EP0790208A1 - Dispositif pour dévier un fil - Google Patents

Dispositif pour dévier un fil Download PDF

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Publication number
EP0790208A1
EP0790208A1 EP97102302A EP97102302A EP0790208A1 EP 0790208 A1 EP0790208 A1 EP 0790208A1 EP 97102302 A EP97102302 A EP 97102302A EP 97102302 A EP97102302 A EP 97102302A EP 0790208 A1 EP0790208 A1 EP 0790208A1
Authority
EP
European Patent Office
Prior art keywords
thread
spring
buckling
pressure point
deflection
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.)
Granted
Application number
EP97102302A
Other languages
German (de)
English (en)
Other versions
EP0790208B1 (fr
Inventor
Patrik Jonas Magnussson
Ulf Raudberget
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.)
Iro AB
Original Assignee
Iro AB
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Filing date
Publication date
Application filed by Iro AB filed Critical Iro AB
Publication of EP0790208A1 publication Critical patent/EP0790208A1/fr
Application granted granted Critical
Publication of EP0790208B1 publication Critical patent/EP0790208B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H59/00—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators
    • B65H59/10—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators by devices acting on running material and not associated with supply or take-up devices
    • B65H59/36—Floating elements compensating for irregularities in supply or take-up of material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H59/00—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators
    • B65H59/40—Applications of tension indicators
    • 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 device of the type specified in the preamble of claim 1.
  • the deflection element is a hook-shaped spring steel lamella, the hook-shaped end region of which deflects the thread from a straight thread path.
  • compressed air is applied to the lamella.
  • the braking effect for the thread can be changed by regulating the compressed air supply (externally controlled thread brake).
  • the thread tension is an important parameter for the proper functioning of the thread processing devices, e.g. Thread delivery devices, entry devices or weaving machines.
  • the thread tension is often proportional to the speed or acceleration of the thread. Crassy thread tension variations are harmful (thread breakage).
  • Deflection brakes are often used for a basic thread tension, in which the braking effect depends on the friction and to a greater extent on the deflection angle. The braking effect can be reduced with controlled thread deflection brakes. This requires a high level of structural and control engineering effort. Deflection brakes without control with a substantially constant deflection force give way with increasing thread tension, so that the deflection angle becomes smaller; however, the braking force then remains undesirably high.
  • Deflection devices are used to determine the thread tension.
  • the dimension with which the deflecting element is shifted from the thread corresponds to the thread tension.
  • a high level of control engineering effort is required to tap the voltage. It remains as a disadvantage that the deflecting element loads the thread with the same restoring force at high thread tension as at low tension, and therefore makes an unsuitable contribution to increasing the tension at high thread tension.
  • the invention has for its object to provide a device of the type mentioned that is structurally simple, reliable and universally applicable in thread processing technology to slow down a thread or determine the thread tension, the device should have an intelligent response without external control, with which the thread is acted upon more strongly when the thread tension is low and the deflection is strong than when the thread tension is high and the deflection is low.
  • the device should be usable as a thread brake and / or as a thread tension sensor.
  • the buckling spring meets the requirements for strong resistance with strong thread deflection, weak resistance for weak thread deflection, an exactly definable switchover point, and automatic resetting from any deflected position.
  • the device according to claim 2 is capable of automatically deflecting the thread vigorously and far without external control to take a strong load on the thread as long as this is needed, and after exceeding the kink pressure point on the thread only a much weaker load or to deflect the thread much less.
  • This can be used profitably in a thread deflection brake (according to claim 16) because the deflection element strongly supports the thread until a high thread tension is reached, exceeds the pressure point when a critical thread tension value is reached, and then suddenly produces only a negligible restoring force when the deflection is reduced.
  • the braking effect is reduced to such an extent that it only makes a negligible contribution to the high tension then present in the thread.
  • the device therefore has a material and / or shape-related self-compensation effect and automatically adapts to the thread tension.
