US3572216A - Fluid force applying device - Google Patents

Fluid force applying device Download PDF

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Publication number
US3572216A
US3572216A US818692A US3572216DA US3572216A US 3572216 A US3572216 A US 3572216A US 818692 A US818692 A US 818692A US 3572216D A US3572216D A US 3572216DA US 3572216 A US3572216 A US 3572216A
Authority
US
United States
Prior art keywords
piston
bore
clamp
guide member
force applying
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
US818692A
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English (en)
Inventor
Donald W Seesody
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.)
Enerpac Tool Group Corp
Original Assignee
Applied Power Industries Inc
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 Applied Power Industries Inc filed Critical Applied Power Industries Inc
Application granted granted Critical
Publication of US3572216A publication Critical patent/US3572216A/en
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
    • F15B15/063—Actuator having both linear and rotary output, i.e. dual action actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q3/00—Devices holding, supporting, or positioning work or tools, of a kind normally removable from the machine
    • B23Q3/02—Devices holding, supporting, or positioning work or tools, of a kind normally removable from the machine for mounting on a work-table, tool-slide, or analogous part
    • B23Q3/06—Work-clamping means
    • B23Q3/08—Work-clamping means other than mechanically-actuated
    • 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
    • B25B5/00—Clamps
    • B25B5/06—Arrangements for positively actuating jaws
    • B25B5/061—Arrangements for positively actuating jaws with fluid drive
    • B25B5/062—Arrangements for positively actuating jaws with fluid drive with clamping means pivoting around an axis parallel to the pressing direction
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q2703/00—Work clamping
    • B23Q2703/02—Work clamping means
    • B23Q2703/04—Work clamping means using fluid means or a vacuum
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide

