WO2013110728A1 - Élément d'amortissement pour un amortisseur de vibrations hydraulique - Google Patents

Élément d'amortissement pour un amortisseur de vibrations hydraulique Download PDF

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Publication number
WO2013110728A1
WO2013110728A1 PCT/EP2013/051377 EP2013051377W WO2013110728A1 WO 2013110728 A1 WO2013110728 A1 WO 2013110728A1 EP 2013051377 W EP2013051377 W EP 2013051377W WO 2013110728 A1 WO2013110728 A1 WO 2013110728A1
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WO
WIPO (PCT)
Prior art keywords
functional
disk
spring
disc
damping element
Prior art date
Application number
PCT/EP2013/051377
Other languages
German (de)
English (en)
Inventor
Jan LUBINA
Original Assignee
Thyssenkrupp Bilstein Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thyssenkrupp Bilstein Gmbh filed Critical Thyssenkrupp Bilstein Gmbh
Priority to EP13701756.2A priority Critical patent/EP2807397A1/fr
Publication of WO2013110728A1 publication Critical patent/WO2013110728A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination

Definitions

  • the invention relates to a damping element for a hydraulic vibration damper, in particular for motor vehicles.
  • the damping element has at least one flow channel and at least one spring disk valve with a spring disk package formed from a plurality of spring disks.
  • the spring disk package is biased against a valve seat surface of the damping element and determines the fluid passage through the flow channel when the working piston in the fluid space of a vibration damper performs piston movements.
  • the damping element can be arranged on the working piston of a hydraulic vibration damper. Such an arrangement is known for example from DE 12 60 899 A.
  • the damping element can also be fixedly arranged on a hydraulic vibration damper and be connected by fluid channels with its working spaces on both sides of the working piston. Such a fixed damping element is also referred to in practice as a comfort valve.
  • a working piston for a hydraulic vibration damper which has a spring disk valve in the form of a spring sheath packet formed from a plurality of spring washers on both end faces.
  • the arranged on the side facing away from the piston rod side of the working piston spring disk valve which opens in a piston movement in the pulling direction of the piston rod and closes in an opposite piston movement in the pressure direction of the flow channel contains at least one by-pass opening.
  • the by-pass orifice is located in the spring washer of the spring washer package resting on the valve seat surface and allows passage of a by-pass fluid flow when the power piston is moving
  • the by-pass opening can be flowed through in both flow directions.
  • the by-pass port is designed for this case and allows substantially unattenuated movements of the working piston, which are performed with small amplitudes and low piston speeds. The result is a high rolling comfort of the vehicle when driving over patched asphalt surfaces, which are also referred to as "patch asphalt".
  • the spring disk valve When the working piston is excited during a journey over an uneven road or when cornering to larger strokes, the spring disk valve responds and adjusts itself by an elastic deformation of the spring washers on the valve seat a valve gap whose gap width depends on the spring characteristic of the spring disk package.
  • the spring characteristic of the spring disk package is to be set so that when driving over uneven distances and when cornering high damping forces can be applied to avoid instabilities of the vehicle body.
  • the by-pass opening of the spring disc valve is disadvantageous. With regard to the interpretation of the by-pass opening, there is a conflict of objectives. On the one hand, a large section of the by-pass opening is sought so that when driving the vehicle z. B.
  • EP 0 632 212 A2 describes a working piston for a hydraulic vibration damper which has at least one overpressure valve which releases at least one by-pass at high liquid pressures.
  • the pressure relief valve may consist of a spring-loaded valve body or a cooperating with a valve seat spring washer.
  • a damping element for a hydraulic vibration damper which has a spring disk packet formed from a plurality of spring disks as a spring disk valve.
  • the spring disk package comprises a first functional disk, which rests on the edge side on a valve seat surface and has at least one throughflow opening for the passage of a by-pass fluid flow.
  • a flexible disk is provided, which covers the flow-through opening of the first functional disk without edge-side fixing within a fluid space enclosed by the valve seat surface. In the idle state of the damping element, the flow-through opening is blocked. The flexible disk releases the through-flow opening of the first functional disk for passing a by-pass fluid flow when the spring disk valve is subjected to a hydraulic pressure in the closing direction.
