WO1991001856A1 - Dispositif actionne pneumatiquement pour la deformation plastique, en particulier pour le poinçonnage - Google Patents

Dispositif actionne pneumatiquement pour la deformation plastique, en particulier pour le poinçonnage Download PDF

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Publication number
WO1991001856A1
WO1991001856A1 PCT/EP1990/001157 EP9001157W WO9101856A1 WO 1991001856 A1 WO1991001856 A1 WO 1991001856A1 EP 9001157 W EP9001157 W EP 9001157W WO 9101856 A1 WO9101856 A1 WO 9101856A1
Authority
WO
WIPO (PCT)
Prior art keywords
magnet
cylinder
guide
adjusting
pneumatically operated
Prior art date
Application number
PCT/EP1990/001157
Other languages
German (de)
English (en)
Inventor
Theo Vogt
Original Assignee
J. Lorch Ges. & Co. Kg
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 J. Lorch Ges. & Co. Kg filed Critical J. Lorch Ges. & Co. Kg
Publication of WO1991001856A1 publication Critical patent/WO1991001856A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/10—Riveting machines
    • B21J15/16—Drives for riveting machines; Transmission means therefor
    • B21J15/18—Drives for riveting machines; Transmission means therefor operated by air pressure or other gas pressure, e.g. explosion pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/24—Drives for hammers; Transmission means therefor for power hammers operated by steam, air, or other gaseous pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D5/00—Centre punches
    • B25D5/02—Automatic centre punches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B44—DECORATIVE ARTS
    • B44B—MACHINES, APPARATUS OR TOOLS FOR ARTISTIC WORK, e.g. FOR SCULPTURING, GUILLOCHING, CARVING, BRANDING, INLAYING
    • B44B5/00—Machines or apparatus for embossing decorations or marks, e.g. embossing coins
    • B44B5/0061—Machines or apparatus for embossing decorations or marks, e.g. embossing coins characterised by the power drive

