DE1921344A1 - Core jig - Google Patents

Description

DIPL.-ING. OR KRETZSCHMAR _a hamburct

IUM ITROHHAUII 3 * PATENT ADVERTISER HUF a * 67 43

K / H - John Dusenbery Company, Inc.

Clifton, New Jersey / USA. April 25, 1959

Legal file: 5422

Core jig

(For this application, priority is derived from UK patent application Ser. No. 37.558 / 68 of August 6, 1968.)

The invention relates to a core jig for fastening a tubular core on a drive shaft.

A rotary movement is applied to the tubular core, which is in particular the shape of a tube or another hollow possesses cylindrical object, transferred. In the case of the tubular The core can in particular be a core to be wound with tape material.

The object of the invention is to provide an improved core clamping device to transfer a drive torque to a shaft located in the clamping device, to accurately wind a web onto one in the jig to achieve fortified core.

The core clamping device according to the invention should be designed so that it is possible to use the central drive shaft the core jig exactly parallel to the axis of the winding drum or some other part on which the tubular Core is attached to hold. In addition, the

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KONTlNi BKIIONIKIANK, KONTO-NK. ··· * · POITICHIOK HAMIUKO NK. 1 ** 76 *

.Kerneinspannvorrichtung according to the invention no eccentricity occur between the clamping device and the core holders

It is difficult to achieve accurate rotary motion of a mounted on a Kerneinspannvorrichtung core, in particular due to the T _a tsache that not only the clamping device is supported by a shaft which is supported at one end only, but the shaft at the upper extremity of a Arm is provided which is of sufficient length that a winding of considerable diameter can be wound on the core.

A preferred field of application of the invention are slitting machines in which sheet-like material, for example a wide roll of plastic film, metal foil or some other web, is passed through a series of guide and smoothing rollers and arrives at a plurality of slitting knives with which the. Web is divided across its width into a number of narrower bands, strips or the like of variable dimensions. The generally used design in modern slitting machines consists in winding up the individual strips produced by the slitting process alternately above and below the feed point or alternately on the front and rear of the machine, so that each of the successive strips does not come into contact with the adjacent strips can be wound up · In a conventional central winding and slitting machine, the tapes are wound up again on cores which are attached to individual winding shafts which are driven to achieve the necessary winding torque. In another embodiment, which is generally more advantageous compared to the device with central winding, the rollers are arranged in such a way that a so-called "central and surface winding ¹¹ is obtained, in which all the strips resulting from the slitting process are wound up again by their surfaces in contact with a

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The full width take-up drum provides most of the torque required to rewind the slotted tapes, typically about 90 % thereof. Each take-up core is mounted on a separate take-up or rewind arm, and the remainder of the torque required for the take-up is usually generated by separate hydraulic motors, one of these motors being provided for each take-up arm. A significant advantage of the center and face winder is that the tapes are wound while they are in contact with the winding drum, which among other things results in a much more compact wound product since the individual tapes are in controllable contact with the winding drum , whereby the air is pressed out between the winding layers, so "that there are largely no air pockets in the winding rollers and a much more tightly wound product is also achieved. If this does not happen, it is possible that air is trapped in the form of thin layers between successive layers, so that the wound tapes can slide or shift in the transverse direction when they are removed from the machine. In this way, the narrow strips do not get the shape of real cylinders with precisely flat end faces when they are rolled over. A particular advantage of the core clamping device according to the invention, arranged on the winding arms of a central and surface slitting machine, is that the fastening of the drive shaft of the core clamping device, which takes place only from one end, together with the exact parallelism that can be achieved, the core clamping device to a large extent for use in central and Makes surface winding devices suitable. The cantilevered arrangement also makes it possible to reduce the transverse distance occupied by each individual winding arm considerably, so that the central and surface winding technique can be used for material of narrow widths to be rolled which was previously not able to be wound by means of the central and surface winding technique.

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The core clamping device created to solve the aforementioned problem is characterized according to the invention by a fixed inner bearing housing through which the drive shaft extends extends, as well as an outer bearing housing and enclosed at an axial distance between the inner and outer bearing housings Bearings, axially aligned core holding members that are slidable along the outer bearing housing, springs carried by the core holding parts and which come into contact with the core when the core holding parts are displaced, as well as a cooperating means engaging both the drive shaft and the core holding members for the axial displacement of the core holding parts when the drive shaft rotates relative to the core holding parts.

