EP1516947A2 - Shaft drive for weaving machines - Google Patents

Abstract

A shaft drive system (2) includes a power takeoff mechanism that is associated with and connected to a heddle shaft (1) to restrain the heddle shaft in resting phases and to impart a motion in phases; and control unit for controlling the current speed of the power takeoff mechanism and the heddle shaft. The power takeoff mechanism also executes a predetermined motion during the resting phases.

Description

The invention relates to a shaft drive for at least a weave of a loom.

For shed forming weaving machines are usually several Shoring provided, each a variety parallel have arranged to each other strands through which Thread eyes the warp threads are guided. Become a specialized education the healds moved up and down very quickly. Serve for that Shaft drives used as dobby or eccentric machines be designated. So-called eccentric machines generate from the rotating movement of a drive shaft the up and down movement of the heald frames, with high weaving speeds can be achieved. However, such are Exzentermaschineninflexibel. The generation of patterns or different bindings is limited. It Therefore, shaft drives are widely used in which between a drive shaft and the eccentric for generating the shaft movement is provided a pawl coupling.

Such a dobby is for example from the DE 697 02 039 T2 known. The between the eccentric and the driving shaft arranged latch switching mechanism is here for each shaft movement, i. for an upward movement of the shaft or for a downward movement of the shaft respectively switched on for half a shaft rotation. Such Dobby machines are very flexible. However, such Dobby machines the working speed of eccentric machines do not reach. The work of the pawl switching mechanisms is susceptible to wear. An increase in the working speed does not only lead to ratchet wear, but also to strand and shank breaks.

On this basis, it is an object of the invention to provide a Shaft drive for the heald of a loom to create at low load on its elements and the connected Webschafts an increased working speed allowed.

This object is achieved with the shaft drive according to claim 1 solved:

According to the invention, the shaft movement is now determined that neither a pure sinusoidally oscillating up and down Movement of the shaft still a swinging up and down movement with downtimes in the upper and lower reversal point is obtained. Rather, the drive does not enforce only during the movement phases, but now also during the resting phases of the shaft in which the shaft otherwise usually in the upper or lower reversal point rest, a continued movement of the same. This measure opens up the possibility of maximum acceleration of the Shank to reduce. The avoidance of acceleration jumps leads to a smooth running of the shafts, the even at high working speeds to no excessive Vibrational excitations.The limit for the working speed, occur in the shaft fractures and strand breaks, can thus very far to higher working speeds be moved. The corresponding, from the shaft to be traversed motion curves, according to a first Embodiment of the invention, by means of freely programmable Drives are achieved, which move the shaft. A the Drives assigned control device calls the drives during the movement phases a high speed off to the shaft as quickly as possible from the one reversing position into another reversal position. This process is for shedding necessary to warp threads from the warp thread level move up or down. approaches the shaft of its intended reversal position slows down the control device the output of the shaft drive, the e.g. formed by connecting rods, and leaves him then commute to the same when reaching the reverse position. ever after residence in the reverse position, the pendulum oscillation go through one or more maxima and minima (wave trains). The pendulum movement in the resting phases has the advantage that the Shaft drive can specify shaft movements, the lower Have acceleration values. For example, the Shaft movement in the course of time in the transition from one Reversal into the other of a harmonic function (sinus or cosinus) and, in the reverse position, enters a time function over, at the beginning of which the acceleration is the same Value has the same as when leaving the curve branch of the transition movement. The acceleration curve is thus continuous. The movement curves (also called "laws of motion" be) for the transition of the shaft from a reversal position in the other, as well as for commuting within the reversal areas can in a simple embodiment in one Data storage to be stored. The controller calls then the respective cams from the data memory on and controls the one or more motors of the shaft drive accordingly at. Alternatively, the cams can also advance or be calculated in real time, with the calculation case by case depending on the respective given boundary conditions according to special Optimization criteria can be done. optimization criteria For example, be that a minimum opening time must not be fallen below, that the maximum accelerations are to limit that acceleration jumps inadmissible are that the shaft speed is to be limited or that given a maximum acceleration a maximum operating speed is calculated. The curves resulting from these optimization criteria can then be cached and for driving the shaft drive be applied. The pendulum movement of the shaft in the upper and lower turning point area has the other Advantage that by the pendulum movement of the Webschaft the Warp threads can be somewhat relaxed, causing the weft stop can facilitate.

It is also possible to go through during the resting phase to mechanically produce the shaft to be performed or movement pretend. For example, the shaft via a Coupling device optionally connected to a first drive be a constant between the two reversals oscillating motion generated, or with another drive, the pendulum about the upper or the lower reversal position Movement generated. The switching is preferably carried out during existing synchronization phases. The corresponding coupling can be a linear motion transmitting clutch.

