EP0025340B1 - Dispositif pour le bobinage en continu d'un toron continu - Google Patents

Dispositif pour le bobinage en continu d'un toron continu Download PDF

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Publication number
EP0025340B1
EP0025340B1 EP19800303078 EP80303078A EP0025340B1 EP 0025340 B1 EP0025340 B1 EP 0025340B1 EP 19800303078 EP19800303078 EP 19800303078 EP 80303078 A EP80303078 A EP 80303078A EP 0025340 B1 EP0025340 B1 EP 0025340B1
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EP
European Patent Office
Prior art keywords
winding spool
spool
strand
winding
main winding
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.)
Expired
Application number
EP19800303078
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German (de)
English (en)
Other versions
EP0025340A1 (fr
Inventor
Koji Nakazawa
Michio Satoh
Shin Kasai
Yutaka Kawaguchi
Toshiaki Kikuchi
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Nitto Boseki Co Ltd
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Nitto Boseki Co Ltd
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Publication date
Application filed by Nitto Boseki Co Ltd filed Critical Nitto Boseki Co Ltd
Publication of EP0025340A1 publication Critical patent/EP0025340A1/fr
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Publication of EP0025340B1 publication Critical patent/EP0025340B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H67/00—Replacing or removing cores, receptacles, or completed packages at paying-out, winding, or depositing stations
    • B65H67/04—Arrangements for removing completed take-up packages and or replacing by cores, formers, or empty receptacles at winding or depositing stations; Transferring material between adjacent full and empty take-up elements
    • B65H67/044—Continuous winding apparatus for winding on two or more winding heads in succession
    • B65H67/048—Continuous winding apparatus for winding on two or more winding heads in succession having winding heads arranged on rotary capstan head
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/30—Handled filamentary material
    • B65H2701/31—Textiles threads or artificial strands of filaments
    • B65H2701/312—Fibreglass strands
    • B65H2701/3122—Fibreglass strands extruded from spinnerets

