US3805672A - Double acting fluid pressure operable cylinder device - Google Patents

Double acting fluid pressure operable cylinder device Download PDF

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Publication number
US3805672A
US3805672A US00302233A US30223372A US3805672A US 3805672 A US3805672 A US 3805672A US 00302233 A US00302233 A US 00302233A US 30223372 A US30223372 A US 30223372A US 3805672 A US3805672 A US 3805672A
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United States
Prior art keywords
passage means
sealing member
piston
cylinder
annular
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
US00302233A
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English (en)
Inventor
E Pekrul
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.)
Westinghouse Bremsen und Apparatebau GmbH
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Westinghouse Bremsen und Apparatebau GmbH
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Filing date
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Application filed by Westinghouse Bremsen und Apparatebau GmbH filed Critical Westinghouse Bremsen und Apparatebau GmbH
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Publication of US3805672A publication Critical patent/US3805672A/en
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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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position

Definitions

  • the resilient member and needle valve are arranged relative to each other so that the resilient member is engaged somewhat in advance of the end of the piston stroke to commence the cushioning effect but not so to prevent free-flow exhaust of fluid pressure from the cylinder chamber until just before the end of the piston stroke when the resilient member is effective for sealing off the unrestricted exhaust path and limiting final exhaust at a restricted rate via an adjustable needle valve.
  • the object of the present invention is to provide a double-acting cylinder device characterized by cushioning means providing positive protection against damages resulting from piston impact at the end of the stroke, said cushioning means being adjustable, without risking loss of maximum cushioning effect, to compensate for misadjustments and wear of the cylinder components.
  • the invention comprises a double-acting fluid pressure operable cylinder device having pressure chambers on opposite sides of the piston adjacent respective cylinder heads at opposite ends of the cylinder, each of said chambers being subjectable to fluid pressure and relief thereof alternately and in reverse order relative to each other, depending on direction of stroke movement of the piston.
  • Each of the cylinder heads is provided with a coaxial tapered recess for accommodating, at the end of the piston stroke in one direction or the other, respective coaxial cylindrical portions carried by the piston rod adjacent to and on opposite sides of the piston.
  • a resilient annular sealing member of particular cross-sectional area is disposed, with both axial and radial spacing, in respective particularly cross-sectionally shaped annular grooves surrounding the openings of each of the tapered recesses, said sealing member being engageable by the adjacent cylindrical portion, during final movement of the piston stroke, in advance of the end of said stroke for initiating cushioning effect of the piston.
  • said sealing member Upon engagement of the sealing member by and sliding movement therethrough of the cylindrical portion, said sealing member is expandingly deformed so as to make sealing contact with the bottom of the groove just prior to the end of the stroke, thereby cutting off free-flow exhaustion of fluid pressure from the pressure chamber and diverting such exhaustion at a restricted rate through an adjustable needle valve, with which the degree of cushioning of the piston can be regulated.
  • the sealing member has a beveled annular portion part of which projects axially out' of the annular groove and into the pressure chamber beyond the inner axial limit of the cylinder head, thus permitting thecylindrical portion of the piston to engage said sealing member and provide cushioning effect ahead of its valve action (seating on the bottom of the groove) before the piston reaches the cylinder head.
  • FIGURE drawing is an axial view, in section, of a double-acting cylinder device embodying the invention.