The shaft drive according to the invention can according to another Embodiment one with a rotary drive device connected input shaft, which ultimately serves to drive a gear assembly, the back and forth generated by the weaving movement. The between the Input shaft and the gear assembly provided clutch assembly has at least two input elements and a Output element connected to the gear assembly is. The input elements generate at tapping the movement from the inside at least temporarily a synchronous movement. Within this time window in which synchronicity of the movement tap exists between two input elements and in which the shaft does not rest, the clutch assembly from one input element to the other input element switch. The switching is thus neither as a jerk nor noticeable as a shock in the drive train. Reducing the Rotational speed of the input shaft is therefore to switch not necessary. It can be done without accepting excessive Wear or shaft or strand breaks a Achieve increased working speed of the loom and even if individual healds are always activated and must be disabled.

In one embodiment of the shaft drive that is first input element is a clutch disc that is fixed with the input shaft is connected and thus one of the rotary drive device predetermined uniform rotational movement performs. The second input element is then a clutch disc, which performs a rotary oscillation movement. The rotational oscillation movement is in selected angular ranges, the upper and lower reversal points of the weave correspond, respectively briefly or completely in synchronism with the rotational movement of the first input element. This is regardless of whether it is the rotational movement or the up and down movement to harmonic or non-harmonic Moves. After a short synchrony turns then the second input element back to after a rotation the first input element by 180 ° turn over a certain angular range in synchronism with the first input element mitzulaufen. These short phases of synchronous movement between both input elements can be used to a pawl or other form-fitting, connected to the output element connecting means of the first input element to the second or vice versa. Is the output element to the first input element coupled, the shaft performs its reciprocating Move. Is the output element on the other hand to the second, only by a limited angle swinging back and forth Input element coupled, is the Shank in its resting phase, in which he only a minor Oscillation movement around its upper or lower reversal point performs. Out of this oscillation movement can however, he engaged during the short synchronizing phases be, with the on the shaft and the involved transmission elements occurring acceleration forces and from it resulting loads are barely larger than with uninterrupted Operation of the shaft. There are at least none significant jumpy changes in the Acceleration forces on.

The oscillating motion of the second input element can be achieved by a cam drive that is rigid with the input shaft is connected. Preferably, however, will used a cam drive whose shaft with double input shaft speed runs, so with a single cam both the short synchronous movement for the upper one Reversal point as well as the short synchronous movement for the lower one Reversal point can be generated. Alternatively, the oscillating movement by electric, hydraulic or pneumatic drives are generated.

As a switching element is preferably one with the output element circulating pawl used that over at least to operate one, preferably two shifter is where she passes. The shifters can directly be operated electrically or pneumatically. It will, however preferred, it via a control clutch from a cam drive to drive. The control clutch can then with very low power are operated, on the other hand sufficient large forces are generated to the shifter too move. The clutch can e.g. via stationary control magnets be controlled and driven by a swinging Selection finger be formed. This gives a precise appealing and low energy controllable Control arrangement for the clutch arrangement.

In an alternative embodiment, the two Input elements of the clutch assembly by cams formed, both in sync with the input shaft rotate and are driven by this. The starting element the coupling arrangement here forms a curve follower, the alternative with one or the other cam can be engaged. The curve follower generates a swinging movement and is therefore not just part of Coupling arrangement but also part of a transmission arrangement for generating the reciprocating motion the rotational movement of the input shaft. Switching the cam follower from the tap of the one cam the other cam takes place in a rotational position of the Cams in which their arcs coincide, so that the here from the one cam tapped movement synchronous to the tapped from the other cam Movement is. One of the two cam discs can be designed in this way be that they have the necessary training for movement generated while the other cam disk as a reversing disk is formed and the oscillating reversal position movement generated. As such, it only has each to take over the cam follower element serving short synchronous arcs and otherwise a profile on the webshaft no shiftworking movement but only the reversal vibration generated. In the simplest case, she is one Disc with double circumferential vibration and less radial stroke. It can also be two or more cams with different working profiles are provided. Between These cam disks can each reversing disks be arranged, which is the oscillating reversal position movement generate at the curve follower. Thus it is possible between To switch cams and neutral discs, so that the outgoing curve follower either at engagement with the with working profile provided cam a transitional movement from reverse to reverse or when tapping the reversing washer one with reduced amplitude around or generated from the reversal swinging output movement.

Further, it is possible for each pulley set its curve follower assign and the curve follower optionally with a Coupling output shaft. The cams then form the input elements of the corresponding curve follower while the output element of the clutch assembly with a Linkage that operates the weave shaft.

Even with such a coupling arrangement can be the switching on and off of the drive of a heald without Slowing down or shutting off the rotary drive of the input shaft to reach. There is a total or one almost harmonic movement of the weave not only in weaving, but also when switching on and off the weave generated. This creates the condition for high weaving speeds with low stress on the machine components involved.

