EP1416165A2 - Vérin pneumatique - Google Patents

Vérin pneumatique Download PDF

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Publication number
EP1416165A2
EP1416165A2 EP03022448A EP03022448A EP1416165A2 EP 1416165 A2 EP1416165 A2 EP 1416165A2 EP 03022448 A EP03022448 A EP 03022448A EP 03022448 A EP03022448 A EP 03022448A EP 1416165 A2 EP1416165 A2 EP 1416165A2
Authority
EP
European Patent Office
Prior art keywords
actuator
piston
damping
drive
drive 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.)
Granted
Application number
EP03022448A
Other languages
German (de)
English (en)
Other versions
EP1416165A3 (fr
EP1416165B1 (fr
Inventor
Manfred Heise
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.)
Bar Pneumatische Steuerungssysteme GmbH
Original Assignee
Bar Pneumatische Steuerungssysteme GmbH
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 Bar Pneumatische Steuerungssysteme GmbH filed Critical Bar Pneumatische Steuerungssysteme GmbH
Publication of EP1416165A2 publication Critical patent/EP1416165A2/fr
Publication of EP1416165A3 publication Critical patent/EP1416165A3/fr
Application granted granted Critical
Publication of EP1416165B1 publication Critical patent/EP1416165B1/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
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type
    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/227—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having an auxiliary cushioning piston within the main piston or the cylinder end face

