EP0656078B1 - Dispositif permettant d'amener une nappe jusqu'a la tete d'une peigneuse - Google Patents

Dispositif permettant d'amener une nappe jusqu'a la tete d'une peigneuse Download PDF

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Publication number
EP0656078B1
EP0656078B1 EP94917538A EP94917538A EP0656078B1 EP 0656078 B1 EP0656078 B1 EP 0656078B1 EP 94917538 A EP94917538 A EP 94917538A EP 94917538 A EP94917538 A EP 94917538A EP 0656078 B1 EP0656078 B1 EP 0656078B1
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EP
European Patent Office
Prior art keywords
drive roller
roll
lap
cotton
circumference
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
EP94917538A
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German (de)
English (en)
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EP0656078A1 (fr
Inventor
Helfried Lang
Raphael Wicki
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.)
Maschinenfabrik Rieter AG
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Maschinenfabrik Rieter AG
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Publication of EP0656078A1 publication Critical patent/EP0656078A1/fr
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Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01G—PRELIMINARY TREATMENT OF FIBRES, e.g. FOR SPINNING
    • D01G19/00—Combing machines
    • D01G19/06—Details
    • D01G19/08—Feeding apparatus

Definitions

  • the invention relates to a device for feeding a cotton tape from a cotton roll, for the formation of which the cotton tape is wound onto a winding tube, to a combing head of a combing machine, with at least one rotatable drive roller and with support means for rotatably holding the cotton roll with the axis of the drive roller parallel axis in such a way that the circumference of the cotton roll is in contact with the circumference of the drive roller during the unwinding of the cotton tape.
  • the combing heads of known combing machines each contain an oscillating pliers in which an intermittently rotating feed cylinder is mounted.
  • a cotton tape is fed to the feed cylinder from a device of the type specified at the outset.
  • the pliers are closed, the front edge of the cotton tape is combed out by a rotating circular comb.
  • the pliers are then opened and the combed fiber beard is torn off the cotton wool by a tear-off device and connected to the end of the comber belt previously formed from the combed material.
  • the means for rotatably holding the wadding roll comprise a second roller which is arranged horizontally at a distance from and parallel to the drive roller.
  • the second roller can be driven in the same way as the drive roller.
  • the circumference of the wad of cotton is placed on the two rollers.
  • the drive roller is rotated at a peripheral speed which is synchronized with the movements of the parts of the combing head described above. The aim is to ensure that the cotton roll always has the same length of cotton tape for each reciprocating movement of the pliers or for each revolution of the circular comb. This should ensure that the comber belt emitted by the combing head always has a constant strength.
  • the thickness of the combing machine belt or the weight of the belt per meter of belt length at the beginning of the unwinding of the cotton tape from a full cotton lap is greater than towards the end of the unwinding when the cotton lap becomes smaller.
  • the deviation which is generally referred to as drift, can be up to 5% depending on the structure of the cotton roll, material and other parameters.
  • the aim of the invention is to reduce the size of the drift described above.
  • the drift in known devices is caused at least in part by the fact that during the unwinding of the cotton tape the diameter and thus the weight of the cotton roll resting on the drive roller and the second roller gradually decrease.
  • the weight of a full wad of cotton can be about 20 to 25 kg, while the empty winding tube only weighs about 4 kg.
  • indentations occur in the area of the wadding roll on the two rollers in the wadding roll, by means of which the distance from the circumference of the drive roller to the axis of the wadding roll becomes smaller than the free outer radius of the wadding roll.
  • the depth of the indentation is of course dependent on the weight of the cotton roll.
  • the drive roller is usually fluted, and the depth of penetration of the cotton into the flutes depends on the weight of the cotton roll. The decrease in weight of the reel during unwinding can also have an impact on the drive system.
  • the inventive device of the type specified above, with which the set goal can be achieved is characterized in that the drive roller and at least one element of the support means are movable with respect to one another during the unwinding of the cotton tape in such a way that when the diameter and the weight of the cotton wadding against this decrease in weight an equalization of the contact force between the cotton roll and the drive roller is achieved.
  • the support means can contain at least one element which can be inserted into the inside of the winding tube in order to bear at least part of the weight of the cotton roll and / or to exert an additional loading force on the roll. Then only the drive roller has to be in contact with the circumference of the cotton roll, which has the advantage that the cotton layers shed less and become matted than when the cotton roll was placed on two rolls. If desired, however, it is also possible to use two drive rollers which are in contact with the circumference of the cotton roll.
