EP1419861A1 - Vorrichtung zum rotativen Stanzen von Stanzgut, insbesondere von extrudierten Endlosprofilen - Google Patents
Vorrichtung zum rotativen Stanzen von Stanzgut, insbesondere von extrudierten Endlosprofilen Download PDFInfo
- Publication number
- EP1419861A1 EP1419861A1 EP03025561A EP03025561A EP1419861A1 EP 1419861 A1 EP1419861 A1 EP 1419861A1 EP 03025561 A EP03025561 A EP 03025561A EP 03025561 A EP03025561 A EP 03025561A EP 1419861 A1 EP1419861 A1 EP 1419861A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drum
- shaped tool
- tool carrier
- toothed belt
- chain
- 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.)
- Granted
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- 238000005520 cutting process Methods 0.000 claims abstract description 23
- 239000000969 carrier Substances 0.000 claims abstract description 16
- 238000004080 punching Methods 0.000 claims description 27
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- 239000000463 material Substances 0.000 claims description 10
- 230000007246 mechanism Effects 0.000 claims description 10
- 125000006850 spacer group Chemical group 0.000 claims description 5
- 230000001360 synchronised effect Effects 0.000 abstract description 3
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Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D28/00—Shaping by press-cutting; Perforating
- B21D28/24—Perforating, i.e. punching holes
- B21D28/36—Perforating, i.e. punching holes using rotatable work or tool holders
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
- B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
- B26D5/02—Means for moving the cutting member into its operative position for cutting
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
- B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
- B26D5/08—Means for actuating the cutting member to effect the cut
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
- B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
- B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
- B26D7/2628—Means for adjusting the position of the cutting member
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
- B26D9/00—Cutting apparatus combined with punching or perforating apparatus or with dissimilar cutting apparatus
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
- B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
- B26F1/02—Perforating by punching, e.g. with relatively-reciprocating punch and bed
- B26F1/06—Perforating by punching, e.g. with relatively-reciprocating punch and bed with punching tools moving with the work
- B26F1/10—Roller type punches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
- B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
- B26F1/38—Cutting-out; Stamping-out
- B26F1/384—Cutting-out; Stamping-out using rotating drums
-
- 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
- B44B5/0004—Machines or apparatus for embossing decorations or marks, e.g. embossing coins characterised by the movement of the embossing tool(s), or the movement of the work, during the embossing operation
- B44B5/0009—Rotating embossing tools
Definitions
- the invention relates to a device for rotary punching of punched material according to the preamble of protection claim 1.
- Rotary punching machines are already known, such as the German one Laid-open publication 23 53 226. With these punching devices, the Punching process between two axially parallel, circumferentially opposite Stamping drums, one as a male with cutting punches and the other as Matrix is formed with cutting holes.
- the radial distance between the two Punching drums are selected so that on the one hand there is a passage gap for the punched material is present and on the other hand penetration of the cutting punch in the Cutting holes in the die takes place.
- the band-shaped material to be cut runs tangentially through the passage gap.
- the synchronous operation of the punch drums is achieved by that at the front of the two punch drums, one with the Stamping drum connected gear is arranged, which is thus the same Rotation speed as the punch drums possesses.
- the gears are designed so that they are in the operating state comb together. As a result, the two punch drums are precisely synchronized guaranteed.
- the maximum possible distance adjustment is limited to a few millimeters, however If the distance between the two punch drums is too large, this will cause mutual interference two gears for synchronization and thus the synchronization of the two Punch drums would be lost.
- a distance adjustment within the above-mentioned limits is off, for example known from DE 41 25 508 C2.
- An opposite rotation of the Eccentric bushes cause a change in the distance between the drive shaft and thus the drum-shaped tool carrier.
- the invention is based on the object To specify punching device in which a significant increase in radial Distance between the two punch drums is possible.
- An advantageous embodiment of the invention provides that the drum-shaped Tool carrier for making a large radial change in distance by one to pivot the axis of rotation parallel to the axis of rotation.
- the Tool carrier rotatably mounted on one or both sides on swivel arms.
- a linear guide is proposed according to the invention, at one or both drum-shaped tool carriers rotatable on a slide are stored, which is arranged displaceably on guide rods.
