DE2361405A1 - CUTTING DEVICE FOR EXTRUDED PROFILES - Google Patents

Description

Separating device for extruded profiles

Device for cutting or cutting to length extruded Profiles, in particular hollow profiles, with a rotatable cutting head which is arranged on a slide and which has at least a cam-controlled, radially displaceable chamfering, separating or Having cutting tool.

It is known in the manufacture of extrusion Plastic profiles to receive the extruded part emerging from the nozzle of the extruder from a haul-off machine and to be fed to a cutting machine in which the profiles are cut to the required length. The device carrying the separating or cutting tools has a movable in the longitudinal direction with the extruded profile Carriage and one or more cutting tools rotatably arranged on the carriage as well as a device for radial Advance of the cutting tools against the extruded profile or back from it.

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When cutting hollow profiles, for example pipes or hoses, the separating or cutting tools become radial brought up to the hollow profile, or guided away from it. Because during this process both a translational movement with the profile as well as a radial movement, the control of these movements brings considerable difficulties with it, especially if the profile has to be chamfered or beveled with a tool before the actual cutting.

The object of the invention is to remedy these difficulties and one in the longitudinal direction and one in the radial direction to create movable, precisely controllable device for separating and cutting to length of extruded profiles in a simple manner.

This object is achieved dadureh according to the invention ^5, that the tool is assigned to a revolving with the cutter head lever mechanism, which that the eccentric disk associated with a likewise rotating with the cutting head, however, is relative to said rotatable eccentric disc in engagement and the relative movement generating device is, and that the curve shape of the eccentric disk is selected such that a radial feed movement of the tool can be generated with each relative movement between the eccentric disk and the cutting head.

In this way, a self-contained control system is created which is relatively less mechanically stressed and which is consequently subject to less wear than the previously known control devices.

The cutting head preferably carries two tools, one of which is an eccentric disk rotating with the cutting head Drivable lever mechanism is assigned, the two eccentric disks preferably lying next to one another and together are arranged rotatably.

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To bring about a change in the work cycle of the tools, are the. both eccentric disks adjustable relative to each other. . : ■ ".-...

The relative movement between the eccentric disk or the Eccentric discs and the cutting head can be used in different ways Wise trained institutions take place. Preferably. is the eccentric disc with a segment of a circle of the Cutting head surrounding movable annular sleeve connected and is a drive device for. Drive the Sleeve and the cutting head provided with the same angular velocity, the relative movement between the eccentric and cutting head causing device a relative angular movement between the sleeve and the cutting head causing Change the drive speed allows.

This drive device has a 'further feature According to the invention, a first toothed washer arranged on the sleeve and a wide toothed washer arranged on the cutting head each of which interacts with a toothed belt and via a common drive shaft in the same transmission ratio are drivable *

According to a further feature of the invention, the device which enables relative movement consists of a tensioning roller arrangement, over which one of the toothed belts is guided, a device being provided with the aid of which two Tensioning rollers of the arrangement are movable in such a way that the over a change in speed can be imposed on the respective toothed pulley guided toothed belt. These two Tensioning rollers are arranged on a movable slide that can be actuated by pressure medium.

In a further embodiment of the inventive concept are at the idler assembly two symmetrical to each other on opposite sides one through the axles

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the common drive shaft and the toothed pulleys Arranged level, the distance between the tensioning rollers and cLen toothed pulleys is less than that between tensioning rollers and drive shaft and the idler assembly has another symmetrical one on opposite sides of the mentioned level, located at a smaller distance from the drive shaft tensioning roller pair on and a third pair of tensioning rollers, which is arranged on the carriage reciprocable perpendicular to said plane in the space between the first and the second tensioning roller pair, wherein the toothed pulley from the drive wheel on the common drive shaft via the third, fifth and first tensioning pulley of the Arrangement and over die.jeweils assigned toothed pulley as well as over the second, sixth and fourth tension pulley back to the Drive wheel is guided.