Definitions

  • the splining between the relatively movable members has generally been such as to cause rotation of the clamp carrying member for the full axial movement thereof. Accordingly, the axial clamping forces imparted by the clamp throughout its effective stroke have heretofore been distorted and otherwise adversely affected by the accompanying rotational movement thereof, thus further increasing the frictional resistance to which the clamp is exposed.
  • Another object of this invention is to provide an improved force mechanism which indexes a given number of degrees in a circular arc and thereafter drives straight ahead solely in an axial direction.
  • Still another object of the invention is to provide an improved hydraulic force applying device which is entirely self-contained in an exceedingly compact and unitary package without need for any external springs or other external mechanisms and without using multiple hydraulic systems.
  • a further object of the present invention is to provide a force mechanism which is especially adaptable for use as a hydraulic swing clamp but which may be readily adapted for either pull or push types of linear actuation,
  • Force applying devices embodying the present improvements comprise generally, a body having a central bore, a cylindrical guide member non-rotatably confined within the bore of said body and having a cam slot formed in the cylindrical exterior thereof, a piston having a portion slidably confined within the bore of said body and having a bore slidably received by the cylindrical guide member, a cam follower carried by the piston and operable in the cam slot of the guide member to guide the piston in its movement, and means for axially displacing the piston along the bore of said body.
  • FIG. 1 is a central longitudinal section through a typical swing clamp having a single acting hydraulic ram and embodying the features of the present invention, the piston and clamp being shown in fully extended position;
  • FIG. 2 is a similar section through the device of FIG. 1 but showing the piston and clamp in indexed and clamping position;
  • FIG. 3 is a central longitudinal section through another embodiment of a swing clamp wherein the ram is of the double acting hydraulic type and the guide member is hollow, the piston and clamp again being shown in fully extended position; and
  • FIG. 4 is a plan view of the swing clamp with the clamping arm being shown as swung to indexed and clamping position by means of broken lines.
  • the typical force applying device shown therein as embodying the invention comprises generally a body 10 formed with a central bore 12 slidably receiving the enlarged portion 16 of a piston 14.
  • the body 10 is provided with a radial port 18 entering the bore 12 on one side of the portion 16 f the piston, the port 18 being formed in a customary manner to receive an inlet fitting adapted to be connected t a suitable source of supply of pressurized hydraulic fluid so that hydraulic fluid under pressure may be Selectively supplied to the bore 12 to forcibly axially displace the piston within the bore of the body 10.
  • the portion 16 of the piston 14 is also provided with the usual annular groove and seal 20, and the reduced portion of the piston 14 is embraced in the usual manner by a suitable sealing ring 22 confined within an annular groove at the end of the bore 12 of the body 10.
  • the piston 14 is displaced axially downwardly by fluid under pressure supplied through the port 18, and a coil spring 24 compressed between the underside of the piston portion 16 and the base 26 of the body serves to return the piston to its extended position upon release of pressurized fluid to the upper portion of the bore 12.
  • a coil spring 24 compressed between the underside of the piston portion 16 and the base 26 of the body serves to return the piston to its extended position upon release of pressurized fluid to the upper portion of the bore 12.
  • the spring 24 in torsion during movement of the piston and compression of the spring, for accomplishing this purpose, the upper end of the spring is suitably attached as at 28 to the piston portion 16 and the lower end of the spring 24 is attached as at 30 to the base 26.
  • the base 26 may be suitably secured to the end of the body 10 as by means of an annular series of machine screws 32 or the like, and the hydraulic force applying device is thus of unitary structure and is entirely selfcontained.
  • the clamping arm 34 which may be provided with a work engaging saddle 38 or the like is swung out of the way of the work upon extension of the piston 14 with the clamp being swung into working engagement upon power movement of the piston.
  • a cylindrical guide member or post 42 is non-rotatably confined within the bore 12 of the body 10, the post 42 being shown as secured at one end within a central aperture 44 of the base 26 as by means of a pin or pins 46.
  • the cylindrical exterior of the guide member 42 is formed with a cam slot 48 of a configuration such as will give the desired indexing to the piston 14 as will hereinafter become apparent.
  • the piston 14 is formed with a central bore 52 slidably received by the inner end of the guide member 42, and a cam follower 54 is carried by the piston 14 so as to be operable in and along the cam slot 48 of the guide member 42 to guide the piston 14 in its movement.
  • the cam follower 54 may conveniently comprise a ball seated within a detent 56 formed in the bore 52 of the piston 14.
  • the piston 14 is moved downwardly upon introduction of fluid under pressure via port 18 to the displacement chamber formed by the bore 12, and as it moves downwardly, the piston simultaneously indexes in a circular motion to move it through a 90 arc by reason of the ball 54 which operates in the cam groove 48. At the end of the 90 index or such other degree of are as might be desired, the piston will be caused to move in a straight line as the ball 54 follows the straight portion 58 of the cam groove.
