EP0073930A2 - Fadenaufwickelmaschine - Google Patents

Fadenaufwickelmaschine Download PDF

Info

Publication number: EP0073930A2
Authority: EP; European Patent Office
Prior art keywords: chuck; winder; thread; friction drive; drive member
Prior art date: 1981-09-03
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

EP82107022A

Other languages

English (en)

French (fr)

Other versions

EP0073930B1 (de

EP0073930A3 (en

Inventor

Kurt Mueller

Walter Vetterli

Markus Feusi

Josef Huber

Heinz Oswald

Peter Pfyffer

Kurt Schefer

Kurt Salvisberg

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

Original Assignee

Maschinenfabrik Rieter AG

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.)

1981-09-03

Filing date

1982-08-04

Publication date

1983-03-16

1981-09-03 Priority claimed from GB08126692A external-priority patent/GB2105378A/en

1982-08-04 Application filed by Maschinenfabrik Rieter AG filed Critical Maschinenfabrik Rieter AG

1983-03-16 Publication of EP0073930A2 publication Critical patent/EP0073930A2/de

1984-03-07 Publication of EP0073930A3 publication Critical patent/EP0073930A3/en

1986-12-03 Application granted granted Critical

1986-12-03 Publication of EP0073930B1 publication Critical patent/EP0073930B1/de

Status Expired 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
- B65H67/00—Replacing or removing cores, receptacles, or completed packages at paying-out, winding, or depositing stations
- B65H67/04—Arrangements for removing completed take-up packages and or replacing by cores, formers, or empty receptacles at winding or depositing stations; Transferring material between adjacent full and empty take-up elements
- 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 present invention relates to developments in the art of winding of threads, particularly but not exclusively filaments of synthetic plastics material.
thread can be wound substantially continuously and without any substantial waste during the transfer operation from one chuck to another.
revolver-type machines are described, e.g. in United States Patent Specifications 3856222; 3941321; 4283019, in European Published Application 78300409 (US Continuation 129625) and British Patent Specification 1455906. Many others are also known.
the winding operation itself assumes precise geometrical relationship of the various parts and a precise interface force between the drive roll and the chuck.It will therefore be appreciated that the winding operation and the operation of transferring thread from an "outgoing" to an "incoming" chuck can be very delicate, particularly when handling threads of fine titer and low extensibility. Such threads cannot stretch to accomodate variations in tension, and they commonly have little strength to resist such variations. Accordingly, thread breaks and winding faults are very common when revolver-type machines are used with such threads. To minimise such breaks it is essential to control movements and forces while winding, and to perform the changeover, with minute exactness so that tension variations are reduced to the minimum. This is obviously very difficult to achieve in a machine designed for practical operation under widely varying circumstances as opposed to specific design for a single highly controlled operation.
This second movement can be achieved in principle by movement of the chuck structure relative to a fixed friction roller, or vice versa, or by a combination of movements of both elements.
the carrier head itself constitutes a mechanical connection between the two chuck structures, making it extremely difficult to effectively isolate one structure from shocks and vibration on the other.
the movements required of the carrier head at particular phases of an operating cycle may be contradictory - for example, the movement of the head to bring a completed package out of the winding position may be in opposition to the movement required to control contact pressure between the new package and the drive roller.
it is always necessary to perform certain control functions within each chuck itself, e.g. release and clamping of packages mounted on the chuck it is necessary to provide complicated rotary connections for control leads extending from the statonary machine frame via the rotary carrier head to each chuck.
the invention provides a winder for thread, particularly but not exclusively synthetic plastics filament, comprising a friction drive member rotatable about a longitudinal axis thereof.
a first chuck is movable along a first predetermined path from a rest position to a winding position in which the chuck is driven into rotation about the longitudinal chuck axis thereof by the friction drive member.
the first chuck is returnable to its rest position by movement along the first path.
a second chuck is movable along a second predetermined path from a rest position to a winding position in which the second chuck is driven into rotation about the longitudinal chuck axis thereof by the friction drive member.
the second chuck is returnable to its rest position by movement along the second path.
the first and second paths can be so disposed that a thread catching means on a chuck moving along its path towards the friction drive member ("incoming" chuck) can intercept a length of thread extending between the friction drive member and a chuck moving along its path away from the friction drive member ("outgoing" chuck).
each of the first and second paths is curvilinear, preferably determined by a swing arm upon which the respective chuck is mounted.
this is not essential.
each chuck may extend cantilever-fashion from the front of a headstock.
the winding position of the first chuck in which the chuck first comes into driving relationship with the friction drive member during its movement towards the latter, is not necessarily identical with the corresponding winding position of the second chuck.
Each such winding position constitutes the end of the respective path adjacent the friction drive member and is referred to hereinafter as the "end winding position" of the respective chuck.
Drive contact between a chuck (or a bobbin tube or package carried thereby) and the friction drive member is preferably made within a predetermined zone of the circumference of the friction drive member, referred to hereinafter as the "winding zone".
the friction drive member is preferably so located in the machine, and the winding zone is preferably so located relative to the friction drive member, that the longitudinal axis of a chuck in its end winding position lies in or near a horizontal plane containing the longitudi- axis of the friction drive member.
the paths of movement of the chucks may be arranged to intersect immediately in front of the winding zone.
the paths of movement of the chucks may be so arranged that the thread catching means on the incoming chuck intercepts the length of thread extending to the outgoing chuck when the incoming chuck is at a location on its path adjacent its end winding position. Normally, it will be preferred to effect the interception when the incoming chuck has reached its end winding position and is in driving relationship with the friction drive member.
the incoming chuck may be temporarily stopped on its path shortly before reaching its end winding position, and a changeover may occur during this temporary stop. After changeover, the incoming chuck will complete its movement to its end winding position.
a movable abutment may be provided against which the incoming chuck, or a part secured thereto, will strike during movement of the incoming chuck towards its end winding position. The abutment' may be moved after completion of changeover to release the incoming chuck to complete movement to the end winding position.
the distance through which the chuck has to move after the changeover is preferably held as short as practically possible.
a controllable moving means is provided to move each chuck along its path.
the preferred form of moving means is a pressure fluid operated means such as a piston and cylinder unit.
the longitudinal axis of the friction drive member is then fixed in the machine frame during winding. Build up of a package between a chuck and the friction drive member is accomodated by return movement of the chuck from its end winding position towards its rest position - drive contact with the friction drive member being of course maintained.
the contact pressure applied between the chuck and the friction drive member must be controlled during the winding operation.
this control is effected by control of the moving means, for example by control of the pressurisation of a pressure fluid operated moving means.
this control is effected during movement of the chuck over a predetermined portion of its path from the end winding position back towards the rest position. After the chuck has moved through said predetermined portion, the package has reached the desired dimensions and the winding operation is broken off.
the moving means is then operated to return the chuck relatively quickly towards the rest position and a changeover operation is initiated as will be further described below.
