EP0538316B1 - Dispositif d'emmagasinage et d'amenee de fil - Google Patents

Dispositif d'emmagasinage et d'amenee de fil Download PDF

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Publication number
EP0538316B1
EP0538316B1 EP19910912562 EP91912562A EP0538316B1 EP 0538316 B1 EP0538316 B1 EP 0538316B1 EP 19910912562 EP19910912562 EP 19910912562 EP 91912562 A EP91912562 A EP 91912562A EP 0538316 B1 EP0538316 B1 EP 0538316B1
Authority
EP
European Patent Office
Prior art keywords
thread
feed
storage
delivery apparatus
drive shaft
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 - Lifetime
Application number
EP19910912562
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German (de)
English (en)
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EP0538316A1 (fr
Inventor
Tore Claesson
Lars-Berno Fredriksson
Pär JOSEFSSON
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Iro AB
Original Assignee
Iro AB
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
Priority claimed from SE9002409A external-priority patent/SE9002409D0/xx
Priority claimed from SE9003780A external-priority patent/SE9003780D0/xx
Priority claimed from SE9003796A external-priority patent/SE9003796D0/xx
Priority claimed from SE9101226A external-priority patent/SE9101226D0/xx
Priority claimed from SE9101234A external-priority patent/SE9101234D0/xx
Priority claimed from DE4119370A external-priority patent/DE4119370A1/de
Application filed by Iro AB filed Critical Iro AB
Publication of EP0538316A1 publication Critical patent/EP0538316A1/fr
Application granted granted Critical
Publication of EP0538316B1 publication Critical patent/EP0538316B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/34—Handling the weft between bulk storage and weft-inserting means
    • D03D47/36—Measuring and cutting the weft
    • D03D47/361—Drum-type weft feeding devices
    • D03D47/362—Drum-type weft feeding devices with yarn retaining devices, e.g. stopping pins

