Classifications

• • D—TEXTILES; PAPER
  • D03—WEAVING
  • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
  • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
  • D03D47/34—Handling the weft between bulk storage and weft-inserting means
  • D03D47/36—Measuring and cutting the weft
  • D03D47/361—Drum-type weft feeding devices
  • D03D47/362—Drum-type weft feeding devices with yarn retaining devices, e.g. stopping pins

Definitions

• the invention relates to a thread storage and delivery device according to the preamble of claim 1 and the preamble of the independent claim 2.
• the separation of the windings as they are fed onto the storage body is an important prerequisite for trouble-free operation.
• the windings can be separated easily by means of feed elements which are moved by an inclined and eccentric cylinder surface from the drive shaft.
• feed elements which are moved by an inclined and eccentric cylinder surface from the drive shaft.
• there is only one unchangeable basic setting of the separation which - because it is also suitable for difficult operating conditions and / or critical thread qualities - represents a compromise in other cases.
• technically very complex solutions have already been proposed to intervene to change the separation in the area of the drive shaft.
• the support elements are suitable for storage bodies with a variable diameter, such as those for weft thread storage and delivery and -measuring devices are used, a wobbling plate edge-like feed element is known, which pushes the first turn only axially forward from the winding side and thereby creates undesirable contact zones between the turns in the supply, because no separation of the turns is possible.
• a thread storage, delivery and eating device in which the support elements of the storage body are adjustable in diameter, and in which feed elements distributed over the circumference are provided for separation during feed, has already been exhibited, but is not yet in practice to be found.
• the invention has for its object to provide a thread storage and delivery device with thread separation, which is easily and universally adaptable to changing operating conditions and / or thread qualities.
• the rapid and precise adjustment of the diameter of the storage body by moving the support elements together does not mean a loss of thread separation during feed because the feed elements are adjusted together by means of the support elements when they are adjusted and so that the separation is maintained during feed. Any desired changeover can be carried out quickly, so that the changeover times are short.
• the switch can be carried out particularly advantageously even with overlying windings and also during operation, because the feed elements forcibly assume their relative positions with respect to the support elements for the separation and feed when they are adjusted. A quick adjustment, for example of the weft thread length, is possible.
• the relative position of each feed element with respect to its associated support element is changed in the case of an unchangeable diameter of the storage body in order to adapt the separation and the feed to the respective operating condition or thread quality.
• the adjustment of the separation to the thread quality can be carried out with overlying turns and even during operation.
• the embodiment of claim 3 represents a departure from the usual drive principle of the feed elements, because these are brought to their feed movement independently of the drive shaft.
• the feed elements are adjusted together with the support elements without endangering the separation during the feed; in the case of a storage body with an unchangeable diameter, the separation is adapted to the operating conditions or the thread quality in a structurally simple manner.
• both the diameter adjustment and the separation adjustment are simple because the feed movement of each feed element with respect to the radial movement component is independent of the radial distance from the drive shaft or movement control elements arranged there. Only axial motion components are derived from the drive shaft.
• the radially adjustable connection is released for this purpose and then fixed again.
• the breakaway resistance of the slip clutch is overcome only for the adjustment, the feed elements are coupled to the drive shaft during operation.
• the storage body is adjustable in diameter, can be particularly quickly and accurately, even during Change operation regarding separation during feed. If the diameter changes, the feed elements are adjusted to the new diameter using the support elements. By at least one revolution of the drive shaft, all of the feed elements are then centered with a basic setting of the height difference. The height difference is increased or decreased by subsequently changing the diameter of the support elements again, as a result of which a different separation is set. This is of particular importance because a change in the diameter, for example of the weft thread length, of the feed elements also changes their raidal lever arm with the drive shaft, which may result in an undesirable change in the separation. As explained above, this change in the separation can be compensated very easily, so that the thread is conveyed with the same separation that is correct for each diameter.
• the adaptation concerns two actually different aspects, namely the operating condition of the thread length and the thread quality on the storage body.
• the height difference and thus the separation is set by means of the adjusting mechanism.
• the diameter of the eccentric circle that rotates in operation with its center around the drive shaft axis, in which the feed elements are inscribed is changed relative to the diameter of the circle, in which support elements are inscribed.
• the feed element With a towing coupling between the feed element and the support element, the feed element is forced to follow a radial adjustment of the support element.