the rest positions of the chucks preferably lie on opposite sides of a plane containing the longitudinal axis of the friction drive member and passing through the winding zone. As indicated above, such a plane is preferably horizontal or nearly so. Accordingly, in the preferred embodiment, one chuck approaches the friction drive member from above, and the other chuck from below. In both cases, means is preferably provided to compensate for the effect of the weight of a package building up on the chuck, since otherwise this increasing weight of package will lead to undesirable variations in the contact pressure exerted between the chuck and the friction drive member. For each chuck, an individual pressure fluid operated means may be provided controllably to effect movement of the respective chuck towards and away from the friction drive member.
Compensation for varying weight of a package on a chuck can be effected by corresponding adjustment of pressure of the pressure fluid medium applied to said fluid operated means.
a pressure varying valve in the pressure fluid supply can be adjusted in dependence upon the position of the chuck along its respective path.
Such compensation systems are already known, and they comprise in principle a cam surface fixed in the machine and a cam follower movable with the chuck, the cam follower being adapted to adjust setting of the appropriate pressure control valve during movement of the associated chuck along its path.
one of the chucks will have a component of its return motion extending in the same direction as the direction of rotation of the friction member, and the other will have a component of its return motion opposed to the direction of rotation of the friction drive member.
the invention is applied to a winding machine of the so-called "print friction" type.
a thread supplied to the machine contacts the friction drive member at a location upstream from the winding zone considered in the direction of rotation of the friction drive member.
means may be provided to ensure that a length of thread remains accessible near the winding zone for intersection by thread catching means on the incoming chuck.
guide means may be provided to deform the thread path between the drive member and the outgoing package so as to limit the wrap angle of the thread on the drive member.
auxiliary guide means Whether or not an auxiliary guide means will be required in any particular case depends on several factors, for example
auxiliary guide means to assist in achieving a compromise between the partially-conflicting constraints placed on the system as already described.
auxiliary guide means may be located above the friction drive member, and may be pivotable about a predetermined pivot axis when moving between a retracted position and an operative position.
the pivot axis may be movable towards the friction drive member as the auxiliary guide means is moved towards its operative positi.on, and the pivot axis may be moved away from the friction drive.member as the auxiliary guide means is returned to its retracted position.
means may be provided to limit movement of the outgoing chuck away from the friction drive member until after the thread has been intercepted by thread catching means on the incoming chuck; said means or suitable alternative thereto therefore limits the reduction in wrap angle on the drive member, produced by movement of the outgoing chuck towards its rest position, until after thread transfer has been achieved.
means may be provided to temporarily halt the outgoing chuck at an intermediate position on its path of movement until after the thread has been intercepted by thread catching means on the incoming chuck.
a temporary halt may be achieved by providing a two stage extensible and retractable means for moving the chuck, the stages being separately controllable.
the piston and cylinder means may comprise a pair of pistons independently movable relative to the cylinder means, one piston being secured to the swing arm and the other being secured to the part fixed to the headstock.
the cylinder means defines a limited degree of travel for one of the pistons (the "first piston”), thus defining a correspondingly limited degree of travel for the chuck along its path.
Means may be provided selectively to prevent relative movement of the other piston (the “second piston”) relative to the cylinder means while the first piston is moving through the limited degree of travel.
pressure fluid operated clamping means is provided within the cylinder means to clamp the second piston to the cylinder means while the first piston is moving through the limited degree of travel. Piston and cylinder means including such pressure fluid operated clamping means are commercially available.
the limited degree of travel can be arranged to correspond to the above-mentioned limited movement of the outgoing chuck away from the friction drive member.
the control system for the winder can be arranged to cause the first piston to move through the limited degree of travel when winding of thread on the corresponding chuck is broken off.
This outgoing chuck is then temporarily held at the position on its path reached upon completion of the limited degree of travel of the first piston until the thread has been intercepted by thread catching means on the incoming chuck.
Secure holding of the outgoing chuck in the required position is ensured by the means preventing movement of the second piston relative to the cylinder means, that is, in the preferred embodiment, the pressure fluid operated clamping means. After the transfer of thread to the incoming chuck has been completed, securing of the second piston to the cylinder means is cancelled and the outgoing chuck is permitted to return to its rest position by movement of the second piston relative to the cylinder means.
movement of the first piston relative to the cylinder means occurs only before and after a winding operation. All movements during a winding operation are effected by movement of the second piston relative to the cylinder means. This division of functions between the two pistons simplifies the requirements on the control system.
a pair of support members may be provided within the headstock, with a shaft extending between and mounted in said support members.
a swing arm is mounted on the shaft between the support members for pivotal movement about a longitudinal axis of the shaft, the swing arm carrying one of the chucks at a location spaced from the shaft. Preferably, the location is at the free end of the swing arm.
a second pair of support members, a second shaft and a second swing arm could be provided for the other chuck.
the second shaft extends between and is mounted in the same pair of support members as the first shaft.
the support members preferably extend substantially vertically from and are secured to a base member of the headstock.
the shafts preferably extend substantially horizontally between the support members, the first shaft being located near to the base member and the second shaft being spaced further therefrom.
first chuck mounting comprising the first shaft and a swing arm carried thereby as defined above
second chuck mounting comprising the second shaft and the swing arm carried thereby
these arrangements are preferably applied to both chuck mountings.
At least one self-aligning bearing is provided to mount the shaft in one of the support members.
the bearing is adjustable in position relative to the support members.
the arm preferably comprises a clamping means which clamps rigidly to a non-rotatable portion of the chuck.
the non-rotatable portion contains bearings enabling rotation of another portion of the chuck about a longitudinal chuck axis extending substantially parallel to the longitudinal axis of the support shaft.
Controllable moving means preferably pressure fluid operated means, is provided to cause controlled pivoting of the swing arm and the chuck about the shaft axis.
an intermediate member is also mounted upon the shaft so as to be pivotable about said shaft axis but fixed against sliding movement relative to the shaft.
the moving means is connected to the intermediate member to pivot the latter about the shaft axis, and a slidable connection is provided between the intermediate member.and the swing arm to cause the latter to pivot with the intermediate member while leaving the swing arm free to perform sliding movement relative to the shaft.
the rotatable portion of the chuck carries a brake disk which engages a brake shoe when the chuck is in its rest position.
the brake disk is preferably located rearwardly of the connection between the chuck and its swing arm.
the chuck includes an auxiliary drive means operable to rotate said rotatable portion of the chuck before the latter comes into driving relationship with the friction drive member.
the auxiliary drive means may comprise an electric motor, the stator being carried by the non-rotatable portion of the chuck secured to the swing arm. This auxiliary drive means may also be disposed rearwardly of the connection between the swing arm and the chuck.
the moving means which cause pivoting of the swing arms upon the shafts comprise a pair of extensible and retractable pressure fluid operating means, e.g. piston and cylinder units
the lines of action of the pressure fluid means are preferably crossed; e.g. assuming that the chucks are located one above the other, the pressure fluid means for the upper chuck may act between the base member of the headstock and the swing arm for the upper chuck, and the pressure fluid means for the lower chuck may act between an upper portion of the headstock and the swing arm of the lower chuck.
the lines of action of the pressure fluid operated means are preferably substantially aligned with the chucks when viewed longitudinally of the chucks in their rest positions.
