ACTUATING DEVICE

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a U.S. National Phase Application of International Application PCT/EP2014/052782 filed Feb. 13, 2014 and claims the benefit of priority under 35 U.S.C. §119 of German Application 20 2013 100 677.7 filed Feb. 14, 2013 the entire contents of which are incorporated herein by reference.

FIELD OF THE INVENTION

The present invention pertains to an actuating device, especially a shedding device on a power loom, having warp thread, wherein the device has a lifter, which is connected to a spring element capable of buckling and bending and can be connected to the mobile element, wherein the actuator forces the spring element to buckle and the lifter is moved in an oscillating manner by alternating buckling deformations of the spring element.

BACKGROUND OF THE INVENTION

Such a shedding device on a power loom is known from WO 2006/114 199 A1. Present in a multiple arrangement, it is part of a Jacquard machine. The individual device has a lifter each, which is connected to a warp thread at the lower end and to a spring element capable of buckling and bending at the upper end. The device has, furthermore, an actuator, which forces the spring element to buckle and thereby generates upwardly and downwardly bulging buckling deformations of the spring element, by which the lifter being carried is caused to perform up and down oscillating motions. The actuator in the prior-art device has hydraulic drives, which act on both sides at the ends of the spring element, are located flush opposite each other and are moved synchronously towards one another to compress and buckle the spring element. The spring element, which is designed as a bar-shaped spring assembly and is tensioned on both sides, undergoes deformation in a sinusoidal buckling mode shape according to Euler case 4. An initiator device with a cylinder, which deflects the spring element stretched in the released position upwardly or downwardly, is provided to define the upward or downward bulging of the spring.

DE 43 35 620 A1 shows another shedding device and a Jacquard machine, in which a spring element capable of buckling and bending is acted on and compressed by two control arms, which act in an articulated manner and are provided with drives. The spring element, which is designed as a metal bar here as well, performs an elastic buckling in the form of half of a sinusoidal line here according to Euler case 2.

DE 296 18 765 U1 teaches a design variant of the aforementioned device with bilaterally articulated mounting of the spring bar and with an oscillating drive on one side, wherein a buckling line according to Euler case 2 becomes established.

SUMMARY OF THE INVENTION

An object of the present invention is to provide an improved actuation technique.

The actuation technique according to the invention, with an actuating device and with the actuation method, has the advantage of having increased performance capacity and greater safety. The speed of the actuating device and of the alternatingly bulging elastic buckling deformations of the spring element can be significantly increased. At the same time, less energy is needed, and, moreover, a considerable amount of space is saved.

The motions and positions of the lifter, which depend on the buckling, can be monitored at every stroke and permanently despite high speed, and incorrect positions can be recognized in time, and they make it possible to stop the device and the shedding machine.

Further advantages are seen in an easier, better and above all less complicated initialization of the device and of a shedding machine. Due to direct, sensor-based detection of the lifter position and optionally of the motion of the lifter, the initialization can be monitored directly and above all unambiguously. It is especially favorable in this connection to carry out the initialization by means of a locking device, which locks the spring element capable of buckling and bending in the desired starting position, which is detected by means of the lifter. The locking device permits, moreover, an especially accurate and specific actuation of the adjustment and shedding, and the shed can be fixed especially over one or more strokes and kept open for several wefts.

In a preferred embodiment, the spring element elastically capable of buckling and bending is clamped nonrotatably in mountings at both ends and is compressed on one side as well as axially by an actuator. Due to the tensioning on both sides, it undergoes deformation in a complete and symmetrical sinusoidal line according to case 4 of the elastic buckling of metal bars according to Euler. Action of the actuator on one side saves space, design effort and energy. It permits a mirror-symmetrical arrangement of a plurality of devices and the actuators thereof in a shedding machine, especially a Jacquard machine.

In another embodiment, an actuator has a linearly guided slider with a mounting for the spring element capable of buckling and bending and a driver for the slider. The slider performs an oscillating motion affected by the driver and possibly the restoring spring element. This is an especially favorable embodiment in terms of design and kinematics, which is of independent inventive significance and which can be advantageously embodied both with the aforementioned first embodiment and the action of the actuator on one side and with the prior-art actuators on both sides mentioned in the introduction to the specification.

Provisions are made in another advantageous embodiment for the actuator to have a controllable locking device for fixing the spring element in a deformed buckled position. This embodiment is also of independent inventive significance and may be combined with one or both of the above-mentioned embodiments and alternatively also with the state of the art mentioned in the introduction.

In one embodiment variant, the driver is designed as a pusher and is a detachable driving connection with a slider. Interaction of the detachable driving connection with a controllable locking device, by means of which the front tensioned position of the slider and hence the tensioned bulged position of the spring element and the respective position of the lifter can be locked. As a result, the driver can become detached from the slider in case of locking and continue to move unhindered. This makes it possible to arrange a common driver for a plurality of sliders, which reduces the design effort and the effort needed for control, facilitates synchronization and increases economic efficiency.

The driver may be in a driving connection with the slider on one side, especially in a pushing driving connection during feed. The restoring forces now originate from the spring element, which is released during the return stroke. This simplifies the drive technique and makes it less expensive, and is favorable for a compact design. As an alternative, the restoring force of the spring element may be supported in another manner, e.g., by magnetic force. The driver may be in a pushing driving connection, e.g., with the slider and in a detachable restoring connection with a restoring element, especially a permanent magnet. In addition, there are several possibilities for the design embodiment of a pusher.

