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EP0768270A2 - Support de bobine pour une bobine ou pour plusieurs bobines, disposées les unes derrière les autres - Google Patents

Support de bobine pour une bobine ou pour plusieurs bobines, disposées les unes derrière les autres Download PDF

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Publication number
EP0768270A2
EP0768270A2 EP96115957A EP96115957A EP0768270A2 EP 0768270 A2 EP0768270 A2 EP 0768270A2 EP 96115957 A EP96115957 A EP 96115957A EP 96115957 A EP96115957 A EP 96115957A EP 0768270 A2 EP0768270 A2 EP 0768270A2
Authority
EP
European Patent Office
Prior art keywords
elements
tube
tensioning
push
clamping
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP96115957A
Other languages
German (de)
English (en)
Other versions
EP0768270A3 (fr
Inventor
Heiner Kudrus
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.)
Neumag GmbH and Co KG
Original Assignee
NEUMAG Neumuenstersche Maschinen und Anlagenbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NEUMAG Neumuenstersche Maschinen und Anlagenbau GmbH filed Critical NEUMAG Neumuenstersche Maschinen und Anlagenbau GmbH
Publication of EP0768270A2 publication Critical patent/EP0768270A2/fr
Publication of EP0768270A3 publication Critical patent/EP0768270A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/40—Arrangements for rotating packages
    • B65H54/54—Arrangements for supporting cores or formers at winding stations; Securing cores or formers to driving members
    • B65H54/543—Securing cores or holders to supporting or driving members, e.g. collapsible mandrels
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T279/00—Chucks or sockets
    • Y10T279/10—Expanding
    • Y10T279/1037—Axially moving actuator

