EP0815301A1 - Gill box - Google Patents

Gill box

Info

Publication number
EP0815301A1
EP0815301A1 EP96904946A EP96904946A EP0815301A1 EP 0815301 A1 EP0815301 A1 EP 0815301A1 EP 96904946 A EP96904946 A EP 96904946A EP 96904946 A EP96904946 A EP 96904946A EP 0815301 A1 EP0815301 A1 EP 0815301A1
Authority
EP
European Patent Office
Prior art keywords
faller
cam
bar
screws
transfer
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Withdrawn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
EP96904946A
Other languages
German (de)
English (en)
Inventor
Michael Walker
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.)
Gill Systems Ltd
Original Assignee
Gill Systems Ltd
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 Gill Systems Ltd filed Critical Gill Systems Ltd
Publication of EP0815301A1 publication Critical patent/EP0815301A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H5/00—Drafting machines or arrangements ; Threading of roving into drafting machine
    • D01H5/02—Gill boxes or other drafting machines employing fallers or like pinned bars
    • D01H5/04—Gill boxes or other drafting machines employing fallers or like pinned bars with pinned bars actuated by screw members

Definitions

  • This invention relates to gillboxes and in particular relates to an improved faller bar transfer mechanism therefor.
  • Gillboxes (sometimes referred to as “draw frames” or “pin drafters”) are used in the primary processing of worsted or semi-worsted yarn manufacture.
  • the worsted card or converter initially forms random or loose fibres into a rope-like form known as "sliver".
  • a gillbox fulfils the function of opening, straightening and mixing the fibres comprising the sliver to ensure that a uniform and level product is supplied to the spinning frame which produces the final yarn.
  • a conventional gillbox consists of a pair of feed rollers, a pair of delivery or front rollers, and between these a number of bars having pins set into them known as faller bars.
  • the sliver is fed into the nip of the feed rollers and is delivered from the front rollers while the faller bars are moved between the two sets of rollers so that the pins of the faller bars provide a combing and straightening action.
  • the faller bars are moved along the gillbox in the direction from the feed rollers to the front rollers and as each faller bar reaches the end of its travel it is transferred to a return run which brings it back to the feed rollers for re-use in a continuous fashion.
  • gillbox It is normal practice for a gillbox to possess a second set of faller bars which operate in an identical manner but are positioned in an inverted fashion above the sliver mass. This type of gillbox is known as an "intersecting" gillbox.
  • the hammers are replaced by cams having a backwardly directed profile starting at the root of the worm-type screw.
  • Corresponding retarding cams are located on the ends of the screw to which the fallers are to be transferred.
  • the ends of the fallers have an unusual and relatively complicated profile to correspond both with the accelerating and retarding cams.
  • the fallers are located considerably below the centre line of the drive screws and are of a length greater than the distance between the roots of the drive screws. This means that the faller bars have poor screw lead control, are relatively expensive to manufacture and cannot easily be removed for cleaning, repair, etc., in use without displacing the saddles of the gillbox.
  • the invention seeks to provide a form of faller bar transfer mechanism for a screw type gillbox improved in the above respects.
  • a faller bar transfer mechanism for a screw type gill box which comprises at least one cam located at the transfer end of each of the working and return screws to contact the faller bars and move them between the working and return screws and vice versa, the cam having a backwardly directed profile with respect to its direction of rotation, characterised in that the faller bars on transfer are fully displaced from the horizontal path of the next following faller bar by a vertical movement less than 85% of the total transfer distance.
  • a faller bar transfer mechanism for a screw type gillbox which comprises at least one cam located at the transfer end of each of the working and return screws to contact the faller bars and move them between the working and return screws and vice versa, the cam having a backwardly directed profile with respect to its direction of rotation, characterised in that the profile of the cam is chosen such that the faller bars are displaced 80% or less of their total transfer distance by the time the cam has rotated through 100° from the point of initial contact with the faller bar.
  • a faller bar transfer mechanism for a screw type gillbox which comprises at least one cam located at the transfer end of each of the working and return screws to contact the faller bars and move them between the working and return screws and vice versa, the cam having a backwardly directed profile with respect to its direction of rotation, characterised in that the cam profile meets the end of the faller bar less than 30° below the horizontal centre line between the screws.
  • a faller bar transfer mechanism for a screw type gillbox which comprises at least one cam located at the transfer end of each of the working and return screws to contact the faller bars and move them between the working and return screws and vice versa, the cam having a backwardly directed profile with respect to its direction of rotation, characterised in that the faller bars are no more than 1 cm (three eighths of an inch) longer than the distance between the driving screw spindles.
