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WO2018171996A1 - Bague d'étanchéité fendue, en particulier pour un amortisseur de vibrations - Google Patents

Bague d'étanchéité fendue, en particulier pour un amortisseur de vibrations Download PDF

Info

Publication number
WO2018171996A1
WO2018171996A1 PCT/EP2018/053968 EP2018053968W WO2018171996A1 WO 2018171996 A1 WO2018171996 A1 WO 2018171996A1 EP 2018053968 W EP2018053968 W EP 2018053968W WO 2018171996 A1 WO2018171996 A1 WO 2018171996A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing ring
vibration damper
radial
profiling
pockets
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2018/053968
Other languages
German (de)
English (en)
Inventor
Jörg Rösseler
Aleksandar Knezevic
Benjamin THIESSEN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
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 WO2018171996A1 publication Critical patent/WO2018171996A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping

Definitions

  • the invention relates to a slotted sealing ring according to the preamble of patent claim 1.
  • a vibration damper with a hydraulic end stop which in a piston has a slotted sealing ring, referred to in this application as a throttle ring.
  • the sealing ring is biased radially in a defined stroke range of a piston rod against an inner wall of the compression space. Outside the compression region, the sealing ring widens in diameter, wherein the expansion movement is limited by a locking of the open ends in the slot area.
  • a vibration damper is described with a sealing ring on a piston, which is formed to limit an expansion of an outer sleeve, for example in the execution of an O-ring or metal ring.
  • the Hubberreich in which the sealing ring from the relaxed state in the compression region enters or exits the largest radial load in the opening direction.
  • the object of the present invention is to minimize the problem of expansion of a sealing ring.
  • the object is achieved, the profiling of radially limited pockets are formed, which exert a radial compressive force component on the piston ring over the circumference of the piston ring.
  • the radial compressive force component counteracts the radial expansion force so that the resulting radial force on the sealing ring is minimized.
  • the pockets protrude into an axial end face of the sealing ring. This is intended to achieve a slight inflow of the working medium into the pockets.
  • two levels of pockets are executed, each level projecting into the respective adjacent end face.
  • the two pocket levels are axially separated from each other, so that no working medium can pass over the sealing ring.
  • the sealing ring has an axially extending slot with two spaced end faces, wherein the resulting compressive force in the peripheral region + or - 90 ° relative to the slot has a maximum. If one applies a radial compressive force in this peripheral region, then an optimally long lever arm acts.
  • a cross-sectional reduction is performed opposite to the slot.
  • cross-section reduction is performed by as an extension of the inner diameter. If the cross-sectional reduction were at the outer diameter, then a radial force would act in the direction of the slot and tend to widen it.
  • the pockets are arranged such that they are made outside a region of reduced cross section due to the radial profiling. It is to be prevented that the radial force causes only a partial deformation of the sealing ring in the region of a thin wall of the sealing ring, but no overall closing movement of the sealing ring in the region of the slot.
  • FIG. 1 sectional view through a vibration damper
  • FIG. 1 front view of a sealing ring according to FIG. 1
  • FIGS. 1 and 2 top view of a sealing ring according to FIGS. 1 and 2
  • Fig. 4 alternative embodiment of a vibration damper
  • FIG. 1 shows a vibration damper 1 in the design of a twin-tube damper, wherein the invention is not limited to this design.
  • a piston rod 5 is guided axially movable together with a piston 7.
  • the cylinder 3 is divided by the piston 7 in a piston rod-side working space 9 and a piston rod remote working space 1 1.
  • Both working spaces 9; 1 1 are completely filled with a damping medium, usually a liquid damping medium.
  • the entire vibration damper is closed by a piston rod guide 13.
  • end stop 15 is arranged in the piston rod-side working space 9 operated by the damping medium.
