EP0334931A1 - Dispositif d'ensouplage croise - Google Patents

Dispositif d'ensouplage croise

Info

Publication number
EP0334931A1
EP0334931A1 EP88908668A EP88908668A EP0334931A1 EP 0334931 A1 EP0334931 A1 EP 0334931A1 EP 88908668 A EP88908668 A EP 88908668A EP 88908668 A EP88908668 A EP 88908668A EP 0334931 A1 EP0334931 A1 EP 0334931A1
Authority
EP
European Patent Office
Prior art keywords
linear
traversing
guide
coupling
belts
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP88908668A
Other languages
German (de)
English (en)
Inventor
Heinz Schippers
Walter Runkel
Klaus Weber
Friedrich Urbahn
Heinz Schippers
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
Barmag Barmer Maschinenfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Barmag AG, Barmag Barmer Maschinenfabrik AG filed Critical Barmag AG
Publication of EP0334931A1 publication Critical patent/EP0334931A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/28—Traversing devices; Package-shaping arrangements
    • B65H54/2821—Traversing devices driven by belts or chains
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/38—Arrangements for preventing ribbon winding ; Arrangements for preventing irregular edge forming, e.g. edge raising or yarn falling from the edge
    • B65H54/385—Preventing edge raising, e.g. creeping arrangements
    • B65H54/386—Preventing edge raising, e.g. creeping arrangements with energy storing means for recovering the kinetic energy at the end of the traversing stroke
    • 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