The first toothed disk is according to a further feature of the invention movable relative to the sleeve * and a first releasable locking device is provided via which the the first toothed disk can be locked in a position that can be rotated with the sleeve, as well as a second locking device, via which the sleeve can be locked with the cutting head for the purpose of moving together, '

The invention is described below with reference to the drawings an exemplary embodiment explained in more detail. Show it:

Fig. 1 is a side view of a separating device in which the

For the sake of clarity, parts have been omitted; FIG. 2 shows a section along the line II from FIG. 1; FIG.

FIG. 3 is a plan view of part of the device in FIG Direction of arrow III in Fig ... 2; -

4 shows a cross section through another part of the separating device nach'Linie IV-IV from Fig. 2 and

Figure 5 is a view of another part of the separator in the direction of arrow V from FIG. 4

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The device for separating or cutting to length of extruded profiles contains, as from Pig. 1 shows a frame 1 which is movable on rollers 2 and can be secured in its position via retractable footrests 3. Two rails 4 running parallel to one another are connected to the frame 1, as well as a main slide 5 on which rollers 6 are arranged, which engage in the rails 4, so that the slide is freely movable to and fro on the rails. The main slide 5 has a front and a rear clamping device 7 and 8, the respective moving parts of which can be actuated via air pistons 9 and Io. The main slide 5 contains a guide tube 11 (FIG. 4) which receives the extruded profile exiting from a nozzle of an extrusion press in a manner not shown here, on which a cutting head 12 rotatably mounted via bearings 1J and 14 is arranged. -.

The guide tube 11 is coaxial with that shown in FIG Clamping devices arranged.

During operation, the device is arranged so that the axis of the guide tube 11 is the axial extension a take-off device, not shown, and the extrusion mold, also not shown, forms. The. Extruded Profile passes through the clamping device 7 and 8 (Fig. 1) and the bore of the guide tube 11. As soon as the clamping devices capture the profile, so the main slide 5 move with the profile together along the rails 4, wherein the still to be described cutting head around the profile can rotate. In this way, profiles of the most varied Diameter according to the largest diameter. the knife of the clamping devices. ■

The cutting head 12 rotatably mounted on the guide tube 11 (FIG. 4) has a spacer sleeve J.5 which, between the Ball bearings 13 and 14 is arranged and another Sleeve 16; one end of which is designed as a flange 17 is. With the sleeve l6 is a first, the drive "'

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the cutting head serving toothed washer 19 via threaded pin, for example the pin 18 connected.

A bearing sleeve Io encloses part of the sleeve and l6 takes about "a wedge 21 with her firmly connected eccentric 22 and 23 on. A pressure piston 24 is located inside the sleeve 16 arranged displaceably, which is connected via a wedge 25 'to the sleeve for common rotation. The piston 24 is acted upon by a helical spring 26 in such a way that that he is in one of four at the same distance νJ from one another recesses 27 lying in the side surface of the eccentric 22 can intervene. The piston 24 and the associated recesses 27 are designed so that a rotation of the eccentric 22,2 ^ counterclockwise (see. Fig. 2) with respect to the sleeve 16 is possible when the piston from the '· ■ ■ Recesses runs out, while a clockwise rotation due to the engagement of the piston in one of the recesses is prevented.

A second toothed disk 28 is located in the area of the eccentric 23 arranged rotatably around the bearing sleeve 2o. A plunger 29 is arranged displaceably in the toothed disk and is firmly connected to it via a wedge Jo. The plunger is acted upon by a cylinder spring 31 such that it is in a of four recesses provided at the same distance from one another, e.g. in recess 32 in one end face of the eccentric 23 can intervene. The piston 29 and the Recesses 32 are formed so that rotation of the Toothed disk 28 with respect to the eccentrics 22,23 clockwise, however, the opposite is not possible.

