US3853037A - Pneumatic holding device - Google Patents

Pneumatic holding device Download PDF

Info

Publication number
US3853037A
US3853037A US00239143A US23914372A US3853037A US 3853037 A US3853037 A US 3853037A US 00239143 A US00239143 A US 00239143A US 23914372 A US23914372 A US 23914372A US 3853037 A US3853037 A US 3853037A
Authority
US
United States
Prior art keywords
cylinder
valve element
valve
piston
pressure
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
US00239143A
Other languages
English (en)
Inventor
E Denzler
R Widmer
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.)
HA Schlatter AG
Original Assignee
HA Schlatter AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by HA Schlatter AG filed Critical HA Schlatter AG
Application granted granted Critical
Publication of US3853037A publication Critical patent/US3853037A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • 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
    • 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
    • F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
    • F15B11/0365—Tandem constructions
    • 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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/7055—Linear output members having more than two chambers
    • F15B2211/7056—Tandem cylinders
    • 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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7716—Control of direction of movement of the output member with automatic return
    • 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
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another

Definitions

  • ABSTRACT A pneumatic holding device with at least one piston which can be impinged with a pressurized fluid medium at one face and displaceable in a cylinder against the action of a restoring force,
  • the cylinder connection leading to the impinged face of the piston can be obturated by a valve mechanism which can be closed by the impinging fluid medium.
  • the valve mechanism contains a valve body in which there is mounted a check or relief valve which opens in the direction of closing of the valve body.
  • the present invention relates to a new and improved construction of pneumatic holding or supporting device with at least one piston which can be impinged by a pressurized fluid medium at one face and which is displaceable in a cylinder against the action of a restoring or return spring.
  • Such devices are especially used in the construction of equipment where, during a given time, it is desired to generate a certain holding force, such as for instance for fixedly supporting a workpiece upon the work table of a processing machine.
  • the holding jaw connected with the piston rod should arrive at the workpiece as free as possible from impact and only thereafter should there be generated the complete holding force.
  • the holding force when no longer required, should be reduced as quickly as possible and the holding jaw should participate as quickly as possible in the return stroke.
  • the first requirement has attempted to be previously fulfilled in that the build-up of pressure in the cylinder during the work stroke has been controlled, for instance, by supplying same via a throttle location or throttle valve. Owing to the foregoing the second and third requirements could not be previously simultaneously and optimally fulfilled.
  • the cylinder was either suddenly vented, while taking into account considerable noise, or attempts were made to reduce the development of noise by slowly venting the cylinder, but ,in such case there had to be taken into account the drawback that pressure reduction only took place very slowly.
  • Another objective of the present invention relates to an improved holding device or holding unit of the aforementioned type wherein all three of the previously discussed requirements can be optimally fulfilled.
  • Yet a further significant object of the present invention relates to a new and improved construction of pneumatic holding device which is relatively simple in design, economical to manufacture, not readily subject to breakdown, requires a minimum of maintenance and servicing, and enables the holding force to be both producedin a controlled manner and quickly reduced, and affords relatively quiet operation of the system.
  • the invention is directed at designing the holding device in such a manner that the return force can be immediately effective independently of the pressure conditions prevailing at the cylin der, that is to say, independently of the momentary degree of venting, and as soon as the'device is cut-off from the pressure source and vented.