  • end stop 15 can also be provided in the piston rod-distant working space 11.
  • the end stop 15 comprises a sealing ring 17 which is supported on the piston rod 5 and delimits a compression space 21 on a cylinder-side wall 19 with a reduced diameter starting from a defined stroke position of the piston rod 5.
  • the cylinder-side wall 19 is formed in this embodiment by a sleeve 23 which is fixed between the cylinder 5 and the piston rod guide 13.
  • the cylinder 5 itself could also have a radial intake, which forms the compression space 21.
  • the compression space 21 is also completely filled with damping medium.
  • the piston rod 5 has a cross-sectionally L-shaped support ring 25 which is caulked into a groove 27.
  • An annular web 29 of the support ring 25 forms a support surface 31st Axially above the support ring 25, the piston rod 5 has a second groove 33, which forms an axial positive connection with radial spring tongues 35 of the sealing ring 17.
  • the Sealing ring 17 is mounted radially elastically and can also be lifted axially within limits of the support surface 31.
  • the sealing ring 17 has at least one throttle opening 37, which is always open, regardless of the position of the sealing ring 17 in the compression space 21st
  • the size and / or the number of throttle openings 37 depend on the desired end stop force.
  • the throttle opening 37 is designed in an end face 39 facing the support ring 25.
  • the sealing ring 17 has at least one pocket 41 in a lateral surface 43 pointing in the direction of the cylinder-side wall 19 (FIGS. 2 and 3).
  • the pocket 41 protrudes into an adjacent axial end face 51 of the sealing ring 17 and is thus connected to the compression space 21 and permanently filled with damping medium.
  • a radially inwardly acting pressure force on the sealing ring 17 sets.
  • the pockets 41 are executed in two planes, each level projecting into the respective adjacent end face 51 of the sealing ring 17.
  • FIG. 3 shows, opposite to the slot 47, a cross-sectional reduction is carried out, which is carried out by an extension of the inner diameter of the sealing ring 17.
  • FIG. 3 further shows that the sealing ring 17 has a radial profiling by the spring tongues 35 at the inner diameter. However, the pockets 41 are arranged so that they are outside the area of reduced cross-section due to the profiling.
  • the sealing ring 17 At a larger stroke movement of the piston rod 5, the sealing ring 17 reaches an inlet slope 55 of the sleeve 23, which causes a smooth transition for the use of Endanschlagsl 5. Shortly before the contact of the sealing ring 17 with the inlet slope 55 is a very small annular gap between the sealing ring 17 and the inlet slope 55 before. In this small annular gap, a pressure builds up, which opposes the internal pressure of the compression space 21. The defined arrangement of the pockets 41, a radial pressure force is generated, which moves the slot 47 in the closing direction and thus supports the lock. When the sealing ring 17 is fully retracted into the compression space 21, then the cylinder-side wall 19 of the compression space 21 takes over the radial support of the sealing ring 17th
  • FIG. 4 shows a further possible embodiment of a vibration damper 1 according to the invention.
  • the piston rod 5 is mounted axially displaceably, on which a first and axially spaced a second piston 7a; 7b are arranged.
  • the arrangement of the two pistons 7a; 7b rigid, however, the invention can also be used when one or both pistons 7a; 7b are movably mounted within limits to the piston rod 5.
  • the cylinder 3 comprises a first longitudinal section 57 having a first diameter D1.
  • This length section 1 1 is closed in the end by a piston rod guide 59 in this embodiment.
  • a second length section 61 connects with a second diameter D2, wherein the second diameter D2 is smaller than the first diameter D1.
  • the two pistons 7a; 7b have a different nominal diameter.
  • the first piston 7 a is adapted to the larger diameter D 1 of the first longitudinal section 57 of the cylinder 3 and has a sealing ring 17 a, the first working space 9 in the direction of the piston rod guide 59 and a tap-side working space 12 between the first piston 7 a and a bottom 63 of the second length section 61 separates.
  • the separation is not hermetically sealed, but via two mutuallyteurströmbare Dämpfventile determined.
