EP0529429A1 - Frein à disques pour fils textiles - Google Patents

Frein à disques pour fils textiles Download PDF

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Publication number
EP0529429A1
EP0529429A1 EP92113807A EP92113807A EP0529429A1 EP 0529429 A1 EP0529429 A1 EP 0529429A1 EP 92113807 A EP92113807 A EP 92113807A EP 92113807 A EP92113807 A EP 92113807A EP 0529429 A1 EP0529429 A1 EP 0529429A1
Authority
EP
European Patent Office
Prior art keywords
brake
disc
plate
carrier
spring
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
EP92113807A
Other languages
German (de)
English (en)
Other versions
EP0529429B1 (fr
Inventor
Günter Alder
Hubert Kremer
Hans Theihsen
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.)
Hacoba Textilmaschinen GmbH and Co KG
Original Assignee
Hacoba Textilmaschinen GmbH and Co KG
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 Hacoba Textilmaschinen GmbH and Co KG filed Critical Hacoba Textilmaschinen GmbH and Co KG
Publication of EP0529429A1 publication Critical patent/EP0529429A1/fr
Application granted granted Critical
Publication of EP0529429B1 publication Critical patent/EP0529429B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • B65H59/20—Co-operating surfaces mounted for relative movement
    • B65H59/22—Co-operating surfaces mounted for relative movement and arranged to apply pressure to material
    • B65H59/225—Tension discs
    • 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 plate brake for textile threads, with a plate axis arranged perpendicular to a horizontal brake carrier of a creel, and with an adjustable upper plate for adjusting the braking force.
  • a known plate brake with the aforementioned features consists of two weight-loaded plates, the plate axis of which is fastened to a bearing plate, which carries wrap pins for a textile thread parallel to the plate axis, with which the thread tension is preset.
  • Such a disk brake does not meet the requirements for fast and accurate thread tension settings, especially not when tension changes have to be set on a large number of disk brakes of a bobbin creel.
  • Disc brakes with a vertical brake carrier are known, in which the upper disc is spring-loaded to adjust the braking force.
  • the compression spring generating the spring force is arranged coaxially to the plate axis and is supported with one end on the upper plate, while the other end can be adjusted more or less in the directions of the plate axis in order to adjust the braking force.
  • the known disk brake is installed in the cavity of the brake carrier designed as an open hollow profile. The brake carrier is therefore disproportionately large in cross section and must be designed specifically for the thread guide.
  • the invention has for its object to improve a disc brake with the features mentioned above so that the entire adjustment range of the brake can be controlled with a single spring, the construction being matched to the horizontal brake carrier.
  • a carrier-parallel brake spring is arranged below the horizontal brake carrier, which engages on the one hand on the brake carrier or on an actuator which is displaceable relative thereto, and on the other hand engages a lever arm of a pivotable fixed bellcrank which is vertical under the influence of the brake spring presses the upper plate.
  • the particularly adapted use of the brake spring is important for the invention, namely its use as a brake spring parallel to the carrier.
  • This use of the brake spring outside the axis of the plate is a prerequisite for being able to vary the load on the upper plate to a considerably greater extent.
  • the arrangement of the brake spring parallel to the brake carrier also enables a space-concentrated design of the adjusting device of the disk brake with respect to the creel. Otherwise, the disk brake can be designed independently of the design of the horizontal brake carrier.
  • the plate brake is advantageously designed such that the deflection lever is a two-armed lever, on one arm of which the brake spring engages and the other arm is angular and presses with one end onto the upper plate via a pressure device.
  • the design of the bell crank as a two-armed lever requires in particular structural freedom of movement for the design of the disk brake and at the same time for the selection of the adjustment range of the braking force.