  • the proposed holding device as contemplated by this development is manifested by the features that the cylinder connection leading to the face or side of the piston which is impinged by the pressurized fluid medium can be operated by means of a valve mechanism which can be closed by the impinging fluid medium.
  • This valve mechanism has a valve body at which there is mounted a check or relief valve which opens in the closing direction of the valve body. The valve mechanism in its open position communicates the impinged face of the piston with the non-impinged face thereof.
  • FIG. 1 is a schematic longitudinal sectional view through a preferred constructional form of holding device or holding unit as designed according to the teachings of this invention.
  • FIG. 2 is a fragmentary sectional view through a portion of a modified embodiment of the invention.
  • holding device or holding unit 1 depicted in FIG. 1 will be understood to comprise a cylindrical housing 2, at one end or end face 3 of which there is formed a guide opening 5 equipped with a seal 4, this guide opening 5 guiding a piston rod 6 which extends towards the outside.
  • a cylinder 8 is arranged internally of the housing 2 while maintaining free therebetween a jacket space or outer compartment 7.
  • the cylinder 8 possesses a so-called tandem construction, that is to say, it contains two axially aligned cylinder compartments 9 and 10 separated from one another by a partition of separation wall 11.
  • a substantially hub-shaped contact or impact support 12 which, in turn, possesses a further guide bore 14 for the piston rod 6, guide bore 14 being equipped with a seal 13, as shown.
  • each of the cylinder compartments 9 and 10 there is mounted a piston plate 15 and 16 respectively so as to be movable to-and-fro.
  • a circumferential seal 17 by means of which, together with the associated piston plate, each cylinder compartment 9 and 10 is subdivided into a chamber or section 9a and 10a respectively which is impinged by pressurized fluid medium and a chamber or section 9b and 10b respectively which is not impinged by such fluid medium.
  • the piston plates and 16 are seated upon the common piston rod 6 in which between both piston plates 15 and 16, there is formed an axial bore 18 which at one end has ports or throughflow openings 19 leading radially out of thepiston rod 6, as shown. Bore 18 and ports 19 thus always flow communicate with one another the chambers 9a and 10a of the cylinder compartments 9 and 10 respectively which are impinged by the pressurized fluid medium.
  • a pressure or compression spring 20 which in the pressureless condition of the system retains the piston 70 in the position depicted in FIG. 1.
  • connection port or opening 22 is constructed as a valve seat 23 for a valve plate 24 of a valve mechanism or unit 71.
  • a suitable sealing ring 25 is mounted at the flat face 24a of the valve plate 24 confronting the valve seat 23.
  • Valve plate 24 also carries a seal 29 at its periphery and, similar to the piston plates, is mounted to be displaceable longitudinally a valve compartment 27 formed at the other end face 26 of the housing 2.
  • a connection opening or port 28 leads to the valve compartment 27 and by means of which the illustrated holding device or unit 1 can be connected via a schematically illustrated compressed air conduit 31 and a suitable valve, such as the electromagnetic 3/2-way valve 32 with a source of pressurized medium e.g. compressed air source 33.
  • a suitable valve such as the electromagnetic 3/2-way valve 32 with a source of pressurized medium e.g. compressed air source 33.
  • the fluid medium-impinged chambers 9a and 10a of both cylinder compartments 9 and 10 respectively are always in flow communication via the bore 18 and the throughflow openings or ports 19 at the piston rod 6, the non-impinged chambers or sections 9b and 10b of both cylinder compartments 9 and 10 respectively, are likewise continuously in flow communication with one another.
  • the jacket compartment 7 is continuously connected via a small opening 36 with the ambient air.
  • the mode of operation of the illustrated embodiment of holder device or holder unit is as follows: If the valve 32 is moved out of its illustrated position, then there is connected the compressed air source 33. Thus initially the valve plate 24, under the action of the incoming compressed air, is displaced towards the left in its valve closing or closure position upon the valve seat 23. Consequently, the connection 22 is cut-off from the jacket 4 or outer compartment 7.
