WO2024110253A1 - Unité piston-cylindre ayant une butée d'extrémité - Google Patents

Unité piston-cylindre ayant une butée d'extrémité Download PDF

Info

Publication number
WO2024110253A1
WO2024110253A1 PCT/EP2023/081751 EP2023081751W WO2024110253A1 WO 2024110253 A1 WO2024110253 A1 WO 2024110253A1 EP 2023081751 W EP2023081751 W EP 2023081751W WO 2024110253 A1 WO2024110253 A1 WO 2024110253A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
end stop
ring
cylinder
support
Prior art date
Application number
PCT/EP2023/081751
Other languages
German (de)
English (en)
Inventor
Stefan Steines
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 WO2024110253A1 publication Critical patent/WO2024110253A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/226—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having elastic elements, e.g. springs, rubber pads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1428—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1457—Piston rods
    • 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
    • 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
    • F16F9/58—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder
    • F16F9/585—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder within the cylinder, in contact with working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke

Definitions

  • the invention relates to a piston-cylinder unit with an end stop according to the preamble of patent claim 1.
  • an end stop is used as an additional element for energy conversion.
  • the load limit of the end stop can be reached if an elastomer element is axially compressed as a spring element and is thereby deformed.
  • a comparatively large elastomer volume is available when an annular elastomer element is used which is chambered in an angle ring, as is the case in DE 102004 007 961 A1, for example.
  • An axially extending ring wall of the angle ring encloses the elastomer element on the outside, with a portion of the elastomer element projecting axially beyond the ring wall in the direction of a piston rod guide.
  • the object of the present invention is to improve an end stop with an elastomer element in such a way that, on the one hand, a radial support of the elastomer element and, on the other hand, the largest possible elastomer volume are available.
  • the object is achieved in that the support element is arranged axially fixed to the cylinder, wherein the support element has an inner diameter which is smaller than a raceway diameter for the piston, wherein the elastomer ring in the axially relaxed state has an outer diameter which is smaller than the inner diameter of the support element.
  • the advantage of the invention is that the support element is not attached to the piston rod side and therefore does not have a radial gap to the cylinder raceway.
  • This annular gap is largely available for the elastomer ring as an additional installation space, particularly because the support element can be made mechanically weaker if necessary.
  • the support element is formed by a support ring within the cylinder.
  • the cylinder therefore acts as part of the support ring.
  • a further advantage of the invention is that the end stop can be designed in two stages if required, in that the end stop has a support disk on the piston rod side, which comes into contact with a stop surface of the support ring depending on the stroke. When the compression path of the elastomer ring is exhausted, the stop surface engages, which additionally protects the elastomer ring from damage.
  • the end stop Due to the simple design of the end stop, it can be combined with a hydraulic end stop. In this way, the hydraulic end stop can be activated before the end stop of the elastomer ring in relation to the stroke of the piston rod.
  • the support ring is arranged within a working space of the hydraulic end stop, whereby the diameter of the working space of the hydraulic end stop is larger than the outer diameter of the elastomer ring. This achieves a strict functional separation between the function of the elastomer ring and the function of the hydraulic end stop. no frictional damping due to contact between the elastomer ring and a wall of the working chamber of the hydraulic end stop.
  • the support ring is preferably designed as an angle ring.
  • An angled end of the support ring can be used, for example, to axially fix the support ring between the cylinder and a piston rod guide. If the end of the support ring is angled radially inwards, a circular ring-shaped base is created, which protects, for example, a bearing bush as a component of the piston rod guide.
  • the supporting effect of the base can be increased, for example, if the support ring is supported axially on a piston rod guide of the piston-cylinder unit.
