EP0406802A2 - Dispositif d'introduction de matière pour machines de traitement de matières, en particulier pour machines automatiques à poinçonner ou à plier - Google Patents

Dispositif d'introduction de matière pour machines de traitement de matières, en particulier pour machines automatiques à poinçonner ou à plier Download PDF

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Publication number
EP0406802A2
EP0406802A2 EP90112688A EP90112688A EP0406802A2 EP 0406802 A2 EP0406802 A2 EP 0406802A2 EP 90112688 A EP90112688 A EP 90112688A EP 90112688 A EP90112688 A EP 90112688A EP 0406802 A2 EP0406802 A2 EP 0406802A2
Authority
EP
European Patent Office
Prior art keywords
slide
carriage
main
clamping
stop
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.)
Withdrawn
Application number
EP90112688A
Other languages
German (de)
English (en)
Other versions
EP0406802A3 (en
Inventor
Otto Bihler
Eduard Brüller
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.)
Otto Bihler Maschinenfabrik GmbH and Co KG
Original Assignee
Otto Bihler Maschinenfabrik GmbH and 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 Otto Bihler Maschinenfabrik GmbH and Co KG filed Critical Otto Bihler Maschinenfabrik GmbH and Co KG
Publication of EP0406802A2 publication Critical patent/EP0406802A2/fr
Publication of EP0406802A3 publication Critical patent/EP0406802A3/de
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F23/00—Feeding wire in wire-working machines or apparatus
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F1/00—Bending wire other than coiling; Straightening wire
    • 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
    • Y10T74/18176—Crank, pitman, lever, and slide