Definitions

  • the present invention relates to a device for continuously winding a continuous elongate element and especially a glass fiber strand.
  • conventional bushings for producing glass fibers have been provided with orifices from 400 to 800 in number and drawn therethrough glass filaments from 10 to 13 microns in diameter.
  • glass filaments from 400 to 800 in number drawn from the single bushing are gathered into a strand and wound around a spool to form a cake of strand thereafter strands are unwound from 15 to 30 cakes the gathered into a roving and wound around another spool to form a package.
  • Japanese Patent Publication No. 36-18369 discloses a method for continuously winding strands by a plurality of winding spools mounted equiangularly on a turntable which is supported by a horizontal shaft and rotated in one direction. Whenever the spool in the winding position becomes full, the turntable is rotated through a predetermined angle so that an empty spool is brought to the winding position and the strand is wound around it. More specifically, when the strand has been transferred onto the empty spool which is rotated at the same speed as the full spool, the latter is decreased in speed so that the strand between the full and empty spools is slackened and caused to adhere to the empty spool so as to be wound around it.
  • Japanese Patent Publication No. 43-8996 discloses a winding device in which a plurality of spools are mounted on a turntable and a supporting plate is disposed in front of the free end of each spool so that when the strand is transferred from a full spool to an empty spool, it is clamped between the plate and the free end of the empty spool.
  • mechanical clamping means driven with a magnet, spring or the like are needed in order to clamp the strand so that the winding spools become very complex in construction and are not adapted to spin at high speeds.
  • strands consisting of a larger number of filaments and having a larger diameter which have a relatively higher degree of rigidity and are relatively fragile, breakages frequently occur when clamped.
  • Japanese Patent Publications Nos. 47-9862 and 48-32626 disclose winding devices of the type using an auxiliary winding spool in order to ensure the smooth and positive transfer of the strand from a full spool to an empty spool.
  • the auxiliary winding spool When one spool becomes full, the auxiliary winding spool is brought to a position in line with the full spool and the strand is transferred from the full spool to the empty spool. Thereafter the full spool is retracted from the winding position while an empty spool is brought to the winding position and subsequently the strand is transferred from the auxiliary winding spool onto the empty spool.
  • the winding device disclosed in Japanese Patent Publication No. 47-9862 is such that the auxiliary winding spool is held stationary while two main winding spools are alternately brought to the winding position in opposed coaxial relationship with the stationary spool.
  • the winding device disclosed in Japanese Patent Publication No. 48-32626 is such that the auxiliary winding spool is so designed and constructed as to be alternately brought into alignment with one of two main winding spools which are held stationary.
  • Both these winding devices have a common defect that when the strand is transferred between the main and auxiliary winding spools, variations in winding tension result so that these devices are unsatisfactory in practice in providing strand packages of uniform configurations and qualities.
  • variations in winding tension result so that these devices are unsatisfactory in practice in providing strand packages of uniform configurations and qualities.
  • remedies or countermeasures cannot be carried out smoothly because of the presence of the auxiliary winding spool.
  • the present invention was made to overcome the above and other problems encountered in the prior art continuous winding devices.
  • One of the objects of the present invention is therefore to provide a continuous winding device capable of continuous and stable winding especially of glass-fiber strands consisting of a larger number of filaments and having a larger diameter, whereby packages of high qualities can be provided.
  • the present invention provides a device for continuously winding a continuous elongate element having:
  • Figure 1 shows a large number of glass filaments being gathered into a strand which in turn is directly wound into a packaged by a winding machine in accordance with the present invention.
  • Molten glass is drawn through from 2000 to 4000 nozzles 2 at the bottom of a bushing 1 into glass filaments 3. After having been applied with a lubricant by a roll sizer 4, they are gathered by a gathering roller 5 into a strand 6 which in turn is wound by the winding device.
  • the winding device has a main body 7 in which are mounted drive motors, hydraulic cylinders, transmission gears, control devices and so on as will be described in detail below.
  • a turret 9 which carries two horizontal winding spools 8a and 8b, a traverse motion 11 mounted on a swinging arm 10, an auxiliary winding spool 13 mounted rotatably on a swinging arm 12 and a strand guide rod 14, which extends at right angles to the axes of the main and auxiliary winding spools 8a, 8b and 13 and the traverse motion 11 and is movable in the same direction as these axes.
  • the strand 6 is shown as being wound around the main winding spool 8a while being traversed by the traverse motion 11.
  • the arm 12 is swung in the direction indicated by the arrow a so that the auxiliary winding spool 13 is brought into abutment with the free end of the main winding spool 8a.
  • the strand guide rod 14 transfers the strand 6 to the auxiliary winding spool 13 so that the latter starts winding the strand 6.
  • the turret 9 is rotated through a predetermined angle to bring the second main winding spool 8b, which is empty, to tne winding position while the first main winding spool 8a is retracted therefrom.