Definitions

  • the invention relates to a bobbin holder for one or more bobbins arranged one behind the other according to the preamble of claim 1.
  • bobbin holders with the greatest possible rigidity are required. This requirement can only be met with a suitable clamping system.
  • a chuck in winding machines for receiving a bobbin which has a rotatable mandrel, a jacket with openings for radial passage of one clamping element each, a plurality of clamping elements and thrust elements arranged in the space between the mandrel and jacket for moving the clamping elements and part of a device for moving the thrust elements.
  • the clamping elements are provided with wedge-shaped surfaces in the axial direction. Along these surfaces, they are axially displaced on corresponding counter surfaces of the thrust elements and thus simultaneously moved radially. It is tensioned by a device for moving the thrust elements with springs, which act on the thrust elements and are compressed to relax by compressed air.
  • the rigidity of the coil holder is determined by the mandrel.
  • a high stiffness of the coil holder therefore requires a certain diameter of the mandrel.
  • the outside diameter of the mandrel is small relative to the inside diameter of the coil to be tensioned. A high stiffness of the coil holder can therefore not be achieved with this system.
  • a coil holder described in DE-B 27 19 853 is similarly constructed with a rotatable main tube, with a jacket sleeve provided with openings for clamping elements and with clamping elements arranged therebetween, cages for the radial movement of the clamping elements and part of a device for moving the cages not suitable for high winding speeds. From DE-B 27 19 853 it is also known to use cylindrical rollers, the axes of which run parallel to the axis of rotation, as clamping elements.
  • a bobbin holder in which clamping elements designed as rolling bodies are arranged on a main tube without a jacket together with fixed bushings and support rings and axially displaceable rings, is known from DE-U 18 73 538.
  • the rings are constantly pressed by springs with their support surfaces against the rolling elements.
  • the diameter and thus the rigidity of the coil holder is limited by the arrangement of the rolling elements, bushings, support rings and rings on the main tube.
  • spring force must always be overcome when sliding on a sleeve. This spool holder is not suitable for high winding speeds.
  • the coil holder has a rotatable main tube, which determines the rigidity, with annular recesses arranged axially one behind the other. Clamping elements are distributed in the cutouts on a circumferential line, the clamping elements being inserted into the cutouts with one part each. Here, too, the clamping elements are displaced radially by axial displacement on wedge-shaped surfaces. From EP-A 06 36 565 it is also known to form the wedge-shaped surfaces by the clamping elements and the contact surface of the recesses.
  • the axial displacement of the clamping elements takes place by means of thrust sleeves which are arranged axially one behind the other on the main pipe and which are provided with openings for the clamping elements.
  • a device with a spring and with a compressed air connection is arranged in the coil holder for the axial displacement of the thrust sleeves. Is tensioned with the help of spring force, in addition to the spring locking the push sleeves, a spring is also provided for each clamping element.
  • Another coil holder in which the tensioning elements are partially arranged in recesses in a main tube, is known from DE-A 21 06 493.
  • wedge-shaped contact surfaces of the cutouts of the main pipe extend in the circumferential direction.
  • an opening which surrounds the main pipe and is provided and which holds the tensioning elements in the tensioning position by means of prestressed springs, is used.
  • the main tube is through the circumferential, about 90% of the circumferential recesses and weakened by further recesses for the springs biasing the cage.
  • the bobbin holder does not have enough rigidity to use it for high winding speeds. In addition, safe, fast acceleration and braking could not be guaranteed with this clamping system.
  • the object of the invention is to develop a bobbin holder according to the preamble of claim 1, which can be operated at even higher winding speeds than the generic bobbin holder.
  • a coil holder according to the invention has a new tensioning system without individual springs.
  • the new clamping system enables simultaneous clamping of all clamping elements by moving the push tubes.
  • the clamping elements are each from a defined starting position, position B, by simultaneous axial
  • clamping position A moves. This means that the sleeves are uniformly clamped centrally.
  • the tensioning elements are held in the tensioning position by the push tubes. Only all clamping elements can be moved at the same time. Individual springs on the clamping elements are not necessary and not possible.