  • a disc valve with a similar structure is also described in DE 32 46 866 A1.
  • EP 1 860 341 A discloses a working piston for a vibration damper which has a flow channel with an associated non-return valve.
  • the check valve is formed by a valve seat disc and a flexible valve disc, wherein the two discs are clamped by means of a spacer ring against each other.
  • the valve seat disc has radially arranged, slot-shaped by-pass openings, which differ from
  • the check valve is arranged on the end face of the working piston facing the piston rod and permits flow through in both directions of flow at low piston speeds. As the piston speed increases in the pulling direction, the valve disc abuts against the surface of the valve seat disc and closes the by-pass openings successively from outside to inside.
  • the damping characteristic of the working piston in a piston movement in the direction of pull is determined by the closing characteristic of the check valve.
  • the non-return valve formed from the valve seat disc and a flexible valve disc replaces the function of a spring disc pack formed from a plurality of spring washers and can not be used in combination with other spring washers.
  • the closing characteristic depends on the geometry and the arrangement of the provided in the valve seat disc by-pass openings, the dimensions of the spacer ring and the spring characteristic of the flexible valve disc. If the damping characteristic of the working piston to be changed, the functional parts described must be re-matched. The design and adjustment of the damping characteristic is technically complex.
  • the invention has the object to provide a damping element for a hydraulic vibration damper, which has at least one by-pass opening for passing a by-pass fluid flow, which can be flowed through at low flow rates in both flow directions and at a higher flow rate closes in a movement direction opening the spring disk valve.
  • the damping element is to allow undamped piston movements of the working piston of a vibration damper with small amplitude and low piston speed and should the damping characteristic of the
  • Vibration damper not adversely affect when large damping forces to prevent instabilities of the vehicle body are required.
  • the damping element comprises, in a manner known per se, at least one flow channel and at least one spring disk valve with a spring disk packet formed from a plurality of spring disks which bears against a valve seat surface of the damping element under tension.
  • the spring disk valve comprises a functional unit comprising at least two functional disks, wherein the first functional disk rests on the valve seat surface and has at least one flow-through opening for passing a by-pass fluid flow and wherein the second functional disk consists of a flexible disk and without edge-side fixing within one of the valve seat surface enclosed fluid space, the flow opening of the first functional disk completely or at least largely covers.
  • the first functional disk which fulfills a valve function of the spring disk package, is stiffer than the flexible second functional disk. This ensures that the second functional disk rests against the surface of the first functional disk when the spring disk valve is opened and the flow opening is still blocked.
  • the arrangement according to the invention has the advantage that the by-pass fluid flow can be optimized under vibration control aspects and can be dimensioned so large that piston movements of the vibration damper, the z. B. caused by a repaired patch or cobblestones, can be taken substantially unattenuated and are not transmitted to the vehicle body.
  • a large flow area for the passage of the by-pass fluid flow does not lead to instabilities of the movement of the vehicle body, because by closing the flow opening when larger, acting in the opening direction of the spring disk valve forces the damping characteristic of the spring disk package is fully effective when the working piston of a Vibration damper when driving over uneven roads or in critical driving situations large piston movements executes with correspondingly high piston speeds.
  • the inventive functional unit consisting of at least two functional disks is also suitable for retrofitting existing vibration dampers. In the case of retrofitting no structural changes must be made to the damping element of the vibration.
  • the spring washer assembly of an existing damping element can be adopted. It is only to insert the functional disks according to the invention in the existing spring washer package.
  • the vibration dampers which are approved for vehicle types and do not yet have the functionality according to the invention, can be easily retrofitted by modifying the spring washer package present on the damping element.