  • the strand guide rod 14 is retracted so that the strand is transferred to the second main winding spool 8b so as to be wound therearound.
  • the auxiliary winding spool 13 is returned to the initial position shown and is ready for the next operation.
  • FIG. 2 is a rear view while Figure 3 is a view mainly used for the explanation of the arrangements and modes of operation of driving mechanisms.
  • the rotations of the two main winding spools 8a and 8b, the auxiliary winding spool 13 and the traverse motion 11 are all provided by a variable speed motor 15 mounted on the bottom of the main body 7.
  • the motor 15 carries two timing pulleys 16 and 17 on its shaft.
  • the timing pulley 16 is drivingly coupled to a timing pulley 19 mounted on the input shaft of an electromagnetic clutch 18 through a timing belt 20.
  • the electromagnetic clutch 18 is of the double-clutch type having two output shafts carrying timing pulleys 21 and 22, respectively. When one clutch is energized, one corresponding output shaft is connected to the input shaft; when both the clutches are energized, both the output shafts are connected to the input shaft; and when the two clutches are de-energized, both the output shafts are disconnected from the input shaft.
  • the main winding spools 8a and 8b are mounted on spindles 25 and 26, respectively, which in turn are rotatably supported by bearings in housings 23 and 24 mounted on the rear surface of the turret 9.
  • Timing pulleys 27 and 28 which are mounted at the rear ends of the spindles 25 and 26, respectively, are drivingly coupled through timing belts 29 and 30, respectively, to the timing pulleys 21 and 22 on the output shafts of the electromagnetic clutch 18.
  • the spindles 25 and 26 are angularly spaced spart from each other for example by 140°.
  • the timing pulley 17 on the motor 15 is drivingly coupled through a timing belt 33 to a timing pulley 32 on the input shaft of an electromagnetic clutch 31.
  • the electromagnetic clutch 31 is also of the double-clutch type having two output shafts carrying timing pulleys 34 and 35, respectively. These timing pulleys 34 and 35 are drivingly coupled through timing belts 36 and 37, respectively, to a timing pulley 38 on the traverse motion 11 and a timing pulley 39 for driving the auxiliary winding spool 13.
  • the traverse motion 11 is most preferably of the type having a strand guide 40 which makes reciprocating movements in response to the rotation of a scroll cam.
  • a pressure roller 41 which is disposed in parallel with the scroll cam and rolls in contact with the surface of the strand package under a suitable pressure while the strand is being wound (see Figure 1
  • the swingable arm 10 which supports the traverse motion 11 is hollow and has its one end securely joined to one end of a hollow shaft 42 so that as the latter is rotated, the former is swung.
  • a rotating shaft 43 is extended through the hollow shaft 42 and the timing pulley 38 is attached to the rear end of the rotating shaft 43.
  • a timing pulley 44 which is mounted at the front end of the rotating shaft 43 is drivingly coupled through a timing belt 45 to a timing pulley 46 mounted on a scroll cam shaft, the belt 45 being extended through the arm 10.
  • the swingable arm 12 which supports the auxiliary winding spool 13 is hollow and has its upper end securely joined to the front end of a hollow shaft 47 so that as the latter is rotated, the former is caused to swing.
  • a rotating shaft 48 is extended through the hollow shaft 47 and the timing pulley 39 is attached to the rear end of the shaft 48.
  • a timing pulley 49 is attached to the front end of the shaft 48 and is drivingly coupled through a timing belt 50 to a timing pulley 51 carried by a spindle of the auxiliary winding spool 13, the timing belt 50 being extended through the arm 12.
  • the turret 9 is imparted with reciprocating rotations by a hydraulic cylinder 53 which in turn is mounted on the bottom of the main body 7 with a bracket 52.
  • a piston rod 54 of the hydraulic cylinder 53 is connected to the lower end of a rack 55 which is mounted for vertical movement and is in mesh with a pinion 56.
  • An intermediate gear 57 is carried by the shaft of the pinion 56 for rotation in unison therewith and is in mesh with a gear 58 securely fixed to the turret 9. Therefore as the cylinder 53 extends or retracts its piston rod 54, the rack 55 is caused to move upward or downward so that the turret 9 is caused to reciprocably rotate through the pinion 56, intermediate gear 57 and gear 58.
  • the first main winding spool 8a is brought to the winding position shown in Figure 1 while at the bottom of the stroke the second main winding spool 8b is brought to the winding position.
  • a variable motor 59 is drivingly coupled to a reduction gear 62 through meshing gears 60 and 61.
  • the reduction gear 62 is directly coupled to an electromagnetic clutch 64 with an output shaft 65 supported by a bearing 63 and carrying two plate cams 66 and 67.
  • the plate cam 66 engages with a cam follower or cylindrical roller 70 rotatably mounted at the upper end of a rack 69 which is vertically slidably supported by brackets 68 (see Figure 2).
  • the rack 69 is in mesh with a sector gear 71 carried by the hollow shaft 42 of the traverse motion so that as the rack 69 is caused to move up and down, the hollow shaft 42 and hence the swinging arm 10 (see Figure 1) are caused to swing. More specifically, during energization of the clutch 64 the rotation of the motor 59 is reduced by the reduction gear 62 at a predetermined ratio and transmitted to the plate cam 66. As the plate cam 66 is rotated, the rack 69 is caused to move upward so that the sector gear 71 is caused to rotate in the clockwise direction in Figure 2 and subsequently the traverse motion 11 is gradually moved away from the main winding spool 8.
  • the plate cam 66 is designed to have such a cam profile that the traverse motion 11 is moved away in proportion to the quadratic increase in diameter of the strand package being formed around the main winding spool 8.
  • a hydraulic cylinder 73 is pivoted to a bracket 72 and the piston rod of this cylinder 73 is pivoted with a pin 74 to the sector gear 71.