Further details of preferred embodiments of Invention will be apparent from the drawings or the description as well as from claims.

Figur 1

einen Webschaft mit Schaftantrieb in schematisierter Darstellung,

Figur 2

den Schaftantrieb nach Figur 1 in schematisierter Darstellung,

Figur 3 bis 5

Zeitverläufe der Schaftbewegung und der Schaftbeschleunigung bei unterschiedlichen Schaftbewegungsverläufen in unterschiedlichen Bewegungsphasen jeweils als Diagramm,

Figur 6

einen Webschaft mit mechanischem Schaftantrieb in schematisierter Darstellung,

Figur 7

Webschäfte und einen zugehörigen Schaftantrieb nach Figur 1 in Draufsicht,

Figur 8

den Schaftantrieb nach Figur 1 in ausschnittsweiser, schematisierter Darstellung,

Figur 9

den Schaftantrieb nach Figur 8 in einer weiteren schematisierten, ausschnittsweisen Darstellung in einem anderen Maßstab,

Figur 10

den Schaftantrieb nach Figur 8 und 9 in ausschnittsweiser Darstellung,

Figur 11

eine abgewandelte Ausführungsform eines Schaftantriebs mit schaltbaren Kurvenscheiben in schematisierter Perspektivdarstellung,

Figur 12

eine schematische Darstellung des Schaftantriebs mit Kurvenscheiben, in schematisierter Darstellung,

Figur 13

eine weitere Ausführungsform eines mechanischen Schaftantriebs in teilweise geschnittener Darstellung und

Figur 14

den Schaftantrieb nach Figur 13 in einer schematisierten Draufsicht.

In the drawings, embodiments of the invention are illustrated. Show it:

FIG. 1

a shaft with shaft drive in a schematic representation,

FIG. 2

the shaft drive of Figure 1 in a schematic representation,

FIGS. 3 to 5

Time courses of the shaft movement and the shaft acceleration with different shaft movement progressions in different movement phases each as a diagram,

FIG. 6

a shaft with mechanical shaft drive in a schematic representation,

FIG. 7

Heald frames and an associated shaft drive according to FIG. 1 in plan view,

FIG. 8

the shaft drive of Figure 1 in a fragmentary, schematic representation,

FIG. 9

8 shows the shaft drive according to FIG. 8 in a further schematized, fragmentary illustration on a different scale,

FIG. 10

the shaft drive of Figure 8 and 9 in a sectional view,

FIG. 11

a modified embodiment of a shaft drive with switchable cams in a schematic perspective view,

FIG. 12

a schematic representation of the shaft drive with cams, in a schematic representation,

FIG. 13

a further embodiment of a mechanical shaft drive in a partially sectioned view and

FIG. 14

the shaft drive of Figure 13 in a schematic plan view.

In Figure 1 is a weaving shank 1 with associated shaft drive 2 illustrates. The weave 1 is by a formed with strands 95 provided frame, which in operation like indicated by an arrow 3 is moved up and down. To the Drive is a linkage 4, which on the weaving 1 to two or more places 5, 6 attaches and the output of the Shaft drive 2 forms. To the shaft drive 2 include a or multiple drive sources, for example in the form of motors M1, M2. These are, for example, electric servomotors, the linkage 4 via a screw jack, a Belt transmission or another, the rotational movement of the motors connected in a linear motion converting gear are. Alternatively, linear motors, linear stepper motors or similar are used. It is enough in some Cases a single engine, while in others two or more Engines are required.

The motors M1, M2 are of an example on controlled by a microcontroller-based controller C, which is connected to a memory unit M. The Control device C controls the motors M1, M2 so that the heald 1 for shedding up and down accordingly becomes. This can for example be based on two or more in the memory unit M stored curves K1, K2 take place, wherein the first curve K1 the movement of the weave shaft 1 pretends between its reversal positions, while the Curve K2 a movement of the hive 1 in his Pretends reversals. In detail, the movement of the Webshaft 1 as follows:

In Figure 3, the shaft movement is based on in the direction of the arrow 3 in Figure 1 designated X coordinate of Webschafts 1 plotted over time t. The course of the Movement is indicated by a curve I, e.g. can follow the shaft movement of a sine function. As soon as the Shank has reached its upper reversal TO, in which he Webtechnisch could persist, the curve goes I of the movement, however, in a vibrational motion with reduced amplitude and reduced acceleration over. This marks a curved branch II. The peculiarity of this Kurvenasts is that this in angular ranges of e.g. ± 15 ° around the upper reversal point TO, which is indicated in FIG Sinusoidal oscillation without technically relevant deviation follows. The special feature of the control device C the motors M1, M2 imprinted movement thus exists in that the weaving 1 in the upper reversal point TO not resting, but a vibration in a turning point area BTO executes. The effect of this measure can be on the dashed curve in the same diagram III recognize that the downside and therefore with negative sign recorded acceleration of the webshaft 1 illustrates. Follow the movement of the webshaft 1, first of sinusoidal motion, is the shaft acceleration also a sine function. In the area of the upper vertex when reaching the upper reversal point TO changes the Control device C now from the curve I to the curve II (Figure 2). This has almost the shape of a harmonious Function, so that the shape of the weaving shaft acceleration turn is similar to a harmonic function. The by the Kurvenast II or the curve II described movement of Webschaft I in his upper dead zone BTO is like that determined that the occurring in the upper reversal point TO Acceleration A2 coincides with acceleration A1, with the heald 1 arrives at the upper reversal point TO.

