US3511048A - Hydropneumatic clamping cylinder - Google Patents

Hydropneumatic clamping cylinder Download PDF

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Publication number
US3511048A
US3511048A US732584A US3511048DA US3511048A US 3511048 A US3511048 A US 3511048A US 732584 A US732584 A US 732584A US 3511048D A US3511048D A US 3511048DA US 3511048 A US3511048 A US 3511048A
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United States
Prior art keywords
pressure
cylinder
piston
ram
clamping cylinder
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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
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US732584A
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English (en)
Inventor
Josef Nemetz
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Individual
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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
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B1/00—Vices
    • B25B1/06—Arrangements for positively actuating jaws
    • B25B1/18—Arrangements for positively actuating jaws motor driven, e.g. with fluid drive, with or without provision for manual actuation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/165—Control arrangements for fluid-driven presses for pneumatically-hydraulically driven presses
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • a pneumatically operated clamping cylinder includes an internal axially slidable assembly which includes at least two independent relatively axially movable elements which, in turn, operate a radially outwardly movable locking element to hold the clamping element in place.
  • all moving parts of the clamping cylinder are combined into a unit by two sleeves contained in the cylinder, the confronting extremities of the sleeves bearing locking cones Which are mounted slidingly on a cylindrical projection of a counter-pressure plate so as to have a limited movement in the direction of the axis.
  • a control valve and a check valve are provided in the locking cone facing the piston ram.
  • a control piston is placed in front of the differential piston, and has an aperture through which the compressed air acts only on a reduced area of the differential piston that is of about the same size as the aperture.
  • an air cushion is created between the piston ram and a bearing plate, which is formed by a plug which slides sealingly on the shaft of the piston ram and is equipped with a pressure relief valve.
  • a somewhat modified, very simple embodiment which can be manufactured at low cost consists in making the sleeve, which contains the assembly of moving parts, of a resilient plastic which, in the area of the high-pressure stroke, is pressed into grooves or threads on the inner wall of the cylinder, thereby producing a locking engagement between the sleeve and the cylinder.
  • FIG. 1 shows a clamping cylinder having a low pres- 3,511,048 Patented May 12, 1970 sure circuit and a high pressure circuit with valve control
  • FIG. 2 shows another embodiment without valve control.
  • FIG. 3 shows a clamping cylinder having no specific expansion locking members.
  • FIG. 4 shows another design of the clamping cylinder.
  • FIG. 1 The embodiment of FIG. 1 will first be described.
  • a pair of internal cyclinders 2a, 2b are displaceably contained, the respective ends of the barrel being closed by caps 1 and 16.
  • the low-pressure piston 4 In the internal cylinder 2a slides the low-pressure piston 4, which is guided sealingly by its stern in the counter-pressure plate 12.
  • Internal cylinder 2a terminates in the expansion lock taper 6, which in turn slidingly receives a projection 12a of the counter pressure plate 12.
  • the other expansion lock member 8 slides on the same projection 12a, and forms a continuation of internal cylinder 2b, being sealed against the wall of the clamping cylinder 2.
  • the high-pressure ram 13 slides in internal cylinder 2b.
  • the extremity of internal cylinder 2b is closed by a plug 15.
  • the sealing against the ram 13 is performed by a cufi gasket 40 whose open side faces the high-pressure piston.
  • An over-pressure valve 11 is provided in the plug 15. Furthermore, two valves 9 and 10 operating in different directions are provided in the expansion lock member 8, and the piston 4 is provided with an oil filter screw 3 for admitting fluid into an inner chamber through opening 5, covered by safety ring 30.
  • the manner of operation of the clamping cylinder is the following:
  • the compressed air enters through the aperture 17, Since there is oil in chamber 21, which is in communication through orifices 23 with the cavity in projection 12a, the entire contents of the clamping cylinder operate as a unit, so that the compressed air pushes internal cylinder parts 2a and 2b as Well as the expansion lock ring 7 ahead of it until the piston ram 13 encounters the workpiece that is to be clamped, and thus forms a solid basis for the operation that follows.
  • the low-pressure piston 4 now moves in the direction of the high-pressure piston.
  • the pressure which it exercises now acts upon the oil-filled spaces.
  • the air escapes from chamber 20 through orifices 22 past expansion lock ring 7 through the opening valve 9 and through passages 14 into the exhaust line 18.
  • the high pressure acting on both of the outer sides of the expansion lock jaws 6 and 8 forces both these members together, so that their tapers act on the expansion lock ring 7, urging the latter tightly against the inner wall of cylinder 2.
  • the clamping cylinder is locked.
  • chamber 15a acts as an air spring, because when there is pressure in this chamber the cuff gasket is urged tightly against ram 13.