  • the piston rod is forced to be retracted so that the sector gear 71 is imparted with a torque in the counterclockwise direction.
  • This torque which is weaker than the torque imparted in the clockwise direction to the sector gear 71 from the rack 69, has double functions of causing the pressure roller 41 to maintain the contact with the surface of the package under a predetermined pressure when moving away therefrom in unison with the traverse motion 11 and preventing the vibrations of both the traverse motion 11 and the pressure roller 41.
  • the electromagnetic clutch 64 is disengaged so that the upward movement of the rack 69 is stopped, the hydraulic cylinder 73 is actuated to extend its piston rod so that the sector gear 71 is further rotated in the clockwise direction and consequently the traverse motion 11 and the pressure roller 41 are moved away from the surface of the strand package, whereby the change in position between the main winding spool 8a and 8b is permitted.
  • the other plate cam 67 controls the speed of the variable motor 15 which drives the main winding spool 8, the scroll cam of the traverse motion 11 and the auxiliary winding spool 13.
  • the strand winding speed that is, the peripheral velocity of the package on the main winding spool must be maintained constant.
  • the rotational speed of the main winding spool must be decreased in inverse proportion to the increase in diameter of the strand package.
  • the plate cam 67 engages a cylindrical roller or cam follower 174 mounted at the left end of a rack 173 which in turn is horizontally slidably supported by brackets 172 and is in mesh with a pinion 76 supported by a bracket 75.
  • a gear 77 (see also Figure 2), which is carried by the shaft of the pinion 76 for rotation in unison therewith, is in mesh with a gear 80 carried by a shaft 79 of a potentiometer or a displacement sensor 78 (see Figure 5).
  • the gear 80 is loaded with a bias spring (not shown) so as to be normally biased in the counterclockwise direction so that the rack 173 is normally imparted with the force acting in the left direction in Figure 4 and consequently the cylindrical roller 174 is pressed against the periphery of the cam plate 67.
  • a bias spring (not shown) so as to be normally biased in the counterclockwise direction so that the rack 173 is normally imparted with the force acting in the left direction in Figure 4 and consequently the cylindrical roller 174 is pressed against the periphery of the cam plate 67.
  • the rotation of the shaft 79 of the potentiometer 78 is converted into a voltage signal and transmitted to a winding speed control panel 81, whereby the speed of the motor 15 for winding the strand is controlled.
  • the plate cam 67 is mounted on the output shaft 65 coaxially with the plate cam 66 in such a way that the starting points of their cam profiles coincide with each other.
  • the cam profile of the plate cam 67 is so determined that the voltage signal from the potentiometer 78 changes its magnitude in response to the increase in diameter of the strand package being wound and subsequently the rotational speed of the motor 15 is gradually decreased so as to maintain the peripheral velocity of the strand package being wound constant.
  • the hollow shaft 47 is extended through a rotatable cylindrical housing 82 and keyed with a key 83 to the housing 82 in such a way that the shaft 47 can slide in the axial direction but is not permitted to rotate.
  • a gear 84 is formed integrally with and coaxially of the cylindrical housing 82 and engages an intermediate gear 88 which in turn is in mesh with a rack 87 which is vertically slidable by a hydraulic cylinder 86 mounted with a bracket 85.
  • a rack 89 is formed at the rear end portion of the hollow shaft 47 and is in mesh with a pinion 90 which is mounted on the shaft of a motor (not shown). Therefore as the motor is driven, the hollow shaft 47 is caused to slide in the axial direction relative to the cylindrical housing 82. Obviously, the direction of the axial movement of the hollow shaft 47 is dependant on the direction of rotation of the motor.
  • the arm 12 supporting the auxiliary winding spool 13 is caused to swing in the direction a in Figure 1 until the auxiliary winding spool 13 comes into line with the first main winding spool 8a.
  • the housing 82 is prevented by the engagement of its extension with a stopper 91 as best shown in Figure 2.
  • the pinion 90 is rotated in such a direction that the hollow shaft 47 is caused to move to the right in Figure 3 and consequently the free end of the auxiliary winding spool 13 is brought into engagement with the mating free end of the main winding spool 8a.
  • the strand guide rod 14 is acuated so that the strand 6 is transferred from the main winding spool 8a to the auxiliary winding spool 13.
  • the rotation of the pinion 90 is reversed so that the hollow shaft 47 is caused to move to the left in Figure 3 toward the initial position.
  • the turret 9 is rotated so that the second empty main winding spool 8b is brought to the winding position.
  • the pinion 90 is rotated again so that the hollow cylinder 47 is advanced and subsequently the free end of the auxiliary winding spool 13 is brought into engagement with that of the second main winding spool 8b which is now in the winding position.
  • the strand guide rod 14 is attached to the free end of the piston rod 93 of a hydraulic cylinder 92 and arranged such that the strand guide rod 14 is in the position indicated by the straight line T when the piston rod 93 is fully extended but in the position indicated by the straight line U when the piston rod 93 is fully retracted. In the position T, the strand guide rod 14 is above the auxiliary winding spool 13 in engagement with the main winding spool 8.
  • auxiliary rod 95 which is supported by brackets 94 for slidable movement in parallel with the piston rod 93 is attached to the strand guide rod 14 and a stopper 96 is attached to the auxiliary rod 95 intermediate its ends.