  • a double-acting cylinder device designated 1 comprises a cylinder casing 2 and a pair of cylinder heads 3 and 4 secured at opposite ends of the cylinder casing, respectively.
  • a piston 5 and a piston rod 6 are operably disposed in the cylinder casing 2, said rod slidably extending exteriorly of the cylinder device through a guide bushing 7 coaxially secured in cylinder head 3 and in sealingly sliding relation with a sealing ring 8 coaxially disposed in said cylinder head adjacent the inner end of said guide bushing.
  • a scraper or cleaning ring 9, disposed coaxially in cylinder head 3 adjacent the outer end of guide bushing 7, provides cleaning action for the piston rod 6 as said rod moves reciprocably therethrough in contacting relation therewith.
  • An adjustable needle valve 10 is mounted in cylinder head 3, forming a variable throttle opening 11 between a radial passageway 12 and axial passageway 13 in cylinder head 3.
  • the piston rod 6 has a pair of enlarged cylindrical portions 14 formed coaxially thereon in juxtaposition to the opposite sides of piston 5, respectively.
  • Coaxial recesses 15 are formed in cylinder heads 3 and for accommodating the cylindrical portions 14, respectively, at the end of the piston strokes.
  • Each of the recesses 15, by being connected to a combined inlet-outlet port 16, provides passage means via which fluid pressure may be admitted to or exhausted from the cylinder device.
  • the radial passageway 12 belonging to needle valve '10' also opens radially into recess 15 between the two ends of the recess, said recess tapering from the open end adjacent piston 5 toward its base adjacent sealing ring 8.
  • Recess 15 is concentrically surrounded at the larger open end thereof facing piston 5 with an annular groove 18.
  • Groove 18 is defined by a cylindrical side wall of greater diameter than the opening of recess 15, an internally beveled annular flange 19 extending radially from the end of said cylindrical side wall adjacent piston 5 and having an inside diameter smaller than said cylindrical side wall but greater than said opening, and an annular flat bottom surface 20 radially disposed between the other end of said cylindrical side wall and the periphery of said opening perpendicularly to the axis thereof.
  • the axial boring 13 belonging to the needle valve 10 also emerges into groove 18 at the bottom surface 20.
  • cylindrical portions 14 can be independent sleeves or bushings, as shown in the drawing, or formed integrally with the piston rod 6 or the piston 5.
  • An elastic annular sealing member 21 is normally loosely disposed in groove 18 with a small axial clearance, as indicated at C.
  • Sealing member 21 is characterized by a flat sealing surface 22 complementarily adapted for sealingly engaging bottom surface 20 and cooperating therewith as a valve.
  • Sealing member 21 is also provided with a beveled front surface 23 facing the piston and complementary to the internally beveled flange19.
  • the beveled front surface 23 joins with a toroidal surface comprising the adjacent internal portion 24 of the sealing member 21 which diminishes diametrally toward the juncture with said toroidal surface, said juncture comprising a smallest diameter 26 substantially smaller than the outer diameter of the cylindrical portion 14 which is provided with a beveled leading end 27.
  • a larger diameter 28 of the conical surface 25 adjacent the bottom of groove 18 is essentially the same or somewhat smaller than the outer diameter of the cylindrical portion 14.
  • Sealing member 21 is further provided with a plurality of angularly spaced and axially disposed throughpassageways 29 connecting a cylinder chamber 30 to the axial passageway 13, associated with needle valve 10, via a commonannular V-shaped channel 31 formed in the sealing surface 22 of sealing member 21 and intersecting said passageways 29. Moreover, a sealing edge. 32 of sealing member 21 makes annular contact with bottom 20 of groove 18 on a circular area between the through-passageways 29 and annular channel 31 and between the central conical surface of the sealing member 21 and said channel 31.
  • one of the passageways 29 opening to channel 31 appears to be axially aligned with passageway l3, thisis not the actual structure. in the actual construction of the invention, none of the passageways 29, for purposes to become evident hereinafter, is permitted to coincide axially with passageway 13.