Definitions

  • the invention relates to a thread storage and delivery device according to the preamble of claim 1.
  • feed elements with this drive principle are coupled to the drive shaft in a motion-transmitting manner and are movable relative to the support elements
  • storage bodies with a variable diameter of the support elements as are used for weft thread storage and delivery and measurement devices, are a tumbling plate-like feed element is known which pushes the first turn axially forward only from the winding side and thereby creates undesirable contact zones between the turns in the supply, because no separation of the turns is possible.
  • a thread storage, delivery and measuring device in which the support elements of the storage body are adjustable in diameter, and in which feed elements distributed over the circumference are provided for separation during feed, has already been exhibited, but is not yet in practice to be found.
  • the invention has for its object to provide a thread storage and delivery device with thread separation, which is easily and universally adaptable to changing operating conditions and / or thread qualities.
  • the relative position of each feed element with respect to its associated support element is changed when the diameter of the storage body is unchanged, in order to adapt the separation and the feed to the respective operating condition or thread quality.
  • the adjustment of the separation to the thread quality can be carried out with overlying turns and even during operation. There is a universal adaptability of the separation to changing operating conditions and / or the thread qualities.
  • the rapid and precise adjustment of the diameter of the storage body by moving the support elements together means no loss of thread separation during feed, because the feed elements are adjusted together by means of the support elements when they are adjusted and so that the separation is maintained during feed .
  • Any desired changeover can be carried out quickly, so that the changeover times are short.
  • the changeover can be carried out particularly advantageously even with overlying windings and also during operation, because the feed elements forcibly assume their relative positions with respect to the support elements when they are adjusted, which are necessary for the separation and the feed.
  • a quick adjustment, for example of the weft thread length, is possible. If the diameter changes, the feed elements are adjusted to the new diameter using the support elements.
  • Another embodiment represents a departure from the usual drive principle of the feed elements, because these are brought to their feed movement independently of the drive shaft.
  • the feed elements are adjusted together with the support elements without endangering the separation during the feed; in the case of a storage body with an unchangeable diameter, the separation is adapted to the operating conditions or the thread quality in a structurally simple manner.
  • both the diameter adjustment and the separation adjustment are simple because the feed movement of each feed element with respect to the radial movement component is independent of the radial distance from the drive shaft or movement control elements arranged there. Only axial motion components are derived from the drive shaft.
  • the radial and axial movement components for the feed element are derived from the drive shaft in a conventional manner
  • the radial adjustability of the feed element is given, which is used for the diameter adjustment and / or for the separation and feed adjustment.
  • the radial adjustment resistance of the connection is not overcome by the contact pressure of the windings, so that these are raised, separated and conveyed forward during feed become.
  • the radially adjustable connection is released for this purpose and then fixed again.
  • the release resistance of the slip clutch is overcome only for the adjustment, the feed elements are coupled to the drive shaft during operation.
  • the height difference and thus the separation are set by means of the adjustment mechanism.
  • the diameter of the eccentric circle that rotates in operation with its center around the drive shaft axis, in which the feed elements are inscribed is changed relative to the diameter of the circle, in which support elements are inscribed.
  • the feed element With a towing coupling between the feed element and the support element, the feed element is forced to follow a radial adjustment of the support element.
  • the inclined and eccentric cylinder surface is the drive control element for the drive shaft driven by the drive shaft Separation and feed movement of the feed elements. If the diameter changes, the feed elements are taken along via the towing coupling. By turning the drive shaft, the feed elements are subsequently centered on the cylinder axis within the radial play, so that they produce the same separation as before the diameter change.
  • the radially adjustable connection blocks during operation.
  • the guide elements are displaced relative to one another.
  • the radially adjustable connection ensures that the radial and axial movement components derived from the rotation of the eccentric and inclined cylindrical surface are transmitted directly to the feed element.
  • the feed element has two additional degrees of freedom, by means of which movement components resulting from the wobbling movement of the cylinder and which disrupt a clean feed movement are kept away from the feed element.
  • the feed element can move along in an ideal path during the feed movement.
  • the clamping ring which is pressed with elastic pretension, produces a fixed stop in the radial direction between the feed element and the handle during operation, wherein the relative rotational movement of the feed element and the cylinder axis is permitted.
  • the slip clutch is structurally simple, reliable and stable.
  • the towing coupling acts in the radial direction, but other movement components of the feed element are not hindered.
  • a stop pin engaging in an oversize bore can be moved on all sides within the scope of the oversize bore.
  • the stops and counterstops are only required for the adjustment. They have no function in operation.
  • the radial excess of the distance creates the possibility of changing the relative height by a subsequent adjustment of the support elements radially inwards or outwards.
  • a simple and rapid change in the diameter of the storage body while maintaining the separation results in a further embodiment.
  • the changeover is possible during operation.
  • the aforementioned goal is achieved in a structurally simple manner if the feed elements are taken along via the towing couplings. Once the new diameter has been set, the drive shaft only needs to be turned at least once to center all the feed elements. If a change in the separation is also desired, the support elements are adjusted radially again.
  • the axial movements are derived from the drive shaft, while the radial movement components are generated from the relative longitudinal movements of the parts of the feed element, since the phase shift between the inclined positions leads to asynchronous axial movements of the two parts.
  • correspondingly inclined radial surfaces can also be used to generate the axial control movements.
  • the radial movement components are generated by means of the rising ramps.
  • an embodiment is also advantageous in which a locomotive movement for the upper part is generated from axial movement components of the two parts of the feed element.
  • These drive the eccentrics like a locomotive undercarriage slipping while standing, cyclically raising and lowering the outside of the feed element and moving it back and forth in the axial direction.
  • the eccentrics are coupled as with two coupling rods offset by 90 ° to one another, so that an unstable dead center position never occurs.
  • the other arms of the angle lever allow the axial and radial components of movement thanks to their elasticity in bending.
  • radial movement components of the upper part are generated by the ramps.
  • Intermediate needle rollers reduce resistance to movement and prevent wear.
  • the displacement is adjusted from the outside, i.e. even during operation. It is important that after reversing the displacement, the thread storage and delivery device can work in the opposite direction with separation during feed.
  • the rotary drive not only can the separation be adjusted, but also the feed for the reverse direction of rotation of the winding member of the thread storage and delivery device can be changed.
  • Another hub can be responsible for the radial movement components, as for the axial movement components.
  • the arm allows the axial components of motion thanks to its elasticity or displaceability, while transmitting radial components of motion.
  • sliding block or link guides work precisely and with little wear.
  • the arm which is flexible in the axial direction, is radially adjustable on the adjusting element of the hub.
  • the feed element can be adjusted radially by axially displacing the hub.
  • the feed element is stably supported under the windings during operation.
  • the breakaway resistance of the slip clutches is overcome.
  • the driver connection transmits the axial movement components.
  • the swivel joints enable the complex movement of the feed element.
  • axial and radial movement components are generated by separate control elements on the drive shaft, which offers the possibility of reversing the phase shift in order to change over to the opposite direction of rotation of the rewinder or to change the separation.
  • a pressure medium chamber with overpressure or underpressure ensures the radial support of the feed element during operation.
  • the feed element can be driven with magnets for feed movement independently of the drive shaft in the support element.
  • the separation is freely selectable. It is possible to carry out a changeover during operation or to remove one or more feed elements Function. Furthermore, this feed control drive can be easily switched to the reverse direction of rotation of the winding member. A change in the diameter of the storage body has no influence on the separation. Furthermore, the separation is independent of the diameter of the storage body.
  • the strip moves from the inner limit position in the following in a further embodiment applied turns under the force of the spring element again to the outer limit position.
  • a thread storage and delivery device F has a stationary base body G, in which is mounted a drive shaft T which can be driven by a drive, not shown, the axis of which is denoted by H.
  • a storage body K is rotatably mounted on the drive shaft T and is blocked against rotation by means not shown, for example permanent magnet pairs.
  • the storage body K is drum-shaped and forms a rotationally symmetrical Storage area for a thread supply consisting of turns W of a thread U, preferably a weft thread for a weaving machine, which is drawn off intermittently, for example, in precisely dimensioned, identical longitudinal sections.