Definitions

  • the invention relates to a pneumatically operated device for plastic deformation, in particular for punching, punching, punching, fitting, riveting, flanging and the like.
  • a striking piston which can be moved in a guide cylinder between two positions and which can be moved by a holding device having at least one holding magnet a release position located at one end of the guide cylinder is held, a deformation tool slidably received at the other end of the guide cylinder, which controls a control valve of a pulse device by means of axial loading via a triggering device, through which the percussion piston can be pressurized on the face side and is released when the holding force of the magnet is exceeded, whereby a percussion pulse is transmitted to the deformation tool and a restoring element through which the percussion piston again engages with the holding device is feasible.
  • Such a compressed air powered impact tool is known from CH-PS 655 680.
  • a percussion piston is shown there, which is slidably mounted in a cylinder space which can be acted upon by compressed air from both ends.
  • the percussion piston is held in the rest position by a magnet at one end of the cylinder.
  • At the other end of the cylinder there is a displaceably mounted tappet, one end of which carries a deformation tool and has two radial flanges which can be displaced into adapted cylindrical cavities in the tappet guide between an upper and lower position.
  • ⁇ ßr plunger is held in a rest position by a compression spring acting in the direction of impact.
  • the position of the tappet flanges in the cavities changes, so that a control device having a plurality of control valves is actuated via compressed air and one end face of the percussion piston is pressurized with air through a bore in the magnet. After overcoming the magnetic holding force, the percussion piston detaches from the magnet and hits the plunger. Then the compressed air is timed Valve of the control device, which in turn is controlled by the position of the tappet flanges, in the other end of the cylinder space, whereby the percussion piston is moved back to its rest position on the magnet.
  • the impact tool described has a number of disadvantages.
  • the impact force of the impact piston can only be changed to a limited extent via the amount of pressure applied. Only when sufficient pressure to overcome the magnetic holding force is built up on the end face of the percussion piston does the percussion piston loosen so that it is pressurized with high pressure from the beginning of its stroke, but the time of detachment and thus the percussion force is dependent on the magnetic holding force.
  • a pressure force that is greater than the magnetic holding force By suddenly applying a pressure force that is greater than the magnetic holding force, a higher impact pulse and, accordingly, a greater impact force can be generated, but a shock pulse whose impact force is lower than the magnetic holding force can never be triggered.
  • Another major disadvantage is that a complicated control device having a plurality of pulse valves is provided in order to pressurize or ventilate the corresponding cavities in the tappet guide and the pressure chamber at the right time, depending on the position of the tappet and the percussion piston.
  • a pneumatic nail hammer device which also have a percussion piston, but which is in the locked position either via compressed air or is held by a mechanical locking device.
  • the striking stroke is also not triggered only when the embossing tool comes into contact with the workpiece, but rather via a manual device, so that there is an unintentional triggering with a corresponding risk to the operator.
  • the invention is based on the object of designing a device of the type mentioned at the beginning in such a way that a variable triggering of a pulse is possible, i.e. the impact power can be changed, - in addition, the aim is to simplify the triggering control.
  • the holding device has an adjusting device for changing the holding force between the magnet and the percussion piston located in the release position, and that the pulse device has a pressure chamber which can be pressurized and vented via a single control valve.
  • This enables a variable setting of the percussion piston pulse, and the available impact / deformation energy of the deformation tool on the workpiece can be varied. If a compression spring of low spring force is arranged between the percussion piston and the lower part of the guide cylinder in a known manner, a valve reversal can be carried out to reset the percussion piston Holding device is omitted, whereby the valve control can be simplified considerably.
  • the pressure chamber of the pulse device in which the pressure required to generate the impact pulses is built up, can thereby be pressurized or vented via a single control valve.
  • a larger amount of air can also be compressed so that, in comparison to the impact tool from CH-PS 655 680, a larger air mass under impulse pressure also drives the percussion piston.
  • Another advantage of this device is that the number of moving parts in the device is greatly reduced and the susceptibility to damage is reduced. Because the pressure that can be generated in the pressure chamber can be varied by changing the magnetic holding force, the impact force of the impact piston on the deformation tool is determined.
  • a particularly simple embodiment provides that the distance between the magnet and the percussion piston in the release position can be changed by the adjusting device. This provides an effective and simple method of how the holding force of the magnet can be changed compared to the applied compression pressure of the pressure chamber.
  • the holding device can have a magnetic cylinder, in which the magnet can be axially displaced to a limited extent in a receiving recess It is recorded that the percussion piston rests in its release position on a bearing face of the magnetic cylinder which has the receiving recess and that the distance of the magnet from the bearing face can be changed by the adjusting device.
  • the magnetic cylinder can have at least one receiving bore in which a fastening element connected to the magnet, in particular a fastening screw, is guided so as to be axially displaceable, and that the magnet counteracts the action of at least one compression spring by engagement of the adjusting device with the fastening element or the magnet in a desired distance to the contact face of the magnet cylinder can be achieved, a so-called "floating support" of the magnet is achieved in the receiving recess, against the action of the compression spring simply adjusting a suitable element of the adjusting device is sufficient to change the distance of the magnet to the contact face .
  • the holding device can have four preferably cylindrical magnets which are accommodated in four receiving recesses arranged equidistantly from one another about the longitudinal axis of the magnet cylinder, so that the magnets can be engaged by them