  • the pressure device enables necessary adjustments in the area between the lever arm end and the upper plate.
  • the disk brake is designed so that one arm of the bell crank with play through a recess in the brake carrier extends into the area of the brake spring parallel to the carrier and has several spring engagement points there.
  • it is therefore only necessary to let the brake spring act at the respectively desired spring application point. This can be achieved in a particularly simple manner by hanging the brake spring when the brake spring parallel to the carrier is a tension spring. Except for moving the brake spring around, no measure is required to change the braking force range of the disk brake.
  • the disc brake can be designed so that the brake spring is suspended at one end in a notch in the arm of the bell crank and is attached at the other end to an adjusting ring which is clamped on the actuator designed as a parallel rod.
  • the disk brake is also suitable for central adjustment, in which the actuator designed as a parallel rod can engage with several adjusting rings on a corresponding number of brake springs of several disk brakes.
  • the mainspring Compared to a compression spring, the mainspring has the advantage of not requiring radial guidance, which leads to an impairment of the effective braking force.
  • the disc brake In order to design the disc brake so that it can be largely preassembled on the horizontal brake carrier, it is designed so that the disc axis is connected to the bellcrank to form a unit that is attached to the brake carrier. This not only favors the assembly of the disc brake with the brake carrier, but also the removal of the disc brake in the event that a component is defective. In this case, the entire assembly can be easily replaced with a new one, which reduces the idle times of the creel.
  • the structural unit is manufactured in particular by connecting the plate axis the pivot axis of the deflection lever is used with the deflection lever to form a structural unit, the ends of which engage in the side walls of a radial slot of a bearing plate of the plate axis.
  • the plate brake is designed in such a way that the bearing plate rests on a mounting plate which can be assembled with the brake carrier and which has thread eyelets held at the level of the plate gap.
  • the disc brake is designed so that the bearing plate has a rotationally symmetrical bearing recess for an axially supported bearing shaft that the carries the lower plate co-axially and passes through the brake carrier with a shaft end, which has a carrier-parallel traversing rod which engages in the shaft end. So there is a reciprocating drive of the bearing shaft, so that fluff and the like. Cannot fix thread abrasion in the area of the plates, as would be the case with stationary plates or with rotating plates.
  • the bearing shaft carries the lower plate with a resilient ring axially displaceable, so that slight axial movements of the lower plate are made possible, for example to let knots of the thread pass.
  • the flexibility is limited in order to be able to press the thread over the upper plate with the required pressure.
  • the plate brake is designed such that the bearing shaft has a spring which engages in the upper plate through a central recess in the lower plate.
  • the spring enables a synchronous drive of the upper plate and a limited relative rotation adjustment of the two plates, which results in their assembly and maintenance intervention in the plate brake is useful, which also favors the normal operation of the disc brake in terms of avoiding malfunctions.
  • the spring is a piece of wire, one end of which is annular and inserted in a circumferential groove of the bearing shaft, and the other end of which protrudes axially parallel to the upper plate, which has one or more recesses for the engagement of one radial section of the other Has piece of wire end.
  • the disc brake is designed so that the length of the pressure pin can be adjusted.
  • the plate brake can be designed so that the bearing plate has on its outer circumference a recess that makes the lower plate laterally accessible. Such a recess can be used to clean the plate brake, in addition to manipulating the lower plate.