  • the deflection element suddenly gives way when a thread tension which is regarded as critical and can be predetermined is reached. This sudden kinking can easily be used to derive a meaningful signal for thread tension.
  • the braking influence on the running thread is very small.
  • the device does not require external control for this built-in multi-stage function.
  • the buckling spring either defines the deflection element directly or the buckling spring is only part of the deflection element.
  • the deflection element - except in the area of the buckling spring - is rigid.
  • the spring lamella receives an integrated high kink resistance until it reaches the pressure point and until it kinks, which suddenly collapses from the pressure point to a negligible restoring force, sufficient to reset the deflection element after the thread tension has dropped (strong Hysteresis).
  • the spring lamella behaves like a roll-up metal or plastic measuring tape that is curved transversely to its longitudinal direction. An approximately horizontally extended part of the measuring tape is stretched even without support with an upward-facing, concave curvature side and kinks almost without hold under the influence of external force or gravity as soon as the kink pressure point of the curved profile is overcome.
  • the measuring tape With a force on the convex curvature side, however, the measuring tape can be bent very easily. There are symmetrical deflection conditions. In special cases, it may be advisable to choose the width extension of the buckling spring at an angle to the thread running direction in order to achieve asymmetrical deflection conditions.
  • the response can be varied easily, for example, the resulting kink of the spring can be moved as far away from the thread.
  • the position of a target kink is structurally predetermined.
  • the deflection element kinks according to claim 10 under the action of the thread at a certain point at a precisely predetermined tension-dependent force, which result from the material specification, the width / strength ratio and the free projection length.
  • the concave bulge side should point to the thread.
  • the response behavior can be varied within a wide range.
  • the effective collar length could also be changed by adjusting the point of application of the thread for support or away from the support.
  • the deflection element is supported like a support supported on both sides in two spaced supports. After the kink pressure point is exceeded, the deflection element kinks under the thread.
  • the convex curvature side should point to the thread here, which may lie directly on the buckling spring.
  • the stroke of the deflecting element can advantageously be adjusted up to the kink pressure point by means of a prestressing spring or a stationary stop. If necessary, the buckling spring is preloaded almost to the pressure point so that it suddenly gives way without any significant stroke.
  • the choice of material or a combination of materials results in long service lives, precisely predictable response behavior and high immunity to soiling, for example fluff from the thread.
  • the thread eyelet can be adjustable in the longitudinal direction of the arm to change the effective length of the arm.
  • a response behavior with two stages or two clearly different braking effects is achieved by the design of the deflecting element.
  • the brake works without complex third-party control like an externally controlled thread brake dependent on the thread tension and has a compensating effect at high thread tension because the deflection is largely eliminated and the braking force is negligible, i.e. it actively contributes to avoiding undesirable, large thread tension variations.
  • This is particularly expedient for an infeed brake of a thread supplier for air jet weaving machines. Strong variations in tension in the thread coming from the supply spool are frozen in the thread windings on the storage body of the thread supplier and released again in the shed.
  • the detachable weft thread length is therefore set to the worst case, ie to the strongest thread tension under which a, especially elastic thread springs back while relaxing in the shed. This avoids too short weft threads (short-picks), leads to excessively long weft threads and a significant waste of thread if the tension in the thread turns on the storage body of the thread supplier is too low. Excessive thread tension changes on the inlet side should be avoided for these reasons, namely in multi-color weaving or in a weaving principle with several thread suppliers delivering the same thread, from which one thread supplier has to take over the delivery function of another, disturbed thread supplier and then delivers at double frequency. This increases the thread tension.
  • the thread deflection brake With the new thread deflection brake, a contribution to avoiding such excessive thread tension changes on the inlet side of the thread supplier can then be achieved if the thread deflection brake is used as self-compensating infeed brake acts and suddenly abruptly weakly brakes and weakly deflects due to a strong increase in thread tension caused by external influences (speed, acceleration).