  • Fastening screws are axially displaceable, the fastening screws through corresponding mounting holes in the rear end wall of the magnetic cylinder in particular, the spacer sleeves can run and are axially movable against the action of compression springs, which are each arranged around the spacer sleeves and non-positively arranged between the rear end wall and a screw holder receiving the screw heads, and that the distance of all magnets to the system end face can be changed simultaneously by the engagement of the adjusting device is.
  • the arrangement of the compression springs outside the receiving recess around the fastening screws ensures that the entire area of the receiving recesses can be used as a displacement area for the magnets.
  • the distance between the magnets and the face of the system can thus be changed by simply axially moving the screw holder.
  • the pressure chamber can be arranged in an axial extension of the guide cylinder within a cylindrical connecting sleeve, the upper end of which is closed by a closure body and the likewise closed lower end of which is at least one pressure bore has, which connects the pressure chamber with the interior of the guide cylinder. This also gives the device a handy shape.
  • the magnetic cylinder can also be used as a connecting element between the connecting sleeve and the guide cylinder for this purpose, the magnetic cylinder has two external thread regions separated from one another by a peripheral flange, which engage in corresponding internal threads for the connecting sleeve or the guide cylinder.
  • the rear end wall of the magnetic cylinder thus forms a lower end of the pressure chamber provided with at least one pressure bore.
  • the control valve can advantageously be designed in the interior of the closure body, in particular in the form of a 3/2-way valve, and can be connected to a compressed air source via a gas connection piece also provided on the closure body.
  • a gas connection piece also provided on the closure body.
  • the control valve it is connected to the triggering device.
  • the pressure chamber is only pressurized when the triggering device is actuated, so that the impact piston is additionally secured in its triggering position.
  • the release device contains the deformation tool, a return spring which is in engagement therewith and a switching rod arranged between the control valve and the deformation tool.
  • control valve can have a cylindrical valve control body which axially in a guide bore via the switching rod against a spring is displaceable, so that when the deformation tool engages with the workpiece to be machined when the shift rod is in the retracted position
  • Valve control body holds a closing cone against the action of spring force in a compressed air release position, as a result of which compressed air enters the guide bore via a gas connecting piece and the pressure chamber is pressurized via a supply channel and that when the selector rod is released, the valve control body and the closing cone are in a closed position, whereby the guide bore is separated from the compressed air source and the pressure chamber is vented via a ventilation duct.
  • the adjusting device can have an adjusting member, in particular an adjusting nut, which is axially displaceable with respect to the magnetic cylinder, which can be adjusted via an adjusting member, in particular an adjusting pin Fastening elements or the magnet engages so that the distance between the magnet and the percussion piston in the release position can be steplessly adjusted between two positions by actuating the adjusting member.
  • the adjusting nut can be a union nut, and this is in engagement with a thread formed at the rear end of the closure body
  • a simple embodiment of the adjusting member is provided, two further Adjusting pins can be placed in a sealing arrangement in axial guide bores of the closure body, so that their ends are in engagement with the adjusting nut and the screw holder, so that the magnet (s) counter to the force of the compression springs in it by rotating the adjusting nut Distance to the front face of the magnetic cylinder can be changed.
  • an deliverable pneumatic device can accommodate the device housing, consisting of guide cylinder and guide sleeve, in an accommodating guide, in particular a cylinder housing, in an axially movable manner, and that the device housing can be moved continuously between a rest position and a working position, in which the deformation tool is in engagement with a workpiece to be machined, by a drive device.
  • the end walls of the cylinder housing are penetrated by both ends of the device housing in a sealing system and that the device housing can have a radially expanded area, in particular a peripheral flange, which can be sealingly guided on the inner peripheral wall of the cylinder housing and thereby forms two annular pressure chambers it is possible by alternating Pressurizing the pressure chambers to move the device housing in the cylinder housing between the working position and the rest position, whereby a simple pneumatic feed device is provided.
  • the cylinder housing can be mounted on a connection plate by means of fastening elements.
  • the device housing can have an axially displaceably arranged stop element which can be fastened in an axial position to the device housing, in particular in the form of a clampable stop.
  • the device housing can be secured against rotation in the cylinder housing by engaging the stop element in a guide of the stop plate.
  • the magnetic cylinder can have the peripheral flange as an integral part, a separate peripheral flange can be avoided.
  • Figure 1 shows a longitudinal section through a pneumatically operated according to the invention Device used, among other things, for punch stamping.
  • Figure 2 shows a guided along the line II-II
  • Figure 3 shows a guided along the line III-III
  • Figure 4 shows a guided along the line IV-IV
  • FIG. 5 shows a longitudinal section through an deliverable pneumatic device which can be axially displaced in a pressure-operated manner in a cylinder housing.
  • Figure 1 shows a cylinder-shaped embodiment of a pneumatically operated device for the plastic deformation of workpieces.
  • a pneumatically operated device for the plastic deformation of workpieces.
  • Such a device is used in particular for punch stamping. It is also possible to use this as a punching, caulking, pressing, riveting or flanging device and the like. That is, wherever there is a plastic deformation by hitting one Deforming tool to be executed on a workpiece.
  • the device housing 1 is formed by two cylindrical sleeves, the guide cylinder 2 and the connecting sleeve 3 which can be connected to this end face 3.
  • the device housing 1 is closed at its rear end by a closure body 4 in a sealing manner.
  • the likewise cylindrical closure body 4 is screwed into the rear end of the connecting sleeve 3 by means of a fine thread and sealed by a housing seal 5 located in a U groove.
  • the device housing 1 has a guide body 6 which can be screwed into the guide cylinder 2 and which has a centrally located, axial through-bore.