  • the tensioning elements are moved into the tensioning position by moving the push sleeves and locked there by the individual springs.
  • the tensioning system according to the invention is made possible by the fact that the tensioning elements of a group are of the same size, the contact surfaces of the cutouts of the main tube are designed identically for a group of tensioning elements and are aligned on a circumferential line of the main tube, the thrust elements are designed as thrust tubes, the thrust tubes in each case comprise at least two groups of tensioning elements and possibly several thrust tubes are rigidly connected to one another, the openings of the thrust tubes for the tensioning elements of a group are aligned on a circumferential line of the thrust tubes and the axial distances between the openings of the thrust tubes, the axial distances of the recesses in the main tube and thus the axial distances of the clamping elements of the groups enclosed by the push tubes match.
  • the component tolerance of the parts of the clamping system is less than 1/10 mm.
  • the clamping system is improved.
  • the rigidity of the main tube compared to that of the main tube of the generic coil holder provided with annular recesses and the security against rotation when accelerating and braking is increased.
  • a bobbin holder according to the invention can be run at a winding speed which is 2000 rpm higher than a bobbin holder of the generic type.
  • the higher winding speed is due to a higher stiffness of the main tube, a lower risk of imbalance and improved security against rotation of the coil holder.
  • the higher rigidity of the main tube is made possible by the smaller recesses in the main tube, in particular by their limitation in the circumferential direction and by the omission of individual springs.
  • the new clamping system leads to a more uniform, central clamping of the sleeves and thus to less unbalance.
  • the clamping system has fewer parts, especially no individual springs, which can lead to imbalance. Any unbalances that occur can be better absorbed with this clamping system because it is not possible for a single clamping element to move in the clamped state. Only all clamping elements can be moved at the same time, for which purpose the force that holds the push tubes and all clamping elements in the clamping position must be overcome. If, on the other hand, a greater force occurs on a tensioning element of a generic coil holder, i. H. an unbalance, a movement of this tensioning element against the force of the individual spring and thus an increase in the unbalance is possible.
  • Improved security against rotation is achieved by the essentially rigid clamping system without individual springs and by the matching of the width of the recesses in the main tube and the expansion of the clamping elements in the circumferential direction. Improved security against rotation enables faster acceleration and deceleration of the bobbin holder.
  • the outer surfaces of the clamping elements are formed round perpendicular to the axis of rotation.
  • the clamping elements can be balls or cylindrical rollers, with their axes in contrast to those known from DE-B 27 19 853 and DE-A 21 06 493 Clamping elements as well as the clamping elements known from DE-U 18 73 538 are arranged perpendicular to the axis of rotation.
  • the tensioning elements When the tensioning elements are moved, they roll off on the contact surfaces of the recesses in the main pipe, only a lower rolling friction instead of sliding friction having to be overcome.
  • balls and cylindrical rollers are easily available and therefore inexpensive parts.
  • a safety wire prevents the tensioning elements from falling out of the openings of the push tube.
  • Cylindrical tensioning elements also have the advantage that when using cardboard tubes during the tensioning, their end faces press somewhat into the tube and thus form a particularly non-rotatable coil holder. The more secure the spool holder is against rotation, the sooner it is possible to accelerate and brake quickly.
  • tensioning elements as balls is the good availability of balls. Another advantage is that the tensioning elements can be made particularly small when using balls. This enables recesses of the main tube with a shallow depth and thus a high rigidity of the coil holder.
  • Sliding pins that can be used as tensioning elements according to claim 7 are also readily available.
  • a spring between its collar and an annular groove at the inner end of the openings of the push tube presses the tensioning elements onto the main tube and prevents the slide pins from protruding due to their weight in the relaxed state.
  • the slope of the front section in the clamping direction is greater than that of the rear, according to claim 8, the path of the clamping elements between the outer diameter of the push tube and the inner diameter of the sleeve is overcome in a short space by the greater increase in the front section.
