EP0151650A2 - Kolben-Zylinder-Einheit - Google Patents

Kolben-Zylinder-Einheit Download PDF

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Publication number
EP0151650A2
EP0151650A2 EP83111456A EP83111456A EP0151650A2 EP 0151650 A2 EP0151650 A2 EP 0151650A2 EP 83111456 A EP83111456 A EP 83111456A EP 83111456 A EP83111456 A EP 83111456A EP 0151650 A2 EP0151650 A2 EP 0151650A2
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
face
pressure medium
cylinder unit
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
EP83111456A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0151650A3 (en
EP0151650B1 (de
Inventor
Josef Büter
Heinrich Büter
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.)
Maschinenfabrik Bueter Te Haren Bondsrepubli GmbH
Original Assignee
Bueter Heinrich
Bueter J & H Maschf GmbH
Bueter Josef
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6207421&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0151650(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Bueter Heinrich, Bueter J & H Maschf GmbH, Bueter Josef filed Critical Bueter Heinrich
Priority to AT83111456T priority Critical patent/ATE37932T1/de
Publication of EP0151650A2 publication Critical patent/EP0151650A2/de
Publication of EP0151650A3 publication Critical patent/EP0151650A3/de
Application granted granted Critical
Publication of EP0151650B1 publication Critical patent/EP0151650B1/de
Expired 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
    • F15B15/1476—Special return means
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • 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
    • 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
    • F15B15/149—Fluid interconnections, e.g. fluid connectors, passages