  • a deformation tool 7 is axially displaceably received in this bore; the deformation tool 7 shown here is designed in the form of a firing pin, whereby other types of design adapted to the intended use can be used. It is also conceivable to screw a deformation attachment adapted to the respective purpose onto the tip of the deformation tool 7 or to fasten it in some other way.
  • a damping ring 8 Arranged between the deformation tool head 7 'and the guide body 6 there is a damping ring 8 made of a hard elastomeric material in the interior of the guide cylinder 2.
  • the deformation tool head 7 ′ is held in contact with the damping ring 8 by a return spring 9, which is arranged at the front end of the guide body 6 in a recess 10 around the deformation tool shaft T and engages with the deformation tool 7 by means of a snap ring attached support ring 11 is engaged.
  • the deformation tool 7 is thus limited axially displaceable against the force of the return spring 9 in the through hole.
  • a cylindrical percussion piston 12 which is preferably made of an extremely hard material such as stainless steel or the like. This is axially movable and is in engagement with the
  • Deformation tool 7 can be brought against the only weak restoring force of a return spring 13.
  • the percussion piston 12 has piston sealing rings 5 ′ which are arranged in circumferential grooves and which are intended to largely ensure that the percussion piston 12 seals against the inner wall of the guide cylinder 2.
  • the magnetic cylinder 14 (FIG. 3, 4) between the guide cylinder 2 and the connecting sleeve 3.
  • the magnetic cylinder 14 is used as a connecting piece between the connecting sleeve 3 and the guide cylinder 2, for this purpose the magnetic cylinder 14 has two external thread areas which are separated from one another by a peripheral flange 15 and which engage in corresponding internal threads of the connecting sleeve 3 or the guide cylinder 2.
  • housing seals 5 are provided for this.
  • the peripheral flange 15 has the same outer diameter as the connecting sleeve 3 and guide cylinder 2.
  • the Circumferential flange 15 is omitted or, as will be shown later, has a substantially larger outer diameter.
  • the magnetic net 14 has four receiving recesses 16 which are arranged equidistantly from one another about the longitudinal axis of the device housing 1 and which, beginning with the guide cylinder on a contact face 17, extend cylindrically into the interior of the magnet cylinder 14.
  • cylindrical magnets 18 are also axially displaceable to a limited extent, and their length is smaller than the receiving recesses 6.
  • the magnets 18 are each axially displaceably held by fastening screws 19 which engage in them and are held in the rear end wall by corresponding axial receiving bores 20 21 of the magnetic cylinder 14.
  • the heads of the fastening screws 19 are arranged sunk in a screw holder 22 at a distance from the rear end wall 21, the screw shafts running within spacer sleeves 23, which lie on the end face between the screw holder 22 and the magnet 18 through the mounting holes 20.
  • the starting position of the magnets 18 at the bottom of the receiving recess 16 is secured by the engagement of pressure springs 24 arranged between the rear end wall 21 of the magnet cylinder 14 and the screw holder 22 around the spacer sleeves 23.
  • a holding device 25 is formed, through which the percussion piston 12 by the magnetic holding force of the magnets 18 in one Trigger position is held on the front face 17 of the magnetic cylinder 14.
  • the distance between the magnets 18 and the end face 17 of the contact can be changed by means of an adjusting device 26.
  • the change in distance of the magnets 18 in relation to the percussion piston 12 only takes place in a small millimeter range, since this is sufficient to influence the magnet holding force sufficiently.
  • the individual magnets 18 can also be replaced by a single annular magnet. If electromagnets are used, another type of change in the holding force between magnet 18 and percussion piston 12 is also conceivable, it not being necessary here to change the distance of the magnets 18 in the magnetic cylinder 14.
  • a pressure chamber 31 is formed within the connecting sleeve 3 between the rear end wall 21 of the magnetic cylinder 14 and the closure body 4. It forms the actual core of a pulse device 30, which further includes a compressed air source, not shown, which can be connected to the pressure chamber 31 via a gas connection piece 32 and a control valve 33.
  • the magnetic cylinder 14 has axial pressure bores 34 which connect the pressure chamber 31 to the interior of the guide cylinder 2 (FIG. 2).
  • the control valve 33 is formed in the interior of the closure body 4 in the form of a 3/2-way valve and has a cylindrical Valve control body 35 which is received in a guide bore 36 extending through the closure body 4 in the longitudinal center axis.
  • a closing cone 37 in an enlarged area of the guide bore 36, which can be moved against a spring by the valve control body 35 from its position closing the guide bore 36, so that 32 compressed air into the interior of the gas connection stub Guide hole 36 "" » can get.
  • the guide bore 36 is in a known manner via a supply channel 38 with the pressure chamber 31
  • a switching rod 41 is provided which projects into the interior of the closure body 4 into the guide bore 36 and is in contact with the valve control body 35.
  • the shift rod 41 extends along the longitudinal axis of the apparatus body 1 by corresponding axial holes in the screw holder 22, the magnet cylinder 14 and the percussion piston 12 and comes into a corresponding receiving bore of the deformation tool head 7 ' ⁇ to lie.
  • the shift rod 41 is part of a triggering device 40, which furthermore has the deformation tool 7 as a contactor and comprises the return spring 9 which is in engagement with the deformation tool 7.
  • the pneumatic device To actuate the pneumatic device, it is pressed against a workpiece with the shaping tool 7; with further delivery, the deformation tool 7 moves against the force of the return spring 9 and transmits this movement to the switching rod 41 coupled to it.
  • the switching rod 41 transmits the short stroke movement to the valve control body 35, which is characterized by the fact that the Pressure chamber 31 is connected via the feed channel 38 through the guide bore 36 and the interior of the valve control body 35 to the ventilation channel 39 - comes into a pressurization position; here the valve control body 35 moves the closing cone 37 from a closed position, the compressed air supply being released into the interior of the pressure chamber 31; the ventilation duct 39 is closed at the same time.