  • stationary thread guide elements stabilize the thread in friction points that are important for the braking effect and an exactly predetermined thread geometry.
  • the distances between the deflection element and the stationary thread guiding elements are expediently adjustable, as is the displacement transversely to the thread running direction.
  • the stop determines the stroke of the deflection element up to the kink pressure point.
  • the stop also reduces pendulum movements of the deflecting element.
  • an end position is predetermined and an oscillation of the displaced deflection element is suppressed.
  • a high basic thread tension is achieved at low thread tension and strong deflection or the thread is stopped.
  • the deflection element clamps the thread against the stop under the force of the buckling spring. If the thread tension increases, the kink pressure point is exceeded (immediately or after an adjustable initial stroke) and the jamming braking effect stops.
  • This deflection brake works, so to speak, with three areas, i.e. an initial area with jamming thread braking, a subsequent area with high restoring force and strong deflection, and an end area with extremely weak restoring force and weak deflection.
  • the three stages are structurally integrated in the deflection brake without external control.
  • the thread tension sensor according to claim 21 uses the buckling pressure point of the buckling spring to report the thread tension. Since the pressure point can be set, the thread tension sensor can be adjusted simply adapt to the thread tension to be determined. The sudden yielding produces a powerful useful signal. In a black / white function (digital 1-0), the tension sensor reports that a certain thread tension value has been reached or exceeded, after which the mechanical load on the thread remains low.
  • the determination of the thread tension is simple in terms of construction and control technology.
  • the mechanical sensor can be an electrical switch actuated by the deflection element.
  • An optoelectronic or optical sensor e.g. a light barrier or a reflection sensor, determines a predetermined position of the deflecting element and / or the thread or monitors their movements.
  • a capacitive sensor responds to changes in the distance of the deflecting element from the sensor, which can be implemented particularly expediently in the case of a deflecting element consisting of metal.
  • a magnetic sensor responds to the change in the magnetic field due to the movement.
  • the piezoelectric sensor either reacts to an impact of the deflecting element or, particularly expediently, to the vibration which occurs when the buckling pressure point of the buckling spring is exceeded and which can be easily sensed, for example, in the support.
  • a device V for deflecting a thread Y according to FIG. 1 can be, for example, a thread deflection brake T or / or a thread tension sensor T '.
  • An elongated deflecting element 1 is freely cantilevered in a support 2 and is designed as an articulated spring with an integrated kink, for example as a spring lamella 3 made of spring steel and / or resilient plastic that is curved transversely to the longitudinal axis. Materials can be used for this that have the spring behavior and resilience as well as the fatigue strength of a metal spring, for example.
  • the curvature 4 follows, for example, a part of a circular arc. In Fig. 1 the curvature over the length of the deflecting element 1 is constant.
  • the width of the spring plate 3 is a multiple of the thickness, and both are constant over the length. The width could vary over the length (see Fig. 5, wedge shape).
  • a thread guide element 5 is attached, for example glued or riveted, the can be designed as a closed or - as shown - open thread eyelet.
  • the thread guide element 5 could be adjustable in the longitudinal direction.
  • the support 2 consists, for example, of components which can be clamped against one another and which make it possible to adjust the spring lamella 3 in the direction of a double arrow 6 in order to change the collar length and / or to vary the curvature 4 in the direction of the arrows 7.
  • the spring lamella 3 whose curvature 4 faces the thread Y with the concave curvature side and whose width axis lies approximately parallel to the thread path, forms the buckling spring K.
  • the deflection element 1 yields under the initial force F of the thread Y proportional to the thread tension from the initial position shown, against an initially high kink resistance in a clockwise direction relative to the support 2, the curvature 4 in the area due to the physical and mechanical behavior of the kink spring the developing kink flattened (Fig. 5 dashed). This deformation causes the increasing kink resistance acting on the thread guide element 5.
  • a kink pressure point DR, Fig.