Definitions

  • the invention relates to a material feed device for material processing machines, in particular punching and bending machines, comprising a feed slide guided in a main guide with a controlled slide-side material clamping device, an oscillation drive in drive connection with the feed slide and a controlled material holding device, the standstill of the slide-side material clamping device in its end position along the Main guide is determined by slide stops and a transmission suspension is provided in the drive connection between the oscillation drive and the slide-side material clamping device.
  • Such a material feed device is known for example from DE-OS 27 41 149. It is there, for example FIG. 5 in connection with page 8, last paragraph, and page 9, first paragraph.
  • the invention is based on the object of reducing the impact energy which is to be absorbed at the moment when the intake sled hits the sled stops.
  • the invention proposes that the feed carriage comprises a main slide connected to the oscillation drive, which is guided in the main guide, that a secondary guide is attached to the main slide substantially parallel to the guide direction of the main guide, that a secondary slide is guided on this secondary guide is that the secondary carriage carries the material clamping device on the carriage, that the secondary carriage interacts with the carriage stops and that at least part of the transmission suspension is arranged between the secondary carriage and the main carriage.
  • the invention therefore proceeds in a fundamentally different way from the one outlined in DE-OS 27 21 149, in which it does not attempt to approximate the curve shape of the feed carriage movement even closer to an ideal shape, for example a trapezoidal shape, but rather aims at according to a first embodiment, to reduce the mass impinging on the slide stops.
  • the mass of the slide required to achieve a clean linear guide is not required as a whole for the entrainment of the material to be processed in each case and that the mass of the secondary slide can therefore be kept relatively small compared to the mass of the main slide .
  • the mass of the secondary carriage can be reduced to a fraction of the mass of the total of main carriage and secondary carriage, for example to 10% to 15% of the sum of the masses of main carriage and secondary carriage.
  • the transmission suspension between the secondary carriage and the main carriage must be strong enough to accelerate the mass of the additional carriage, to accelerate the wire or strip material and, if necessary, to move the wire or strip material through a straightening device by dividing the feeder according to the invention achieve a significant reduction in the energy to be absorbed at the respective slide stops in a main slide and a secondary slide.
  • the parts of the additional suspension lying between the secondary slide and the main slide are preferably placed under a pre-tension already existing in the idle state in order to be able to transmit the forces to be applied to the secondary slide.
  • the essential parts of the material clamping device on the slide must be attached to the secondary slide, i.e. two clamping surfaces, one of which can generally be fixed to the secondary slide, while the other must be capable of a clamping and detaching movement with respect to the former.
  • the not inconsiderable masses that are required to control the material clamping device on the slide side can be displaced to a substantial extent from the secondary slide to the main slide, whereby the mass of the secondary slide can be further reduced. This applies regardless of how the carriage-side material clamping device is controlled, that is, regardless of whether the clamping control for the carriage-side material clamping device is a purely mechanical, a hydraulic or an electrical control.
  • the slide-side material clamping device comprises a clamping point fixed to the secondary slide and a clamping element mounted on the secondary slide and capable of a clamping movement
  • a pressing element which can be carried along the main guide and which is intended to act on the clamping element can be attached to the main slide and a relative movement the clamping member along the main guide is capable. For example, you can let the pressure element moved with the main slide simply act on the sliding element mounted on the secondary slide on a slide surface.
  • the transmission suspension between the secondary slide and the main slide can be designed in the simplest way so that the secondary slide is clamped on the main slide between two transmission springs acting in opposite directions parallel to the main guide, and - as already mentioned above - these transmission springs are preferably already in the idle state under Pre-tension.
  • At least part of the feed carriage and in particular at least the secondary carriage can be braked before hitting a carriage stop.
  • a proximity button for braking the secondary slide, which interacts with a slide engaging surface that is fixed against the slide stop when the secondary slide approaches the slide stop and that the latter stops Proximity button on the secondary carriage whose approach speed acts braking on the respective stop.
  • the proximity button it is possible to provide directly on the secondary slide.
  • the proximity switch acts on the secondary slide via a push-button mechanism supported on the main slide.
  • the pushbutton transmission can be designed approximately in the form that the proximity switch is attached to one leg of an angle lever pivotally mounted on the main slide and that another leg of this angle lever acts on the secondary slide.
  • the impact-resistant button engagement surface be inclined at an acute angle to the guide direction of the main guide.
  • the button engagement surface can be inclined over its entire engagement length with a constant angle of inclination against the guide direction of the main guide.