The invention will be described by way of in Figs. <\ Illustrated to 3 of the drawing, particularly preferred embodiment of a Kerneinspannvorrichtung · explained Kerneinspannvorrichtung This is particularly suitable for use on a winding arm and a central surface tape slitting and winding machine. However, the invention is not restricted to this exemplary embodiment, but can be carried out successfully with the features given here and for a wide variety of applications. Show it:

Fig. 1: a schematic front view of the main parts of a winding arm on which a core clamping device according to the invention is attached,

Fig. 2: a schematic side view of the Aufwicke larms according to Fig. 1 and

Fig. 5: one shown on an enlarged scale Axial section through the core clamping device according to FIGS. 1 and 2.

A central and surface winding machine essentially consists of a pair of opposing side frame members passed through a plurality of shafts and rollers for holding the wound and web to be slit as well as for holding the individual tapes into which the web has been slit, and also to hold the rollers and other necessary rotating parts together are connected. In a typical arrangement of this type, the support shaft for the web is, for example, one Spool of plastic film 15.24 cm wide on one side of the machine and stored so that it can rotate between the opposing side plates and the Web drawn around a series of tension or tension rollers together with a spreading or smoothing roller of known construction the latter can take the form of a so-called "banana roller" or own "Mount Hope" roller. Then the web drawn around a slitting roller that carries several slitting knives. These slitting knives are set axially to the machine, see above that they divide the web into the required number of bands of predetermined widths. The individual through the slitting process The ribbons produced are then partially guided around the surface of a winding drum. The vetch drum is usually axially to the top of the machine and has a series of take-up arms attached to each of its sides are so that ribbons produced by the slitting alternate around part of the face of the winding drum to a winding arm can be guided either at the front or at the rear of the machine. On each side of the winding drum is a stationary frame part, for example a T-beam, is provided for supporting the row of winding arms in question.

A T-beam of this type is denoted by 10 in FIGS. 1 and 2 and carries a support rail on its upper horizontal surface 11 trapezoidal cross-section. Several take-up arms can be attached to this mounting rail in such a way that the

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winding arms are axially adjustable. As best shown in Fig. 2 recognizes, each winding arm has a main support block 12, which extends upwards and forms a rigid bearing for a short horizontal spindle 14 and a Baar on one side has horizontal projections 25, the purpose of which will be given below is explained. The main support block 12 further comprises an undercut lower part 15 and a slidable rail 16, which can be adjusted by a manually adjustable clamping screw 17 or is ascertainable, so that the main support block 12 is clamped in any predetermined position on the support rail 11 or can be resolved.

The take-up arm includes a vertical plate 18 attached to one side of the main support block 12 on one end of the spindle 14 is and with a narrower L-shaped side plate 19 cooperates. The latter plate is on the other end of the spindle 14 on the other side of the main support block 12 in the same Way attached. Between the opposite parallel parts of the vertical plate 18 and the Ir-shaped plate 19 a transverse web 20 is attached, for example by means of screws 21, to make the take-up arm assembly extremely strong and rigid. Due to the massive structure, which is due to the Main support block 12 and through the spindle 14 and the solid and rigid construction of the take-up arm itself is located the plate 18 is always in a vertical plane perpendicular to the axis of the spindle 14 and therefore in a plane perpendicular to the axis of the support rail 11. The lower extension 22 of the L-shaped plate 19 is parallel to the lowermost Part of the vertical plate 18 in front, and the space between takes on a spindle 24, which is the upper bearing for a A cylinder and piston assembly for controlling the pivot position of the take-up arm relative to the main support block 12 around the spindle 14 forms. The aforementioned projections 25 provided on the main support block 12 are located under the Spindle 24 and carry or hold the upper arm of the hydraulic

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or pneumatic cylinder assembly 28. The piston rod 27 of this cylinder arrangement is connected to the spindle 24 by means of a rotating block 26. The bin and exit the piston and cylinder arrangement 27 »28 denoted by 29 and 30, respectively. It is particularly easy to see in Fig. 2 recognize that the introduction of a hydraulic or pneumatic fluid into the inlet 29, the piston rod 27 pushes out of the cylinder 28. As a result, the spindle 24 is raised and the winding arm around the spindle 14 opposite the position shown in Fig. 2 is pivoted. When moving back the arm may approach the position shown in Fig. 2, with the movement of the upper end of the winding arm is indicated by the double arrow 31.

