WO2016134898A1 - Ensemble cylindre-tige de piston à tube intermédiaire - Google Patents

Ensemble cylindre-tige de piston à tube intermédiaire Download PDF

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Publication number
WO2016134898A1
WO2016134898A1 PCT/EP2016/051477 EP2016051477W WO2016134898A1 WO 2016134898 A1 WO2016134898 A1 WO 2016134898A1 EP 2016051477 W EP2016051477 W EP 2016051477W WO 2016134898 A1 WO2016134898 A1 WO 2016134898A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston rod
guide
pipe section
cylinder
cylinder unit
Prior art date
Application number
PCT/EP2016/051477
Other languages
German (de)
English (en)
Inventor
Christian Müller
Stefan Berger
Original Assignee
Zf Friedrichshafen 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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2016134898A1 publication Critical patent/WO2016134898A1/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
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/185—Bitubular units

Definitions

  • the invention relates to a piston rod-cylinder unit according to the preamble of patent claim 1.
  • intermediate tubes are used, which together with a cylinder form an annular flow connection.
  • This flow connection must z.
  • the intermediate tube can also be modular, d. H. it includes a pipe section and z. B. two separate guide sections, in which said ring seals are arranged.
  • the advantage of this design is that such an intermediate tube can be made very variable in terms of its length.
  • the guide sections can be manufactured as a standard component and for the specific application then only the pipe section is adjusted.
  • the object of the present invention is to provide an intermediate tube in which a particularly short piston rod guide can be used.
  • the piston rod guide has a radial clamping surface on which the guide portion is axially supported with an annular bottom.
  • the clamping surface has the advantage that at this point a sealing function can be achieved without a separate seal. Consequently, the space for a seal can be saved.
  • the clamping surface can be used when the guide portion is fixed by an end face of the cylinder on the piston rod guide.
  • the clamping is then done with an already existing component, which also requires no change and therefore no additional space.
  • seal carrier pipe section rests on the inside of the pipe section. This design has the advantage that the seal tends to be biased by the pressure effect of the working medium on the intermediate tube.
  • the seal carrier pipe section can bear against the pipe section on the outside. This design offers the advantage that the pipe section is particularly easily secured in its axial position.
  • the pipe section is designed with a seal holder.
  • the guide section can then be designed as a very simple angle ring.
  • the intermediate tube is supported at least indirectly on a base valve body of the cylinder.
  • a support ring is attached in the bottom valve body, on which the intermediate tube is supported.
  • Fig. 1 section through a piston rod-cylinder unit
  • FIG. 1 shows a piston rod-cylinder unit 1 in the design of an adjustable vibration damper.
  • a piston rod 5 is guided axially movable together with a piston 7.
  • the piston 7 divides the cylinder 3 in a piston rod side 9 and a piston rod remote working space 1 1, both of which are completely filled with a damping medium.
  • the end of the cylinder 3 is bounded by a piston rod guide 13, which has a bearing 15 for the piston rod.
  • a bottom valve body 17 is arranged, which has at least one check valve 19 for the flow of damping medium from a compensation chamber 21.
  • An outer container tube 23 encloses the piston rod guide 13, the cylinder 3 and the bottom valve body 17 and forms the compensation chamber 21, which is partially filled with damping medium.
  • an intermediate tube 25 is arranged, that forms a flow connection 27 to an adjustable damping valve device 29 with the outer wall of the cylinder 3.
  • a connection opening 31 connects the piston rod-shaped working space 9 with the flow connection 27, in which the same pressure prevails, as in the piston rod side working space 9.
  • FIG. 1 shows that the intermediate tube 25 has a modular construction. It comprises a guide section 33 and a pipe section 35, wherein the guide section 33 is at least indirectly sealed to the piston rod guide 13 centered to the piston rod guide.
  • the piston rod guide 13 has a radial clamping surface 37, on which the guide portion 33 is axially supported by an annular bottom 39.
  • the sealing function is achieved by the simple contact of the bottom 39 with the clamping surface 37. In principle, different types of prestressing of the soil at the clamping surface would be possible.
  • the guide section 37 is fixed to the piston rod guide 13 by an end face 41 of the cylinder 3.
  • the cylinder 3 in turn is biased in a tensioning chain between a bottom 43 of the outer container tube 23, the bottom valve body 17 and the piston rod guide 13 and a roll 45.
  • the intermediate tube 25 is supported at the end at least indirectly on the bottom valve body 17 of the cylinder 3.
  • a support ring 47 is attached to the bottom valve body 17, on which the intermediate tube 25 is supported. This bias is the closure of the container tube, z. B. by means of the roll 45 on an outer side of the cover 49 of the piston rod guide 13 is generated.
  • a seal carrier pipe section 51 as part of the guide section 33 is in axial overlap with the pipe section 35.
  • the pipe section 35 can move axially within limits to the guide section 33.
  • the seal carrier pipe section 51 is in this embodiment on the outside of the pipe section 35 and has a circumferential seal receptacle in the shape of a bead 53 for receiving a known ring seal 55. Because of the outside arrangement of the seal carrier pipe section 51, a pipe section 35 used with a relatively small diameter be, whereby a weight advantage can be achieved.
  • an identical guide portion 33 can be arranged in mirror image, according to the construction principle of a simple cap, which is placed on the pipe section 35.
  • Figures 2 and 3 show variants in which the seal carrier pipe section 51 rests on the inside of the pipe section 35. This design is useful if the flow connection 27 is to allow large volume flows.
  • the ring seal 55 is arranged in the seal carrier pipe section 51, comparable to FIG. 1.
  • the pipe section 35 may be performed with the bead 53.
  • the guide portion 33 may also be formed by a simple angle ring.
  • FIG. 4 shows a construction of the intermediate tube 25, in which the tube section 35 has an annular bottom 57 at its end which forms the guide section 33.
  • a guide section according to FIGS. 1 to 3 is then optionally used, wherein in the case of FIG. 3, the tubular body 35 has to receive the annular seal 55.
  • FIG. 5 is based on the design principle according to FIG. 2.
  • the guide section 33 is formed instead of a sheet-metal bent part by a metal-cutting or forged component with different wall thicknesses.
  • the guide section 33 has on the inside a stepped opening 59 for receiving the cylinder 3.
  • the cylinder 3 is supported with its end face 41, which in turn biases the guide section 33 onto the clamping surface 37.
  • the bottom 39 of the guide section 33 has the wall thickness Si up to the step opening 59.
  • the sum of the wall thickness S 2 in the region of the step opening 59 and the wall thickness S 3 of the cylinder 3 is slightly smaller than the wall thickness S-
  • the clamping surface 37 and the bottom 39 form a second sealing portion 67th