• An expedient embodiment with a diameter-adjustable storage body can be seen from claim 11.
• the inclined and eccentric cylinder surface is the drive control element driven by the drive shaft for the separation and feed movement of the feed elements. If the diameter changes, the feed elements are taken along via the towing coupling. By turning the drive shaft, the feed elements are subsequently centered on the cylinder axis within the radial play, so that they produce the same separation as before the diameter change.
• the radially adjustable connection blocks during operation.
• the guide elements are displaced relative to one another.
• the radially adjustable connection ensures that the radial and axial movement components derived from the rotation of the eccentric and inclined cylindrical surface are transmitted directly to the feed element.
• the feed element has two additional degrees of freedom, by means of which result from the tumbling movement of the cylinder and disruptive movement components are kept away from the feed element for a clean feed movement.
• the feed element can move along in an ideal path during the feed movement.
• a particularly expedient embodiment is further evident from claim 14.
• the clamping ring which is pressed with elastic pretension, produces a fixed stop in the radial direction between the feed element and the hub during operation, permitting the relative rotational movement of the feed element and the cylinder axis.
• the frictional force of the clamping ring is briefly overcome in order to move it radially inwards or radially outwards into a new setting position.
• the slip clutch is structurally simple, reliable and stable.
• the embodiment of claim 15 is advantageous because the towing coupling acts in the radial direction, but does not hinder other movement components of the feed element.
• a stop pin engaging in an oversize bore can be moved on all sides within the scope of the oversize bore.
• the embodiment of claim 16 is simple in terms of assembly technology and production technology.
• the stops and counter-stops are only required for the adjustment. They have no function in operation.
• the embodiment according to claim 17 has proven itself because a larger number of stops and counter-stops ensures that the feed element arrives in the correct position during adjustment.
• the embodiment according to claim 18 offers a particularly expedient possibility for statically adjusting the relative height between the outside of the feed element and the outside of the support element and thus the separation during the feed.
• a further advantageous embodiment of a thread storage and delivery device with a diameter-adjustable storage body emerges from claim 19.
• the radial excess of the distance creates the possibility of changing the relative altitude by a subsequent adjustment of the support elements radially inwards or outwards. If the support elements are again adjusted outwards by the eccentricity after the diameter has been increased and the feed elements have been centered, separation no longer occurs. Intermediate settings reduce the separation during feed.
• a simple and rapid changeover of the diameter of the storage body while maintaining the separation results in the embodiment according to claim 20.
• the changeover is possible during operation.
• the aforementioned goal is achieved with the embodiment of claim 21.
• the feed elements are taken along via the tow couplings. Once the new diameter has been set, the drive shaft only needs to be turned at least once to center all the feed elements. If you want to change the separation, then the support elements are used again radially adjusted.
• the axial movements are derived from the drive shaft, while the radial movement components are generated from the relative longitudinal movements of the parts of the feed element, since the phase shift between the inclined positions leads to asynchronous axial movements of the two parts.
• correspondingly inclined radial surfaces can also be used to generate the axial control movements.
• the radial movement components are generated by means of the rising ramps.
• a selectable coordination of the phase shift can be used to precisely determine the axial path of the outside of the upper part to raise the outside with the turns. In this way, the feed and the separation can be precisely adjusted or adjusted.
• the embodiment of claim 24 is also advantageous, in which a locomotion movement for the upper part is generated from axial movement components of the two feed element parts.
• These drive the eccentrics like a locomotive undercarriage slipping while standing, cyclically raising and lowering the outside of the feed element and moving it back and forth in the axial direction.
• the eccentrics are coupled as with two coupling rods offset by 90 ° to one another, so that there is never an unstable dead center.
• a similar feed control drive emerges from claim 25.
• the angle levers are cyclically pivoted back and forth from the lower part, raising and lowering the upper part, which in turn is moved axially back and forth by phase-shifted axial movements.
• radial movement components of the upper part are generated by the ramps.
• Intermediate needle rollers reduce resistance to movement and prevent wear.
• the embodiment of claim 29 is simple and reliable.
• the displacement is carried out from the outside, i.e. even during operation. It is important that after reversing the displacement, the thread storage and delivery device can work in the opposite direction with separation during feed.