  • the functional unit has a third functional disk with at least one by-pass opening, wherein the by-pass opening of the third functional disk and the throughflow opening of the first functional disk are in fluid communication.
  • the supported on the valve seat surface first functional disk has a curvature due to the bias of the spring disk package.
  • the curvature of the first functional disk can be used to realize the fluid gap required for a by-pass flow between a fluid space surrounded by the valve seat surface and the flow-through opening of the first functional disk.
  • the curvature of the first functional disk supported on the valve seat surface and a planar surface of the second functional disk are coordinated so that the necessary fluid gap is formed between the surfaces mentioned.
  • the spring washer valve rests on a biasing disc, wherein the thickness of the biasing disc is measured so that the valve seat surface protrudes further than the biasing disc.
  • the second functional disk has a lower spring stiffness than the first functional disk.
  • the third functional disk of the functional unit expediently has a plurality of by-pass openings, which are arranged in the circumferential direction with preferably the same pitch.
  • the by-pass openings extend in particular to the outer edge of the third functional disk.
  • the number of by-pass openings and the shape as well as the number of flow-through openings in the first functional disks are to be matched to one another in such a way that there is sufficient overlap between the by-pass openings and the flow-through openings.
  • the openings are expedient to determine the openings in such a way that the flow-through openings are simultaneously closed by elastic deformation of the second functional disk. They are in particular arranged so that they are covered by a circumferential ring surface of the second functional disk.
  • the first functional disk preferably has a plurality of arcuate, slot-shaped throughflow openings curved in plan view.
  • the flow-through openings are preferably arranged at their ends so as to be radially offset on the disk surface of the first functional disk such that overlapping of the by-pass openings and throughflow openings independent of the alignment of the two functional disks results.
  • This arrangement has the advantage that the first and third functional disk can be rotated against each other without the flow characteristic of the functional unit thereby changing.
  • the functional disks of the functional unit can therefore be mounted without having to pay attention to the angle of rotation of the functional disks.
  • the damping element according to the invention can be arranged as a comfort valve fixed to a vibration damper.
  • it has a housing which can be flanged, for example, to the cylinder of the vibration damper and is in fluid communication with the working spaces on both sides of the working piston.
  • the working piston of a hydraulic vibration damper may have an inventive damping element. This is expediently arranged on the side facing away from the piston rod end face of the working piston.
  • Fig. 2 shows a detail of a working piston for a hydraulic
  • Vibration damper which is equipped with an inventively designed spring washer valve
  • Fig. 3 and 4 functional disks of the spring disk valve shown in Fig. 2.
  • Fig. 5a to 5 c variants of the functional disks as Einzelteil- drawings and in the assembled state.
  • FIG. 1 shows a working piston for a hydraulic vibration damper according to a prior art known from practice.
  • the working piston 101 is connected to a piston rod 102 and performs piston movements in the direction of movement a and pressure direction b of the piston rod 102 in the fluid space of an only indicated vibration damper 103.
  • the working piston 101 has flow channels 104, 104 'and spring disk valves 105, 105', which are arranged on the end faces of the working piston 101 and determine the fluid passage through the associated flow channel 104 or 104 'during a movement of the working piston 101 in the fluid space of the vibration damper 103 ,
  • the spring disk valves 105, 105 'each have a spring disk package of a plurality of spring disks 106, 106', which rest under prestress against a valve seat surface 107, 107 'of the working piston.
  • the spring disk valve 105 opens during a movement of the working piston in the pulling direction wherein the spring stiffness of the spring disks 106, the number of spring disks and the dimensions of the spring disks of the spring disk package determine the damping characteristic of a piston movement in the pulling direction a.
  • the spring disk valve 105 on the end face of the working piston 101 facing away from the piston rod 102 is therefore also referred to below as a rebound stage valve.