  • the button engagement surface as an engagement path, the inclination of which The main guiding direction increases with increasing duration of the engagement between the proximity button and the button engagement surface, so that the deceleration effect increases with decreasing speed of the feed slide or of the secondary slide, so the energy absorption is distributed approximately evenly over a certain braking distance.
  • the button engagement path then assumes a curved curve shape that deviates from the linear course.
  • the braking of the feed carriage or - in the case of a division of the feed carriage into main and secondary carriages - the secondary carriage can be a purely elastic braking.
  • this caster relative movement can be used to clamp the carriage on the slide direction to control, such that the control of the carriage-side clamping device is derived from the caster relative movement of the main carriage relative to the secondary carriage, which occurs after the secondary carriage strikes the respective carriage stop.
  • the tracking relative movement then represents, so to speak, the control signal for the carriage-side clamping device.
  • This signal can be used in various ways to actuate the carriage-side clamping device, for example hydraulically, but possibly also purely mechanically.
  • a purely mechanical control of the clamping device can be realized, for example, in such a way that a clamping wedge is provided for controlling the material clamping device, which can be clamped or released by the relative tracking movement.
  • the solution with a clamping wedge can be realized in a very simple manner in such a way that the clamping wedge is arranged between a clamping member of the carriage-fixed clamping device mounted on the secondary slide on the one hand and a wedge contact surface attached to the secondary slide and interacts with wedge action stops of the main slide acting on it in the guide direction of the main guide.
  • the carriage-side clamping device should preferably be spring-loaded, in order not to cause clamping of the wire or strip material which leads to material damage. Applied to the clamping wedge solution, this means that at least one of the wedge action stops can be sprung, which causes the clamping of the carriage-fixed clamping device.
  • this control of the material holding device can be realized in such a way that the main slide has a holding device control stop, which acts on a holding device control gear.
  • the main slide has two holding device control stops, of which one or the other in depending on the direction of movement of the main slide acts in opposite directions on the holder control gear.
  • the holding device control gear can be carried out in the simplest way with a linkage running in the guide direction of the main guide, which is designed with n counter-stops on the control gear side to be acted upon by the holding device control stops.
  • the holding device control gear can in turn also act on the material holding device via a clamping wedge device, an elastic intermediate member being able to be provided here again in the area of the holding device control or the clamping wedge for gentle treatment.
  • the position of the button engagement surface is regularly fixed relative to the position of the respective carriage stop. This gives the possibility of a simplified machine setting in that the stop-proof push-button engagement surface is connected in an unchangeable manner to the respective slide stop.
  • a further simplification of the machine setting can be achieved in the presence of a control gear for controlling the material holding device as a function of the relative caster movement of the main slide in that the slide stops are connected to adjustment stop surfaces which serve to adjust the counter-stops on the linkage on the linkage.
  • a processing machine must be adjustable to different feed strokes in order to be able to adjust the feed stroke to the length of the wire or strip section required in each case.
  • this setting is effected by changing the eccentricity if it is an eccentric drive or by replacing the cam disc if it is a cam disc instinct acts; alternatively, a change in the gear ratio of a transmission lever switched between the oscillation drive and the main slide is also conceivable. Accordingly, the distance between the sled stops must of course also be changed. Accordingly, it is provided that at least one of the slide stops is adjustable and lockable in the guide direction of the main guide.
  • the material clamping device and the material holding device are controlled in such a way that the material to be supplied is detected by at least one of these devices at each time of operation.
  • FIG. 1 is a. Oscillation drive designated 10. It comprises an eccentric disk 12 which is driven by the main shaft of a bending machine and which rotates continuously about an axis 14 at a constant rotational speed. An eccentric pin 16 with variable eccentricity e is attached to the eccentric disk 12. A connecting rod 18 leads from the eccentric pin 16 to a pivoting lever 20, which is driven by the connecting rod 18 oscillating about a pivot axis 22. The pivoting lever 20 is connected in drive connection to a main slide 26 by means of an articulated lug 24. The main slide 26 is guided in a straight line in the direction of the double arrow 28 on a main guide (not shown). On the main slide 26, a secondary slide 30 is guided in the direction of the double arrow 32 in a secondary guide, not shown. The secondary guide 32 of the secondary slide 30 is parallel to the main guide 28 of the main slide 26.
  • the secondary slide 30 is in drive connection with the main slide 26 by two transmission springs 34a and 34b, which will be discussed in more detail in connection with FIG. 4.
  • the transmission springs engage on a nose 36 of the secondary slide 30 and are on support surfaces 38a and 38b of the Main carriage supported 2G.
  • the two transmission springs 34a and 34b are in the idle state of the material feed device under spring preload.
  • the secondary carriage 30 is responsible for the material feed.
  • a secondary surface fixed to the secondary slide 30 is attached to the secondary slide 30 and also a clamping member 44 in the form of a clamping lever 44 which is pivotably mounted on the secondary slide 30 about a pivot bearing 46.