Definitions

  • the invention relates to a traversing device in a winder for a thread according to the preamble of claim 1.
  • Such a traversing device is with a belt as a linear drive e.g. known from DE-OS 34 44 648.
  • the invention solves the problem in a traversing device whose traversing stroke is easily adjustable and whose traversing stroke is continuously reduced and enlarged (breathing) even during the winding travel and / or continuously depending on the growing diameter to produce a bobbin with flattened (biconical ) End edges can be reduced, the moving masses can be reversed in their movement without significant energy loss in the stroke reversal points.
  • the invention according to the characterizing part of claim 1 provides that the coupling member, with which the carriage can be connected alternately to one of the two parallel linear drives, is forcibly guided in the reversal areas on a 180 ° cam track and driven at the traversing speed.
  • the Au dishwasher can be configured so that the traversing stroke can be shortened continuously at one or both ends of the stroke or continuously changed between a maximum and a minimum during the winding cycle. Due to the continuous shortening of the traversing stroke, a coil is created conical or biconical faces. The recurring change in the traversing stroke between a maximum value and a minimum value is called "breathing". It is a very special advantage of the invention that this breathing also causes a mirror disturbance.
  • the cam tracks which are arranged in the stroke ends, run continuously in the longitudinal direction of the traversing stroke as a function of the growing diameter (biconical winding) or as a function of time or the winding diameter or according to another program adjusted.
  • the coupling member is driven in the embodiment of the invention according to claim 3 in that the coupling member is designed as a linear element of finite length (belt, chain, belt or the like), which extends over a partial length of twice the traversing stroke and one in the reversal areas carries out continuous, unchecked movement, so that it moves with undiminished speed from the leading linear drive to the returning linear drive and vice versa in the other stroke reversal area from the returning linear drive to the leading linear drive and always with one of the linear drives in mechanical, magnetic, electromagnetic drive connection.
  • the coupling member is so long that it is in the stroke reversing areas at the same time with both linear drives in drive connection. Overlapping the ends of the linear coupling member is prevented by the linear coupling member is not longer than its distance covered at a d oppelten shortest traverse stroke (Hmin) route.
  • Belts are particularly suitable as linear drives.
  • the two linear drives can be the belt belt running in and the belt belt running back of an endless belt.
  • the linear coupling link is a piece of a chain, a belt or a belt.
  • the endless belt can extend over several winding units and traverse strokes.
  • the contact between the coupling member and the linear belt can be produced in a mechanical manner by providing pressure guides between the two linear rims which always press the linear coupling member onto the linear belt at least at one point (claim 4).
  • the deflection rollers arranged in the stroke reversal areas, which form the inner guide of the cam track, also serve as pressure guides.
  • the pressure guides are designed as pressure rollers or as an endless belt which extends and rotates as an island between the linear drives over the traversing stroke and thereby the coupling member movably guided on the slide against one or the other presses another linear actuator.
  • a constant and tight contact of the coupling belt on the linear belt is achieved if the length of the coupling belt is greater than the greatest possible distance between the deflecting guide and the next pressing guide or between two pressing guides, since the coupling belt always engages with it at two points one or both linear drives.
  • a non-mechanical connection between the coupling belt and the linear belt can also be achieved by magnetic and • magnetizable inserts in both elements, as is provided by claim 5. This prevents mechanical wear.
  • a particularly advantageous because wear-free drive option also consists in the fact that the linear drives are designed as electrical linear drives (claim 7). These linear drives extend parallel to each other.
  • the linear coupling elements, coupling belts or the like consist or have an insert made of a magnetizable material. A linearly propagating electromotive force is exerted on the coupling element by the electromagnetic linear drive.
  • the coupling member is guided along the linear drive in such a way that it enters the cam tracks provided there at the ends of the traversing stroke and can be directed onto the other linear drive.
  • the special feature here is that the linear drives move at twice the traversing speed.
  • a guide roller is provided on the coupling chain, preferably at the tip, which lies in a different plane from the linear belts and the drive rollers in one plane namely, in which the outer deflection of the cam track lies.
  • the guide roller moves on the outer deflection guide of the cam track, while the drive rollers roll on the inner reversing guide in the reversing areas.
  • the inner reverse guide lies in the plane of the linear belts and the drive rollers.
  • the guide island consists in at least one longitudinal area of superimposed plates, lamellae or the like, which overlap and which can be displaced relative to one another, without thereby interrupting the flanks of the guide island facing the linear belt (Claim 10).
  • the slide track of the slide can be curved such that additional decelerations and / or accelerations are superimposed on the sinusoidal reversing movement of the slide block during transmission to the traversing slide.
  • the drive takes place in the reversing ranges by a drive element which extends along a runway at a constant distance and which is driven at twice the linear speed of the linear drives.
  • the cam track is formed by the stationary roller track and a drive surface concentric to it.
  • the driving surface can surround the runway on the outside and then has the shape of an endlessly revolving timing belt (claim 15).
  • the linear driving surface can also lie within the curved path (claim 13). It then preferably has the form of a belt which rotates endlessly between the traversing stroke ends (claim 14) or in each case a rotatably driven roller arranged in the reversing regions.
  • the coupling member is a double-sided gripper which is movably guided on the carriage and has a freely rotatable roller mounted thereon.