The toothed disk 19 is connected to a toothed wheel 34 via a Toothed belt 33 (Fig. L) driven, with the gear on one stored in bearings 36 and 37 and via an electric motor 38 driven drive shaft 35 is seated. The dental

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Disk 28 is driven via a toothed belt 39 connected to a toothed wheel 4o (FIG. 1) on the drive shaft 35. The lter toothed belt is guided over a roller system which has upper tensioning rollers 41 and 42 and lower fixed tensioning rollers 45 and 44 (FIG. 2). The toothed belt is guided between the tensioning rollers 41 and 43 via a further tensioning roller 45 and between the tensioning rollers 42 and 44 via a tensioning roller 46. The tensioning rollers 45 and 46 are rotatable on, not shown, on. an auxiliary slide 47 provided. waves arranged. The auxiliary slide 47 is on a rail 48 in the direction of the double arrows in FIG. 2. movable. The auxiliary slide 47 has rollers 49 and 5o (FIG. 3) which engage in the rail 48. In addition, the auxiliary slide is connected via a cross member 51 to the cylinder 52 of an air pressure piston, the piston rod 55 of which is connected to a cross member 5 ^ firmly connected to the frame of the main slide 5. (Fig. 3). When the piston is actuated, the auxiliary slide 47 can move between the position shown in FIG. 2 and a corresponding end position indicated by dashed lines in FIG. 2. ·

On the front surface of the flange 17, which is not shown in FIG. 1, two tools are arranged, a chamfering and a a cutting or parting tool. In the drawings, only the control for the cutting tool is shown, since the Control of the chamfering tool is identical to that of Control arrangement for the cutting tool, however, on flange 17 is arranged at an angular distance from this. That Cutting tool 55 is in one via an adjusting screw 56 Tool carrier 57 attached, and is guided by a guide 58 in a guide device 59 (Fig. 5). Of the Tool carrier 5.7 has centering pins 60 and 6l which in each case in bores 62 or 63 in the guide device 59

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can intervene. The centering pins are each made of a cylinder spring 64 and 65 enclosed by which the tool carrier and the guide device 59 according to Figure 5 at a distance be kept from each other. The tool guide 59 is connected to the flange 17 in such a way that it is connected to the sleeve 16 is rotatable. A feed lever 66 for the tool acts on a part of the tool carrier 57 and is with a shaft 67 passed through flange I7, which is rotatably mounted on the flange. The other end of the shaft 67 has a lever 68 on his free end carries a plunger roller 69, which with the eccentric is engaged.

Anyone? Eccentrics 22 and 23 white; four equally spaced mutually arranged elevations or cams. With each rotary movement of the eccentric with respect to the sleeve 16, in the If a cam comes under the ram roller 69, the levers 68 and 66 pivot in such a way that the tool carrier and thus also the tool can be moved radially inward with respect to FIG. The angular distance between the eccentrics 22 and 23 is chosen so that cutting and beveling tools are not moved radially at the same time during a work cycle.

The mode of operation of the device described is as follows:

As already mentioned, the extruded profile gets into the Drill the tube 11 and it must now be a rotating chamfering tool be introduced to the scope of the profile, after which After the chamfering, a cutting tool cuts through the extruded profile according to the length required in each case.

For this purpose, the electric motor 38 drives the shaft 35. the Toothed pulleys 33 and 39 transmit the drive to the toothed pulleys 19 and 28. About the toothed washer 19, the sleeve l6, the Flange 17 and the cutting tools arranged thereon in the direction of the arrow in Fig. 5 moves clockwise. By

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When the toothed disk 28 is rotated counterclockwise, the piston 29 is moved against the recess J52, so that the eccentrics 22 and 23 and the bearing sleeve 2o are driven by the toothed disk 28. Since the transmission ratio between the shaft J55 and the toothed disks 19 and 28 is the same, there is no relative movement between the toothed disks 19 and 28 during normal operation, and the eccentrics 22 and 23 rotate at the same speed as the sleeve. 16. The cam follower 69 for the cutting tool 55 now rests on part of the circumference of the eccentric 23, while the cam follower for the beveling tool cooperates with a corresponding part of the eccentric 22. There is no relative movement between the eccentrics and the cam followers, so that the control levers for the tools both assume the position shown in FIG. the tools are in their outermost end position radially. By the force of the springs 64 and 65 and by the centrifugal force generated during drive, the tools are held in this position, see "also FIG. 5. The lever 66 is a vertically extending shaft 67 for the rod 7ο connected" at its The free end carries a balancing weight 71 which can be adjusted in any desired position.