  • the element or elements that can be inserted into the winding sleeve and the drive roller must of course be movable with respect to one another, so that during the unwinding of the cotton tape, the diameter of the cotton roll gradually decreasing, the circumference of the cotton swab comes into contact with the circumference of the drive roller remains.
  • a force load (by springs and / or by weights) could then act on the bearings of the drive roller, which ensures that with the decreasing diameter of the cotton roll, the force with which the drive roller is pressed against the circumference of the cotton roll does not change significantly ( eg by less than ⁇ 10%).
  • a combing head of a combing machine contains a rotating circular comb 1 and two pairs of tear-off cylinders 2, 3, all of which are mounted in a machine frame 4, and a reciprocating pliers 5, in which an intermittently rotating feed cylinder 6 is mounted.
  • a cotton tape W is fed to the feed cylinder 6 and is unwound from a cotton roll 7.
  • the pliers 5 are closed, the front edge of the cotton tape W is combed out by the circular comb 1.
  • the pliers 5 are then opened, as shown, and the combed fiber beard is torn off the cotton tape W by the tear-off cylinders 2, 3 and connected to the end of the comber tape, which was previously formed from combed material.
  • the cotton roll 7 consists in the usual way of a winding tube 8 and the cotton tape, which is wound on the winding tube.
  • the cotton roll 7 is rotated by a drive roller 9, which is rotatably mounted in the machine frame 4 and the circumference of which is in contact with the circumference of the cotton roll 7.
  • the drive roller 9 is driven synchronously with the combing tools of the combing head, in particular with the circular comb 1, the tear-off cylinders 2, 3, the tongs 5 and the feed cylinder 6.
  • the cotton roll 7 is held with an axis of supporting means parallel to the axis of the drive roller 9 in such a way that the circumference of the cotton roll 7 is in contact with the circumference of the drive roll 9 during the unwinding of the cotton tape W.
  • the support means contain two coaxial support pins 10 and 11, which are inserted into the ends of the winding tube 8 during operation and bear part of the weight of the cotton bobbin 7.
  • the trunnions 10 and 11 are rotatably mounted on arms 12 and 13, respectively, which are pivotable about an axis A fixed to the frame.
  • the arms 12 and 13 carry journals 12.1 and 13.1, respectively, which are mounted in the machine frame 4.
  • the axis A of the journals 12.1 and 13.1 runs parallel to the axis of the drive roller 9, so that the arms 12 and 13 and thus the support pins 10 and 11 can be moved with respect to the drive roller 9 in directions perpendicular to the axis thereof.
  • the position of the axis A with respect to the drive roller 9 and the length of the arms 12 and 13, measured from the axis A to the axis of the support pins 10 and 11, are chosen so that during the unwinding of the cotton tape, the diameter of the cotton roll 7 being smaller and the weight of the cotton roll decreases from 100% to less than 25%, the force with which the circumference of the cotton roll 7 rests on the circumference of the drive roller 9 changes by less than ⁇ 20%.
  • a full cotton wrap 7 is shown with solid lines, which have a weight of 100%.
  • the arms 12 and 13 are relatively steep.
  • the weight of the full wadding 7 generates a torque about the axis A, which is given by the size of the weight and the horizontal distance between the axis A and the axis of the trunnions 10 and 11.
  • a small torque which depends on the weight of the Arms 12 and 13 and the parts carried by them.
  • the cotton roll 7 rests on the drive roller 9 with a force which generates a counter torque about the axis A, which is equal to the sum of the torques mentioned above.
  • the diameter of the cotton roll 7 becomes smaller, and the trunnions 10 and 11 move along arc b around the axis A.
  • the weight of the cotton roll 7 decreases, while the horizontal distance between the axis A and the axis of the trunnion 10 and 11 gets bigger.
  • the torque generated by the weight of the cotton roll 7 (and the arms 12 and 13) decreases only slightly, and the contact force of the cotton roll 7 on the drive roller 9, which contact force generates the corresponding counter torque, changes by less than ⁇ 20%.
  • FIGS. 1 and 2 shows the magnitude of the contact force F (in Newtons) as a function of the diameter d (cm) of the cotton roll 7 for an arrangement according to FIGS. 1 and 2, in which the diameter of the full cotton roll is 60 cm, the mass of the full Cotton roll, with the winding sleeve 8, 24 kg (20 kg cotton tape + 4 kg mass of the empty winding sleeve), the diameter of the empty winding sleeve is 20 cm, the axis A from the axis of the drive roller 9 has a horizontal distance of 35 cm and 6 cm is lower than the axis of the drive roller 9.
  • the length of the arms 12 and 13, from the axis A to the axis of the support pins 10 and 11, is 24 cm, and the mass of the arms 12 and 13 is 3.8 kg.