  • the sleeves are clamped by the clamping elements with a slight increase in the contact surface. Since the clamping effect of the clamping elements is greater, the smaller the slope of the recess, a large clamping effect is achieved in the clamping area.
  • a device for displacing the thrust tube has an ejector plate fastened to an ejector rod and partially enclosing the thrust tube.
  • ejection plates are known for longer bobbin holders for pushing off the sleeves.
  • the push tube is provided with a collar at its housing end. For tensioning the push tube is through the towards the housing, i.e. H. axially displaced in the tensioning direction, moving ejection plate acting on the collar of the thrust tube. The pressure is released by pushing the sleeve away from the housing through the ejection plate and first taking the push tube with it.
  • an ejection ring as a means for moving the push tube further simplifies the construction of the bobbin holder and promotes high winding speed.
  • FIGS. 1 to 4 an inventive coil holder for a coil, in which the tensioning elements are designed as hollow cylinders, is shown in FIGS. 1 to 4.
  • Figures 1 and 2 are horizontal sections parallel to the axis of the coil holder and Figures 2 and 3 vertical sections perpendicular to the axis of the coil holder.
  • Figures 1 and 3 show the bobbin holder in the tensioned state with the sleeve and Figures 2 and 4 in the relaxed state without the sleeve.
  • FIGS. 5 to 10 show clamping elements of examples 2, 3 and 4 on the basis of sections from representations which correspond to FIGS. 1 and 2.
  • Example 2 is shown in FIGS. 5 and 6, example 3 in FIGS. 7 and 8 and example 4 in FIGS. 9 and 10, FIGS. 5, 7, 9 showing the tensioned state and FIGS. 6, 8, 10 show the relaxed state.
  • FIGS. 11 to 16 An example 5 with a new device for displacing the thrust tube is shown in FIGS. 11 to 16 on the basis of representations corresponding to FIGS. 1 and 2.
  • FIGS. 17 to 20 are excerpts from the representations corresponding to FIGS. 1 and 2.
  • FIGS. 17 and 19 show the tensioned state and FIGS. 18 and 20 the relaxed state.
  • the bobbin holders of Examples 6 and 7 are provided with the device for moving Example 5.
  • a coil holder according to the invention for a coil has a rotatable main tube 1, tensioning elements 2, a push tube 3 and a device for displacing the push tube 3.
  • Figures 1 and 3 show a sleeve 4 for winding a coil which surrounds the push tube 3 in the tensioned state.
  • the main tube 1 projects with its one end into a housing 5 and is rotatably supported there by rotary bearings 6 arranged on its outer circumference.
  • the clamping elements 2 are distributed in several axially arranged groups, each on a circumferential line of the main pipe 1.
  • the clamping elements 2 of a group are the same size.
  • the main tube 1 has corresponding cutouts on its outer circumference, into which the clamping elements 2 are inserted.
  • the contact surfaces of the cutouts of the main pipe 1 for a group of clamping elements 2 are of identical design and are aligned on a circumferential line of the main pipe 1.
  • the widths of the recesses of the main tube are limited in the circumferential direction and correspond to the dimensions of the tensioning elements 2 in the circumferential direction.
  • five clamping elements 2 distributed on a circumferential line of the main pipe 1 form a group.
  • a group consists of at least three tensioning elements 2, but it can also have seven, nine or more tensioning elements 2 in the case of coils with a large inner diameter and corresponding sleeves 4.
  • the sleeve 4 is tensioned by two groups of clamping elements 2.
  • several groups for example 20 for a 1 m long sleeve 4, can also be arranged on the main tube 1 of the coil holder.
  • the cutouts of the main tube 1 are rectangular, one side of the rectangle running parallel to the axis of rotation.
  • the bearing surfaces have two sections 8, 9 lying one behind the other in the axial direction, the gradient being greater in a section 8 at the front in the clamping direction than in a rear section 9.
  • the section 8 at the front in the clamping direction 7 has the shape of a circular section and the rear section 9 in the tensioning direction 7 exhibits a linear increase.
  • the clamping elements 2 consist of hollow cylinders, for example of pipe sections.
  • the length of the pipe sections and thus the extent of the tensioning elements 2 in the circumferential direction corresponds to the width of the cutouts of the main pipe 1 in the circumferential direction except for a movement gap, ie. H. there are clearance fits between the clamping elements 2 and the recesses in the main tube 1.
  • the clamping elements 2 protrude from the recesses by one third to half.
  • a securing wire 10, which is open on one side and which is guided in a groove of the push tube 3, runs through the clamping elements 2 designed as tube sections.
  • the thin-walled thrust tube 3 surrounds the main tube 1 and is guided on slide bearings 11, for example plastic strips.
