EP0556588B1 - Cylindre de travail - Google Patents

Cylindre de travail Download PDF

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Publication number
EP0556588B1
EP0556588B1 EP93100982A EP93100982A EP0556588B1 EP 0556588 B1 EP0556588 B1 EP 0556588B1 EP 93100982 A EP93100982 A EP 93100982A EP 93100982 A EP93100982 A EP 93100982A EP 0556588 B1 EP0556588 B1 EP 0556588B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
space
working
bore
piston
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.)
Expired - Lifetime
Application number
EP93100982A
Other languages
German (de)
English (en)
Other versions
EP0556588A2 (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
Buemach Engineering International BV
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 Buemach Engineering International BV filed Critical Buemach Engineering International BV
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 single-acting working cylinder, in particular a pressure cylinder-operated pull cylinder according to the preamble of claim 1.
  • the pressure relief valve preventing air exchange in the spring chamber has to be adjusted to a correspondingly high dynamic pressure, which in turn requires a structurally complex piston-side sealing of the spring chamber for long-term stable functionality of the working cylinder .
  • the invention has for its object to develop a single-acting cylinder, in particular pressure-actuated pull cylinder of the type specified.
  • the working cylinder is improved in such a way that advantageously unobstructed piston movement into the starting position and, on the other hand, a sufficiently tight closure of the remaining cylinder space in the area of the associated cylinder end to the outside is achieved.
  • the working cylinder In the starting position of the piston, the working cylinder has a predetermined remaining cylinder space with a defined compressed gas volume in front of the cylinder end, whereby the amount of gas in the remaining cylinder space remains constant even with changing gas density in accordance with the presetting of the gas exchange lock, and at the same time the admission pressure in the remaining cylinder space when the piston is in contact is dimensioned at the associated cylinder end in such a way that a state of equilibrium avoids an 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 annular 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 being able to be expressed in larger quantities if necessary via the gas exchange lock.
  • a pulling cylinder designated as a whole as 1 and designed as a single-acting hydraulic cylinder, is shown in the area of a cylinder base 2, an axial section illustrating both the individual 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 in such a way 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 rests with a sealing element 15 on a corresponding counter surface 16 of the air exchange bore 3, which is effective as a shut-off valve and only forms a passage in one direction out of the remaining cylinder space 11 when the counter pressure of the spring element 14 is overcome.
  • a spherical sealing element 15 is provided, which may optionally also be conical (FIG. 3) or plate-shaped (not shown), so that under the effect of the 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 achieved when the pressure of the spring element 14 is greater than the internal pressure in the area of the remaining 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 region of Sealing surface 16 causing bias.
  • the filter body 18 also 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 introduced 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 perpendicular 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 and the installation conditions for the pull cylinder 1 are correspondingly narrow 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, thus achieving improved accessibility.
  • the extension member 9 protruding 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 by the piston 6 being displaced 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 forming in the remaining cylinder space 11, which is in a weighted condition 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 ring 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.
  • a pull cylinder is created which can be used with high reliability under rough operating conditions, for example with high atmospheric humidity in the environment.
  • an inert inert gas for example nitrogen, can also be introduced, so that further improved corrosion protection is achieved in the remaining cylinder chamber 11 or in 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 on its end face 31 facing the cylinder working space 12' has a shape projection 32 which projects beyond it and is coaxial with the cylinder axis 20 and forms the attachment element.
  • the molding attachment can also be provided directly on the piston surface 7 ′ and correspondingly brought into abutment 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 '.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Actuator (AREA)
  • Fluid-Damping Devices (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Glass Compositions (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lock And Its Accessories (AREA)

Claims (12)

