DD202592A5 - FLAT KNITTING MACHINE WITH A VARIABLE CELLING DEVICE - Google Patents

Abstract

In a flat knitting machine with a variable bobbin with cam arrangements for controlling the advance of a yarn guide of a ram, which is effected by a differential in each direction of the Kulierbewegung and by a variable transmission ratio with different size, can be a simple variable Kuliermechanismus, in the yarn guide and Rössel positively driven by a differential, create by a holder (46) carries a pair of forward control locks (56,58) and is movable together with a Kulierexenterstößel to the locks (56,58) with the holder (46 ) by a degree corresponding to the amount of the sinker movement, and the locks (56, 58) individually relative to the support (46) for cooperation with a feed control scanner (72) at the end of the sinking movement to actuate the differential for retaining the thread guide (106) and building a ge Wanted yarn guide advance at different Kulierweiten are movable. FIG. 2

Description

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553 1

"Flat knitting machine with a variable circling device"

Field of application of the invention

The invention relates to a flat knitting machine with a variable tilting device with cam arrangements for controlling the advance of a yarn guide in front of a rudder, which is effected by a differential in each direction of the Kulierbewegung and by a variable transmission ratio of different size.

The invention is particularly intended for high speed flat knitting machines as described in British Patent Specification 2,015,039.

Characteristics of the known technical solutions Flat knitting machines with variable Kuliereinrichtungen are known. When the reciprocating motion at the time of coagulation is increased or decreased by changing the drive geometry of the variable couliser, the

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To achieve variation of the knitting width, the speed of the eccentric shaft is varied in order to maintain the maximum possible linear yarn guide speed. The knitting quality is kept the same while the productivity is improved.

A known variable tilting device is described in US Pat. No. 2,872,798 and uses a conventional friction drive. The eccentricity of a Kulierexzenters is transmitted with different transmission ratios to the rudder and the friction drive. End stops are moved to stop the thread guides in the desired portion of the pad and to ensure that the stopped thread guides again run in front of the pin during the next transverse movement.

British Patent Specification 2,015,039 describes a variable tilting device which does not use a friction drive but which guides both the thread guide and the pusher directly (positively) by means of a differential drive. A cross-shaped eccentric alters the timing of the differential drive, thereby ensuring proper thread guide advance in front of the ram during each cross-pass. Such an arrangement is expensive and requires considerable maintenance.

Object of the invention

The invention has for its object to provide a flat knitting machine with a variable Kuliereinrichtung, in which the Kuliereinrichtung is simple and are positively driven in the thread guide and the rattle on a differential.

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Explanation of the essence of the invention;

This object is achieved in that a holder carries a pair of flow control locks and is movable together with a Kulierexzenterstößel to move the locks with the bracket by a degree that corresponds to the extent of the Kulierbewegung, and that the locks individually relative to the support for cooperating with a lead-controlling scanner at the end of the picking movement for actuating the differential for retaining the yarn guide and establishing a desired yarn guide advance at different Kulierweiten are movable.

In the inventive Kuliereinrichtung of the flow controlling control cam has a solid litter and is suitable to perform the desired deceleration of the yarn guide and the forward reversal at the end of a cross-over in a large Kulierbreitenbereich. The cams with the fixed throw are controlled by the varied movement of the first differential gear input in such a way that the desired movement is given to the second differential gear input. The variable tilting device can be constructed stably and reliably, so that an extended high-speed operation is ensured.

Preferably, the first differential gear input is rotatably mounted and has a first toothed segment for driving a

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Gear of the differential. The first differential input may be connected to a second sector gear which drives a rack which linearly moves the lead for the advancing cam. Such a function of the differential causes speed variations of the differential and the lead-controlling cam without cams, so that an accurate synchronization of the movement of the ram and the thread guide is given.

In a preferred embodiment, the parts which scan the eccentric cam are connected to a block arranged on a screw in a pendulum lever. The screw is rotated in proportion to the desired fill width and the block is slidably supported in a slot of a member carried by a pair of parallel arms. The first Differentialgetrie beeingang is formed by a lever which is rotatable together with the parallel arms. The screw in the pendulum lever can be rotated in proportion to the screw that shifts the thread guide end stops within the available scope. A compensation of a non-linear characteristic of the first differential gear input with respect to the change of the end stop positions by a separate device is not required.

It is advantageous if the cam advancing cam has a pair of screws and cam shells on each of the screws, the pair of screws being rotated together and moving the cam shrouds in opposite directions. The pair of screws may be connected to a splined shaft, which is rotated together with the screws in the pendulum lever to

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to effect a proportional linear displacement of the lock shells relative to each other. The scanner preferably performs a tilting movement at the end of each transverse run and is provided with an arm for cooperating with each of the locks and with a switching device for coupling the respective arm in the associated lock at the end of each transverse run. The switching means displaces the scanner axially and is controlled by a cam which moves together with the grinding eccentric. The screws, locks and switching means allow the scanner to be rotated at the end of each transverse run and then positively held in place by a linear cam track until the changeover means become effective again.