  • the drive shaft T carries a tubular winding member I which winds successive windings W, from which the thread is drawn off overhead in the direction of the arrow.
  • a stop device B is attached to the housing G with a stop element B ′ which can be moved radially back and forth and which, as is known, engages in the thread path between the pull-off cycles and is withdrawn for the pull-off.
  • the storage area of the storage body K is defined by stationary rod-shaped support elements A distributed in the circumferential direction and rod-shaped feed elements V assigned to them.
  • the feed elements V - as will be explained later - are driven to a feed movement while the drive shaft I is running, in order to move the windings W in FIG. 1 forward from left to right and to separate them at predetermined intermediate distances.
  • the support elements A are mounted in the storage body K in a radially adjustable manner and engage with engagement elements 1 in a face thread 2 of an adjusting washer Q, which can be driven to rotate, possibly by an actuator E, in order to change the outer diameter of the storage body K defined by the support elements A. .
  • the outer sides of the support elements can be written in a circle concentric to the axis H.
  • Each feed element V is arranged with play on all sides in a support element A. But it could also be between two support elements A.
  • a sleeve 3 On the drive shaft T, a sleeve 3 is fixed, the outside of which has a cylindrical surface Z, the axis 8 of which is inclined at an angle with respect to the drive shaft axis H and is also (FIG. 2) eccentric to the drive shaft axis H (eccentricity e). In the direction of rotation of the drive shaft T, an offset of, for example, 90 ° (see FIG. 7) is provided between the inclined position and the eccentricity.
  • a hub H which is coaxial with the cylinder axis 8, is mounted on the cylinder surface Z, on which the feed elements V are attached together like spokes. Each feed element V is connected to the hub N with a connection C which can be adjusted in the radial direction and which in FIG.
  • the feed element V has a cylindrical shaft 6 which engages in a sleeve 4 with a sliding fit and is fixed by a clamping ring 7.
  • the sleeve 4 is mounted with stub axles 5 (axis 9) in the hub N in Fig. 1 from and into the plane of the drawing to a limited extent.
  • the support element A has an approximately axial shaft A 'for receiving the feed element V.
  • the sleeve 4 can be pivoted to a limited extent in an opening 16 of the hub N with the stub axles 5 in bores 10 about the axis 9, the axis 9 approximately is parallel to the cylinder axis 8.
  • the shaft 6 can be rotated with the feed element V about an axis 11 defined by a bore 12 of the sleeve 4 and radial to the cylinder axis 8, since the clamping ring 7 sits in a groove 13 of the shaft 6 with little radial and axial play and with elastic prestress against the wall of the bore 12 is pressed.
  • the towing coupling S is formed according to FIGS. 1 to 3 by stops 14 on the feed element V and by counter stops 15 of the support element A, a predetermined radial play being provided.
  • each feed element V is first moved radially outwards over the outer side of the support element A and then after one revolution of the drive shaft T from a position in which its outside lies radially below the outside of the support element A. additionally moved to the right in the axial direction in FIG. 1 in order to lift the windings W, to carry them forward and to separate them, before it steps back under the support element A and is set to the left in the axial direction. All feed elements V execute the same movement one after the other in the direction of rotation.
  • the drive shaft T stops. If thread U is then required, the stop element B 'is withdrawn and the required turns W are withdrawn. Falls below the number of turns W on the storage body K a certain size, the drive shaft T is rotated again and the stock is replenished.
  • the thread U drawn off during a withdrawal has a predetermined length, which is set by adjusting the diameter of the storage body K.
  • the adjusting ring disc Q is rotated, the support elements A jointly moving radially outwards or radially inwards.
  • the stop device B on the housing E is released and the distance between the storage body K and the stop device B is set.
  • the feed element V are taken along with the adjustment via the drag clutches S.
  • the breakaway resistance of the slip clutches R is overcome during the adjustment. Since the feed elements V are initially concentric to the drive shaft axis H during this adjustment by the support elements A, but should define a circle for the separation during the feed, which is concentric to the cylinder axis 8, the drive shaft T is rotated at least once so that the feed elements V by means of the Towing couplings S and the support elements A are centered about the cylinder axis 8.
  • the device F is then ready for operation again.
  • the adjustment can be carried out remotely by means of the actuator E, and also during the operation of the device F.
  • the resistance of the slip clutches R is greater than the contact pressure of the windings W, so that the windings W are unable to connect the radially adjustable connections C. to adjust automatically.
  • radially adjustable can be detached and fixed again in another way Connections may be provided.
  • Two groups of stops 14 and counter-stops 15 are provided on each longitudinal side of the feed element V.
  • the radial distance between the counter-stops 15 corresponds to at least twice the eccentricity e plus the radial thickness X of the stop 14. This ensures that the feed elements V are in the same each time the support elements A and the subsequent rotary movement of the drive shaft T are adjusted Center the relative position with respect to the support elements A because each stop 14 is intercepted once at the upper counter-stop 15 and once at the lower counter-stop 15.
  • the feed and separation effect is therefore independent of the radial setting position of the support elements A.
  • the separation can, however, increase with increasing diameter of the support elements A because the lever arm of the feed elements V increases.
  • 5a and 5b show two alternative options for individually adjusting the feed and the separation. But it is also possible to combine these alternatives.
  • the fixed relative arrangement of the stops 14 and counter-stops 15 always results in the same relative position between the outside of the feed element V designated by 25 and the outside of the support element A designated by 26.
  • the relative height difference between the outside 25 of the feed element V and the outside 26 of the support element A can be changed universally in order to be able to change the separation arbitrarily. This is a Principle that is expedient both in the case of a storage body K according to FIG.
  • variable diameter for example to set a different separation for a different thread quality or to keep the separation constant even with increasing diameter
  • a storage body K with an unchangeable diameter Fig. 21 to adapt the separation to a different thread quality or to different operating conditions.
  • the stop 14 By statically changing the radial position of the stop 14 in the direction of a double arrow 19 by means of an adjusting device J in relation to the outside 25 according to FIG. 5a, the outside 25 then projects less or further beyond the outside 26 during operation.
  • the stop 14 is radially displaceable in a recess 17 of the feed element V by means of a screw spindle 18.
  • an element 21 which can be raised and lowered in a recess 20 of the support element A in the direction of a double arrow 19 can be provided, which carries the two counter-stops 15 and is adjusted by means of a screw spindle 22.
  • FIG. 7 the vertical axis corresponds to the eccentricity e or the target diameter D of the support elements A and the axial path s of the feed elements V in the positive and negative directions.
  • the horizontal axis shows the rotation of the Drive shaft T over a 360 o revolution.
  • the horizontal solid line 28 corresponds to the nominal diameter D of the outer sides 26 of the support elements A in FIG. 4.
  • the rising and falling line 30 corresponds to the radial movement of the feed element V taking place between 0 o and 360 o during one revolution of the drive shaft D due to the Eccentricity e.
  • the top 25 is -e below the top 26.
  • the outer sides 25, 26 are at the same radial height, namely 0.
  • the outer side 25 is + e above the outer side 26 before it moves downwards, at 270 o at D and at 360 o finally by -e below the outside 26.
  • the feed element V becomes 0 o according to the solid line 31 (indicated by downward-pointing arrows) counter to the feed direction, ie moved to the left in Fig. 1 until it axially reverses at 90 o and begins a movement (arrows up) in the feed direction (to the right in Fig. 1) continues until 270 o and then reverses again.
  • the top 25 lies between 90 o and 270 o (area O) above the top 26, the thread turns W are carried along and separated over a maximum area.
  • a separate adjustment mechanism J is provided for each feed element V or each support element A.
  • a common adjustment mechanism J for all feed elements or all support elements in order to be able to make the adjustment centrally.
  • the adjustment mechanism J could then as in Fig. 1, e.g. work with a flat washer.
  • the common adjustment device of the support elements can be used in a particularly advantageous manner to change the separation and the feed, e.g. the collar Q according to Fig. 1 with the drive C, e.g. a stepper motor.
  • the radial distance according to FIG. 6a between the counter-stops 15 is chosen to be an oversize Y larger than twice the eccentricity e plus the radial thickness x of the stop 14.
  • the oversize Y suitably corresponds approximately to the eccentricity e.
  • the support elements A are first adjusted in the direction of an arrow 23 to a diameter D2 which is larger than the nominal diameter D.
  • the advance element V in accordance with the it is assumed that the eccentricity e is in the 90 o -Drehlage the drive shaft T Fig. 6a, is entrained on the stop 14. Then the drive shaft T is turned at least once (FIG. 6b), the feed element V being raised by the eccentricity e from the lower counter-stop 15. Because of the oversize Y, there is still no separation with this setting, because the upper side 25 does not protrude over the upper side 26 at any time. 6c, the support element A OP is adjusted in the direction of an arrow 24 downward by the oversize Y until the outside 26 lies on the diameter D. Then there is a maximum feed with maximum thread separation, because the forward movement (curve 31 between 90 o and 270 o ) is effective over the area O of curve 30.
  • the support element A is adjusted radially outwards in the direction of an arrow 27, for example by means of the set collar Q in FIG. 1, until the outside 26 lies on the diameter D1.
