EP0556588A2 - Vérin tirant - Google Patents

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Publication number
EP0556588A2
EP0556588A2 EP93100982A EP93100982A EP0556588A2 EP 0556588 A2 EP0556588 A2 EP 0556588A2 EP 93100982 A EP93100982 A EP 93100982A EP 93100982 A EP93100982 A EP 93100982A EP 0556588 A2 EP0556588 A2 EP 0556588A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
space
pull
piston
cylinder 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
EP93100982A
Other languages
German (de)
English (en)
Other versions
EP0556588B1 (fr
EP0556588A3 (en
Inventor
Josef 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.)
Buemach Engineering International BV
Original Assignee
HYDRAULIK TECHNIEK
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 HYDRAULIK TECHNIEK filed Critical HYDRAULIK TECHNIEK
Publication of EP0556588A2 publication Critical patent/EP0556588A2/fr
Publication of EP0556588A3 publication Critical patent/EP0556588A3/de
Application granted granted Critical
Publication of EP0556588B1 publication Critical patent/EP0556588B1/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
    • F15B15/1433—End caps
    • 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
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding

Definitions

  • the invention relates to a pressure-operated pull cylinder according to the preamble of claim 1.
  • a force exerted by a fluid moves a plunger in one direction, for example by introducing pressure oil on a ring piston side into a cylinder working space in the region of the piston rod and the plunger from a stroke end position in the region of the cylinder head towards the region of a cylinder base is moved into a starting position, from which the return stroke can then take place by means of an external force.
  • the plunger is displaced along an inner cylinder wall, a piston seal separating the cylinder head space containing fluid from an associated cylinder bottom space connected to the environment.
  • the piston chamber is provided with an air exchange bore in the region of the cylinder bottom enables repeated air exchange with the environment per piston stroke. Under correspondingly rough operating conditions, this can lead to accelerated corrosion in the area of the cylinder working space and to corresponding wear on the piston seals, so that the functionality of such pull cylinders is adversely affected.
  • the invention has for its object to improve a pressure-actuated pull cylinder of the type mentioned in such a way that greater reliability and long-term durability can be achieved with simple means.
  • the traction cylinder is improved in terms of operational safety with advantageously little design effort in that, with a gas exchange lock integrated in the air exchange bore, on the one hand an unimpeded piston movement and on the other hand a sufficiently tight closure of the piston chamber in the region of the cylinder base to the outside is possible, the Pull cylinder in the initial position of the piston in front of the cylinder base has a residual cylinder space with a defined compressed gas volume, the gas composition of which, even when the piston stroke is repeated, ensures reliable corrosion protection in the region of the cylinder inner wall even under rough operating conditions.
  • the resiliently adjustable gas exchange lock designed as a poppet valve, it can be achieved that the amount of gas in the remaining cylinder space remains constant even with changing gas density according to the presetting of the valve, the pre-pressure in the remaining cylinder space being dimensioned when the piston rests on the cylinder base in such a way that a state of equilibrium avoids unwanted piston movement.
  • Pressure oil components introduced into the piston chamber in front of the cylinder base via a piston seal from the area of the ring piston side can bring about an advantageous improvement in the lubrication of the cylinder inner wall and increase functional reliability, with oil entering the remaining cylinder chamber, if necessary, being able to be expressed in larger quantities via the gas exchange lock.
  • a pull cylinder designated as a whole as 1 and designed as a single-acting hydraulic cylinder, is shown in the region of a cylinder base 2, an axial section illustrating both the parts in an air exchange bore 3 and the individual parts in a cylinder 4.
  • a piston 6 located on a piston rod 5 and designed as a plunger piston via a fluid located on an annular piston side 7, e.g. Pressure oil (not shown), shifted into the illustrated starting position such that an attachment member 9 fixed on an end face 8 of the piston 6 bears against an inner bottom side 10 of the cylinder base 2 and thereby forms a residual cylinder space 11 of a cylinder space 12 surrounded by the cylinder 4.
  • the air exchange bore 3 located in the cylinder base 2 is designed as a stepped through bore into which an adjustable gas exchange lock, designated overall by 13, is introduced.
  • the gas exchange lock 13 is provided as a seat valve that can be pretensioned with a spring element 14 and adjoins a sealing element 15 on a corresponding counter surface 16 of the air exchange bore 3, which acts as a shut-off valve and only forms a passage in one direction out of the residual cylinder space 11 when the counter pressure of the spring element 14 is overcome.
  • a spherical sealing element 15 is provided in each case, which may optionally also be conical (FIG. 3) or plate-shaped (not shown), so that under the effect of as one Compression spring provided spring element 14 in the area of the respective counter surface 16 of the sealing element, a leakage current-free closure of the air exchange bore 3 is reached when the pressure of the spring element 14 is greater than the internal pressure in the area of the residual cylinder space 11.