Definitions

  • the invention relates to a pneumatic actuator with a cylindrical housing, at least one in this axially mounted drive piston, which is acted upon by a working pressure between an inner stop position and an outer stop position is movable and with a rotatable output shaft, the rotation of which with the axial Movement of the drive piston is forcibly coupled and radially out of the housing exit.
  • Such well-known pneumatic actuators belong to the order of the Pressure transmission and transmission using a medium that can only be subjected to pressure a movement from the input to the output.
  • a gas (especially air) as a medium acts under pressure on a drive element designed as a piston and displaces it in a cylinder in the axial direction.
  • the output member is a rotatable shaft, whereby each axial displacement of the drive piston in the cylinder immediately causes a rotation the output shaft.
  • pneumatic actuators are presented in brochure No. S1-01-361 "Pneumatic actuators" from bar GmbH, Dattenberg, DE.
  • the rotation of the output shaft here is a swivel angle of (depending on the type) 90 °, 120 ° or 180 ° limited.
  • the output shaft has a toothing on the circumference. In this interlocking engage two racks lying opposite each other on the circumference, which in turn with oppositely moving drive pistons that add up in their effect are firmly connected.
  • This type of pneumatic actuator is also called a “double-piston rotary actuator” denotes and is used in particular for the automatic control of fittings between two defined switching positions.
  • the drive piston becomes the output shaft between its basic position (or “0 ° position”) and a second defined position (for example a "90 ° position") pivoted.
  • a flap valve arranged on the output shaft between the positions “open” and “closed” or a ball valve between two different passage positions can be switched.
  • Such a pneumatic actuator can also be used as a 3-position actuator by means of two additional pistons be carried out.
  • Single-acting actuators of the aforementioned type, whose drive pistons can only be loaded with the working medium on one side can be realized with safety springs. If there is a pressure loss in the working medium, there is one Can be reset to a defined position.
  • An inhibition of the mobility of the element to be placed can both wear or poor lubrication of this element, deposits in this element (for example, jammed particles from the media stream to be controlled), as well as in incorrect design of the element or temporarily unfavorable process parameters be justified.
  • the flawless mobility of an element to be provided can therefore are not generally considered to be given.
  • the use of the well-known actuators therefore regularly requires either "oversizing" for the (rare) malfunction or regular thorough checks of all relevant components and process parameters - or a combination of both measures - with the consequence of high plant, operating and personnel costs and, if applicable, a limited operating time due to the need for shorter maintenance intervals.
  • the invention has for its object to propose an actuator, which also inhibited movement of the element to be set a trouble-free and safe operation allows.
  • this object is achieved according to the invention solved that the axial movement of the drive piston by means of a pneumatic Damping device can be damped.
  • a damping device is according to the invention can be acted upon with a working gas such that it prevents axial movement of the Driving piston opposes a damping force.
  • the pneumatic damping has different principles Advantages on: on the one hand is in the otherwise pneumatically operated actuator mixing of the working media is not critical, on the other hand, a "gas cushion" is dependent from the volume reduction to a progressively increasing pressure so effective even at high speeds - and until reaching the End position shock-free - damping.
  • the damping device with the working air of the actuator - that is with the same pressure - applied.
  • the actuator according to the invention then requires compared to the known actuators, no additional device for supplying Working medium.
  • the drive piston and the damping device be supplied with the working medium via common connections.
  • the invention Actuator then has no other than the known actuators Connections on and can - for example using the same 5/2-way valve - without further changes to the system in exchange for a known actuator operate
  • the damping device has a Damping cylinder and in this axially movable damping piston, wherein the outer diameter of the damping piston with the outer diameter of the drive piston matches.
  • the damping device is particularly simple with the known To combine actuators. In principle, it is also conceivable to use the damping piston to be provided with a smaller outside diameter. This is particularly true in Actuators that only have a single drive piston if drive and Damping pistons should be subjected to the same working pressure. Otherwise the applied areas of both pistons would be the same and the forces would increase cancel each other out.
  • the drive piston has a rod running in the axial direction of the housing, on which the damping piston is arranged.
  • the drive and damping cylinders can be particularly constructive can be easily separated from each other when the rod is a partition in the housing pierces, so that on both sides a drive and a damping pressure chamber are trained.
  • drive and damping pistons would also be conceivable constructively united in a single piston.
  • the damping device one Such actuator according to the invention would then have to control the pressures in allow the chambers of the cylinder on either side of the piston. Because one Control, on the one hand, is very complex - and therefore costly - and, on the other hand Such an implementation is not preferred simply because of its complexity.
  • the damping piston is preferably on the rod between an inner stop position and an outer stop position axially displaceable. So the rod - and so that the drive piston - can be moved axially in a defined section without at the same time to force a movement of the damping piston. In this defined Section, the movement of the drive piston is not damped.
  • the damping piston in such an actuator according to the invention preferably consists from a sleeve penetrated by the rod and a force-fitting thereon attached piston plate.
  • the sleeve and piston plate can also be made in one piece for example, can be manufactured in a casting process.
  • the cast manufacturing is however for example, be manufactured in a casting process. However, the cast manufacturing is only first economically with comparatively large quantities.
  • an actuator according to the invention there is preferably an axially adjustable one on the rod Arranged stop element which abuts the housing when the drive piston reached its inner stop position.
  • the inner stop of the drive piston and thus the swivel angle of the output shaft is adjustable in the basic position.
  • the one described can alternatively be used Damping device on one drive piston and on the other one Be bore through which a rod axially fixed to the housing runs, a stop element on the side of the drive piston facing the output shaft having.
  • this basically known variant is because of the additional between the pierced piston and the axially movable rod therein Leaks not preferred