  • the movements of the curves 30, 31 are only superimposed over the area P.
  • This setting can be made for all feed elements together and also during operation, for example via the rotary drive E. If the diameter D is to be maintained with regard to a desired weft thread length, one must be used To reduce the separation from FIG. 6c, the feed element V is again set slightly downward with the upper counter-stop 15 before the support element A is again set to the diameter D.
  • each feed element V is divided into an upper part 32 and a lower part 33, the upper part 32 being axially displaceably guided on the lower part 33.
  • a spring element 39 secures the feed elements V on the storage body K.
  • Each part 32, 33 is coupled via a radially adjustable, telescopic and kinkable driver connection 34 with its own hub N so that axial movement components of the hubs N are transmitted.
  • Each hub N is rotatably supported on a cylindrical surface Z, which is inclined but not eccentric with respect to the drive shaft axis. Between the inclinations of the Both hubs N are offset in the direction of rotation of the drive shaft T.
  • the driver connection 34 consists of a tube 35 or 36 formed on the respective part 32 or 33, into which a spherical driver body 38 of a spoke 37 engages.
  • the lower part 33 is mounted with ramps 41 on ramps 40 of the stationary support element A rising in the axial direction.
  • an actuating shaft 42 is displaceably accommodated, which carries an adjusting pin 43 which engages in an oblique adjusting link 44 on the inside of a sleeve 44a defining the cylinder surface Z.
  • an external actuator 46 By means of an external actuator 46, the actuating shaft 42 can be driven for a reciprocating movement in the direction of a double arrow 45.
  • the displacement between the two cylinder surfaces Z can be changed arbitrarily (separation adjustment) and even reversed, so that the device F can be operated advantageously in both directions of rotation.
  • two hubs N (not shown) and the driver connection 34 are provided, as in FIG. 8.
  • two eccentric drives 47 mounted in the support element A are provided between the lower part 33 and the upper part 32.
  • the eccentric drives 47 are forcibly coupled to one another via double coupling rods, namely the upper part 32 and the lower part 33, in the manner of a locomotive connection, so that a dead center-free cyclical movement of the upper part 32 occurs, the upper side 25 of which is moved forwards and downwards against the direction of advance when raised.
  • the separation can be changed by adjusting the offset between the inclined positions of the two hubs as in FIG. 8.
  • two hubs N are also provided, as in FIG. 8, in order to move the lower part 33 and the upper part 32 axially.
  • the lower part 33 is integrated with its tube 35 into a control lever 49, which is articulated at 53 on angle levers 50 which are pivotably mounted in the support element A about axes 51.
  • the other arms of the angle lever 50 engage with rotary slide guides 52 in axial shafts of the upper part 32, so that only lifting and lowering movements are transmitted to the upper part 32, while the tube 36 generates axial movements.
  • FIG. 11 A similar embodiment is shown in FIG. 11.
  • the lower part 33 is incorporated with its tube 35 into the lever 49, which is articulated at both ends at 53 on the angle mist 50.
  • the angle lever 50 are pivotally mounted in the support element A about axes 51 and with their other arms 54 integrally with the Upper part 32 connected.
  • the arms 54 are flexible.
  • two hubs N are used to axially adjust the upper part 32 and the lower part 33.
  • the lower part 33 is axially movably guided on supports 55 in the support element A and has axially rising ramps 40 on which counter ramps 41 of the upper part 32 rest.
  • needle rollers 57 can be inserted.
  • the embodiment in FIG. 13 has towing couplings S in the form of oversize holes as counter-stops 15 and transverse pins as stops 14.
  • the feed element V is in one piece and has inwardly projecting, fork-like extensions 60, to which magnet arrangements 61 are attached. Between the magnet arrangements 61, an annular disk 58, which contains magnets 59, engages with the hub H on the drive shaft and concentric with the axis H thereof. The magnets 59 are offset from one another and hold different polarities.
  • the rotary movement of the annular disk 58 produces alternating axial and radial magnetic forces which are used for the feed movement of the feed element within the scope of the stroke limitation of the tow clutches in the support element.
  • FIG. 14 Another drive principle for the feed element adjustable in the radial direction with the support element A can be seen from FIG. 14.
  • the feed element V is attached to a transverse axis 62 of a hub N with arms 64 which are flexible in the axial direction, namely in a radially adjustable link bracket 63.
  • the hub N is rotatably mounted on a cylindrical surface Z, which belongs to a sleeve 65, and is eccentric to the drive shaft T. Radial movement components are transmitted from the hub N to the feed element V.
  • Another hub N is rotatably mounted on a sleeve 66 which defines a cylinder surface Z inclined to the drive shaft T.
  • the axial driver 67 ' acts on the feed element V from the inclined hub only in one axial direction, while a spring 73 accommodated in the support element A acts in the opposite direction.
  • the feed element V is movably mounted in the support element, e.g. via driver 71 in corresponding grooves 72 and is driven in the radial direction by the eccentric hub N.
  • the connection C which is adjustable in the radial direction, is a link guide 70.
  • the arms 64 'of the feed element V can be axially displaced within the connection C, which is adjustable radially.
  • the radially adjustable connection C is fixed during operation and can only be adjusted to change the diameter of the storage body.
  • the feed element V is axially spaced and flexible arms 64 connected to an inner part 74 which is radially adjustably mounted on an adjusting element 76 of the hub N in that pins 75 engage in oblique grooves 77.
  • the hub N has an extension 78 which is connected to an actuating part 79 in an axial movement-transmitting connection, the actuating part 79 being axially adjustable by means of an adjusting nut 80.
  • axial movement components are applied by a driver 67 which sits on a hub which is inclined with respect to the drive shaft.
  • the embodiment according to FIG. 17 has two spaced hubs N which are rotatably mounted on eccentric cylinder surfaces, between which a further hub (not shown) is rotatably mounted on an inclined cylinder surface of the drive shaft T.
  • the feed element V has two tubes 83 on the underside, into which plungers 82 attached to the hubs N engage, each of which, as in the embodiment of FIGS. 2 and 3, has a clamping ring 7 (slip clutch R).
  • a plunger 37 of the central hub engages in a central tube 81 as an axial drive member.
  • the tappets 82 are mounted on the hubs N via joints 84, preferably ball joints.
  • the feed element V is movably guided in brackets 85 in the support element A (towing coupling S).
  • the embodiment according to FIG. 18 uses pressure medium pistons 86 which engage in the tubes 83 designed as cylinder tubes and are attached to the tappets 82.
  • the tubes 83 delimit with the pistons 86 pressure medium chambers 87, which are filled with a pressure medium under a certain positive or negative pressure.
  • a displacement of the pistons 86 is prevented due to the pressure filling of the pressure chambers 87, so that the radial movement components are transmitted.
  • it is possible to move the pistons 86 in the tubes 83 for example by throttle valves 88 permitting a slow change in the filling of the pressure medium chambers 87.
  • the axial movement components are generated via the central tube 81 and an inclined cylindrical surface.
  • the radial movement components are derived from purely eccentric hubs.
  • an electromagnetic drive is provided for the feed movement of the feed element V.
  • the feed element V is designed as a radially movable plate 89 in the support element, act on the magnets 90 and 91, which are cyclically controlled via supply lines 92, so that one magnet produces radial movements and the other magnet produces axial movements on the feed element V.
  • the drag couplings S between the support element A and the feed element V limit the stroke and guide the feed element V.
  • the magnetic forces are generated between the support element A and the feed element V, so that the feed element V is independent of the drive shaft. Regardless of the respective diameter of the support elements, the feed control remains the same.
  • the separation can be achieved by modulating the excitation of the two magnets 90, 91 and change the feed or switch to the opposite direction of rotation of the device.
  • the feed element V according to FIG. 20 is intended for a thread storage and delivery device F according to FIGS. 1 and 8 with a variable storage body diameter.
  • the outer side 25 of the feed element V is provided on a longitudinal bar 93, which is only supported in a radially movable manner via guide and limiting parts 94 in the feed element V and is loaded radially outwards by a spring element 95.
  • the spring element 95 normally holds the strip 93 in a radially outer limit position under the contact pressure of the windings W.
  • the spring element 95 then yields and the bar 93 only returns to the radially outer limit position when new windings are applied with less contact pressure. In this way, a possible thread break is built up.
  • FIG. 21 illustrates a storage body K of a thread storage and delivery device F 'with an unchangeable diameter DF with separation.
  • the feed elements V are jointly attached to the hub N.
  • the hub N is rotatably supported on a cylindrical surface Z which is inclined and eccentric with respect to the drive shaft axis H.
  • the hub N has a radially outwardly projecting cylindrical extension, forming a guide part 96, with a bore 99, into which an extension of the feed element V, which is round in cross section, is immersed as a counter-guide part 97.
  • the groove 98 provided provides access to an adjusting mechanism J.
  • This consists of an adjusting screw 105 which is screwed with its shaft 106 into a threaded bore 101 of the hub N.
  • An outer screwed-in stop 104 and an underlying stop 103 fix the adjusting screw 105 in the feed element V radially.
  • the shaft 106 passes through a bore 102 of the feed element.
  • a wedge 100 may prevent an undesired rotational movement of the feed element V about the screw axis and serves (not shown) as an upper and lower stroke limitation for the possible adjustment path between the guide parts 97 and 96.
  • the radially adjustable connection C or slip clutch R created in this way is adjusted in order to statically change the relative height difference between the outside 25 and the outside 26.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Transmission Devices (AREA)
  • Knitting Machines (AREA)