  • An arm 97 (see also Figure 2), which is extended radially outwardly from the housing 82, is adapted to engage with the stopper 96 so that further advancement of the strand guide rod 14 beyond the line S toward the line T is prevented when the auxiliary winding spool 13 is in the initial inoperative position shown in Figure 1.
  • a supporting ring 101 is securely joined to the hollow supporting arm 12 adjacent its lower end and a rotary barrel 104 is rotatably supported by bearings 102 and 103 which are mounted in the supporting ring 101.
  • the auxiliary winding spool 13 is fitted over flanges 105 and 106 of the rotary barrel 104, the flange 105 being formed at the front end (the right end in Figure 7) while the flange 106 is intermediate the ends of the rotary barrel 104.
  • the timing pulley 51 which is mounted at the rear end (the left end in Figure 7) of the rotary barrel 104 is drivingly coupled through the timing belt 50 to the timing pulley 49 carried by the rotating shaft 48 (see also Figure 3).
  • One end (rear end) of a hollow shaft 109 which extends through the center bore of the rotary barrel 104 is securely fixed to the lower end of the supporting arm 12 and a circular retaining member 111 is fitted over the other end of the hollow shaft 109 and securely keyed thereto with a key 110.
  • a disk 112 is mounted on the retaining member 111.
  • the timing pulley 51 and the rotary barrel 104 are supported by bearings 113 and 114 mounted on the hollow shaft 109 so as to be rotatable relative to the hollow shaft 109.
  • a hydraulic motor 115 of the oscillating type is mounted on the supporting arm 12 adjacent its lower end, and the output shaft of the motor 115 is connected to an oscillating shaft 116 extending coaxially through the hollow shaft 109.
  • a cutting blade 118 is pivoted with pin 117 to the disk 112 and an oscillating arm 119 is carried by the shaft 116 at its front end (see also Figures 8a and 8b).
  • one end of a connecting rod 121 is pivoted with a pivot pin 120 to the free end of the oscillating arm 119 while the other end is pivoted with a pin 122 to the rear end of the cutting blade 118.
  • Figure 8a shows the cutting blade 118 in its inoperative position.
  • the motor 115 is energized so as to cause the oscillating arm 119 to rotate in the counterclockwise direction in Figure 8a.
  • the cutting blade 118 is caused to rotate in the counterclockwise direction about the pivot pin 117 and projected radially outwardly through the space between the free ends of the main and auxiliary winding spools 8 and 13 as shown in Figure 8b so that the strand 6 bridging between the main and auxiliary winding spools 8 and 13 is cut off.
  • the disk 112 is formed with a partially circular protective flange 123 which extends axially forwardly (to the right in Figure 7) from the periphery of the disk 112.
  • the protective flange 123 is not completely circular because it must provide a passage for the cutting blade 118. The counterclockwise rotation of the cutting blade 118 is stopped when it engages with the upper end of the protective flange 123 as shown in Figure 8b.
  • the end face of the main winding spool 8 which is in opposed relationship with the end face of the auxiliary winding spool 13 is formed with a cylindrical recess 124 which is slightly greater in diameter than the free end of the auxiliary winding spool 13 so that when the auxiliary winding spool 13 is connected to the main winding spool 8, the free end of the spool 13 projects into the recess 124 and is surrounded by the peripheral wall 8' thereof.
  • This arrangement is very effective for smoothly transferring the strand between the main and auxiliary winding spools 8 and 13 as will be described in detail later.
  • the glass filaments from 2000 to 4000 in number drawn from the bushing 1 are applied with lubricant by the roller sizer 4 and gathered by the gathering roller 5 into a strand 6.
  • An operator brings the strand 6 past the front side of the strand guide rod 14 toward the main winding spool 8a and winds it around the front end portion 8a' thereof.
  • the motor 15 is enerized and the double-action electromagnetic clutch 18 is so actuated that the timing pulley 21 is rotated and the main winding spool 8a is rotated (see Figure 3).
  • the axial position of the main winding spool 8a is so determined that the strand 6 leaving from the gathering roller 5 is naturally forced to move toward the center of the main winding spool 8a by the tension of the strand 6, but at the start the path of the strand 6 is so restrained by the strand guide rod 14 at the position S that the strand 6 is wound around the front end portion 8a' only until the strand 6 reaches a predetermined diameter and the rotational speed of the motor 15 reaches a predetermined speed.
  • the motor 15 is energized
  • the motor 59 for displacing the traverse motion 11 (see Figure 4) is also energized, but the electromagnetic clutch 64 is kept disconnected so that the plate cams 66 and 67 are stationary.
  • the piston rod 93 of the hydraulic cylinder 92 is retracted so that the strand guide rod 14 is retracted to the position U. Then, under its own tension the strand 6 moves toward the center of the main winding spool 8a.
  • the double-action electromagnetic clutch 31 is so actuated that the timing pulley 34 is rotated and consequently the scroll cam of the traverse motion 11 is rotated, whereby the strand guide 40 starts its straight reciprocating movements.
  • the electromagnetic clutch 64 is energized so that the plate cams 66 and 67 are rotated.
  • the rack 69 is caused to move upward so that the sector gear 71, which is in mesh with the rack 69, is caused to rotate in the clockwise direction against the force which is imparted from the hydraulic cylinder 73 and tends to rotate the sector gear 71 in the counterclockwise direction.
  • the traverse motion 11 is caused to move away from the main winding spool 8a.
  • the plate cam 66 has such a cam profile that the retracting speed of the traverse motion 11 corresponds to the rate at which the strand package is increased in diameter.
  • the traverse motion 11 is always maintained in predetermined spaced apart relationship with the surface of the strand package during the winding.