- a first way of realizing the secondary synchronization of the two drum-shaped tool carriers consist of the use of their own motor as a drive for the tool carrier.
- the motors preferably in the form of a step or Linear motors are electronically controlled, with a microprocessor The speed of both motors is monitored and control pulses are triggered if there is a speed difference sends one or both motors to achieve synchronism.
- An alternative embodiment of the invention provides secondary synchronization with the help of chain or toothed belt wheels, each indirectly or are directly connected to the rotating tool carriers in a rotationally fixed manner. Under Interposition of a compensating mechanism through the radial Change in distance between the two drum-shaped tool carriers Change in the course of the timing belt compensated.
- the Tension in the belt preferably kept constant.
- the compensation mechanism consists essentially of a deflection wheel that the Change in the course of the synchronization belt follows. This can be done, for example, by linear guidance of the deflection wheel takes place, with a change in position of the deflection wheel against the spring force of a spring element, so that also a return to the original position is guaranteed.
- An advantageous embodiment of the invention alternatively provides the deflection wheel to attach to an angle lever, which is operated via a connecting rod. Since in the course of radial changes in the distance between the tool carriers, the angle levers and the If the connecting rod moves relative to each other, a Pivotal movement of the angle lever and thus to adjust the deflection wheel to the extent that the timing belt is changed.
- the connecting rod has a tension spring between the connecting rod and the fixed bearing point of the Connecting rod works.
- the spring force applied by the tension spring is used for Timing belt tension.
- the resilience can be Adjustable using a screw nut placed on the connecting rod his.
- an embodiment of the invention is preferred in which by use Another deflection wheel influences the course of the synchronization belt is that as large a contact area as possible between the drive belt and the toothed belt wheels.
- the enlargement of the contact area ensures greater security in achieving synchronization of the two tool carriers.
- the drive for the drum-shaped tool carrier is advantageously used the means for secondary synchronization.
- the drive motor can its drive sprocket directly on the belt for synchronization or else via another chain or toothed belt wheel with the synchronization belt be coupled. The latter case enables the diameter of the Chain or toothed belt wheels perform a step-up or step-down on the Drive side.
- drum-shaped tool carrier not on both sides on a continuous shaft, but at least only one of the two drum-shaped tool carriers to store on one side. This has the advantage of also axially inserting the material to be cut To be able to thread passage gap between the two tool carriers.
- FIG. 1 is a rectangular Designated footplate, from which two axially opposite one another Guide rods 2 protrude.
- the upper ends of the guide rods 2 carry one Head plate 3, which is arranged in a plane parallel to the foot plate 1 and in the Vertical projection with this is congruent.
- Both the footplate 1 and the Head plate 3 have a circumferential offset 4 at its edge, which for Includes housing walls, not shown.
- the footplate 1 has one circular opening 6 on (Fig. 1) through which the accumulating during operation Punching waste is passed out of the housing.
- the guide rods 2 are in the lower region of one of the guide rods 2 connecting camp chair 7 with a front 10 and a rear 11 fixed enclosed, which is also connected to the base plate 1. Footplate 1, Guide rods 2 and bearing chair 7 thus form a rigid unit.
- the middle part 8 of the bearing bracket 7 bridging the distance between the guide rods 2 forms a pivot bearing for a hollow shaft 9 which rotates about a horizontal axis 14.
- a hollow shaft 9 which rotates about a horizontal axis 14.
- On at the front end of the hollow shaft 9 is a cylindrical coaxial Centering pin 12.
- On the opposite rear end of the hollow shaft 9 a coaxial shaft nose 13 is also set.
- the middle part 8 of the bearing chair 7 has on the front 10 a coaxial around the Centering pin 12 extending circular disc-shaped depression 15 ( Figure 1), the one on the centering pin 12 stationary gear 16 receives.
- the centering pin 12 one-sided through a front disk body 17th closed perforated drum 18 as a stamping die, the outer circumference with a Sequence of radially aligned cutting holes 19 is provided.
- the bearing slide 21 is composed lateral vertical guide bushes 22 which are slidable on the guide rods 2 sit and a middle part 23 connecting the guide bushings 22 for training a pivot bearing.