  • the deflection element 1 Up to the kink pressure point DR, the deflection element has a braking area I with a strong braking effect. From the kink pressure point DR, the deflection element 1 operates in a braking area II with a significantly lower braking effect. If the thread Y runs in the longitudinal direction of the thread, the device V works as a thread deflection brake T with self-compensation at a high thread tension.
  • the device V can also be a thread tension sensor T 'for a running or a standing thread Y, since the break pressure point DR is exceeded suddenly Give a clear statement on the thread tension achieved.
  • the thread tension sensor T ' is provided with at least one sensor 8, 8', 8 '' which generates a signal representing the thread tension from the movement of the deflecting element 1, the thread guide element 5, the thread Y or from the exceeding of the kink pressure point.
  • a piezoelectric sensor 8 is arranged in the tilt support 2 and responds with a voltage signal to the vibration resulting when the kink pressure point DR is exceeded.
  • an optoelectronic, capacitive or magnetic sensor 8 'could be provided, which monitors the movement of the deflecting element 1 or its absence or presence in a defined scanning zone.
  • a mechanical sensor 8 '' 'could be a switch which is actuated by the stop of the deflecting element in the braking area II.
  • An optoelectronic or optical sensor 8 ′′ could monitor the movement of the thread Y or the deflecting element 1.
  • a stationary stop 9 prestresses the deflection element 1 or the buckling spring in the direction of the buckling pressure point DR.
  • the stop 9 is expediently adjustable.
  • a biasing spring 9 'with a limited effective stroke could bias the deflection element 1 in the direction of the kink pressure point.
  • the spring 9 'could be fixed as a leaf spring in the support 2.
  • the thread braking function and thread tension sensing function can be combined in one device V.
  • the deflection element 1 is an elongated buckling spring with an integrated buckling point, which is supported in two spaced supports 2, 2 '.
  • the thread Y engages between the two tilt supports 2, 2 '.
  • the buckling spring is a spring lamella arched transversely to the longitudinal direction 3, the convex side of the bulge facing the thread Y.
  • a thread guiding element 5 is not absolutely necessary, but can be useful for unambiguously determining the point of application and for ensuring predetermined friction conditions. 2, the deflecting element 1 works in the first braking area I.
  • the deflection element 1 could contain a buckling spring only in a short longitudinal section.
  • the deflecting element 1 automatically returns to the starting position after a corresponding decrease in the thread tension, with a noticeable snap function as soon as the curvature which has been flattened up to then deforms in the kink.
  • the buckling resistance up to the pressure point is high and increases, while the bending resistance effective from the pressure point is considerably lower and possibly essentially constant.
  • the device V of FIGS. 2, 2A can be used as a thread deflection brake T or / and as a thread tension sensor T '(with at least one of the sensors of FIG. 1).
  • An adjustable stop 9 or a prestressing spring 9 '(or prestressing springs for both supports 2, 2') could be provided (analogously to FIG. 1).
  • FIG. 3 shows the response behavior of the deflecting element 1 of FIG. 1 or 2 in a force / displacement diagram (F / S).
  • Curve 10 shows how the kink resistance of the deflecting element 1 increases up to the pressure point DR, then drops almost suddenly and then remains approximately constant.
  • the force F at the pressure point DR is proportional to the thread tension. Since the pressure point DR with respect to the force F and the path S is adjustable, it can be determined at which thread tension and after which way the buckling spring exceeds the pressure point and yields.
  • the dashed curve 11 illustrates the restoring force via a restoring pressure point DR 'to the starting position.
  • H is the relatively large hysteresis of the buckling spring K, which is also clearly evident in a characteristic related to the thread or the thread tension.
  • 4A, 4B illustrate that stationary, preferably adjustable, thread eyelets 12 and 13 are provided upstream and downstream of the deflecting element 1, so that the thread Y is deflected into a zigzag shape.