  • the thrust tube 3 comprising the two groups of tensioning elements 2 has openings 12 for the tensioning elements 2, wherein the openings 12 for the tensioning elements 2 of a group are each aligned on a circumferential line of the thrust tube 3.
  • the axial distances between the openings 12 of the push tube 3 and the axial distances between the cutouts of the main tube 1 match.
  • the axial spacings of the clamping elements 2 arranged in the cutouts thus also match.
  • the openings 12 of the push tube 3 are rectangular and one side is arranged parallel to the axis of rotation, ie in the axial direction.
  • Their size in the axial direction corresponds approximately to the diameter and their size in the circumferential direction approximately to the length of the tube sections forming the clamping elements 2.
  • a device for displacing the push tube 3 has a pneumatic connection 13 with a rotary entry at the end of the main tube 1 mounted in the housing 5 and a spring 14 installed under tension, which is located between two parallel plates 15 arranged perpendicular to the axis of rotation in the interior of the main tube 1, 16 is located on.
  • the plate 15 facing the housing 5 is connected via a screw 17 to a cover 18 of the push tube 3, which projects beyond the main tube 1.
  • the screw 17 is located in the center of the spring 14.
  • the plate 16 facing away from the housing 5 is arranged at the end of the main pipe 1 and is supported to the outside by a shaft retaining ring 20 located in a groove 19.
  • the pneumatic connection 13 is, for example through a bore in the case of a solid construction of the section of the main pipe 1 mounted in the housing 5, with the interior of the main pipe 1 and through bores 21 in the plate 15 and a central opening 22 in the plate 16 with a pressure chamber 23 connected in front of the cover 18 of the push tube 3.
  • the pressure chamber 23 is formed by the part of the thrust tube 3 projecting beyond the main tube 1 and sealed by an O-ring 24 arranged at the outer end of the main tube 1 between the main tube 1 and the thrust tube 3.
  • the spring 14 is extended in the tensioned state.
  • the pressure chamber 23 formed between the main pipe 1 and the push pipe 3 accordingly has its smallest extent.
  • the spring 14 exerts force on the push tube 3 via the plate 15, the screw 17 and the cover 18 in the tensioning direction (arrow 7).
  • the tensioning elements 2 are located on the rear, in the tensioning direction, with a small angle, linearly rising section 9 of the contact surfaces of the recesses of the main pipe 1 in position A. They are by the front edges of the openings 12 in the tensioning direction Thrust tube 3 held exactly in its axial and thus in its radial position.
  • the compressed air is released via the pneumatic connection 13.
  • the spring 14 expands and moves the push tube 3 in the tensioning direction.
  • the tensioning elements 2 are displaced in the tensioning direction, the tensioning elements 2 designed as cylindrical tube sections rolling on the contact surfaces of the cutouts of the main tube 1 and being moved radially outward due to the gradient of the contact surfaces.
  • the clamping elements 2 Due to the greater slope of the front section 8 of the support surfaces, the clamping elements 2 are first moved radially outwards to bridge the distance between the push tube 3, up to which they protrude in the relaxation position B, and sleeve 4 in a shorter axial path. In the rear section 9, a certain axial displacement only leads to a substantially small radial movement.
  • the clamping position A is reached when the force of the spring 14 corresponds to the clamping force of all clamping elements 2.
  • several push tubes 4 can be arranged axially one behind the other.
  • a push tube 4 comprises at least two groups of clamping elements 2.
  • the push tubes are axially rigid, e.g. B. connected by pins.
  • the clamping elements 2 are formed by balls.
  • the diameter of these balls is not significantly larger than the thickness of the push tube 3.
  • the cutouts of the main tube 1 for receiving the clamping elements 2 are less deep and narrower in the circumferential direction.
  • the openings 12 in the push tube 3 are designed as cylindrical bores, the diameter of the bore in the outer region decreasing so that the outer diameter of the bore is smaller than the diameter of the ball.
  • the push tube 3 forms a collar 25 at each opening 12, which prevents the balls from falling out.
  • Such a collar 25 can also be formed by a ring inserted into an annular groove at the outer end of the opening.
  • example 2 corresponds to example 1.
  • Example 3 corresponds to Example 2 except for the differences described below.
  • the push tube 3 also has openings 12 designed as cylindrical bores.
  • the push tube 3 is provided with a circumferential groove 27 in the outer region of the bores. The width of the circumferential groove 27 is wider than the diameter of the balls formed clamping elements 2.