  • the bottom 63 is used in this embodiment, a bottom valve with a mutual flow to an annular compensation chamber 65 between the cylinder 3 and an externa ßeren container tube 67.
  • the entire cylinder 3 is completely filled with a damping medium.
  • the second piston 7b is adapted to the second diameter D2 of the second length portion 61 and thus smaller than the first piston 7a.
  • the vibration damper 1 in a defined construction position, in which the first piston 7a slides sealingly in the first longitudinal section 57 and only the damping valves in the first piston 7a generate a damping force.
  • the second piston 7b is also in the first longitudinal section 57, but is surrounded by the damping medium, since the sealing ring 17 of the second piston 7b has no sealing contact with the inner wall of the first longitudinal section 57. Consequently, the second piston 7a can not generate a significant damping force due to the open annular gap.
  • the sealing ring 17 abuts against the inner wall of the second length portion 61, so that then the second piston 9 with its damping valves within the compression space 21 a damping force generated, which adds to the damping force of the first piston 7a.
  • the second longitudinal portion 61 is formed by the cylinder 3.
  • z. B. at the bottom 63 a pointing in the direction of the second piston 7a sleeve would be fastened, which has a smaller inner diameter D2 than the first longitudinal section 57th
  • the sealing ring 17 of the second piston 7b When entering the second longitudinal section 61, the sealing ring 17 of the second piston 7b is slightly elastically reduced in diameter, so that the sealing ring 17 bears against the inner wall of the second longitudinal section 61 under radial prestressing.
  • a conical inlet slope 55 executed between the first and the second longitudinal section 1 1; 15 of the cylinder 3 also a conical inlet slope 55 executed.
  • FIG. 5 shows the second piston 7b between the first and second longitudinal sections 57; 61 of the cylinder 3.
  • annular groove 69 for receiving the sealing ring 17 is executed.
  • the sealing ring 17 has a radial clearance 41 to a groove bottom 73 of the annular groove 69. It remains even a radial clearance obtained when the sealing ring 17 is immersed in the second longitudinal portion 61.
  • a slight angular offset between the first and second pistons 7a; 7b can be compensated by the radial clearance 71, without the sealing ring 17 of the second piston 7b having to be radially biased on one side for this purpose.
  • the sealing ring 17 has a radially extending slot 47, so that the sealing ring 17 can be radially elastically deformed.
  • the diameter of the sealing ring 17 is slightly larger than the diameter D 2 of the inner wall of the second longitudinal section 61.
  • a stop 75 limits the radial expandability of the sealing ring 17, wherein the stop 75 is formed by a collar 17 separate from the cuff.
  • the sealing ring 17 has an externa ßere annular groove 77, which receives the sleeve 75.
  • the sealing ring 17 therefore also has a U-shaped cross-section.
  • the sleeve 75 is guided so deep in the annular groove 69 is that the inner wall of the cylinder 3 is basically a radial clearance.
  • the cuff 75 assumes no sealing function.
  • For a sealing web 81 is available, which is separated via the outer annular groove 77 of a retaining web 83.
  • the holding web 83 has a smaller outer diameter than the sealing web 81, so that the sleeve 75, in particular if it is formed by a metallic clamping ring, is easy to assemble, as when passing over the retaining ring a smaller radial expansion is necessary than when holding web 83 and sealing ridge 81 would have the same outer diameter.
  • FIG. 5 shows that an area of the sealing ring 17 located outside the annular groove 69, for example an outer circumferential area, is connected via the at least one radial opening 85 to an inner through opening 87 of the sealing ring 17.
  • the radial opening 85 may, for. B. by the annular groove 77, by the retaining web 83, the sealing web 81 but also be designed as a transverse channel in the end face 51 of the sealing ring 17. This ensures that within an annular space 89 between the passage opening 87 of the sealing ring 17 and the annular groove 69 existing damping medium during retraction of the second piston 7b in the second longitudinal section 61 and the associated reduction of the annular space 89 can flow out of the annular space 89 and blocked in any case is.