Abstract

Un dispositif d'emmagasinage et d'amenée de fil comprenant un système de séparation du fil, en particulier pour un fil de trame, comporte un corps d'emmagasinage pour une réserve de fil constituée de fil enroulé. Le corps d'emmagasinage est monté rotatif sur un arbre d'entraînement mais bloqué pour ne pas être entraîné par l'arbre. Des éléments de support approximativement axiaux et en forme de barres sont répartis sur la périphérie du corps d'emmagasinage, et les côtés extérieurs desdits éléments de support sont inscrits dans un cercle concentrique par rapport à l'arbre d'entraînement. Des éléments d'amenée en forme de barres sont intercalés entre les éléments de support et leurs côtés extérieurs sont inscrits dans un cercle excentrique par rapport à l'arbre d'entraînement. Les éléments d'amenée peuvent être entraînés, par rapport aux éléments de support fixes, dans un mouvement d'avance ayant des composantes radiales et axiales, et, le cas échéant, les écarts radiaux entre les éléments de support et l'axe de l'arbre d'entraînement, écarts qui sont égaux, peuvent être modifiés conjointement par réglage des éléments de support. Lorsque les éléments de support sont réglés, les écarts radiaux entre les éléments d'amenée et le centre (axe 8) du cercle excentrique, écarts qui sont égaux, peuvent être modifiés conjointement par réglage des éléments de support et/ou les différences radiales de hauteur, différences qui sont égales, entre les côtés extérieurs des éléments de support et les côtés extérieurs des éléments d'amenée, aux mêmes points de la périphérie du corps d'emmagasinage, peuvent être modifiées.

Claims (37)