  • the traverse motion 11 is urged toward the main winding spool 8a so that the pressure roller 41 is pressed against the surface of the strand package under a predetermined pressure while the pressure roller 41 being retracted as the diameter of the strand package is increased.
  • the plate cam 67 which rotates in unison with the cam 66, controls the motor 15 so as to gradually decrease the rotational speed of the main winding spool 8a in inverse proportion to the increase in diameter of the strand package being wound so that the winding speed or the surface velocity of the strand package can be maintained always constant.
  • the strand is wound under a constant tension regardless of the increase in diameter of the strand package.
  • the pressure roller is always pressed against the surface of the strand package being wound under a predetermined pressure so that strand packages with uniform qualities can be obtained.
  • the electromagnetic clutches 18 and 31 are so energized that the timing pulleys 22 and 35 are rotated so as to rotate the empty main winding spool 8b and the auxiliary winding spool 13.
  • the hydraulic cylinder 86 is actuated to raise the rack 87 so that the auxiliary winding spool-housing 82 is caused to rotate in the clockwise direction in Figure 2 through the gears 88 and 84.
  • the auxiliary winding spool 13 is caused to swing to the operative position at which the spool 13 is in line with the main winding sleeve 8a and is axially spaced apart therefrom by a predetermined short distance.
  • the pinion 90 (see Figure 3) is caused to rotate in the clockwise direction so that the hollow shaft 47 is caused to move to the right and the free end of the auxiliary winding spool 13 is fitted into the recess 124 at the free end 8a' of the main winding spool 8a as shown in Figure 7.
  • the electromagnetic clutch 64 is de-energized so that the rotations of the plate cams 66 and 67 are stopped and subsequently the hydraulic cylinder 73 (see Figure 2) is so actuated as to extend its piston rod so that the hollow shaft 42 is caused to rotate in the clockwise direction through the sector gear 71 and as a result the traverse motion 11 and the pressure roller 41 are caused to move away from the fully wound strand package, thereby releasing the strand 6 from the strand guide 40.
  • the rotation in the clockwise direction of the sector gear 71 causes the rack 69 to rise so that the cylindrical roller 70 is moved away from the cam plate 66.
  • the cam plate 66 is returned to its initial position under the force of a bias spring (not shown).
  • the hydraulic cylinder 92 (see Figure 6) is actuated to advance the strand guide rod 14.
  • the arm 97 of the housing 82 is retracted away from the path of the stopper 96 carried by the auxiliary rod 95 which is advanced in unison with the strand guide rod 14 so that the strand guide rod 14 is advanced to the position T. Accordingly, the strand 6 which is being wound around the center portion of the main winding spool 8a is transferred over the front portion 8a' thereof to the auxiliary winding spool 13 which is rotating at the same speed as the main winding spool 8a.
  • the pinion 90 (see Figure 3) is caused to rotate in the counterclockwise direction so that the auxiliary winding spool 13 is disconnected from the main winding spool 8a.
  • the motor 115 (see Figure 7) is energized so that the cutting blade 118 is swung radially outwardly through the space between the auxiliary and main winding spools 13 and 8a, thereby cutting off the strand 6 bridging between them.
  • the motor 115 is reversed in rotation so that the cutting blade is returned to its initial position shown in Figure 8a. This strand cutting operation is almost instantly accomplished.
  • the electromagnetic clutch 18 is actuated to disconnect the timing pulley 21. Simultaneously, a brake pad 98a (see Figure 2) is pressed against a brake disk 99a (see also Figure 2) mounted on the spindle 25 of the main winding spool 8a, whereby the latter is stopped.
  • the strand guide rod 14 is then retracted from the position T to the position U (see Figure 6) so that the strand 6 which has been being wound around the auxiliary winding spool 13 is not automatically transferred toward the center of the main auxiliary winding spool 8b under the tension of the strand itself.
  • the traverse motion 11 is advanced again from its retracted position toward the main winding spool 8b and in the course of this advancement the strand guide 40, which is making the rectilinear reciprocating movements, catches the strand 6 again, whereby the strand 6 is traversed while being wound around the main winding spool 8b.
  • the pressure roller 41 is pressed against the surface of the package being formed on the main winding spool 8b.
  • the clutch 64 (see Figure 4) is energized again so that the retracting movements of the traverse motion 11 and the pressure roller 41 are controlled by the plate cam 66 while the winding speed of the strand 6, that is the peripheral speed of the package on the main winding spool 8b, is controlled by the plate cam 67 in the manner described.
  • the auxiliary winding spool 13 is axially moved away from the spool 8b and almost concurrently the cutting blade 118 is actuated again, thereby cutting off the strand 6 bridging between the spool 13 and the spool 8b.
  • the strand 6 can be wound around the auxiliary winding spool 13 without any interruption.
  • the strand winding is carried out at the same position.
  • the auxiliary winding spool 13 is held in the inoperative position remote from the winding position during the time when the strand is being wound to be formed into a package around the main winding spool 8a or 8b, so that an operator can be easy of access to the main winding spool 8a or 8b in the winding position when the strand 6 is broken or when the lubricant is solidified on the strand.
  • the strand 6 is cut off by the cutting blade 118 so that the formation of fuzz at the cut ends can be avoided and consequently the degradation in quality due to the presence of fuzz can be prevented.

