EP1715194A2 - Vérin hydraulique - Google Patents

Vérin hydraulique Download PDF

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Publication number
EP1715194A2
EP1715194A2 EP05027904A EP05027904A EP1715194A2 EP 1715194 A2 EP1715194 A2 EP 1715194A2 EP 05027904 A EP05027904 A EP 05027904A EP 05027904 A EP05027904 A EP 05027904A EP 1715194 A2 EP1715194 A2 EP 1715194A2
Authority
EP
European Patent Office
Prior art keywords
seal
cylinder
piston
rod
unit according
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.)
Granted
Application number
EP05027904A
Other languages
German (de)
English (en)
Other versions
EP1715194A3 (fr
EP1715194B1 (fr
Inventor
Marcus Dr. Fischer
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.)
Weber Hydraulik GmbH Germany
Original Assignee
Weber Hydraulik GmbH Germany
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 Weber Hydraulik GmbH Germany filed Critical Weber Hydraulik GmbH Germany
Publication of EP1715194A2 publication Critical patent/EP1715194A2/fr
Publication of EP1715194A3 publication Critical patent/EP1715194A3/fr
Application granted granted Critical
Publication of EP1715194B1 publication Critical patent/EP1715194B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B15/08—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
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F15B15/1452—Piston sealings
    • 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
    • F15B15/1461—Piston rod sealings