  • This relief valve 11 brings it about that the bias is constant through the entire high-pressure range.
  • expansion lock tapers 6a and 8a are not made in one piece with the two internal cylinders parts, but are separate elements that are sealed against the internal cylinder parts and the projection of the low-pressure piston. Furthermore, recesses 60 are provided on the expansion lock tapers 6a and 8a in order that the friction of engagement between the expansion lock ring 7a and expansion lock members 6a and 8a may be lower than the friction of engagement between the expansion lock ring and the exterior cylinder. Also, in this embodiment a throttling check valve 27 is installed in a known manner in passage 18. The cross section of the air relief grooves 14 is smaller, to the greatest possible extent, than the throttle cross section, so as to retard the loss of pressure between the expansion lock tapers 7a and 8a.
  • FIG. 3 shows another very simple embodiment, but one which is functionally equivalent to the first two embodiments.
  • the internal cylinder members 2av and 2b of FIGS. 1 and 2 are here replaced by an internal cylinder 31 which is made of a resilient plastic.
  • cylinder 2 In the highpressure area, cylinder 2 has grooves 33, in the shape of a screw thread if desired.
  • the plastic cylinder 31 In the area of the high-pressure ram 13 and plug 34, the plastic cylinder 31 is reinforced by a metal sleeve 32, which is not subject to deformation.
  • the pressure in chamber 15a builds up until the plastic cylinder 31 deforms in the high-pressure area and produces a frictional as Well as positive engagement on grooves 33.
  • This engagement may be frictional only, if desired, if the inside surface of the outer cylinder and the outside surface of the plastic cylinder are made of appropriate materials and are so designed that, when high pressure occurs, the friction between cylinder 2 and cylinder 31 is greater than the force moving the pistons.
  • a plate 24 can again :be used, as represented in the upper crosssectional portion of the drawing, or a spring-loaded catch 3a can be used with practically the same action.
  • the counter-pressure plate 35 is fastened by means of a snap ring 36 to a flange formed on the plastic cylinder 31.
  • FIG. 4 shows an embodiment that is approximately equivalent to the one in FIG. 1.
  • Plug 15 is also different from FIG. 1: in this case the cross section of the air relief grooves can be kept large, so that a rapid unlocking can be accomplished through the check valve 150.
  • the throttling in the working stroke is performed by the nozzle'hole 15a in conjunction with seal 15b.
  • the same action can also be achieved if the nozzle hole 15a and seal 15b are eliminated, by providing a corresponding clearance 15d or an air relief groove.
  • Cylinder parts 28 with the cones 6 and 8 are then constructed the same'as in FIG. 1.
  • the systems are also interchangeable with one another. It is also possible for the counter-pressure plate 12 to be affixed to the expansion clamp cone 8 facing the ram 13.
  • a fluid operated clamping mechanism including a cylinder, an axially slidable assembly contained therein, said assembly including a pair of relatively axially slidable pistons defining an expansible closed fluid filled chamber there-between, one of said pistons being attached to a ram for clamping an object, the other of said pistons comprising a counter pressure plate, a low-pressure differential piston axially movable in said cylinder and having a stern of reduced diameter slidable in said counter pressure plate, one side of said low-pressure differential piston being in communication with the interior of the expansible chamber, the other side of the low-pressure differential piston being in communication with an actuating fluid, said assembly also including radially expansible locking means for engagement with the inner wall of said cylinder, and means responsive to pressure in said expansible chamber for actuating said locking means when said ram engages with an object to be clamped.
  • said axially slidable assembly includes a pair of internal cylinders having opposed end walls, said two relatively axially slidable pistons being slidable respectively in said internal cylinders, said internal cylinders being provided with cooperating conical surfaces for actuating said locking means, said piston comprising the pressure plate being provided with a hollow stem slidably received in the end walls of the internal cylinders and in sealing engagement therewith for providing communication between the spaces in said internal cylinders defined by said end walls and the respective pistons, and means for limiting the relative axial movement of said internal cylinders in one direction.
  • a control piston is axially slidably positioned in said cylinder between a source of actuating fluid and said other side of said low-pressure differential piston, said control piston having a bore therethrough, and seal means for confining the area of the differential piston exposed to the actuating fluid when said control piston is in abutting engagement with the difierential piston.
  • said locking means includes a cylindrical resilient sleeve portion in sliding engagement with the inner Wall of said cylinder, a portion of said inner wall being provided with circumferential rib means, said resilient sleeve portion being expansible into locking engagement with said rib means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Clamps And Clips (AREA)
US732584A 1967-06-08 1968-05-28 Hydropneumatic clamping cylinder Expired - Lifetime US3511048A (en)