To illustrate the benefits of Umkehrpunktschwingung in the upper or corresponding at the lower reversal point reference is made to Figure 3, in which a dot-dash curve branch IV connects the upper vertices of the shaft movement together. If the heald shaft 1 would follow this curve IV after reaching its upper reversal point TO, the acceleration which just has the value A1 would suddenly fall to the value 0 at the time T1. The resulting acceleration peak generated on the weaving shank 1 and the strands and on all associated transmission parts loads that can lead to shaft and strand breaks. Such loads are minimized or largely limited by the pendulum movements, because by the same accelerations are kept to a minimum.
FIG. 4 illustrates that the reversal point oscillation can be sustained over several cycles. The rest phase R occurring between the first and the last vertex may extend over one, two or more cycles of the basic oscillation of the shaft movement represented by dashed lines. By fundamental vibration is meant the harmonic function, with which the heald 1 is transferred from its lower reversal point TU to its upper reversal point TO. The latter takes place during its movement phases B.

Figure 5 illustrates a modified implementation of the idea illustrated above, namely the weave 1 during its resting phase R a movement with less Imposing amplitude, with the movement in the upper Reverse point range BTO or just in a lower Reversing point area remains. Again, the vertices are the dashed basic vibration of the hedge 1, for the transfer of a reversal point in the serves other, marked by a Kurvenast V whose second time derivative in the times t1, t2, the Mark vertices of the fundamental, the same Acceleration value has the same as the fundamental. Thus is the acceleration of the heald 1 continuously or steadily, as curve branch VI illustrates. But there are curves according to Figure 3 or 4 because of the associated with them web technical advantages preferred.

The mentioned movements of the loin 1 in the phases of movement B and the resting phases R can also be used with a mechanical Shaft drive 2 can be achieved, as in the Figures 6 to 10 is illustrated. For the illustrated in Figure 6 Linkage 4 include angle lever 7, 8, the Shaft movement from the movement of a pull and push rod 9 derive and on the one hand with the weaving 1 and on the other directly or indirectly with the pull and push rod 9 are connected. This is connected to the shaft drive 2, the output side a rocker 11, the one Pivoting movement follows. The shaft drive 2 generates from the uniform rotational movement of an input shaft 12th the illustrated in Figure 6 by an arrow 13 hinund Moving movement, this movement on the weave 1 as largely harmonic oscillatory motion in Appearance occurs.

As Figure 7 illustrates, can be at a small distance several heald frames 1, 1a, 1b can be arranged one behind the other, that of the common shaft drive 2 and thus of the common input shaft 12 are driven. This is with a rotary drive device 14 connected by a Servomotor, another electric motor or an output shaft a central drive device is formed, the other organs of the loom drives.

The shaft drive 2 (Figure 7) comprises for each weave 1, 1a, 1b are each a gear assembly 15 (15a, 15b) for converting the rotational movement of the input shaft 12 in the reciprocating motion of the respective output side Levers 11 (11 a, 11 b), and a coupling arrangement 16 (16a, 16b) over which the gear assembly 15 optionally with connect to the input shaft 12 and to separate from this is. The clutch assembly 16 and the transmission assembly 15th are illustrated schematically in Figures 8 and 9. The coupling arrangement serves to control the movement of the Webschafts and is in this respect the mechanically trained here Controller C. The structure (Figure 9) is as follows:

The gear assembly 15 is replaced by an eccentric 17th formed, the lever 11 via a connecting rod 18 (Figure 7) swinging drives. The gear assembly 15 thus serves for converting the rotational movement of the eccentric 17 in a reciprocating motion. The eccentric 17 is at the same time the output element of the coupling arrangement 16 (FIG. 7), to the two input elements in the form of a first Disc 21 and a second disc 22 belong. Both Discs 21, 22 preferably have the same diameter on. However, they can also have different diameters and are for the sake of clarity in FIG 9 also illustrated with different diameters. The first disc 21 is connected to the input shaft 12 and over this connected to the rotary drive device 14. She is rotating thus evenly with substantially constant speed. This symbolizes in Figure 9, an arrow 23. The second Disk 22 is rotatably mounted about the same axis of rotation 24 like the first disc 21. However, it is not constantly turning but turning back and forth, i. rotationally oscillating or driven swinging pendulum. This is illustrated by arrow 25.