• the rotary drive By means of the rotary drive, not only can the separation be adjusted, but also the feed for the reverse direction of rotation of the winding member of the thread storage and delivery device can be changed.
• An expedient alternative embodiment is set out in claim 30.
• Between the feed element and the Drive shaft is a non-contact drive connection based on magnetic forces, with which the radial and axial movement components for the feed element are generated. Both the diameter of the storage body and the separation can be easily adjusted. It is also possible to switch the feed with separation to the reverse direction of rotation of the winding member.
• Another hub is responsible for the radial movement components as for the axial movement components.
• the arm allows the axial components of motion thanks to its elasticity or displaceability, while transmitting radial components of motion.
• the embodiment of claim 32 is expedient because sliding block or link guides are precise and low-wear.
• the arm which is flexible in the axial direction, is radially adjustable on the adjusting element of the hub.
• the feed element can be adjusted radially by axially displacing the hub.
• a particularly useful embodiment is also based on claim 37.
• the feed element can be driven with magnets for feed movement independently of the drive shaft in the support element.
• the separation is freely selectable. It is possible to make a change during operation or to disable one or more feed elements. Furthermore, this feed control drive can be easily switched to the reverse direction of rotation of the winding member. A change in the diameter of the storage body has no influence on the separation. Furthermore, the separation is independent of the diameter of the storage body.
• the embodiment of claim 38 is advantageous.
• the bar moves from the inner limit position in the following applied turns under the force of the spring element again to the outer limit.
• FIG. 1 shows a longitudinal section of part of a thread storage and delivery device with a diameter-adjustable storage body
• FIG. 4 shows a detail section in FIG. 1 in the plane IV-IV
• Fig. 8 shows a partial longitudinal section of a
• Thread storage and delivery device with a variable-diameter storage body in a modified version, 9, 10, 11, detailed variants of the embodiment of FIG. 8,
• FIG. 13 shows a longitudinal section through a detailed variant of a magnetic drive system
• 21 shows a section through a detail variant for a storage body with an unchangeable diameter.
• a thread storage and delivery device F has a stationary base body G, in which is mounted a drive shaft T which can be driven by a drive, not shown, the axis of which is denoted by H.
• a storage body K is rotatably mounted on the drive shaft T and is blocked against rotation by means not shown, for example permanent magnet pairs.
• the storage body K is drum-shaped and forms a rotationally symmetrical Storage area for a thread supply consisting of turns W of a thread U, preferably a weft thread for a weaving machine, which is drawn off intermittently, for example, in precisely dimensioned, identical longitudinal sections.
• the drive shaft T carries a tubular winding member I which winds successive windings W, from which the thread is drawn off overhead in the direction of the arrow.
• a stop device B is attached to the housing G with a stop element B ′ which can be moved radially back and forth and which, as is known, engages in the thread path between the pull-off cycles and is withdrawn for the pull-off.
• the storage area of the storage body K is defined by stationary rod-shaped support elements A distributed in the circumferential direction and rod-shaped feed elements V assigned to them.
• the feed elements V - as will be explained later - are driven to a feed movement while the drive shaft I is running, in order to move the windings W in FIG. 1 forward from left to right and to separate them at predetermined intermediate distances.
• the support elements A are mounted in the storage body K in a radially adjustable manner and engage with engagement elements 1 in a face thread 2 of an adjusting washer Q, which can be driven to rotate, optionally by an actuator E, around the outer diameter of the storage body K defined by the supports A change.
• the outer sides of the support elements can be written in a circle concentric to the axis H.
• Each feed element V is arranged with play on all sides in a support element A. But it could also be between two support elements A. Between the support element ent A and the associated feed element V, a drag coupling S is provided which is effective in the radial direction and which takes the feed element V with it when the support element A is adjusted radially.
• a sleeve 3 On the drive shaft T, a sleeve 3 is fixed, the outside of which has a cylindrical surface Z, the axis 8 of which is inclined at an angle with respect to the drive shaft axis H and springs (FIG. 2) are eccentric to the drive shaft axis H (eccentricity e). In the direction of rotation of the drive shaft T there is an offset of e.g. 90 ° (see Fig. 7) provided.
• a hub N coaxial to the cylinder axis 8 is rotatably mounted, to which the feed elements V are attached together like spokes. Each feed element V is connected to the hub N with a connection C which can be adjusted in the radial direction and which in FIG.