  • the thread guide element 5 is offset transversely to the thread running direction with respect to the stationary thread eyelets 12, 13.
  • the pressure point DR of the buckling spring K lies between the positions of the thread guiding element 5 which the thread guiding element 5 passes through between FIGS. 4a and 4B (braking areas I and II).
  • 4A indicates that there is more than just one deflection element 1 and, if necessary, a further stationary thread eyelet 12 'between two deflection elements 1 (multiple deflection).
  • Fig. 4B it is indicated that to create asymmetrical deflection conditions the deflection element 1 gives obliquely to the longitudinal direction of the thread (stroke 1 ').
  • 5 (5A to 5E) illustrates a selection of training options for the deflecting element 1 or its buckling spring K.
  • FIG. 5A the cross section of the deflecting element 1 or the buckling spring K corresponds to that of FIGS. 1 and 2.
  • the buckling spring K is a spring lamella 3 and is curved so as to be rounded transversely to the longitudinal axis.
  • the flattened curvature at the kink is indicated by dashed lines.
  • 5B shows a spring lamella 3 with a wide open V cross section, ie a V-shaped camber 4 '.
  • FIG. 5C shows a trough-like edged curvature 4 ′′.
  • 5D shows the strength of the buckling spring K increases from the center to the edge regions.
  • the result is a concave curvature 4 and a flat rear side 14.
  • Other cross-sectional shapes e.g. a double convex cross-sectional shape or the like, conceivable.
  • 5E shows the spring lamella 3 as an articulated spring K with a predetermined kink 17 (recesses 15, 16) in a front view.
  • the spring lamella 3 can be wider at the top (point of application of the thread) than at the bottom (wedge-shaped) in order to move the kink 17 close to the support (even without edge recesses 15, 16).
  • a buckling spring K in the form of a disc with a curvature, which can be deformed via a buckling pressure point and springs back again, would also be conceivable. The support could then attack the circumference of the pane.
  • the deflection element 1 or its thread guide member 5 cooperates with the stop 9 in the buckling spring K causing a bias towards the buckling pressure point in the manner of a mechanical thread clamp, which not only deflects the thread Y but also clamps it in a force-locking manner.
  • the buckling spring is biased towards its buckling pressure point. If the embodiment according to FIG. 6 is used in a deflection brake, then this deflection brake has three braking areas, between which it switches automatically depending on the thread tension. In the first braking area, the thread is deflected and clamped on the stop 9. Either a high basic tension can be generated or the thread can be held.
  • the buckling spring K As soon as the thread tension increases, the buckling spring K is bent in the direction of its buckling pressure point; the clamping of the thread Y is given up.
  • the brake works in a second braking area with deflection and strong friction up to the kink pressure point DR. From the kink pressure point DR, the brake works in the third braking area with little braking effect, ie little deflection and low frictional forces due to the extremely low restoring force. If the thread tension drops again accordingly, then the kink spring K returns the deflecting element 1 to the starting position shown in FIG. 6. It would be conceivable to provide the stop 9 with a friction-active covering in order to increase the clamping braking effect.
  • the buckling spring K designed as a curved spring plate 3 is only a part of the deflection element 1, which is formed in the remaining areas of its length from rigid (and lightweight) parts 1 ′′ and 1 ′′ ′′.
  • the thread guide element 5 can be integrated in part 1 ′′.
  • Part 1 '' ' is fixed in the support 2.
  • the buckling spring defines a specific kink in the deflection element 1.
  • the parts 1 ′′, 1 ′′ ′′ are force transmission elements between the thread Y, the support 2 and the buckling spring K. This construction principle of the deflection element 1 could also be used in the previously described embodiments.
  • a plurality of buckling springs K are placed one behind the other in the direction of action of a first deflection element 1 by the force F of the thread on the thread guide element 5.
  • the buckling springs can act in the same way or be designed with increasing or decreasing buckling strength.
  • the two rear buckling springs are each shorter than the buckling spring of the deflection element 1.