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Application Number Priority Date Filing Date Title
DEN0030666 1967-06-08

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US (1) US3511048A (de)
DE (1) DE1627852C3 (de)
FR (1) FR1599881A (de)
GB (1) GB1228058A (de)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3831456A (en) * 1973-04-13 1974-08-27 Kms Ind Inc Linear actuator with lock
US4072013A (en) * 1974-10-10 1978-02-07 Aldo Barbareschi Fluid pressure actuated operator cylinder with incorporated stress converter
US4305565A (en) * 1980-04-07 1981-12-15 Hydril Company Variable position ram lock for blowout preventers
US4633758A (en) * 1983-10-26 1987-01-06 Wabco Westinghouse Steuerungstechnik Gmbh & Co. Double-acting working cylinder having a piston-dampening arrangement
US4787206A (en) * 1986-07-30 1988-11-29 Herbert Haenchen Kg Hydraulic pressure transducer
US5067323A (en) * 1990-06-13 1991-11-26 United Technologies Corporation Three position actuator arrangement
US5140904A (en) * 1990-06-29 1992-08-25 Alfred Teves Gmbh Piston sealing arrangement for pressure-fluid-operated systems
US5218821A (en) * 1992-04-23 1993-06-15 Doben Limited Pressure intensifier cylinder utilizing air
US5247872A (en) * 1991-12-27 1993-09-28 Hideo Hoshi Multi-stage hydraulic actuator
US5526644A (en) * 1995-06-07 1996-06-18 Brieschke; Todd M. Oil intensifier cylinder
US5682806A (en) * 1995-05-27 1997-11-04 Kretzschmar; Michael Pressure medium pliers
CN106321892A (zh) * 2016-11-03 2017-01-11 孟琴 一种气动阀装置及气动钳
US20180266445A1 (en) * 2017-03-15 2018-09-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
US20180266446A1 (en) * 2017-03-15 2018-09-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
JP2018155402A (ja) * 2017-03-15 2018-10-04 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
JP2018155406A (ja) * 2017-03-15 2018-10-04 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーク接合装置、ワーク固定装置、シリンダ装置動作方法、ワークプレス方法、ワーク接合方法、及びワーク固定方法
JP2018155401A (ja) * 2017-03-15 2018-10-04 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
JP2019044965A (ja) * 2017-08-29 2019-03-22 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
US10821564B2 (en) * 2017-03-15 2020-11-03 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2811083A1 (de) * 1978-03-14 1979-09-20 Hilti Ag Vorrichtung zum eintreiben von bolzen und naegeln mittels druckluft
JPS6050635B2 (ja) * 1978-06-02 1985-11-09 株式会社昭和製作所 船舶推進機のトリム・チルト装置
FR2477960A1 (fr) * 1980-03-12 1981-09-18 Therond Marcel Mecanisme de presse hydraulique a course rapide puis lente
JP6999439B2 (ja) * 2017-03-15 2022-01-18 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2632425A (en) * 1950-05-26 1953-03-24 Reginald L Grover Piston lock
US3135171A (en) * 1962-06-06 1964-06-02 Mechanical Power Corp Power cylinder
US3208759A (en) * 1963-12-05 1965-09-28 Firestone Collet
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3320861A (en) * 1965-12-22 1967-05-23 Mechanical Power Corp Locking fluid cylinder