Definitions

  • the invention relates to a double-acting piston-cylinder unit, the piston guided in the cylinder and fastened to a piston rod on its (first) end face to which a pressure medium, in particular hydraulic oil, is to be applied, which is controlled via a first connecting piece arranged on an end section of the cylinder is to be conducted into the cylinder and to be acted upon on its opposite other (second) end face with pressure medium which is located in one of a middle section of the piston rod and the inner wall of the cylinder, the second end face of the piston and a cylinder end piece formed annular chamber and is connected to a pressure medium reservoir which is connected to the annular chamber via a second connecting piece arranged at the other end section of the cylinder.
  • Such generic piston-cylinder units are usually operated hydraulically and accordingly - in accordance with the terminology customary in practice - also referred to below as a hydraulic cylinder.
  • hydraulic cylinders with so-called hydraulic accumulators, that is to say the second connecting piece has been provided, as in the known design described at the outset, but is not connected to a pressure medium connecting line, but rather to a so-called hydraulic accumulator.
  • This is a pressure described further below using the exemplary embodiment memory with a substantially closed housing, in which a membrane is arranged, on one side, which forms a closed chamber with the corresponding housing section, a pressurized gas (generally nitrogen) is arranged, while the opposite side of the membrane the remaining part of the housing having the connecting piece is connected to the connecting piece of the cylinder.
  • a pressurized gas generally nitrogen
  • the pressure medium thus compresses the gas while deforming the membrane in its chamber and builds up a corresponding pressure which, depending on the pressure conditions prevailing at the connecting piece of the hydraulic accumulator, therefore again to the outside - ie here in the annular chambers of the hydraulic cylinder - can be released.
  • the present invention has for its object to improve the piston-cylinder unit of the type described above while avoiding the aforementioned and further disadvantages in that, despite the basically unavoidable leakage losses, there is still no pressure reduction and the piston-cylinder unit therefore despite the inevitably occurring leakage losses remain operational. It should also be possible to dispense with a separate filling process for the annular chamber and the hydraulic accumulator with pressure medium under appropriate pressure. It is also an aim that, in the event of operational malfunctions, a repair or an exchange of the piston-cylinder unit or the hydraulic accumulator can be carried out by laypersons without any risk to the person concerned.
  • the solution to this problem is characterized in that between the first connecting piece and the second connecting piece the piston-cylinder unit: there is a connecting line via which pressure equalization can take place when the piston is at its first face from the pressure medium is pressurized / and that the connecting line is interrupted if the piston is not pressurized by the pressure medium on its first end face, that is to say the inflow and outflow line connected to the first connecting piece is "open", ie is without pressure and the pressure medium, So generally the hydraulic oil flows back in a known and customary manner, recognizable as a control or shut-off gear in the line leading to the first connecting piece of the piston-cylinder unit, only a simple ball valve or the like. needs to be present.
  • connection line is preferably arranged within the cylinder, and that it extends' in accordance with a preferred embodiment of the invention by the piston and a portion of the piston rod, it being arranged for the realization of the locking operation described above, in the connecting line a non-return valve.
  • the connecting line is designed as a (double) through-bore, which extends from the first end face of the piston to a peripheral section of the piston rod, which is always in contact with the annular chamber Connection is established.
  • the check valve preferably consists of a ball and a compression spring which is supported at one end on the piston rod and at its other end on the ball and this in the direction of the first end face the ball presses against a ball seat, the prestressing of the spring being able to be preferably changed, if necessary by replacing it, in order to be able to easily implement different back pressure conditions.
  • this flow path can be designed as at least one slot-shaped recess on the second ball seat, which always connects the sections of the connecting line which are adjacent to the second ball seat on both sides.
  • the drawing shows a double-acting piston-cylinder unit 1 according to the invention with a pressure medium accumulator 2 for hydraulic actuation, thus therefore a hydraulic cylinder with a hydraulic accumulator, the piston 6 of which is guided in the cylinder 3 and fastened to a piston rod 4 on its above and below with "first" Hydraulic oil is to be applied to the end face designated one end face 7, which is to be guided into the cylinder 3 in a controlled manner via a connecting piece 8 arranged on an end section of the cylinder 3.
  • the cylinder 3 essentially consists of a tube section 3 ', at the ends of which a cylinder end piece 9 or 10 is arranged.
  • the pipe section 3 ' is not permanently connected to the cylinder end piece 10 located there, in order to be able to carry out the assembly and, if necessary, disassembly of the piston rod 4 of the piston 6. Rather, the sleeve-shaped cylinder end piece 10 is provided with an external thread 14 and screwed into a corresponding internal thread, which is located at this end of the pipe section 3 '.
  • a seal 16 is arranged between the cylinder end piece 9 and the inside of the tube section 3 'of the cylinder 3 in order to achieve the required tightness net, which is a normal standard gasket ..
  • Two further seals 17 are arranged at this end of the piston-cylinder unit 1 between the piston rod 4 and the inside of the cylinder end piece 10, which is circular in cross section.
  • connection piece 18 for the hydraulic accumulator 2 which is screwed into the connection piece 18 with a connection 19 provided with a corresponding external thread.
  • the end of the piston rod 4 located at this end - like the articulation lug 13 - has a bore 21 and, as cannot be seen in the side view shown in the drawing, is provided in the center with a slot which extends from its free outer end via a Section extends in the direction of the other end of the piston rod 4, as is known per se.
  • the piston 6, which also has a seal 22 to the inner wall 23 of the piston 3, is also provided on its circumferential surface with a guide band 24 and has a configuration on its radial and external application side 7, which is referred to above and below as "first end face", which prevents that the first end face 7 can lay on the inside of the cylinder end piece 9 in full size without leaving a space 26. Rather, as can be seen from the drawing, it is always one Space 26 available so that a pressure can build up in this when pressure fluid under pressure is supplied via the connecting line (not shown in the drawing) to the first connecting piece 8 in the direction of arrow 27 in the room 26 (the pressure medium can pass through the connecting piece 8 through a bore 28 located in the cylinder 3 flows into the space 26).
  • the operator concerned opens one in the first Connection pipe 8 connecting line arranged ball valve and there is a flow of hydraulic oil in the direction of arrow 27 in the space 26, and then a force is exerted on the piston 6, which multiplies the product of the pressure built up (for example, 180 bar) corresponds to the projection surface of the first end face 7 on a plane running at right angles to the central axis 31, and this pressure causes the piston rod 4 to move in the direction of the arrow 29.
  • the area of the second end face 33 of the piston 6 is smaller than its first end face, so that in the annular chamber 32 in normal operating state when the space 26 is pressurized with pressure medium, there is a lower pressure than in the space 26.
  • this connecting line is arranged inside the cylinder 3, namely it extends through the piston 6 and a section of the piston rod 4. Both are provided with a bore 34 or 36 lying on the central axis 31, a radially extending bore 37 adjoining the axially extending bore 36, which leads to the annular chamber 32 and is connected to the latter in every piston position.
  • the bore 34 provided in the piston 6 widens at the end of the piston 6 facing the piston rod 4 and there forms a seat 38 for a ball 39 which can lie in the extension section 34 'of the bore 34, that is to say has a diameter which is smaller than the length of the extension section 34'.
  • the bore 36 also has an expansion section 36 '.
  • a prestressed compression spring 41 is arranged, which is therefore supported at one end on the shoulder 42, which is formed due to the expansion of the bore 36, and with its other end on the ball 39, so that it first of all holds in contact with ball seat 38.
  • pressure medium can also flow into the bore 34 of the piston 6 and press the ball 39 against the action of the compression spring 41 , wherein the ball 39 comes to rest on the free end of the extension section 36 '. There, however, it does not seal the extension section 36 'and thus the bore 36, but slots 43 are provided on this "second" ball seat, at which pressurized pressure medium always passes from the bore 34 - past the ball 39 - into the bore 36 can flow.
  • the piston-cylinder unit according to the invention manages with standard seals and not particularly high-quality surfaces, because the size of the leakage loss (of course within reasonable limits) in contrast to the prior art described above is completely uncritical. At the same time, however, this also results in a longer service life, since it is known that seals with low leakage losses require greater contact forces on the sealing surfaces, which in turn leads to correspondingly higher wear with a corresponding relative movement.
  • the piston-cylinder unit according to the invention therefore fulfills all of the tasks according to the requirements placed on it in an almost optimal manner, the measures taken for this purpose, namely the formation of the bores 34, 36 and the arrangement of the compression spring 41 and the ball 39 with extremely little effort are to be practiced, since the piston rod has already been clamped for machining purposes and therefore no additional alignment work is required to produce the bores.
  • the assembly of the spring and the ball is obviously very simple, and there is also the fact that these additional costs are at least partly.
  • the inner wall 23 of the cylinder 3 does not have any particularly high smoothing requirements and, furthermore, because of their standard designs, the seals that are used are noticeably cheaper than the special seals that must be provided in the comparable prior art in order to prevent leakage and associated pressure drop as small as possible.
EP83111456A 1983-08-25 1983-11-16 Kolben-Zylinder-Einheit Expired EP0151650B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83111456T ATE37932T1 (de) 1983-08-25 1983-11-16 Kolben-zylinder-einheit.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3330670 1983-08-25
DE3330670A DE3330670A1 (de) 1983-08-25 1983-08-25 Doppeltwirkende kolben-zylinder-einheit