  • an axially adjustable stop element can be arranged on the housing, against which the rod stops when the drive piston reaches its outer stop position.
  • this can alternatively also Stop element may be arranged on the second drive piston.
  • the drive piston of an actuator according to the invention particularly preferably has one in the axial direction of the housing extending rack, which in a on the circumference of the Output shaft arranged toothing engages. So with a long service life of the Actuator according to the invention always an accurate transmission of the piston stroke guaranteed on the pivoting movement of the output shaft.
  • the drive piston can be loaded with the working pressure on both sides.
  • the movement of the The drive piston is then in both directions by alternately acting on controllable the working medium.
  • one of the switch positions of the actuator to be spring-loaded, so that the other position in the case a failure of the working pressure is controlled as a defined "safety position".
  • tension or compression springs supported on the housing can be used are used.
  • An embodiment of the actuator according to the invention is also preferred has two drive pistons movable in opposite directions in the housing, between which the output shaft is arranged.
  • the output shaft is then not radial overall, but only loaded in the circumferential direction, which in particular relieves the load on the output shaft arranged sealing elements brings with it. But also the output shaft itself does not experience any bending stress and can be designed to be correspondingly smaller.
  • the actuator of the invention is only slightly increased in construction volume the torque that can be achieved at the output shaft at the same working pressure doubled.
  • Figure 1 shows a pneumatic actuator 1 according to the invention with rack and pinion principle and a cylindrical housing 2, two axially mounted in this and self-centering, oppositely movable drive pistons 3, 4 and one radially from the housing 2 emerging rotatable output shaft 5.
  • the axial movement of the Drive piston 3, 4 can be damped by means of a pneumatic damping device 6.
  • the rotation of the output shaft 5 is connected to the drive pistons 3, 4 by two Racks 7, which are arranged axially in the housing 2 and in a, not shown, on Engage the circumference of the drive shaft arranged teeth with the axial movement the drive piston 3, 4 firmly coupled.
  • the housing 2 is composed of a drive cylinder 8 and a damping cylinder 9 each same wall thickness 10 and the same inner diameter 11 built up by a partition 12 are separated.
  • the inner sides 13 of the two drive pistons 3, 4 enclose in the drive cylinder 8 the inner drive pressure chamber 14, in which also the racks 7 and the output shaft 5 run.
  • the outer sides 15, 16 of the drive piston 3, 4 close with the inside 17 of the partition 12 and the cover 18, the outer drive pressure chambers 19, 20.
  • the inside 21 of the Damping piston 22 closes the inner damping pressure chamber with the outside 23 of the partition wall 12 24 and the outside 25 of the damping piston 22 with the cover 26, the outer damping pressure chamber 27.
  • the drive cylinder 8, the damping cylinder 9, the two covers 18, 26 and the partition 12 and the pistons and racks 7 are made of an aluminum alloy Die casting process manufactured.
  • the outer surfaces are anodized and can additionally coated with epoxy resin.
  • the output shaft 5 is made of stainless steel and for connection to the element to be placed with a 2-flat, not shown Mistake. Alternatively, square or octagonal holders are also available. at The output shaft 5 can also be made of less nickel-plated steel, in the case of smaller sizes, the covers 18, 26 can also be made of plastic.
  • a rod 28 is screwed through the partition 12 and the cover 26 is guided and covered with a cylindrical cap 29.
  • the Damping piston 22 consists of a piston plate 30 and one connected to it cylindrical sleeve 31 which is axially displaceable on the rod 28.
  • the sleeve 31 is in a guide bush 32 and guided in the partition 12, which is fixed in the cover 26 is.
  • the rod 28 has a thread (not shown) and one on it Lock nut 33 and - secured with a lock nut 34 - a sleeve-shaped stop element 35 on.
  • the cover 18 has an Allen screw 36, which is from the outside is accessible and protrudes into the outer drive pressure chamber 20 in a manner not shown.
  • the pressure chambers are each in a manner not shown with nitrile rubber seals sealed against each other and to the outside.
  • the axially displaceable against each other Components each have - also not shown - sliding surfaces made of a sliding-friendly Plastic on.
  • the actuator 1 has a nominal swivel angle of 120 ° on. Alternatively, versions with nominal swivel angles of 90 °, 180 ° and 240 ° as standard, other angles are available on request.
  • the actuator 1 brings on the element to be set at a control pressure between 2 and 10 bar (on request also 1 to 16 bar) a torque of 3 to 8000 Nm.
  • FIG. 2 shows a circuit diagram for this actuator 1 according to the invention its two switching positions, the actuator 1 has two connections A, B, which by means of a switching element 37 alternately acted upon or vented with the working medium can be.
  • the first port A connects the inner drive pressure chamber 14 and the outer damping pressure chamber 27, via port B, the outer drive pressure chambers 19, 20 and the inner damping pressure chamber 24 is applied.
  • Figure 3 shows a schematic representation of a switching cycle of this invention Actuator 1.
  • the representations a) and e) show the drive piston 3 and Damping piston 22 in the basic position (or "0 ° position") of the invention Actuator 1, illustration c) shows the other end position, here the "120 ° position”.
  • the Pressure lines are designed (in a manner not shown) so that the outer Drive pressure chamber 19 quickly, inner damping pressure chamber 24 slowly vented becomes.
  • the drive piston 3 moves from position a) to the position Representation b).
  • the drive piston 3 travels the stroke 38 undamped. Only in position b), the drive piston 3 is in contact with the damping piston 22. Both pistons travel the stroke 39 together, the pressure in the outer damping pressure chamber 27 the pressure in the inner drive pressure chamber 14 counteracts, whereby the axial movement of the drive piston 3 is braked.
  • the second drive piston (not shown here) lies in the second end position according to illustration c) 3 on the stop element, also not shown.
  • the drive piston 3 moves from representation c) into the position after representation d).
  • the drive piston 3 in turn covers the stroke 40 undamped. Only in the Position according to illustration d), the drive piston 3 is in contact with the damping piston 22. Both pistons travel the stroke 41 together again, the pressure in the inner damping pressure chamber 24 the pressure in the outer drive pressure chamber 19 counteracts, which also brakes the axial movement of the drive piston 3 here becomes.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Driven Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
EP03022448A 2002-10-23 2003-10-07 Vérin pneumatique Expired - Lifetime EP1416165B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10249509 2002-10-23
DE10249509A DE10249509A1 (de) 2002-10-23 2002-10-23 Pneumatischer Stellantrieb