  • the worm drive screws on most gillboxes have two leads and therefore deliver two faller bars per revolution. Thus in this case two cams would be provided 180° apart. If a triple lead screw is employed, it will be necessary to have three cams mounted 120° apart. In this case, of course, the 100° referred to above is reduced in the ratio 120:180; and a similar adjustment would need to be made for any other number of screw leads.
  • the remaining description will be with reference to a double lead screw but it will be appreciated that the invention is equally applicable to screws with single, triple, or higher numbers of leads.
  • the cam profile of the invention is, as already indicated, directed backwardly with respect to the rotation of the cam so that the acceleration imparted to the faller bar is gradual and the knocking or "hammering" action of the bulk of previous gillboxes is avoided completely.
  • the profile is preferably shaped so that the faller bar is brought up to a speed in the first portion of the cam revolution which will transfer between the two sets of screws. The profile is thereafter lowered so that, in normal use, the faller bar does not contact the cam at all.
  • the ends of the faller bars need to be modified from the normal square end. It has been found that for both ease of manufacture and efficiency of operation a simple rounding of the ends of the faller bars is preferred. However other profiles of faller bar end may be employed as described more fully hereinafter.
  • the faller bars should be of a size that their profile ends just fit between the roots of the screw drives. Moreover in normal operation it is preferred that the faller bars be located very slightly (1 or 2 mm) below the centre line of the screw drives. While this improves operation in accordance with the invention it is desirable to avoid the faller bars being located too much below the centre line of the screw drives as this introduces unwanted problems including poor faller end/screw control, and the force which is exerted by the fibres on the pins leads to excessive leverage the further the faller bars are positioned from the centre line. While no hard and fast limit can be placed on this, it is preferred that the distance which the faller bars are positioned below the centre line of the screw drives should not exceed approximately 5mm or 6mm, with 8mm being the maximum distance allowable.
  • the cam rises from the root of the screw.
  • the cam preferably contacts the end of the faller bar at approximately the horizontal position, that is on the horizontal centre line between the screws. While the contact may be up to 30° below the horizontal centre line, it is preferred that the contact point in practice be no more than 15° past the horizontal since this leads to the following advantages: improved faller bar removal; improved screw lead/faller bar end control; reduced faller bar/fibre leverage; and simpler and lighter faller bar construction.
  • Figures 1 to 3 are respectively side, front end and top views of a conventional gillbox
  • Figure 4 is a partial diagrammatic representation similar to figure 2 in accordance with the invention.
  • FIG. 5(a) to (c) illustrate different cam profiles
  • Figure 6 illustrates a different faller end profile
  • Figures 7(a) and (b) illustrate the degree of lift given to the faller bar
  • Figure 8 is a similar view to figure 4 with a modified cam profile.
  • a conventional gillbox arrangement generally designated 10 is illustrated having two pairs of screws 12 and 14, one pair positioned above the other.
  • the lower pair of screws 14, the "return screws”, are connected together by a cross shaft 16 and bevel drive 18.
  • the upper pair of screws 12, known as the "working screws”, are driven by spur gears 20,22 from the return screws 14.
  • a plurality of faller bars 24 each having a multiplicity of vertically directed pins 26 are provided (for instance 20 or 30 to a machine).
  • the faller bars 24 are of such a length as to slot into the leads or grooves of each pair of screws as illustrated in figure 3.
  • the faller bars 24 when in the leads of the working screws 12 are supported by a pair of slide bars 28 known as "working saddles".
  • lower saddles 30 Corresponding slide bars known as “lower saddles” 30 are provided below the return screws 14. At the point where the faller bars 24 are transferred between working and return screws there are situated a pair of outer guides 31 known as “conductor guides”.
  • the guides 31 are normally spring loaded from a pivot point and act to restrain and guide the fallers 24 on their passage past the working saddle ends into the opposing screws leads.
  • the downstream ends (adjacent front rollers 32) of the working screws 12 are fitted with cams 34. Similar cams (not shown) are fitted to the downstream ends (adjacent feed rollers 36) of the return screws 14.
  • sliver is fed from the feed rollers 36 across the top of the working screws 12 to the front rollers 32.
  • the pins 26 penetrate the sliver and comb and straighten it.
  • the screw drives 12 and 14 are driven so that the faller bars 24 move in the direction of arrow A in figure 1, i.e. from the feed rollers towards the front rollers.
  • the speed of drive is generally set so that the speed of the fallers 24 is a little more than the speed of feed of the feed rollers 36.
  • the peripheral speed of the front rollers 32 is generally set considerably faster, normally four to eight times faster, which results in the fibres being pulled through the pins 26 of the faller bars, imparting a combing action to the fibres. This is commonly referred to as "drafting" the fibres.
  • the cams 34(a) are of a profile which is sloped in a backward direction with respect to the direction of rotation shown by arrow B.