  • a clamping lug 48 of the clamping lever 44 on the one hand and the clamping point 42 on the other hand the material to be drawn in, that is to say a band or a wire, can be clamped.
  • the clamping and releasing movement of the clamping lever 44 is effected by a clamping control 50, which will be discussed in more detail below.
  • the wire or strip to be processed in the wire or strip bending machine is drawn in from the right to the left in the direction of the arrow 52 in FIG. 1.
  • the clamping lug 48 is pressed down by the clamping control 50, with the result that the wire or strip material is clamped between the clamping lug 48 and the clamping point 42. If the secondary carriage 30 then moves from right to left, the wire or strip material is through the secondary carriage 30 to the left end position Position of the secondary carriage 30 entrained, ie in the position of the secondary carriage 30, which is determined by the carriage stop 40a.
  • the transmission spring 34b must therefore be strong enough due to its structure and due to its pretension to pull the wire or strip material from a supply reel, to pull it through a straightening device and thereby to accelerate it in accordance with the movement sequence of the main slide 26; further explanations in connection with FIG. 6.
  • the clamping control 50 becomes effective in the sense of a solution of the clamping of the wire or strip material, so that the secondary carriage 30 is subsequently returned from the left to the right the tape or wire material remains in place.
  • the time required for the wire or strip material to be fed through the secondary carriage 30 in the direction of arrow 52 is referred to as the "pull-in time".
  • This pull-in time is not available for the bending and punching processes on the wire or strip material. Rather, only the downtime is available for bending and punching. It is therefore desirable that the pull-in time be as short as possible and on the other hand that the downtime in the course of a movement period be as long as possible, ie that as much time as possible be available for the bending and punching operations.
  • the standstill time begins when the secondary slide 30 has reached its left end position by moving on the slide stop 40a and then has ended, when the next feed begins.
  • a material holding device 54 is provided, which is arranged stationary on the punching and bending machine.
  • This material holding device also includes a clamping point 56 and a clamping member 58 in the form of a clamping lever.
  • the clamping member 58 is pivotable about a pivot bearing 60 and has a clamping nose 62, so that the wire or strip material during the downtime, i.e. is clamped between the clamping nose 62 and the clamping point 56 during processing by the bending and punching tools.
  • the oscillation drive 10 can be designed as described in DE-OS 27 41 149, for example in FIG. 2 there; this means that the movement of the main slide 26th Compared to a sine curve, the apex of the sine curve can be flattened and the flanks of the curve have been flattened. Nevertheless, the secondary carriage 30 still hits the carriage stops 40a and 40b at a considerable speed, so that a considerable amount of energy must be absorbed at the moment of impact, although the impacting mass of the secondary carriage 30 has already been considerably reduced compared to one of the prior art Solution in which the clamping device 42, 44 is rigidly attached to the main slide.
  • the energy to be absorbed at the moment of impact of the secondary slide 30 on the slide stop 40a or 40b essentially results from the mass of the secondary slide 30 and from the speed of impact of the secondary slide 30 with respect to the stop 40a or 40b.
  • An angle lever 64 is pivotally mounted on the main slide 26 about a pivot bearing 66. This angle lever 64 engages with a lever arm 64a on the secondary slide 30 and carries on its other lever arm 64b an approach button 68 in the form of a button roller. Before the secondary slide 30 moves to the left on the slide stop 40a during the movement of the main slide 26, the feeler roller 68 interacts with a push button engagement surface 70 which is in a fixed position relative to the slide stop 40a fixed on the frame of the punching and bending machine by a clamping device 41 is arranged.
  • the button engagement surface 70 forms a small acute angle of, for example, 20 ° with the direction 32 of the main guide 28, as can be seen from FIG. 1.
  • a further angle lever 72 with a lever arm 72a and a lever arm 72b is provided, this angle lever 72 about a pivot bearing 74 in turn is pivotable on the main slide.
  • the lever arm 72b carries a further proximity button 76, which cooperates with a button engagement surface 78 in exactly the same way as previously stated with respect to the proximity button 68.
  • main slide 26 executes a caster relative movement with respect to the secondary slide 30 after the secondary slide 30 strikes the slide stop 40a or 40b. It will now be shown in the following that these tracking relative movements can be used to control the material clamping device 42, 48 on the slide side and to control the material holding device 56, 62.
  • the wedge action stop 80 hits the clamping wedge 82, this is displaced to the left relative to the wedge contact surface 84, ie it can deflect upwards due to the course of the wedge contact surface 84 going to the left and upwards.
  • the clamping wedge nose 86 attached to the clamping wedge 82 lifts off the clamping member 44 and this can lift off the clamping point 42 under the action of a helical compression spring 88.
  • a wedge action stop 90 attached to the main slide 26 presses on the clamping wedge 82 and attempts to move it to the right.
  • the clamping wedge 82 must go due to the right and downward inclination of the Keilanla surface 84 and therefore pushes the clamping member 44 down, so that the wire or strip material is clamped between the clamping nose 48 and the clamping point 42.