  1. Dispositif d'emmagasinage et d'amenée de fil (F), avec séparation de fils, notamment pour des fils de trame (U), comportant un corps d'emmagasinage (K) d'une réserve de fil se composant de spires (W), monté de façon tournante sur un arbre d'entraînement (T) et soumis à un blocage contre une rotation d'accompagnement, des éléments de soutien (A) se présentant à peu prés sous la forme de barreaux axiaux, répartis sur le pourtour du corps d'emmagasinage (K) et dont les côtés extérieurs (26) peuvent être inscrits dans un cercle concentrique à l'axe (H) de l'arbre d'entraînement, des éléments d'avancement (V) et se présentant à peu près sous la forme de barreaux axiaux, associés respectivement aux éléments de soutien, répartis sur le pourtour du corps d'emmagasinage et dont les côtés extérieurs (25) peuvent être inscrits dans un cercle excentrique à l'axe (H) de l'arbre d'entraînement, et qui peuvent être entraînés par rapport aux éléments stationnaires de soutien (A) sous la forme d'un mouvement d'avancement constitué de composantes radiales et de composantes axiales, caractérisé en ce que, pour modifier le diamètre du cercle excentrique, dans lequel les côtés extérieurs (25) des éléments d'avancement (V) peuvent être inscrits, il est prévu un dispositif de réglage radial pour les éléments d'avancement (V).
  2. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 1, caractérisé en ce que pour les éléments de soutien (A), il est prévu un mécanisme commun de réglage de diamètre et en ce que les éléments d'avancement (V) sont réglables ensemble au moyen des éléments de soutien (A) radialement par rapport au centre du cercle excentrique.
  3. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 1 ou 2, caractérisé en ce que chaque élément d'avancement (V) est monté de façon mobile dans l'élément de soutien (A) et en ce qu'un entraînement de commande d'avancement, de préférence magnétique et mécaniquement indépendant de l'arbre d'entraînement (T) est monté directement sur l'élément d'avancement (V).
  4. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 1 ou 2, caractérisé en ce qu'il est prévu entre l'élément d'avancement (V) et l'élément de soutien (A) un entraînement mécanique de commande d'avancement, qui est accouplé, exclusivement dans une direction axiale, avec les éléments de commande de mouvement axial de l'arbre d'entraînement (T).
  5. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 1 ou 2 caractérisé en ce qu'il est prévu sur l'arbre d'entraînement (T) un entraînement mécanique de commande d'avancement et en ce qu'il est prévu entre l'entraînement de commande d'avancement et l'élément d'avancement (V) une liaison (C) réglable radialement et comportant, dans une position d'enclenchement de marche, une résistance au déplacement radial qui est plus grande que la pression d'appui des spires (W).
  6. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 5, caractérisé en ce que la liaison (C) réglable radialement est agencée sous forme d'un accouplement pouvant être libéré et bloqué.
  7. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 5, caractérisé en ce que la liaison (C) réglable radialement est agencée comme un accouplement à glissement (R).
  8. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1 à 7, caractérisé en ce qu'il est prévu un mécanisme d'ajustement (J) pour le réglage et la modification de la différence de hauteur radiale entre le côté extérieur (26) de l'élément de soutien (A) et le côté extérieur (25) de l'élément d'avancement (V), en étant disposé de préférence entre chaque élément d'avancement (V) et au moins un élément de soutien (A) adjacent, ou bien en étant prévu de façon commune pour tous les éléments d'avancement (V).
  9. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 3 à 7 caractérisé en ce que la disposition mobile de l'élément d'avancement (V) dans l'élément de soutien (A) est agencé sous la forme d'un accouplement de retenue (S) opérant radialement par conjugaison de formes.
  10. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 9, caractérisé en ce que les éléments d'avancement (V) sont disposés ensemble sur un moyeu (N), qui est monté de façon tournante sur une surface cylindrique (Z) de l'arbre d'entraînement (T), cette surface étant excentrique et disposée en oblique par rapport à l'axe (H) de l'arbre d'entraînement, et en ce que l'accouplement de retenue (S) est agencé de façon à avoir un jeu radial correspondant au moins au double de l'excentricité (e) de la surface cylindrique (Z).
  11. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1 à 9, caractérisé en ce que les éléments d'avancement (V) sont disposés ensemble sur un moyeu (N), qui est monté de façon tournante sur une surface cylindrique (Z) de l'arbre d'entraînement (T), cette surface cylindrique étant excentrique et disposée en oblique par rapport à l'axe (H) de l'arbre d'entraînement, en ce que la liaison (C) réglable radialement se compose d'éléments de guidage (96, 97), mobiles et s'accrochant les uns dans les autres, de l'élément d'avancement (V) et du moyeu (N) et en ce que le mécanisme d'ajustement (J) est disposé entre les éléments de guidage ou bien entre l'élément d'avancement et un élément de soutien adjacent ou bien entre l'élément d'avancement et le moyeu (N).
  12. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 10 et 11, caractérisé en ce que l'élément d'avancement (V) est monté sur le moyeu (N) de façon à pouvoir tourner autour d'un axe (9) à peu près parallèle à l'axe de cylindre (8) et autour d'un axe (11) à peu près radial par rapport à l'axe de cylindre (8).
  13. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 7, caractérisé en ce que l'accouplement à glissement (R) est une unité à cylindre et piston à mouvement télescopique et en ce qu'il est prévu soit sur la paroi de cylindre, soit sur la paroi de piston, au moins une bague de serrage (7) pouvant tourner autour de l'axe de cylindre (8) mais ne pouvant par contre pas se déplacer en translation dans la direction de l'axe de cylindre (8) et qui s'appuie avec une précontrainte élastique contre la paroi de piston ou bien contre la paroi de cylindre.
  14. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 9, caractérisé en ce que l'accouplement de retenue (S) comporte des butées (14) et des contre-butées (15), se présentant par exemple sous la forme de têtons de butée s'engageant dans un trou de dimension supérieure et venant s'accrocher mutuellement les unes derrière les autres au moins dans une direction radiale.
  15. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 14, caractérisé en ce qu'il est prévu sur l'élément d'avancement (V) au moins une butée (14) qui s'engage entre deux contre-butées (15) de l'élément de soutien (A), espacées dans une direction radiale.
  16. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 15, caractérisé en ce qu'il est prévu respectivement deux butées (14) sur deux côtés longitudinaux de l'élément d'avancement (V).
  17. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 8, caractérisé en ce que la butée (14) ou les contre-butées (15) sont déplaçables radialement au moyen du mécanisme d' ajustement (J), intégré de préférence dans l'élément d'avancement (V) ou/et dans l'élément de soutien (A).
  18. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1 à 15, caractérisé en ce que l'espacement radial entre les contre-butées (15) correspond au double de l'excentricité (e) de la surface théorique (Z) en plus de l'épaisseur radiale (X) de la butée et en plus d'une surcote radiale (Y) qui est approximativement égale à l'excentricité (e).
  19. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1 et 2, caractérisé en ce que le mécanisme de réglage de diamètre des éléments de soutien (A) est disposé dans le corps d'emmagasinage (K) et en ce qu'il est prévu sur ce corps d'emmagasinage (K) un entraînement (E), de préférence à moteur électrique et télécommandé, pour le mécanisme de réglage.
  20. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 19, caractérisé en ce que les éléments de soutien (A) sont déplaçables dans des alvéoles radiales de guidage du corps d'emmagasinage (K) et s'engagent par des éléments d'accrochage (1) dans un filetage (2) d'un disque annulaire de réglage (Q), pouvant tourner sur le corps d'emmagasinage (K) sur son côté frontal libre, et en ce que l'entraînement (E) est un entraînement en rotation pour le disque annulaire de réglage (Q).
  21. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 4 et 5, caractérisé en ce que l'élément d'avancement (V) se compose d'une partie inférieure (33) et d'une partie supérieure (32), pouvant se déplacer au moins longitudinalement l'une par rapport à l'autre, en ce que la partie supérieure et la partie inférieure sont chacune reliées, par l'intermédiaire d'une liaison télescopique réglable radialement (35, 36, 37), avec respectivement un moyeu (N), monté de façon tournante sur l'arbre d'entraînement (T) par l'intermédiaire d'une surface cylindrique (Z) orientée en oblique par rapport à l'axe (H) de l'arbre d'entraînement et en ce qu'il est prévu entre les positions en oblique des surfaces cylindriques (Z) un déphasage - dans le sens de rotation de l'arbre d'entraînement (T) -.
  22. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 21, caractérisé en ce que la partie supérieure (32) est appuyée sur la partie inférieure (33) avec possibilité de translation axiale et en ce que la partie inférieure (33) est guidée en translation sur au moins une rampe (40), montant dans une direction axiale, de l'élément de soutien (H).