- the bearing slide 21 is thus able to perform a linear movement run along the guide rods 2.
- a spindle drive 24 is provided as the drive for the linear movement Adjustment spindle 25 in the middle and axially parallel between the guide rods 2 in one screwed to the head plate 3 screw bearing 26 is freely rotatable.
- the Adjustment spindle 25 interacts with a spindle nut 27 which is centered on the Top of the middle part 23 of the bearing carriage 21 is attached.
- a vertical bore 28 in the Middle part 23 introduced to the adjusting spindle 25 during a lifting movement of the To be able to accommodate slide 21.
- That from the top of the head plate 3 projecting end of the adjusting spindle 25 carries a handwheel 29 for actuating the Spindle drive 24.
- the bearing slide 21 leads one linear lifting and lowering movement, which is limited by the top plate 3 is and down by spacers 40 which on the top of the bearing block 7th are loosely arranged in the area around the guide rods 2.
- the middle part 23 of the bearing slide 21 connecting the two guide bushings 22 again forms a pivot bearing for a hollow shaft 29 which is horizontal and for Axis 14 rotates parallel axis 30.
- the front end of the hollow shaft 29 carries a coaxial centering pin 31.
- On the opposite rear end of the Hollow shaft 29 in turn has a coaxial shaft nose 32.
- a coaxial toothed belt wheel 39 is fixed to the shaft nose 32 screwed.
- the hollow shaft 29, the centering pin 31, the Shaft nose 32, gear wheel 34, punch drum 36 and toothed belt wheel 39 a rigid unit rotating about the axis 30, which is stationary with respect to the Bearing carriage 21, but linearly displaceable with respect to the guide rods 2 the base plate 1 or head plate 3 is arranged.
- the bearing slide 21 In the operating state, the bearing slide 21 is in the lowered position, wherein the underside of the bearing carriage 21 makes direct contact with those on the top of the Bearing chair 7 has spacers 40 lying.
- the lowered position can by Actuation of the spindle drive 24 can be achieved, the spacers 40 a form the stop limiting the lowering movement.
- the perforated drum 18 and the punch drum 36 lie with it their circumference in a small radial defining a passage gap 41 (FIG. 4) Distance opposite.
- the passage gap 41 serves the horizontal and with respect to the Perforated drum 18 or punch drum 36 does not perform tangentially punched goods shown.
- the height of the passage gap 41 becomes dependent the thickness of the punched material by using spacers 40 of different thicknesses set.
- the perforated drum 18 and the punch drum 36 are in one defined relative position to each other, in which the cutting punch 37 in the course of engage counter-rotating rotation in the cutting holes 19. That it defined relative position of the perforated drum 18 and punch drum 36 to one another remains achieved by a primary synchronization with the help of gears 16 and 34, which at comb the lowered carriage 21 together.
- Low Distance adjustments in the millimeter range to adapt to the thickness of the punched material are compensated for by a suitable design of the tooth flanks, whereby the requirement is that the backlash must be less than the cutting clearance between cutting punch 37 and cutting holes 19.
- Perforated drum 18 and punch drum 36 are on the back of the Device according to the invention, means for a secondary synchronization provided, which are shown in particular in FIG. 3.
- the secondary synchronization means include those already included described toothed belt wheels 20 and 39 additionally a deflection wheel 42 and Compensation mechanism 43.
- the deflection wheel 42 is in the immediate vicinity of the Toothed belt wheel 20 and in one plane with this rotatable on the central part 8 of the Bearing chair 7 attached.
- the compensating mechanism 43 has a two-armed angle lever 44 which a fixed fulcrum 45 pivotally mounted with respect to the bearing block 7 is.
- the vertical arm of the bell crank 44 rotates at its end mounted deflection wheel 47.
- the horizontal arm is articulated at its end a spring-loaded connecting rod 49, the other end in the bearing point 50 is attached to the bearing slide 21.
- the bearing point 50 enables storage of the Connecting rod 49 with two degrees of freedom, the pivoting movement of the Connecting rod 49 around the bearing point 50 and a longitudinal displacement of the Allow connecting rod 49 radially to bearing point 50.