To the clutch assembly 16 of Figure 7 also belongs a switching element 26, shown in Figure 9, in the form of a Rocker 27, which pivotable about a pin 28 on the Eccentric 17 is stored. The rocker switch has a first Switching nose 29 and a second switching nose 30, wherein the Switching lugs 29, 30 on different sides of the pin 28 are arranged. The switching nose 29 are two each other 180 ° opposite recesses 31, 32 in the Disc 21 assigned. The switching nose 30, however, are two each other by 180 ° opposite recesses 33, 34th assigned. By a not further illustrated spring is the rocker switch 27 with its switching nose 29 on the Disc 21 biased towards. At its the switching nose 31 adjacent End is the rocker switch 27 with a control roller 35 provided, which thus by the spring of the rocker switch 27 in Regulated relative to the axis of rotation 24 radially outwardly is. The shape of the switching lugs 29, 30 and the recesses 31 to 34 is shown in FIG. Preferably the switching lugs 29, 30 and the recesses 31 to 34th designed so that the engagement and disengagement as possible facilitated is. These are the switching nose 29 and the front and Rear edge of the recesses 31, 32 preferably about radially oriented. The leading edge of the recesses 31, 32 is slightly lowered against the circumference to the Engaging the switching nose 29 in the recesses 31, 32nd to facilitate. By contrast, the recess 33, 34 and the switching nose 30, the reciprocating disc 22nd is assigned, preferably inclined forward against the radial. Run the locking lug 30 on the sloping trailing edge the latching recess 33, 34, the latching lug 30th pulled into the disc 22. This will be the switching process accelerated and clearly defined. Has, however, the locking lug 29 at least partially in the recess 31, 32 found and oscillates the disc 22 back, pushes their preferably rounded front edge of the locking lug 30 to the outside and thus causes the switching completely the rocker switch 27.

In addition, it may be appropriate to the rocker 27 perform two-part, so that the switching nose 29 carrying Arm and the switching nose 30 bearing arm independently from each other around the pin 28 can rotate. Thereby can during the synchronous phase, in which the discs 21, 22 briefly run synchronously, both detents 29, 30 engaged be. The period in which both detents 29, 30 engaged are, can and may be due to the division of the rocker switch 27 be larger compared to the one-piece design. By relieving the respective disengageable switching nose 29, 30, this can then at the appropriate moment from its recess Find out 31, 32 or 33, 34.

The rocker 27 are two levers 36, 37 associated (Figure 9), each one for actuating the control roller 35 serving cylindrically curved button 38, 39th exhibit. The buttons 38, 39 are approximately concentric to the rotation axis 24. The shift lever 36, 37 can, as from Figure 8 shows, pivoted radially inwards and outwards become. They are about pivot axes 41, 42 pivoted. The inner pivot position is chosen so that the switching nose 29 from its respective recess 31, 32nd is lifted when the control roller 35 at the button 38, 39 runs along. Accordingly, then the Switching nose 30 engaged in the recess 33, 34.

To actuate the shift lever 36, 37 is a cam drive 43 (Figure 8), which is connected to the input shaft 12 and, for example, has two cams. This is associated with a cam follower lever 44, which is designed as an angle lever and the shift lever 36, 37 actuated via a selection finger 45, which serves as a control clutch 46. The selection finger 45 is vertically oscillated by the cam follower lever 44 and thus actuates depending on the pivot position either the free end 47 of the shift lever 36 or the free end 48 of the shift lever 37 by the respective end 47, 48 for the time of the deflection of the cam follower lever 44 is pressed down. In order to adjust the pivoting position of the selection finger 45 as desired are on both sides of the same control magnets 51, 52 are arranged, which, when energized, pull the selection finger 45 and hold in this position.
While the disc 21 is constantly driven to rotate, the disc 22, as mentioned, driven rotationally oscillating or drehpendelnd. This purpose is a connected to the disc 22 cam follower 53 (Figure 8), for example in the form of a roller which is mounted at the end of a rigidly connected to the disc 22 lever. The cam follower 53 is actuated by a cam 54, for example, rotates at twice the speed of the input shaft 12 and has only a single survey. Thus, the disc 22 receives twice per revolution of the input shaft 12 a reciprocating motion.

The shaft drive 2 described so far operates as follows (FIG. 9):

It is initially assumed that the eccentric 17 should rotate constantly. For this purpose, the rocker switch 27 must be constant connect the disc 21 with the eccentric 17. To this to reach each of the shift lever 36 and the shift lever 37 always dodge to the outside when the rocker switch 27 as a result of the rotation of the disc 21 at the respective Shift lever comes over. These are the control magnets 51, 52 alternately driven so that the selection finger 45 pushes the end 47 down when the rocker switch 27 at the shift lever 36 passes and that the selection finger 45 the end 48 pushes down when the rocker switch 27 at the shift lever 37 passes.