  • the clamping arm 34 is swung from an inactive out-of-the-way position to a position wherein it is aligned with the work, and during the straight terminal portion of its movement, a clamping force is provided which is not in any way distorted or otherwise adversely affected by torsional strains.
  • the piston is free to move upwardly and such movement is provided in the embodiment of FIGS. 1 and 2 by the compression spring 24.
  • the piston 14 During its return stroke, the piston 14 obviously initially moves in a straight upward path and subsequently indexes in an are as provided by the cam 48 back to its starting position whereby the clamp 34 is out of the way of the work to permit unobstructed access to the work.
  • the force applying device shown therein is essentially the same as that shown in FIG. 1 except that hydraulic pressure is used for actuating the ram in both directions and the guide member is formed hollow for the reception of suitable implements.
  • the device still includes a body formed with a central bore 112 which slidably receives the enlarged portion 116 of the piston 114.
  • the body 110 is again provided with a radial port 118 entering the bore 112 about the portion 116 of the piston, and the usual seals 120 and 122 are again provided for sealing between the piston and the body.
  • the body 110 is formed with a second radial port 124 communicating with the lower portion of the chamber formed by the bore 112 below the enlarged portion 116 of the piston.
  • the piston is extended by introducing pressurized fluid via port 124 to the lower portion of the chamber 112, and the piston is moved axially downwardly toward clamping position by exhausting fluid from port 124 and admitting pressurized fluid through port 118 to the chamber 112 above the piston portion 116.
  • the base 126 may again be suitably secured to the end of the body 110 as by means of an annular series of machine screws 132 or the like, and an annular seal is preferably provided for sealing between the end of the body 110 and the base 126. Also, since the device of FIG. 3 is fully pressurized for actuation of the piston in both directions, it is preferable to provide a seal 128 between the bore 152 of the piston and the exterior of the guide member 142.
  • the piston 114 of the device shown in FIG. 3 is again rotatable during a portion of its axial movement, and the extending end thereof may be provided with a suitable clamping arm 134 as hereinabove described with reference to FIGS. 1 and 2.
  • the clamping arm 134 may be suitably secured as by means of a bolt 136 to the end of the piston, and the extending end of this arm may be provided with a suitable work-engaging saddle 138 or the like,
  • the indexing operation is performed by means of a cylindrical guide member 142 non-rotatably confined within the bore 112, and in this instance, the guide member 142 is shown as being in the nature of a tube or hollow cylindrical member which may be suitably adapted to receive any desired implement.
  • the tubular guide member 142 is again preferably secured within a central aperture 144 of the base 126 as by means of pins 146, and the cylindrical external surface of the member 142 is formed with a cam slot 148 of desired configuration.
  • the piston 114 is formed with a bore 152 slidably received by the end of the guide member 142 and a cam follower 154 is seated within a detent 156 formed in the bore of the piston 114.
  • a convenient cam follower is again shown as being in the nature of a ball seated within the detent 156, the ball being operable in and along the cam slot 148 as hereinabove described, the arcuate portion 148 of the cam slot terminating in a straight portion 158 so that the clamp will follow a straight line path after indexing in an arcuate path for performance of the clamping action.
  • a work holding swing clamp comprising a body having a central bore
  • a cylindrical guide member fixed within the bore of said body, said member having a cam slot therein including an arcuate portion and a straight terminal portion,
  • a piston assembly having a first portion slideably confined within the bore of said body and also having a second portion extending outwardly of said body in slideable and sealable contact therewith,
  • cam follower carried by said piston assembly and 0perable in said cam slot of said guide member to impart a rotary motion to said piston assembly on movement of said cam follower through said arcuate portion of said cam slot and axial motion to said piston assembly on movement of said cam follower through said straight terminal portion of said cam slot
  • cam follower includes a ball element confined partially within a detent formed in said piston assembly.
  • a work holding swing clamp comprising a body having a central bore
  • a hollow open ended guide member fixed within the bore of said body, said member member having a cam slot therein including an arcuate portion and a straight terminal portion,
  • a piston assembly having a first portion slideably confined Within the bore of said body and a second portion extending outwardly of said body in slideable and scalable contact therewith,
  • a cam follower carried by said piston assembly and operable in said cam slot of said guide member to impart a rotary motion to said piston assembly on movement of said cam follower through said arcuate portion of said cam slot and axial motion to said piston assembly on movement of said cam follower through said straight terminal portion of said cam slot