Publications (3)

Publication Number Publication Date
EP0151650A2 true EP0151650A2 (de) 1985-08-21
EP0151650A3 EP0151650A3 (en) 1985-10-30
EP0151650B1 EP0151650B1 (de) 1988-10-12

Family

ID=6207421

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83111456A Expired EP0151650B1 (de) 1983-08-25 1983-11-16 Kolben-Zylinder-Einheit

Country Status (4)

Country Link
US (1) US4633665A (no)
EP (1) EP0151650B1 (no)
AT (1) ATE37932T1 (no)
DE (2) DE3330670A1 (no)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0478841A1 (de) * 1990-10-05 1992-04-08 Walter Hunger Hydraulischer Teleskopzylinder für die Kippbrücke von Kipperfahrzeugen
EP1619430A1 (de) 2004-07-22 2006-01-25 Bümach Engineering International B.V. Ventil
WO2014079528A1 (de) * 2012-11-22 2014-05-30 Hydac System Gmbh Turbinenventilstellvorrichtung

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4759260A (en) * 1978-05-17 1988-07-26 Lew Yon S Super reliable air-spring return air cylinder
US5974797A (en) * 1996-10-08 1999-11-02 Tokimec Inc. Hydraulic actuator package
FR2758938B1 (fr) * 1997-02-03 1999-04-23 Kuhn Sa Reglage automatique de l'allegement d'une unite de travail d'une machine : procede, dispositif et machine
AT407661B (de) * 1998-08-04 2001-05-25 Hygrama Ag Druckmittelzylinder, weichenventil und druckmittelbetätigte arbeitseinheit
EP1387090B1 (de) * 2002-08-02 2014-04-30 Bosch Rexroth AG Hydraulischer Antrieb
US8360097B2 (en) * 2008-04-22 2013-01-29 Honeywell International Inc. Valve actuator and throttle valve assembly employing the same
DE102008025480B3 (de) * 2008-05-27 2009-12-24 Robert Bosch Gmbh Steuereinrichtung und Verfahren zur Beeinflussung der Motordrehzahl sowie des Schlupfgrads einer Kupplung eines Schiffsantriebs
DE102015118839B4 (de) * 2015-11-03 2017-06-01 Tkr Spezialwerkzeuge Gmbh Hydraulikeinheit für ein mobiles Hydraulikwerkzeug
US11015624B2 (en) 2016-05-19 2021-05-25 Steven H. Marquardt Methods and devices for conserving energy in fluid power production
US10550863B1 (en) 2016-05-19 2020-02-04 Steven H. Marquardt Direct link circuit
US10914322B1 (en) 2016-05-19 2021-02-09 Steven H. Marquardt Energy saving accumulator circuit
DE202017001547U1 (de) * 2017-03-23 2018-06-26 Bümach Engineering International B.V. Doppelt wirkendes Überströmventil eines Arbeitszylinders und Master-Arbeitszylinder
US10947022B2 (en) * 2017-03-30 2021-03-16 Kimberly-Clark Worldwide, Inc. Integrated carton and shipping container design and filling manufacture process