The buttons 38, 39 of the shift levers 36, 37 extend over an angular range, as the switching range can be viewed. The cam follower 53 forms together with the cam 54 a pendulum drive 55th This imposes a rotary pendulum movement on the disc 22, always then synchronous with the movement of the disc 21, when the Rocker 27 passes through the switching areas. These phases of movement are characterized in that the cams of Cam drive 43 the end of the cam follower lever 44 after crowd on the outside.

During the phase of the synchronous operation of the discs 21, 22nd the clutch assembly 16 can be switched by the respective shift lever 36 or 37 does not escape to the outside. Thereby (Figure 9) e.g. the switching nose 29 from the locking recess 31 is pushed out and the switching nose 30th engaged in the recess 33. The concerned Shift lever 36 or 37 then remains activated by the shift levers 36, 37, e.g. by springs 56, 57 (FIG 8) held in its inner position and by the selection finger 45 is not moved outward. The eccentric 17 performs only a back and forth in this state Movement, because he is bound to the disc 22. The by a few degrees, e.g. 10 °, reciprocating motion causes in the upper or lower reversal point of the weave shaft only a slight up and down movement of the same at most a few millimeters. This disturbs the shedding and weaving process Not. However, it allows a synchronous restart, by only the respective shift lever 36, 37, in which the rocker switch 27 is pivoted outwards becomes. The cam drive 43 effects this at the moment of synchronization the two discs 21, 22, leaving a softer bumpless restart of the eccentric 17 takes place.

By the above-explained interplay of the clutch assembly 16 receives the weaving 1 according to the course of movement FIG. 3 or FIG. 4, in each case at the apex of FIG Dashed fundamental vibration is interposed Sleep phases and movement phases switched. Either follows the eccentric of the passing disc 21 (movement phase) or the oscillating disc 22 (resting phase). Corresponding is either the sinusoidal adjustment movement from TU to TO or go through TO to TU (move phase) or it will go through the rest phase R, in which the pendulum movement according to Curve branch II is traversed. Switching takes place during a synchronous phase S (-15 ° to + 15 ° around the vertex the movement curve of the movement phase B), in which the Vibrations of the movement phase B and the resting phase R sufficient are synchronous.

A modified embodiment of the shaft drive 2 is apparent from Figure 11. The input shaft 12 is here with provided a profile teeth and carries one of several Cams 61, 62, 63 existing disc package. The Cams 61, 62, 63 form the input elements of Coupling arrangement 16. The output element is here by a Kurvenfolgerelement formed, the outer circumference of a the cam disks 61, 62, 63 scans. This serves a role 64, rotatably mounted at one end of a rocker 65 is. The role is thus both an initial element the clutch assembly 16 as well as the other gear arrangement 15 for converting the rotational movement of the shaft 12 in a reciprocating motion. The other end of the seesaw 65 is connected via the connecting rod 18 with the lever 11 to to give this a pivoting movement. A fluid cylinder 66 may also serve to keep the roller 64 constantly against to bias the cams 61, 62, 63.

The cams 61, 62, 63 are as a package on the profiled input shaft 12 mounted axially displaceable. To shift a control fork 67 and one of these serves assigned, only schematically illustrated linear Actuator 68.

The cams 61, 62, 63 have, e.g. from FIG 12, different circumferential profiles. For example, the cam disks 61 and 63 may be used as neutral disks be formed, which is the reversing point oscillation in the upper and in the lower reversal point pretend. Are they active i.e. rolls off the roller 64 at its periphery, performs the rocker 65 a pivoting movement, so that the weave around its reversal point e.g. with double frequency in proportion vibrates to the fundamental (range R of Figure 3). At least one of the adjacent disks 61, 62, 63 has a Outer circumference, which serves as a working profile. This is in the present embodiment, the between the discs 61, 63 arranged disc 62. It has a work profile on, from an inner minimum diameter R1 to a Maximum diameter R2 and leads back from this. follows the roller 64 its profile, the shaft performs a working movement (Area B of Figure 3). In each case relative small synchronous angular ranges S1, S2 agrees the circumferential profile each with the profile of the cam 61 and 63, respectively match. The cam 61 is designed as a neutral disc, who swing the weave in a turning point leaves when the roller 64 runs at its periphery. The cam 63, on the other hand, leaves the weave in the other turning point swing when the roll runs along it. In the synchronous angle ranges S1, S2, the from the cams 61, 62, 63 existing package will be moved axially, around the roller 64 with the adjacent cam 61st or 63 to engage. That way, the movement can of the lever 11 within the synchronous areas S1, S2 smoothly switched on and off. As with the above described embodiment, the input and Turning off the drive here, too, that switching from one input element to another during one short synchronous phase happens. In the embodiment According to Figure 11, the synchronous operation refers to the radial component of movement of the roller 64 while they are in the embodiment of Figure 6 to 10 on the Rotational movement of the discs 21, 22 relates.