  • the cam 34(a) thus contacts the faller bar 24 at or close to the horizontal centre-line position between the two screws, at the lowest and inwardmost portion of the cam profile, accelerating the faller bar in a relatively gentle manner over nearly 180° of the screw rotation, in contrast to the violent hammering action of the conventional gillbox. in practice it is convenient to complete the transfer in approximately 160° of rotation and to have a cam profile portion 40 which holds the faller bar in place through the last 20° or so that it is picked up by the screw thread of the lower screw 14.
  • the first part of the profile 42 is relatively steeper than the bulk of the profile 44.
  • the length of this portion 42 is determined so as to be sufficient to impart to the faller bar 24 sufficient speed for it to safely transfer between pairs of screws.
  • the portion 44 of the cam will not normally be contacted by the faller bar 24 (although if the machine is operated slowly the bar will ride the whole of the cam surface).
  • the cams operating to transfer the faller bars 24 from the lower screws 14 to the working screws 12 operate in precisely the same way.
  • the shape of the cam is such that in the first 100° of rotation (out of the preferred 160° to complete the transfer) , the faller bar 24 has moved less than 80% of the total transfer distance.
  • Figure 5 illustrates different shapes of cams which may be employed.
  • Figure 5(a) shows a cam similar to that already described while figure 5(b) shows one having a comparatively steeper initial profile 42 from the root 38. This will result in a faster initial motion of the faller bar 24 making it possible to apply fairly severe braking to the bar at the later stages of its flight.
  • figure 5(c) a slower initial movement is imparted keeping the flight speed lower and not allowing as much braking action to be applied to the bar owing to the possibility of the outer profile of the cam impacting onto the bar.
  • figure 6 it will be seen that an alternative form of profile of the faller end 36 is illustrated.
  • the end profiles of the faller bars are required to be of such a form as to allow the cam profiles to impart a smooth rolling or sliding action to the bar as transfer is performed but their precise shapes may differ.
  • the faller bars are positioned substantially on the centre line with the screws and they must also be able to be easily removed from the screws for cleaning purposes. This restricts the length and position of the bars 24 to substantially within the peripheries of the two screw roots or shafts 38.
  • the use of a normal square ended faller bar would result in a locking action as the cam profiles tried to initially move the bar.
  • a profile as illustrated in figure 6 will give a reasonable rolling or sliding action between the cams without locking the faller bar.
  • Other variations of this form are of course possible but for many purposes the smoothly rounded end illustrated earlier is preferred both for ease of manufacturing and efficiency in use.
  • FIG 7 it can be seen that in a preferred arrangement the faller bar 24 is mounted so that its centre is slightly below the centre line of the root 38 of the screw 12, e.g. l_mm (l/16th inch).
  • Figure 7(b) illustrates the position 90° of rotation later.
  • the faller bar has moved about 1.75cm (ll/16th of an inch) from its initial position.
  • the total displacement is approximately 3.9cm (1.532 inches) and thus at this point the displacement is just over 45% of the total.
  • the displacement is approximately 55%.
  • the faller bars in the working screws are spaced closely together, the spacing being dependent upon the pitch of the screws.
  • a screw pitch of 9mm or there abouts is normally used leaving a gap between the faller bars in the working screws of between approximately lmm and 1.5mm.
  • Faller bars in accordance with the preferred form of the present invention have rounded ends, but the ends are not cranked as with certain prior art designs. This minimises the faller bar depth. It has been found that in order to keep clearance between faller bars on transfer it is necessary for the transferring bar to have completed full displacement from the next following faller bar in the first 100° rotation of the cam. This requirement applies to most mechanisms using screws of around 9mm pitch. These conditions are easily met when traditional hammer type actions are employed as fast initial faller bar acceleration is in any event a feature of these mechanism. On the other hand, when backwardly directed cam profiles are used in order to impart gradual faller bar acceleration, a faller bar of lesser depth is advantageous since it can be removed vertically from the transfer zone sufficiently quickly, without having to impart a high acceleration.
  • the faller bar depth is some 55% of the total distance between working and return runs compared to 90% with some prior art designs, particularly those having faller bars with cranked ends. It is therefore necessary, with the invention, only to move the transfer faller bar 55% of its total vertical distance in the first 100° of spindle rotation, compared to 90% of the total distance with the prior art designs. This explains to some extent why the prior art designs impart such high accelerations: it is necessary to physically move the transfer bar out of the way of the next following bar.
  • the apparatus of the invention enables gillboxes to operate at up to twice the conventional speed without excessive wear and without requiring complex or expensive components.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Attitude Control For Articles On Conveyors (AREA)
  • Transmission Devices (AREA)
  • Reciprocating Conveyors (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)