the geometry of the system will normally be subject to predetermined constraints. For example, the minimum diameter of the chucks, and hence of bobbin tubes carried by the chucks, will usually be a given factor which is not subject to substantial alteration. The diameter of the friction drive roller may also be given, and not subject to substantial variation. The user of the machine will normally demand the largest possible package diameters within the smallest possible overall machine dimensions. Finally, it is desirable that the path of travel of each chuck between its rest position and its end winding position should be kept as short as possible. Clearly the final machine geometry in any individual case will be a compromise between these various factors, and still further factors may also have an influence.
the rest positions of the chucks can lie relatively close to their end winding position(s). If, however, there is no provision for rapid removal of a full package after return of a chuck to the rest position, then the latter must be spaced further away from the friction drive member in order to avoid interference between completed packages temporarily "stored" on the chuck in the rest position and new packages forming on a chuck in the winding position. If desired, automatic doffing systems of known types may be used to ensure rapid removal of full packages from chucks in their rest positions.
the line of contact between a package and the friction drive member wanders around the circumference of the latter as the chuck bearing the package moves back from its end winding position towards the rest position during the winding operation, i.e. there will be a variation in the wrap angle of the thread around the friction drive roller.
a wrap angle of at least 120° is maintained throughout a winding operation, this variation in wrap angle is not believed to introduce any undesirable effects.
the wrap angle is maintained higher than 150 throughout each winding operation.
the invention is applicable to chucks having thread catcher means of existing, well-known types. Suitable thread catchers are shown e.g. in U.S. Patent Specifications 3801038 and 4106711. In these patents, the illustrated thread catcher systems are built into the chuck structure. This is not essential. The thread catcher could be incorporated in a bobbin tube upon which a package is formed during the winding operation and which is removed from the chuck with the package and replaced by a new bobbin tube ready for winding of a further package. Further, the thread catcher means shown in the patents referred to incorporate or are associated with thread severing means for severing the outgoing package from the continuously delivered thread.
Such severing means are essential, or at least desirable, in the case of strong threads, usually those of high titer. They are not necessary in the case of weaker threads, generally of finer titer, where the thread can be caused to break between the outgoing package and the incoming chuck.
the thread catching means can also usually be of a simpler construction, e.g. a simple notch extending along a part of the circumference of the bobbin tube may provide an adequate thread catcher for such threads.
auxiliary guide means to cause the thread to perform a limited movement longitudinally of the chuck during the transfer operation. Such limited movements may be effected in order to bring the thread into operative contact with a thread catching means or a thread severing means or to provide a so called "transfer tail" upon the bobbin tube prior to starting formation of the main package thereon.
Such mechanisms are shown in US Patent Specifications 3920193 and 4019690. They are also applicable, without substantial alteration, to winders according to the present invention.
each thread may be composed of a mono-filament or may be a multi-filamentary structure.
a suitable control means including suitable timing means, must be provided to coordinate the movements of the outgoing and incoming chucks.
the changeover operation can be triggered by a suitable signal developed when a package reaches a predetermined size.
the control and timing system will then operate to cause movement of the chuck carrying the full packages in the return direction towards its rest position and to cause coordinated movement of the empty chuck towards its end winding position.
the same control and timing system will cause operation of the various auxiliary means described above to ensure that an appropriate length of thread is presented to thread catching means on the incoming chuck to enable it to take over the thread for formation of new packages.
Fig. 1 The machine illustrated in Fig. 1 is intended for winding synthetic plastics threads, e.g. textile threads, tire cord, textured carpet yarn. These thread types are given by way of example only, and are not intended to be exhaustive.
Figure 2 indicates three separate thread lines 10,12 and 14. The machine could be designed to handle any other number of thread lines. Each thread may be a mono-filament or a multi-filamentary structure.
the present winder comprises a main housing 16 containing drive motors, bearing systems, electrical, electronic and pneumatic control systems and connection points.
the housing together with its operational contents makes up a headstock.
Extending cantilever-fashion from the front of the housing is a friction drive roller 18 drivable by a suitable motor (not shown) about its longitudinal axis indicated by dotted line 20.
a traverse mechanism 22 Upstream from the friction roller, considered in the direction of travel of the thread into the machine, is a traverse mechanism 22, also driven by a suitable drive system (not shown) located in the housing 16.
mechanism 22 For each thread line, mechanism 22 comprises a suitable traverse unit which reciprocates the corresponding thread longitudinally of the drive roller axis.
each thread is laid upon the surface of the drive roller and it travels around the drive roller in contact with the surface thereof until it reaches the portion of the roller circumference indicated at Z in Figure 1.
the thread is transferred from the friction roller surface to the surface of a respective package which is forming upon a chuck 24 or 26.
the chucks also extend cantilever-fashion from the front of the housing 16, being mounted, by means to be described below, within that housing.
the system thus far described is of an already well known type, examples of which can be seen in U.S. Patent Specification 4283019. This system differs substantially, however, from the prior art in the manner in which chucks 24 and 26 are mounted and moved towards and away from the friction drive roller 18, and these mounting and moving systems will now be described.
Each chuck 24, 26 is carried upon the free end of a swing arm 28,30 respectively.
Arm 28 is pivoted upon a bearing shaft 32 fixed in the upper part of housing 16, and arm 30 is pivoted on a similar shaft 34 fixed in the lower part of the housing.
Arms 28 and 30 are each of a fixed length, and pivotable by any suitable means through a predetermined arc A (for arm 28) and B (for arm 30). These arcs may be equal or unequal as required.
the uppermost limit of the arc of swing of arm 28 defines a rest position 36 for the chuck 24 which is then spaced from the drive roller 22.
the lowermost limit of the arc B of arm 30 defines a corresponding rest position 38 for the chuck 26.
each chuck 24, 26 extends into the housing 16, and is connected therein to the end of its corresponding swing arm 28,30, the latter arms being located wholly within the housing.
the manner in which each chuck is connected to its swing arm is not shown in detail.
Each arm must however carry at its free end a bearing structure which supports the chuck while enabling rotation the chuck about its longitudinal chuck axis 25, 27 respectively.
the corresponding chuck 24, 26 will sweep out an arcuate path of movement, which is represented in Figure 1 by the lines 29, 31 representing the paths of movement of the chuck axes 25, 27 respectively.
each chuck Since the axis 20 of drive roller 18 is fixed in the machine frame, each chuck must move back along its movement path 29, 31 towards its respective rest position to allow a space between the chuck surface and the drive roller 18 as packages build up on the bobbin tubes. This return movement can be controlled by appropriate control of movement of the swing arm 28, 30 respectively.
the locations of the shafts 32 and 34 in relation to the axis 20 may be adjusted so that each chuck 24, 26 first contacts the drive roller 18 at substantially the same angular location on the circumference of the roller. This is however, not absolutely necessary.
the "wrap angle” is the angle subtended on the axis of the friction roller by radii extending from the axis to the points of first and last contact of the thread with the roller as viewed longitudinally of the roller, said angle containing the portion of the roller circumference contacted by the thread during a winding operation.
the point of last contact of the thread with the roller (a) during a given winding operation and (b) immediately thereafter, during changeover.
the winding zone Z can be viewed as the zone of maximum designed displacement of the point of last contact of the thread with the friction roller for normal winding operations.
the point of last contact of the thread with the friction roller may wander outside the winding zone Z as will be further described below.
the winding zone Z should extend over only a limited extent of the roller circumference adjacent or, preferably, containing the horizontal plane through axis 20.