Landscapes

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

Abstract

L'invention concerne un ensemble cylindre-tige de piston (1) comprenant un cylindre (3) dans lequel une tige de piston (5) est montée au moyen d'un guide de tige de piston (13) de manière à coulisser axialement, un tube intermédiaire (25) étant disposé côté extérieur par rapport au cylindre (3), de sorte à se centrer au moins indirectement au niveau du guide de tige de piston (13), le tube intermédiaire (25) étant conçu en plusieurs parties et comprenant une partie guide (33) et une partie tube (35), la partie guide (33) étant rendue étanche vis-à-vis du guide de tige de piston (13). Ledit ensemble cylindre-tige de piston se caractérise en ce que le guide de tige de piston (13) présente une surface de serrage (37) radiale sur laquelle la partie guide (33) s'appuie axialement par un fond (39) annulaire.
PCT/EP2016/051477 2015-02-27 2016-01-26 Ensemble cylindre-tige de piston à tube intermédiaire WO2016134898A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015203522.0 2015-02-27
DE102015203522.0A DE102015203522A1 (de) 2015-02-27 2015-02-27 Kolbenstangen-Zylinderaggregat mit einem Zwischenrohr

Publications (1)

Publication Number Publication Date
WO2016134898A1 true WO2016134898A1 (fr) 2016-09-01

Family

ID=55272449

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/051477 WO2016134898A1 (fr) 2015-02-27 2016-01-26 Ensemble cylindre-tige de piston à tube intermédiaire

Country Status (2)

Country Link
DE (1) DE102015203522A1 (fr)
WO (1) WO2016134898A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107559370A (zh) * 2017-09-28 2018-01-09 浙江路得坦摩汽车部件股份有限公司 一种单向循环油路阀系

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017220344A1 (de) * 2017-11-15 2019-05-16 Volkswagen Aktiengesellschaft Dämpfer für ein Fahrzeug
DE102020210540A1 (de) 2020-08-19 2022-02-24 Thyssenkrupp Ag Schwingungsdämpfer und ein Mittelrohr für einen Schwingungsdämpfer
DE102022208321A1 (de) 2022-08-10 2024-02-15 Thyssenkrupp Ag Schwingungsdämpfer für ein Fahrzeug

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2108881A (en) * 1937-03-15 1938-02-22 Houde Eng Corp Hydraulic shock absorber
US2500708A (en) * 1946-08-26 1950-03-14 Gen Motors Corp Shock absorber
FR1450262A (fr) * 1964-10-20 1966-05-06 Armstrong Patents Co Ltd Perfectionnements aux amortisseurs télescopiques hydrauliques
DE102005053394A1 (de) * 2004-11-11 2006-05-18 Zf Friedrichshafen Ag Schwingungsdämpfer mit verstellbarer Dämpfkraft

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3732978A1 (de) * 1987-09-30 1989-04-13 Fichtel & Sachs Ag Vorrichtung zur beruhigung von verschaeumtem daempfermedium in stossdaempfern
DE9108291U1 (de) 1991-07-05 1991-10-02 Fichtel & Sachs Ag, 8720 Schweinfurt Zwischenrohr für einen Schwingungsdämpfer mit verstellbarer Dämpfung
JPH1096440A (ja) * 1996-09-20 1998-04-14 Kayaba Ind Co Ltd 積載量感応型ショックアブソーバ
JPH10278529A (ja) * 1997-04-08 1998-10-20 Unisia Jecs Corp 車両懸架装置
US7926632B2 (en) * 2007-04-16 2011-04-19 Tenneco Automotive Operating Company Inc. Shock absorber having a continuously variable valve with base line valving
JP4898613B2 (ja) * 2007-09-18 2012-03-21 カヤバ工業株式会社 緩衝器
DE102013003841B4 (de) * 2012-12-21 2016-11-24 Fludicon Gmbh Schwingungsdämpfer

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2108881A (en) * 1937-03-15 1938-02-22 Houde Eng Corp Hydraulic shock absorber
US2500708A (en) * 1946-08-26 1950-03-14 Gen Motors Corp Shock absorber
FR1450262A (fr) * 1964-10-20 1966-05-06 Armstrong Patents Co Ltd Perfectionnements aux amortisseurs télescopiques hydrauliques
DE102005053394A1 (de) * 2004-11-11 2006-05-18 Zf Friedrichshafen Ag Schwingungsdämpfer mit verstellbarer Dämpfkraft

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107559370A (zh) * 2017-09-28 2018-01-09 浙江路得坦摩汽车部件股份有限公司 一种单向循环油路阀系

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