Definitions

  • the invention relates to a generic hydraulic cylinder unit according to the preamble of the main claim, namely a hydraulic cylinder unit having an inner shell having a cylinder tube guided on this, having an outer shell piston, with a piston rod connected to this, the rod surface on a rod-side cylinder chamber final cylinder head out is, with at least one, the piston rod-side cylinder space from the vicinity of the cylinder unit between the rod surface and the cylinder head by means of a rotationally symmetrical inner seal sealing, arranged in this rod seal and with at least one piston rod side cylinder space and formed by the cylinder bottom and the piston cylinder space between the inner shell and the outer jacket of the piston by means of a rotationally symmetrical seal outer jacket sealing, arranged in the piston piston rod tung.
  • cylinder units For various applications, particularly low-friction cylinder units are of interest. These include cylinders for suspension and steering functions, or working cylinder with high demands on the sensitivity and positioning. Increased friction has a negative effect on the effective force, that is, the useful force of the cylinder, and the theoretical pressure. This leads inter alia to the fact that the cylinder must be designed larger than theoretically necessary in order to provide a sufficient effective force available.
  • the ratio of static friction to sliding friction is also of interest because large differences between the two values can lead to undesirable vibrations or vibrations (so-called stick-slip effect).
  • the invention is therefore based on the object to design a generic hydraulic cylinder unit according to the preamble of the main claim particularly low friction.
  • the inventively provided rotationally symmetrical rod seal thus touches along a circumferentially closed line, hereinafter called inner equator, on its inner seal jacket the outer surface of the piston, and / or the likewise rotationally symmetrical piston seal also touches along a likewise circumferentially closed line, hereinafter called outer equator on its sealing outer jacket the inner shell of the cylinder tube.
  • the line can also form a certain width to form a circumferential contact surface.
  • the gap to be converged in the direction of the equator thus has, with decreasing distance from the equator, a preferably continuously smaller free cross-section for the passage of the displaced hydraulic fluid.
  • the shape of that gap-limiting region which deviates from the shape of the shell of a vertical circular cylinder, not only due to its rotational symmetry in the circumferential direction, but in addition also be curved in the axial direction. But it is also a wedge-shaped gap without additional Curvature in the axial direction possible.
  • the inventive principle uses the hydrodynamic effect of the hydraulic fluid in the convergent gap in order to minimize the frictional forces between preferably the piston seal and the cylinder tube on the one hand, the rod seal and the piston rod on the other hand.
  • the nature of the tread is not the subject of the invention, it must be designed so that they in cooperation of the running surface (inner shell of the cylinder tube or outer shell of the piston rod) with the seal for optimum friction and wear behavior provides.
  • the piston seal two -von the mantle of a vertical circular cylinder deviating-substantially wedge-shaped column, of which a gap to the cylinder chamber and the other to the rod-side cylinder chamber is open.
  • the gap in the rod seal with respect to its center plane is asymmetrical and open to the piston rod side cylinder chamber, so that at least in the extension direction of the piston rod results in the hydrodynamic, the friction-reducing Aufschwimm bin.
  • the cylinder unit designated overall by 5 in FIG. 1 has a cylinder tube 6, on the inner casing 7 of which an outer casing 9 having a piston 8 is guided.
  • a piston rod generally designated 10
  • a rod surface 11 which is extended by a cylinder head, designated as a whole by 12, out of the cylinder unit 5 upon pressurization of the cylinder space 14 formed between the piston 8 and the cylinder bottom 13 with pressurized hydraulic fluid , If the cylinder unit 5 is double-acting, so can the piston rod side annular space cylinder chamber 15, which is formed by the piston rod 10, the cylinder head 12 and the piston 8, be pressurized, whereby the piston rod 10 is retracted.
  • a total of 16 designated piston seal is provided on the piston 8. Accordingly, between the outer environment of the cylinder unit 5 and the piston rod-side cylinder chamber 15 on the cylinder head 12, a total of 17 designated rod seal provided.
  • the piston seal 16 is shown in more detail in FIG.
  • the piston 8 in this case has three circumferential, spaced-apart grooves 181, 182 on the outer casing 9 of the piston. In the two outer, outwardly open grooves 181 each have a guide ring 19 is inserted.
  • the central groove 182 is provided with the seal, generally designated 16, which consists of two parts, namely the piston seal 161 designed as a sliding and sealing element and the prestressing element 162 arranged underneath, e.g. is arranged in the form of an elastomeric ring, which provides already in the assembled state for a certain basic pressing of the sliding and sealing element 161 to the cylinder inner circumferential surface 7.
  • the coop seal 161 has a seal outer jacket 163 formed symmetrically with respect to the center plane 164 (FIG. 4) of the piston seal 161 with respect to the cylinder inner shell 7 of the cylinder tube 6, deviating from the skirt of a vertical circular cylinder of two converging gaps 165 (FIG. 4) is.
  • In the area of the median plane 164 is the highest point and at the same time the longest circumferential, closed contact line, the outer equator 166, the seal outer shell 163 with the inner shell 7 of the cylinder tube 6.
  • the converging in the direction of the outer ⁇ uquator 166 two column 165 thus have with decreasing distance from this 166 one steadily smaller free cross section for the passage of the displaced hydraulic fluid.
  • the rod seal used in the cylinder head 12, designated overall by 17, is shown in more detail in FIG.
  • a scraper 20 and in the piston rod side cylinder chamber 15 closest groove a rod guide 21 are provided in the outermost groove.
  • the rod seal 17 is likewise provided in two parts with a seal 171 embodied as a sliding and sealing element and an underlying biasing element 172 which corresponds to the element 162 already discussed according to FIG.
  • the inner sealing jacket 173 of the rod seal 171 is formed asymmetrically with respect to the center plane and has either only a wedge-shaped gap, or two columns with different gap angles and / or their length.
  • the gap is preferably open to the piston rod-side cylinder chamber 15.
  • a total of 22 designated additional seal is arranged between the rod seal 171 and the outer periphery of the cylinder unit. Between this and the rod seal 171 serving as a reservoir for the hydraulic fluid recess 23 is arranged in the cylinder head, in the hydraulic fluid, which is towed out during the extension stroke of the piston rod as a lubricating film under the rod seal 171, is collected. This quantity of oil can in turn be dragged back into the rod-side cylinder chamber 15 via the return capacity of the stand seal during the subsequent retraction stroke of the piston with its piston rod.
  • the asymmetrical shape of the seal inner wall 173 is provided, by which the return conveyance of the previously removed amount of hydraulic fluid is ultimately ensured.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sealing Devices (AREA)
  • Actuator (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP05027904.1A 2005-04-20 2005-12-20 Vérin hydraulique Expired - Lifetime EP1715194B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005018442A DE102005018442A1 (de) 2005-04-20 2005-04-20 Hydraulische Zylindereinheit

Publications (3)

Publication Number Publication Date
EP1715194A2 true EP1715194A2 (fr) 2006-10-25
EP1715194A3 EP1715194A3 (fr) 2008-05-21
EP1715194B1 EP1715194B1 (fr) 2014-06-04

Family

ID=36607376

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05027904.1A Expired - Lifetime EP1715194B1 (fr) 2005-04-20 2005-12-20 Vérin hydraulique

Country Status (3)

