WO2016151015A1 - Amortisseur de vibrations présentant une longueur raccourcie - Google Patents

Amortisseur de vibrations présentant une longueur raccourcie Download PDF

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Publication number
WO2016151015A1
WO2016151015A1 PCT/EP2016/056380 EP2016056380W WO2016151015A1 WO 2016151015 A1 WO2016151015 A1 WO 2016151015A1 EP 2016056380 W EP2016056380 W EP 2016056380W WO 2016151015 A1 WO2016151015 A1 WO 2016151015A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
damper
vibration damper
longitudinal axis
guide tube
Prior art date
Application number
PCT/EP2016/056380
Other languages
German (de)
English (en)
Inventor
Daniel ADAEV
Andreas Lehnen
Joachim Frey
Original Assignee
Thyssenkrupp Bilstein Gmbh
Thyssenkrupp Ag
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, Thyssenkrupp Ag filed Critical Thyssenkrupp Bilstein Gmbh
Publication of WO2016151015A1 publication Critical patent/WO2016151015A1/fr

Links

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
    • F16F9/3207—Constructional features
    • F16F9/3235—Constructional features of cylinders
    • F16F9/3257—Constructional features of cylinders in twin-tube type devices
    • 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
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/064—Units characterised by the location or shape of the expansion chamber
    • F16F9/065—Expansion chamber provided on the upper or lower end of a damper, separately there from or laterally on the damper
    • 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
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/066—Units characterised by the partition, baffle or like element
    • F16F9/067—Partitions of the piston type, e.g. sliding pistons