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, comprenant une bague d'étanchéité (17) élastique radialement. La bague d'étanchéité est exposée à une force d'élargissement radiale et est réalisée dans la zone d'une surface extérieure radiale avec un profilage sur lequel une contrainte de pression liée à un milieu de travail agit. Le profilage est formé par des compartiments (41) délimités radialement, qui exercent sur la bague d'étanchéité une composante de force de pression radiale sur la périphérie de la bague d'étanchéité.
PCT/EP2018/053968 2017-03-23 2018-02-19 Bague d'étanchéité fendue, en particulier pour un amortisseur de vibrations Ceased WO2018171996A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017204923.5A DE102017204923A1 (de) 2017-03-23 2017-03-23 Geschlitzter Dichtungsring, insbesondere für einen Schwingungsdämpfer
DE102017204923.5 2017-03-23

Publications (1)

Publication Number Publication Date
WO2018171996A1 true WO2018171996A1 (fr) 2018-09-27

Family

ID=61274236

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/053968 Ceased WO2018171996A1 (fr) 2017-03-23 2018-02-19 Bague d'étanchéité fendue, en particulier pour un amortisseur de vibrations

Country Status (2)

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DE (1) DE102017204923A1 (fr)
WO (1) WO2018171996A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117083472A (zh) * 2021-02-16 2023-11-17 Zf腓特烈斯哈芬股份公司 具有渐进的阻尼力特征线的阻尼阀装置

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019212966A1 (de) 2019-08-29 2021-03-04 Zf Friedrichshafen Ag Dämpfventileinrichtung mit progressiver Dämpfkraftkennlinie
DE102019212971A1 (de) * 2019-08-29 2021-03-04 Zf Friedrichshafen Ag Schwingungsdämpfer mit einer Dämpfventileinrichtung
DE102020209113A1 (de) * 2020-07-21 2022-01-27 Zf Friedrichshafen Ag Drosselstelle für einen Schwingungsdämpfer
WO2022175215A1 (fr) * 2021-02-16 2022-08-25 Zf Friedrichshafen Ag Ensemble soupape d'amortissement pour un amortisseur de vibrations
DE102021201425A1 (de) * 2021-02-16 2022-08-18 Zf Friedrichshafen Ag Dämpfventileinrichtung mit progressiver Dämpfkraftkennlinie
DE102021201430A1 (de) * 2021-02-16 2022-08-18 Zf Friedrichshafen Ag Dämpfventileinrichtung für einen Schwingungsdämpfer
DE102021201434B3 (de) * 2021-02-16 2022-08-18 Zf Friedrichshafen Ag Dämpfventileinrichtung für einen Schwingungsdämpfer
DE102021201438B3 (de) * 2021-02-16 2022-05-12 Zf Friedrichshafen Ag Dämpfventileinrichtung mit progressiver Dämpfkraftkennlinie
DE102021201436B4 (de) * 2021-02-16 2024-01-11 Zf Friedrichshafen Ag Dämpfventileinrichtung mit progressiver Dämpfkraftkennlinie
DE102021201426B3 (de) * 2021-02-16 2022-05-25 Zf Friedrichshafen Ag Dämpfventileinrichtung mit progressiver Dämpfkraftkennlinie
DE102021211490B4 (de) 2021-10-12 2023-10-05 Zf Friedrichshafen Ag Kraftfahrzeugschwingungsdämpfer mit einem hydraulischen Endanschlag
DE102021213457B4 (de) 2021-11-30 2023-07-20 Zf Friedrichshafen Ag Dämpfventileinrichtung
DE102021213455B4 (de) 2021-11-30 2023-07-20 Zf Friedrichshafen Ag Dämpfventileinrichtung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2166696A1 (es) * 2000-03-06 2002-04-16 Ap Amortiguadores S A Tope de rebote hidraulico para amortiguadores hidraulicos.
DE102014203598A1 (de) 2014-02-27 2015-08-27 Zf Friedrichshafen Ag Schwingungsdämpfer mit einem Endanschlag
DE102016202007A1 (de) 2016-02-10 2017-08-10 Zf Friedrichshafen Ag Kolbenzylinder-Aggregat

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2166696A1 (es) * 2000-03-06 2002-04-16 Ap Amortiguadores S A Tope de rebote hidraulico para amortiguadores hidraulicos.
DE102014203598A1 (de) 2014-02-27 2015-08-27 Zf Friedrichshafen Ag Schwingungsdämpfer mit einem Endanschlag
DE102016202007A1 (de) 2016-02-10 2017-08-10 Zf Friedrichshafen Ag Kolbenzylinder-Aggregat

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117083472A (zh) * 2021-02-16 2023-11-17 Zf腓特烈斯哈芬股份公司 具有渐进的阻尼力特征线的阻尼阀装置

Also Published As

Publication number Publication date
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