a set of bobbin tubes carried in use by the arm 24 will engage the surface of the drive roller 18 within the winding zone Z. Rotation of the drive roller 18 in the direction of the arrow shown in Figure 1 then causes corresponding rotation of the chuck, and thread reaching the winding zone Z is laid upon the bobbin tubes and built into packages. As the packages build up upon the bobbin tubes on chuck 24, arm 28 swings through the arc A in the return direction towards the rest position 36.
auxiliary guide member 44 which is mounted for pivotable movement on pivot axis 46.
guide member 44 is pivoted in a clockwise direction as viewed in Figure 4 (by any suitable operating means, not shown) to an operative position shown in the Figure, in which the guide means deforms the thread path between drive roller 18 and package 40. This deformation is such as to decrease or maintain the wrap angle of thread on the drive member 18 and to ensure that thread extending between the guide member 44 and the drive member 18 is readily accessible to the incoming chuck 26.
member 44 is pivoted in a counterclockwise position about axis 46 to a retracted position in which it does not interfere with any of the normal operations of the machine.
the actual location of the intermediate position along the path of chuck 26 depends upon the dimensions of the package 42. Allowance must be made for formation of packages of varying dimensions according to the requirements of the user of the machine, and also the machine must be able to cope with fault conditions in which a winding operation must be broken off before completion of the desired package. Thus, the thread length T must be accessible as described over a range of conditions varying from a virtually bare bobbin (for example, a "laboratory package" intended for yarn tests) to a package of the maximum dimensions for which the machine is designed.
means to be described below, is provided to ensure that chuck 26 halts after travelling through a controlled length of its return path after breaking off of a winding operation, regardless of the position of the chuck axis along the path at the time when the winding operation is broken off.
FIG. 5 This latter Figure corresponds with Figure 1, but the front plate of the housing 16 and the parts forward of that plate have been removed to show, diagrammatically, elements within the housing.
the drive motor for the traverse mechanism is indicated at 44
the drive shaft for the friction drive roller 18 is indicated at 46.
the pivot shafts 32 and 34 and the swing arms 28 and 30 are also shown.
Unit 48 is pivoted at one end 52 to the housing 16 and at its other end to a projection 54 fixed to or integral with the arm 28.
unit 50 is pivoted to the machine frame at 56 and to a projection 58 . on the arm 30.
Extension of unit 48 moves chuck 24 from its rest position to the end winding position, and retraction of the unit causes return to the rest position.
Extension and retraction of unit 50 has a similar effect for chuck 26.
the shape of the surface on cam member 64 must be adjusted in dependence upon the type of thread being wound and the dimensions of the package required.
the weight of package will be a function of the diameter thereof; the diameter of the package will determine the position of the chuck on its return path, and hence the position of the cam follower 62 on the surface of the cam member 64; the latter elements adjust the pressure in unit 48 in dependence upon package diameter to give the desired contact pressure between the package and the friction drive roller 18.
the unit 48 is subjected to internal pressure in one chamber thereof such as to urge the chuck 24 towards the friction drive roller and produce a predetermined contact pressure therebetween.
the increasing weight of the package during the winding operation can be compensated by gradually increasing pressure in a second chamber of the unit 48, opposing the initial pressurisation thereof and the weight of the package.
Arm 30 is fitted with a similar compensation system comprising valve 66, cam follower 68 and cam member 70. It will be appreciated, that in this case pressure in the unit 50 must be controlled to urge arm 30 and chuck 26 towards the friction drive roller 18 as the package weight increases.Otherwise, however, the compensation system is essentially the same as that described for arm 28 and chuck 24, and detailed description is believed to be unnecessary.
Figure 5 also illustrates a mechanism for halting chuck 26 after it is moved a substantially predetermined distance along its return path after breaking off a winding operation.
This mechanism comprises a flexible element, e.g. a wire 72, which is secured at one end to the projection 58 on arm 30.
the wire is wound upon a take up device 74 fixed in the housing 16.
a brake mechanism 76 which is triggerable in response to the overall machine control system.
the control system will cause unit 50 to withdraw arm 30 in a counterclockwise direction so that chuck 26 moves towards its rest position.
the control system energizes brake mechanism 76 to halt the take up device 74 and thus halt the movement of chuck 26 along its return path. This ensures the production of the required length of thread T as shown in Figure 3.
brake 76 is released, and unit 50 is permitted to return arm 30 fully in the counterclockwise direction, thus returning chuck 26 to the rest position.
FIGs 7 to 14 inclusive show a practical embodiment of the invention. As far as possible, the reference numerals used in these Figures correspond with those used in the earlier Figures which were used primarily to explain the novel principles involved.
Figure 8 shows in perspective the relative physical configuration of some of the main elements of the winder. Chucks 24, 26 project cantilever-fashion from the front of a headstock housing 16, the structure of which will be further described below.
Friction roller 18 is carried at one end in the head stock housing, and at the other end in a bearing member 100, 101 which also projects cantilever-fashion from the front face of housing 16.
the traverse mechanism is hidden behind bearing member 100 in the perspective view.
the bearing member 100, 101 can be omitted if desired, the rigidity of the friction roller structure being increased to compensate for the omission of the outboard bearing.
FIG. 8 shows the machine in its non-operating condition, the chucks being illustrated in their respective rest positions.
Each chuck is shown carrying two bobbin tubes 102 and the friction roller has two corresponding treated surfaces 104 designed to form a good driving connection with packages building up on the bobbin tubes 102.
Each chuck has two thread catching/severing structures, which will not be described in detail in the present application, but which are formed in accordance with US Patent Specification Nr. 4106711.
one such structure is located in alignment with the gap 106 between the bobbin tubes 102, and the other one is provided at the location 108 outboard of but adjacent to outer bobbin tube 102.
the catching/severing structures of the chuck 24 are provided at corresponding locations.
the front face of housing 16 is provided by a plate 110, which provides a mere facing for the front of the machine and is not a load bearing part thereof.
Plate 110 has two arcuate slots 112, 114 respectively representing the respective paths of movement of chucks 24, 26. Where these slot converge, the drive shaft l16 of friction roller 18 can be seen extending into the housing 16 to a drive motor (not shown) mounted therein on a rearward support member 132 ( Figure 9) which will be described further below.
the generally triangular shaped members 118 are push-out shoes, each of which is reciprocable longitudinally of its associated chuck 24, 26 respectively, by means of a respective operating shaft 120.
Each shoe 118 engages behind the bobbin tubes 102 on the associated chuck, when the latter is in its rest position as shown, and can be moved along the chuck to force the bobbin tubes (and packages carried thereby) off the chuck during a doffing operation. This is a standard doffing mechanism, and will not be described in detail herein.
the auxiliary guide 44 used for deforming the thread length L can also be seen in Figure 8.
An operating mechanism for this guide will be described below with reference to Figure 13.
Rollers 122, carried on an arm 124 fixed to the bearing member 100 above the friction drive roller 18, are used as will be described below, to assist in manual threading up of the machine when it is first put in operation.
a hood 126 extends from the housing 16 forwardly over the operating region in front of that housing.
the main load bearing elements of housing 16 comprise a base plate 128, a pair of upright plates 130, 132 respectively and an upper plate 134 secured to the upper ends of the plates 130, 132. Additional bracing struts, such as 135 ( Figure 8) may be incorporated into the housing as required, but will not be referred to further herein.
uprights 130, 132 extend across approximately half the width of the machine on the right hand side thereof as viewed from the front. The left hand side of the machine is left free for movement of the chucks and the parts associated therewith.
Figure 10 shows the swing arm 28 and the mounting therefor. It will be understood that the swing arm 30 and the mounting therefor are the same in all important respects.