  • the spring washer of the rebound valve 105 lying on the valve seat surface 107 contains at least one by-pass opening 108 for the passage of a by-pass fluid flow when the working piston 101 performs movements in the fluid space of the vibration damper 103.
  • the by-pass opening 108 can be flowed through in both flow directions and allows piston movements of the working piston 101 with small amplitude and small piston speed without the spring disk package of the rebound valve 105 responding.
  • the by-pass opening 108 of the rebound valve 105 increases the ride comfort of a vehicle equipped with the vibration damper when the vehicle wheel z. B. under a so-called "patch asphalt", ie on a repaired in many places asphalt surface rolls. Improved piston movements are absorbed without damping and do not transfer to the vehicle body.
  • the spring disk package of the rebound valve 105 is responsive and opens a flow gap between the valve seat surface 107 and cooperating with the valve seat surface spring washer 106 of the spring disk package.
  • the spring characteristic of the spring disk package determines the damping characteristic of the vibration damper in the pulling direction a.
  • the effluent portion of the hydraulic fluid reduces the damping forces that may be generated by the spring disc package of the rebound valve 105 and can lead to instabilities in the movements of the vehicle body, when in extreme driving situations, when cornering or when driving over uneven paths large damping forces are required.
  • the by-pass opening should be dimensioned as large as possible, so that the ride comfort when driving over asphalt surfaces is as large as possible.
  • a large by-pass cross section is disadvantageous when driving situations require large damping forces.
  • the working piston 101 shown in FIG. 1 has a further spring disk valve 105 'in the form of a spring disk package, which is arranged on the end face of the working piston 101 facing the piston rod 102.
  • the piston rod side arranged spring disk valve 105 ' opens the flow path through the working piston 101 during a movement of the working piston 101 in the pressure direction b and is therefore also referred to as a pressure stage valve.
  • the pressure stage valve 105 ' also has a by-pass opening 108', which, however, can only be flowed through in one direction and locked in the opposite flow direction by a series-connected check valve 109.
  • the blocking of the by-pass path by the additional check valve 109 has disadvantages, because the entire fluid flow must flow through the check valve 109.
  • the valve disc of the check valve 109 must make a large stroke. Further, due to the large fluid flows at the check valve 109, flow noises are possible. The check valve 109 is also exposed to a large load, so that sometimes the service life is unsatisfactory. Furthermore, the integration of the check valve 109 in the working piston 101 is structurally complex.
  • a working piston 1 is shown with an inventively designed spring disk valve 5, which operates in the embodiment as a rebound valve. It is arranged on the end face of the working piston 1 facing away from the piston rod 2 and determines the fluid passage through a flow channel 4 of the working piston during a movement of the working piston 1 in the fluid space of the vibration damper 3.
  • the spring disk valve 5 has a spring disk package of several spring disks 6 and is under prestress on a valve seat surface 7 of the working piston 1 at. It comprises a functional unit made up of three resilient functional disks 10, 11, 12.
  • a first functional disk 1 1 of the functional unit rests on the edge of the valve seat surface 7 and has at least one through-flow opening 13 for the passage of a by-pass fluid flow.
  • the flow-through opening is at a distance from the valve seat surface 7 and has no overlap with the valve seat surface 7.
  • a second functional disk 10 of the functional unit consists of a flexible disk and covers the flow-through opening 13 of the first functional disk 1 1 completely or at least for the most part without fixing at the edge within a fluid space enclosed by the valve seat surface 7. Between the adjacent surfaces of the two functional disks 10, 1 1 there remains a fluid gap s, which can be closed by an elastic deformation of the second functional disk 10 as a result of a rear-side hydraulic pressure application.
  • the functional unit may comprise a third functional disk 12 which has at least one by-pass opening 8. The by-pass opening extends in the exemplary embodiment to the edge of the third functional disk and is in fluid communication with the flow-through opening 13 of the first functional disk 11.