  • the wedge action stop 90 is cushioned by a helical compression spring 92. This helical compression spring 92 prevents the wire or strip material from being clamped too strongly between the clamping lug 48 and the clamping point 42, which could lead to damage to the wire or strip material.
  • the control of the material holding device 54 can also be derived from the caster relative movement of the main slide 26 relative to the secondary slide 30, as will be explained in the following.
  • a holder control stop 94 is attached to the main slide 26 and is cushioned by a helical compression spring 96. This holding device control stop encounters a counter stop 98 which is clamped onto a linkage 100.
  • the linkage 100 is guided in linear guides 102 and 104 of the machine frame of the punching and bending machine in the direction of the double arrow 106.
  • a further clamping wedge 108 is attached to the left end of the linkage 100. This clamping wedge 108 interacts with a clamping plunger 110, which belongs to the material holding device 54.
  • the clamping plunger 110 is guided in a block 112 which is fixedly arranged on the frame of the punching and bending machine.
  • the carriage stops 40a and 40b are fixed in a fixed position relative to the respective button engagement surface 70 and 78, respectively on a block 122 and 124, respectively.
  • These blocks 122 and 124 have moreover adjustment stop surfaces 126 and 128 for the counter stops 98 and 120 and thus for the linkage 100.
  • the control stroke of the linkage 100 is designated by h in the area of block 124 in FIG. This stroke h must always remain the same size, as long as the structure of the material holding device 54 remains unchanged. If, after adjusting the eccentric pin 16 in its eccentricity e relative to the axis of rotation 14, the slide stops 40a, 40b are set in accordance with the desired stroke of the secondary slide 30, the corresponding adjustment of the button engagement surfaces 70 and 78 inevitably also results.
  • the counter stops 98 and 120 are clamped accordingly on the linkage 100.
  • the correct setting of the counter stops 98 and 120 can be obtained by adjusting the stroke h between the adjusting stop surface 128 and the counter stop 120 by means of a gauge, after the counter stop 98 has been brought into contact with the adjusting stop surface 126.
  • the rough adjustment of the stops 40a and 40b according to the respective choice of the eccentricity e can take place in that a fastening block 130 carrying the slide stop 40b is firmly clamped on a frame part 132 by means of fastening screws 134. Interacting teeth 136 can be attached to the frame part 132 and the fastening block 130.
  • the counter stop 98 is brought to bear on the adjustment stop surface 126.
  • the counter stop 120 is released from its clamping on the linkage 100.
  • the counterstop 120 is then moved until a spring-loaded ball 140 attached to the block 124 snaps into a ball engagement notch 142 of the counterstop 120. Then the counter stop 120 is clamped on the linkage 100. This is shown in Figure 1a.
  • FIG. 2 again shows the main slide 26 and the secondary slide 30 as well as the slide stops 40a and 40b.
  • the clamping member 44 in the form of a clamping lever can be seen on the secondary slide 30.
  • the clamping lever is here under the action of a hydraulically operated clamping plunger 145, which acts on the clamping lever 44 with a clamping roller 147.
  • a tension coil spring 149 keeps the clamp lever 44 in constant engagement with the clamp roller 147.
  • other control options are also conceivable.
  • parts analogous to FIG. 1 are again provided with the same reference numerals as there.
  • FIG. 3 Another possibility of clamping is shown in a highly schematic manner in FIG. 3. From the carriage-side clamping device, one can only see the clamping lever 44 with the clamping lug 48.
  • an eccentric 153 is shown here, which is pivotably mounted on the secondary carriage 30 about an axis of rotation 155.
  • the eccentric 153 is firmly connected to a control arm 157.
  • This control arm 157 is movable against stops 90 and 80 of the main slide 26.
  • the eccentric 153 is pivoted in the sense of a solution of the material clamping device.
  • the stop 90 is approached by the control arm 156, the material clamping device is clamped at 48.
  • FIG. 4 shows a modification to FIG. 1 in that a helical compression spring 158 is provided between the clamping wedge 82 and the clamping lever 44.
  • the wedge action stop 90 need not be spring-loaded.
  • Figure 5 shows a related solution.
  • the clamping wedge 82 is sprung by a slot 161.
  • a ball catch 163 is provided in FIG. 4, which can of course also be used in the embodiment according to FIG. 1.
  • the main slide 26 and the secondary slide 30 can again be seen in FIG. 6.
  • the support surfaces 38a and 38b, on which the support springs 34a and 34b are supported, are in turn attached to the main slide 26.
  • These are in turn helical compression springs 34a and 34b.
  • the helical compression springs 34a and 34b act on intermediate pieces 35a and 35b, which in turn abut the nose 36 of the secondary slide 30.
  • the helical compression springs 34a, 34b are penetrated by compression maintenance anchors 37a, 37b, which are anchored in the main slide 26. Stop heads 39a and 39b are attached to the compression maintenance anchors 37a and 37b and are received by sleeves 41a, 41b.
  • FIG. 6 shows the rest position of the secondary slide 30 with respect to the main slide 26, in which both helical compression springs 34a, 34b are maximally relaxed, but both are under compressive pretension.
  • the stop flanges 43a and 43b lie on the stop heads 39a and 39b and the mutually facing ends 45a, 45b of the sleeves 41a, 41b rest on the nose 36 of the secondary carriage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Advancing Webs (AREA)
  • Feeding Of Workpieces (AREA)
EP19900112688 1989-07-04 1990-07-03 Device for forwarding material for material treating machines, in particular automatic punching or folding machines Withdrawn EP0406802A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3921997A DE3921997C1 (fr) 1989-07-04 1989-07-04
DE3921997 1989-07-04