  23. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 21, caractérisé en ce que la partie supérieure (32) est accouplée à la partie inférieure (33) par l'intermédiaire de deux excentriques (45) montés dans l'élément de soutien (A) et comportant une double liaison de locomotion.
  24. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 21, caractérisé en ce que la partie supérieure (32) est accouplée à la partie inférieure (33) par deux leviers coudés (50) montés dans l'élément de soutien (A), la partie inférieure (33) est articulée sur un des bras des leviers coudés tandis que par contre la partie supérieure (32) est guidée en translation longitudinale sur les autres bras respectifs des leviers coudés (50).
  25. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 21, caractérisé en ce que la partie supérieure (32) est accouplée à la partie inférieure (33) par deux leviers coudés (50), montés dans l'élément de soutien (A), la partie inférieure (33) est articulée sur un des bras des leviers coudés (50) tandis que par contre la partie supérieure (32) est installée en position fixe sur les autres bras respectifs (54) des leviers coudés (50) et en ce que les autres bras respectifs (54) des leviers coudés sont axialement élastiques en flexion.
  26. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 21, caractérisé en ce que la partie inférieure (33) est guidée en translation longitudinale sur des appuis (65) prévus dans l'élément de soutien (A) et en ce qu'il est prévu entre la partie supérieure (32) et la partie inférieure (33) des rampes (40, 41) montant dans une direction axiale, en étant de préférence pourvues de roulements à aiguilles (57) interposés dans la zone des rampes entre la partie supérieure et la partie inférieure.
  27. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 21, caractérisé en ce que les surfaces cylindriques (Z) peuvent tourner l'une par rapport à l'autre autour de l'axe (H) de l'arbre d'entraînement et en ce qu'il est prévu pour au moins une surface cylindrique (Z) un dispositif d'entraînement en rotation pouvant être actionné de l'extérieur.
  28. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 27, caractérisé en ce que l'arbre d'entraînement (T) est un arbre creux pourvu dans sa paroi d'une fente pour un tourillon de manoeuvre (43) d'un arbre de manoeuvre (42), qui est engagé dans l'arbre creux avec possibilité de rotation et de translation, en ce que le tourillon de manoeuvre (43) s'engage dans une coulisse inclinée de manoeuvre (44) d'un manchon (44a), monté à rotation sur l'arbre d'entraînement (T) et portant une surface cylindrique Z, et en ce que l'arbre de manoeuvre (42) est accouplé à un entraînement (46), avantageusement à moteur électrique et télécommandé.
  29. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1 à 3, caractérisé en ce qu'il est prévu sur l'arbre d'entraînement (T) un disque annulaire (58), concentrique, l'accompagnant en rotation et qui comporte des électro-aimants (59) décalés alternativement dans une direction circonférentielle, en ce qu'il est prévu, sur l'élément d'avancement (V), maintenu avec possibilité de déplacement dans l'élément de soutien (A) au moyen de l' accouplement de retenue (S), des appendices (60) entourant sans contact à la façon d'une fourche le disque annulaire (58) et en ce que les appendices (60) comportent un ensemble d'électro-aimants (61), comportant des électro-aimants de polarités opposées, dirigés vers les électro-aimants du disque annulaire (58).
  30. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1 et 5, caractérisé en ce que les éléments d'avancement (V) sont disposés sur un moyeu commun (N) au moyen de liaisons (C) déplaçables radialement, ce moyeu est monté en rotation sur une surface cylindrique (Z) excentrique par rapport à l'axe (H) de l'arbre d'entraînement, en ce qu'un autre moyeu (N), portant une partie axiale d'entraînement (67), est monté de façon tournante sur une surface cylindrique (Z) disposée en oblique par rapport à l'axe (H) de l'arbre d'entraînement, en ce que la partie axiale d'entraînement (67) est accouplée avec les éléments d'avancement (V), de préférence de façon à transmettre un mouvement axial au moins dans une direction, et en ce qu'il est prévu entre chaque élément d'avancement (V) et le moyeu (N) au moins un bras (64) élastique en flexion ou pouvant être décalé dans le sens axial.
  31. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 30, caractérisé en ce que la liaison (C) déplaçable radialement est constitué par un guide à coussinet ou à coulisse (62, 63 ; 70) qui est disposé entre le moyeu (N), appuyé sans possibilité de translation axiale sur l'arbre d' entraînement (T), et le bras (64) de l'élément d'avancement (V).
  32. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 31, caractérisé en ce que l'élément d'agencement (4) est disposé, avec le bras (64) pouvant s'infléchir élastiquement dans une direction axiale, sur une partie intérieure (74) qui est montée avec possibilité de translation radiale sur un élément d'actionnement (76) du moyeu (N) au moyen de guides coulissants inclinés (71), en ce que le moyeu (N) est monté avec possibilité de translation axiale sur l'arbre d'entraînement (T) et en ce qu'il est prévu un mécanisme de manoeuvre (80, 79), pouvant être actionné de l'extérieur, pour assurer une translation axiale du moyeu (N).
  33. Dispositif d'emmagasinage et d'amenée de fil selon les revendications 1, 2 et 5, caractérisé en ce que chaque élément d'avancement (V) est disposé au moyen de deux accouplements glissants (R) espacés axialement sur un moyeu (N), de préférence en deux parties, qui est monté de façon tournante sur une surface cylindrique (Z) de l'arbre d'entraînement (T) qui est excentrique par rapport à l'axe (H) de cet arbre d'entraînement, en ce qu'il est prévu un autre moyeu (N) monté de façon tournante sur une surface cylindrique (Z) de l'arbre d'entraînement (T) qui est disposée en oblique par rapport à l'axe (H) de cet arbre d'entraînement, ledit moyeu (N) étant accouplé avec l'élément d'avancement (V) dans une direction axiale par l'intermédiaire d'une liaison d'entraînement (36, 37, 81), déplaçable radialement de façon télescopique et pouvant subir un flambage, et en ce qu'il est prévu entre chaque accouplement glissant (R) et le moyeu (N) une articulation de pivotement (84), de préférence une articulation à rotule.
  34. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 33, caractérisé en ce que chaque accouplement glissant (R) se compose d'un tube (83) monté sur l'élément d'avancement (V) et d'un poussoir (82) disposé sur le moyeu (N) et pénétrant dans le tube (83), ainsi que d'au moins une bague de serrage (7) disposée sur le poussoir (82) et ayant une résistance radiale au glissement de valeur prédéterminée.
  35. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 33, caractérisé en ce que chaque accouplement glissant (R) se compose d'un cylindre (83) monté sur l'élément d'avancement (V) et d'un piston (86) pénétrant dans le cylindre (83) et maintenu sur le moyeu (N), en étant mobile de façon étanche dans le tube cylindrique (83) et en délimitant une chambre à fluide sous pression (87), et en ce qu'il est prévu une soupape (88) pour commander la pression dans la chambre à fluide sous pression (87), de préférence une soupape d'étranglement disposée dans le piston (86).
  36. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 3, caractérisé en ce que l'élément d'avancement (V) est agencé en forme de plaque (89) et est monté de façon mobile dans l'élément de soutien (A), et en ce que l'entraînement de commande d'avancement comporte des électro-aimants respectivement axial et radial (90, 91) pouvant être excités de façon synchronisée.
  37. Dispositif d'emmagasinage et d'amenée de fil selon la revendication 1, caractérisé en ce que le côté extérieur (25) de l'élément d'avancement (V) est disposé sur un profilé en forme de barre (93), qui est guidé sur l'élément d'avancement (V) avec possibilité de mouvement radial limité et en ce qu'au moins un élément formant ressort (95) est interposé entre la barre (93) et l'élément d'avancement (V), de façon à maintenir la barre dans la position limite radialement extérieure alors que, lorsque la pression d'appui des spires (W) est augmentée en fonction du réglage, il est déformable temporairement jusqu'à la position limite radialement intérieure de la barre.
EP19910912562 1990-07-11 1991-07-11 Dispositif d'emmagasinage et d'amenee de fil Expired - Lifetime EP0538316B1 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
SE9002409A SE9002409D0 (sv) 1990-07-11 1990-07-11 Fournissoer foer textilmaskin och foerfarande foer aendring av omkretsmaatt paa fournissoerens garnlager uppbaerande enhet
SE9002409 1990-07-11
SE9003780A SE9003780D0 (sv) 1990-11-26 1990-11-26 Metod och anordning vid maetfournissoer foer textilmaskiner, speciellt vaevmaskiner av air- eller water-jet-typ
SE9003796A SE9003796D0 (sv) 1990-11-27 1990-11-27 Instaellningsanordning vid fournissoer
SE9003796 1990-11-27
SE9101226A SE9101226D0 (sv) 1991-04-21 1991-04-21 Fournissoer med garnseparation, foeretraedesvid en maetfournissoer foer en luft- eller vatten-jet-vaevmaskin
SE9101234A SE9101234D0 (sv) 1991-04-23 1991-04-23 Fournissoer med garnseparation, foeretraedesvis en maetfourmissoer foer en luft- eller vatten-jet-vaevmaskin
DE4119370 1991-06-12
DE4119370A DE4119370A1 (de) 1990-07-11 1991-06-12 Fadenspeicher- und -liefervorrichtung
PCT/EP1991/001302 WO1992001101A1 (fr) 1990-07-11 1991-07-11 Dispositif d'emmagasinage et d'amenee de fil