  • the two support pins 10 and 11 are preferably axially movable with respect to one another, so that they can be used to replace the cotton roll, that is to say to remove the empty winding tube 8 (after the cotton tape W has been completely unwound) and to insert a new full cotton roll 7 from the Ends of the winding tube 8 can be pulled out.
  • one of the arms 12 and 13, or both arms can be axially displaced on the bearing journal 12.1 or 13.1 (or with these bearing journal).
  • a pneumatic cylinder 14 can be arranged between the two arms 12 and 13 and can be actuated to move the arms 12 and 13 away from one another when the support pins 10 and 11 are to be withdrawn from the winding tube 8.
  • the empty winding tube 8 can then be removed. Then a new wadding 7 can be lowered between the trunnions 10 and 11.
  • the new wad of cotton lies first on the drive roller 9 and on a storage rod 15 arranged between the arms 12 and 13.
  • the support pins 10 and 11 are conical, as shown in Fig. 2, so that they now by axially moving the arms 12 and 13 - by means of the pneumatic cylinder 14 and / or by means of a tension spring 16 arranged between the arms 12 - in the ends of the Winding sleeve 8 of the new wadding are introduced can.
  • the conical trunnions 10 and 11 slightly lift the wadding 7 from the support rod 15.
  • the force with which the circumference of the cotton roll is pressed against the circumference of the drive roller should preferably decrease by less than ⁇ 20% and expediently by less than when the diameter and the weight of the cotton roll decrease during the unwinding of the cotton tape Change ⁇ 10%.
  • this is achieved essentially solely by the geometrical arrangement of the pivot axis A of the arms 12 and 13 with respect to the drive roller 9 and the length of these arms 12 and 13.
  • the elements supporting the trunnions could also be loaded with pneumatic or hydraulic cylinders, and in such a case the magnitude of the load during the unwinding of the cotton tape could be regulated so that the pressing force of the cotton roll against the drive roller 9 remains approximately constant.
  • the contact pressure could be measured directly, e.g. with force transducers arranged on the bearings of the drive roller.
  • FIG. 4 schematically shows an embodiment of the device according to the invention, in which the elements carrying the trunnions for the cotton lap are loaded with additional weights.
  • FIG. 4 again shows a cotton roll 17 which is in contact with a drive roller 19 mounted in the machine frame, not shown. A part of the weight of the cotton roll 17 is carried in operation by carrying pins 20 inserted into the ends of the winding sleeve of the cotton roll.
  • the elements supporting the trunnions 20 are also arms 22 which are pivotable about an axis A on Machine frame are stored.
  • the support pins 20 are rotatably mounted on the arms 22.
  • the arms 22 are force-loaded with additional weights 24 which are attached to arms 22.1 rigidly connected to the arms 22.
  • the gravity acting on the additional weights 24 exerts an additional torque on the arms 22, which presses the cotton roll 17 against the drive roller 19.
  • the size and position of the additional weights 24, the position of the pivot axis A with respect to the drive roller 19 and the length of the arms 22 are selected so that during the unwinding of the cotton tape, the diameter of the cotton roll 17 becomes smaller and the weight of the cotton roll of 100 % decreases to less than 25%, the force with which the cotton roll 17 is pressed against the drive roller 19 changes by less than ⁇ 20%.
  • the support pins 20 with the empty winding tube are pivoted into a left end position 20.1 shown with broken lines.
  • the combing machine is then switched off.
  • the arms 22 with the support pins 20 can now - by hand or by means of a suitable drive - be pivoted into a right end position 20.2, also shown with broken lines, in which the support pins hold the empty winding tube over a tube tray 25.
  • the empty tube is then placed on the tube tray 25.
  • the arms 22 are then pivoted back into the position shown in solid lines and a new full wadding 17 is inserted between the trunnions 20, after which the combing machine can be put into operation again.
  • FIG. 5 shows a further embodiment of the device according to the invention, in which the elements carrying the support pins for the wadding roll are loaded with springs.
  • the elements carrying the support pins for the wadding roll are loaded with springs.
  • a cotton roll 27 which is in contact with a drive roller 29 mounted in the machine frame, not shown here.
  • support pins 30 which carry the cotton roll.
  • the elements carrying the support pins 30 are sliding pieces 32, which are displaceably guided on inclined guide rails 34 which are fixed to the frame.
  • the supporting pins 30 are rotatably mounted on the sliding pieces 32.
  • One end of a tension spring 35 engages on the sliders 32, the other end of which is anchored to an element 36 fixed to the frame.
  • the springs 35 pull the sliders 32 and thus the wadding roll 27 obliquely upwards against the action of gravity along the guide rails 34, so that the circumference of the wadding roll 27 is pressed against the circumference of the drive roller 29.