Definitions

  • the present invention relates to a vibration damper with an oil-filled damper tube, in which a damper piston is guided in a liftable manner in a longitudinal axis of the vibration damper and a first working space separates from a second working space in the damper tube.
  • the vibration damper further comprises a piston rod which is connected to the damper piston and is led out of the damper tube sealed. Also provided is a compensating space filled with a gas, which is separated from the second working space by means of a separating piston.
  • DE 43 10 341 Cl shows a vibration damper of a type of interest here, and the compensation chamber is arranged in the longitudinal axis direction below the second working space and separated by the separating piston.
  • the expansion chamber is filled with gas, and the separating piston separates the filled with oil second working space of the gas-filled compensation chamber.
  • the compensation chamber is used to compensate for the displacement of the oil in the work spaces in the damper tube when the piston rod enters the damper tube, so that the separating piston performs a movement in the longitudinal axis direction and reduces the compensation space. If the piston rod moves out of the damper tube again, the expansion chamber increases again due to a relaxation of the gas. For this, the compensation chamber must be under pressure.
  • the vibration damper further comprises a damping valve system, which is arranged as an external module laterally on the vibration damper.
  • the damping valve system consists of two in a cylindrical valve housing coaxial with each other arranged damping valves, each with a pressure-dependent valve and an electromagnetically controllable, cooperating with at least one flow, axially movable spool.
  • the damping valve system serves to control damping forces in the rebound and compression stages of the shock absorber.
  • the vibration damper Due to the adjoining in the longitudinal axis direction of the work spaces in the damper tube compensation space, the vibration damper has an increased overall length, installation situations are known which require a vibration damper as short as possible. It would therefore be desirable to form the compensation chamber outside the damper tube, such that the compensation chamber does not lead to an extension of the overall length of the vibration damper in the longitudinal axis direction.
  • Vibration damper having an external compensation space such as DE 696 03 324 T2 shows, have a cylinder body which extends parallel to the longitudinal axis of the damper tube.
  • a damping valve system which is also included in an external, for example, cylindrical module tube, as known from DE 43 10 341 Cl, for space reasons, depending on the installation situation, another external module with a compensation chamber in a parallel to the longitudinal axis aligned Extension not be arranged in addition to the damping valve system laterally on the damper tube.
  • the object of the invention is the development of a vibration damper with an improved arrangement of a compensation chamber.
  • the overall length of the vibration damper should be minimized, the space around the damper tube should remain free at least in its essential extension length.
  • the vibration damper should allow in relation to its overall length large spring travel.
  • the invention includes the technical teaching that the compensation chamber is formed in a guide tube extending along a tube longitudinal axis, wherein the separating piston in the guide tube along the tube longitudinal axis is guided hubbeweglich and wherein the tube longitudinal axis is aligned perpendicular to the longitudinal axis of the damper tube.
  • the guide tube takes on the separating piston in the same way as a separating piston, which is accommodated in the longitudinal axis direction of the damper tube movable in this.
  • the direction of movement of the separating piston takes place in the tube longitudinal axis direction of the guide tube, and the function of the "breathing" compensation chamber can be implemented in the same way as a compensation chamber, which adjoins the second working space in the longitudinal axis direction
  • the longitudinal axis of the damper tube may include a right angle, wherein in principle a longitudinal axis aligned pipe axis can already lead to the desired result of shortening the length of the vibration damper
  • the guide tube may be mounted in the lower region of the damper tube on the outside of the vibration damper, the lower portion is formed at the end of the vibration damper, which is opposite to the lead-out piston rod.
  • this has a cladding tube which at least partially encloses the damper tube to form an annular gap between the outside of the damper tube and the inside of the cladding tube, wherein the guide tube is arranged at least indirectly on the cladding tube.
  • the guide tube is arranged at least indirectly on the cladding tube.
  • the cladding tube is in particular that the arrangement of the guide tube does not have to be made directly to the damper tube, in which the damper piston is guided and must meet special accuracy requirements.
  • the vestibule is fluidly connected to the second working space and filled with oil.
  • the vibration damper is designed as a single-tube vibration damper and operates according to the so-called single-chamber operating principle.
  • the guide tube can also be arranged at least indirectly on the outside of the damper tube and communicate fluidly with the second working space on the rod side facing away from the piston rod.
  • the vibration damper regardless of the design with or without an externally arranged damping valve system with an external compensation chamber in perpendicular projecting design be executed, in particular also regardless of whether the vibration damper is designed as a single-tube vibration damper or as a two-tube vibration damper.
  • the guide tube projecting substantially at right angles from the jacket tube is designed to be closed at its free end, wherein independently of the closed design of the guide tube a flange element can be provided at the open end with which the guide tube is arranged on the outside of the jacket tube ,
  • the one-sided closed guide tube can be fastened in a simple manner on the flange, and the flange can be arranged outside holding the guide tube.
  • the flange element may have a fluid channel which is at least partially brought into coincidence with an opening made in the cladding tube. Consequently, the opening and Oil is flowed through the fluid channel when the piston rod enters and exits the damper tube.
  • the guide tube has an open receiving end opposite the free, closed end, wherein the flange element is inserted at least partially into the open receiving end, so that the guide tube encloses the flange element at least over a partial length.
  • the guide tube can consequently be pushed onto the flange element, and with particular advantage the guide tube can be connected in a form-fitting manner to the flange element by means of the receiving end in the tube longitudinal axis.
  • the positive connection between the receiving end of the guide tube and the flange element may be formed by a plastic curling a peripheral bead in a groove externally provided on the flange element groove.
  • isolated caulkings can be provided on the circumference, which also produces the positive connection between the guide tube and the flange element.
  • the plastic molding into undercuts, recesses, grooves or notches in the outer peripheral surface of the flange element is particularly advantageous, so that a mechanically high loadable connection between the guide tube and the flange element can be generated in a simple manner.