  • the check or relief valve opens and in accordance with its throughflow capacity compressed air flows to the impinged chambers 9a and 10a of the cylinder compartments 9 and 10 respectively. The thus occuring pressure build-up, after overcoming the force of the spring 20, displaces the piston plates 15 and 16 towards the left until the piston plate 16 comes to bear against the free end face of the contact piece or stud 12. When this condition has been reached then the pressure in the fluid mediumimpinged chambers of the cylinder compartments 9 and 10 corresponds approximately to the pressure delivered by the compressed air source 33.
  • the check valve 30 opens for pressure equalization between both faces of the valve plate 24.
  • the volume content of the jacket compartment 7 with regard to the inner volume or swept capacity of the cylinder 2 and with regard to the throughflow-capacity of the opening 36 are accommodated to one another in such a manner that presupposing a periodic work stroke the jacket compartment 7 so to speak acts like an expansion chamber or surge tank and venting occurs continuously via the opening 36.
  • holder unit or holder device of this invention possesses a still further advantage. Since the return stroke of the piston 70 embodying the piston plates 15, 16 takes place at a higher pressure than the atmospheric pressure of the surroundings, during the return stroke there does not occur any suction action upon the non-impinged face of the piston plates 15, 16. Accordingly, measures are also provided which ensure that no contaminants are sucked-up from the surroundings which, as is well known, could considerably reduce the longevity of the seals, in this case the seals 4, 13 and 17. i
  • the invention is not limited to the exemplary illustrated tandem construction. If it is imagined for instance for the illustrated embodiment of holder device 1 that the opening 35 is closed, the bore 18 closed, there is omitted the piston plate and the partition wall 11 is displaced to the left and coincides with the end wall 3, then there is realized a construction of holder device which as far as its external dimensions are concerned is approximately of the same size, however, has approximately twice the stoke with approximately half the force.
  • FIG. 2 of the drawings there is illustrated a variant embodiment of inventive holder device or unit in which the valve mechanism 71 embodying the components 23, 24, is indirectly controlled by the impinging fluid medium, i.e. is servo-controlled.
  • FIG. 2 more specifically there will be recognizeda portion of the housing 2 in which there is arranged the cylinder 8 while again maintaining free therebetween the jacket or outer compartment 7.
  • the closure flange 21 of the cylinder 8 is constructed in the same manner as for the embodiment of FIG. 1.
  • the valve plate 24 on the other hand is not only mounted so as to be displaceable to-and-fro within the valve compartment 27, rather additionally is subjected to the action of compression or pressure springs which strive to displace valve plate 24 to the right of FIG.
  • a piston extension or projection 41 is formed at the valve plate 24, which, in turn, is displaceably mounted in a piston compartment 42 and leads to the check or relief valve 30 via the onethroughflow opening 43 communicating with such check valve.
  • the piston projection 41 carries at one end a seal 44 which is destined to cooperate with the throughflow opening 46 at the piston compartment 42, which throughflow opening 46 was a valve seat 45.
  • the throughflow opening 46 opens into the inlet 47 to the holder device which is directly connected with a compressed air network.
  • a further throughflow opening 48 leads from this inlet 47 into the valve compartment 49 of a solenoid valve 50. From this valve compartment 49 there leads a further continuously open throughflow opening 51 into the valve compartment 27 as well as past the plunger-type armature 52 of the solenoid valve which is subjected to the action of a compression or pressure spring 53, to a throughflow opening or channel 54 which opens into the jacket or outer compartment 7.
  • the plunger-typearmature 52 is provided at both' end faces with the seals SSwhich serve to close the mouths of the throughflow openings 48 and 54 depending upon the position of such armature 52.
  • the mode of operation of this embodiment of the invention is as follows: It is assumed that the inlet 47 is directly connected to a compressed air source and that the coil of the solenoid valve 50 is not excited. Accordingly, the plunger-type armature 52 is in its extended position and closes by means of its seal 55 the mouth of the throughflow opening 48.
  • the throughflow openings 51 and 54 are in communication with one another and therefore also the face 24b of the valve plate 24 facing away from the cylinder 8 with the face 24a of the valve plate 24 confronting the cylinder 8.