  • a progressive or degressive or constant characteristic of the deflection device can be achieved.
  • the buckling pressure points of the several buckling springs can be exceeded one after the other or overlapping or arbitrarily offset.
  • the device V is a thread deflection brake T.
  • a base body 28 carries upright walls 32 and 33.
  • a round shielding plate 29 is attached to the wall 32.
  • the thread Y passes through the shielding plate 29 and the wall 32 in a stationary thread eyelet 30.
  • a further stationary thread eyelet 34 is provided in the wall 33, which is either offset with respect to the thread eyelet 30 or is arranged coaxially 34 'therewith.
  • a wall 31 forms a right stop for the deflecting element.
  • the limit stop 31 is adjustably supported on the base body 28 in FIG. 6.
  • a counter-holder 35 is provided, which is surrounded by a ring 36.
  • the ring 36 can be pulled with a grub screw 37 against the counter-holder 35 in order to clamp one end of the deflecting element 1 or the buckling spring K.
  • a cutout 38 in the base body 28 allows the deflection element 1 to be inserted further for adjustment.
  • the support 2 can be transversely adjusted in an opening 39 in the base body 28 and carries the stationary adjustable stop 9, against which the thread guiding element 5 rests under pretension in the starting position.
  • the thread Y not shown in FIG. 6, enters through the thread eyelet 30, is deflected transversely to the thread running direction to the thread guide element 5 and runs from there through the thread eyelet 34 or 34 '.
  • the running thread Y is braked at three deflection points (depending on the friction conditions and the deflection angles).
  • the thread guide element 5 If the thread tension rises to a predetermined value, the thread guide element 5 is lifted from the stop 9 and the buckling spring is bent up to the buckling pressure point with increasing resistance. When the pressure point is exceeded, the resistance drops and the thread guiding element 5 continues to yield. The braking effect is greatly reduced because the bending resistance is significantly less than the buckling resistance and because the deflection angle is significant are larger. If the thread tension drops accordingly, the deflecting element 1 automatically shifts back into the starting position shown in FIG.
  • the thread deflection brake T according to FIG. 9 is expedient as a so-called run-in brake for a thread delivery device, in which a certain basic tension of the thread drawn off from a supply spool is required, whereas the thread tension with increased withdrawal resistance from the supply spool and / or strong acceleration of the thread supply device is as little as possible should rise.
  • the self-compensating thread deflection brake T according to FIG. 6 responds to an increase in tension in the thread and suddenly reduces the braking effect to an almost negligible extent (self-compensation of increases in tension).
  • the thread deflection brake according to FIG. 9 could be supplemented with components which simultaneously or alternatively enable the thread tension sensing function, it being advantageous that the contribution of the buckling spring which increases the thread tension largely disappears or is only minimal once the sensed thread tension is reached.
  • the thread tension sensing function is also possible with a stationary thread in which the thread tension varies.
  • FIG. 10A it can be seen how the thread tension t increases with increasing speed v (acceleration phase) from a basic tension t1 in a curve 18 (by the acceleration and by the deflecting and frictional action of the deflecting brake) until at the kink pressure point DR Buckling spring kinks and the thread tension t drops sharply before it increases again moderately with a further increase in speed.
  • Dashed lines indicate that the thread tension t would continue to increase progressively without the buckling spring.
  • the delay phase is indicated in FIG. 10B (curve 19).