  • a welded connection between the guide tube and the flange element may be provided, wherein it is also conceivable that the guide tube is screwed with its open receiving end on the outside of the flange.
  • connection between the flange element and the outside of the cladding tube can be produced by a welded connection, and the flange element can have a contact surface which has a concave curvature and which is brought into conformity with the curvature of the outside of the cladding tube.
  • the vibration damper on the outside of the cladding tube may have an external damping valve system for adjusting the damping force of the vibration damper. It can be formed between the damper tube and the cladding tube fluid channels between the damping valve system and the annulus, so that the damping valve system fluidly communicates at least with the annulus.
  • Fig. 1 is a cross-sectional view of a vibration damper with an inventively designed compensation space
  • Fig. 2 is an enlarged view of the connection of a guide tube to a
  • Figure 1 shows in a cross-sectional view a vibration damper 1 with a damper tube 10 which extends around a longitudinal axis 12 and is filled with oil.
  • a damper piston 11 is received in the longitudinal axis 12 hubbeweglich performed so that is formed by the damper piston 11 formed in the damper tube 10, filled with oil space in a first working space A and in a second working space B.
  • the vibration damper 1 has a piston rod 13, which is connected within the damper tube 10 with the damper piston 11 and which is guided out of the damper tube 10 sealed by means of a closure package 32.
  • the possible end positions of the damper piston 11 are marked with 1 ⁇ , wherein a first end position of the damper piston 1 ⁇ is shown adjacent to the closure package 32 at fully extended piston rod 13, and a further end position of the damper piston 1 ⁇ is shown in the opposite bottom region, to the one Connector 31 of the vibration damper 1 is arranged.
  • the vibration damper 1 further has a cladding tube 18 which encloses the damper tube 10 between the outside of the damper tube 10 and the inside of the cladding tube 18 to form an annular gap 19.
  • a damping valve system 29 is mounted, which communicates fluidically with the annular space 19 and over which the damping forces in the tension and compression stage are adjustable or controllable.
  • a flange 22 is disposed, and on the flange 22, a guide tube 17 is received.
  • the free end 21 of the guide tube 17 is executed closed and the opposite receiving end 25 of the guide tube 17 is made open.
  • the guide tube 17 is pushed with the receiving end 25 on the flange 22 on the outside and arranged on this holding.
  • a separating piston 15 is guided in a liftable manner along a pipe longitudinal axis 16 of the guide tube 17 and subdivides an anteroom 20 of a compensation chamber 14.
  • the compensation chamber 14 is filled with gas and forms a buffer space for displaced oil volume during retraction and extension of the piston rod 13 in the Damper tube 10.
  • the annular gap 19 is in fluid communication with the second working space B, and in the region of the arrangement of the flange 22, an opening 24 is introduced in the cladding tube 18, which is in register with a fluid channel 23 in the flange 22.
  • a separated from the separating piston 15 vestibule 20 in the external guide tube 17 communicate with the annular gap 19 and consequently with the second working space B, so that during retraction and extension of the piston rod 13 in and out of the damper tube 10 of the separating piston 15 under compression and expansion of the gas in the compensation chamber 14 can perform its lifting movement along the pipe axis 16.
  • the tube longitudinal axis 16 is aligned so that it is perpendicular to the longitudinal axis 12, so that the separating piston 15 performs a lifting movement, which is aligned transversely to the lifting movement of the piston rod 13 with the damper piston 11.
  • the vibration damper 1 is thus adapted in an advantageous manner to a required installation situation, in which an external guide tube 17 is provided, and in which the compensation chamber 14 is arranged, so that the vibration damper 1 despite the compensation chamber 14 in its longitudinal axis 12 need not be extended.
  • the essential peripheral region of the damper tube 10 or of the jacket tube 18 remains free, since this free space is necessary for the corresponding installation situation of the vibration damper 1.
  • Figure 2 shows a detailed view of the lower end of the vibration damper 1 in the region of the connecting piece 31, with which the vibration damper 1 can be connected, for example, to an axle of a vehicle.
  • the connecting piece 31 is attached to the cladding tube 18, which surrounds the damper tube 10 to form an annular gap 19.
  • the illustration shows the damper piston in an end position 1 ⁇ , wherein the in the annular gap 19 passing end of the damper tube 10 is made open, so that the annular gap 19 communicates fluidically with the working space in the damper tube 10.
  • the flange 22 On the outside of the cladding tube 18, the flange 22 is attached by means of a weld 33, so that in addition to the retaining arrangement of the flange 22 on the outside of the cladding tube 18 and a pressure-tight connection is made so that flowing through the fluid channel 23 oil flowing through a gap between the Flange member 22 and the outside of the cladding tube 18 can escape.
  • the contact surface 28 of the flange element 22 facing the cladding tube 18 may have a curvature which is adapted to the curvature of the outside of the cladding tube 18.
  • the flange 22 For form-closing reception of the guide tube 17 on the outside of the flange 22, the flange 22 has a groove 27 into which a material region of the guide tube 17 is rolled to form a peripheral bead 26.
  • a sealing element 30 is provided, which is designed as an O-ring and is seated in a groove on the outside in the flange.
  • the particular advantage of the embodiment shown for the formation of the compensation chamber 14 outside the damper tube 10 and in particular outside the cladding tube 18 is that the tube longitudinal axis 16 extends approximately perpendicular to the longitudinal axis 12. Consequently, the vibration damper 1 can be made shorter in the longitudinal axis direction, wherein not in addition to the damping valve system 29, a further external module parallel to the damper tube 10 and the cladding tube 18 adjacent thereto must be arranged.
  • the area in which the guide tube 17 protrudes from the cladding tube 18 is made non-binding in many installation situations of a vibration damper 1 for forming a strut for a motor vehicle without the protruding design of the guide tube 17 would structurally interfere with the formation of the compensation chamber 14.
  • the structural design of the vibration damper 1 thus enables new installation situations for vibration damper 1 in motor vehicle construction, while at the same time a valve damping system 29 can be arranged externally on the damper tube 10 and the cladding tube 18 as an external module.
  • a design which is possible according to the invention results in a particularly advantageous manner, according to which the damper piston retracts in its end position Piston rod has only a very short distance to a connector at the axle-side end of the vibration damper. The remaining dead volume in the second working space, which faces the axle-side end of the vibration damper, can be minimized when the piston rod is fully retracted.