Figure 10 shows shaft 32 mounted with its longitudinal axis 33 substantially horizontal between uprights 130 and 132. Mounting of the shaft is effected on reduced end portions 136, 138 thereof.
a ball bearing unit 140 is provided between shaft portion 136 and upright 130, and is secured to the shaft and to the upright so as to prevent movement of the shaft to the right as viewed in Figure 10.
the outer race 139 of this unit has a part-spherical inner face centred on the point C which lies on the axis 33. Unit 140 therefore permits orientation of axis 33 to lie at any disposition within an imaginary cone (not shown) the apex of which lies at point C.
a roller bearing unit is provided between shaft portion 138 and upright 132, and is secured to the shaft and the upright so as to prevent movement of the shaft to the left as viewed in Figure 10.
Unit 142 comprises a flanged annular support 144 carrying an outer bearing race which is formed in two parts 146, 148 respectively. Parts 146 and 148 contact each other on a part-spherical interface 150 having a center on the axis 33. Parts 146 and 148 are relatively slidable at the interface 150 so as to provide a limited degree of "universal" relative movement of those parts.
Unit 142 is mounted in an opening 143 in upright 132 by means of bolts, such as bolt 145, passing through the flange 144 and the upright 132. Opening 143 has a diameter larger than the external diameter of the cylindrical portion of unit 142 which is located in it in use, and the bolt holes in upright 132 also leave play (not shown) around the bolts.
the position of unit 142 is therefore adjustable relative to upright 132 to enable adjustment of the orientation of axis 33 within the imaginary cone described above.
Arm 28 is mounted on shaft 32 between the uprights 130, 132 by means of a ball bearing 152.
the dimension of arm 28 longitudinally of shaft 32 is less than the spacing between uprights 130, 132, so that the arm is slidable longitudinally on the shaft 32, for a purpose to be described hereinafter.
arm 28 At its free end, arm 28 carries two clamping jaws 154 which clamp rigidly onto a housing portion 156 of the chuck 25.
Pivoting of arm 28 about the axis 33 is effected by a piston and cylinder unit, the cylinder of which is shown at 158 in Figure 8 and the piston of which is connected by rod 160 (Figure 8) to the arm 28 by way of an intermediate member 162 ( Figure 10).
Member 162 is mounted on shaft portion 138 which extends rearwardly beyond upright 132 for this purpose.
a key 164 is provided between intermediate member 162 and shaft 32 so that member 162 is fixed against both sliding and pivotal motion relative to the shaft.
member 162 carries projections 166 by means of which a pinned knuckle-joint (not shown) is made with the connecting rod 160.
a rod 168 is rigidly secured at one end to the intermediate member 162 and extends forwardly thereof into a bearing bush 170 secured to the underside of arm 28.
Rod 168 is freely slidable within bush 170 as arm 28 slides longitudinally of shaft 32.
rod 168 secures arm 28 to intermediate member 162 so that both will pivot together about axis 33.
the sliding motion of arm 28 on shaft 32 is produced by selective pressurization of an auxiliary piston and cylinder unit, the cylinder 172 of which is secured to the underside of arm 28 at pivot 174 and the piston (not shown) of which is connected by rod 176 and a suitable pin-joint (not shown) to rod 168.
the non-slidable intermediate member 162 also carries the cam follower 62 and pressure reducing valve 60 described above with reference to Fig. 1.
FIG 11 shows additional detail of the end portion of chuck 24 within housing 16. Again, it will be understood that the corresponding end portion of chuck 26 is the same in all important respects.
Chuck housing 156 is shown to comprise a sleeve-like wall structure 178 which is not shown in detail since it forms no part of thus invention.
the wall carries the outer race 180 of a ball bearing 182 by means of which a coaxial rotatable portion (shaft 184) of the chuck is mounted in the non-rotatable portion 156.
the inner race 186 of the bearing is mounted on a reduced end portion 188 of the shaft.
Rearwardly of the jaws 154 wall 178 has an outwardly projecting flange 190 joining a semi-cylindrical portion 192.
portion 192 When viewed longitudinally of the chuck axis 25 (see the reduced scale detail Figure 12) portion 192 is partially cut away so that brake disk 194 stands radially proud therefrom. Disk 194 is keyed to shaft portion 188 at 195 and is rotatable with the shaft. Where it projects from portion 192, disk 194 engages a brake shoe 196 ( Figure 7) when chuck 24 is in the rest position. Shoe 196 is carried by support element-198 secured to the underside of plate 134 of housing 16. The corresponding structure 200, for chuck 26,is carried by base plate 128 of the housing.
portion 192 carries a cap 202 fixedly secured thereto.
Cap 202 carries the stator windings 204 of an accelerating electric motor, the rotor windings 206 of which are secured to the shaft 184 of the chuck by way of an extension on the brake disk 194. By means of flexible leads (not shown) this motor can be energized after the chuck has been moved away from the brake shoe 196 and before it reaches its end winding position, so that the chuck is accelerated to a desired rotational speed before reaching the latter position.
Cap 202 carries a connection socket 208 for flexible leads feeding a pressure medium (pneumatic or hydraulic) to the interior of the chuck structure to operate a bobbin clamping mechanism therein.
Control of supply of pressure fluid via socket 208 can be effected by means responsive to contact of the chuck with the brake shoe, for example as described in US Patent Specifications 3701492 and 4036446.
the rotatable shaft 184 is secured to a rotatable shell rightwardly of the chuck portion shown in Fig. 11.
This shell is of approximately the same outer diameter as wall 178 which terminates rightwardly of Fig. 11 to leave space for the shell.
the latter provides a package receiving structure and houses the operating parts of the chuck such as bobbin clamping mechanisms.
the shell and the other mechanisms are conventional.
cylinder 158 is connected to a boss 210 on the base plate 128 by means of a knuckle-joint (not seen).
the cylinder 212 of the piston and cylinder unit which operates chuck 26 can also be seen in this Figure, but the rod connecting the piston to the arm 30 is hidden behind cylinder 158.
Cylinder 212 is connected to a boss 214 on the underside of plate 134 by means of a knuckle-joint (not seen).
the lines of action of these two main piston and cylinder units are represented by the chain dotted lines 216, 218 respectively in Figure 7.
Line 216 represents the line of action of the first piston and cylinder unit to hold chuck 24 in its rest position, the unit being pressurized for this purpose.
Line 218 represents the initial line of action of the second piston and cylinder unit as it draws chuck 26 upwardly from its rest position, the unit also being appropriately pressurized for this purpose. Movement of the chucks to the winding position involves in each case a contraction of the associated piston and cylinder unit. The lines of action of these units swing through arcs corresponding with the arcs of movement of their respective chucks 24, 26. It will be seen from Figure 7, however, that the lines 216, 218 cross when viewed longitudinally of the chucks 24, 26 and are located in general alignment with the chucks when viewed in the same direction.
FIG 13 shows in further detail the operating mechanism for the auxiliary guide 44 shown in Figure 7 and Figure 8.
the purpose of this mechanism is to move guide 44 between its retracted position (shown in full lines) and its operative position (shown in chain dotted lines).
This movement involves a pivotal component occurring in a clockwise direction about the pivot shaft 220 to which guide 44 is secured by means of lug 222.
Shaft 220 is itself vertically movable along a guide slot 224 provided, for example, in facing plate 110 or in a part secured thereto.
a similar guide slot can be provided upon the member 101 ( Figure 8) at the other end of guide 44. Slots 224 define a path of movement for shaft 220 towards and away from the friction roller 18.
Movement of guide 44 is effected by a piston and cylinder unit, the cylinder 226 of which is pivoted at 228 to a frame member 230 providing part of the bearing member 100.
the piston (not shown) is connected via rod 238 to one end of a link 240, the other end of which is pivoted at 242 to another lug 244 secured to guide member 44.
Link 240 is pivotable around shaft 246 which extends in a fixed position between housing 16 and the outboard bearing member 101.
Extension and retraction of the piston and cylinder unit causes movement of guide 44 between its retracted and operative positions shown in Figure 13, the retracted position being such that the guide does not interfere with the normal winding operation.
Slots 224 may be unnecessary in some machine designs depending upon machine geometry.
the same mechanism locates the thread in a substantially predetermined position relative to the chuck so that the thread over- winds its package 42 at a substantially predetermined location thereon.
the thread catching/severing devices 106, 108 are built into the chuck structure and lie adjacent the ends of the bobbin tubes 102. In order to align these devices 106, 108 with the corresponding threads 12, 14, it is necessary to retract the chuck by an appropriate distance into the housing 16, as shown for the chuck 24 in Figure 14.