  • the sealing element 15 and / or the counter surface 16 can advantageously be formed from plastic or the like. Elastic material, so that its shape-elastic behavior forms a reliably sealed barrier.
  • the spring element 14 according to FIG. 1 is supported on the side opposite the sealing element 15 against a filter body 18 which is pressed so deeply into the air exchange bore 3 under appropriate radial prestressing that it acts as a counterpart to the spring element 14, the blocking effect in the area of Sealing surface 16 causing bias.
  • the filter body 18 simultaneously forms additional protection against moisture and dust particles in the environment.
  • the spring element 14 'formed by a cylindrical elastomer body is pressed against the sealing element 15 with an insert body 19 inserted into the air exchange bore 3, so that the necessary pretension can be generated.
  • the insert body 19 is in an arrangement with the spring element designed as a compression spring 14 combined, wherein the assignment of the filter body 18 can also be provided (not shown).
  • the air exchange bore 3 can be provided as a bore opening perpendicularly to the cylinder axis 20 in the region of the wall of the cylinder 4 into the residual cylinder space 11, so that the design effort is reduced if necessary and the installation conditions for the pull cylinder 1 are restricted Can be taken into account.
  • an effective gas exchange barrier can also be formed in that the air exchange bore 3 is designed as an angular channel emerging laterally from the cylinder base 2 and thus improved accessibility is achieved.
  • the extension member 9 projecting into the remaining cylinder space 11 is provided as a screw pin 21, which essentially determines the volume of the remaining cylinder space 11 via an axially variable projection length, with a lock nut 22, so that, with little effort, a distance between the Face 8 of the piston 6 and the bottom 10 certain pre-setting of the volume of the remaining cylinder space 11 is possible.
  • the pull cylinder 1 is completed during assembly with the piston 6 by moving it from the area of the cylinder head (not shown) towards the area of the cylinder base 2 through the cylinder working space 12 in an arrow direction 23, an annular piston seal 24 being gas-tight on the inner wall of the cylinder 4 abuts.
  • the gas volume located in front of the end face 8 of the piston 6 is compressed so far in its density that the gas pressure generated reaches a value which is greater than the counterpressure of the prestressed spring element 14, 14 'on the sealing element 15, 15'.
  • the sealing element 15 is briefly displaced against the spring element 14, a certain amount of gas is emitted to the environment via the air exchange bore 3, and then the sealing element 15, 15 'is pressed back into the bearing position on the sealing surface 16.
  • the gas exchange lock 13 closes, as described above, a pre-pressure acting as internal pressure being formed in the remaining cylinder space 11, which is in a state of equilibrium with the pressure force of the spring element 14 and one Opposing force of the piston 6 is located, so that an unwanted piston movement is safely avoided.
  • the admission pressure in the residual cylinder space 11 is approximately 0.1 to 0.3 bar, the initial volume of the residual cylinder space 11 being 5 to 10% of the fluid-filled cylinder working space 12 in the area of the annular piston side 7.
  • the reliability and long-term stability of the support of the piston 6 in the area of the piston ring seals 24 can be improved by introducing small amounts of lubricant during assembly in the inner area of the wall of the cylinder 4, which also enable long-term lubrication, since premature aging due to external influences is safely avoided.
  • an inert inert gas for example nitrogen, can also be filled in, so that a further improved corrosion protection is achieved in the remaining cylinder chamber 11 or the cylinder work chamber 12.
  • the hydraulic cylinder 1 'forming a plunger has a plunger 6' which is designed without piston rings on its circumference and can advantageously be used for piston pumps, hydraulic lifting devices and the like.
  • the air exchange bore 3 ' is provided in the region of a cylinder head 30, which has on its end face 31 facing the cylinder working space 12' an annular projection 32 which projects beyond it and is coaxial with the cylinder axis 20 and forms the attachment member.
  • the molding attachment can also be provided directly on the piston surface 7 ′ and correspondingly brought to bear on the end face 31.
  • the outer diameter of the ring-shaped projection 32 is dimensioned such that when the plunger 6 'is in contact with the face (shown with a dash-dot line) on the cylinder head 30, the remaining cylinder space 11' is formed between the piston side 7 'and the end face 31 of the cylinder head 30, which has a volume of about 5 to 15%, preferably 10%, of the volume of the cylinder working space 12 '.
  • the plunger 6' can move into the contact position on the cylinder base 2 'without pressure and then repeatedly perform a working stroke by means of a fluid entering the working space region 12' 'via a supply line 33, the one in the remaining cylinder space 11' in each case Gas volume is compressed or expanded.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Actuator (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Fluid-Damping Devices (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lock And Its Accessories (AREA)
  • Glass Compositions (AREA)
EP93100982A 1992-02-15 1993-01-22 Cylindre de travail Expired - Lifetime EP0556588B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9201972U 1992-02-15
DE9201972U DE9201972U1 (de) 1992-02-15 1992-02-15 Zugzylinder