- the connecting rod 49 is over one Part of its length is surrounded by a compression spring 51, the spring force of which on the Connecting rod 49 seated adjusting nut 53 is adjustable, in that of the Adjusting nut 53 is biased against the bearing point 50.
- the spring 51 applies a compressive force to the end of the horizontal arm of the bell crank 44, which causes an outward sideways movement of the deflection wheel 47.
- the secondary synchronization means comprise a closed and double-sided toothed belt 52 which runs over the upper toothed belt wheel 39 and is continued with changing the contact side to the lower toothed belt wheel 20.
- the Toothed belt 52 passed over the pulley 42 and from there to Compensation mechanism 43, where a return to the upper via the deflection wheel 47 Toothed belt wheel 39 takes place.
- the tension of the toothed belt 52 is in the described type achieved via the setting of the pressure force of the spring 51.
- the operation of the compensating mechanism 43 is shown when lifting the Bearing slide 21 from the lowered operating position in the direction of the head plate 3.
- the vertical movement taking place is via the bearing point 50 on the Connecting rod 49 and further on the end of the horizontal arm of the Transfer lever 44, which then pivots around the fixed Pivot 45 executes. Due to the swivel movement, a Horizontal movement of the deflection wheel 47 seated at the end of the vertical arm initiated, the amount of which corresponds exactly to the vertical movement.
- the Toothed belt 52 ensures the synchronization of even at a large distance Hole drum 18 and punch drum 36, which ensures that when Lowering the bearing slide 21 in the operating position engaging the gears 16 and 34 takes place and the primary synchronization is thus restored.
- the drive for the rotary punching device according to the invention is also from FIG 3 can be seen.
- the toothed belt wheel 55 and the deflection wheel 42 are non-rotatably on a common shaft, so that the Rotation of the toothed belt wheel 55 is transmitted to the smaller deflection wheel 42 and such a reduction of the drive is realized.
- the drive for the punch drum 36 and the perforated drum 18 thus takes place starting from the deflection wheel 42, which over the Toothed belt 52 and the toothed belt wheels 20 and 39 drives the hollow shafts 9 and 29.
- the speed of the drive motor can be regulated via its torque, which the The advantage is that adaptation to fluctuating throughput speeds of the punched material takes place independently.
- Another way of controlling the Drive motor can be determined by detecting the actual throughput speed, for example using a measuring wheel. From the actual Throughput speed can then determine a control pulse for the drive motor and be transferred.
- FIG. 5 An alternative embodiment of the invention for synchronizing the rotation of the Stamping drum 36 and perforated drum 18 are shown in FIG. 5.
- the basic structure of the rotary punching device corresponds to that of the storage chair 7, the bearing slide 21, the punch drum 36th and the perforated drum 18 and the Gears 16 and 34 of those described in Figures 1 to 4, so that for the same Parts with the same reference numerals are used.
- the secondary synchronization takes place via a Microprocessor 60, the data cable 61 and 62 with both motors 56 and 58 is connected and monitors the respective speed of the two motors 56 and 58, compares with each other and in the event of a speed difference control pulses to one or both motors 56, 58 are transmitted to achieve synchronization.
- the primary Synchronization takes place as described under Figures 1 to 4 using the Gears 34 and 16.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Forests & Forestry (AREA)
- Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
Abstract
Description
- Fig. 1
- eine Schrägansicht auf eine erfindungsgemäße Stanzvorrichtung,
- Fig. 2
- eine Vorderansicht auf die in Fig. 1 dargestellte Stanzvorrichtung,
- Fig. 3
- eine Rückansicht der in Fig. 1 dargestellten Stanzvorrichtung,
- Fig. 4
- einen Vertikalschnitt durch die erfindungsgemäße Stanzvorrichtung entlang der in Fig. 3 dargestellten Linie IV-IV und
- Fig. 5
- eine schematische Darstellung einer alternativen Anordnung zur Synchronisation zweier trommelförmiger Werkzeugträger.