chuck 24 is shown in its extended position, and it can be drawn leftward into the retracted position shown in Figure 14 by suitable pressurization of the cylinder 172 ( Figure 10) to force the latter leftward along the rod 176, bush 170 sliding simultaneously leftward along rod 168.
a further auxiliary mechanism moves the. thread through a limited distance longitudinally of the chuck, causing catching and severing of the thread as described in United States Patent Specification Nr. 4106711. Cylinder 172 is then pressurized so as to force it rightward as viewed in Figure 10, chuck 24 thus moving from the retracted position shown in Figure 14 to the extended position shown in Figure 10. Due to axial movement of the auxiliary mechanism together with this axial movement of the chuck, a transfer tail is wound upon each bobbin tube 102, e.g. as described in U.S. Patent Specifications Nr. 3920193 and 4019690, which latter also describe auxiliary mechanisms for controllably removing thread from the traverse units. The transfer tail is wound on an end portion of the bobbin tube 102 lying beside the normal package traverse. When chuck 24 reaches its extended position, the thread is returned to its traverse unit, and normal winding of a package begins.
the catching/severing devices 106, 108 may be omitted and simple slots may be provided in the bobbin tubes 102 as already well known in this art. Each slot catches a thread as the latter is moved over it by the auxiliary mechanism referred to above, and the fine thread breaks between the new bobbin tube and the outgoing package.
the auxiliary mechanism may be adapted to wind a transfer tail, and the axial movements of the chucks may then be omitted.
the axial movement of the chucks may also be omitted where the winder is intended to deal with strong threads and catching/severing units are built into the chucks, if suitable guiding means are substituted for the axial movement.
guide 44 may be adapted to hold the upstream portion of thread length L at the desired location on packages 40 while a suitable auxiliary mechanism moves the downstream portion thereof axially of the chuck 26 into alignment with catching/ severing devices 106, 108 thereon.
An additional guide must also be provided to hold the upstream portion of thread length T (Fig. 3) at the desired location on package 42 in a changeover of the type shown in Figure 3. It is preferred, however, not to incorporate such guide systems, as control thereof is complex and it is desirable to maintain the space around the friction roller 18 as clear as possible during the changeover operations.
the machine Upon pressing of a start button, the machine now operates automatically to carry out a "changeover" of the type illustrated in Figure 4, that is, with the lower chuck 26 moving from its rest position into its end winding position and taking up the length of thread between guide 44 and friction roll 18.
the severed threads most of which extend upstream from guide 44 to the guide rollers 122, is taken up by the aspirator.
the winding operation now proceeds normally, and further changeover is effected automatically as already described. It is not essential to start up the machine after shut down by using the lower chuck to take up a thread length. However, it is normally necessary to provide additional guides to assist the attendant to locate the thread in the desired position for initial take up by one of the chucks.
the auxiliary guide 44 is already available and can be used for this purpose, and the additional guide rollers 122 can be conveniently located under the machine hood 126 where they do not interfere with operations in the "working zone" of the machine.
Axial shifting of the thread by means of guide 44 can prove especially useful in the string-up operation where thread vibration can be caused by the air pistol.
Figure 15 shows to scale a "geometry" suitable for a machine of a particular type.
the user may not have automatic doffing equipment available.
the machine attendants may not be available "on call” to remove full packages from the machine.
the machine is designed to store a full package of maximum dimensions in either the upper or the lower rest position without interference with a winding operation forming a full package of maximum dimensions on the other chuck. There must also be no interference with return movement of the other chuck to its rest position. If the package on the first chuck has not by then been removed, the machine will shut down automatically. There is, of course, nothing to prevent an automatic doffing mechanism being applied to the winder shown in Figure 15 despite its "storage" ability.
the reference numerals used in Figure 15 correspond with those used in the other Figures.
the part indicated at 129 is a balance foot projecting forwardly from the housing 16 on the right hand side thereof as viewed from the front.
the balance foot is omitted on the left hand side in order to leave room for a full package of maximum dimensions in the lower rest position.
the machine is illustrated at the completion of winding of a full package on the lower chuck, a full package being "stored” in the rest position 36 on the upper chuck.
the rest position of the lower chuck lies immediately below rest position 36, the axis of the lower chuck then lying at the intersection of the path 31 with the horizontal line 250 in Figure 15.
the following dimensions are given by way of example only -
the winding zone on the friction roller must include the horizontal plane through the roller axis.
the winding zone could be located on the underside of the roller (include the vertical plane through the roller axis).
a cantilevered chuck tends to bend along its length as package weight increases, especially when a long chuck is used. Location of the winding zone to include the horizontal plane lessens the effect of this bending on drive contact between the roller and package.
each chuck structure 24,26 preferably includes an accelerating motor for driving the chuck to a desired rotational speed after it leaves its rest position and before it arrives in its end winding position.
each chuck is temporarily halted on its path of movement towards the end winding position while the accelerating motor is operated to drive the chuck to the required speed.
Figure 16 shows the piston and cylinder means which operates the lower chuck 26 by acting (indirectly) upon the swing arm 30.
the cylinder means 212 comprises two chambers 252 and 254 respectively separated by a partition 256 fixed relative to the cylinder.
Chamber 252 is bounded at its upper end (remote from partition 256) by the end wall of the cylinder.
Chamber 254 is bounded at its lower end by a second partition 258 which is also fixed relative to the cylinder.
An auxiliary chamber 260 is defined between partition 258 and the lower end wall of the cylinder.
a piston 262 is reciprocable in chamber 252 and is connected by rod 264 and knuckle-joint 214 to the under side of plate 134.
a piston 266 is reciprocable in chamber 254 and is connected by the rod 268 to the swing arm structure 30.
Rod 268 passes through auxiliary chamber 260.
a clamping means in the form of a frusto-conical wedging member 270, having a wedging surface tapering towards the lower end wall of the cylinder.
Wedging member 270 is firmly fixed to the cylinder.
a plurality of balls 272 is located between member 270 and rod 268. The balls can be acted upon by either of two clamp operating pistons 274 and 276 respectively. Since the operation of this clamp forms no part of the present invention, being a commercially available article, the details of the manner in which clamping pistons 274 and 276 act upon balls 272 are not illustrated or described.
piston 274 when piston 274 is operated to urge balls 272 towards the lower end wall of the cylinder, rod 268 will be clamped rigidly to the cylinder.
piston 276 when piston 276 is operated to move balls 272 away from the lower end wall of the cylinder, rod 268 and hence piston 266 will be free to move relative to the cylinder.
Figure 16 also illustrates valves and relays of a control means suitable for controlling pressurization of the piston and cylinder means by a pressure medium from a suitable source to carry out the operating cycle for chuck 26 described above.
relay SO ( Figure 17) must be operated (by manual operation of a button on a control panel - not shown) to pressurize cylinder 316 thereby releasing mechanical safety clamps 318 which otherwise prevent movement of chucks 24,26. Clamps 318 are automatically biased to their operative positions. Relay SO remains operated until the machine is shut down once again (at time T21 shown in Figure 18).
Relay Sl ( Figure 16) controls operation of valve SlV to pressurize and exhaust the upper portion of chamber 252, that is the portion above piston 262.
the cylinder is moved upwards relative to the fixed piston 262 until the latter engages partition 256. This corresponds to the movement of chuck 26 away from its rest position into its acceleration position (when piston 262 engages partition 256).
Reference to the timing diagram in Figure 18 shows that the above described movement of chuck 26 to its accelerating position is the first major step (starting at time Tl) in start up of the machine.
Relay Sl and the other relays which will be described below, are operated in a timed sequence under the control of a suitable clock means (not shown) the timing sequence beginning with operation of relay SO at time T 0.
