EP0222735A1 - Vérin à simple effet - Google Patents

Vérin à simple effet Download PDF

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Publication number
EP0222735A1
EP0222735A1 EP86890301A EP86890301A EP0222735A1 EP 0222735 A1 EP0222735 A1 EP 0222735A1 EP 86890301 A EP86890301 A EP 86890301A EP 86890301 A EP86890301 A EP 86890301A EP 0222735 A1 EP0222735 A1 EP 0222735A1
Authority
EP
European Patent Office
Prior art keywords
piston
space
working
pressure medium
volume
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.)
Withdrawn
Application number
EP86890301A
Other languages
German (de)
English (en)
Inventor
Herbert Frisch
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.)
ENFO Grundlagen Forschungs AG
Original Assignee
ENFO Grundlagen Forschungs 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 ENFO Grundlagen Forschungs AG filed Critical ENFO Grundlagen Forschungs AG
Publication of EP0222735A1 publication Critical patent/EP0222735A1/fr
Withdrawn legal-status Critical Current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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam

Definitions

  • the invention relates to a single-acting working cylinder, which is actuated by a pneumatic pressure medium and is provided with an automatic return device, with a cylinder tube and a piston which is guided in a sealed manner and which has on one side the working space connected to the pressure medium supply and on the other side a return space limited, which is penetrated by a piston rod connected to the piston and led out sealed from the cylinder tube, communicates with the latter via a non-return valve blocking the pressure medium supply and is connected to a return volume which is closed off from the outside.
  • a working cylinder of this type with a device for automatically resetting the piston is known from DE-OS 3 233 739.
  • Devices with single-acting cylinders are known to be less expensive than comparable arrangements that use double-acting cylinders.
  • the consumption of pressure medium is considerably lower, because in the double-acting cylinders pressure medium must also be supplied for the resetting, which is then discharged into the open air or into a storage tank.
  • the reset device for single-acting working cylinder only the working chamber of the cylinder lying on the front of the piston is pressurized by a control valve.
  • the resetting space on the cylinder side, which is penetrated by the piston rod, is in connection with an additional volume, so that the pressure medium in the resetting space and in the additional volume is compressed during the working stroke of the piston. After the pressure has been released from the working space, the compressed pressure medium in the return space causes the piston to be returned to its starting position.
  • the known reset device is therefore relatively simple.
  • a pressure reducing valve is provided between the pressure medium supply to the working space and the return space, which acts as a pressure relief valve and discharges excess pressure medium through a ventilation opening.
  • a certain pressure for the restoring movement is provided in the restoring space and in the additional restoring volume connected to it, which pressure must be smaller than the working pressure of the pressure medium to be supplied even when the piston rod is fully extended, because otherwise the piston could not perform its full stroke movement.
  • a check valve is provided in addition to the pressure reducing valve, which opens the connection to the pressure medium supply when the pressure in the return space is too low, so that pressure can flow in medium.
  • a throttle upstream or downstream of the check valve prevents the recovery space from being charged too quickly.
  • An essentially identical working cylinder is also known from DE-OS 33 29 832.
  • the piston rod which is passed through the resetting space is made relatively thick, so that it occupies a considerable part of the cylinder interior.
  • the piston area effective from the side of the recovery space is therefore relatively small. This is to avoid excessive restoring force.
  • the reset space is connected to a pressure regulator which prevents an excessively high pressure in the reset space and maintains a pressure in the latter which is below the working pressure of the pressure medium supplied.
  • the resetting volume is provided in the hollow piston rod and is greater than the volume of the resetting space surrounding the fully retracted piston rod, which is in a permanently open connection with the resetting volume via at least one channel.
  • This training is structurally advantageous because a compact, self-contained construction of the working cylinder is made possible without the need for additional facilities outside the cylinder.
  • the diameter of the piston rod is chosen to be as large as possible, in any case so large that the pressure of the pressure medium acting on the differential area between the piston and the piston rod is just sufficient to reset the piston, since the reset space is charged to the full working pressure no pressure regulator required.
  • the effective piston area acted upon by the pressure medium in the working space is at least twice as large as the effective area of the piston acted upon by the pressure medium in the annular resetting space.
  • this configuration ensures that the piston executes the full stroke movement on each working stroke and is then returned to its starting position.
  • a further simplification and improvement can be achieved according to the invention in that the resetting volume is connected to the working space of the cylinder via the piston seal, which is designed to seal only in the direction from the resetting space to the working space.
  • the reset space and the reset volume are automatically filled to the full working pressure of the pressure medium with each working stroke of the piston, while any leakage losses are compensated for at the same time.
  • the piston seal which is effective in the direction from the recovery room to the working area, prevents the recovery volume from being depressurized.
  • the piston seal can consist of a grooved ring with a sealing lip, which clears the passage from the work space to the return space, whereby the desired effect of the piston seal as a check valve is easily achieved.
  • a conventional piston seal acting in both directions can also be used.
  • the piston seal is bridged by a channel passing through the piston with a check valve arranged therein.
  • FIG. 1 shows a working cylinder according to the invention in longitudinal section
  • Fig. 2 shows a detail in an enlarged sectional view
  • Fig. 3 shows a variant in longitudinal section through the piston of the working cylinder.
  • the seal 6 there consists of a groove ring 6 'known per se with a lip 15 which bears against the inner wall of the cylinder tube 2.
  • the pressure medium coming from the working space 11 can lift the lip 15 off the inner wall of the cylinder tube 2.
  • the pressure medium supplied through the connection 4 into the working space 11 therefore not only acts on the piston 5 but also passes around the seal 6 into the resetting space 12.
  • the resetting space 12 and out of it via the channels 13 also the restoring volume 14 is filled until the same pressure prevails on both sides of the piston 5. Since the effective piston area in the If the working space 11 is larger by the cross section of the sealed piston rod 7 than on the restoring space 12 side, the piston 11 then executes the working movement.
  • the pressure medium is further compressed in the resetting space 12 and in the resetting volume 14, but the pressure rise remains limited because - as can be clearly seen from FIG. 1 - the volume of the resetting space 12 is considerably smaller than the resetting volume 14 Piston 5 can thereby carry out the full stroke movement, although at the end of the piston stroke the pressure in the working space 11 is lower than in the resetting space 12.
  • the pressure prevailing in the resetting space 12 acts on the annular surface of the piston rod 7 located outside Piston 5 and returns it to its original position.
  • Fig. 3 shows a variant in which the seal 6 of the piston 5 consists of an O-ring which seals in both directions.
  • a channel 16 is provided, which on its outlet side lying inside the piston 5 is designed as a valve seat for a ball 17 which is loaded by a spring 18.
  • the spring 18 is supported on a spring plate 19 which is fastened in the interior of the piston 5 and has through openings 20.
  • the ball 17 thus forms, together with the spring 18, a check valve which opens the passage from the working space 11 to the restoring volume 14 and thus also to the restoring space 12, but prevents flow in the opposite direction.
  • the Check valve 17, 18 thus also enables the resetting volume 14 and the resetting space 12 to be charged when the working space 11 is pressurized without the seal 6.
  • the operation in the resetting movement is the same as in the embodiment according to FIGS. 1 and 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP86890301A 1985-11-13 1986-11-05 Vérin à simple effet Withdrawn EP0222735A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT329085A AT383871B (de) 1985-11-13 1985-11-13 Einfachwirkender arbeitszylinder
AT3290/85 1985-11-13