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  • Replacing, Conveying, And Pick-Finding For Filamentary Materials (AREA)
  • Winding Filamentary Materials (AREA)

Claims (5)

1. Dispositif pour bobiner de manière continue un long élément continu comportant:
une tourelle (9) qui porte deux bobines principales (8a, 8b) espacées angulairement d'un angle prédéterminé et qui présente un axe de rotation parallèle aux axes des deux bobines principales montées sur cette tourelle, de sorte que chaque fois que la tourelle est tournée d'un certain angle, les deux bobines principales sont amenées en alternance dans une position de bobinage,
une bobine auxiliaire (13) qui est montée à une extrémité d'un bras de support (12) dont l'autre extrémité est reliée à une extrémité d'un arbre tournant (47) parallèle à l'axe de rotation de la tourelle (9) et proper à être déplacé axialement, qui peut être déplacée vers une position inactive espacée d'un distance considérable de l'axe de la bobine principale (8a) en position de bobinage et dont l'extrémité libre peut attaquer l'extrémité libre de la bobine principale (8a) en position de bobinage;
un dispositif à mouvement de va-et-vient (11) mobile entre une première position adjacente à la bobine principale (8a) en position de bobinage dans laquelle le dispositif à mouvement de va-et-vient communique le mouvement de va-et-vient à l'élément (6) bobiné autour de la bobine principale (8a) en position de bobinage et une seconde position espacée de la bobine principale (8a) en position de bobinage d'une distance prédéterminée à laquelle le dispositif à mouvement de va-et-vient est dégagé de l'élément en cours de bobinage; et
une tige de guidage (14) mobile dans une direction parallèle à l'axe de la bobine principale entre une première position située au-dessus de la bobine auxiliaire (13) engagée avec la bobine principale (8a) en position de bobinage et une seconde position située au-delà de l'extrémité de la bobine principale (8a) en position de bobinage éloignée de son extrémité libre; caractérisée en ce que:
un arrêt (96) est animé d'un mouvement de va-et-vient à l'unisson avec la tige de guidage (14) et un bras (97) qui peut pivoter en même temps que l'arbre tournant (47) du bras de support (12) sont prévus, le bras étant placé de sorte que, lorsque la bobine auxiliaire (13) est rétractée vers sa position inactive, le bras (97) soit amené dans le trajet de l'arrêt (96), de sorte que, lorsque la tige de guidage (14) est avancée, le bras (97) est amené en contact avec l'arrêt (96), l'avancement de la tige de guidage (14) étant ainsi limité à une position adjacent à l'extrémité libre de la bobine principale (8a) en position de bobinage.
2. Dispositif suivant la revendication 1 dans lequel:
l'extrémité libre de la bobine auxiliaire a un diamètre inférieur à celui de l'extrémité libre de chaque bobine principale; et
chaque bobine principale présente un évidement qui est formé dans son extrémité libre et qui est destiné à recevoir l'extrémité libre de la bobine auxiliaire.
3. Dispositif suivant la revendication 1 ou 2, dans lequel la bobine auxiliaire peut se déplacer axialement vers la bobine principale en position de bobinage ou depuis celle-ci et comprend un dispositif sectionneur comportant une lame de coupe qui pivote radialement vers l'extérieur lorsque la bobine auxiliaire est écartée de la bobine principale en position de bobinage, sectionnant ainsi l'élément qui les ponte.
4. Dispositif suivant la revendication 3, dans lequel le dispositif sectionneur comporte:
un élément de retenue immobile qui est disposé près de l'extrémité libre de la bobine auxiliaire et sur lequel la lame est montée de telle sorte qu'elle puisse pivoter autour d'un axe parallèle à l'axe de rotation de la bobine auxiliaire;
un bras pouvant pivoter autour de l'axe de rotation de la bobine auxiliaire par rapport à l'élément de retenue; et
un levier de liaison qui assure la liaison entre l'extrémité postérieure de la lame de coupe éloignée de son tranchant et l'extrémité libre du bras.
5. Dispositif suivant la revendication 4, dans lequel:
l'élément de retenue est relié à une extrémité d'un arbre fixe creux qui traverse coaxialement la bobine auxiliaire;
le bras pivotant est relié à une extrémité d'un arbre oscillant qui traverse coaxialement l'arbre fixe creux, et
l'autre extrémité de l'arbre oscillant est relié à l'arbre de sortie d'un moteur monté près de l'autre extrémité de l'arbre fixe creux pour produire les mouvements d'oscillation du bras.
EP19800303078 1979-09-07 1980-09-03 Dispositif pour le bobinage en continu d'un toron continu Expired EP0025340B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11487479A JPS5643164A (en) 1979-09-07 1979-09-07 Continuous winder for linear material
JP114874/79 1979-09-07