  • the plate brake so that the bearing plate has on its outer circumference, at least in the area determined by the thread eyelets, a thread sliding surface extending from the height of the plate gap to the vicinity of the mounting plate. This is particularly advantageous in order to prevent the thread from getting caught in the area of the plate brake. A slack thread can be easily pulled into the plate gap on the thread sliding surface when the thread is re-tensioned with another warping or slip.
  • the thread 11 shown in FIG. 2 is drawn from a bobbin (not shown) of a creel in the direction of arrow 11 'by a winding machine, for example by a warping machine or a warping machine.
  • the thread 11 passes through the plate brake 10, which gives it the thread tension required for winding.
  • the plate brake 10 has an upper plate 14 which rests on a lower plate 26. Both form a plate gap 35 with the visible flattened portions, through which the thread 11 is drawn into and through the plate brake 10.
  • the plates 14, 26 are shell-shaped pressed sheet metal parts, the outer shell edges of which point parallel to a central axis 41 upwards or downwards.
  • the plates 14, 26 have inner recesses 14 ', 26' formed by inner edges parallel to the outer edges, so that the plates 14, 26 are actually annular.
  • a plate brake 10 is arranged with its plates 14, 26 on a horizontally extending brake carrier 12 which, according to FIG. 3, has the F-shaped cross section shown there, for example.
  • a mounting plate 39 is provided which carries thread eyelets 40 with bends 39 ', which are arranged at the level of the plate gap 35 and, as a result of the counter arrangement shown in FIG. 2, the passage area of the thread 11 through the thread brake Set 10.
  • the mounting plate 39 is screwed to the brake carrier 12 at the points 39 ′′.
  • the mounting plate 39 carries a plate axis 13 for supporting the plates 14, 26.
  • the support is provided with a flexible ring 28, for example a foam ring.
  • this ring 28 is stiff enough to be able to support the necessary pressure forces exerted by a pressure device 20 on the upper plate 14.
  • the flexible ring 28 must in turn be supported directly or indirectly on the plate axis 13.
  • the plate axis 13 is provided with a bearing plate 36 on which the ring 28 could be supported. This would be the case if the disk brake 10 were designed without a drive for thread cleaning.
  • the ring 28 is supported indirectly via a bearing shaft 25 with which the lower plate 26 is to be driven in rotation via the ring 28.
  • the bearing shaft 25 has a shaft end 25 'which passes through the brake carrier 12 transversely.
  • the bearing shaft 25 is not supported directly on the brake carrier 12, but in a bearing recess 24 formed by the bearing plate 36, which is formed by an annular projection 42 of the bearing plate 36.
  • This bearing recess 24 is radially expanded above the brake carrier 12 and within the bearing plate 36 so that the bearing shaft 25 can receive the ring 28 with an outer circumferential groove 25 '' such that the ring 28 is radially spaced from the adjacent bearing plate 36, relative to the he turns.
  • the extent of the movement is such that the lower plate 26 rotates a little more than 360 °.
  • the traversing rod 27 engages with a rack piece 27 'in the toothing 25''' of the bearing shaft end 25 'according to FIG.
  • the drive of the bearing shaft 25 acts only on the lower plate 26. So that the upper plate 14 is also pivoted back and forth to the same extent, a spring 29 is provided, which is formed from a piece of wire. One end 29 'of which is openly ring-shaped and resiliently clamped in a groove 30 of an inner wall 44 of the hollow bearing shaft 25.
  • the inner diameter of the hollow bearing shaft 25 is dimensioned so large that the inner plate rim projecting radially towards the brake carrier 12 in the bearing shaft 25 can engage.
  • the other end 29 '' of the piece of wire initially projects axially in the direction of the upper plate 14 and engages in its inner recess 14 ', where it is angled radially and projects radially into the region of the axial inner edge of the plate 14, where it engages with one Radial section 32 engages in a recess 31 of the plate 14 or the annular plate inner edge.
  • a single recess 31 is shown as a bore. It goes without saying, however, that a plurality of recesses 31 can also be present here as bores or as slots in order to facilitate assembly.
  • the pressure device 20 is provided which presses on the upper plate 14.