  1. Vérin à simple effet comprenant un piston plongeur mobile (6; 6') qui, par l'action d'un fluide sous pression, peut être déplacé d'une position de fin de course situé dans la zone d'une extrémité de cylindre à travers une chambre de travail de vérin (12; 12'; 12") en direction de l'autre extrémité de cylindre vers une position de départ, dans laquelle l'extrémité de cylindre correspondante est pourvue d'au moins une lumière d'échange d'air (3; 3') contenant un dispositif d'arrêt d'échange de gaz réglable (13) et reliant la chambre de cylindre résiduelle (11; 11') à l'environnement, caractérisé en ce que la grandeur de la chambre de cylindre résiduelle (11; 11'), la force de retenue du dispositif d'arrêt d'échange de gaz (13) et la force antagoniste du piston plongeur sans pression (6; 6') sont coordonnées entre elles de telle sorte que, dans sa position de départ, le piston (6; 6') est maintenu dans une position d'équilibre empêchant un mouvement de retour indésiré dû à la pression interne de gaz formée dans la chambre de cylindre résiduelle (11; 11').
  2. Vérin suivant la revendication 1, caractérisé en ce que la chambre de cylindre résiduelle (11; 11') présente un volume initial représentant 5 à 10% de la chambre de travail de vérin (12; 12') pouvant être remplie de fluide.
  3. Vérin suivant la revendication 1 ou 2, caractérisé en ce que la pression interne de gaz présente dans la chambre de cylindre résiduelle (11; 11') est réglée à une valeur comprise entre 0,1 et 0,3 bar.
  4. Vérin suivant l'une quelconque des revendications 1 à 3, caractérisé en ce qu'un clapet à siège sollicité par un ressort (14; 14') est prévu en tant que dispositif d'arrêt d'échange de gaz (13).
  5. Vérin suivant la revendication 4, caractérisé en ce que le clapet à siège est pourvu d'un obturateur (15; 15') en forme de bille, de cône ou de plateau reposant sur une surface opposée correspondante (16).
  6. Vérin suivant la revendication 5, caractérisé en ce que l'obturateur (15; 15') et/ou la surface opposée (16) sont en matière plastique.
  7. Vérin suivant la revendication 5, caractérisé en ce que le ressort (14) prend appui entre l'obturateur (15; 15') et un corps filtrant (18).
  8. Vérin suivant la revendication 4, caractérisé en ce que dans la lumière d'échange d'air (3; 3') est prévu un corps inséré (19) qui l'obture et qui offre appui au ressort (14; 14').
  9. Vérin suivant l'une quelconque des revendications 1 à 8, caractérisé en ce que la lumière d'échange d'air (3; 3') est conçue comme un canal angulaire partant du fond (2) du cylindre ou de la tête (30) du cylindre et débouchant latéralement.
  10. Vérin suivant l'une quelconque des revendications 1 à 8, caractérisé en ce que la lumière d'échange d'air (3; 3') est prévue sous la forme d'une lumière s'ouvrant dans la chambre résiduelle de cylindre (11; 11') perpendiculairement à l'axe de cylindre (20).
  11. Vérin suivant l'une quelconque des revendications 1 à 10, caractérisé en ce que le piston (6) est pourvu, dans la zone de sa face d'about (8), d'un élément antérieur (9) faisant saillie dans la zone de la chambre de cylindre résiduelle (11) et portant en position de départ contre le fond (2) du cylindre.
  12. Vérin suivant la revendication 11, caractérisé en ce que l'élément antérieur (9) est conçu comme une tige filetée (21) avec un écrou de blocage (22) déterminant principalement le volume de la chambre résiduelle de cylindre (11) par une longueur de saillie modifiable axialement.
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 EP0556588A2 (fr) 1993-08-25
EP0556588A3 EP0556588A3 (en) 1993-09-15
EP0556588B1 true 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 (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

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
DE29922530U1 (de) 1999-12-21 2000-04-20 Claas Industrietechnik GmbH, 33106 Paderborn Einfachwirkende Kolbenzylindereinheit
DE202004011532U1 (de) 2004-07-22 2004-09-30 Bümach Engineering International B.V. Ventil
CN105003484A (zh) * 2015-05-05 2015-10-28 上海大学 一种液压动力轴孔压紧器

Family Cites Families (10)

* 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
DE3125127A1 (de) * 1981-06-26 1984-08-30 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Arbeitszylinder
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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Also Published As

Publication number Publication date
ATE150139T1 (de) 1997-03-15
EP0556588A2 (fr) 1993-08-25
DE59305679D1 (de) 1997-04-17
DE9201972U1 (de) 1993-06-17
EP0556588A3 (en) 1993-09-15

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