Publications (2)

Publication Number Publication Date
EP0538316A1 EP0538316A1 (fr) 1993-04-28
EP0538316B1 true EP0538316B1 (fr) 1995-01-04

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JP (1) JP3160646B2 (fr)
WO (1) WO1992001101A1 (fr)

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CN102530333A (zh) * 2011-12-14 2012-07-04 福州宝井钢材有限公司 一种用于捆带的抽取装置
WO2016119947A1 (fr) 2015-01-26 2016-08-04 Picanol Mécanisme de séparation de fil pour un dispositif d'alimenteur de trame

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DE4240709A1 (de) * 1992-12-03 1994-06-09 Iro Ab Schußfaden-Meßfournisseur
IT231450Y1 (it) * 1993-07-19 1999-08-03 Lgl Electronics Spa Alimentatore di trama con piastra portamagneti dotata di scanalatura anulare fungente da elemento di centraggio e ritegno del tamburo e
JP3366243B2 (ja) * 1998-01-16 2003-01-14 津田駒工業株式会社 緯糸測長貯留装置におけるドラム径の設定装置

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CH579499A5 (en) * 1974-06-28 1976-09-15 Sulzer Ag Reserve holder for yarn, wire, etc., esp. weft - undulating cage progresses windings towards overend take-off point
IT1176259B (it) * 1984-06-04 1987-08-18 Roy Electrotex Spa Alimentatore di trama per telai di tessitura
ES2029086T3 (es) * 1988-03-02 1992-07-16 L.G.L. Electronics S.P.A. Dispositivo de alimentacion de trama, particularmente para telares.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102530333A (zh) * 2011-12-14 2012-07-04 福州宝井钢材有限公司 一种用于捆带的抽取装置
WO2016119947A1 (fr) 2015-01-26 2016-08-04 Picanol Mécanisme de séparation de fil pour un dispositif d'alimenteur de trame

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WO1992001101A1 (fr) 1992-01-23
EP0538316A1 (fr) 1993-04-28
JPH05508446A (ja) 1993-11-25
JP3160646B2 (ja) 2001-04-25

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