• the feed element V has a cylindrical shaft 6 which engages in a sleeve 4 with a sliding fit and is fixed by a clamping ring 7.
• the sleeve 4 is supported with stub axles 5 - (axis 9) in the N-abe N in Fig. 1 from and into the plane of the drawing to a limited extent.
• the support element A has an approximately axial shaft A 'for receiving the feed element V.
• the sleeve 4 can be pivoted to a limited extent in an opening 16 of the hub N with the axle ends 5 in bores 10 about the axis 9, the axis 9 being approximately is parallel to the cylinder axis 8.
• the shaft 6 can be rotated with the feed element V about an axis 11 defined by a bore 12 of the sleeve 4 and radial to the cylinder axis 8, since the clamping ring 7 sits in a groove 13 of the shaft 6 with little radial and axial play and with elastic prestress against the wall of the bore 12 is pressed.
• the towing coupling S is formed according to FIGS. 1 to 3 by stops 14 on the feed element V and by counter stops 15 of the support element A, a predetermined radial play being provided.
• each feed element V is first moved radially outwards over the outer side of the support element A and then after one revolution of the drive shaft T from a position in which its outside lies radially below the outside of the support element A. additionally moved in the axial direction in FIG. 1 to the right in order to raise the windings W, to carry them forward and to separate them, before it steps back under the support element A and is set to the left in the axial direction. All feed elements V execute the same movement one after the other in the direction of rotation.
• the drive shaft T stops. If thread U is then required, the stop element B 'is withdrawn and the required turns W are withdrawn. Falls below the number of turns W on the storage body K a certain size, the drive shaft T is rotated again and the stock is replenished.
• the thread U drawn off during a withdrawal has a predetermined length, which is set by adjusting the diameter of the storage body K.
• the adjusting ring disc Q is rotated, the support elements A jointly moving radially outwards or radially inwards.
• the stop device B on the housing E is released and the distance between the storage body K and the stop device B is set.
• the feed element V are taken along with the adjustment via the drag clutches S.
• the breakaway resistance of the slip clutches R is overcome during the adjustment. Since the feed elements V are initially concentric with the drive shaft axis H during this adjustment by the support elements A, but are intended to define a circle for the separation during feed, which is ' eccentric to the cylinder axis 8, the drive shaft T is rotated at least once so that the feed elements V by means of the tow clutches S and the support elements A are centered about the cylinder axis 8.
• the device F is then ready for operation again.
• the adjustment can be carried out remotely by means of the actuator E, and also during the operation of the device F.
• the resistance of the slip clutches R is greater than the contact pressure of the windings W, so that the windings W are unable to connect the radially adjustable connections C. to adjust automatically.
• radially adjustable can be detached and fixed again in another way Connections may be provided.
• Two groups of stops 14 and counter-stops 15 are provided on each longitudinal side of the feed element V.
• the radial distance between the counter-stops 15 corresponds to at least twice the eccentricity e plus the radial thickness X of the stop 14. This ensures that the feed elements V are in the same each time the support elements A and the subsequent rotary movement of the drive shaft T are adjusted Center the relative position with respect to the support elements A because each stop 14 is intercepted once at the upper counter-stop 15 and once at the lower counter-stop 15.
• the feed and separation effect is therefore independent of the radial setting position of the support elements A.
• the separation can, however, increase with increasing diameter of the support elements A because the lever arm of the feed elements V increases.
• 5a and 5b show two alternative options for individually adjusting the feed and the separation. But it is also possible to combine these alternatives.
• the fixed relative arrangement of the stops 14 and counter-stops 15 always results in the same relative position between the outside of the feed element V designated by 25 and the outside of the support element A designated by 26.
• the relative height difference between the outside 25 of the feed element V and the outside 26 of the support element A can be changed universally in order to be able to change the separation arbitrarily. This is a Principle that is expedient both in the case of a storage body K according to FIG.
• variable diameter for example in order to set a different separation for a different thread quality or to keep the separation constant even with increasing diameter
• a storage body K with an unchangeable diameter Diameter according to FIG. 21 in order to adapt the separation to a different thread quality or to different operating conditions.
• the stop 14 By statically changing the radial position of the stop 14 in the direction of a double arrow 19 by means of an adjusting device J in relation to the outside 25 according to FIG. 5a, the outside 25 then projects less or further beyond the outside 26 during operation.