In the figures 13 and 14 is a modified embodiment of the reversible cam drive illustrates which manages without sliding curves. As FIG. 14 illustrates, belong to the cam drive a total of four cams 60, 61, 62, 63, wherein, for example, the cam discs Figures 60 and 62 are dashed lines in Figures 3, 4 and 5, respectively illustrated fundamental vibrations for the transfer of the weave 1 from one reversal to the other, while the cams 61, 63 the vibration in the upper or in the lower reversing point position. The use of four cams 60, 61, 62, 63 allows it, the up and down movement of a heald 1 in time to move. This will be the hedge 1, after he moved by the cam 60 in the upper reversal point was, by means of the cam 61 in a pendulum motion from which he then by means of the cam 62nd down to the lower reversal point is transferred. This is equal to a phase shift by 180 degrees. Every cam 60 to 63 each with a curve follower 71, 72, 73, 74 in conjunction. FIG. 13 illustrates the Curve follower 74, the outer circumference of the cam 63rd with two rollers 75, 76 scans.

The cam followers 71, 72, 73, 74 are pivotally mounted a rotatably mounted shaft 77, which via a lever 78 and a link 79, the rocker 11 is actuated. The wave 77 can be designed as a hollow shaft and the clutch assembly 16, optionally one of the curve followers 71, 72, 73, 74 rotationally fixed to the shaft 77 is connected. To the clutch assembly 16 is then one of the shaft 16th passing cylindrical body 81, which is for each curve follower 71 to 74 each with a radially oriented Fluid channel 82 is provided. In this sitting piston 83, 84, their flattened part-cylindrical heads for the operation of Coupling rollers 85, 86 serve. These sit in radial bores the hollow shaft 77 and can from the piston 83, 84 to pressed outside. They take into appropriate recesses 87, 88 of the respective cam follower 71 to 74 corresponding selectively accessible radial ports 91, 92, 93, 94 (Figure 14), the pistons 83, 84 of each cam follower 71 to 74 specifically targeted separately to only one of the cam follower 71 to 74 with the hollow shaft 77 to couple. In this way, one of the most the cams 60, 61, 62, 63 given movement profiles be selected, the switching in each case in the Synchronization phases according to Figure 3 to 5 takes place.

A novel shaft gearbox for harmonic in and out Turn off individual healds and derive their Motion from the rotation of a single input shaft has a coupling arrangement with two input elements 21, 22, 61, 62. During one of the input elements serves to the output element of the clutch assembly 16 to drive permanently, the other input element 22, 62 only to the output element 17 and 64 for a short time to synchronize to the first input element 21, 61. The Switching takes place in the short synchronization phases in selected Angular ranges corresponding to the upper or lower reversal point correspond to the weave. Such new shaft drives do not require a catch of the input shaft or Shaft drive for switching.

LIST OF REFERENCE NUMBERS

1, 1a, 1b

heald

95

braid

2

shaft drive

3

arrow

4

Downforce (e.g., linkage)

5, 6

Put

7, 8

bell crank

9

Pull and push rod

11

wing

12

input shaft

13

arrow

14

Drehantreibseinrichtung

15

transmission assembly

16

clutch assembly

17

eccentric

18

pleuel

21, 22

Input element / disc

23

arrow

24

axis of rotation

25

arrow

26

switching element

27

rocker

28

spigot

29, 30

switching tabs

31, 32, 33, 34

recesses

35

control roller

36, 37

gear lever

38, 39

button

41, 42

swivel axis

43

cam drive

44

Cam follower lever

45

selection finger

46

control clutch

47, 48

The End

51, 52

control magnets

53

cam follower

54

cam

55

pendulum drive

56, 57

feathers

60, 61, 62, 63

Input element / cams

64

role

65

seesaw

66

fluid cylinder

67

control fork

68

actuator

71, 72, 73, 74

cam follower

75, 76

roll

77

wave

78

lever

79

handlebars

81

body

82

fluid channel

83, 83

piston

85, 86

clutch rollers

87, 88

recesses

91, 92, 93, 94

connections

A1, A2

acceleration

B

movement phases

C

control device

K1, K2

curves

M

storage unit

M1, M2

Engines

T0, TU

Reverse position, reversal point

BTO

Reversal point range

t

Time

R

dormancy

R1, R2

radii

S

synchronous phase

S1, S2

synchronous areas

ω1, ω2

angular frequency

Claims (21)