  • a flat metal ring 28 lies in the groove. In the relaxed state, the outer diameter of the metal ring 28 corresponds to that of the push tube 3. In the tensioned state, the metal ring 28 deforms polygonally.
  • the clamping elements are as pins, i.e. H. formed as short, radially arranged pipe sections with an outer collar 29 facing the axis of rotation.
  • pins are known for example as plain bearings for shafts.
  • the recesses of the main tube 1, in which the clamping elements 2 designed as pins are arranged, correspond to that of Example 1.
  • the depth of the recess is approximately the thickness of the collar 29 of the pins.
  • the openings 12 of the push tube 3 are designed as cylindrical bores, the diameter of the bore corresponding to the outer diameter of the pins. At the inner diameter of the push tube 3, the holes have a larger diameter.
  • the collars 29 of the pins enter the annular groove formed at the openings 12 when the tensioning elements 2 are moved radially outward for tensioning by axial displacement of the push tube 3. The pins are locked in the clamping position A by the ring groove.
  • Example 4 corresponds to Example 1.
  • the spool holder of Example 5 differs from the others in that a device for displacing the push tube 3 has an ejection plate 31 which is fastened to an ejection rod 32.
  • the ejection plate 31 can be open on one side. Its inner diameter corresponds approximately to the inner diameter of the sleeves 4 and its thickness approximately that of a thicker sleeve 4.
  • the push tube 3 is provided at its end facing the housing 5 with an annular collar 33 projecting outwards. The thickness of the collar 33 corresponds to the thickness of the ejection plate 31.
  • the ejection plate 31 at least partially encloses the push tube 3 in the tensioning direction in front of the collar 33.
  • the attachment to the ejection rod 32 is carried out, for example, by means of a tab.
  • the ejector rod 32 can be designed as an axial cylinder and is connected to a control device by means of which the ejector rod 32 and thus also the ejector plate 31 can be locked at certain operating positions I, II, III.
  • the device for displacing the push tube 3 also has locking elements 34 inserted into the main tube 1.
  • the locking elements 34 are 2 consecutive grooves 35, which are attached to the inner circumference of the thrust tube 3 so that the locking elements 34 in the tensioning position A in the clamping direction (arrow 7) front groove 35 of the thrust tube 3 and in the relaxation position B in the rear groove 35 protrusions, assigned.
  • the locking elements 34 are small pressure pieces, for example disc springs, on each of which a ball is attached. Otherwise, the coil holder of Example 5 corresponds to that of Example 1.
  • the thrust tube 3 is locked relative to the main tube 1 in the tensioned state (FIG. 11) by the locking elements 34 in the front groove 35.
  • the ejection plate 31 is in the operating position I, in which it has neither contact with the collar 33 of the push tube 3 nor with the sleeve 4.
  • the ejection plate 31 is displaced by the ejection rod 32 against the tensioning direction, touches the sleeve 4 and also pushes the sleeve 4 against the tensioning direction.
  • the sleeve 4 takes the clamping elements 2 and the push tube 3 with them until the clamping elements 2 lose contact with the sleeve 4.
  • the sleeve 4 then lies by its weight on the outer diameter of the push tube 3 and takes the push tube 3 axially to the relaxation position B.
  • the ejection plate 31 is locked in operating position II.
  • the sleeve 4 is pushed onto the spool holder until it stops against the ejection plate 31.
  • the ejection plate 31 is moved in the clamping direction (arrow 7). It hits the collar 33 of the thrust tube 3 and shifts it axially in the clamping direction.
  • the tensioning elements 2 are initially moved along the front section 8 of the contact surfaces of the cutouts of the main pipe 1. As soon as they reach the rear section 9, they touch the sleeve 4.
  • the coil holder of Example 6 (FIGS. 17 and 18) is designed for a conical sleeve 4. Otherwise, it corresponds to the coil holder of Example 5.
  • the coil holder For tensioning the conical sleeve 4, the coil holder has two groups of tensioning elements 2, the tensioning elements 2 of the first group facing the housing 5 being larger than that of the second group in the tensioning direction (arrow 7).
  • the clamping elements 2 of both groups are, as in Example 1, designed as pipe sections of the same length.
  • the diameter of the clamping elements 2 of the first group is approximately 1.1 to 2 times larger than that of the clamping elements 2 of the second group.
  • the contact surfaces of the sections 8 and 9 of the recesses in the main tube for the clamping elements 2 of both groups are of the same design.
  • FIGS. 19 and 20 show a bobbin holder of example 7 which corresponds to that of example 6.
  • Figures 19 and 20 show that this coil holder is also suitable for conical sleeves 4, the inner diameter of which has a step at its rear end in the tensioning direction (arrow 7).