For cutting small diameter profile strands to length the cutting tool must move further inwards in the radial direction moved and in this new position by the adjusting screw secured. In this case, lower Centrifugal forces are balanced, and the balance weight is to be found accordingly closer to the shaft 67.

The auxiliary slide 4.7 is located during normal operation, which carries the tension rollers 45 and 46, in the one shown in FIG position shown in solid lines. . ,

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For the radial advance of the tools until they attack the extruded profile, the auxiliary slide 47 is via the Air pressure piston 52 and the piston rod 55 in the in Figure position shown in dashed lines. As a result of this movement, the toothed belt 59 becomes somewhat in its upper area accelerated, so that the toothed disk 28 is driven faster than the toothed disk 19. Through this acceleration the toothed disk 28 are the eccentrics 22 and 25 and the Bearing sleeve 2o driven counterclockwise relative to the sleeve l6. The piston rod 24 arrives during this Drive the eccentrics 22 and 25 out of the recess 27. During this movement, the cams of the eccentrics are moved beyond the cam followers, so that the associated levers 67, 68 be pivoted for the radial advance of the tools until they attack the extruded profile. The cams of the eccentric 22 and 25 have a certain angular distance, so that During the relative movement of the eccentrics, a cam on the eccentric 22 actuates the chamfering tool before a cam on the eccentric 25 actuates the cutting tool. Through the Configuration of the eccentric determines the work cycle of the respective tools and the correct work sequence of tools guaranteed.

The path of the auxiliary slide 47 is dimensioned so that between the eccentrics 22, 25 and the sleeve l6 essentially one Relative movement of 90 ° takes place; At the end of this rotary movement, the piston 24 moves into the next recess 27, so that the eccentrics are fixed and rotate together with the sleeve l6. The return of the auxiliary slide 47 in the position shown in solid lines also takes place via the air pressure piston 52. Since the eccentric during of the return are held by the piston 24, the piston 29 disengages from the recess 52 so that between the ■ Toothed disk 28 and the eccentrics 22 and 25 a relative movement is possible. The rotation of the toothed disk 28 relative to the gear wheel and the sleeve 2o is slowed down. Get through this the parts to their starting position for a new work cycle

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return. During the next work cycle, the described drive connections actuated by the next following cams on the eccentrics »

During each work step, the söhaltwirikel is between the eccentrics and the sleeve essentially 90 ° * so that four cams on the eccentrics are required for compliance with the correct work sequence. The choice of others Switching angle for the cutting process would require a corresponding change in the number of elevations on the eccentrics. For example, there could be three ridges in one angular movement of 20 ° between the eccentrics and the sleeve can be provided for one cutting process or two for a corresponding angular movement of 18Ö. In addition, it can be provided that the eccentrics 22 and 25 with respect to the device in the stationary state are adjustable · so that the time sequence in the advance of chamfering and Cutting tool is adjustable. The arrangement 'of the tensioning rollers can of course also from the may differ from the arrangement described, and instead of the toothed belt drive a differential gear can be selected. For example, the eccentric and the sleeve of one or several motors are driven at different speeds, the drive system in this Pail an overrunning clutch would have to contain the relative movement at the desired point in time.

The eccentric and the sleeve could also be driven by separate motors, or by a common motor, whereby the drive ratio between motor and eccentrics or motor and sleeve changing gear would be provided.

To ensure a vibration-free run, can the air pressure piston actuating the auxiliary slide 47 parallel to a hydraulic damping device

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are switched, due to which the speed of movement of the slide does not exceed a predetermined maximum value exceeds. The connection between the cam followers and the tools and the means for guiding the tools can also differ from the type described.