Claims (15)
- Vorrichtung zum rotativen Stanzen von Stanzgut, insbesondere von extrudierten Endlosprofilen,
mit einem um eine erste Achse (30) rotierenden trommelförmigen Werkzeugträger (36), der über den Umfang verteilt radiale Schneidstempel (37) aufweist und mit einem um eine zweite Achse (14) rotierenden trommelförmigen Werkzeugträger (18), der über den Umfang verteilt radiale Schneidlöcher (19) aufweist, wobei die erste Achse (30) und zweite Achse (14) achsparallel und im Abstand zueinander derart angeordnet sind, dass zwischen dem ersten Werkzeugträger (36) und dem zweiten Werkzeugträger (18) ein radialer Abstand zur Bildung eines Durchtrittsspalts (41) für das Stanzgut vorhanden ist und dass die über den Umfang hinausragenden Schneidstempel (37) im Zuge der gegenläufigen Rotation der trommelförmigen Werkzeugträger (36, 18) in die Schneidlöcher (19) eindringen,
und mit primären Synchronisationsmitteln für den Gleichlauf der beiden trommelförmigen Werkzeugträger (36, 18), die ein erstes Zahnrad (34) umfassen, das koaxial zur ersten Achse (30) und ortsfest bezüglich des ersten trommelförmigen Werkzeugträgers (36) angeordnet ist und ein zweites Zahnrad (16) umfassen, das koaxial zur zweiten Achse (14) und ortsfest bezüglich des zweiten trommelförmigen Werkzeugträgers (18) angeordnet ist, wobei das erste Zahnrad (34) und das zweite Zahnrad (16) miteinander kämmen,
dadurch gekennzeichnet, dass der erste trommelförmige Werkzeugträger (36) und/oder der zweite trommelförmige Werkzeugträger (18) zur Herstellung eines großen radialen Abstands entlang einer Bahn derart verschieblich gelagert sind, dass die Zähne des ersten Zahnrads (34) und die Zähne des zweiten Zahnrads (16) nicht mehr miteinander in Eingriff stehen und dass sekundäre Synchronisationsmittel zur Einhaltung des Gleichlaufs bei großem radialem Abstand der beiden trommelförmigen Werkzeugträger (36, 18) angeordnet sind. - Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass zur Veränderung des radialen Abstands wenigstens ein trommelförmiger Werkzeugträger (36, 18) an einem oder mehreren Schwenkarmen drehbar gelagert ist, wobei der oder die Schwenkarme um ein zur ersten und zweiten Achse achsparalleles Achslager verschwenkbar sind.
- Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass zur Veränderung des radialen Abstands wenigstens ein trommelförmiger Werkzeugträger (36, 18) an einem Schlitten (21) drehbar gelagert ist, der entlang von Führungsstangen (2) verschiebbar ist.
- Vorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Schlitten (21) oder die Schwenkarme mit Hilfe eines Spindeltriebs (24) bewegbar sind.
- Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Synchronisationsmittel zur Einhaltung des Gleichlaufs bei großem radialem Abstand einen ersten Motor (56) zum Antrieb des ersten trommelförmigen Werkzeugträgers (36) und einen zweiten Motor (58) zum Antrieb des zweiten trommelförmigen Werkzeugträgers (18) umfassen, wobei der Gleichlauf des ersten Motors (56) und des zweiten Motors (58) elektronisch gesteuert ist.
- Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die Vorrichtung einen Mikroprozessor (60) aufweist, der per Datenleitungen (61, 62) mit beiden Motoren (56, 58) verbunden ist und der die aktuellen Rotationsgeschwindigkeiten der trommelförmigen Werkzeugträger (36, 18) miteinander vergleicht und bei abweichenden Rotationsgeschwindigkeiten einen Steuerimpuls errechnet und an zumindest einen der beiden Motoren (56, 58) ausgibt.
- Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die sekundären Synchronisationsmittel ein erstes Ketten- oder Zahnriemenrad (39) umfassen, das koaxial zur ersten Achse (30) und ortsfest zum ersten trommelförmigen Werkzeugträger (36) angeordnet ist und ein zweites Kettenoder Zahnriemenrad (20) umfassen, das koaxial zur zweiten Achse (14) und ortsfest mit dem zweiten trommelförmigen Werkzeugträger (18) angeordnet ist, wobei die beiden Ketten- oder Zahnriemenräder (39, 20) über eine geschlossene Kette oder Zahnriemen (52) miteinander verbunden sind und dass die sekundären Synchronisationsmittel weiter einen Ausgleichsmechanismus (43) umfassen, durch welchen die Kette oder der Zahnriemen (52) zur Kompensation der radialen Abstandsänderung zwischen dem ersten Werkzeugträger (36) und dem zweiten Werkzeugträger (18) geführt ist.
- Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass der Ausgleichsmechanismus (43) ein Umlenkrad (47) aufweist, das unter Beibehaltung der Spannung in der Kette oder dem Zahnriemen (52) in der Ebene der Kette oder des Zahnriemens (52) verschieblich gelagert ist.
- Vorrichtung nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass der Ausgleichsmechanismus (43) einen zweiarmigen Winkelhebel (44) aufweist, der an einem ortsfest gegenüber des einen trommelförmigen Werkzeugträgers (18) drehbar gelagert ist und dessen erster Arm ein Umlenkrad (47) für die Kette oder den Zahnriemen (52) aufweist und dessen zweiter Arm über eine Pleuelstange (49) ortsfest gegenüber dem anderen trommelförmigen Werkzeugträger (36) verbunden ist.
- Vorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass die Pleuelstange (49) mit einer Spannfeder (51) versehen ist, vorzugsweise mit einer in der Federkraft einstellbaren Spannfeder (51).
- Vorrichtung nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass der Winkelhebel (44) derart ausgebildet und angeordnet ist, dass eine im wesentlichen vertikale radiale Abstandsänderung in eine im wesentlichen horizontale Ausgleichsbewegung umsetzbar ist.
- Vorrichtung nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass in der Ketten- oder Zahnriemenebene mindestens ein weiteres Umlenkrad (42) zur Vergrößerung der Kontaktfläche zwischen der Kette oder dem Zahnriemen (52) und dem ersten oder zweiten Zahnriemenrad (39, 20) angeordnet ist.
- Vorrichtung nach einem der Ansprüche 7 bis 12, dadurch gekennzeichnet, dass der Antrieb für die trommelförmigen Werkzeugträger (36, 18) auf die Kette oder den Zahnriemen (52) der sekundären Synchronisationsmittel einwirkt.
- Vorrichtung nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass die Dicke des Durchtrittsspalts (41) durch Distanzscheiben (40) definiert ist, die in der Kontaktfläche zwischen der Lagerung des ersten trommelförmigen Werkzeugträgers (36) und der Lagerung des zweiten trommelförmigen Werkzeugträgers (18) angeordnet sind.
- Vorrichtung nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass zumindest ein trommelförmiger Werkzeugträger einseitig gelagert ist, vorzugsweise beide trommelförmigen Werkzeugträger (36, 18).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SI200330098T SI1419861T1 (sl) | 2002-11-18 | 2003-11-08 | Priprava za preoblikovanje gradiva, zlasti ekstrudiranih brezkoncnih profilov, s krozilnim stanjcanjem |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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DE20217870U | 2002-11-18 | ||
DE20217870 | 2002-11-18 | ||
DE20306090U DE20306090U1 (de) | 2002-11-18 | 2003-04-15 | Vorrichtung zum rotativen Stanzen von Stanzgut, insbesondere von extrudierten Endlosprofilen |
DE20306090U | 2003-04-15 |
Publications (2)
Publication Number | Publication Date |
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EP1419861A1 true EP1419861A1 (de) | 2004-05-19 |
EP1419861B1 EP1419861B1 (de) | 2005-09-28 |
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EP03025561A Expired - Lifetime EP1419861B1 (de) | 2002-11-18 | 2003-11-08 | Vorrichtung zum rotativen Stanzen von Stanzgut, insbesondere von extrudierten Endlosprofilen |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1419861B1 (de) |