A hydraulic or otherwise operated motor 32 is screwed to the vertical plate 18 above the extension 22. The motor 32 has input and output connections 34 and 3b. The motor 32 is coupled to a drive pulley 36 which is arranged on the side of the vertical plate 18 which is remote from the motor 32. An adjustment roller 37 is attached to a slide block 37a (Fig. 2) above the drive pulley so that the tension of a drive belt 38 wrapped around the pulleys 36 and 37 can be adjusted. The drive belt 38 is also placed around a driven pulley 39, which is located at the upper end of the vertical plate 18 and is mounted on a driven , ie He 40. This shaft 40 forms the main shaft of the core clamping device, as will be explained in more detail below. The drive belt 38 and its associated pulleys 36, 37 and 39 are normally enclosed in a removable housing 41 (FIGS. 1 and 3) «

With particular reference to FIG. 3, it should be noted that the driven pulley 39, like the drive and Adjusting washers 36 and. 37 "flanges on which

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speaking end of the drive shaft 40 of the Kerneinspannvorriohtung by means of a had-screw 42 is attached. Pie grub screw 42 is located in a radial opening 44 and presses on a flat one formed at the relevant end of the shaft 40 Surface 43. Around the shaft 40 for precise rotation on To support the end of the vertical plate 18 of the wind-up army, so that the axis of the shaft 40 runs exactly perpendicular to the plate 18, an inner bearing housing 45 is rigid in the opening 46 arranged in the end of the plate 18.

The inner bearing housing 45 has a tubular structure and has an inner smooth finish 4? on, which is in the opening 46 in the Press fit engages or soldered or welded into this opening is. In addition, a radial flange 48 is formed, which is an abutment surface for the arrangement of the inner bearing housing 45 in a suitable position relative to the outside of the Plate 18 forms. The outer surface of the remaining portion of the tubular inner housing 45 forms the inner housing a pair of spaced bearings as discussed below. Within the inner bearing housing 45 are in Two ball bearings 49 and 50 arranged at a distance from one another, whose outer races attached by a press fit within the bore of the inner bearing housing 45 and - if necessary in their position are held by means of snap rings 51, which in turn in suitable hats 52 in the inner surface of the interior Bearing housing 45 are arranged · As with that in Fig. 3 on the left located bearing 49 can be seen, the balls run in a groove and located in the inside of the race are also in a circumferential groove 55 in the corresponding part of the Shaft 40 arranged. In the shaft 40 there is an identical groove, not shown, for receiving the balls of the other bearing 50 intended. The square 40 is therefore due to its large size and number of balls of the bearings 49 and 50 and the relatively large axial distance between the individual bearings rigidly aligned mounted for free rotation within the inner bearing housing s 45. .

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On the outside of the inner * bearing housing 45 two axially spaced apart ball bearings 58 and 59 are arranged. These ball bearings are arranged with a press fit on the outside of the bearing housing 45. In addition, a spacer sleeve 60 is provided between the two ball bearings. The outer races of the bearings 58 and 59 carry an outer bearing housing 61 which is in the form of a tubular part with a radial flange 62 integrally at the inner end adjacent the corresponding surface of the vertical plate 18. This flange 62 forms an axially inwardly directed stop for a core shoulder ring 64 which is applied to the outside of the outer bearing housing 61 with a seizure fit. The annular end face of the core shoulder ring 64 next to the flange 62 of the outer bearing housing 61 has a flanged ring 66 which forms an inner stop for a tubular core 76 which is to be attached to the clamping device in the manner explained in more detail below. The other annular end face of the core shoulder ring 64 is bevelled so that a conical surface 67 results which cooperates with a spring tension ring 68 · by Hing 68 is fixed so that it can slide freely on the outer bearing housing 61, and each its annular end face is beveled in the same way as the conical surface 67 of the core shoulder ring 64. This bevel is shown at 69. The pair of beveled surfaces 67 and 69t, the ^8- core shoulder ring 64 or on the spring tension ring 68, result in a circumferential, V-shaped cross-section groove in which a retaining spring 70 is arranged, Ih In the same way, a beveled Nbckenring 71 is provided on the outer surface of the bearing housing 61 and is secured against rotational movement by means of a slotted split pin 72 which engages in a short axial slot 74 in the outer bearing housing 61. In the V-shaped circumferential groove, which is formed by the mutually facing beveled surfaces of the spring clamping ring 68 and the cam ring 71, there is a further retaining spring 75 »Aus

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the axial dimensions of the slot 74 can be seen that the cam ring 71 has limited axial movement relative to the outer bearing housing 61 can run, and that the spring clamping ring 68 axially between the core shoulder ring 64 and the cam ring 71 can move freely. You can see that with one axial inward movement of the cam ring 71 the axial adjustment is passed through the spring clamping ring 68. The latter therefore causes the retaining springs 70 and 75 to rotate » so that their outer parts assume a larger diameter. Therefore, if a cardboard tube or other core 76 is placed on the Outer surface of the jig defined by the outer cylindrical surfaces of the core shoulder ring 64, the spring tension ring 68 and the cam ring 71 is formed, pushed on then the cam ring is axially displaced, with an axial displacement of the spring tension ring 68 also occurring, so that both springs are stretched in the same way and the outer parts of the coils of the spring are stretched to the inside of the ear attack or core 76.