  • the thread tension initially decreases gradually until the buckling spring deforms back beyond the reset buckling pressure point DR ', as a result of which the thread tension increases somewhat and then only gradually decreases.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Looms (AREA)
EP97102302A 1996-02-16 1997-02-13 Dispositif pour dévier un fil Expired - Lifetime EP0790208B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19605844A DE19605844A1 (de) 1996-02-16 1996-02-16 Vorrichtung zum Umlenken eines Fadens
DE19605844 1996-02-16

Publications (2)

Publication Number Publication Date
EP0790208A1 true EP0790208A1 (fr) 1997-08-20
EP0790208B1 EP0790208B1 (fr) 1999-06-16

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EP97102302A Expired - Lifetime EP0790208B1 (fr) 1996-02-16 1997-02-13 Dispositif pour dévier un fil

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008012093A3 (fr) * 2006-07-26 2008-03-27 Niederrhein Hochschule Procédé et agencement pour déterminer la qualité du fil et/ou la qualité de bobine d'un fil continu à l'aide d'anémometrie laser doppler
IT202100009470A1 (it) * 2021-04-15 2022-10-15 Lgl Electronics Spa Sensore di tensione del filato per macchine tessili

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Publication number Priority date Publication date Assignee Title
DE10103583A1 (de) * 2001-01-26 2002-08-01 Schlafhorst & Co W Arbeitsstelle einer Kreuzspulen herstellenden Textilmaschine
DE102009021066A1 (de) 2009-05-13 2010-11-18 Oerlikon Textile Gmbh & Co. Kg Fadenspeicher für eine Arbeitstelle einer Offenend-Spinnmaschine

Citations (7)

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Publication number Priority date Publication date Assignee Title
US2814685A (en) * 1954-10-28 1957-11-26 Rheostatic Co Ltd Snap action device
GB826914A (en) * 1955-03-16 1960-01-27 Mackie & Sons Ltd J Improvements in and relating to winding machines
DE2119880A1 (en) * 1970-04-28 1971-11-18 Vyzk Ustav Bavlnarsky Tensioning yarns passed through brakes
EP0268550A1 (fr) * 1986-10-20 1988-05-25 GebràœDer Sulzer Aktiengesellschaft Tendeur de fils pour machine textile
FR2626862A1 (fr) * 1988-02-05 1989-08-11 Caminade Henri Amortisseur a section decroissante de maintien de tension de fil
DE4131656A1 (de) * 1991-09-23 1993-03-25 Iro Ab Verfahren und webmaschine
DE4419265A1 (de) * 1994-06-01 1995-12-07 Schieber Universal Maschf Fournisseur

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2814685A (en) * 1954-10-28 1957-11-26 Rheostatic Co Ltd Snap action device
GB826914A (en) * 1955-03-16 1960-01-27 Mackie & Sons Ltd J Improvements in and relating to winding machines
DE2119880A1 (en) * 1970-04-28 1971-11-18 Vyzk Ustav Bavlnarsky Tensioning yarns passed through brakes
EP0268550A1 (fr) * 1986-10-20 1988-05-25 GebràœDer Sulzer Aktiengesellschaft Tendeur de fils pour machine textile
FR2626862A1 (fr) * 1988-02-05 1989-08-11 Caminade Henri Amortisseur a section decroissante de maintien de tension de fil
DE4131656A1 (de) * 1991-09-23 1993-03-25 Iro Ab Verfahren und webmaschine
DE4419265A1 (de) * 1994-06-01 1995-12-07 Schieber Universal Maschf Fournisseur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008012093A3 (fr) * 2006-07-26 2008-03-27 Niederrhein Hochschule Procédé et agencement pour déterminer la qualité du fil et/ou la qualité de bobine d'un fil continu à l'aide d'anémometrie laser doppler
CN101501490B (zh) * 2006-07-26 2013-12-04 威克股份有限公司 基于激光多普勒测速法确定运行线的纱线质量和/或卷轴质量的方法和装置
IT202100009470A1 (it) * 2021-04-15 2022-10-15 Lgl Electronics Spa Sensore di tensione del filato per macchine tessili
EP4074638A1 (fr) * 2021-04-15 2022-10-19 L.G.L. Electronics S.p.A. Capteur de tension de fil pour machines textiles

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DE59700204D1 (de) 1999-07-22
DE19605844A1 (de) 1997-08-21

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