slippage between the bearings 310 and the elongated holes 110, 310 or the coupling part 300 can be prevented from being damaged.

As another form of the gear teeth 500, the gear teeth 500 can be replaced by friction surfaces. A friction surface, which is in contact with the inner circumferential surface of the elongated hole 110 and the outer circumferential surface of the bearing 310, It is possible to prevent a slip between the elongated hole 310 and the elongated hole 110 from being generated.

According to the vibration reduction device for a vehicle having the above-described structure, it is possible to reduce the occurrence of vibration due to twisting as the mass moves relative to the rotation of the engine and to provide a bearing and a stopper at a position where friction can be generated, It is possible to prevent the occurrence of residual vibration and noise due to the impact.

Further, since the bearings are provided between the elongated holes and the engaging portions so that the engaging portions are slid against the elongated holes, rather than being moved, the rolling movement is performed, thereby reducing resistance due to friction slip and smooth and smooth movement.

In addition, it can be designed to operate mechanically and simplify the structure to improve productivity and reduce costs.

While the present invention has been particularly shown and described with reference to specific embodiments thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the following claims It will be apparent to those of ordinary skill in the art.

100: base plate 110: long hole
120: contact protrusion 200: mass
300: engaging portion 310: bearing
311: Flange 400: Stopper
500: gear

Claims (10)

  1. A base plate coupled to the rotating shaft and rotating together, the at least one elongated hole being formed;
    A pair of mass bodies provided on the front and rear sides of the base plate and coupled to each other through an engaging portion penetrating the elongated hole; And
    And a bearing provided between the engaging portion and the inner peripheral portion of the long hole to reduce the frictional force of the engaging portion moving along the long hole,
    Wherein a gear tooth meshing with each other is formed on an inner peripheral surface of the long hole and an outer peripheral surface of the bearing.
  2. The method according to claim 1,
    Wherein the elongated holes are formed only in the base plate and are not formed in the mass body.
  3. The method according to claim 1,
    Wherein the elongated holes are formed in arc shapes so that imaginary tangent lines of the elongated holes are perpendicular to each other.
  4. The method according to claim 1,
    The pair of mass bodies each having both ends extending to both side ends of the base plate so that both ends of the pair of mass bodies are coupled to each other via the coupling portion, Wherein the base plate is provided at the upper end and the lower end of the base plate, respectively.
  5. The method according to claim 1,
    Wherein the coupling portion is a rivet.
  6. The method according to claim 1,
    Wherein the bearing has an inner circumferential surface in contact with an outer circumferential surface of the engaging portion and a flange protruding toward the circumferential portion of the elongated hole on the outer circumferential surface of the bearing to partially surround the circumferential portion of the elongated hole.
  7. The method according to claim 1,
    And a hemispherical contact protrusion protruding toward the pair of mass bodies is provided on the front and rear surfaces of the long hole-side base plate.
  8. The method of claim 7,
    Wherein an end of the contact projection is formed to be higher than an end of the bearing in a protruding direction so as to be in contact with the mass.
  9. delete
  10. The method of claim 4,
    Wherein a stopper is provided on the base plates on both end sides of the mass body so as to be in contact with the ends of the mass body so that the engaging portion does not contact the end of the long hole.
KR1020140175528A 2014-12-09 2014-12-09 Apparatus for reducing vibration for vehicle KR101655597B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020140175528A KR101655597B1 (en) 2014-12-09 2014-12-09 Apparatus for reducing vibration for vehicle

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KR1020140175528A KR101655597B1 (en) 2014-12-09 2014-12-09 Apparatus for reducing vibration for vehicle
DE102015103415.8A DE102015103415B4 (en) 2014-12-09 2015-03-09 Vibration reduction device for a vehicle

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KR20160070201A KR20160070201A (en) 2016-06-20
KR101655597B1 true KR101655597B1 (en) 2016-09-08

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Citations (4)

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Publication number Priority date Publication date Assignee Title
JP2008057584A (en) 2006-08-29 2008-03-13 Bridgestone Corp Torsional damper
JP2012523533A (en) * 2009-04-14 2012-10-04 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフトSchaeffler Technologies GmbH & Co. KG Centrifugal pendulum
JP2013210006A (en) 2012-03-30 2013-10-10 Aisin Aw Co Ltd Centrifugal pendulum vibration absorbing device
WO2013156733A1 (en) 2012-04-20 2013-10-24 Valeo Embrayages Pendular damping device, especially for a motor vehicle transmission

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20000025389A (en) 1998-10-10 2000-05-06 홍종만 Device for reducing vibration for vehicle and method thereof
DE102006028556B4 (en) 2005-07-11 2019-10-10 Schaeffler Technologies AG & Co. KG Torque transfer device
DE102009042156A1 (en) 2008-10-09 2010-05-06 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Centrifugal pendulum mechanism for reducing noise and vibration in power train of motor vehicle, has pendulum mass exhibiting higher density than iron or steel concerning total volume of mass, where mass is hung at rotary carrier disk
DE102011100895C5 (en) 2010-06-10 2019-02-21 Schaeffler Technologies AG & Co. KG centrifugal pendulum
DE102013204713A1 (en) 2013-03-18 2014-09-18 Zf Friedrichshafen Ag Tilgerschwingungsdämpfer
DE102014211613A1 (en) 2014-06-17 2015-12-17 Schaeffler Technologies AG & Co. KG Centrifugal pendulum device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008057584A (en) 2006-08-29 2008-03-13 Bridgestone Corp Torsional damper
JP2012523533A (en) * 2009-04-14 2012-10-04 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフトSchaeffler Technologies GmbH & Co. KG Centrifugal pendulum
JP2013210006A (en) 2012-03-30 2013-10-10 Aisin Aw Co Ltd Centrifugal pendulum vibration absorbing device
WO2013156733A1 (en) 2012-04-20 2013-10-24 Valeo Embrayages Pendular damping device, especially for a motor vehicle transmission

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DE102015103415B4 (en) 2019-04-25
KR20160070201A (en) 2016-06-20
DE102015103415A1 (en) 2016-06-09

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