  • the pressure built up in the pressure chamber 31 is applied via the pressure bores 34 through the magnetic cylinder 14 to the rear end surface of the percussion piston 12. If a pressure force that slightly exceeds the holding force between the magnet 18 and the percussion piston 12 is generated in the pressure chamber 31 during the pressure build-up phase, the percussion piston 12 instantly detaches itself from the magnet cylinder 14. After the percussion piston 12 has been released from the magnetic cylinder 14, no further pressure build-up takes place in the pressure chamber 31, so that the percussion piston 12 is accelerated with the pressure force of the air pressure that is currently available. This moves, driven by the force of the compressed air, which acts on the entire end face of the percussion piston 12 and that of the weight force 20th
  • the percussion piston 12 is superimposed in the direction of the deformation tool 7.
  • the air in the guide cylinder 2 escapes through four radially arranged in the guide cylinder 2 vent holes 43, which are 6-arranged in the lower area near the guide body.
  • An impact transmission from the impact piston 12 to the deformation tool 7 takes place and thus a plastic deformation of the workpiece resting on it.
  • the return spring 13 is provided in order to bring the percussion piston 12 out of its striking position into its release position.
  • the deformation tool head 7 ′′ is brought back into contact with the guide body 6 by the return spring 9; the shift rod 41 is in turn brought back into the starting position by a spring arranged between the closing cone 37 and the valve control body 35.
  • the control valve 33 is closed on the compressed air side, the vent position being reached at the same time.
  • the percussion piston 12 is now pressed into the release position by the return spring 13.
  • the magnetic holding force with which the magnets 18 hold the percussion piston 12 in the release position on the magnetic cylinder 14 can be changed by means of an adjusting device 26; this results in a change in the impact impulse force with which the impact piston 12 strikes the deformation tool 7, since the impulse with which the impact piston 12 hits the Deformation tool 7 hits, depending on the distance of the magnets 18 to the percussion piston 12 in the release position. If the distance between the percussion piston 12 and the magnet 18 is reduced, then there is a strong holding force in the release position, if the distance is increased, the holding force is reduced and accordingly the pressure in the pressure chamber 31 applied until the triggering time.
  • an adjusting nut 27 'and two adjusting pins 28 are provided in the exemplary embodiment shown here.
  • the adjusting nut 27' can be rotated in the form of a union nut at the rear end of the closure body 4 by means of an external thread formed thereon
  • Two adjusting pins 28 are received in sealing contact in axial guide bores 29 of the closure body 4 and are located with their ends on the one hand in engagement with the adjusting nut 27 'and on the other hand through the pressure chamber 31 with the screw holder 22.
  • the adjusting nut 27' can now be turned in such a way that the screw holder 22 is moved against the force of the compression springs 24 along the axial axis of the device housing 1 and thus the distance of the magnets 18 from the contact face 17 of the magnetic cylinder 14 is changed, depending on the thread pitch selected on the closure body 4 u nd adjusting nut 27 * * provided thread there is a continuously fine adjustment of the distance of the magnets 18 to the striking piston 12 in the release position and thus the magnet holding force.
  • the pneumatic device described in this way is suitable for manual operation. In order to keep the device within reach at the workplace, it has a mounting bracket 42 attached to the closure body 4. If, on the other hand, the pneumatic device described is to be integrated into automatic processes, for example in assembly, testing, measuring or production facilities for stamping a test mark, flanging or the like, an deliverable pneumatic device as shown in FIG. 4 is provided.
  • the receiving guide consists of a cylinder housing 50, in which the device housing 1 is accommodated in an axially movable manner, the end walls 51 ′, 51 ′′ of the cylinder housing 50 each having a cylindrical pressure break through which the rear and front ends of the device housing 1 In order to achieve a sealing contact "of the smoothly ground device housing 1 in the openings of the end walls 51 / , 51", these have sealing rings 52 in circumferential grooves.
  • the rear end wall 51 " is provided as a removable cover which is attached to the circumferential wall 51 of the Cylinder housing 50 in a sealing system is attached.
  • the device housing 1 has a circumferential flange 53 which extends radially to the longitudinal axis and which bears in a form-fitting manner on the inner circumferential wall 51.
  • two annular pressure chambers 54, 54 ' are formed, which are delimited by the wall of the device housing 1, the peripheral flange 53, and the peripheral wall 51 and the end walls 51, 51 ".
  • the circumferential flange 53 has an O-ring-shaped flange seal 55 which bears against the inner circumferential wall 51.
  • the circumferential flange 53 is an integral part of the magnetic cylinder 14 and thus corresponds to the circumferential flange 15, which, as already stated , has a larger diameter than the device housing 1.
  • the circumferential flange 53 can, however, also be designed as a separate component between the guide cylinder 2 and the connecting sleeve 3 in the form of an annular disk, which can be attached to the magnetic cylinder 14 or by means of suitable fastening means, for example an integrated thread one of the device housing parts 2, 3 can be connected. Due to this configuration of the device housing 1 with the radially widened area, ie the peripheral flange 53, the pneumatic device can be regarded as a piston rod with pistons, which is held displaceably in the cylinder housing 50 between two positions.
  • the cylinder housing 50 has two compressed air access ports 56, 56', each of which with one of the Pressure chambers 54,54 'are connected.
  • An alternating pressurization of the pressure chambers 54, 54 ′ is thus possible, as a result of which the pneumatic device can be brought into engagement with the workpiece and can be moved back out of this engagement.
  • the percussion piston 12 is released from the release position in the same manner as the release in the case of the manually operated pneumatic device.
  • the device housing 1 has, at the end having the closure body 4, an axially displaceable stop ring 57 which can be clamped in an axial position on the device housing 1.
  • the stop ring 57 comes to rest on the rear end wall 51 "of the cylinder housing 50.
  • the cylinder housing 50 is mounted by means of fastening screws on a connecting plate 58. By engagement of a corresponding groove of the stop ring in a guide rail of the connecting plate 58, a connection is simultaneously made Rotation of the pneumatic device within the cylinder housing 50 is prevented.
  • Other drive concepts are also possible that can automatically move the pneumatic device on the receiving guide (cylinder housing). This can be done mechanically or in any other known manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Automation & Control Theory (AREA)
  • Actuator (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