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2632425A (en) * 1950-05-26 1953-03-24 Reginald L Grover Piston lock
US3135171A (en) * 1962-06-06 1964-06-02 Mechanical Power Corp Power cylinder
US3208759A (en) * 1963-12-05 1965-09-28 Firestone Collet
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3320861A (en) * 1965-12-22 1967-05-23 Mechanical Power Corp Locking fluid cylinder

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3831456A (en) * 1973-04-13 1974-08-27 Kms Ind Inc Linear actuator with lock
US4072013A (en) * 1974-10-10 1978-02-07 Aldo Barbareschi Fluid pressure actuated operator cylinder with incorporated stress converter
US4305565A (en) * 1980-04-07 1981-12-15 Hydril Company Variable position ram lock for blowout preventers
US4633758A (en) * 1983-10-26 1987-01-06 Wabco Westinghouse Steuerungstechnik Gmbh & Co. Double-acting working cylinder having a piston-dampening arrangement
US4787206A (en) * 1986-07-30 1988-11-29 Herbert Haenchen Kg Hydraulic pressure transducer
US5067323A (en) * 1990-06-13 1991-11-26 United Technologies Corporation Three position actuator arrangement
US5140904A (en) * 1990-06-29 1992-08-25 Alfred Teves Gmbh Piston sealing arrangement for pressure-fluid-operated systems
US5247872A (en) * 1991-12-27 1993-09-28 Hideo Hoshi Multi-stage hydraulic actuator
US5218821A (en) * 1992-04-23 1993-06-15 Doben Limited Pressure intensifier cylinder utilizing air
US5682806A (en) * 1995-05-27 1997-11-04 Kretzschmar; Michael Pressure medium pliers
US5526644A (en) * 1995-06-07 1996-06-18 Brieschke; Todd M. Oil intensifier cylinder
CN106321892A (zh) * 2016-11-03 2017-01-11 孟琴 一种气动阀装置及气动钳
JP2018155401A (ja) * 2017-03-15 2018-10-04 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
US20180266446A1 (en) * 2017-03-15 2018-09-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
JP2018155402A (ja) * 2017-03-15 2018-10-04 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
JP2018155406A (ja) * 2017-03-15 2018-10-04 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーク接合装置、ワーク固定装置、シリンダ装置動作方法、ワークプレス方法、ワーク接合方法、及びワーク固定方法
US20180266445A1 (en) * 2017-03-15 2018-09-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
CN108621460A (zh) * 2017-03-15 2018-10-09 精工电子有限公司 缸装置、冲压装置、工件夹持装置、缸装置的工作方法、工件的夹持方法及工件的冲压方法
US10821564B2 (en) * 2017-03-15 2020-11-03 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
US10941790B2 (en) * 2017-03-15 2021-03-09 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
US10982690B2 (en) * 2017-03-15 2021-04-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
JP7058135B2 (ja) 2017-03-15 2022-04-21 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
JP2019044965A (ja) * 2017-08-29 2019-03-22 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法

Also Published As

Publication number Publication date
DE1627852C3 (de) 1974-09-19
GB1228058A (de) 1971-04-15
DE1627852B2 (de) 1974-02-14
FR1599881A (de) 1970-07-20
DE1627852A1 (de) 1971-02-25

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