  • the working piston 1 If the working piston 1 is moved in the traction direction a in the fluid space of the vibration damper 3, a pressure builds up on the rear side of the second functional disk 10, under the effect of which the flexible functional disk 10 tightly abuts the first functional disk 11 and closes the throughflow opening 13. If the hydraulic pressure reaches a limit value during a faster piston movement, the first functional disk 11 lifts off the valve seat surface 7 and releases a gap between the spring disk package and the valve seat surface.
  • the first functional disk 1 1 is part of the spring disk package and defined in cooperation with the other spring disks 6, the damping characteristic of the spring disk valve 5 at larger and executed with a correspondingly large piston speed movements of the working piston. 1 Because the by-pass is closed when the spring washer package responds and clears the flow path, the by-pass cross-section does not lead to instabilities in the movements of the vehicle body when high damping forces are required.
  • FIG. 2 reveals that the spring disk valve 5 rests on a pretensioning disk 20, wherein the thickness of the pretensioning disk 20 is dimensioned such that the valve seat surface 7 projects further on the end face of the working piston than the pretensioning disk 20 and consequently the first functional disk 1 1 as a result of the bias of the spring disc package has a curvature.
  • a fluid gap s is formed between the curved surface of the first functional disk 11 and a flat surface of the second functional disk 10, through which a by-pass fluid flow can flow in both directions of flow.
  • the second functional disk 10 has a lower spring stiffness than the first functional disk 11 and lays itself down even when small hydraulic pressures occur
  • FIG. 3 shows the third functional disk 12 in a plan view.
  • the functional disk 12 has a plurality of by-pass openings 8, which are arranged in the same direction in the circumferential direction and preferably extend as far as the outer edge of the functional disk.
  • the first functional disk 1 1 is shown.
  • the latter has a plurality of slot-shaped through-flow openings 13 curved arcuately in plan view.
  • the through-flow openings 13 of the first functional disk 1 1 and the by-pass openings 8 of the third functional disk 12 are matched to one another such that adequate overlap of the by-pass openings 8 and the throughflow openings 13 is ensured.
  • FIGS. 5a to 5c show further embodiment variants of the functional disks 11, 12.
  • the flow-through openings 13 of the first functional disk 1 1 are arranged at their ends so as to be radially offset on the disk surface of the functional disk such that overlapping of by-pass openings 8 and through-flow openings substantially independent of the alignment of the two functional disks 11, 12 occurs 13 results.
  • 5c shows the overlapping of the openings 8, 13.
  • the functional disks 1 1, 12 can be rotated relative to each other, whereby a sufficient and substantially constant coverage is always ensured.
  • spring disk valve 5 is arranged on the side remote from the piston rod 2 end face of the working piston 1 and acts as a rebound valve.
  • the working piston 1 can be a compression valve.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne un élément d'amortissement destiné à un amortisseur de vibrations hydraulique comprenant au moins un canal d'écoulement (4) et au moins une soupape à rondelles élastiques (5). La soupape à rondelles élastiques (5) comporte un groupe de rondelles élastiques constitué de plusieurs rondelles élastiques (6), lequel prend appui sous l'effet d'une précontrainte sur une surface de siège de soupape (7) de l'élément d'amortissement et comprend un groupe fonctionnel constitué d'au moins deux rondelles fonctionnelles (10, 11). La première rondelle fonctionnelle (11) du groupe fonctionnel repose côté bord sur la surface de siège de soupape (7) et comporte au moins une ouverture d'écoulement (13) pour le passage d'un fluide de dérivation. La deuxième rondelle fonctionnelle (10) du groupe fonctionnel est composée d'une rondelle flexible et recouvre en totalité ou du moins en grande partie l'ouverture d'écoulement de la première rondelle élastique, sans fixation côté bord, à l'intérieur d'un espace pour fluide entouré par la surface de siège de soupape (7). Entre les surfaces adjacentes des deux rondelles fonctionnelles (11, 10) reste une fente pour fluide (s) qui peut être fermée par une déformation élastique de la deuxième rondelle fonctionnelle (10) du fait d'une contrainte de pression hydraulique exercée sur la face arrière.
PCT/EP2013/051377 2012-01-27 2013-01-24 Élément d'amortissement pour un amortisseur de vibrations hydraulique WO2013110728A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13701756.2A EP2807397A1 (fr) 2012-01-27 2013-01-24 Élément d'amortissement pour un amortisseur de vibrations hydraulique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012100690.3A DE102012100690B4 (de) 2012-01-27 2012-01-27 Dämpfungselement für einen hydraulischen Schwingungsdämpfer
DE102012100690.3 2012-01-27