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2194209A (en) * 1938-08-03 1940-03-19 Int Harvester Co Fluid-operated device
US3192717A (en) * 1962-06-19 1965-07-06 Keclavite Hydraulics Ltd Hydraulically operated reciprocating apparatus
GB1142172A (en) * 1966-06-09 1969-02-05 Paul Snowden Improvements in or relating to impact devices
DE6801286U (de) * 1968-10-07 1969-08-07 Waldenmaier J E H Kraftkolbenantrieb fuer armaturen
DE3233739A1 (de) * 1981-10-01 1983-04-21 Hoerbiger Ventilwerke AG, 1110 Wien Einrichtung zum selbsttaetigen rueckstellen eines stellzylinders

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3476016A (en) * 1967-10-20 1969-11-04 Cascade Corp Apparatus for producing coordinated,simultaneous actuation of multiple rams
GB1275747A (en) * 1968-06-17 1972-05-24 Bomford & Evershed Ltd Improvements relating to hydraulic ram safety devices
DE1800424B1 (de) * 1968-10-01 1970-02-26 Waldenmaier J E H Kraftkolbenantrieb fuer Armaturen
DE2405105C3 (de) * 1974-02-02 1982-01-21 Carl Schenck Ag, 6100 Darmstadt Verfahren und Vorrichtung zum Absperren von Druckspeichern
US4226167A (en) * 1978-05-17 1980-10-07 Lew Yon S Air-spring return air cylinder
BE878647A (nl) * 1979-09-07 1979-12-31 Christ Van De Keybus P V B A Inrichting voor het besturen van een orgaan onder invloed van een fluidium met wisselende druk
FR2509652A1 (fr) * 1981-07-17 1983-01-21 Montabert Ets Perfectionnement au systeme d'etancheite entre le milieu hydraulique et le milieu exterieur d'un appareil a percussions
FR2538468A1 (fr) * 1982-12-22 1984-06-29 Petroles Cie Francaise Verin-amortisseur hydraulique notamment pour equipement sous-marin

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2194209A (en) * 1938-08-03 1940-03-19 Int Harvester Co Fluid-operated device
US3192717A (en) * 1962-06-19 1965-07-06 Keclavite Hydraulics Ltd Hydraulically operated reciprocating apparatus
GB1142172A (en) * 1966-06-09 1969-02-05 Paul Snowden Improvements in or relating to impact devices
DE6801286U (de) * 1968-10-07 1969-08-07 Waldenmaier J E H Kraftkolbenantrieb fuer armaturen
DE3233739A1 (de) * 1981-10-01 1983-04-21 Hoerbiger Ventilwerke AG, 1110 Wien Einrichtung zum selbsttaetigen rueckstellen eines stellzylinders

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0478841A1 (de) * 1990-10-05 1992-04-08 Walter Hunger Hydraulischer Teleskopzylinder für die Kippbrücke von Kipperfahrzeugen
EP1619430A1 (de) 2004-07-22 2006-01-25 Bümach Engineering International B.V. Ventil
WO2014079528A1 (de) * 2012-11-22 2014-05-30 Hydac System Gmbh Turbinenventilstellvorrichtung
US10066645B2 (en) 2012-11-22 2018-09-04 Hydac System Gmbh Turbine valve actuator

Also Published As

Publication number Publication date
EP0151650A3 (en) 1985-10-30
ATE37932T1 (de) 1988-10-15
EP0151650B1 (de) 1988-10-12
DE3330670A1 (de) 1985-03-14
US4633665A (en) 1987-01-06
DE3378224D1 (en) 1988-11-17

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