Publications (2)

Publication Number Publication Date
EP0025340A1 EP0025340A1 (fr) 1981-03-18
EP0025340B1 true EP0025340B1 (fr) 1984-07-11

Family

ID=14648838

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800303078 Expired EP0025340B1 (fr) 1979-09-07 1980-09-03 Dispositif pour le bobinage en continu d'un toron continu

Country Status (6)

Country Link
EP (1) EP0025340B1 (fr)
JP (1) JPS5643164A (fr)
AU (1) AU519820B2 (fr)
BE (1) BE885103A (fr)
CA (1) CA1137950A (fr)
DE (1) DE3068527D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4511095A (en) * 1982-02-27 1985-04-16 Shimadzu Corporation Method and apparatus for winding glass fibers
JP2667516B2 (ja) * 1989-06-19 1997-10-27 日本トムソン株式会社 有限直動案内ユニット
CN1135203C (zh) * 1997-10-06 2004-01-21 纳幕尔杜邦公司 合成纤维卷绕器和卷绕合成纤维的方法
CH709605A1 (de) * 2014-05-08 2015-11-13 Rieter Ag Maschf Textilmaschine zur Herstellung von Vorgarn sowie Verfahren zum Betrieb einer entsprechenden Textilmaschine.
CN109399913B (zh) * 2018-12-17 2023-09-26 泰安佳成机电科技有限公司 一种玻璃纤维φ260大卷重直接纱拉丝机

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1255852B (de) * 1962-06-07 1967-12-07 Gerresheimer Glas Ag Vorrichtung zur Durchfuehrung des Aufwickelvorganges
US3523650A (en) * 1965-05-14 1970-08-11 Owens Corning Fiberglass Corp Roving and method and apparatus for forming and packaging same
BE755154A (fr) * 1969-08-22 1971-02-22 Saint Gobain Pont A Mousson Dispositif de bobinage de fils en matiere thermoplastique, en particulier de fils de verre au cours de leur fabrication
AT302786B (de) * 1969-10-20 1972-10-25 M A G Maschinen Und Appbau Ges Spulenwechselvorrichtung an eingängigen oder mehrgängigen Wickelstationen in Drahtverarbeitungsanlagen
DE2032225A1 (en) * 1970-06-30 1972-01-05 Kloeckner Werke Ag Glass thread coiling machine - for uninterrupted coiling of melt derived thread
GB1456638A (en) * 1972-12-01 1976-11-24 Winget Ltd Continuous spooling apparatus
GB1554143A (en) * 1975-06-26 1979-10-17 Plastona Waddington Ltd John Plastics sheet material and articles produced therefrom
JPS5428511Y2 (fr) * 1976-03-29 1979-09-12

Also Published As

Publication number Publication date
AU6207580A (en) 1981-03-12
BE885103A (fr) 1980-12-31
JPS572629B2 (fr) 1982-01-18
EP0025340A1 (fr) 1981-03-18
CA1137950A (fr) 1982-12-21
JPS5643164A (en) 1981-04-21
AU519820B2 (en) 1981-12-24
DE3068527D1 (en) 1984-08-16

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