  • Fig. 1 Cross section through a piston-cylinder unit in the area of the end stop
  • Fig. 1 shows a cross section through a piston-cylinder unit 1 in the form of a vibration damper.
  • the invention can also be used, for example, in a gas spring or an actuating cylinder.
  • the piston-cylinder unit 1 comprises a cylinder 3, which is closed at the end by a piston rod guide 5.
  • the piston rod guide 5 comprises a sealing arrangement 7 and, if necessary, a bearing bush 9 for guiding and sealing in connection with an axially movable piston rod 11, on which a piston 13 of any design is arranged.
  • An inner wall 15 of the cylinder 3 represents a track for the piston 13.
  • the embodiment of the invention is designed as a two-tube vibration damper in which an outer container 17 encloses the cylinder 3. The piston rod is clamped to the cylinder via an angled end of the container.
  • the piston rod guide 5 could also be connected directly to the cylinder 3, as is generally known, for example, in single-tube vibration dampers.
  • An end stop 21 is arranged in a piston rod-side working chamber 19 of the cylinder 3, which comprises an elastomer ring 23 surrounding the piston rod and a piston rod-side support disk 25 for the elastomer ring 23.
  • the elastomer ring 23 essentially follows the axial working movement of the piston rod 11 synchronously. For example, there may be a slight permanent preload between the elastomer ring and the piston rod.
  • the end stop 21 comprises a support element 27 and a stop surface 29 on the piston rod guide 5 pointing in the direction of the support disk 25.
  • the elastomer ring 23 is compressed from an application point of the end stop 21, at which the elastomer ring rests against the stop surface, wherein a radial increase in diameter of the elastomer ring 23 is limited by an axial compression by the support element 29.
  • the support element 29 is arranged axially fixed to the cylinder 3 and can also be formed by the cylinder itself.
  • the support element 29 has an inner diameter Is that is smaller than a raceway diameter II for the piston 13.
  • the elastomer ring 23 In the axially relaxed state, the elastomer ring 23 has an outer diameter that is in turn smaller than an inner diameter Is of the support element. Consequently, an annular gap 31 exists between the elastomer ring 23 and the inner wall of the cylinder 3.
  • the support element 27 is formed by a support ring within the cylinder 3.
  • the support ring 27 is designed as an angle ring which is fixed axially between the piston rod guide 5 and an end face 33 of the cylinder 3.
  • the support ring 27 is also supported axially on the piston rod guide 5 of the piston-cylinder unit 1.
  • the embodiment according to Fig. 2 differs from the end stop 21 according to Fig. 1 in that the support disk 25 on the piston rod side comes to rest on a stop surface 39 of the support ring 27 depending on the stroke.
  • the support disk 25 has a slightly larger outer diameter than in Fig. 1, i.e. the outer diameter of the support disk 25 is larger than the inner diameter Is of the support ring 27.
  • the material thickness of the support disk 25 can also be slightly larger. This results in a two-stage stop, the first stage of which is determined by the spring rate of the elastomer ring 23 and the second stage of which is determined by the axial position of the stop surface 39 and, if necessary, the material properties of the support disk 25.
  • FIG. 3 shows an embodiment of the invention in which the end stop 21 is combined with a hydraulic end stop 41 based on Figure 2.
  • the hydraulic end stop 41 comprises, for example, a support disk 43 for a throttle ring 45, which, for example, together with the support disk 43 forms at least one throttle cross section 47.
  • the throttle ring 45 can also have a groove profile on its outer surface.
  • the throttle ring 45 generates a hydraulic damping force when it enters an end stop sleeve 49 by displacing damping medium within the piston rod-side working chamber 19 from a working chamber of the hydraulic end stop 51 between the throttle ring 45 and the piston rod guide 5.
  • the support ring 27 is arranged within the working space 51 of the hydraulic end stop, wherein the diameter IE of the working space 51 of the hydraulic end stop is larger than the outer diameter of the elastomer ring 23.
  • the dimensioning of the working space cross sections ensures that the end stop 21 of the elastomer ring 23 is only supported radially when the elastomer ring dips into the support ring 27 and is correspondingly axially compressed.
  • the support ring 27 is also designed as an angle ring, wherein the angled region extends in the direction of the piston rod 11 and thus creates a ring base 53 which rests against the piston rod guide 5, so that the support ring 27 is reliably fixed when maximum load occurs.