  • the diameter of the cotton roll 27 gradually becomes smaller, and at the same time the weight of the cotton roll decreases accordingly.
  • the tension springs 35 are shortened, as a result of which the tensile force exerted by them on the sliders 32 decreases.
  • the inclination of the guide rails 34 relative to the horizontal, the spring constant of the tension springs 35 and the length thereof or the position of the anchoring elements 36 fixed to the frame with respect to the axis of the drive roller 29 are selected such that during the unwinding of the cotton tape W, the diameter of the cotton roll 27 becomes smaller and the weight of the cotton roll decreases from 100% to less than 25%, the force with which the cotton roll is pressed against the drive roller 29 changes by less than ⁇ 20%, preferably by less than ⁇ 10%.
  • the support means which hold the wadding roll in such a way that it is in contact with the drive roller during the unwinding of the wadding tape each contain the two trunnions which, in operation, enter the ends of the Winding sleeve of the cotton swab are introduced. Only the one drive roller is in contact with the circumference of the cotton roll. This has the advantage that the cotton wool is less hairy and matted than with Wadding roll placed on two rollers.
  • the trunnions can fix the axial position of the cotton roll so that the cotton tape always runs in the middle of the pliers of the combing head.
  • the support means for the wadding roll contain two support rollers on which the wadding roll rests.
  • a drive roller which is separate from the support rollers and which is movable with respect to the support rollers would be used for rotating the cotton roll in order to achieve a uniform contact force between the cotton roll and the drive roller as the diameter and weight of the cotton roll decrease.
  • An embodiment of this type is shown schematically in FIG. 6.
  • FIG. 6 again shows a cotton roll 37, which consists of a winding tube 38 and a cotton tape wound on the winding tube.
  • the support means for the cotton roll 37 contain two parallel support rollers 40 and 41, on which the cotton roll rests.
  • the support rollers 40 and 41 are rotatably mounted in the machine frame, not shown here.
  • a drive roller 39 parallel to the support rollers 40 and 41 is rotatably and drivably mounted on levers 42, which are pivotable about an axis 43 fixed to the frame.
  • the bearings of the drive roller 39, ie the levers 42, are force-loaded in order to press the drive roller against the circumference of the cotton roll 37.
  • the levers 42 are designed with two arms, and the force loading of the levers is generated by weights 44 which are fastened on the ends of the levers 42 remote from the drive roller 39.
  • the drive roller 39 is pressed against the circumference of the cotton roll 37 with a force which is largely independent of the diameter (and weight) of the cotton roll.
  • the force loading of the levers 42 carrying the drive roller 39 could also be generated with springs instead of or in addition to the weights 44.
  • Fig. 7 shows schematically an embodiment of the invention with trunnions, the supporting elements of which are loaded with pneumatic or hydraulic cylinders.
  • a cotton roll 47 is in contact with a drive roller 49 which is rotatably mounted in the machine frame, not shown.
  • the cotton roll 47 is held in the operation of support means, which include, on the one hand, support pins 50 inserted into the ends of the winding sleeve of the cotton roll and, on the other hand, a support roller 53 mounted in the machine frame, on which the cotton roll 47 rests with its circumference.
  • the support roller 53 can be driven in the same way as the drive roller 49.
  • the support pins 50 are rotatably mounted on arms 52, which are connected to piston rods 54 of hydraulic or pneumatic cylinders 55 and are displaceable with these piston rods.
  • a valve device 56 permits the supply of a pressure medium with an adjustable pressure either into one or the other end of the cylinder 55.
  • the valve device 56 is controlled by a control device 57 in such a way that the forces exerted by the support pins 50 in the upward or downward direction be exerted on the cotton roll 47 below, together with the weight of the cotton roll result in an approximately constant contact force of the cotton roll on the drive roller 49 and the support roller 53.
  • the control device 57 reduces the forces exerted by the support pins 50 upwards on the cotton roll 47 (and / or increases the downward forces).
  • the control device 57 can be a program control device which controls the forces according to a predetermined program.
  • the control device 57 can also control the forces as a function of the diameter of the cotton winder 47.
  • a position transmitter (not shown) could, for example, determine the position of the piston rods 54 and emit a corresponding signal to the control device 57.
  • the contact force could be measured with force transducers (not shown) arranged on the bearings of the rollers 49 and 53, and the control device could then compare the output signals of the force transducers with a setpoint signal and keep the contact force practically constant.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Preliminary Treatment Of Fibers (AREA)