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Jigs For Machine Tools (AREA)
  • Clamps And Clips (AREA)
  • Actuator (AREA)
US818692A 1969-04-23 1969-04-23 Fluid force applying device Expired - Lifetime US3572216A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US81869269A 1969-04-23 1969-04-23

Publications (1)

Publication Number Publication Date
US3572216A true US3572216A (en) 1971-03-23

Family

ID=25226176

Family Applications (1)

Application Number Title Priority Date Filing Date
US818692A Expired - Lifetime US3572216A (en) 1969-04-23 1969-04-23 Fluid force applying device

Country Status (9)

Country Link
US (1) US3572216A (fr)
JP (1) JPS4941550B1 (fr)
BE (1) BE739204A (fr)
CH (1) CH502873A (fr)
ES (1) ES371356A1 (fr)
FR (1) FR2039366A1 (fr)
GB (1) GB1260870A (fr)
NL (1) NL6916181A (fr)
SE (1) SE363380B (fr)

Cited By (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3724837A (en) * 1970-09-02 1973-04-03 Dover Corp Retracting clamp
JPS4835680U (fr) * 1971-08-31 1973-04-27
JPS4841385A (fr) * 1971-09-28 1973-06-16
US3948502A (en) * 1973-11-26 1976-04-06 Spenklin Limited Power-operated work clamping devices
US4164344A (en) * 1976-12-30 1979-08-14 Deragne Maurice M Hydraulic clamping apparatus
US4265434A (en) * 1979-08-08 1981-05-05 Barry Wright Corporation Hydraulic clamp
US4351516A (en) * 1980-08-20 1982-09-28 Maschinenfabrik Hilma Gmbh Swing clamp
EP0085169A1 (fr) * 1982-01-15 1983-08-10 Maschinenfabrik Hilma GmbH Dispositif de fixation pivotant
US4560152A (en) * 1984-04-27 1985-12-24 Applied Power Inc. Swing clamp
US4583631A (en) * 1981-08-04 1986-04-22 Aioi Keiki K.K. Apparatus for positioning and clamping work clamp pallet for machine tools
US4662397A (en) * 1983-01-26 1987-05-05 Callison & Associates Limited Part. Scheduled fluid control valve
US4778163A (en) * 1987-07-31 1988-10-18 Spear Larry R Air actuated clamp
US4799657A (en) * 1987-11-24 1989-01-24 Applied Power Inc. Swing clamp
US5013015A (en) * 1990-06-11 1991-05-07 General Dynamics Corporation Mechanically actuated swing clamp
US5408737A (en) * 1993-10-04 1995-04-25 Solar Turbines Incorporated Apparatus for stabilizing a work piece of ring configuration
US5437440A (en) * 1993-08-20 1995-08-01 Compact Air Products, Inc. Swing apparatus
US5695177A (en) * 1996-11-27 1997-12-09 Vektek, Inc. Hydraulic swing clamp apparatus having speed control mechanism
US5820118A (en) * 1997-01-24 1998-10-13 Vektek, Inc. Swing clamp apparatus
US5836573A (en) * 1995-12-26 1998-11-17 Toyoda Koki Kabushiki Kaisha Clamping device