Landscapes

  • Winding Filamentary Materials (AREA)
  • Jigs For Machine Tools (AREA)
EP96115957A 1995-10-13 1996-10-04 Support de bobine pour une bobine ou pour plusieurs bobines, disposées les unes derrière les autres Withdrawn EP0768270A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19538262 1995-10-13
DE19538262A DE19538262A1 (de) 1995-10-13 1995-10-13 Spulenhalter für eine oder mehrere, hintereinander angeordnete Spulen

Publications (2)

Publication Number Publication Date
EP0768270A2 true EP0768270A2 (fr) 1997-04-16
EP0768270A3 EP0768270A3 (fr) 1997-09-03

Family

ID=7774838

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96115957A Withdrawn EP0768270A3 (fr) 1995-10-13 1996-10-04 Support de bobine pour une bobine ou pour plusieurs bobines, disposées les unes derrière les autres

Country Status (4)

Country Link
US (1) US6113025A (fr)
EP (1) EP0768270A3 (fr)
JP (1) JPH09169471A (fr)
DE (1) DE19538262A1 (fr)

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RU2526735C2 (ru) * 2009-12-18 2014-08-27 Сэнт-Гобен Перформанс Пластикс Пампус Гмбх Узел для подкрепляющего кольца и способ его изготолвения
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CN107080365B (zh) * 2016-11-22 2019-05-07 义乌市开晶进出口有限公司 一种物品摆放架
CN107458931A (zh) * 2017-09-04 2017-12-12 通鼎互联信息股份有限公司 一种线缆盘具快速装卸装置
CN107826822B (zh) * 2017-12-01 2024-02-20 山东电航电力设备科技有限公司 非晶薄带全自动换卷机用卷芯锁紧装置
CN108483138B (zh) * 2018-05-14 2024-05-14 蚌埠金黄山凹版印刷有限公司 烫金机及电化铝卷材的收放装置
DE102018132484A1 (de) * 2018-12-17 2020-06-18 Saurer Technologies GmbH & Co. KG Spinnspulenträger für eine Zwirnmaschine
DE102020110288A1 (de) * 2020-04-15 2021-10-21 Oerlikon Textile Gmbh & Co. Kg Spindel für eine Spulenwickelvorrichtung

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JPS5135744A (ja) * 1974-09-17 1976-03-26 Toray Industries Bobinchatsuku
SU617173A1 (ru) * 1976-07-19 1978-07-30 Предприятие П/Я Г-4967 Оправка
DE2719853C3 (de) * 1977-05-04 1980-01-31 Barmag Barmer Maschinenfabrik Ag, 5660 Remscheid Spulenhalter
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DD153487A3 (de) * 1980-02-21 1982-01-13 Lutz Brenner Huelsenspannvorrichtung fuer mehrfach-spulentraeger
DE3039064A1 (de) * 1980-10-16 1982-09-09 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Spannfutter in spulmaschinen
JPS5914409A (ja) * 1982-07-08 1984-01-25 Sakae Seisakusho:Kk 被加工物のチヤツク装置
JPS61166472A (ja) * 1985-01-17 1986-07-28 Asahi Chem Ind Co Ltd 高速巻取機用ボビンホルダ−
DE3663902D1 (en) * 1985-03-14 1989-07-20 Klaus Tesch Device for the reciprocal centering and gripping of two pieces of pipe for welding together
US4767077A (en) * 1986-02-03 1988-08-30 Hiroshi Kataoka Support shaft for winding/unwinding sheets
SU1745656A1 (ru) * 1990-10-15 1992-07-07 Ленинградское машиностроительное объединение им.Карла Маркса Оправка дл закреплени цилиндрических втулок
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DE4335258C2 (de) * 1993-10-15 2000-11-02 Hans Grimm Pneumatisch-mechanische Spannvorrichtung für Wickelwellen, Spannköpfe und dergleichen
DE4335259A1 (de) * 1993-10-15 1995-04-20 Hans Dr Ing Grimm Spannvorrichtung für mindestens eine auf einem Schaft festzulegende Wickelhülse o. dgl.
IT1270018B (it) * 1994-09-27 1997-04-16 Cognetex Spa Mandrino portabobine perfezionato di un gruppo di raccolta di filo a bava continua

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DE19538262A1 (de) 1997-04-17
US6113025A (en) 2000-09-05
JPH09169471A (ja) 1997-06-30
EP0768270A3 (fr) 1997-09-03

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