Publications (1)

Publication Number Publication Date
WO2013110728A1 true WO2013110728A1 (fr) 2013-08-01

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EP (1) EP2807397A1 (fr)
DE (1) DE102012100690B4 (fr)
WO (1) WO2013110728A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9500251B2 (en) 2014-11-25 2016-11-22 Tenneco Automotive Operating Company Inc. Shock absorber having orifice check disc
US9845839B2 (en) 2016-02-18 2017-12-19 Tenneco Automotive Operating Company Inc. Shock absorber having check disc for orifice passage

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020209288A1 (de) * 2020-07-23 2022-01-27 Thyssenkrupp Ag Schwingungsdämpfer-Ventilanordnung mit schaltbarem Bypass

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1260899B (de) 1962-01-11 1968-02-08 Christian Marie Lucien Louis B Federscheibenventil, insbesondere fuer Stossdaempferkolben
US4197929A (en) * 1978-01-13 1980-04-15 Kayaba Kogyo K.K. Device for producing damping force in hydraulic shock absorbers
DE3246866A1 (de) 1981-12-18 1983-07-14 Tokico Ltd., Kawasaki, Kanagawa Hydraulischer daempfer
US5316113A (en) * 1987-11-19 1994-05-31 Atsugi Motor Parts Company Ltd. Hydraulic shock absorber
EP0632212A2 (fr) 1993-07-01 1995-01-04 August Bilstein GmbH & Co. KG Piston pour un amortisseur de vibrations hydraulique
EP0955483A1 (fr) * 1998-05-07 1999-11-10 Delphi Technologies, Inc. Amortisseur
EP1600662A1 (fr) * 2004-05-25 2005-11-30 Hitachi, Ltd. Amortisseur hydraulique
US20050279597A1 (en) 2004-06-07 2005-12-22 Hiroyuki Yamaguchi Hydraulic shock absorber
EP1860341A2 (fr) 2006-05-24 2007-11-28 Koni B.V. Clapet de non retour pour absorbeur de choc

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1260899B (de) 1962-01-11 1968-02-08 Christian Marie Lucien Louis B Federscheibenventil, insbesondere fuer Stossdaempferkolben
US4197929A (en) * 1978-01-13 1980-04-15 Kayaba Kogyo K.K. Device for producing damping force in hydraulic shock absorbers
DE3246866A1 (de) 1981-12-18 1983-07-14 Tokico Ltd., Kawasaki, Kanagawa Hydraulischer daempfer
GB2113355A (en) * 1981-12-18 1983-08-03 Tokico Ltd Hydraulic damper
US5316113A (en) * 1987-11-19 1994-05-31 Atsugi Motor Parts Company Ltd. Hydraulic shock absorber
EP0632212A2 (fr) 1993-07-01 1995-01-04 August Bilstein GmbH & Co. KG Piston pour un amortisseur de vibrations hydraulique
EP0955483A1 (fr) * 1998-05-07 1999-11-10 Delphi Technologies, Inc. Amortisseur
EP1600662A1 (fr) * 2004-05-25 2005-11-30 Hitachi, Ltd. Amortisseur hydraulique
US20050279597A1 (en) 2004-06-07 2005-12-22 Hiroyuki Yamaguchi Hydraulic shock absorber
EP1860341A2 (fr) 2006-05-24 2007-11-28 Koni B.V. Clapet de non retour pour absorbeur de choc

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9500251B2 (en) 2014-11-25 2016-11-22 Tenneco Automotive Operating Company Inc. Shock absorber having orifice check disc
US9845839B2 (en) 2016-02-18 2017-12-19 Tenneco Automotive Operating Company Inc. Shock absorber having check disc for orifice passage

Also Published As

Publication number Publication date
DE102012100690B4 (de) 2015-09-10
DE102012100690A1 (de) 2013-08-01
EP2807397A1 (fr) 2014-12-03

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