Abstract

La nappe (W) à acheminer jusqu'à la tête (1, 2, 3, 5, 6) de la peigneuse est dévidée d'un rouleau de nappe (7). Le rouleau (7) contient un mandrin (8) sur lequel la nappe est enroulée. Le dispositif comprend des supports (10, 12) pour maintenir le rouleau de nappe (7) de façon qu'il puisse tourner, que son axe soit parallèle à un rouleau entraîneur (9) et que sa périphérie soit en contact avec ledit rouleau entraîneur (9). Pendant le dévidage, le rouleau entraîneur (9) et au moins un élément des supports (10, 12) effectuent un déplacement relatif par rapport à la nappe (w), de manière à arriver à équilibrer la force de contact entre le rouleau de nappe (7) et le rouleau entraîneur, en dépit de la diminution graduelle du poids du rouleau de nappe (7) et en fonction de cette diminution, ce qui permet à la périphérie du rouleau de nappe (7) d'appuyer avec une pression approximativement constante sur le point de contact. Ce dispositif permet d'éviter que la quantité de nappe dévidée du rouleau de nappe (7) à chaque tour du rouleau entraîneur (9) diminue graduellement pendant le dévidage.

Claims (10)

  1. Arrangement pour l'amenée d'une nappe de rubans depuis un rouleau de nappe, pour la formation duquel la nappe de rubans est enroulée sur un bobinot de rouleau, vers une tête de peignage d'une peigneuse, avec au moins un rouleau d'entraînement rotatif (9; 19; 29; 39; 49), et avec des moyens de support (10, 11; 20; 30; 40, 41; 50) pour maintenir d'une manière rotative le rouleau de nappe (7; 17; 27; 37; 47) ayant son axe parallèle à l'axe du rouleau d'entraînement, de telle manière que, pendant le déroulement de la nappe de rubans (W), la circonférence du rouleau de nappe se tient en contact avec la circonférence du rouleau d'entraînement (9; 19; 29; 39; 49),
    caractérisé par le fait que,
    pendant le déroulement de la nappe de rubans (W), le rouleau d'entraînement (9; 19; 29; 39; 49) et au moins un élément (10, 11; 20; 30; 40, 41; 50) des moyens de support sont mobiles l'un par rapport à l'autre dans le sens que, lors de la diminution du diamètre du rouleau de nappe (7; 17; 27; 37; 47) et de son poids, une égalisation de la force de contact entre le rouleau de nappe et le rouleau d'entraînement est obtenue, malgré cette diminution de poids.
  2. Arrangement selon revendication 1,
    caractérisé par le fait que
    les moyens de support comprennent au moins un élément (10, 11; 20; 30; 50) qui peut être introduit dans l'intérieur du bobinot de rouleau (8), afin de porter au moins une partie du poids du rouleau de nappe (7; 17; 27; 47).
  3. Arrangement selon revendication 2,
    caractérisé par le fait que
    les moyens de support comprennent deux tourillons porteurs coaxiaux (10, 11; 20; 30; 50) qui peuvent être introduits dans les extrémités du bobinot de rouleau (8), afin de porter au moins une partie du poids du rouleau de nappe (7; 17; 27; 47).
  4. Arrangement selon revendication 3,
    caractérisé par le fait que
    les deux tourillons porteurs coaxiaux (10, 11; 20; 30; 50) sont maintenus d'une manière rotative sur des éléments (12, 13; 22; 32; 52) lesquels, par rapport au rouleau d'entraînement (9; 19; 29; 49), sont mobiles dans des directions perpendiculaires relatives à son axe, afin de maintenir la circonférence du rouleau de nappe (7; 17; 27; 47) en contact avec la circonférence du rouleau d'entraînement (9; 19; 29; 49) pendant le déroulement de la nappe de rubans (W).
  5. Arrangement selon revendication 4,
    caractérisé par le fait que
    les éléments (12, 13; 22; 32; 52), sur lesquels sont maintenus les tourillons porteurs (10, 11; 20; 30; 50), sont guidés d'une manière mobile et/ou sont chargés par une force, de telle sorte que, pendant de déroulement de la nappe de rubans (W), pendant lequel le diamètre du rouleau de nappe (7; 17; 27; 47) devient plus petit, et le poids du rouleau de nappe diminue depuis 100% à moins de 25%, la force avec laquelle la circonférence du rouleau de nappe est pressée contre la circonférence du rouleau d'entraînement (9; 19; 29; 49), varie de moins de ± 20%, de préférence de moins de ± 10%.
  6. Arrangement selon revendication 4 ou 5,
    caractérisé par le fait que
    les éléments sur lesquels sont maintenus les tourillons porteurs (10, 11; 20; 30), sont des bras (12, 13; 22) pivotant autour d'un axe (A) fixe sur le bâti.
  7. Arrangement selon une des revendications 3 à 6,
    caractérisé par le fait que
    les tourillons porteurs (10, 11; 20; 30; 50) sont mobiles axialement l'un par rapport à l'autre, de manière à pénétrer dans les extrémités du bobinot de rouleau (8) et à se retirer de ces extrémités.
  8. Arrangement selon revendication 7,
    caractérisé par le fait que
    les tourillons porteurs (10, 11; 20; 30; 50) sont coniques.
  9. Arrangement selon revendication 7 ou 8,
    caractérisé par
    au moins un élément d'appui (15) qui est disposé à distance du rouleau d'entraînement (9; 19; 29) de telle manière qu'un rouleau de nappe plein (7; 17; 27) peut être posé sur le rouleau d'entraînement (9; 19; 29) et sur l'élément d'appui (15), avant que les tourillons porteurs (10, 11; 20; 30) ne soient introduits dans les extrémités du bobinot de rouleau (8).
  10. Arrangement selon revendication 1,
    caractérisé par le fait que,
    pour le rouleau de nappe (37), les moyens de support comprennent deux rouleaux porteurs (40, 41), parallèles au rouleau d'entraînement (39), et que, par rapport aux rouleaux porteurs (40, 41), le rouleau d'entraînement (39) est mobile d'une manière perpendiculaire aux axes de ceux-ci, et est chargé par une force pour la mise en contact sur la circonférence du rouleau de nappe (37).
EP94917538A 1993-06-21 1994-06-20 Dispositif permettant d'amener une nappe jusqu'a la tete d'une peigneuse Expired - Lifetime EP0656078B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH185093 1993-06-21
CH1850/93 1993-06-21
PCT/CH1994/000122 WO1995000686A1 (fr) 1993-06-21 1994-06-20 Dispositif permettant d'amener une nappe jusqu'a la tete d'une peigneuse