  • the freely rotatable roller is clamped in the reversing ranges between the stationary runway and the driving surface moving at the double traversing speed and thereby guided with the traversing speed through the cam track in such a way that the gripper stands out from one linear drive and bears against the other linear drive.
  • the drive surface according to claim 14 or 15 is an endlessly rotating control belt.
  • the deflection pulleys of this timing belt are mounted in the reversing areas of the traversing stroke and can be adjusted along the traversing stroke to shorten or lengthen the traversing stroke together with the cam tracks.
  • the timing belt is guided by deflection rollers so that when the traversing stroke is shortened or lengthened, a corresponding length compensation of the timing belt takes place.
  • the timing belt is guided so that the change in the traversing stroke length has no influence on the length of the timing belt.
  • the belt is guided in a W-shaped manner at each movable reversing area, in that a belt strand of the endlessly rotating control belt at each movable traversing stroke end by means of a compensating roller that can be displaced together with the deflecting roller and a further stationary compensating roller again 180 ° out of the traversing stroke region and by 180 ° is deflected again in the direction of the traverse stroke.
  • the control belt can extend over a plurality of winding stations and traversing areas, the traversing strokes being able to be changed independently of one another and without changing the belt length.
  • FIG. 1 top view and section through a first embodiment
  • Fig. 2A top view and section through a second embodiment to 2D example
  • Fig. 3 supervision of a third embodiment
  • a guide surface of the up to 4C cam track is a driving surface
  • Fig. 5 an embodiment in which the outer surface 5A, the cam track is formed by a circumferential belt 5B.
  • the traversing thread guide 1 is fastened to a carriage 2.
  • the carriage 2 is straight in rods 3.
  • the carriage 2 has a straight slot 13 perpendicular to the rods 3, which serves as a slide track.
  • a sliding block 14 is guided in the sliding track 13.
  • the sliding block 14 sits on a coupling link 10, which has the shape of a chain, a belt, a band or the like.
  • the coupling member 10 is driven by the linear drives 4 and 5, which extend along the straight guides 3 and have the opposite direction of movement.
  • the link guide 13 extends between the two linear drives 4 and 5.
  • the linear drives 4 and 5 are linear belts.
  • the linear drives 4 and 5 are linear belts.
  • the linear speed of the belts 4, 5 is twice the predetermined traversing speed.
  • a pressure guide (guide island) with a stationary part 6 and a movable part 7 lies in the middle between the linear belts 4 and 5.
  • the pressure guide extends along the two linear belts.
  • the side flanks of the pressure guide form a narrow gap with the linear belt 4 or linear belt 5.
  • a curved track is fastened with an inner deflection guide 8 and an outer deflection guide 9.
  • the coupling link 10 is a finite chain.
  • the sliding block 14 is seated at the head of the chain.
  • pinch rollers (drive rollers) 11 are each freely rotatable.
  • a drive roller 11 and a freely rotatable deflection roller 12 are seated on the head of the chain, specifically axially in different parallel planes, as shown in FIG. 1A.
  • the outer deflection guide 9 In a plane above the linear belts 4 and 5, in the same plane as the deflection roller 12, the outer deflection guide 9 also sits in the form of an approximately semicircular bracket which is open to the traversing stroke H. The ends of the outer deflection guide 9 are parallel to the linear belts 4 and 5 and to the parallel flanks of the pressure guide 6 and 7, so that the guide roller 12 can move smoothly and smoothly into the deflection guide and extend from the deflection guide.
  • FIGS. 1 and 1A The other end of the stroke also has a mirror-image arrangement of a movable part 7 of the pressure island with an inner deflection guide 8 and an outer deflection guide 9.
  • the traversing thread guide 1 is now driven via the stroke H and is moved back and forth in that the drive rollers 11 are pressed by the linear belts 4 and 5 onto the flanks of the pressure island 6, 7 and thereby roll on the flanks.
  • the speed of the traversing thread guide 1 corresponds here to the speed of the chain.
  • the guide roller 12 rolls on the outer deflection guide 9.
  • the chain 10 is now pushed by the following rollers 11 until the first drive roll 11 enters the gap between the returning linear belt 5 and the facing flank of the pressure island 6, 7.
  • an additional guide roller 15 can be provided on the axis of the last drive roller 11 (shown in broken lines). This guide roller 15 will sit in the same plane as the guide roller 12 and be guided in the stroke end region by the outer deflection guide 9.
  • the law of motion with which the traversing thread guide 1 reverses its direction of movement in the stroke end range depends on the distance between the linear belts 4, 5, the shape of the outer deflection guide 9 and the diameter of the guide roller 12.
  • the outer deflection guide 9 can be designed with selectable functions in a circular, parabolic, sinusoidal manner.
  • the diameter of the guide roller 12 can be smaller or larger than shown, in particular also smaller than the drive rollers 11.
  • the law of movement of the traversing thread guide can also be influenced by the shape of the sliding track 13. This will be described later with reference to Fig. 2D.
  • the distance between the linear belts can be freely designed in the specified frame.
  • the stationary part 6 and the movable part 7 of the pressure island are connected to one another in that the two parts overlap one another in the manner of a lamella, the lamellae being able to be moved towards one another. This ensures that the drive rollers 11 can also roll on an uninterrupted flank in the separating area between the stationary part 6 and the movable part 7 of the pressure island.
  • Fig. 1A it is shown that the parting plane is perpendicular to the axes of the drive rollers 11, approximately on the axial center of the drive rollers 11.
  • the stroke length H can be adjusted in order to breathe (reversing shortening and lengthening of the stroke) or to produce biconical coils (continuous shortening of the stroke during the beginning or the whole course or a partial course or end of the winding travel). It should be particularly pointed out that this device also causes a mirror disturbance at the same time as breathing, since breathing also changes the ratio of the coil speed to the traversing frequency which is decisive for the mirror disturbance in the wild winding.