Publications (1)

Publication Number Publication Date
EP0222735A1 true EP0222735A1 (fr) 1987-05-20

Family

ID=3548277

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86890301A Withdrawn EP0222735A1 (fr) 1985-11-13 1986-11-05 Vérin à simple effet

Country Status (2)

Country Link
EP (1) EP0222735A1 (fr)
AT (1) AT383871B (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0872646A1 (fr) * 1997-04-19 1998-10-21 Technomatik Maschinenelemente GmbH & Co.Fertigungs KG Vérin pneumatique
EP1715192A1 (fr) * 2005-04-21 2006-10-25 Krontec Maschinenbau GmbH Vérin pneumatique
DE202008015477U1 (de) * 2008-11-13 2010-04-08 Krontec Maschinenbau Gmbh Pneumatischer Wagenheber
FR3070450A1 (fr) * 2017-08-24 2019-03-01 Societe Des Usines Quiri Et Cie Dispositif de verin simple effet avec rappel par fluide compressible

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT411783B (de) * 2001-01-29 2004-05-25 Weber Walter Hydraulische kolben-zylinderanordnung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1183020A (fr) * 1957-04-10 1959-07-02 Renault Perfectionnements aux vérins pneumatiques à pression différentielle
US3232181A (en) * 1964-07-24 1966-02-01 Leland F Blatt Differential area gas cylinder
US3232180A (en) * 1963-02-11 1966-02-01 Westinghouse Freins & Signaux Percussion cylinder device with pneu-matically cushioned back-stroke
US3401604A (en) * 1967-05-17 1968-09-17 Ind Specialties Inc Differential area gas cylinder

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE758207A (fr) * 1969-11-25 1971-04-01 Weyman Henry W Ensembles de cylindre pneumatique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1183020A (fr) * 1957-04-10 1959-07-02 Renault Perfectionnements aux vérins pneumatiques à pression différentielle
US3232180A (en) * 1963-02-11 1966-02-01 Westinghouse Freins & Signaux Percussion cylinder device with pneu-matically cushioned back-stroke
US3232181A (en) * 1964-07-24 1966-02-01 Leland F Blatt Differential area gas cylinder
US3401604A (en) * 1967-05-17 1968-09-17 Ind Specialties Inc Differential area gas cylinder

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0872646A1 (fr) * 1997-04-19 1998-10-21 Technomatik Maschinenelemente GmbH & Co.Fertigungs KG Vérin pneumatique
EP1715192A1 (fr) * 2005-04-21 2006-10-25 Krontec Maschinenbau GmbH Vérin pneumatique
DE202008015477U1 (de) * 2008-11-13 2010-04-08 Krontec Maschinenbau Gmbh Pneumatischer Wagenheber
EP2186696A3 (fr) * 2008-11-13 2010-09-22 Krontec Maschinenbau GmbH Cric pneumatique
FR3070450A1 (fr) * 2017-08-24 2019-03-01 Societe Des Usines Quiri Et Cie Dispositif de verin simple effet avec rappel par fluide compressible

Also Published As

Publication number Publication date
AT383871B (de) 1987-09-10
ATA329085A (de) 1987-01-15

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Inventor name: FRISCH, HERBERT