Publications (2)

Publication Number Publication Date
EP0656078A1 EP0656078A1 (fr) 1995-06-07
EP0656078B1 true EP0656078B1 (fr) 1996-10-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP94917538A Expired - Lifetime EP0656078B1 (fr) 1993-06-21 1994-06-20 Dispositif permettant d'amener une nappe jusqu'a la tete d'une peigneuse

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Country Link
EP (1) EP0656078B1 (fr)
CN (1) CN1111063A (fr)
DE (1) DE59400899D1 (fr)
WO (1) WO1995000686A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006024555B4 (de) * 2006-05-23 2012-04-05 Oerlikon Textile Gmbh & Co. Kg Kämmmaschine mit Reservewickelmulde
EP2783888B1 (fr) * 2013-03-26 2016-11-02 Inalfa Roof Systems Group B.V. Ensemble store à enrouleur
CN107326481B (zh) * 2017-07-16 2023-08-08 经纬智能纺织机械有限公司 一种单眼光电检测棉条断条的装置及其应用的精梳机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB340686A (en) * 1929-11-04 1931-01-08 Percy Clough Improvements relating to noble's combing machines
DE3935657A1 (de) * 1989-10-26 1991-05-02 Zinser Textilmaschinen Gmbh Zufuehreinrichtung fuer eine kaemmaschine
JP2763968B2 (ja) * 1990-05-02 1998-06-11 マシーネンフアブリーク リーテル アクチエンゲゼルシヤフト ラップ処理機械におけるラップの接合方法及びラップ処理機械

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Publication number Publication date
CN1111063A (zh) 1995-11-01
DE59400899D1 (de) 1996-11-28
WO1995000686A1 (fr) 1995-01-05
EP0656078A1 (fr) 1995-06-07

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