  • port 16 of theright cylinder head 3 is-being supplied with fluid pressure, while the corresponding port 16 on the opposite cylinder head 4 is exhausted.
  • port 16 in cylinder head 3 will be referred to hereinafter as the right port, while port 16 in cylinder head 4 will be referred to as the left port.
  • piston 5 is moved toward the right.
  • the compressed air located in cylinder chamber escapes, at first unthrottled, through the space formed between piston rod 6 and central opening 25 of sealing member 21, recess 15 of cylinder head 3, and the combined inlet and outlet right port 16 to atmosphere.
  • the cylindrical portion 14 on the right side of piston 5 enters into the central conical opening 25 of sealing member 21 while causing sealing member 21 to be expanded radially by means of the front beveled end 27.
  • sealing member 21 tightly encircles the cylindrical portion 14, especially at the point of the smallest diameter 26 of said sealing member, so that unrestricted flow of fluid pressure medium from the cylinder chamber 30 into recess 15 of cylinder head 3 is interrupted at this point.
  • the compressed air remaining in chamber 30 can only escape through the through-passageways 29 and annular channel 31 of sealing member 21 through the throttle opening 11 into recess 15 adjusted by means of needle valve 10 which is located between passageways 12 and 13 of cylinder head 3.
  • piston 5 Shortly before reaching an inner wall 33,0f cylinder head 3, piston 5 is elastically caught and braked by the beveled surface 23 of sealing member 21 axially projecting beyond the axial limit of said inner wall into the cylinder chamber 30, the toroidal surface 24 being the first to come into contact with piston 5. in this way, possible damage resulting from a hard metallic contact of piston 5 with inner wall 33 of cylinder head 3, which is normally of metal construction, is avoided, such damage being more apt to occur when throttle opening 11 is adjusted to a relatively large opening of needle valve 10 or a weak initial cushioning of the piston movement is effected;
  • sealing memeber 21 Upon renewed venting of left port 16 or supply of fluid pressure to right port 16, sealing memeber 21 is axially displaced leftwardly by the measure of its axial clearance to the point of contact with the internal beveled surface of flange 19 of annular groove 18 as a result of the pressure building up in recess 15 of cylinder head 3 due to the concurrent choking or throttle action of needle valve 10 and the initially slowly retreating piston 5, so that the sealing surface 22 and particularly the sealing edge 32 is loosened from the bottom 20 of annular groove 18.
  • the fluid pressure medium can now enter into cylinder chamber 30 through the communication thus produced, with a slight throttling effect, via annular channel 31 and axial passageways 29 of sealing memeber 21 to strongly act on piston 5.
  • annular channel 31 and axial passageways 29 of sealing memeber 21 After cylindrical portion 14 has emerged from central opening 25 of sealing member 21, all barriers to unrestricted flow of fluid pressure into chamber 30 are removed so that piston 5 can be acted on by the full fluid pressure.
  • sealing member 21 is especially simple and advantageous with respect to the flow of pressure medium.
  • a cylinder device having at least one cylinder head in which is formed a combined fluid pressure supply and exhaust cylindrical recess for reciprocably accommodating therein, with radial clearance, an end portion of the piston rod of a piston and rod assembly and a diametrally enlarged portion of the piston rod formed in juxtaposition to the adjacent one side of the piston, in combination:
  • annular groove formed in said cylinder head coaxially with and adjacent to the opening of said recess, said annular groove being defined by two oppositely facing and spaced apart end walls radially disposed relative to the wall of said recess and joined by a cylindrical surface forming the side wall of said groove;
  • annular sealing member disposed in said groove for axial movement therein relative to said recess between the limits defined by said spaced apart end walls, said annular sealing member, when in a relaxed state, having an inner diameter larger than said end portion and smaller than said enlarged portion of the piston rod and an outer diameter less than that of said side wall of said annular groove to provide an expansion clearance therebetween;