Publications (3)

Publication Number Publication Date
EP1416165A2 true EP1416165A2 (fr) 2004-05-06
EP1416165A3 EP1416165A3 (fr) 2004-09-15
EP1416165B1 EP1416165B1 (fr) 2006-05-03

Family

ID=32087144

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03022448A Expired - Lifetime EP1416165B1 (fr) 2002-10-23 2003-10-07 Vérin pneumatique

Country Status (3)

Country Link
EP (1) EP1416165B1 (fr)
AT (1) ATE325276T1 (fr)
DE (2) DE10249509A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007006557A1 (fr) 2005-07-11 2007-01-18 Laeis Gmbh Agencement piston-cylindre
CN107642517A (zh) * 2017-10-29 2018-01-30 刘福珍 一种农业机械用气缸行程受阻控制装置
CN107690905A (zh) * 2017-10-29 2018-02-16 刘福珍 农业用移栽机夹苗机构气缸定位结构
CN107830010A (zh) * 2017-10-29 2018-03-23 刘福珍 一种气缸行程受阻定位装置
CN117450133A (zh) * 2023-12-13 2024-01-26 江苏亚力亚气动液压成套设备有限公司 一种缓冲液压缸

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007023303B4 (de) 2007-05-16 2015-10-01 Ingo Bruchhold System zur Endlagendämpfung von Stellantrieben sowie Stellantrieb
DE202015102250U1 (de) 2015-05-04 2016-08-05 H2R Automation GmbH Steuereinrichtung für Schwenkantriebe sowie Schwenkantrieb mit einer solchen Steuereinrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3213760A (en) * 1963-10-23 1965-10-26 Flo Tork Inc Fluid cushion
DE3434033A1 (de) * 1983-09-17 1985-04-11 Shoketsu Kinzoku Kogyo K.K., Minato Pneumatischer zylinder mit daempfungsmechanik und verfahren zum daempfen des pneumatischen zylinders
JPH10169608A (ja) * 1996-12-05 1998-06-23 Koganei Corp ロータリアクチュエータ
EP0976931A1 (fr) * 1998-07-29 2000-02-02 G.T. Componenti Srl Dispositif pour l'ajustement de la position centrale des pistons et de la position angulaire d'un pignon d'un vérin qui entraíne une soupape

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19803819B4 (de) * 1998-01-31 2004-05-13 Festo Ag & Co Fluidbetätigte Drehantriebsvorrichtung
JP3469525B2 (ja) * 2000-03-03 2003-11-25 Ｓｍｃ株式会社 クッション機構付空気圧ロータリアクチュエータ
JP3696103B2 (ja) * 2001-02-23 2005-09-14 Ｓｍｃ株式会社 クッション機構付きシリンダにおける高速加圧方法及びその機構

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3213760A (en) * 1963-10-23 1965-10-26 Flo Tork Inc Fluid cushion
DE3434033A1 (de) * 1983-09-17 1985-04-11 Shoketsu Kinzoku Kogyo K.K., Minato Pneumatischer zylinder mit daempfungsmechanik und verfahren zum daempfen des pneumatischen zylinders
JPH10169608A (ja) * 1996-12-05 1998-06-23 Koganei Corp ロータリアクチュエータ
EP0976931A1 (fr) * 1998-07-29 2000-02-02 G.T. Componenti Srl Dispositif pour l'ajustement de la position centrale des pistons et de la position angulaire d'un pignon d'un vérin qui entraíne une soupape

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN Bd. 1998, Nr. 11, 30. September 1998 (1998-09-30) -& JP 10 169608 A (KOGANEI CORP), 23. Juni 1998 (1998-06-23) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007006557A1 (fr) 2005-07-11 2007-01-18 Laeis Gmbh Agencement piston-cylindre
US7481161B2 (en) 2005-07-11 2009-01-27 Laeis Gmbh Plunger-cylinder assembly
CN107642517A (zh) * 2017-10-29 2018-01-30 刘福珍 一种农业机械用气缸行程受阻控制装置
CN107690905A (zh) * 2017-10-29 2018-02-16 刘福珍 农业用移栽机夹苗机构气缸定位结构
CN107830010A (zh) * 2017-10-29 2018-03-23 刘福珍 一种气缸行程受阻定位装置
CN107690905B (zh) * 2017-10-29 2019-09-06 潍坊学院 农业用移栽机夹苗机构气缸定位结构
CN117450133A (zh) * 2023-12-13 2024-01-26 江苏亚力亚气动液压成套设备有限公司 一种缓冲液压缸

Also Published As

Publication number Publication date
EP1416165A3 (fr) 2004-09-15
ATE325276T1 (de) 2006-06-15
DE50303172D1 (de) 2006-06-08
EP1416165B1 (fr) 2006-05-03
DE10249509A1 (de) 2004-05-13

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