Shaft drive for at least one heald (1) of a weaving machine,
having at least one output (4) associated with and connected to the heald (1) to hold it in resting phases (R) and to impart movement in phases of movement (B),
with a control device (C, 16) for controlling the current speed of the output (4) and thus of the hull (1),
characterized in that the output (4) also during the resting phases (R) performs a predetermined movement. Shaft drive according to claim 1, characterized in that the predetermined movement of the resting phases of the control device (C, 16) is determined. Shaft drive according to claim 1, characterized in that the output (4) at the beginning of a rest phase (R) has an acceleration which coincides with its acceleration to the end of the previous movement phase (B). Shaft drive according to claim 1, characterized in that the output (4) at the beginning of a movement phase (B) has an acceleration which coincides with its acceleration to the end of the previous resting phase (R). Shaft drive according to claim 1, characterized in that the output (4) during the resting phases (R) performs a swinging movement. Shaft drive according to claim 1, characterized in that the drive (2) a movement without sign reversal of the acceleration (Figure 5). Shaft drive according to claim 1, characterized in that the control device (C) under specification of the shaft movement one or more servo motors (M1, M2) controls position-controlled to generate the predetermined during the resting phases (R) shaft movements. Shaft drive according to claim 5, characterized in that the servomotors (M1, M2) are rigidly connected to the heald shaft (1) on the drive side. Shaft drive according to claim 1, characterized in that the drive (2) has a coupling arrangement (16) which is arranged between a drive device (14) and a gear arrangement (15) for transmitting the drive movement to the heald shaft (1),
and
in that the clutch arrangement (16) has a first input element (21) connected to the drive arrangement (14) and a second input element (22) and an output element (17) which can be selectively connected to the first or the second input element (21, 22) wherein the drive device (14) gives the first input element (21) a movement with constant direction of movement and wherein the second input element (22) is imprinted with a movement with changing direction of movement. Shaft drive according to claim 1, characterized in that the drive device (14) is a rotary drive device,
the first input element (21) is rotationally driven,
that the second input member (22) is driven to rotate back and forth and
in that the gear arrangement (15) is a device for converting a rotational movement into a reciprocating movement. Shaft drive according to claim 9, characterized in that the first input element (21,) and the second input element (22) are driven synchronously at least for a short time and that the switching is performed during the synchronous phase. Shaft drive according to claim 9 or 10, characterized in that the second input element (22) with a pendulum drive (55) is connected, which gives the second input element (22) an oscillating. Shaft drive according to claim 9, characterized in that the coupling arrangement (16) comprises means (36, 37, 46, 44, 43) with a switching member (26) permanently connected to the output member (17) and optionally to the first or the second input element (21, 22) is to be connected. Shaft drive according to claim 9 or 10, characterized in that the rotational oscillation movement of the second input element (22) to the switching means (36, 37, 46, 44) predetermined switching positions in synchronism with the rotational movement of the first input element (21) and
in that the means (36, 37, 46, 44, 43) include at least one shift lever (36, 37) associated with the shift member (26) for engaging or disengaging it at at least one predetermined shift position. Shaft drive according to claim 13, characterized in that the switching member (26) with the output member (17) is connected and rotates with this. Shaft drive according to claim 15, characterized in that the switching member (26) is a switching rocker (27) each having at least one positive-locking element (29, 30) for each input element (21, 22). Shaft drive according to claim 15, characterized in that the switching member (26) consists of two, independently of the pin (28) rotatably mounted, rockers, the time independently with their positive-locking elements (29, 30) in the locking elements (31, 32, 33, 34) of the input elements (21, 22) can enter and exit. Shaft drive according to claim 14 ,. characterized in that the shift lever (36, 37) is connected via a control clutch (46) to a cam drive (43), that the control clutch (46) has a selection finger (45) which is adjustably mounted between at least two positions to the Actuation of the shift lever (36, 37) by the cam drive (43) to activate and deactivate and that the selection finger (45) by at least one control magnet (51, 52) is movable. Shaft drive according to claim 1, characterized in that the drive (2) has a coupling arrangement (16) which is arranged between a drive device (14) and a gear arrangement (15) for transmitting the drive movement to the heald (1), and
in that the clutch arrangement (16) has a first input element (61, 63) connected to the drive arrangement (14) and a second input element (60, 62) and an output element (64) which is selectively connected to the first or the second input element (61 , 62),
wherein the first input member and the second input member are respective cams (60, 61, 62, 63) and that the output member is a cam follower (64) selectively engageable with one of the input members (60, 61, 62, 63) , Shaft drive according to claim 19, characterized in that the first input element and the second input element are in each case cam followers (71, 72, 73, 74) in engagement with different cams (60, 61, 62, 63) and that the output element is a shaft ( 77) selectively connectable to one of the cam followers (71, 72, 73, 74) in drive connection. Shaft drive according to claim 19, characterized in that the cam discs (60, 61, 62, 63) on the circumference each have a circumferential surface with a matching profile section with non-constant radius as switching area.

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