  • linear belts 4 and 5 are again used as linear drives, which are driven in opposite directions at the traversing speed. It can be the running belt drum 4 and the return belt belt 5 of an endlessly rotating belt. Between the two linear belts 4 and 5 there is a stationary pressure guide 6 in the form of a freely rotatable pressure channel and a movable pressure guide 7, to which the inner deflection guide 8 in the form of a freely rotatable guide roller and the outer deflection guide 9 in the form of a deflection curve are attached.
  • the pressure rollers 6 and deflection rollers 8 have the same diameter.
  • other can also be on the movable pressure guide Pressure rollers, which can have the same diameter as the pressure roller 6 (not shown), are attached.
  • the linear coupling member 10 here has the shape of a finite belt, at the beginning of which the sliding block 14 engaging in the sliding track 13 of the ship 12 is fastened.
  • the coupling belt 10 is pressed by the pressure rollers 6 and the deflection rollers 8 against the linear belt 4 and thereby driven.
  • pressure rollers 6 and deflection rollers 8 have a diameter which essentially corresponds to the distance between the linear belts 4 and 6.
  • the pressure rollers 6 and deflection rollers 8 act to clamp the coupling belt 10 on the two linear belts 4 and 5.
  • the length of the coupling belt 10 is greater than the greatest distance between two successive pressure rollers 6 or between two successive pressure and deflection rollers and greater than half the circumference of the deflection rollers. This ensures that the belt is always in line contact with one of the linear belts 4 or 5 and is already reclaimed in the reversal areas both by one linear belt 4 and at the same time by the other linear belt 5.
  • the coupling belt 10 is at least as long as the distance between the pressure roller 6 and the deflection roller 8. In the case shown, it is twice as long as this distance. As shown in FIG. 2A, the distance between the deflection rollers 8 can nevertheless be reduced, so that there is a minimum traversing stroke H m _ n . To at the shortest In order to avoid an overlap of the belt ends, the coupling belt is shorter than the sum of the double oscillation stroke and the circumference of the deflection roller minus the diameter of the deflection roller. To guide the coupling belt 10, the pressure island can in turn have side flanks which are adjacent to the linear belts 4 and 5.
  • a double traversing stroke means a movement plus a back movement of the traversing thread guide.
  • the law of movement of the traversing thread guide 1 in the reversal areas is determined by the diameter of the deflecting roller 8. Variations of the law of movement are made possible if a rigid deflecting guide with a specifically designed path is provided as the curved path. It is also possible to provide individual rollers of smaller diameter along a specifically designed deflection path for deflecting the coupling belt 10.
  • the guide track 13 is curved, namely S-shaped. If, in this embodiment of the guide track 13, the slide 2 moves to the left and the coupling member 10 with the guide block 14 into the left circular one cam device, so the sliding block a sinusoidal movement leads 14, although in the traversing direction, however, since at the same time slides on the curved slide track 13, he gives the carriage -. in the illustrated case - during the movement through the first quarter of the guide path 13 a ⁇ relative additional movement to the left, to move through the second and third quarters of the slide track a qualify ⁇ move to the right and to move through the last quarter of the slide track again an additional movement to the left.
  • the shape of the guide path can thus be another motion law superimposed on the sinusoidal motion law, so that a suitable traversing motion is obtained for the slide. It should be expressly emphasized that such a shape of the slide tracks can also be considered for the exemplary embodiments according to FIGS. 1 and 3.
  • the sliding block 11 is in turn seated on a coupling belt 10.
  • the coupling belt 10 is driven by the linear belts 4 and 5, which in turn can be the belt spaces of an endlessly rotating belt.
  • the linear belts 4 and 5 and the coupling belt 10 have magnetic inserts which ensure that the coupling belt 10 fits tightly against the linear belts 4 and 5.
  • the outer deflection guide 9 is designed here so that it protrudes with a sharp corner into the angle between the inner deflection guide 8 and the leading linear belt and thereby peels the coupling belt 10 against the magnetic holding forces from the linear belt 4.
  • the inner and outer deflection guides are in turn movable at least on one side between the end points of a maximum traverse stroke and a minimum traverse stroke.
  • the inner deflection guides are in turn freely rotatable deflection rollers, the diameter of which essentially corresponds to the distance between the belt spaces 4, 5.
  • the linear drives are linear belts 4 and 5, which are driven with the opposite direction of movement and ganging speed. It can be, for example, belt dreams of an endlessly rotating belt which extends over several traversing points.
  • the traversing carriage 2 is straight on rods 3. It has the traversing thread guide 1 at its front end.
  • a gripper is movably guided in a straight guide 17 on the slide.
  • the gripper has gripping jaws 18.R on its opposite ends and 18.L.
  • the gripper is urged by compression springs 19 and 20 in "its end positions.
  • the spring 20 is supported on the carriage 2 so that the abutment on the Mittel ⁇ line between the two linear belts 4, 5 are located.
  • the cam track arranged in each reversal area and displaceable in the traversing stroke direction consists on the one hand of a fixed deflection guide 9 and on the other hand of a rotatably driven roller 8 as an inner deflection guide.
  • the outer deflection guide 9 extends with a semicircular arc from one belt drum 4 to the other belt drum 5, in such a way that its outlet ends form a tangent to the roller 23 when the roller 16 is in one of the end positions.
  • the deflection roller 8 is arranged concentrically to the arc of the outer deflection guide. Both deflection rollers 8 are driven at a peripheral speed that is twice the traversing speed.
  • the diameter of the deflecting rollers 8 is so large that the circumference of the deflecting roller 8 with the outer deflecting guide 9 forms a gap from the width of the diameter of the roller 23 on the gripper 16.