Publications (3)

Publication Number Publication Date
EP0556588A2 true EP0556588A2 (fr) 1993-08-25
EP0556588A3 EP0556588A3 (en) 1993-09-15
EP0556588B1 EP0556588B1 (fr) 1997-03-12

Family

ID=6876190

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93100982A Expired - Lifetime EP0556588B1 (fr) 1992-02-15 1993-01-22 Cylindre de travail

Country Status (3)

Country Link
EP (1) EP0556588B1 (fr)
AT (1) ATE150139T1 (fr)
DE (2) DE9201972U1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105003484A (zh) * 2015-05-05 2015-10-28 上海大学 一种液压动力轴孔压紧器

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4413279A1 (de) * 1994-04-16 1995-10-19 Guenther Hahn Hydraulische Einrichtung
DE4419213A1 (de) * 1994-06-01 1995-12-07 Zahnradfabrik Friedrichshafen Hydraulischer Arbeitszylinder
DE202004011532U1 (de) 2004-07-22 2004-09-30 Bümach Engineering International B.V. Ventil
DE202011102288U1 (de) 2011-06-24 2011-11-30 Bümach Engineering International B.V. Gasaustauschsperre für druckmittelbetriebene Verbraucher
DE102017114164A1 (de) 2017-06-27 2018-12-27 Amazonen-Werke H. Dreyer Gmbh & Co. Kg Hydraulischer Arbeitszylinder

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3125127A1 (de) 1981-06-26 1984-08-30 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Arbeitszylinder

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3645170A (en) * 1969-08-01 1972-02-29 Theodore A Varouxis Air cylinder with self-contained pneumatic piston return
US3913328A (en) * 1974-07-10 1975-10-21 Westinghouse Air Brake Co Oil leakage recycler
JPS5536293Y2 (fr) * 1975-07-18 1980-08-26
CA1100386A (fr) * 1978-04-03 1981-05-05 Dana Corporation Purgeur automatique
DE2904805C2 (de) * 1979-02-08 1987-03-26 Schröder, Werner, 8157 Dietramszell Druckluftgetriebener Arbeitszylinder
DE2945782C2 (de) * 1979-11-13 1985-09-19 Kleindienst GmbH, 8900 Augsburg Spannvorrichtung bei einer Anordnung für die Verstellung der Hublänge eines Hubmotors
DE3214777A1 (de) * 1982-04-21 1983-10-27 Ernst 7996 Meckenbeuren Hunger Einfachwirkender pneumatischer zylinder
DE8323775U1 (de) * 1983-08-18 1988-02-11 Festo KG, 7300 Esslingen Einfachwirkender Arbeitszylinder
SE458945B (sv) * 1985-02-18 1989-05-22 Vaexjoe Protes Ab Hydraulanordning,speciellt foer benprotes

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3125127A1 (de) 1981-06-26 1984-08-30 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Arbeitszylinder

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105003484A (zh) * 2015-05-05 2015-10-28 上海大学 一种液压动力轴孔压紧器

Also Published As

Publication number Publication date
ATE150139T1 (de) 1997-03-15
DE9201972U1 (de) 1993-06-17
EP0556588B1 (fr) 1997-03-12
DE59305679D1 (de) 1997-04-17
EP0556588A3 (en) 1993-09-15

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