  • the compression springs 40 to raise the valve plate 24 from the valve seat 23 and the therewith connected piston 41 to shift until the throughflow opening 46 is closed by the seal 44.
  • the compression or pressure springs 40 are designed such that their force overcomes the force of the pressure at the inlet 47 upon the surface circumscribed by the seal 44 of the piston extension 41. If however the inlet 46 to the piston compartment 42 is closed then no compressed air arrives at the throughflow opening 43 and therefore at the cylinder 8. The holder unit remains in its retracted position.
  • vent opening 36 which connects the jacket or outer compartment 7 functioning as the expansion chamber with the external air
  • a pneumatic holding device comprising: a cylinder having a first and an opposite second end;
  • piston rod for supporting and guiding pistons, said piston rod extending through both said piston compartments toward said cylinder first and second ends;
  • both said pistons being sealingly movable through the respective said compartments and each said piston thereby divides its respective said compartment;
  • said pistons being spaced apart on said rod and being simultaneously movable by said rod;
  • said pistons and said piston rod being shiftable axially through said cylinder toward said cylinder ends; both said pistons having a respective first face facing toward said cylinder first end and having a respective second face facing toward said cylinder second end; means normally biasing said pistons toward said cylinder first end;
  • pressurized fluid inlet having a first cross section and being connected to said cylinder; a valve located between said pressurized fluid inlet and said cylinder; said valve having an inlet communicating with said fluid inlet and an outlet communicating with said cylinder; said valve outlet communicating into said cylinder first compartment at a location such that pressure may be applied through said fluid inlet to the said first face of said first piston; a pressure transmitting conduit communicating between said valve outlet and said cylinder second compartment at a location such that pressure may be applied through said fluid inlet to said first face of said second piston;
  • valve comprising: a valve element compartment ofa second cross section larger than said first cross section of said pressurized fluid inlet; a movable valve element in said valve element compartment, said valve element having a cross section such that it is sealably movable through said valve element compartment and being movable in said valve element compartment toward and away from said cylinder under the influence of pressure in said valve element compartment and in said cylinder; said valve element having a pressure inlet side facing toward said valve inlet and said fluid inlet and having a pressure outlet side facing toward said valve outlet and said cylinder;
  • said cylinder carrying a valve seat for said valve element against which said valve element pressure outlet side is scalable; when said valve element pressure outlet side, which said section has a third cross-section which is smaller than said valve element second cross-section and which said valve element section is exposed to the sections of said first and said second compartments and thereby is exposed to the cylinder pressure at said first side of both said pistons; with said valve element moved through its said compartment onto said valve seat, the entire said pressure inlet side of said valve element is exposed to the inlet pressure in said fluid inlet and in said valve element compartment;
  • pressure equalization conduit connected to both said piston compartments in said cylinder at respective locations in said compartments such that said pressure equalization conduit is always at the pressure at both said piston second faces; said pressure equalization conduit also communicating with said piston compartments at respective locations so that it is in communication with said first sides of therefor;
  • said equalization conduit passes said tending across said valve element compartment to valve element and said valve seat, such that with join said fluid inlet with said cyliner; a one-way said valve element on said valve seat, said equalizacheck valve in said narrowed passage permitting tion conduit is blocked, and with said valve eleonly inlet to said cylinder through said narrowed ment off said valve seat, said equalization conduit passage; is open; said cylinder carrying a valve seat for said valve elecylinder housing surrounding and spaced from said ment against which said valve element pressure cylinder and in which said cylinder is mounted and outlet side is scalable; when
  • a pneumatic holding device comprising: a cylinder having a first and an opposite second end;