  • the deflecting roller 8 and the outer deflecting guide 9 assigned to each " reversal area " are mounted on a common support, just like the roller 23 in a plane that lies above the belts 4 and 5, respectively.
  • the gripper 16 is pressed by the springs 19, 20 into one of the clamping positions. This creates a positive or non-positive connection between the respective belt drum and the sled. In the case shown, the carriage moves to the right.
  • the roller 23, which stands on the gripper 16 comes tangentially into the gap between the circumference of the deflection roller 8 and the outer deflection guide 9. This has the consequence that the roller 23 by the circumference of the roller 8 with the double traversing speed is driven. Consequently, the roller 23 rolls on the outer deflection guide and receives a linear speed which corresponds to the traversing speed of the belts 4 and 5, respectively.
  • the roller In the gap between the deflection roller 8 and the outer deflection guide 9, the roller is simultaneously given a movement in the direction of the slide path 17. As a result, the gripper 16 is lifted from the belt drum 4 and, when the roller 23 runs out of the gap between the deflection roller 8 and the outer deflection guide 9, is placed on the belt drum 5 running to the left. As a result, the carriage 2 now receives frictional or positive contact with the belt belt 5 running to the left and is carried by it to the other reversing area, where the same functions are repeated in the opposite direction.
  • a fixed outer deflection guide 9 and a deflection roller 8 are arranged in each reversing area.
  • the deflection rollers are driven at a circumferential speed which is equal to twice the traversing speed.
  • An endlessly rotating control belt 24 is placed over the two deflection rollers 8 arranged in the stroke reversing areas.
  • the control belt 24 is tensioned by tensioning device 25.
  • the tensioning device has two or more stationary, freely rotatable tensioning rollers for the timing belt. Between the stationary tensioning rollers, the timing belt is moved straight out of it by movable tensioning rollers 26 Direction deflected.
  • the movable tensioning rollers 26 are mounted on a support 28 which is movable under a tensile force, for example spring force 27.
  • Each deflecting roller 8 and the associated outer deflecting guide 9 are arranged concentrically to one another, the deflecting guide 9 describing a semicircular arc.
  • the radii and diameters of the deflection roller 8 with the control belt 24 and the outer deflection guide 9 are designed such that a gap with the width of the diameter of the roller 23 mounted on the gripper is formed between the two.
  • Each deflection roller 8 and the associated outer deflection guide 9 are arranged on a common support which can be moved in the traversing stroke direction. The change in length of the control belt 24 to be compensated is compensated for by the tensioning device 25.
  • deflection rollers 8, deflection guides 9 and the roller 23 attached to the gripper lie in a common plane which lies above the plane of the two belt spaces 4 and 5.
  • the drive motor 29, which also serves to drive the endlessly rotating belt 4, 5, is used to drive the deflection rollers 8.
  • the necessary transmission ratio is established via a countershaft 30.
  • the countershaft 30 is arranged and the belt connection to the deflection roller 8 is designed so that the deflection roller 8 has the necessary freedom of movement to shorten the stroke or to extend the stroke.
  • a pulley 33 is rotatably arranged on a carrier 34.
  • the carrier 34 are mounted on a threaded spindle and guided in guides 36 and secured against rotation.
  • the threaded spindles have threads of opposite pitch, which are assigned to each of the carriers 30.
  • a deflection roller 37 is also rotatably arranged on each carrier 34.
  • the deflection rollers 38 are fixed in place in the machine frame. As shown in FIG. 5A, one of the deflection rollers 38 is driven by a motor 29 via a countershaft 30, which also serves to drive the deflection roller 32 of the belt 4, 5.
  • An endless belt is looped over the pulleys 33 and the deflection rollers 37 and 38 in such a way that the belt loops around the pulleys 33 at 180 °, that one belt strand extends directly between the belt pulleys 33 and that the other belt drum on the belt pulleys 37 and 38 is deflected at 180 ° each before the belt ends meet.
  • This W-shaped belt guide of the control belt at each stroke end ensures that the traversing stroke, which is determined by the spacing of the deflection rollers 33, can be changed without the belt length changing.
  • An inner deflection guide 8 with a semicircular guideway is also attached to the carrier 34 on a rigid axis 39 concentrically to the pulley 33, but in a non-rotating manner.
  • the width of the control belt 24 is greater than the width of the belt pulley 33.
  • the control belt 24 wrapping around the belt pulley 33 therefore forms a semicircular-shaped gap with the inner deflection guide 8. The width of this gap corresponds to the diameter of the roller 23 rotatably mounted on the gripper 16.
  • control element with its deflecting elements 33, 37, 38 is located in one plane on the underside of the carrier 34.
  • the roller 23 is mounted on the top of the gripper 16 in the same plane as the underside of the control belt 24.
  • the motor 29, which also serves to drive the endlessly rotating belt 4, 5, is used to drive the control belt 24.
  • the necessary transmission ratio is established via a countershaft 30.
  • the countershaft 30 is rotatably connected to one of the fixed deflection rollers 38.
  • the gear ratio is such that the timing belt is driven at twice the traversing speed.
  • the carriage 2 is conveyed to the right by clamping the belt strand 4 between the gripper 16 and the gripping jaw 21.R.
  • the roller is already on the inside of the timing belt 24. Your scope therefore receives an absolute speed that is twice as large as the traversing speed.
  • the circumference of the roller comes tangentially into contact with the inner deflection guide 8.
  • the roller is clamped between the inner deflection guide 8 and the inside of the control belt 24.
  • the roller now rolls on the inner deflection guide 8 and is conveyed at the traversing speed.
  • the gripper 16 Since the gap between the inner deflection guide 8 and the control belt 24 also has a component in the direction of the slide track 17, the gripper 16 is lifted off the belt drum 4 and finally placed on the belt drum 5. The carriage is now conveyed in the opposite direction, ie to the left, until the same process is repeated at the other end of the stroke.
  • Deflection pulley pulley carrier threaded spindle guides deflection pulley, pulley deflection pulley, pulley rigid axle