Country Link
US (1) US7762177B2 (fr)
EP (1) EP1715194B1 (fr)
DE (1) DE102005018442A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975402A4 (fr) * 2006-01-16 2011-04-13 Nok Corp Pompe a carburant haute pression et systeme d etancheite associe
EP2253846A3 (fr) * 2009-05-13 2013-03-06 Borsig Compressor Parts GmbH Compresseur linéaire
CN113494610A (zh) * 2021-07-08 2021-10-12 西华大学 具有阻尼支撑的浮动环结构及机械密封装置

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7607383B2 (en) * 2007-05-01 2009-10-27 Nagel Robert W System for backup rod seal for hydraulic cylinder
CN102782376B (zh) * 2010-03-04 2015-09-02 Nok株式会社 密封装置
DE102011119181A1 (de) 2011-11-23 2013-05-23 Robert Bosch Gmbh Zylinder, insbesondere Hydraulikzylinder für die Tiefsee
US10330187B2 (en) * 2014-04-11 2019-06-25 Eaton Corporation Hydraulic control unit for a limited slip differential
JP2016080115A (ja) * 2014-10-21 2016-05-16 株式会社鷺宮製作所 流体制御弁
US9702382B2 (en) * 2014-12-16 2017-07-11 World Friendship Co., Ltd. Oil hydraulic cylinder and spindle thereof
KR102743155B1 (ko) 2016-02-23 2024-12-13 이턴 인텔리전트 파워 리미티드 충전 포트를 갖는 유압 제어 유닛
FR3054277B1 (fr) * 2016-07-19 2018-07-13 Airbus Helicopters Resonateur, et aeronef muni de ce resonateur
US10272891B2 (en) * 2016-07-28 2019-04-30 Kelsey-Hayes Company Compliant torque coupler for a dual acting plunger assembly of a vehicle brake system
EP3290719B1 (fr) * 2016-08-31 2019-07-17 Goodrich Actuation Systems SAS Agencement d'étanchéité pour un actionneur
DE102017204810A1 (de) * 2017-03-22 2018-09-27 Robert Bosch Gmbh Fluidzylinder mit verbessertem Dichtungselement und Herstellungsverfahren dafür
DE102021111383A1 (de) 2021-05-03 2022-11-03 Elringklinger Ag Dichtungsanordnung
CN118591703A (zh) * 2022-02-15 2024-09-03 Nok株式会社 密封装置及支撑环

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2349170A (en) 1942-01-23 1944-05-16 Woodling George V Sealing device
US4566703A (en) 1981-04-24 1986-01-28 Microdot Incorporated Seal assembly
DE19717652A1 (de) 1996-04-27 1997-11-27 Tokico Ltd Zylindervorrichtung
US20040164496A1 (en) 2001-06-04 2004-08-26 Masatoshi Okada Sealing device

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2325000B2 (de) * 1973-05-17 1978-04-13 Busak & Luyken Gmbh & Co Dichtung fuer hydraulische kolben oder kolbenstangen
DE19526783A1 (de) * 1995-07-21 1997-01-23 Amtec Spannhydraulik Gmbh Zylinder-Kolbeneinheit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2349170A (en) 1942-01-23 1944-05-16 Woodling George V Sealing device
US4566703A (en) 1981-04-24 1986-01-28 Microdot Incorporated Seal assembly
DE19717652A1 (de) 1996-04-27 1997-11-27 Tokico Ltd Zylindervorrichtung
US20040164496A1 (en) 2001-06-04 2004-08-26 Masatoshi Okada Sealing device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975402A4 (fr) * 2006-01-16 2011-04-13 Nok Corp Pompe a carburant haute pression et systeme d etancheite associe
EP2253846A3 (fr) * 2009-05-13 2013-03-06 Borsig Compressor Parts GmbH Compresseur linéaire
CN113494610A (zh) * 2021-07-08 2021-10-12 西华大学 具有阻尼支撑的浮动环结构及机械密封装置
CN113494610B (zh) * 2021-07-08 2023-06-27 西华大学 具有阻尼支撑的浮动环结构及机械密封装置

Also Published As

Publication number Publication date
US7762177B2 (en) 2010-07-27
DE102005018442A1 (de) 2006-10-26
US20060272498A1 (en) 2006-12-07
EP1715194A3 (fr) 2008-05-21
EP1715194B1 (fr) 2014-06-04

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