The axial movement is brought about by means of the cam ring 71, which has a cam-shaped or cam-shaped outer ring surface 77 .

In order to bring about the adjustment of the cam ring 71 and also to transfer the rotary movement of the shaft 40 to the core tube 76, a clamping and drive ring 78 is clamped on the outer free end of the shaft 40. This ring 78 has a radial incision 79 bridged by an adjusting screw 80, as a result of which the ring 78 can be placed on the shaft 40 and clamped. The drive ring 78 forms a support for a gimbal ring 81 which is mounted in Fig. 2 shown Kardanaufhängungsstifte 82 'opposing means of a pair. The fastening pins 82 are arranged along a diameter of the cam ring 71 and the gimbal ring 81 carries on its outside on a diameter

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■ a *

at right angles to this, bearing journals 84 for a pair of nylon cam rollers 85. As FIG. 2 shows, the cam surface of the cam ring 71 is divided into six radially equal fields or cam surfaces divided, of which opposite pairs each lie in a plane perpendicular to the axis of the shaft 40 and then inwardly and then outwardly inclined so that they are a wide, flat, V-shaped part on opposite sides Form pages that represent the position of the outermost setting of the cam ring 71 relative to the outer bearing housing 61 « This can be viewed as the normal or start-up setting of the core chuck as retaining springs 70 and 75 assume their smallest diameter in this state and are adjusted so that normally a core tube 76 is free over the outside of the jig up to the through the annular flange 66 formed end stop can be pushed.

In operation of the device, a core tube 76 is pushed onto the clamping device in the manner described above and then the hydraulic or pneumatic circuit is put into operation, whereby the piston and cylinder 28 are actuated and the winding arm is pivoted so that the plate 18 in the direction of the As a result of this movement, the outer surface of the core tube 76 comes into contact with the winding cylinder of the machine, and the rapid rotation of the core tube 76 caused by this contact leads to an inertial twist of the core tube, so that the Cam ring 71 is rotated relative to the cam rollers 85 Therefore, the cam rollers 85 move from the bottom areas of the V-shaped grooves to the cylindrical sections, causing the cam ring to move axially inward towards the vertical plate 18 and the retaining springs 70 and 75> stretched. In this way, the retaining springs 70 and 70 engage the inside of the core tube 76, as already described above.

was purified. As can be seen from this, the inventive Core jig has a very useful and advantageous self-locking effect. At the same time will caused by the operation of the hydraulic motor a rotation of the V / Elle and the core tube 76 in this way precisely twisted, with about 90% of its torque being through touch with the reel of the machine and the remainder are taken up by the shaft 40 by inertial rotation. The main func ion of the shaft 40 is to ensure that the core tube 76 remains precisely parallel and free of eccentricity the very rigid mounting of the shaft 40, made possible by the white axial, as a result of the construction described above Distance between the bearings 49 and 50 is created, the Achieve desired goals.

If desired, place the core tube on the jig by hand to fasten or to be clamped in the clamping device, then the flange 66 can advantageously be a give larger axial ./eite, as indicated by the dashed lines is indicated at 65, and the exterior is that created in this way cylindrical surface can advantageously be knurled so that the ring 64 can be gripped by hand, while the gimbal ring 81 is rotated to clamp the core tube in the intended position.

The advantages of the rotary transmission bearing according to the invention consist of the following, among others;

1. The drive shaft is exactly parallel to the winding drum held.

2. The arm is designed so that it can be used throughout its Pivoting movement maintains exact parallelism, whereby it should be noted that during the winding of the slotted Tape on the core tube, the radius of the core, which is wound in contact with the winding roll, increases,

1 92134A

so that the arm gradually into its shown in FIG The starting position returns.

3. The above-described cam ring arrangement makes it possible or to take very firmly the core tube clamp _e, so as to resist the torque exerted by the shaft 4-0, and also a complete control with respect to a possible eccentricity between the core and the Kerneinspannvorrichtung maintained . In this way, the tapes are wound exactly and known disadvantages such as. avoiding the formation of loops.