• the stop 14 is radially displaceable in a recess 17 of the feed element V by means of a screw spindle 18.
• an element 21 which can be raised and lowered in a recess 20 of the support element A in the direction of a double arrow 19 can be provided, which carries the two counter-stops 15 and is adjusted by means of a screw spindle 22.
• the result is the same, namely a static change in the relative altitude between the tops 25 and 26 and thus a change in the separation when feeding in the dynamic range. This will be explained using the diagram in FIG. 7:
• the vertical axis corresponds to the eccentricity e or the target diameter D of the support elements A and the axial path s of the feed elements V in the positive and negative directions.
• the horizontal axis shows the rotation of the Drive shaft T over a 360 ° revolution.
• the horizontal solid line 28 in FIG. 4 corresponds to the nominal diameter D of the outer sides 26 of the support elements A.
• the rising and falling line 30 corresponds to the radial movement of the feed element V taking place between 0 ° and 360 ° during one revolution of the drive shaft D due to the Eccentricity e.
• the top 25 is -e below the top 26.
• the outside 25, 26 are at the same radial height, namely 0.
• the outside 25 is + e above the outside 26 before it moves downwards, at 270 ° at D and at 360 ° finally by -e below the outside 26.
• the feed element V Due to the phase shift (eg 90 °) between the inclined position and the eccentricity e, the feed element V becomes 0 ° according to the solid line 31 (indicated by downward-pointing arrows) counter to the feed direction, ie moved to the left in FIG. 1 until it reverses axially at 90 ° and begins a movement (arrows up) in the feed direction (to the right in FIG. 1) that begins continues up to 270 ° and then reverses again. Since the upper side 25 lies between 90 ° and 270 ° (area 0) above the upper side 26, the thread windings W are carried along and separated over a maximum area.
• a separate adjustment mechanism J is provided for each feed element V or each support element A.
• a common adjustment mechanism J for all feed elements " or all support elements in order to be able to carry out the creation centrally.
• the adjustment mechanism J could then work as in FIG. 1, for example with an adjusting washer with a flat thread.
• the common adjusting device of the support elements for changing the separation and the feed can be used in a particularly advantageous manner, for example the collar disk Q according to FIG. 1 with the drive C, for example a stepping motor.
• the radial distance according to FIG. 6a between the counter-stops ⁇ 15 is chosen to be an oversize Y larger than the double eccentricity e plus the radial thickness x of the stop 14.
• the oversize Y suitably corresponds approximately to the eccentricity e .
• the support elements A are first adjusted in the direction of an arrow 23 to a diameter D2 which is larger than the nominal diameter D.
• the feed element V according to FIG. 6a for which it is assumed that the eccentricity e is in the 90 ° rotational position of the drive shaft T, is dragged along via the stop 14. Then the drive shaft T is turned at least once (FIG. 6b), the feed element V being raised by the eccentricity e from the lower counter-stop 15. Because of the oversize Y, there is still no separation with this setting, because the upper side 25 does not come over the upper side 26 at any time.
• the support element A OP is adjusted in the direction of an arrow 24 downward by the oversize Y until the outside 26 lies on the diameter D. Then there is a maximum feed with maximum thread separation because the forward movement (curve 31 between 90 ° and 270 °) is effective over the area O of curve 30.
• the support element A is adjusted radially outwards in the direction of an arrow 27, for example by means of the set collar Q in FIG. 1, until the outside 26 is on the diameter Dl.
• the movements of the curves 30, 31 are only superimposed over the area P.
• This setting can be made for all feed elements together and also during operation, for example via the rotary drive E. If the diameter D is to be maintained with regard to a desired weft thread length, one must be used To reduce the separation from FIG. 6c, the feed element V is again set slightly downward with the upper counter-stop 15 before the support element A is again set to the diameter D.
• each feed element V is divided into an upper part 32 and a lower part 33, the upper part 32 being axially displaceably guided on the lower part 33.
• a spring element 39 secures the feed elements V on the storage body K.
• Each part 32, 33 is coupled via a radially adjustable, telescopic and kinkable driver connection 34 with its own hub N so that axial movement components of the hubs N are transmitted.