US6113086A (en) * 1996-11-06 2000-09-05 Kabushiki Kaisha Kosmek Rotary clamping apparatus
WO2001032388A1 (fr) * 1999-10-29 2001-05-10 Ichimaru Giken Co., Ltd. Dispositif de blocage automatique d'appareil pour la vulcanisation de pneumatiques
US6237905B1 (en) * 1999-04-26 2001-05-29 Erwin Halder KG Hold-down clamp
EP1264659A1 (fr) * 2001-06-05 2002-12-11 A. Römheld GmbH & Co KG Dispositif de serrage avec dispositif de serrage pivotant et bride de fixation
EP1310329A2 (fr) * 2001-11-13 2003-05-14 Kabushiki Kaisha Kosmek Moyen de serrage rotatif
US20030151183A1 (en) * 2002-02-13 2003-08-14 Kabushiki Kaisha Kosmek Operation detecting device of clamp
US20030234478A1 (en) * 2002-06-24 2003-12-25 Steele Kenneth A. Swing-arm clamp
US6886820B1 (en) * 2004-03-17 2005-05-03 Vektek, Inc. Swing clamp apparatus with spring biased cam assembly
EP1918066A1 (fr) 2006-11-03 2008-05-07 Michel Yerly Dispositif support de pièce
US20100066002A1 (en) * 2007-02-23 2010-03-18 Hideaki Yokota Device for detecting operation of clamp
CN101829970A (zh) * 2010-05-21 2010-09-15 宁海县海浴铝业有限公司 工件压紧夹具
US20100230882A1 (en) * 2009-03-10 2010-09-16 Hong Fu Jin Precision Industry (Shenzhen) Co., Ltd Clamp apparatus
US20100308580A1 (en) * 2008-02-18 2010-12-09 Takayuki Kuroda Fluid passage connection device
CN102658530A (zh) * 2012-05-10 2012-09-12 河北中迈机电设备有限公司 一种具有旋转和直线运动轨迹的液压夹具及其使用方法
CN103032404A (zh) * 2011-09-29 2013-04-10 鸿富锦精密工业（深圳）有限公司 气缸
CN103158015A (zh) * 2011-12-13 2013-06-19 春兴铸造(苏州工业园区)有限公司 一种气动旋转拉杆装置
CN103185045A (zh) * 2011-12-29 2013-07-03 富泰华工业（深圳）有限公司 气缸
US20140060220A1 (en) * 2012-08-30 2014-03-06 Hon Hai Precision Industry Co., Ltd. Positioning device and positioning mechanism for same
CN104033442A (zh) * 2013-03-05 2014-09-10 台湾气立股份有限公司 改良的转角缸结构
CN104816176A (zh) * 2015-04-30 2015-08-05 湖北三江航天万峰科技发展有限公司 一种快锁机构
US9259816B2 (en) * 2012-09-07 2016-02-16 Fu Tai Hua Industry (Shenzhen) Co., Ltd. Locking mechanism
CN105345551A (zh) * 2015-12-05 2016-02-24 重庆腾通工业设计有限公司 刹车蹄加工用固定装置
CN105729354A (zh) * 2016-04-20 2016-07-06 苏州鸿普精密模具有限公司 汽车门锁扣生产线的铜柱换位组件
CN106081603A (zh) * 2016-08-22 2016-11-09 苏州市吴中区胥口健浩五金加工厂 电磁阀阀体上料机的升料单元
CN106737276A (zh) * 2016-12-05 2017-05-31 中国航天科工集团第四研究院十七所 一种工作台用差动螺纹手动锁紧装置
CN109048541A (zh) * 2018-08-22 2018-12-21 宁波高新区意川汽车零部件有限公司 一种汽车齿轮去毛刺装置
CN111496711A (zh) * 2020-04-29 2020-08-07 博众精工科技股份有限公司 一种固定夹持机构
CN112262015A (zh) * 2018-06-12 2021-01-22 克斯美库股份有限公司 作动缸
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CN113369943A (zh) * 2021-08-16 2021-09-10 徐州汇易容金属科技有限公司 一种电动机端盖制造加工固定装置
CN113400044A (zh) * 2021-08-20 2021-09-17 徐州鑫业达环保科技有限公司 一种减速器壳体加工固定工装