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Jigs For Machine Tools (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
US00239143A 1971-04-06 1972-03-29 Pneumatic holding device Expired - Lifetime US3853037A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH507171A CH518158A (de) 1971-04-06 1971-04-06 Pneumatisches Halteaggregat

Publications (1)

Publication Number Publication Date
US3853037A true US3853037A (en) 1974-12-10

Family

ID=4287451

Family Applications (1)

Application Number Title Priority Date Filing Date
US00239143A Expired - Lifetime US3853037A (en) 1971-04-06 1972-03-29 Pneumatic holding device

Country Status (11)

Country Link
US (1) US3853037A (enExample)
AU (1) AU464983B2 (enExample)
BE (1) BE780994A (enExample)
CA (1) CA947590A (enExample)
CH (1) CH518158A (enExample)
DE (1) DE2211909A1 (enExample)
FR (1) FR2132061B1 (enExample)
GB (1) GB1352963A (enExample)
IT (1) IT960307B (enExample)
NL (1) NL7202788A (enExample)
SE (1) SE382770B (enExample)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4204513A (en) * 1978-11-15 1980-05-27 California Controls Company Hydraulic safety mechanism
US4318550A (en) * 1979-10-26 1982-03-09 Central Hydraulics Co. Hydropneumatic system
US5031508A (en) * 1990-09-05 1991-07-16 Emhart Inc. Rivet setting tool
US5615595A (en) * 1995-06-30 1997-04-01 Bettis Corporation Tandem cylinder control
US5893317A (en) * 1996-12-18 1999-04-13 Netter Gmbh Pneumatic beater
US6314862B1 (en) * 2000-01-24 2001-11-13 Retterer Manufacturing Co., Inc. Combination cylinder and pistons
CN102554662A (zh) * 2011-12-22 2012-07-11 上海三一精机有限公司 工作台自定心及工件夹紧装置及其控制方法
CN111906711A (zh) * 2020-07-31 2020-11-10 芜湖芬特勘测服务有限公司 一种基于接近式检测的缓冲式夹具装置及其调控系统
CN112414358A (zh) * 2020-12-08 2021-02-26 安徽信息工程学院 一种高精度量革机

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2431625A2 (fr) * 1978-07-17 1980-02-15 Polymatic Sa Tete de bridage de securite a organe de controle d'alimentation incorpore
HU187363B (en) * 1981-04-16 1985-12-28 Autoipari Kutato Intezet Pneumatic working cylinder woth four piston particularly for stage selector mechanism of motor vehicle
WO1982004415A1 (en) * 1981-06-11 1982-12-23 Richard Furneaux Kinnersly Mechanism and device for applying a force,in particular the application of a manually-generated force to a workpiece,for example in the separation of co-operating male and female parts
DE3408909A1 (de) * 1984-03-10 1985-09-12 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Hydraulischer antrieb
DE3532514C1 (de) * 1985-09-12 1987-04-23 Bode & Co Geb Antriebsvorrichtung fuer eine Drehsaeule,insbesondere zur Bewegung von Schwenktuerfluegeln an Kraftfahrzeugen
IT1238427B (it) * 1990-01-10 1993-07-26 Dispositivo attuatore pneumatico temporizzatore
DE4233115C2 (de) * 1992-10-02 1995-04-13 Ulrich Keller Hydraulisch betätigte Verriegelungs- und Kupplungsvorrichtung
DE19602390A1 (de) * 1995-01-28 1996-08-01 Ulrich Keller Arbeitszylinder
DE29902773U1 (de) 1999-02-17 1999-05-12 Bümach Engineering International B.V., Emmen Druckmittelbetriebener Arbeitszylinder mit fluidischer Wegsperrung
DE202007015770U1 (de) * 2007-11-09 2009-03-19 Gebr. Bode Gmbh & Co. Kg Antriebsvorrichtung für Ein- und Ausstiegseinrichtungen

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1441759A (en) * 1920-03-04 1923-01-09 Gen Electric Valve
US1681579A (en) * 1927-03-25 1928-08-21 Westinghouse Air Brake Co Brake cylinder
US2888909A (en) * 1953-12-24 1959-06-02 Gratzmuller Jean Louis Liquid dumping valve arrangement for a hydraulic jack
US3307454A (en) * 1964-06-19 1967-03-07 Atlas Copco Ab Rotary piston machines and cylinder housings
US3456561A (en) * 1967-09-25 1969-07-22 William Laikam Jr Air pressure actuated cylinder unit
US3464321A (en) * 1966-11-29 1969-09-02 Bruno Piotrowski Jr One-way directional fluid control valve and system
US3485141A (en) * 1967-08-28 1969-12-23 Sargent & Co Multipiston pressure cylinder for tools
US3584639A (en) * 1965-06-08 1971-06-15 Gasudarstuenny Nii Orch Polvpr Discrete-operating pneumatic element for logical function

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH485948A (de) * 1966-12-14 1970-02-15 Frieseke & Hoepfner Gmbh Schubkolbentrieb mit Eilhub und Krafthub