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embodiments

The invention will be explained in more detail below with reference to exemplary embodiments illustrated in the drawing. Show it:

FIG. 1

a schematic view of the main parts to form a first differential gear input of a variable, fire device according to the invention.

FIG. 2:

a schematic view of the main parts to form a second differential gear input

FIG. 3:

a section through parts shown in Figure 2

FIG. 4:

a schematic view of the main parts of another variable, firing device according to the invention for a flat knitting machine in a first working position

Figures 5, 6, 7, 8, 9:

other working positions

FIG. 10:

a schematic view from the front of a part of a flat knitting machine with the Kuliereinrichtung of Figures 4 to 9

FIGS. 11 and 12

the positions of a leading cam follower in Figure 5 and 6th

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In the embodiment shown in Figures 1 to 3 a Kulierexzenter 2 is driven by a rotating at half revolution speed shaft so that the Kulierexzenter 2 once-rotates when the Hauptexzenterwelle makes two full revolutions, in each case a knitting and a Kulierzyklus performed becomes. A Kulierexzenter plunger assembly consists of a pair of rollers 4, which are arranged on diametrically opposite sides of the Kulierexzenters 2 on bearings 6, which are connected by rods 8. A set of the rods 8 is arranged on each side of the Kulierexzenters 2. The cam follower assembly is supported on one side by a dangling pendulum lever 10 and on the other side by an upright lever 12, both of which are mounted on side posts of the flat knitting machine. The cam follower assembly is connected via a substantially horizontally disposed connecting member 14 with. a block 16 which is guided in an upright slot 18 of an A-shaped member 20. The lever 10 has two connected, the A-shaped member spanning members, of which the rear is connected to the connecting member 14.

The position of the block 16 in the slot 18 - and thus the ratio at which the movement is transferred from the cam follower assembly to the A-shaped member 20 - can be achieved by moving the block along a screw 22 by turning the screw which is in another pendulum lever 24, which in turn is also attached to the side stand of the machine is stored. The A-shaped member 20 is of

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two parallel arms 26 and 28 held. An arm 28 is rotatable about the same axis 29 about which a quadrant 30 connected to it via a pin 29 is also rotatable. The quadrant 30 is therefore moved together with the arm 28. The quadrant has at 32 teeth which constitute a first input for a differential gear assembly incorporating a differential 34 and constructed as described in British Patent Specification 2,015,039.

The first input is directly connected to a Rössel drive and varies the amplitude of the Rösselbewegung in dependence on the rotation of the screw 22 (see Figure 10).

As can be seen in Figure 2, carries the quadrant 30 at its lower end a toothed segment 40 which meshes with a gear 42, which in turn is in operative connection with a rack 44. The rack 44g moves linearly back and forth with the same change as transmitted through the differential 34 to the ram. , ..

The rack 44 carries a cam holder 46 which is slidably mounted on guide rails 51 and 53 (Figure 3). The cam holder 46 rotatably carries a pair of screws 60 and 62. Each screw carries a set of upper and lower guide rods 48 and 50 and lock shells 52 and 54, respectively, which provide a fixed offset with leading, opposed and mutually inclined control cam surfaces 56 and 58 are. (Figure 3). The cam surfaces 56 and 58 form

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Ramps. The lock coats 52 and 54 are threaded so that they are displaceable on screws 60 and 62 together with the associated guide rods 48 and 50 and are guided in the sliding movement and secured against rotation by the guide rails 51 and 53. The screws 60 and are rotated by a rod 64 (Figure 1) so that the screws are rotated at the same time and to the same extent as the screw 22. Both the rod 64 and the screw 22 are gradually driven by an edge screw 121 on the machine (FIG. 10) which moves the end stops to cooperate with the yarn guides at the end of their transverse movement. For transmitting the movement of the edge screw 121 to the rod 64 and the screw 22, suitable chains, etc. (refer to the chain 120 in Figures 4 to 9) may be used. The screws 60 and 62 have meshing gears (see gears 121 in Figure 11) and act in opposite directions. In this way, the cam-advancing cam surfaces 56, 58 are linearly moved in opposite directions as the shoe width is increased or decreased. The linear motion between the interaction of the cam follower lever with the associated cam surface changes proportionally to the fillet width.