  • the pressure device 20 consists essentially of a pressure plate 33 which is fixedly connected to the inner edge of the plate 14, which therefore rotates with it, provided the plate 14 is driven.
  • the pressure device 20 is loaded by a pressure pin 34 which engages in a blind hole 33 'of the pressure plate 33 and is relatively movable therein. Relative to the pressure plate 33, this pressure pin 34 therefore stands still and has the required play which is required for a low-friction pressure force transmission in the axial direction.
  • the pressure pin 34 is acted upon by a bell crank 17 with a brake spring 15.
  • the deflection lever 17 is designed as a two-armed lever, the pivot axis 17 'of which is supported on the bearing plate 36, so that the deflection lever 17 is connected to the entire plate axis 13 to form a structural unit.
  • the bell crank 17 is arranged in a radial slot 38 of the bearing plate 36.
  • the pivot axis 17 'of the bell crank 17 engages with its ends in side walls 37 of the radial slot 38.
  • the bearing plate 36 has on its outer surface facing the mounting plate 39 a mounting slot 46 into which the ends of the pivot axis 17' are pressed with mounting pieces, not shown, which are seated on them and which are assembled after the mounting of the bearing plate 36 cannot fall out again with the mounting plate 39.
  • the deflection lever 17 is a two-armed lever with a lever arm 18 which passes through the mounting plate 39 and the brake support 12 with movement play, for which purpose the brake support 12 has a recess 21 which provides movement play. This play of movement allows the lever arm 18 to be adjusted in both pivoting directions according to FIG.
  • the other lever arm 19 is angled or V-shaped.
  • One V-leg extends in the direction of the lever arm 18 and the other V-leg is arranged parallel to the brake carrier 12 and carries an adjusting screw 45 with a lock nut 45 'at its end 19' or a threaded hole therein.
  • the set screw 45 can raise or lower the pressure pin 34 and thus bring about a fine adjustment of the pressure force of the upper plate 14 on the lower plate 26 or on the thread 11, depending on the abutment force of the ring 28.
  • the brake spring 15 designed as a tension spring engages with one end 15 ′, which is hooked into a spring engagement point 22 of this arm 18.
  • the other end 15 ′′ of the spring 15 is attached to an adjusting ring 23 which is clamped on an actuator 16 designed as a rod.
  • the brake spring 15 can also be attached directly to a brake carrier 12.
  • the brake spring 15 can be tensioned to a greater or lesser extent, so that a more or less large pressure force is exerted on the upper plate 14 or on the thread 11 with the deflection lever 17.
  • the actuator 16 can be provided with a plurality of adjusting rings 23 for further disc brakes, so that there is a central adjustment for several disc brakes or for all disc brakes of a creel.
  • the arm 18 of the deflection lever 17 projects transversely to the adjustment direction of the actuator 16 under the horizontal brake support 12 or into the horizontal movement range of the actuator 16 and has a plurality of spring engagement points 22 there.
  • These spring engagement points 22, which are designed as notches, are at different distances from the pivot axis 17 '.
  • the braking force of the disk brake 10 is different. It is the lowest in the uppermost spring application point 22 because the lever arm is shortest here, and the braking force is greatest in the lowest spring application point 22.
  • the bearing plate 36 is raised approximately to the height of the plate gap 35, so that it can serve there, in particular when the thread 11 is not under tension.
  • the bearing plate 36 is provided with a thread sliding surface 36 'which extends into the vicinity of the mounting plate 39 and which, in the case of a tension-free, possibly somewhat sagging thread, can be used to pull it into the plate gap 35 without entanglement during further winding.
  • the bearing plate 36 also serves to protect the lower plate 26, which it encompasses on the outside except for a recess 36 ′′ which makes the plate 26 laterally accessible. As a result of the recess 36 ′′, fluff adhering to the edge of the plate 26 can be removed.
  • Spacious annular plate recesses 47 have the effect that the outer edge of the lower plate 26 projecting axially in the direction of the brake carrier 12 can circulate freely.