• Each hub N is rotatably supported on a cylindrical surface Z, which is inclined but not eccentric with respect to the drive shaft axis. Between the inclinations of the Both hubs N are offset in the direction of rotation of the drive shaft T.
• the driver connection 34 consists of a tube 35 or 36 formed on the respective part 32 or 33, into which a spherical driver body 38 of a spoke 37 engages.
• the lower part 33 is mounted with ramps 41 on ramps 40 of the stationary support element A rising in the axial direction.
• an actuating shaft 42 is displaceably accommodated, which carries an adjusting pin 43 which engages in an oblique adjusting link 44 on the inside of a sleeve 44a defining the cylinder surface Z.
• an external actuator 46 By means of an external actuator 46, the actuating shaft 42 can be driven for a reciprocating movement in the direction of a double arrow 45.
• the displacement between the two cylinder surfaces Z can be changed arbitrarily (separation adjustment) and even reversed, so that the device F can be operated advantageously in both directions of rotation.
• the eccentric drives 47 are forcibly coupled to one another via double coupling rods, namely the upper part 32 and the lower part 33, in the manner of a locomotive connection, thus creating a cyclical movement of the upper part 32 without dead center, the upper side 25 of which, when raised, is moved forward and lowered counter to the feed direction is moved.
• the separation can be changed by adjusting the offset between the inclined positions of the two hubs as in FIG. 8.
• two hubs N are also provided, as in FIG. 8, in order to move the lower part 33 and the upper part 32 axially.
• the lower part 33 is integrated with its tube 35 into a control lever 49, which is articulated at 53 on angle levers 50 which are pivotably mounted in the support element A about axes 51.
• the other arms of the angle levers 50 engage with rotary-sliding guides _ 52 in the axial slots of the upper part 32 a, so that only lifting and lowering movements can be transferred to the upper part 32 while the tube 36 produces axial movements.
• FIG. 11 A similar embodiment is shown in FIG. 11.
• the lower part 33 is incorporated with its tube 35 into the lever 49, which is articulated at 53 on the angle levers 50 at both ends.
• the angle lever 50 are pivotally mounted in the support element A about axes 51 and with their other arms 54 integrally with the Upper part 32 connected.
• the arms 54 are flexible.
• two hubs N are used to axially adjust the upper part 32 and the lower part 33.
• the lower part 33 is axially movably guided on supports 55 in the support element A and has axially rising caterpillars 40, on which counter ramps 41 of the upper part 32 rest.
• needle rollers 57 can be inserted.
• the embodiment in FIG. 13 has towing couplings S in the form of oversize holes as counter-stops 15 and transverse pins as stops 14.
• the feed element V is in one piece and has inwardly projecting, fork-like extensions 60 to which magnet arrangements 61 are attached. Between the magnet arrangements 61, an annular disk 58, which contains magnets 59, engages with the hub H on the drive shaft and concentric with the axis H thereof. The magnets 59 are offset from one another and hold different polarities. The rotary movement of the annular disk 58 produces alternating axial and radial magnetic forces which are used for the feed movement of the feed element within the scope of the stroke limitation of the tow clutches in the support element.
• FIG. 14 Another drive principle for the feed element adjustable in the radial direction with the support element A can be seen from FIG. 14.
• the feed element V is attached to a transverse axis 62 of a hub N with arms 64 which are flexible in the axial direction, namely in a radially adjustable link bracket 63.
• the hub N is rotatably mounted on a cylindrical surface Z, which belongs to a sleeve 65, and is eccentric to the drive shaft T. Radial movement components are transmitted from the hub N to the feed element V.
• Another hub N is rotatably mounted on a sleeve 66 which defines a cylinder surface Z inclined to the drive shaft T.
• the axial driver 67 ' acts on the feed element V from the inclined hub only in one axial direction, while a spring 7-3 accommodated in the support element A acts in the opposite direction.
• the feed element V is movably mounted in the support element, e.g. via driver 71 in corresponding grooves 72 and is driven in the radial direction by the eccentric hub N.
• the connection C which is adjustable in the radial direction, is a link guide 70.
• the arms 64 'of the feed element V can be axially displaced within the connection C, which is adjustable radially.
• the radially adjustable connection C is fixed during operation and can only be adjusted to change the diameter of the storage body.
• the feed element V is axially spaced and flexible arms 64 connected to an inner part 74 which is radially adjustably mounted on an adjusting element 76 of the hub N in that pins 75 engage in oblique grooves 77.