Landscapes

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

Abstract

L'invention concerne un amortisseur de vibrations (1) rempli d'huile, comprenant un tube d'amortisseur (10), dans lequel un piston d'amortisseur (11) est guidé de manière mobile en élévation dans un axe longitudinal (12) de l'amortisseur de vibrations (1) et sépare une première chambre de travail (A) d'une deuxième chambre de travail (B) dans le tube d'amortisseur (10). Ledit amortisseur de vibrations comporte par ailleurs une tige de piston (13), qui est reliée au piston d'amortisseur (11) et qui est guidée de manière étanchéifiée hors du tube d'amortisseur (10). Une chambre d'équilibrage (14) remplie d'un gaz est séparée de la deuxième chambre de travail (B) au moyen d'un piston de séparation (15). Selon l'invention, la chambre d'équilibrage (14) est réalisée dans un tube de guidage (17) s'étendant le long d'un axe longitudinal de tube (16). Le piston de séparation (15) est guidé de manière mobile en élévation dans le tube de guidage (17) le long de l'axe longitudinal de tube (16). L'axe longitudinal de tube (16) est orienté de manière perpendiculaire par rapport à l'axe longitudinal (12) du tube d'amortisseur (10).
PCT/EP2016/056380 2015-03-25 2016-03-23 Amortisseur de vibrations présentant une longueur raccourcie WO2016151015A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015104494.3A DE102015104494A1 (de) 2015-03-25 2015-03-25 Schwingungsdämpfer mit verkürzter Baulänge
DE102015104494.3 2015-03-25

Publications (1)

Publication Number Publication Date
WO2016151015A1 true WO2016151015A1 (fr) 2016-09-29

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ID=55642439

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/056380 WO2016151015A1 (fr) 2015-03-25 2016-03-23 Amortisseur de vibrations présentant une longueur raccourcie

Country Status (2)

Country Link
DE (1) DE102015104494A1 (fr)
WO (1) WO2016151015A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180094691A1 (en) * 2016-09-30 2018-04-05 Thyssenkrupp Bilstein Gmbh Vibration damper for a motor vehicle and a method for producing a press fit between a damper inner tube and at least one separating plate
CN109552604A (zh) * 2018-11-13 2019-04-02 中国直升机设计研究所 一种兼具对中功能的减摆器
USD866408S1 (en) 2017-08-28 2019-11-12 Qa1 Precision Products, Inc. Shock absorber
USD869259S1 (en) 2017-08-28 2019-12-10 Qa1 Precision Products, Inc. Valve component
USD872837S1 (en) 2017-08-28 2020-01-14 Qa1 Precision Products, Inc. Bleed needle
CN110953282A (zh) * 2019-12-26 2020-04-03 宁波鸿裕工业有限公司 新型减震器
US11085502B2 (en) 2017-08-28 2021-08-10 Qa1 Precision Products, Inc. Bleed needle for a hydraulic system
US11105390B2 (en) 2017-08-28 2021-08-31 Qa1 Precision Products, Inc. Shock absorber with dry valving
US11454292B2 (en) 2020-08-14 2022-09-27 DRiV Automotive Inc. Damper assembly