  • unrestricted passage means comprising said radial clearance between said piston rod and said cylindrical recess and the radial clearance between said inner diameter of said annular sealing member and said end portion of the piston rod for providing unrestricted flow of fluid under pressure to and from a cylinder chamber formed adjacent said one side of the piston during axial movement of said end portion of the piston rod through said unrestricted passage means coinciding with movement of the piston in one direction toward the cylinder head or in the opposite direction away therefrom; and
  • restricted passage means disposed in said cylinder head in parallel relation to said unrestricted passage means with one end opening to said annular groove and the other end opening to said cylindrical recess, said enlarged portion of the piston rod being effective, when moving axially through said sealing member, for cutting off said unrestricted passage means and limiting flow of fluid pressure between said cylinder chamber and said cylindrical recess to a restricted rate through said restricted passage means only,
  • said sealing member having communicating passage means formed therein for communicating said cylinder chamber with said restricted passage means during such time that said unrestricted passage means is cut off and having an annular frontal portion projecting axially out of said groove into said cylinder chamber, said frontal portion being abuttingly engaged by the piston during final movement thereof for providing final cushioning effect on the piston and consequent distortion of the sealing member in said groove against said one end of said restricted passage means for cutting off said communicating passage means from said restricted passage means and, therefore, said restricted flow through the restricted passage means during said final movement of the piston in said one direction.
  • a cylinder device as set forth in claim 1, wherein the axial dimension of that portion of the sealing member confined within said annular groove is less than the axial distance between said end walls of the groove.
  • a cylinder device as set forth in claim 1, wherein said frontal portion of said sealing member comprises an annular toroidal surface formed adjacent the inner diameter of the sealing member and in facing relation to the cylinder chamber, said toroidal surface joining at its inner periphery with a tapered concentric opening expanding diametrically toward the cylindrical recess and at its outer periphery with a beveled'surface sloping away from the toroidal surface toward said cylindrical recess, the end wall of said annular groove adjacent the cylinder chamber being complementarily beveled and uniformly axially spaced from the beveled surface of the sealing member;
  • a cylinder device as set forth in claim 1, wherein said communicating passage means in said sealing member comprises a plurality of angularly spaced passageways extending axially therethrough for communicating said cylinder chamber with said restricted passage means for effecting said restricted flow to and from said cylinder chamber during said axial movement of said enlarged portion through said sealing member.
  • a cylinder device as set forth in claim 4, wherein a communication between said angularly spaced passageways and said one end of said restricted passage means is provided via a common annular channel formed on the side of said sealing member opposite said frontal portion and to which said spaced passageways open, said channel also registering with said one end of said restricted passage means opening to said annular groove.
  • a cylinder device as set forth in claim 5, wherein distortion of the sealing member resulting from engagement thereof by said piston moving in said one direction causes said annular channel to be compressed against the respective adjacent end wall of said annular groove and cooperating therewith for sealing off said communication between said angularly spaced passageways and said one end of the restricted passage means.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
US00302233A 1971-12-27 1972-10-30 Double acting fluid pressure operable cylinder device Expired - Lifetime US3805672A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2164832 1971-12-27