Publications (2)

Publication Number Publication Date
EP0406802A2 true EP0406802A2 (fr) 1991-01-09
EP0406802A3 EP0406802A3 (en) 1991-08-28

Family

ID=6384286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900112688 Withdrawn EP0406802A3 (en) 1989-07-04 1990-07-03 Device for forwarding material for material treating machines, in particular automatic punching or folding machines

Country Status (4)

Country Link
US (1) US5167358A (fr)
EP (1) EP0406802A3 (fr)
JP (1) JPH0379252A (fr)
DE (1) DE3921997C1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995004618A1 (fr) * 1993-08-09 1995-02-16 Gebr. Felss Gmbh & Co. Kg Unite a machoires de serrage
WO1995004630A1 (fr) * 1993-08-09 1995-02-16 Gebr. Felss Gmbh & Co. Kg Unite a machoires de serrage
CN103707119A (zh) * 2013-12-30 2014-04-09 金华市亚虎工具有限公司 一种全机动送料打孔机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4330783A1 (de) * 1993-09-10 1995-03-16 Otto Bihler Stelleinrichtung in einer Bearbeitungsmaschine
IT1314119B1 (it) * 1999-12-10 2002-12-04 Carlo Salvi & C S R L Apparecchiatura di movimentazione per macchine stampatrici.

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH543932A (de) * 1971-10-01 1973-11-15 Bruderer Ag Vorrichtung zum schrittweisen Vorschieben eines Werkstückes
DE2631193A1 (de) * 1976-07-10 1978-01-19 Kaiser Kg Otto Vorschubeinrichtung
DE2741149C2 (de) * 1977-09-13 1986-08-14 Bihler, Otto, 8959 Trauchgau Antriebsvorrichtung für Draht- bzw. Bandzuführeinrichtungen an Stanz-Biegeautomaten
DE2711693C3 (de) * 1977-03-17 1985-11-21 Otto 8959 Trauchgau Bihler Druckmittelbetätigungssystem für die Vorschub- und die Rückhaltezange einer Bandvorschubeinrichtung
DE2850944C2 (de) * 1978-11-24 1987-01-15 Bihler, Otto, 8959 Trauchgau Materialeinzugsvorrichtung an Draht- und/oder Bandbearbeitungsmaschinen
US4580710A (en) * 1982-08-10 1986-04-08 Plessey Incorporated Stock feeder with hydraulic shock absorber

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995004618A1 (fr) * 1993-08-09 1995-02-16 Gebr. Felss Gmbh & Co. Kg Unite a machoires de serrage
WO1995004630A1 (fr) * 1993-08-09 1995-02-16 Gebr. Felss Gmbh & Co. Kg Unite a machoires de serrage
CN103707119A (zh) * 2013-12-30 2014-04-09 金华市亚虎工具有限公司 一种全机动送料打孔机
CN103707119B (zh) * 2013-12-30 2016-05-25 金华市亚虎工具有限公司 一种全机动送料打孔机

Also Published As

Publication number Publication date
JPH0379252A (ja) 1991-04-04
US5167358A (en) 1992-12-01
EP0406802A3 (en) 1991-08-28
DE3921997C1 (fr) 1990-08-16

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