Sur un dispositif actionné pneumatiquement pour la déformation plastique, en particulier pour le poinçonnage, l'estampage, le matage, l'emboîtage, le boulonnage, le bordage, etc., constitué d'un piston frappeur (12) actionné avec de l'air comprimé et se déplaçant entre deux positions à l'intérieur d'un cylindre de guidage (2), piston qui est maintenu dans une position de déclenchement située à l'une des extrémités du cylindre de guidage (2) par un dispositif (25) comprenant au moins un aimant de maintien (18), constitué également d'un outil de déformation (7) coulissant à l'autre extrémité du cylindre de guidage (2), outil qui commande un clapet de commande (33) d'un dispositif d'impulsion (30) par une charge axiale exercée sur le dispositif de déclenchement (40), par lequel le piston frappeur (12) est actionné sous pression sur la face avant et libéré lorsque la force exercée est supérieure à la force de maintien de l'aimant (8) et par lequel la percussion est transférée sur l'outil de déformation (7), et constitué en outre d'un élément de rappel (13) au moyen duquel le piston frappeur (12) peut être mis à nouveau en position de fonctionnement avec le dispositif de maintien (25), on obtient un déclenchement variable de l'impulsion de percussion, c'est-à-dire une modification de la force de percussion et une simplification du dispositif de déclenchement par le fait que le dispositif de maintien (25) présente un dispositif de rappel (26) servant à modifier la force de maintien exercée entre l'aimant (18) et le piston frappeur (12) en position de déclenchement et que le dispositif d'impulsion (30) présente une chambre de compression (31) qui est mise sous pression et purgée au moyen d'un seul clapet de commande (33).
PCT/EP1990/001157 1989-08-01 1990-07-14 Dispositif actionne pneumatiquement pour la deformation plastique, en particulier pour le poinçonnage WO1991001856A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8909282U DE8909282U1 (de) 1989-08-01 1989-08-01 Pneumatisch betriebene Vorrichtung zur plastischen Verformung, insbesondere zum Schlagstempeln
DEG8909282.1U 1989-08-01