Abstract

L'invention concerne un mécanisme de transfert à barrettes à aiguilles pour un gill box (10) du type à vis comprenant au moins une came (34) se trouvant à l'extrémité de transfert de chacune des vis de travail et de retour (12, 14) pour venir en contact avec les barrettes à aiguilles (24) et les déplacer entre les vis de travail et de retour, et vice versa. La came a un profil dirigé vers l'arrière par rapport à sa direction de rotation. Les barres à aiguilles lors du transfert sont déplacées complètement depuis le trajet horizontal de la barrette à aiguilles suivante par un mouvement vertical inférieur à 85 % de la distance de transfert totale. On choisit un profil de came permettant aux barres à aiguilles de se déplacer de 80 % ou moins de leur distance de transfert totale au moment où la came a tourné de 100 % par rapport au point de contact initial avec la barrette à aiguilles. Le profil de la came rencontre l'extrémité de la barrette à aiguilles moins de 30 % en dessous de la ligne centrale horizontale entre les vis. Les barrettes à aiguille ne dépassent pas en longueur plus de 1 cm (trois huitièmes d'un pouce) la distance entre les broches d'entraînement des vis. L'accélération donnée à la barrette à aiguilles par la came est graduelle, ce qui permet d'éviter complètement le martelage ou cognement de la masse du gill box classique. Le profil (44a) est formé de préférence de manière à ce que la barrette à aiguilles soit amenée à une vitesse dans la première partie de la rotation de la came qui sera transférée entre les deux jeux de vis. Le profil est ensuite réduit pour que, lors d'une utilisation normale, la barrette à aiguilles ne vienne pas du tout en contact avec la came. Grâce à ce système, il est possible d'accélérer la barrette à aiguilles à la vitesse minimale nécessaire pour qu'elle puisse effectuer un transfert correct sans poursuivre son accélération au-delà de ce point, ce qui minimise le ralentissement à appliquer à la barrette à aiguilles quand elle atteint sa destination et permet à la machine de fonctionner beaucoup plus rapidement.
EP96904946A 1995-03-17 1996-03-06 Gill box Withdrawn EP0815301A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GBGB9505389.8A GB9505389D0 (en) 1995-03-17 1995-03-17 Gillbox
GB9505389 1995-03-17
PCT/GB1996/000502 WO1996029454A1 (fr) 1995-03-17 1996-03-06 Gill box

Publications (1)

Publication Number Publication Date
EP0815301A1 true EP0815301A1 (fr) 1998-01-07

Family

ID=10771356

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96904946A Withdrawn EP0815301A1 (fr) 1995-03-17 1996-03-06 Gill box

Country Status (11)

Country Link
EP (1) EP0815301A1 (fr)
JP (1) JPH11502271A (fr)
AR (1) AR001246A1 (fr)
AU (1) AU4886096A (fr)
GB (1) GB9505389D0 (fr)
PE (1) PE47697A1 (fr)
PL (1) PL322171A1 (fr)
TR (1) TR199600210A1 (fr)
UY (1) UY24182A1 (fr)
WO (1) WO1996029454A1 (fr)
ZA (1) ZA961753B (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105297191B (zh) * 2015-11-17 2018-08-31 武汉汉麻生物科技有限公司 一种自清洁梳箱针板

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE206208C (fr) *
GB295750A (en) * 1927-05-19 1928-08-20 Willie Holdsworth Improvements in or relating to gill-drawing frames
US2116201A (en) * 1936-02-27 1938-05-03 Holdsworth Willie Gill drawing frame
DE2833166A1 (de) * 1978-07-28 1980-02-07 Hergeth Gmbh Bremen Werk Vorrichtung zur verminderung der bei der ueberfuehrungsbewegung von nadelstaeben auftretenden stosskraefte an nadelstabstrecken

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9629454A1 *

Also Published As

Publication number Publication date
JPH11502271A (ja) 1999-02-23
TR199600210A1 (tr) 1997-03-21
AR001246A1 (es) 1997-09-24
PE47697A1 (es) 1997-12-04
WO1996029454A1 (fr) 1996-09-26
AU4886096A (en) 1996-10-08
UY24182A1 (es) 1996-09-10
PL322171A1 (en) 1998-01-19
GB9505389D0 (en) 1995-05-03
ZA961753B (en) 1997-01-07

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