A lead cam follower is provided in the form of a lever 72 and cooperates with the cam surfaces 56 and 58. The lever has two rollers 68 and 70 pointing in opposite directions and an output arm 66 which is connected to a rod 73 which is the second

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Input of the differential 34 forms. The lever 72 is rotatably mounted on a shaft 74. A screw 76 acts on the lever 6 and moves it axially to the shaft 74 to bring the plungers 68 and 70 in the path of movement of the associated cam surfaces 56 and 58, respectively. The screw 76 is adjustable by means of a rod 78 and a toggle lever 80 which cooperates with a corresponding eccentric 82 on the half-speed rotating shaft. As a result, the lever 72 is displaced at the end of each picking step during the time the knitting takes place and the pusher is at rest.

In a modified arrangement shown in Figs. 4 to 10, the quadrant 30 is operated by a variable transmission ratio mechanism similar to the mechanism previously described, but for structural reasons the pendulum lever 24 is disposed on the other side. The quadrant drives a gear assembly, including a differential 34, to drive a ram and a thread carrier in a similar manner. The quadrant 30 further includes the segment for reciprocating the cam holder. The most significant difference is that the cam follower controlling the advance is moved axially by a cam eccentric 102 via a plunger and a rod 103 which projects through the side frame of the flat knitting machine, thereby substantially simplifying the mechanism for controlling the axial plunger movement. The screws 60 and 62 are driven in the opposite direction by a splined shaft 63.

by which the bevel gears are connected to the rod 64.

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The procedures of the operations for controlling the Kulierbewegung will be described with reference to Figures 4 to 9. Figures 4, 5 and 6 show the successive stages during a wide Kulierbewegung, and Figures 7, 8 and 9 during a narrow Kulierbewegung. For a wide Kulierbewegung the screw 22 and the screws 60 and 62 are rotated simultaneously with the screw 121. The screw 121 carries the end stop 104 for the yarn guide 106 and brings the end stops 104, the block 1.6 and the locks 52 and 54 in the positions that are suitable for the particular Kulierbewegung, wherein a chain 120 and a rotating shaft 124 with a gear 126 meshing with a gear on the screw 121 (see Fig. 10) is used. The block 16 is brought into a low position in the slot by the screw 22. The rear camshaft 54 is disposed to the left of the front camshaft 52 by the screws 60 and 62.

At the beginning of the active part of the sinking cycle (Figure 4), the quadrant 30 is rotated, whereby a gear 108 of the differential 110 rotates. The gear 108 is directly connected by a shaft 112 and a belt 114 to a plow 116. The roller 68 of the lead-controlling cam follower lever 72 is disposed between the upper and lower guide rods 48 and 50 and is held there by the action of the eccentric 102 and the rod 103. The angular position of the lever 72 is transmitted via the rod 73 for controlling a pinion carrier 115 of the differential 110 and holds it in the position, in

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the thread guide 106 runs in the same direction as the rattle through a belt and pulley drive at the same speed, but with a predetermined flow in front of the rower (Figure 10). As the quadrant moves further, the sector gear 40 moves the eccentric support and allows the guide rods 48 and 50 to slide behind the roller 68 without moving the lever 72. In Figs. 4, 5 and 6, portions of the front guide rods 48 and 50 are broken away to show the parts behind them.

In the next step (Figure 5), the cam surface 56 approaches the roller 68 as the yarn guide 106 approaches the end stop 104. The moment the yarn guide 106 hits the end stop 104, the rollers 68 and cam surface 56 cause the lever 72 to tilt. The pinion carrier 114 is rotated and compensates for the continuing movement of the gear 108 that drives the ram 116. When the roller 68 has run up on the cam surface 56, the rider has overtaken the yarn guide 106, which is pressed against the stop 104. The cam surface 56 thus brakes the yarn guide 106 as it hits the stop 104 and properly positions the yarn guide 106 for edge formation. Furthermore, it is ensured that the yarn guide 106 runs once more in front of the ram 116 during the following cross-section. During the described movement, the lever 72 is in the position relative to the cam holder 46 which is shown in FIG.

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is placed. As the roller 68 is raised, the roller 70 is lowered between the various guide rods.

The Kulierzyklus ends in this stage. A knitting cycle takes place during which the quadrant 30 remains stationary and thread guides and rams are not moved. The offset eccentric 102 moves the rod 103 and shifts the lever 72 in its axis of rotation. The roller 70 passes between its upper and lower guide rods 48 and 50, while the roller 68 is pulled out of the way of the cam surface 56 forming member (Figure 12).

Figure 6 illustrates a condition of the pasting reciprocating movement following the end of a knitting cycle. At the end of this sinking movement, the rear cam surface 58 tilts the lever 72 and places the differential in the position shown in Figure 4 so that the cycle begins again can.