the timer After allowing sufficient time for acceleration of the chuck, the timer operates relay S3 at time T3, and this relay in turn operates valve S3V to pressurize the lower portion of chamber 254, that is the portion beneath piston 266.
the clamping system is in its release condition, so that piston 266 is driven upwardly relative to the cylinder, thereby drawing the chuck into its end winding position.
relay S4 is operated to pressurize cylinder 226 (already described with reference to Figure 13) thereby moving auxiliary guide 44 to its operative position (see Figure 4) .
valve S3V When chuck 26 has arrived in its end winding position (time T4), relay S3 drops out, permitting valve S3V to switch to a condition in which pressurization of the lower portion of chamber 254 is controlled via the adjustable pressure reducing valve 66.
the instantaneous setting of valve 66 is determined by a cam-follower 68 which engages a cam 70 fixed in the machine headstock, so that movement of swing arm 30 along its return path will be accompanied by movement of cam-follower 68 along cam 70, thereby continuously adjusting the setting of valve 66 and pressurization of the lower portion of chamber 254.
Valve 66 is connected in circuit with valve S3V at time T3 by operation of switch 320 in response to operation of AND gate 322 which is connected (by means not shown) to relays S4 and S2. Switch 320 remains in this set condition until reset via line 324 as will be described later.
relay S5 is operated to pressurize cylinder 280 thereby moving transfer tail guide 282 longitudinally of the chuck axis.
Guide 282 first moves the thread 14 into engagement with the catching/cutting zone on chuck (as already described with reference to Figure 14) and then begins formation of a transfer tail between the catching zone and the region upon which the final package will be formed.
relay S2 drops out at time T5, causing pressurization of cylinder 172 to move the chuck 26 to its extended position. Formation of a transfer tail by joint movement of an auxiliary guide and of the chuck is described, for example, in our prior U.S. Patent 3920193 or 4019690.
Chuck 26 is now (time T6) ready to begin winding of a package, and relays S4 and S5 also both drop out.
Auxiliary guide 44 returns to its non-operative position, under the bias of a spring provided in cylinder 226, and transfer tail guide 282 returns to its starting position (to the left in Figure 16) under the influence of a spring provided in cylinder 280.
chuck 26 moves gradually back along its path 31 ( Figure 7) towards its rest position, contact being maintained between the package building up on the chuck and friction drive roller 18.
Piston 266 moves correspondingly downwardly in its cylinder.
the control of the length of filament wound into a package is independent of the system shown in Figure 16.
Length measuring devices are well known in this art, and will not be described herein.
the length measuring system can be initiated, for example, by a position sensor 284 ( Figure 16) located adjacent the pivot mounting 34 of swing arm 30.
the length measuring system will normally be adjustable, so that the user can determine the size of package built up during the winding operation.
the piston 266 may therefore be at any of a number of different positions along the cylinder at the time of breaking off the winding operation, the particular position being dependent upon the size of package chosen by the end user.
the cylinder means 158 shown in Figure 17 also comprises two chambers 286 and 288 respectively, separated by a partition 290 fixed relative to the cylinder.
a piston 292 is reciprocable in chamber 288, and is connected by a rod 294 to a knuckle-joint 210 on the base plate 128 of the headstock.
a piston 296 is reciprocable in chamber 286 and is connected by a rod 160 (also described with reference to Figure 8) to the swing arm structure 28.
Chamber 288 is bounded at its lower end (remote from partition 290) by the lower end wall of the cylinder.
Chamber 286 is bounded at its upper end by a second partition 298 which is also fixed relative to the cylinder.
An auxiliary chamber 300 is defined between partition 298 and the upper end wall of the cylinder.
Auxiliary chamber 300 contains a clamping means or system similar to that already described with reference to Figure 16, but substantially simpler.
the clamping system comprises a wedging member 302, a plurality of balls 304 and an auxiliary piston 306 for releasing the clamping effect of the balls 304 around rod 160.
the system is such that the clamp is automatically effective unless piston 306 is specifically operated to release it. This is a safety Measure to ensure that the upper chuck 24 cannot simply fall under its own weight against friction drive roller 18 in the absence of pressurization of the chamber 286.
the piston and cylinder means shown in Figure 17 is in the fully extended condition there illustrated. Chambers 286 and 288 are pressurized, so that the cylinder is in its raised position relative to the fixed piston 292, and piston 296 is in its fully raised position relative to the cylinder.
the first step in preparation of chuck 24 prior to breaking off winding on chuck 26 is the operation of relay S6 (at time T7) to vent chamber 288, permitting partition 290 to move downwards against piston 292. Chuck 24 therefore moves away from brake shoe 196 to its accelerating position.
a position sensor 308 adjacent pivot mounting 32 senses the arrival of chuck 24 in its accelerating position, and initiates operation of the acceleration motor built into the chuck structure.
relay S7 is operated at time T8 to pressurize the upper portion of chamber 286 (above piston 296) and vent the lower portion of that chamber.
relay S8 is operated to pressurize piston 306 to urge it upwards against the balls 302, releasing the safety clamp on rod 160. Piston 296 is therefore now free to move downwardly along the cylinder under the effect of the pressurization in the upper portion of chamber 286.
relay S9 is operated to pressurize the cylinder 172A associated with swing arm 28 to draw chuck 24 into its retracted position.
piston 266 Regardless of the instantaneous position of piston 266 in the cylinder, therefore, it is secured to the cylinder and must follow the movement of the latter as it travels downwardly relative to the fixed piston 262 under the weight of the package 42 ( Figure 3) carried by the chuck 26.
the downward movement of the cylinder continues until piston 262 reaches the upper end wall of the cylinder.
the cylinder and piston 266 travel through a predetermined distance corresponding to the spacing between partition 256 and the upper end wall of the'cylinder.
Swing arm 30 travels through a corresponding arc and chuck 26 moves through a corresponding portion of its path 31, to create the thread length T ( Figure 3).
the timer After allowing sufficient time for chuck 26 to withdraw its packages sufficiently from friction drive roller 18, the timer operates double relay Sll (Fig. 17) at time T10. These relays operate the corresponding switches S11V to provide additional pressure to the upper portion of chamber 286 thereby driving chuck 24 more rapidly downwardly towards its end winding position.
relay S5 Fig. 16
time Tll time Tll
relay S9 Fig. 17
time T12 time T12
valve S7 takes over pressurization of chamber 286, control of such pressurization now being effected via adjustable pressure reducing valve 66A? cam-follower 68A and cam 70A which correspond with the similarly numbered parts of the weight compensation system already described for chuck 26.
Packages now begin to form on the upper chuck, which begins its return movement along the path 29.
relay S4 ( Figure 16) has been operated at time T10 during the final stage of movement of chuck 24 towards its end winding position.
relays S4 and S10 together initiate operation of a time delay mechanism 312 details of which will not be described herein.
the time delay mechanism operates automatically after a predetermined delay to cancel operation of the auxiliary clamping piston 274 and to operate instead the release piston 276 so that rod 268 is left free for further movement relative to its cylinder.
Relay S4 also incidentally causes operation of the auxiliary guide 44, but this is of no significance in the transfer operation illustrated in Figure 3 and described immediately above.
a position sensor 314 ( Figure 17) is associated with the pivot mounting 32 of swing arm 28 and initiates operation of a length measuring system as soon as chuck 24 reaches its end winding position.
the measuring system once again initiates operation of the timer to begin the series of operations already described for the relays Sl to 5 so that the lower chuck is brought into its end winding position and begins to take up filament.
the control system may include suitable sensors, of well know types, to indicate thread breaks or other faults and initiate appropriate control cycles, e.g. premature breaking off of winding and/or shut down of the machine.
pressure fluid containing piston and cylinder units can be provided between the swing arms and suitable abutments in the headstocks. These units are additional to the pressure fluid operated arm moving cylinders, the additional units serving as damping means. Such damping units are generally well known and will not be described in detail. By way of example only, flow of pressure fluid between chambers within the cylinder may be caused by movement of the piston and may the throttled to give the required damping.