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6353806U (fr) * 1986-09-29 1988-04-11
DE4028785A1 (de) * 1990-09-11 1992-03-12 Bayerische Motoren Werke Ag Hydraulischer stossdaempfer fuer kraftfahrzeuge
DE19527849C1 (de) * 1995-07-29 1996-08-14 Fichtel & Sachs Ag Schwingungsdämpfer mit außenliegendem Dämpfventil
WO2008097183A1 (fr) * 2007-02-06 2008-08-14 öHLINS RACING AB Elément amortisseur comportant des conduites hydrauliques
DE102013009987A1 (de) * 2013-06-14 2013-12-19 Daimler Ag Schwingungsdämpfer für ein Fahrzeug

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
DE4310341C1 (de) 1993-03-31 1994-08-25 Bilstein August Gmbh Co Kg Regelbarer Schwingungsdämpfer für Kraftfahrzeuge
SE512020C2 (sv) 1995-05-18 2000-01-17 Oehlins Racing Ab Anordning vid stötdämpare
DE19755039C2 (de) * 1997-12-11 1999-10-21 Mannesmann Sachs Ag Federbein mit außenliegendem Speicher
CA2350548A1 (fr) * 1998-11-11 2000-05-18 Kenmar Company Trust Unite de commande de suspension et vanne de commande
DE10153011B4 (de) * 2001-10-26 2006-03-09 Zf Sachs Race Engineering Gmbh Schwingungsdämpfer mit einstellbarer Dämpfungskraft
FR2908486B1 (fr) * 2006-11-13 2008-12-26 Messier Dowty Sa Sa Organe telescopique a butee interne effacable
DE102009016225B4 (de) 2008-04-09 2013-05-23 Zf Friedrichshafen Ag Kolben-Zylinder-Aggregat
WO2012165332A1 (fr) * 2011-05-31 2012-12-06 本田技研工業株式会社 Véhicule à moteur à deux roues

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6353806U (fr) * 1986-09-29 1988-04-11
DE4028785A1 (de) * 1990-09-11 1992-03-12 Bayerische Motoren Werke Ag Hydraulischer stossdaempfer fuer kraftfahrzeuge
DE19527849C1 (de) * 1995-07-29 1996-08-14 Fichtel & Sachs Ag Schwingungsdämpfer mit außenliegendem Dämpfventil
WO2008097183A1 (fr) * 2007-02-06 2008-08-14 öHLINS RACING AB Elément amortisseur comportant des conduites hydrauliques
DE102013009987A1 (de) * 2013-06-14 2013-12-19 Daimler Ag Schwingungsdämpfer für ein Fahrzeug

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180094691A1 (en) * 2016-09-30 2018-04-05 Thyssenkrupp Bilstein Gmbh Vibration damper for a motor vehicle and a method for producing a press fit between a damper inner tube and at least one separating plate
US10570982B2 (en) * 2016-09-30 2020-02-25 Thyssenkrupp Bilstein Gmbh Vibration damper for a motor vehicle and a method for producing a press fit between a damper inner tube and at least one separating plate
USD866408S1 (en) 2017-08-28 2019-11-12 Qa1 Precision Products, Inc. Shock absorber
USD869259S1 (en) 2017-08-28 2019-12-10 Qa1 Precision Products, Inc. Valve component
USD872837S1 (en) 2017-08-28 2020-01-14 Qa1 Precision Products, Inc. Bleed needle
US11085502B2 (en) 2017-08-28 2021-08-10 Qa1 Precision Products, Inc. Bleed needle for a hydraulic system
US11105390B2 (en) 2017-08-28 2021-08-31 Qa1 Precision Products, Inc. Shock absorber with dry valving
CN109552604A (zh) * 2018-11-13 2019-04-02 中国直升机设计研究所 一种兼具对中功能的减摆器
CN110953282A (zh) * 2019-12-26 2020-04-03 宁波鸿裕工业有限公司 新型减震器
US11454292B2 (en) 2020-08-14 2022-09-27 DRiV Automotive Inc. Damper assembly

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