For a closer clamping movement, the screws 22, 60 and 62 are rotated simultaneously with the end stop 104, so that the Elock 16 reaches a higher position and the rear one

 Lock member 54 is moved opposite to the front lock member 52. The time in which the lever 72 is held by the guide rods, shortens accordingly

 Figures 7, 8 and 9 show the successive stages for a very narrow grinding movement in which the differential 110 retains the yarn guide during almost the entire short grinding movement. It is clear that the Kulierweite gradually

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gradually changed during knitting of a flat garment. Figures 4, 5 and 6 on the one hand and 7, 8 and 9 ande-. on the other hand show extreme situations.

In Figure 7, the quadrant 30 tilts for a tight grinding movement, and is shown in the center of its tilting movement. In this stage, the lever 72 is tilted by the action of the cam surface 56 and the roller 68, whereby the roller 70 is lowered. The yarn guide 106 is decelerated for the longest time of the Kulierzyklus.

In Figure 8, the roller 68 has fully risen up and the quadrant 30 has reached the end of its movement. The Rössel has now run in front of the yarn guide 106 and causes the flow. It can be seen that the roller 70 can now be lifted by the ramp when the lever 72 has been moved axially during the next knitting cycle.

During the next grinding cycle, the rattle will overrun, but the yarn guide will be stopped almost from the beginning by moving the lever 72. The pusher then picks up the thread guide when it is pressed against the end stop and overtakes it to restore the lead for the next cross pass. The end position shown in Figure 9 shows the roller 70 which has been lifted by the cam surface 58.

It can be seen that despite the reduction of the Kulierweite the

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Cam surfaces 56 and 58 are displaced on the bracket, so that they still cooperate with the plunger lever 72 at the end of the reduced Kulierbewegung.

The described function can be achieved with simple cam shapes.

The overall arrangement has the effect that is braked earlier for a narrow Kulierweite the yarn guide. This fits in with the necessary deceleration of the rattle.

In this case, the deceleration is distributed over a larger angle of the camshaft rotation because the rollers 68, 70 must run up the cam tracks, using the derived from the quadrant movement, which has undergone a reduction in the transmission. Thus, the required Abbremscharakteristik the thread guide can be ensured even if higher camshaft speeds are applied for narrow Kulierweiten so that the linear yarn guide speed remains unchanged.

Claims (7)

242553 1 claims: A flat knitting machine having variable cam means with camming arrangements for controlling the advance of a yarn guide (106) in front of a ram (116) caused by a differential (34) in each direction of the Ku movement and by a variable transmission ratio of different size characterized in that a holder (46) carries a pair of fore-controlling locks (56, 58) and is movable together with a grinding eccentric pusher (4, 6) to extend the locks (56, 58) with the holder (46) to shift, which corresponds to the degree of the Kulierbewegung, and in that the locks (56, 58) are individually relative to the support (46) for cooperating with a feed control (72) at the end of the sinking movement to actuate the differential (34) to retain the yarn guide (106) and build up a desired one 242 553 1 Fadenführervoreilung be moved at different Kulierweiten. 2. flat knitting machine according to item 1, characterized in that the holder (46) for a linear sliding movement by rails (51,53) is held and connected to a rack (44), and that a pick lever (30) carries a toothed segment (40) for actuating the rack (44) and is connected to a toothed segment (32) with the differential (34). 3. flat knitting machine according to item 1 or 2, characterized in that the holder (46) has a pair of screws (60,62) carrying a lock shell (52,54) with locks (56,58) and the lock shells (52 , 54) in the opposite direction. 4. flat knitting machine according to item 1, characterized in that a spline arrangement (59) of a control screw (2) is for the variable Kuliergrößeneinrichtung (16,18,22,24, 26,28,30) for common rotation driven and the displacement of the holder (46) allowed while the rotation control of the screws (60,62) is maintained. 5. flat knitting machine according to item 4, characterized in that the control screw (22) is mounted in a lever (24) and controls the position of a block (16) connected to a connecting member (14) with the Kulierexzenterstößel (4,6) is. 242 5 and that the block (15) is drivable in a slot (18) in a part (20) held by a pair of parallel arms (26, 28) to produce a variation in the width of the picking motion that is substantially linear with the movement of the block (16) caused by the screw (22). 6. flat knitting machine according to one of the Punkire 1 to 5, characterized in that the flow-controlling scanner (72) between the respective locks (56,58) is arranged, that a cam (82) controls a drive for the scanner (72) along its axis of rotation, whereby this scanner (72) with a selected one of the locks (56,58). interacts. 7. Flat knitting machine according to Punki: 6, characterized in that the scanner (72) has a pair of rollers (68,70) for cooperation with each lock (56,58) and that a straight guide track (48,50) is provided for holding the rollers (68,70) to ensure the maintenance of the appropriate Fadenführervoreilung during the Kulierbewegung. - For this 10 sheets drawings - patent attorneys
Grams + lins
Li / Fe