Publications (1)

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US3805672A true US3805672A (en) 1974-04-23

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US00302233A Expired - Lifetime US3805672A (en) 1971-12-27 1972-10-30 Double acting fluid pressure operable cylinder device

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US (1) US3805672A (fr)
BE (1) BE793149A (fr)
DE (1) DE2164832C2 (fr)
FR (1) FR2166024B1 (fr)

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4012174A (en) * 1975-10-20 1977-03-15 Caterpillar Tractor Co. Fuel priming pump
US4015728A (en) * 1975-02-24 1977-04-05 Caterpillar Tractor Co. Material handling apparatus
US4088061A (en) * 1973-11-07 1978-05-09 Kurt Stoll Piston/cylinder assemblies
US4181066A (en) * 1978-02-10 1980-01-01 Mcneil Corporation Expansible chamber motor
US4307997A (en) * 1979-05-08 1981-12-29 The United States Of America As Represented By The United States Department Of Energy Free piston inertia compressor
US4406215A (en) * 1981-03-26 1983-09-27 Ernest Lacasse Drive cylinder
US4458717A (en) * 1983-03-14 1984-07-10 Aeroquip Corporation Cylinder cushion seal
US4862786A (en) * 1987-08-27 1989-09-05 Bimba Manufacturing Company Fluid cylinder cushioning system
US5117526A (en) * 1990-05-03 1992-06-02 The Serco Corporation Vertically storing dock leveler
DE4039172A1 (de) * 1990-12-05 1992-06-11 Mannesmann Ag Arbeitszylinder mit endlagendaempfung
US5188016A (en) * 1992-03-25 1993-02-23 Tung Fung Eng Cylinder structure for a pneumatically operated tool
US5228380A (en) * 1991-10-15 1993-07-20 Festo Kg Linear drive
US5252042A (en) * 1991-08-09 1993-10-12 Kabushiki Kaisha Kosmek Gas booster assembly for fluid pressure piston driving apparatus
GB2278642A (en) * 1993-06-03 1994-12-07 Mannesmann Ag Piston and cylinder device
US5850776A (en) * 1996-04-18 1998-12-22 Ckd Corporation Fluid pressure cylinders provided with impact absorbing mechanisms
EP0918163A1 (fr) * 1997-11-24 1999-05-26 Howa Machinery Limited Un amortisseur élastomérique pour vérin
EP1041293A2 (fr) 1999-03-29 2000-10-04 Luciano Migliori Vérin pneumatique avec dispositif d'amortissement
EP1199480A2 (fr) 2000-10-16 2002-04-24 Luciano Migliori Vérin compact pneumatique avec dispositif amortisseur
US6536327B2 (en) * 2001-06-08 2003-03-25 Festo Corporation Double acting cylinder with integral end position volume chambers
US20030056507A1 (en) * 2001-07-09 2003-03-27 Mentink Laurentius Andreas Gerardus Hydraulic control device
US6619182B2 (en) 2001-04-25 2003-09-16 Delaware Capital Formation, Inc. Flow control device
US20040156690A1 (en) * 2002-12-06 2004-08-12 Rohm Gmbh & Co. Kg Opening actuator for collet chuck
US20040237774A1 (en) * 2003-03-07 2004-12-02 Smc Kabushiki Kaisha Cylinder apparatus
US20060016328A1 (en) * 2004-07-23 2006-01-26 Belanger Rene F Impact plate for component assembly
US20060137336A1 (en) * 2003-06-12 2006-06-29 Norbert Krimbacher Hydraulic drive for displacing an actuator
US20060272497A1 (en) * 2005-05-12 2006-12-07 P. & M. Design & Consulting Ltd. Pneumatic cylinder
US20080122187A1 (en) * 2006-11-03 2008-05-29 Carl Freudenberg Kg Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
US20080135363A1 (en) * 2006-12-06 2008-06-12 Smc Kabushiki Kaisha Damper Fixing Mechanism
US20100077916A1 (en) * 2008-10-01 2010-04-01 Larry Brunn Hydraulic cylinder with cushion
US20130255245A1 (en) * 2010-07-23 2013-10-03 Sany Heavy Industry Co., Ltd. Hydraulic oil cylinder, hydraulic cushion system, excavator and concrete pump truck
US8578837B1 (en) 2010-05-12 2013-11-12 John C. A. Burhoe Pressure unloading valve to cushion a pneumatic cylinder
US20140090555A1 (en) * 2012-09-29 2014-04-03 Shenzhen China Star Of Optoelectronics Technology Co., Ltd Cylinder
US11421716B2 (en) * 2020-06-10 2022-08-23 Smc Corporation Gas cylinder

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3623143C2 (de) * 1986-07-09 1995-03-09 Leibfried Maschinenbau Gmbh Fluidbetätigter Zylinder
FR2658872A1 (fr) * 1990-02-27 1991-08-30 Joucomatic Sa Perfectionnements apportes aux verins pour fluide sous pression.
SE510773C2 (sv) * 1996-02-13 1999-06-21 Mecman Ab Rexroth Anordning vid kolvcylinderaggregat samt kolvcylinderaggregat med åtminstone en dylik anordning
DE102009014817B4 (de) * 2009-03-25 2011-07-21 FESTO AG & Co. KG, 73734 Fluidbetätigter Linearantrieb
DE102015002036A1 (de) * 2015-02-17 2016-08-18 Festo Ag & Co. Kg Fluidbetätigte Lineareinheit