The finished roll can easily be removed from the core jig, as this removal is in is easily achieved by turning the gimbal ring (for example, using the knurling of the Surface 65 »so that the squat ring as a result of the existing Endeavor of the retaining springs to relax can move axially with contraction) »

5ο A new core can be easily inserted into the core clamping device in the same way be introduced, advantageously from the above-mentioned locking effect Use can be made.

Although the invention was explained using the example of a boom attachment for the drive shaft of the clamping device, other fastenings can also be provided, for example one consisting of two parallel arms and in U.S. Patent 3,122,335.

As can be seen, a very accurate and reliable core clamping device is proposed by the invention, which especially for take-up arms of slitting machines of the central and surface winding type. In addition, lets However, the device according to the invention is advantageously in

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use a variety of different machines in which a rotational movement transmission with precise parallelism is desired is ο

In summary, the invention relates to a device for fastening a tubular core on a drive shaft ,, The Drive shaft runs through an inner bearing housing »One end of the bearing housing is attached to a retaining plate. In axially spaced bearings are enclosed between the inner bearing housing and an outer bearing housing, wherein the latter carries axially displaceable core retaining rings. the Core retaining rings in turn carry a pair of retaining springs, and the The ring surface of one ring is provided with cam or control surfaces molded into it. In the cam or »control surfaces two cam or »control rollers engage with the drive shaft are rotatable, whereby the rings are moved and an expansion of the retaining springs until they come into contact with the Core is effected.

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Claims (1)

DIPL.-ING. OR KRETZSCHMAR , _{2 HAMBU} j | _< 9 ₁ 2 13 4 AT STROHHAUSE 34 PATENT ADVERTISER RUF a «67« 3 κ / η John Dusenbery Company, Inc. _Ä _ m + *. ι- τ / π «2 5 April 1969 Clifton, Ivew Jersey / USA Attorney file: 3422 Protection address 1, Kerneinspannvorrichtung for securing elle a tubular core at a .antriebsv /, _& ejcennzeichnet the drive shaft (40) extends through the through a fixed, inner bearing housing (45) ", and an outer bearing housing (61) and the axial distance between inner (45) and the outer bearing housing (61) enclosed bearings (58, 59) »axially aligned core holding parts (op, 66, 71) which are displaceable along the outer bearing housing (61) £, l ^e i ^ ^{en (} i are, springs (70, 7;) carried by the a.ernhalterteile (65, 65, 71), which when moving the core holding parts (65, o6, 71) * aiu the core (76) get into Beri.irunrj as well as a die -usaiunenwirxung if you end on the , 71) during a rotational movement of the drive shaft (40) relative to the core holding portions (6p, ₁ 6c, .71). 2. Apparatus according to claim 1, characterized in, äa, z the inner bearing housing (4p) attached to a support arm (13) is », the drive shaft (40) being axially spaced from and carried by the inner bearing housing (4p) Bearings (49, 50) is supported. - 1 - ORIGINAL BATHROOM 009827/1066 ACCOUNTS · DRESD N E «BANK. ACCOUNT NO. 8599 POST CHECK HAMBURG NO. 1937 66 5. Device according to. Claim. 1 or 2, indicated by rings (65 »68, 71) arranged at a distance as core holding parts, wherein the adjacent annular surfaces (67, 69) are bevelled so that grooves extending around the circumference ¥ -shaped cross-section and the tongues in the grooves arranged retaining springs (70, 75) are. 4. Apparatus according to claim 1, 2 or 3 »characterized in that the means bringing about the cooperation on the annular surface of one end ring (71) has cam or control surfaces (J? 7) , with those of the drive shaft (4-0 ) supported rollers (85) are in engagement over their peripheral surfaces. 5 «device according to claim 4, characterized in that one end of the outer bearing housing (61) in an outward direction directed flange (62) ends and the other end has a longitudinal slot (74-), the one end ring (71) against Rotation about the outer bearing housing (61) is fixed by means of a split pin (72) extending into the slot iso and that the other end ring (64) turns outwards extending flange (66) which is attached to the outer bearing housing (61) immediately adjacent to the flange (62) 6. Device according to one of claims 1 to 5 »characterized in that the drive shaft (40) is mounted by means of axially spaced bearings (4V, 50) in the inner bearing housing [M- ^ j and extends through this and that the outer bearing housing (61) is arranged concentrically to the inner bearing housing (45). L e r s e i t e