Landscapes

Replacing, Conveying, And Pick-Finding For Filamentary Materials (AREA)
Winding Filamentary Materials (AREA)

EP19820107022 1981-09-03 1982-08-04 Fadenaufwickelmaschine Expired EP0073930B1 (de)

Applications Claiming Priority (6)

Application Number	Priority Date	Filing Date	Title
GB08126692A GB2105378A (en)	1981-09-03	1981-09-03	Thread winding machine
GB8126692		1981-09-03
GB8128122		1981-09-17
GB8128122		1981-09-17
GB8133836		1981-11-10
GB8133836		1981-11-10

Publications (3)

Publication Number	Publication Date
EP0073930A2 true EP0073930A2 (de)	1983-03-16
EP0073930A3 EP0073930A3 (en)	1984-03-07
EP0073930B1 EP0073930B1 (de)	1986-12-03

Family

ID=27261290

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP19820107022 Expired EP0073930B1 (de)	1981-09-03	1982-08-04	Fadenaufwickelmaschine

Country Status (5)

Country	Link
EP (1)	EP0073930B1 (de)
BR (1)	BR8205152A (de)
DE (1)	DE3274541D1 (de)
IE (1)	IE54100B1 (de)
IN (1)	IN158954B (de)

Cited By (1)

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Publication number	Priority date	Publication date	Assignee	Title
WO2023027651A3 (en) *	2021-08-26	2023-08-17	Domeks Maki̇ne Anoni̇m Şi̇rketi̇	Method providing the winding of the cable in automatic cable winding machines and a flap apparatus thereof

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Publication number	Priority date	Publication date	Assignee	Title
US4598876A (en) *	1985-03-01	1986-07-08	Rieter Machine Works Limited	Winding machine for filament packages equipped with package screening means
GB8531151D0 (en) *	1985-12-18	1986-01-29	Rieter Ag Maschf	Winder layout
GB8601453D0 (en) *	1986-01-22	1986-02-26	Rieter Ag Maschf	Thread guiding & screening elements
DE59005704D1 (de) *	1989-04-06	1994-06-23	Rieter Ag Maschf	Spulautomat.

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US2789774A (en) *	1953-11-10	1957-04-23	Celanese Corp	Textile winding
US3310247A (en) *	1964-10-26	1967-03-21	Du Pont	Continuous yarn windup mechanism
US3758042A (en) *	1971-10-14	1973-09-11	Petty Machine Co	Continuous yarn winding apparatus
DE2065653B2 (de) *	1969-10-03	1977-01-13	Ausscheidung aus: 20 48 416 Maschinenfabrik Rieter AG, Winterthur (Schweiz)	Verfahren zum fuehren und trennen des fadens beim automatischen wechseln der spulen einer aufwickelvorrichtung sowie aufwickelvorrichtung zum durchfuehren des verfahrens
DE2827178A1 (de) *	1977-06-24	1979-01-11	Karlsruhe Augsburg Iweka	Vorrichtung zum aufspulen textiler faeden
US4166587A (en) *	1978-06-01	1979-09-04	Industrie-Werke Karlsruhe Augsburg Aktiengesellschaft	Method and aparatus for transferring yarn on a nearly full package to an empty bobbin

1982
- 1982-08-04 DE DE8282107022T patent/DE3274541D1/de not_active Expired
- 1982-08-04 EP EP19820107022 patent/EP0073930B1/de not_active Expired
- 1982-08-20 IE IE201582A patent/IE54100B1/en unknown
- 1982-09-02 BR BR8205152A patent/BR8205152A/pt unknown
- 1982-09-03 IN IN1026/CAL/82A patent/IN158954B/en unknown

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US2789774A (en) *	1953-11-10	1957-04-23	Celanese Corp	Textile winding
US3310247A (en) *	1964-10-26	1967-03-21	Du Pont	Continuous yarn windup mechanism
DE2065653B2 (de) *	1969-10-03	1977-01-13	Ausscheidung aus: 20 48 416 Maschinenfabrik Rieter AG, Winterthur (Schweiz)	Verfahren zum fuehren und trennen des fadens beim automatischen wechseln der spulen einer aufwickelvorrichtung sowie aufwickelvorrichtung zum durchfuehren des verfahrens
US3758042A (en) *	1971-10-14	1973-09-11	Petty Machine Co	Continuous yarn winding apparatus
DE2827178A1 (de) *	1977-06-24	1979-01-11	Karlsruhe Augsburg Iweka	Vorrichtung zum aufspulen textiler faeden
US4166587A (en) *	1978-06-01	1979-09-04	Industrie-Werke Karlsruhe Augsburg Aktiengesellschaft	Method and aparatus for transferring yarn on a nearly full package to an empty bobbin

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WO2023027651A3 (en) *	2021-08-26	2023-08-17	Domeks Maki̇ne Anoni̇m Şi̇rketi̇	Method providing the winding of the cable in automatic cable winding machines and a flap apparatus thereof

Also Published As

Publication number	Publication date
DE3274541D1 (en)	1987-01-15
IE822015L (en)	1983-03-03
EP0073930B1 (de)	1986-12-03
EP0073930A3 (en)	1984-03-07
IN158954B (de)	1987-02-28
IE54100B1 (en)	1989-06-21
BR8205152A (pt)	1983-08-09

Publication	Publication Date	Title
US4340187A (en)	1982-07-20	Bobbin changing apparatus
US5029762A (en)	1991-07-09	Yarn winding apparatus and method
US5526995A (en)	1996-06-18	Yarn winding method
US5005776A (en)	1991-04-09	Process and device to guide and sever a thread upon bobbin replacement
US4052017A (en)	1977-10-04	Method and apparatus for automatically changing textile bobbins on a cantilevered bobbin chuck of a textile winding machine
JPH09156831A (ja)	1997-06-17	綾巻きパッケージを巻成する繊維機械の綾巻きパッケージ交換装置
US4770356A (en)	1988-09-13	Filament winding machine
US4497450A (en)	1985-02-05	Filament winding machine
EP0073930B1 (de)	1986-12-03	Fadenaufwickelmaschine
US4186890A (en)	1980-02-05	Mechanism and method for transferring yarn from a full package to an empty bobbin
EP0288840B1 (de)	1991-09-04	Fadenfang-Einrichtung und Aufwickelvorrichtung
US4524918A (en)	1985-06-25	Filament winding machine
US4606508A (en)	1986-08-19	Bobbin inserting device
JPS61203077A (ja)	1986-09-08	糸パツケージ用ワインダ
US5082191A (en)	1992-01-21	Method of, and apparatus for, changing bobbins in automatic winders
US6662542B2 (en)	2003-12-16	Open-end spinning device and process for temporary receiving a yarn
US4948058A (en)	1990-08-14	Apparatus and method for winding yarn
US5431353A (en)	1995-07-11	Bobbin winding machine
EP0025507B1 (de)	1986-02-12	Schwenkarm für Spulmaschine
GB2087936A (en)	1982-06-03	Yarn winding apparatus and method
JPH0717313B2 (ja)	1995-03-01	巻き取り機
ITMI950024A1 (it)	1996-07-10	Dispositivo per il posizionamento controllato delle spole in una stazione di una roccatrice automatica
US4741485A (en)	1988-05-03	Winder layout
GB2179066A (en)	1987-02-25	Forming overwrapped thread reserves on bobbins
JPH07137942A (ja)	1995-05-30	連続的に供給される糸を巻き取る方法および巻取り機

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EP0073930A2 - Fadenaufwickelmaschine - Google Patents

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