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3267815A (en) * 1965-10-21 1966-08-23 Ortman Miller Machine Company Cushioning structure for power cylinders
US3651740A (en) * 1969-11-24 1972-03-28 Spotnails Pneumatic driving tool with a fail-safe mechanism

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1370356A (fr) * 1963-09-28 1964-08-21 Vérin à coussins amortisseurs

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3267815A (en) * 1965-10-21 1966-08-23 Ortman Miller Machine Company Cushioning structure for power cylinders
US3651740A (en) * 1969-11-24 1972-03-28 Spotnails Pneumatic driving tool with a fail-safe mechanism

Cited By (51)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4088061A (en) * 1973-11-07 1978-05-09 Kurt Stoll Piston/cylinder assemblies
US4015728A (en) * 1975-02-24 1977-04-05 Caterpillar Tractor Co. Material handling apparatus
US4012174A (en) * 1975-10-20 1977-03-15 Caterpillar Tractor Co. Fuel priming pump
US4181066A (en) * 1978-02-10 1980-01-01 Mcneil Corporation Expansible chamber motor
US4307997A (en) * 1979-05-08 1981-12-29 The United States Of America As Represented By The United States Department Of Energy Free piston inertia compressor
US4406215A (en) * 1981-03-26 1983-09-27 Ernest Lacasse Drive cylinder
US4458717A (en) * 1983-03-14 1984-07-10 Aeroquip Corporation Cylinder cushion seal
US4862786A (en) * 1987-08-27 1989-09-05 Bimba Manufacturing Company Fluid cylinder cushioning system
US5117526A (en) * 1990-05-03 1992-06-02 The Serco Corporation Vertically storing dock leveler
DE4039172A1 (de) * 1990-12-05 1992-06-11 Mannesmann Ag Arbeitszylinder mit endlagendaempfung
US5207145A (en) * 1990-12-05 1993-05-04 Mannesmann Aktiengesellschaft Work cylinder, such as the work cylinder of a rodless piston cylinder
US5252042A (en) * 1991-08-09 1993-10-12 Kabushiki Kaisha Kosmek Gas booster assembly for fluid pressure piston driving apparatus
US5228380A (en) * 1991-10-15 1993-07-20 Festo Kg Linear drive
US5188016A (en) * 1992-03-25 1993-02-23 Tung Fung Eng Cylinder structure for a pneumatically operated tool
GB2278642A (en) * 1993-06-03 1994-12-07 Mannesmann Ag Piston and cylinder device
GB2278642B (en) * 1993-06-03 1997-03-19 Mannesmann Ag Piston and cylinder device
US5850776A (en) * 1996-04-18 1998-12-22 Ckd Corporation Fluid pressure cylinders provided with impact absorbing mechanisms
EP0918163A1 (fr) * 1997-11-24 1999-05-26 Howa Machinery Limited Un amortisseur élastomérique pour vérin
US6186484B1 (en) 1997-11-24 2001-02-13 Howa Machinery, Ltd. Elastomer damper for an actuator cylinder
CN1080395C (zh) * 1997-11-24 2002-03-06 丰和工业株式会社 作动缸的弹性材料减震器
EP1041293A2 (fr) 1999-03-29 2000-10-04 Luciano Migliori Vérin pneumatique avec dispositif d'amortissement
US6382074B1 (en) 1999-03-29 2002-05-07 Luciano Migliori Pneumatic cylinder with damping device
US6553889B2 (en) * 2000-10-16 2003-04-29 Luciano Migliori Compact pneumatic cylinder, with cushioning device
EP1199480A2 (fr) 2000-10-16 2002-04-24 Luciano Migliori Vérin compact pneumatique avec dispositif amortisseur
US6619182B2 (en) 2001-04-25 2003-09-16 Delaware Capital Formation, Inc. Flow control device