AT (1) | ATE305372T1 (de) |
DE (1) | DE50301255D1 (de) |
DK (1) | DK1419861T3 (de) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008024681A1 (de) * | 2008-05-21 | 2009-12-03 | WINKLER+DüNNEBIER AG | Maschinengestelltraverse zur Lagerung einer drehbaren Schneidwalze zum Schneiden von Flachmaterialstücken oder Materialbahnen |
DE102010015804A1 (de) | 2010-04-20 | 2011-10-20 | Herter Verpackung Gmbh & Co. Kg | Vorrichtung und Verfahren zur Herstellung von Rollkantenschutzvorrichtungen aus Pappe oder Papier |
CN107521275A (zh) * | 2017-09-30 | 2017-12-29 | 佛山市审美铝业有限公司 | 一种抽芯式管材压花方法及设备 |
CN114589246A (zh) * | 2022-01-25 | 2022-06-07 | 绍兴文理学院元培学院 | 一种金属加工连续冲压装置 |
CN115078759A (zh) * | 2022-07-20 | 2022-09-20 | 岚图汽车科技有限公司 | 一种测风***、测风控制方法及相关设备 |
CN117299947A (zh) * | 2023-11-28 | 2023-12-29 | 河北滚冲精密机械制造有限公司 | 一种滚动式连续冲孔设备 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014102428A1 (de) | 2014-02-25 | 2014-08-28 | Baust Stanztechnologie GmbH | Vorrichtung zum rotierenden Bearbeiten von Bearbeitungsgut |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2353226A1 (de) * | 1973-10-24 | 1975-05-07 | Welte Maschinenbau Kg Konstruk | Stanzvorrichtung fuer das ausschneiden im freischnitt |
EP1145791A1 (de) * | 1999-06-04 | 2001-10-17 | Mitsubishi Heavy Industries, Ltd. | Fliegende schere mit zylindrischem drehkörper |
-
2003
- 2003-11-08 EP EP03025561A patent/EP1419861B1/de not_active Expired - Lifetime
- 2003-11-08 DK DK03025561T patent/DK1419861T3/da active
- 2003-11-08 DE DE50301255T patent/DE50301255D1/de not_active Expired - Lifetime
- 2003-11-08 AT AT03025561T patent/ATE305372T1/de active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2353226A1 (de) * | 1973-10-24 | 1975-05-07 | Welte Maschinenbau Kg Konstruk | Stanzvorrichtung fuer das ausschneiden im freischnitt |
EP1145791A1 (de) * | 1999-06-04 | 2001-10-17 | Mitsubishi Heavy Industries, Ltd. | Fliegende schere mit zylindrischem drehkörper |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008024681A1 (de) * | 2008-05-21 | 2009-12-03 | WINKLER+DüNNEBIER AG | Maschinengestelltraverse zur Lagerung einer drehbaren Schneidwalze zum Schneiden von Flachmaterialstücken oder Materialbahnen |
DE102010015804A1 (de) | 2010-04-20 | 2011-10-20 | Herter Verpackung Gmbh & Co. Kg | Vorrichtung und Verfahren zur Herstellung von Rollkantenschutzvorrichtungen aus Pappe oder Papier |
CN107521275A (zh) * | 2017-09-30 | 2017-12-29 | 佛山市审美铝业有限公司 | 一种抽芯式管材压花方法及设备 |
CN114589246A (zh) * | 2022-01-25 | 2022-06-07 | 绍兴文理学院元培学院 | 一种金属加工连续冲压装置 |
CN114589246B (zh) * | 2022-01-25 | 2023-09-05 | 绍兴文理学院元培学院 | 一种金属加工连续冲压装置 |
CN115078759A (zh) * | 2022-07-20 | 2022-09-20 | 岚图汽车科技有限公司 | 一种测风***、测风控制方法及相关设备 |
CN117299947A (zh) * | 2023-11-28 | 2023-12-29 | 河北滚冲精密机械制造有限公司 | 一种滚动式连续冲孔设备 |
CN117299947B (zh) * | 2023-11-28 | 2024-02-13 | 河北滚冲精密机械制造有限公司 | 一种滚动式连续冲孔设备 |
Also Published As
Publication number | Publication date |
---|---|
ATE305372T1 (de) | 2005-10-15 |
DK1419861T3 (da) | 2006-02-06 |
DE50301255D1 (de) | 2006-02-09 |
EP1419861B1 (de) | 2005-09-28 |
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