• the hub N has an extension 78 which is connected to an actuating part 79 in an axial movement-transmitting connection, the actuating part 79 being axially adjustable by means of an adjusting nut 80.
• axial movement components are applied by a driver 67 which is seated on a hub which is inclined with respect to the drive shaft.
• the embodiment according to FIG. 17 has two spaced hubs N which are rotatably mounted on eccentric cylinder surfaces, between which a further hub (not shown) is rotatably mounted on an inclined cylinder surface of the drive shaft T.
• the feed element V has two tubes 83 on the underside, into which plungers 82 attached to the hubs N engage, each of which, as in the embodiment of FIGS. 2 and 3, has a clamping ring 7 (slip clutch R).
• a plunger 37 of the central hub engages in a central tube 81 as an axial drive member.
• the tappets 82 are mounted on the hubs N via joints 84, preferably ball joints.
• the feed element V is movably guided in brackets 85 in the support element A (towing coupling S).
• the embodiment according to FIG. 18 uses pressure medium pistons 86 which engage in the tubes 83 designed as cylinder tubes and are attached to the tappets 82.
• the tubes 83 delimit with the pistons 86 pressure medium chambers 87, which are filled with a pressure medium under a certain positive or negative pressure.
• a displacement of the pistons 86 is prevented due to the pressure filling of the pressure chambers 87, so that the radial movement components are transmitted.
• it is possible to move the pistons 86 in the tubes 83 for example by throttle valves 88 permitting a slow change in the filling of the pressure medium chambers 87.
• the axial movement components are generated via the central tube 81 and an inclined cylindrical surface.
• the radial movement components are derived from purely eccentric hubs.
• the feed element V is designed as a plate 89 which is movable radially in the support element and on which magnets 90 and 91 act, which act via
• Supply lines 92 are controlled in cycles, so that one magnet produces radial movements and the other magnet produces axial movements on the feed element V.
• the drag couplings S between the support element A and the feed element V limit the stroke and guide the feed element V.
• the magnetic forces are generated between the support element A and the feed element V, so that the feed element V is independent of the drive shaft. Regardless of the respective diameter of the support elements, the feed control remains the same.
• the separation can be achieved by modulating the excitation of the two magnets 90, 91 and change the feed or switch to the opposite direction of rotation of the device.
• the feed element V according to FIG. 20 is intended for a thread storage and delivery device F according to FIGS. 1 and 8 with a variable storage body diameter.
• the outer side 25 of the feed element V is provided on a longitudinal bar 93, which is only supported in a radially movable manner via guide and limiting parts 94 in the feed element V and is loaded radially outwards by a spring element 95.
• the spring element 95 normally holds the strip 93 under the contact pressure of the windings W in a radially outer limit position.
• FIG. 21 illustrates a storage body K of a thread storage and delivery device F 'with an unchangeable diameter DF with separation.
• the feed elements V are jointly attached to the hub N.
• the hub N is rotatably supported on a cylindrical surface Z which is inclined and eccentric with respect to the drive shaft axis H.
• the hub N has a radially outwardly projecting cylindrical extension, forming a guide part 96, with a bore 99, into which an extension of the feed element V, which is round in cross section, is immersed as a counter-guide part 97.
• the groove 98 provided provides access to an adjusting mechanism J.
• This consists of an adjusting screw 105 which is screwed with its shaft 106 into a threaded bore 101 of the hub N.
• An outer screwed-in stop 104 and an underlying stop 103 fix the adjusting screw 105 in the feed element V radially.
• the shaft 106 passes through a bore 102 of the feed element.
• a wedge 100 may prevent an undesired rotational movement of the feed element V about the screw axis and serves (not shown) as an upper and lower stroke limitation for the possible adjustment path between the guide parts 97 and 96.
• the radially adjustable connection C or slip clutch R created in this way is adjusted in order to statically change the relative height difference between the outside 25 and the outside 26.

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• 1991
  • 1991-07-11 EP EP19910912562 patent/EP0538316B1/de not_active Expired - Lifetime
  • 1991-07-11 JP JP51164991A patent/JP3160646B2/ja not_active Expired - Fee Related
  • 1991-07-11 WO PCT/EP1991/001302 patent/WO1992001101A1/de active IP Right Grant

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