Landscapes

  • Braking Arrangements (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Warping, Beaming, Or Leasing (AREA)
EP92113807A 1991-08-22 1992-08-13 Frein à disques pour fils textiles Expired - Lifetime EP0529429B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9110404U DE9110404U1 (de) 1991-08-22 1991-08-22 Tellerbremse für Textilfäden
DE9110404U 1991-08-22

Publications (2)

Publication Number Publication Date
EP0529429A1 true EP0529429A1 (fr) 1993-03-03
EP0529429B1 EP0529429B1 (fr) 1995-07-05

Family

ID=6870507

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92113807A Expired - Lifetime EP0529429B1 (fr) 1991-08-22 1992-08-13 Frein à disques pour fils textiles

Country Status (5)

Country Link
US (1) US5318155A (fr)
EP (1) EP0529429B1 (fr)
JP (1) JPH05201620A (fr)
DE (2) DE9110404U1 (fr)
ES (1) ES2076632T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9311971U1 (de) * 1993-08-11 1994-12-15 Hacoba Textilmaschinen GmbH & Co KG, 42281 Wuppertal Tellerbremse für Textilfäden
WO1999061691A1 (fr) * 1998-05-27 1999-12-02 Sucker-Müller-Hacoba Gmbh & Co. Tendeur de fil

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103088505A (zh) * 2012-12-28 2013-05-08 苏州焕乾纺织有限公司 一种织布机的纱线张力器
EP3334673B1 (fr) * 2015-08-11 2020-05-13 American Linc LLC. Tendeur de fil réglable et tambour d'alimentation en fil

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR563232A (fr) * 1922-05-23 1923-11-29 Dispositif perfectionné pour l'embobinage des fils
US2537476A (en) * 1944-11-22 1951-01-09 Sulzer Ag Thread brake
DE2830205A1 (de) * 1978-07-10 1980-01-24 Schlafhorst & Co W Fadenbremse
DE3228282A1 (de) * 1982-07-29 1984-02-09 W. Schlafhorst & Co, 4050 Mönchengladbach Aggregat von traeger und fadenspannvorrichtungen fuer ein spulengatter

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2264069A (en) * 1939-01-16 1941-11-25 Hemphill Co Stocking top and method of knitting same
US3146969A (en) * 1962-05-10 1964-09-01 Elbert B Lindsey Thread tensioning device
US3575360A (en) * 1968-11-20 1971-04-20 Lawson Hemphill Universal compensating tension device
CS149785B1 (fr) * 1970-04-28 1973-08-23
US4209881A (en) * 1978-03-21 1980-07-01 Phillips Petroleum Company Knitting intermittently drawn yarns
DE3416195C2 (de) * 1984-05-02 1987-01-08 Gustav 7290 Freudenstadt Memminger Fadenliefervorrichtung für fadenverarbeitende Textilmaschinen, bspw. Rundstrick- oder -wirkmaschinen
DE3609719A1 (de) * 1986-03-21 1987-10-01 Schieber Universal Maschf Verfahren und vorrichtung zum beeinflussen der laenge und des maschenbildes von strickstuecken
US4880175A (en) * 1987-04-14 1989-11-14 Murata Kikai Kabushiki Kaisha Tension setting and controlling method and apparatus in an automatic winder

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR563232A (fr) * 1922-05-23 1923-11-29 Dispositif perfectionné pour l'embobinage des fils
US2537476A (en) * 1944-11-22 1951-01-09 Sulzer Ag Thread brake
DE2830205A1 (de) * 1978-07-10 1980-01-24 Schlafhorst & Co W Fadenbremse
DE3228282A1 (de) * 1982-07-29 1984-02-09 W. Schlafhorst & Co, 4050 Mönchengladbach Aggregat von traeger und fadenspannvorrichtungen fuer ein spulengatter

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9311971U1 (de) * 1993-08-11 1994-12-15 Hacoba Textilmaschinen GmbH & Co KG, 42281 Wuppertal Tellerbremse für Textilfäden
EP0638506A2 (fr) * 1993-08-11 1995-02-15 Hacoba Textilmaschinen GmbH & Co KG Frein à disques pour fils textiles
EP0638506A3 (fr) * 1993-08-11 1996-04-03 Hacoba Textilmaschinen Frein à disques pour fils textiles.
WO1999061691A1 (fr) * 1998-05-27 1999-12-02 Sucker-Müller-Hacoba Gmbh & Co. Tendeur de fil

Also Published As

Publication number Publication date
JPH05201620A (ja) 1993-08-10
ES2076632T3 (es) 1995-11-01
DE9110404U1 (de) 1991-11-28
DE59202799D1 (de) 1995-08-10
EP0529429B1 (fr) 1995-07-05
US5318155A (en) 1994-06-07

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