Publications (1)

Publication Number Publication Date
WO1991001856A1 true WO1991001856A1 (fr) 1991-02-21

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Application Number Title Priority Date Filing Date
PCT/EP1990/001157 WO1991001856A1 (fr) 1989-08-01 1990-07-14 Dispositif actionne pneumatiquement pour la deformation plastique, en particulier pour le poinçonnage

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Country Link
EP (1) EP0411249A1 (fr)
DD (1) DD295584A5 (fr)
DE (1) DE8909282U1 (fr)
WO (1) WO1991001856A1 (fr)

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DE102004057229A1 (de) * 2004-10-20 2006-04-27 Borries Markier-Systeme Gmbh Prägevorrichtung mit Druckluftantrieb
EP1698487A2 (fr) * 2004-12-15 2006-09-06 Detlef Joniskeit Poinçon pneumatique manuel avec récipient remplissable de gaz propulseur

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EP0723492B1 (fr) * 1994-08-19 1999-10-27 SYNTHES AG, Chur Element percutant
DE102004005859A1 (de) * 2004-02-05 2005-08-25 Claas Fertigungstechnik Gmbh Vorrichtung zur Fixierung von Nietelementen in Bauteilen
DE102004057200B4 (de) * 2004-10-20 2006-08-10 Borries Markier-Systeme Gmbh Prägevorrichtung mit Druckluftantrieb und Einheit zur Zuschaltung von Druckluft dafür
CN102776860A (zh) * 2012-08-14 2012-11-14 韶关学院 气动冲击式破冰机

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DE2426181A1 (de) * 1974-05-29 1976-01-22 Erwin Ing Grad Lueer Druckluftbetaetigter regelbarer schlagzylinder
DE3112463A1 (de) * 1981-03-28 1982-10-07 Eugen 6550 Bad Kreuznach Zinck Druckluftramme

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FR1510061A (fr) * 1966-12-06 1968-01-19 Poclain Sa Marteau à masse mobile
DE2017007A1 (de) * 1970-04-09 1971-10-21 Geisel K Pneumatisch hydraulischer Kolben trieb
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DE2111653A1 (de) * 1971-03-11 1972-09-21 Erwin Pneumatischer Klopfer
DE2426181A1 (de) * 1974-05-29 1976-01-22 Erwin Ing Grad Lueer Druckluftbetaetigter regelbarer schlagzylinder
DE3112463A1 (de) * 1981-03-28 1982-10-07 Eugen 6550 Bad Kreuznach Zinck Druckluftramme

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004057229A1 (de) * 2004-10-20 2006-04-27 Borries Markier-Systeme Gmbh Prägevorrichtung mit Druckluftantrieb
DE102004057229B4 (de) * 2004-10-20 2006-07-13 Borries Markier-Systeme Gmbh Prägevorrichtung mit Druckluftantrieb
EP1698487A2 (fr) * 2004-12-15 2006-09-06 Detlef Joniskeit Poinçon pneumatique manuel avec récipient remplissable de gaz propulseur
EP1698487A3 (fr) * 2004-12-15 2006-10-18 Detlef Joniskeit Poinçon pneumatique manuel avec récipient remplissable de gaz propulseur

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DD295584A5 (de) 1991-11-07
DE8909282U1 (de) 1989-09-14
EP0411249A1 (fr) 1991-02-06

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