US6536327B2 (en) * 2001-06-08 2003-03-25 Festo Corporation Double acting cylinder with integral end position volume chambers
US6739235B2 (en) * 2001-07-09 2004-05-25 Actuant Corporation Hydraulic control device
US20030056507A1 (en) * 2001-07-09 2003-03-27 Mentink Laurentius Andreas Gerardus Hydraulic control device
US20040156690A1 (en) * 2002-12-06 2004-08-12 Rohm Gmbh & Co. Kg Opening actuator for collet chuck
US7201547B2 (en) * 2002-12-06 2007-04-10 Rohm Gmbh Opening actuator for collet chuck
US7021192B2 (en) * 2003-03-07 2006-04-04 Smc Kabushiki Kaisha Cylinder apparatus
US20040237774A1 (en) * 2003-03-07 2004-12-02 Smc Kabushiki Kaisha Cylinder apparatus
US7395748B2 (en) * 2003-06-12 2008-07-08 Linz Center Of Mechatronics Gmbh Hydraulic drive for displacing an actuator
US20060137336A1 (en) * 2003-06-12 2006-06-29 Norbert Krimbacher Hydraulic drive for displacing an actuator
US6997100B1 (en) * 2004-07-23 2006-02-14 Hamilton Sundstrand Impact plate for component assembly
US20060016328A1 (en) * 2004-07-23 2006-01-26 Belanger Rene F Impact plate for component assembly
US20060272497A1 (en) * 2005-05-12 2006-12-07 P. & M. Design & Consulting Ltd. Pneumatic cylinder
US7395749B2 (en) 2005-05-12 2008-07-08 Michael R Adams Pneumatic cylinder
US20110074114A1 (en) * 2006-11-03 2011-03-31 Gonzalo Barillas Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
US20080122187A1 (en) * 2006-11-03 2008-05-29 Carl Freudenberg Kg Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
US8234970B2 (en) * 2006-11-03 2012-08-07 Carl Freudenberg Kg Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
US7866252B2 (en) * 2006-11-03 2011-01-11 Carl Freudenberg Kg Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
US20080135363A1 (en) * 2006-12-06 2008-06-12 Smc Kabushiki Kaisha Damper Fixing Mechanism
US20100077916A1 (en) * 2008-10-01 2010-04-01 Larry Brunn Hydraulic cylinder with cushion
US8578837B1 (en) 2010-05-12 2013-11-12 John C. A. Burhoe Pressure unloading valve to cushion a pneumatic cylinder
US20130255245A1 (en) * 2010-07-23 2013-10-03 Sany Heavy Industry Co., Ltd. Hydraulic oil cylinder, hydraulic cushion system, excavator and concrete pump truck
AU2011282322B2 (en) * 2010-07-23 2016-11-24 Hunan Sany Intelligent Control Equipment Co., Ltd Hydraulic oil cylinder, hydraulic cushion system, excavator and concrete pump truck
US9863407B2 (en) * 2010-07-23 2018-01-09 Hunan Sany Intelligent Control Equipment Co., Ltd. Hydraulic oil cylinder, hydraulic cushion system, excavator and concrete pump truck
US20140090555A1 (en) * 2012-09-29 2014-04-03 Shenzhen China Star Of Optoelectronics Technology Co., Ltd Cylinder
US9103357B2 (en) * 2012-09-29 2015-08-11 Shenzhen China Star Optoelectronics Technology Co., Ltd Cylinder
US11421716B2 (en) * 2020-06-10 2022-08-23 Smc Corporation Gas cylinder

Also Published As

Publication number Publication date
FR2166024A1 (fr) 1973-08-10
FR2166024B1 (fr) 1976-07-23
DE2164832B1 (de) 1973-05-10
DE2164832C2 (de) 1973-11-29
BE793149A (fr) 1973-06-21

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