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JP2005329525A (ja) * 2004-05-21 2005-12-02 Kosmek Ltd 旋回式クランプ
CN106944811A (zh) * 2016-01-07 2017-07-14 南京大量数控科技有限公司 拔销器
CN105798812B (zh) * 2016-05-30 2017-07-04 苏州赛腾精密电子股份有限公司 一种压紧机构
CN112091843A (zh) * 2020-09-07 2020-12-18 福瑞斯特汽车技术(苏州)有限公司 一种汽车不规则金属配件加工设备及加工方法
CN117381499B (zh) * 2023-12-13 2024-02-27 广东德玛士智能装备有限公司 一种转位气缸夹具

Cited By (76)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3724837A (en) * 1970-09-02 1973-04-03 Dover Corp Retracting clamp
JPS4835680U (fr) * 1971-08-31 1973-04-27
JPS4841385A (fr) * 1971-09-28 1973-06-16
US3948502A (en) * 1973-11-26 1976-04-06 Spenklin Limited Power-operated work clamping devices
US4164344A (en) * 1976-12-30 1979-08-14 Deragne Maurice M Hydraulic clamping apparatus
US4265434A (en) * 1979-08-08 1981-05-05 Barry Wright Corporation Hydraulic clamp
US4351516A (en) * 1980-08-20 1982-09-28 Maschinenfabrik Hilma Gmbh Swing clamp
US4583631A (en) * 1981-08-04 1986-04-22 Aioi Keiki K.K. Apparatus for positioning and clamping work clamp pallet for machine tools
US4508327A (en) * 1982-01-15 1985-04-02 Maschinenfabrik Hilma Gmbh Swing clamp
EP0085169A1 (fr) * 1982-01-15 1983-08-10 Maschinenfabrik Hilma GmbH Dispositif de fixation pivotant
US4662397A (en) * 1983-01-26 1987-05-05 Callison & Associates Limited Part. Scheduled fluid control valve
US4560152A (en) * 1984-04-27 1985-12-24 Applied Power Inc. Swing clamp
US4778163A (en) * 1987-07-31 1988-10-18 Spear Larry R Air actuated clamp
US4799657A (en) * 1987-11-24 1989-01-24 Applied Power Inc. Swing clamp
US5013015A (en) * 1990-06-11 1991-05-07 General Dynamics Corporation Mechanically actuated swing clamp
US5437440A (en) * 1993-08-20 1995-08-01 Compact Air Products, Inc. Swing apparatus
US5778511A (en) * 1993-08-20 1998-07-14 Compact Air Products, Inc. Swing apparatus and method
US5408737A (en) * 1993-10-04 1995-04-25 Solar Turbines Incorporated Apparatus for stabilizing a work piece of ring configuration
US5836573A (en) * 1995-12-26 1998-11-17 Toyoda Koki Kabushiki Kaisha Clamping device
US6113086A (en) * 1996-11-06 2000-09-05 Kabushiki Kaisha Kosmek Rotary clamping apparatus
WO1998023407A1 (fr) * 1996-11-27 1998-06-04 Vektek, Inc. Dispositif de serrage pivotant hydraulique dote d'un mecanisme de regulation de vitesse
US5695177A (en) * 1996-11-27 1997-12-09 Vektek, Inc. Hydraulic swing clamp apparatus having speed control mechanism
US5820118A (en) * 1997-01-24 1998-10-13 Vektek, Inc. Swing clamp apparatus
US6237905B1 (en) * 1999-04-26 2001-05-29 Erwin Halder KG Hold-down clamp
WO2001032388A1 (fr) * 1999-10-29 2001-05-10 Ichimaru Giken Co., Ltd. Dispositif de blocage automatique d'appareil pour la vulcanisation de pneumatiques
EP1264659A1 (fr) * 2001-06-05 2002-12-11 A. Römheld GmbH & Co KG Dispositif de serrage avec dispositif de serrage pivotant et bride de fixation
EP1310329A3 (fr) * 2001-11-13 2004-05-19 Kabushiki Kaisha Kosmek Moyen de serrage rotatif
EP1310330A2 (fr) * 2001-11-13 2003-05-14 Kabushiki Kaisha Kosmek Moyen de serrage rotatif
US20030090046A1 (en) * 2001-11-13 2003-05-15 Kabushiki Kaisha Kosmek Rotary clamp
EP1310330A3 (fr) * 2001-11-13 2004-05-19 Kabushiki Kaisha Kosmek Moyen de serrage rotatif
EP1310329A2 (fr) * 2001-11-13 2003-05-14 Kabushiki Kaisha Kosmek Moyen de serrage rotatif
CN100410010C (zh) * 2001-11-13 2008-08-13 克斯美库股份有限公司 转动夹具
US6902158B2 (en) 2001-11-13 2005-06-07 Kabushiki Kaisha Kosmek Rotary clamp
US20030151183A1 (en) * 2002-02-13 2003-08-14 Kabushiki Kaisha Kosmek Operation detecting device of clamp
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CN105729354A (zh) * 2016-04-20 2016-07-06 苏州鸿普精密模具有限公司 汽车门锁扣生产线的铜柱换位组件
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CN112262015A (zh) * 2018-06-12 2021-01-22 克斯美库股份有限公司 作动缸
CN109048541B (zh) * 2018-08-22 2019-11-19 宁波高新区意川汽车零部件有限公司 一种汽车齿轮去毛刺装置
CN109048541A (zh) * 2018-08-22 2018-12-21 宁波高新区意川汽车零部件有限公司 一种汽车齿轮去毛刺装置
CN111496711A (zh) * 2020-04-29 2020-08-07 博众精工科技股份有限公司 一种固定夹持机构
CN113021035A (zh) * 2021-04-22 2021-06-25 常州机电职业技术学院 一种水泵壳体零件车端面夹具
CN113369943A (zh) * 2021-08-16 2021-09-10 徐州汇易容金属科技有限公司 一种电动机端盖制造加工固定装置
CN113400044A (zh) * 2021-08-20 2021-09-17 徐州鑫业达环保科技有限公司 一种减速器壳体加工固定工装
CN113400044B (zh) * 2021-08-20 2021-11-19 徐州鑫业达环保科技有限公司 一种减速器壳体加工固定工装

Also Published As

Publication number Publication date
JPS4941550B1 (fr) 1974-11-09
FR2039366A1 (fr) 1971-01-15
CH502873A (de) 1971-02-15
NL6916181A (fr) 1970-10-27
SE363380B (fr) 1974-01-14
ES371356A1 (es) 1971-10-16
BE739204A (fr) 1970-03-02
GB1260870A (en) 1972-01-19

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