Landscapes

  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Structure Of Belt Conveyors (AREA)
  • Treatment Of Fiber Materials (AREA)

Abstract

Pour le mouvement de va-et-vient des fils, on emploie des dispositifs d'ensouplage croisé à guide-fil droit (1). Le guide-fil est soumis à un mouvement de va-et-vient par l'action d'un entraînement linéaire. Dans les régions d'inversion de la course, le guide-fil doit normalement être découplé de l'entraînement linéaire et il est nécessaire d'annuler son énergie cinétique et d'appliquer l'énergie à fournir pour le mouvement de retour. Pour éviter l'annulation de l'énergie et le désaccouplement, le guide-fil est relié à l'entraînement linéaire par un élément de couplage qui est guidé dans les régions d'inversion de la course entre deux guides de renvoi (8, 9) et entraîné avec la vitesse d'ensouplage. L'élément de couplage (10) peut être linéaire et plus court que le double de la plus petite course de l'ensouple. L'élément de couplage comporte un coulisseau (14) qui se déplace dans la coulisse (13). L'élément de couplage peut comporter un galet (23) mis en mouvement par une surface d'entraînement tournante dans les régions d'inversion de la course.
EP88908668A 1987-10-09 1988-10-06 Dispositif d'ensouplage croise Withdrawn EP0334931A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3734225 1987-10-09
DE3734225 1987-10-09
DE3809112 1988-03-18
DE3809112 1988-03-18

Publications (1)

Publication Number Publication Date
EP0334931A1 true EP0334931A1 (fr) 1989-10-04

Family

ID=25860640

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88908668A Withdrawn EP0334931A1 (fr) 1987-10-09 1988-10-06 Dispositif d'ensouplage croise

Country Status (4)

Country Link
US (1) US4973007A (fr)
EP (1) EP0334931A1 (fr)
JP (1) JPH02501565A (fr)
WO (1) WO1989003359A1 (fr)

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WO1989003359A1 (fr) 1989-04-20
US4973007A (en) 1990-11-27

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