Landscapes

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

Abstract

L'invention concerne une unité piston-cylindre ayant une butée d'extrémité à l'intérieur d'un cylindre, la butée d'extrémité comprenant une bague élastomère, qui est déplacée axialement par une tige de piston avec un piston à l'intérieur du cylindre en fonction de la course et est comprimée à partir d'un point de mise en prise de la butée d'extrémité, un agrandissement radial du diamètre de la bague élastomère résultant de la compression axiale étant limité par un élément de support, caractérisé en ce que l'élément de support est axialement fixe par rapport au cylindre, l'élément de support ayant un diamètre intérieur qui est plus petit qu'un diamètre de piste pour le piston, et la bague élastomère ayant, dans l'état axialement relâché, un diamètre extérieur qui est plus petit qu'un diamètre intérieur de l'élément de support.
PCT/EP2023/081751 2022-11-25 2023-11-14 Unité piston-cylindre ayant une butée d'extrémité WO2024110253A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102022212616 2022-11-25
DE102022212616.5 2022-11-25
DE102023211273.6 2023-11-13
DE102023211273 2023-11-13

Publications (1)

Publication Number Publication Date
WO2024110253A1 true WO2024110253A1 (fr) 2024-05-30

Family

ID=88839778

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2023/081751 WO2024110253A1 (fr) 2022-11-25 2023-11-14 Unité piston-cylindre ayant une butée d'extrémité

Country Status (1)

Country Link
WO (1) WO2024110253A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR810000852Y1 (ko) * 1979-12-05 1981-07-11 타케마타 타카토시 유압 완충기
EP0059150A1 (fr) * 1981-02-23 1982-09-01 Société J.G. ALLINQUANT Dispositif de butée de fin de course d'amortisseur et appareil téléscopique analogue
US20020053495A1 (en) * 2000-11-09 2002-05-09 Daido Metal Company Ltd. Hydraulic shock-absorber
DE102004007961A1 (de) 2003-04-17 2004-10-28 Zf Sachs Ag Schwingungsdämpfer mit einem Zuganschlag
DE10323730A1 (de) 2003-05-24 2004-12-09 Daimlerchrysler Ag Lenksäulenanordnung für ein Kraftfahrzeug
US20150247549A1 (en) * 2014-02-28 2015-09-03 Hitachi Automotive Systems, Ltd. Cylinder apparatus
FR3051867A1 (fr) * 2016-05-25 2017-12-01 Peugeot Citroen Automobiles Sa Amortisseur hydraulique comportant une butee de detente et un moyen de purge de la chambre superieure
DE102018207909B3 (de) 2018-05-18 2019-09-05 Zf Friedrichshafen Ag Zuganschlag für einen Schwingungsdämpfer

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR810000852Y1 (ko) * 1979-12-05 1981-07-11 타케마타 타카토시 유압 완충기
EP0059150A1 (fr) * 1981-02-23 1982-09-01 Société J.G. ALLINQUANT Dispositif de butée de fin de course d'amortisseur et appareil téléscopique analogue
US20020053495A1 (en) * 2000-11-09 2002-05-09 Daido Metal Company Ltd. Hydraulic shock-absorber
DE102004007961A1 (de) 2003-04-17 2004-10-28 Zf Sachs Ag Schwingungsdämpfer mit einem Zuganschlag
DE10323730A1 (de) 2003-05-24 2004-12-09 Daimlerchrysler Ag Lenksäulenanordnung für ein Kraftfahrzeug
US20150247549A1 (en) * 2014-02-28 2015-09-03 Hitachi Automotive Systems, Ltd. Cylinder apparatus
FR3051867A1 (fr) * 2016-05-25 2017-12-01 Peugeot Citroen Automobiles Sa Amortisseur hydraulique comportant une butee de detente et un moyen de purge de la chambre superieure
DE102018207909B3 (de) 2018-05-18 2019-09-05 Zf Friedrichshafen Ag Zuganschlag für einen Schwingungsdämpfer

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