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1441759A (en) * 1920-03-04 1923-01-09 Gen Electric Valve
US1681579A (en) * 1927-03-25 1928-08-21 Westinghouse Air Brake Co Brake cylinder
US2888909A (en) * 1953-12-24 1959-06-02 Gratzmuller Jean Louis Liquid dumping valve arrangement for a hydraulic jack
US3307454A (en) * 1964-06-19 1967-03-07 Atlas Copco Ab Rotary piston machines and cylinder housings
US3584639A (en) * 1965-06-08 1971-06-15 Gasudarstuenny Nii Orch Polvpr Discrete-operating pneumatic element for logical function
US3464321A (en) * 1966-11-29 1969-09-02 Bruno Piotrowski Jr One-way directional fluid control valve and system
US3485141A (en) * 1967-08-28 1969-12-23 Sargent & Co Multipiston pressure cylinder for tools
US3456561A (en) * 1967-09-25 1969-07-22 William Laikam Jr Air pressure actuated cylinder unit

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4204513A (en) * 1978-11-15 1980-05-27 California Controls Company Hydraulic safety mechanism
US4318550A (en) * 1979-10-26 1982-03-09 Central Hydraulics Co. Hydropneumatic system
US5031508A (en) * 1990-09-05 1991-07-16 Emhart Inc. Rivet setting tool
EP0475678A1 (en) * 1990-09-05 1992-03-18 Emhart Inc. Rivet setting tool
US5615595A (en) * 1995-06-30 1997-04-01 Bettis Corporation Tandem cylinder control
US5893317A (en) * 1996-12-18 1999-04-13 Netter Gmbh Pneumatic beater
US6314862B1 (en) * 2000-01-24 2001-11-13 Retterer Manufacturing Co., Inc. Combination cylinder and pistons
CN102554662A (zh) * 2011-12-22 2012-07-11 上海三一精机有限公司 工作台自定心及工件夹紧装置及其控制方法
CN102554662B (zh) * 2011-12-22 2014-10-22 上海三一精机有限公司 工作台自定心及工件夹紧装置的控制方法
CN111906711A (zh) * 2020-07-31 2020-11-10 芜湖芬特勘测服务有限公司 一种基于接近式检测的缓冲式夹具装置及其调控系统
CN112414358A (zh) * 2020-12-08 2021-02-26 安徽信息工程学院 一种高精度量革机

Also Published As

Publication number Publication date
GB1352963A (en) 1974-05-15
FR2132061A1 (enExample) 1972-11-17
IT960307B (it) 1973-11-20
DE2211909A1 (de) 1972-10-19
BE780994A (fr) 1972-07-17
CA947590A (en) 1974-05-21
CH518158A (de) 1972-01-31
SE382770B (sv) 1976-02-16
FR2132061B1 (enExample) 1977-03-18
AU4028472A (en) 1973-10-25
AU464983B2 (en) 1975-08-21
NL7202788A (enExample) 1972-10-10

Similar Documents

Publication Publication Date Title
US3853037A (en) Pneumatic holding device
US3818801A (en) Fluid actuating mechanism having alternatively selectable fast and slow modes of operation
US5894781A (en) Hydraulic hammer
US20110265544A1 (en) Hydraulic cylinder for a hydraulic drawing cushion
US2804055A (en) Fluid motor with piston actuated valve means
GB2045899A (en) Electromagnetically operated valves
GB1092406A (en) Evacuating valve assembly for a hydraulic jack
US4706548A (en) Two-hand safety control mechanism
US3597121A (en) Air-driven hydraulic pump
US3213762A (en) Hydraulic devices for reciprocating elements having high inertia
US3817152A (en) Hydraulic jack
US4729289A (en) Power brake booster for an automotive vehicle
US3405606A (en) Control of double-acting pressure medium energized servo-motors
ES8603048A1 (es) Perfeccionamientos en valvulas accionadas por un fluido a presion
US4050356A (en) Apparatus for controlling a fluid medium
US3744374A (en) Hydraulic valve control apparatus
US4114515A (en) Adjustable self-reciprocating operator
GB1139604A (en) Fluid motor and control valve assembly
US4348160A (en) Metering syringe
US4531540A (en) Servocontrolled pressure limiting valve
EP0428406A1 (en) Reciprocating actuator
US3776101A (en) Control device for controlling a pneumatic piston
JP2002527296A (ja) 流体駆動式作動装置
KR102016852B1 (ko) 배관용 자동 밸브
US3522821A (en) Pilot actuated valve