Patent claims:

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Claims (13)

P a t ent requests 1.) Device for separating or cutting to length extruded profiles, in particular hollow profiles, with a rotatable cutting head arranged on a slide, which has at least one 'cam-controlled, radially, displaceable chamfering, separating or cutting tool, thereby geke η η ζ calibrated η et that the tool (55) with the cutting head (12) revolving lever mechanism (66,67, 68) is assigned, which is also connected to the _; The eccentric disk (23) revolving around the cutting head but rotates relative to it is engaged, that the eccentric disk (23) is assigned a device (47) generating the relative movement, and that the curve shape of the eccentric disk is selected in such a way that for each relative movement between Eccentric disc and cutting head a radial feed movement of the tool can be generated * 2. Device according to claim 1, characterized in 'that g, the cutting head (12) has two tools (ζ.B "55) which is assigned to a von.einer with the cutter head rotating cam (22 ,, 23) drivable lever mechanism. ' 3 "Device according to claim 2 _S characterized in that both eccentric disks (22, 23) are adjacent and. are arranged so that they can be rotated together * 4. Vorrichtnng according to claims 2 or 3, characterized in that the two eccentric disks (22,23) are adjustable relative to one another in order to change the feed time of the tools. 5 · Device according to claims 1 to 4, characterized characterized in that the eccentric disks are surrounded by a segment of a circle of the cutting head (12) movable annular sleeve (l6) are connected, and that a drive device for driving the sleeve and of the cutting head is provided with the same angular velocity, and that the relative movement between Eccentric disks and cutting head causing a .eine relative angular movement between the sleeve and Allows the cutting head to change the drive speed, 6. Apparatus according to claim 5 * characterized in that that the drive device has one on the sleeve (l6) arranged first toothed disk (19) 'and one on the cutting head (12) arranged, second toothed pulley (28), each of which interacts with a toothed belt (33 or 39) and via a common drive shaft (35) in the can be driven with the same transmission ratio. 7. Apparatus according to claim 6, characterized e t. That the relative movement enabling device consists of a tensioning roller assembly (47) via which one of the toothed belts is guided, and that a device is provided with the help of which two tensioning " rollers of the arrangement are movable so that the -15 · 409824/0 889 O QP Ί U Π ^ respective pulley guided toothed belt a Change in speed is enforceable. 8. Apparatus according to claim 6, characterized in that the first toothed belt (33) on the '. . Tensioner assembly is performed. . ■ ' 9. Apparatus according to claim 7 or 8, characterized in that g e k e η η, that the two tensioning rollers (46,46) of the system on a reciprocating slide (47) are arranged. ''. " 10. The device according to claim 9, characterized in that in the tensioning roller arrangement two symmetrical to one another are arranged on opposite sides of a plane defined by the axes of the common drive shaft (35) and the toothed disks, wherein the distance between the tensioning rollers and the toothed disks is less than that between the tensioning rollers and the drive shaft (35) and that the tensioning roller arrangement has a further tensioning roller pair which is arranged symmetrically to one another on opposite sides of the said plane and is located at a smaller distance from the drive shaft, and that a third A pair of tensioning rollers is provided, which is arranged on the carriage (47) movable to and fro perpendicular to said plane in the space between the first and second pair of tensioning rollers, and that the toothed belt (33) via the third, fifth and first tensioning roller of the arrangement and via the respectively assigned toothed disk and via the second, sixth and fourth tension pulley is led back to the drive wheel. 11. Device according to one of claims 5 to lo, characterized ge denotes that the first toothed disc is movable relative to the sleeve, and that a first 4098 24/0889 releasable locking device (piston 24) is provided, via which the first toothed disk in one with the sleeve (16) rotatable position can be locked, and that a second locking device (29) is provided via the the sleeve (16) can be locked to the cutting head (12) for the purpose of moving together. 12. The device according to claim 11, characterized in that the first locking device a first spring-loaded piston (24) movable with the first toothed disc and which is in one of a plurality on a surface of the eccentric disk or disks arranged recesses (27) can be latched, and that the second Locking device consists of a second spring-loaded piston (29) which is synchronized with the cutting head (12) is movable and in one of a plurality of provided on another surface of the eccentric disc or discs Recesses (32) can be latched. 13. The device according to claim 12, characterized in that that the pistons (24,29) and the associated recesses (27,32) are designed such that the pistons can be moved out of the recesses, such that a Relative movement between the components previously locked in one direction is possible, but that one Relative movement in the opposite direction is prevented. 409824/0889