It is advantageous, furthermore, if the lifter has a connector for the mobile connection to the spring element capable of buckling and bending. This may be especially a sliding connection. This embodiment variant is also of independent inventive significance and may be advantageously combined with one or more of the above-mentioned other embodiments as well as with the state of the art mentioned in the introduction.

Provisions are made in an embodiment variant for the actuating device and the shedding device to have a sensor system, which detects the lifter. This embodiment is likewise of independent inventive significance and may be combined with one or more of the above-mentioned embodiment or alternatively also with one of the prior-art devices mentioned in the introduction.

Further, it is favorable in an embodiment variant if the lifter, designed as a flat bar, has a spacer for an adjacent lifter. This offers special advantages for avoiding sticking effects and undesirable mutual effects of the lifter motions on one another. This design, which likewise represents an independent invention, may be combined with one or more of the aforementioned embodiments or alternatively also with one of the prior-art devices mentioned in the introduction.

The actuation technique being claimed may be used for different purposes. Any desired mobile elements can be moved and their positions can be adjusted by the lifter. In a preferred embodiment, this is a warp thread of a power loom, and a shed, preferably a double-stroke open shed, is preferably formed by means of the adjustment thereof. The shed geometry can be defined and controlled by the defined end positions of the lifter.

The arrangement of a plurality of such a device with the one or more above-mentioned aspects of the present invention in a shedding machine, especially a Jacquard machine, offers special advantages. The shedding machine may have an especially compact design thanks to the slender design of the sliders. The adaption of the sliders to locking devices with a plurality of rows of locking elements is also favorable here. The density of lifters and the number of lifters can be increased hereby. In addition, the design of the actuator with a detachable driving connection, which is optionally arranged on one side, in connection with a locking device, is advantageous in this connection.

It is, in addition, advantageous for the increased performance capacity mentioned in the introduction and the high frequency of actuation for shedding to provide a mobile transfer device between the slider and a pusher of the actuator. Wear is reduced by this rotary mobility, and deformation of the contact points, which interferes with the function, is avoided. In addition, a common bar-shaped transmission device, which is arranged at pushers, especially oscillating levers, which are provided only individually and located at spaced locations in the axial direction, can be provided for a plurality of sliders. This saves space, design effort and energy.

In case of a multiple arrangement of actuating devices and a row of lifters in the direction of the warp thread, uniform shed geometries and warp thread angles can be set by adapting the strokes of the lifter, which can be achieved by different bulging of the spring and/or actuator strokes.

The slider design with a stop and a recess, which forms a free space for a locking element of the adjacent slider, is especially favorable for a compact and efficient embodiment. The locking element can be actuated with prestress and snaps as a result especially rapidly into the stop position.

The present invention is schematically shown in the drawings as an example. The various features of novelty which characterize the invention are pointed out with particularity in the claims annexed to and forming a part of this disclosure. For a better understanding of the invention, its operating advantages and specific objects attained by its uses, reference is made to the accompanying drawings and descriptive matter in which preferred embodiments of the invention are illustrated.

BRIEF DESCRIPTION OF THE DRAWINGS

In the drawings:

FIG. 1 is a schematic view of a Jacquard machine with a plurality of actuating devices on a power loom;

FIG. 2 is an enlarged schematic view of two actuating devices arranged one on top of another;

FIG. 3 is a simplified schematic view of an actuator;

FIG. 4 is a partially cut-away side view of a slider in different installation and rotation positions;

FIG. 5 is a partially cut-away side view of a slider in different installation and rotation positions;

FIG. 6 is a cut-sway perspective view of a plurality of sliders and locking devices;

FIG. 7 is a cut-away perspective view of a plurality of actuating devices with actuators and locking devices as well as spring elements;

FIG. 8 is a side view of a lifter;

FIG. 9 is an enlarged view of detail IX from FIG. 8;

FIG. 10 is an enlarged view of detail X from FIG. 8;

FIG. 11 is an enlarged view of detail XI from FIG. 8 with a connector;

FIG. 12 is a rear view of the connector from FIG. 11;

FIG. 13 is a side view of a mounting for the spring element with a support spring, showing the machine frame;

FIG. 14 is a side view of a mounting for the spring element with a support spring;

FIG. 15 is a perspective view of a mounting for the spring element with a support spring; and

FIG. 16 is a partially sectional view showing a variant of the actuator from FIG. 3.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The present invention pertains to an actuating device (1) and an actuation method for a mobile element (5). The mobile element (5) is designed as a warp thread in the exemplary embodiments shown, and the actuating device (1) is a shedding device with such a warp thread (5). Furthermore, the present invention pertains to a shedding machine (2), especially a Jacquard machine, with a plurality of such devices (1), as well as to a corresponding method.

FIG. 1 schematically shows a shedding machine (2) with a machine frame (4) and with a plurality of such actuating devices or such shedding devices (1). The devices or actuating devices (1) are arranged at several levels at vertically spaced locations from one another.

The shedding machine (2) is arranged on a schematically indicated power loom (3), in which a plurality of warp threads (5) are guided in a warp thread direction (k), wherein a shed (6), especially a double-stroke open shed, is formed by the controlled lifting and lowering of the warp threads (5). A weft thread can be moved in the power loom (3) through the sheds (6) in the weft thread direction (s). The warp thread and weft thread directions (k, s) are defined as the directions in which the respective threads extend. The weaving direction is designated by (w).

FIG. 2 shows two such actuating devices (1) in an enlarged view. The individual actuating device (1) has an elongated lifter (7) each, a spring element (9) capable of buckling and bending with mountings (13, 15) and an actuator (11). The lifter (7) is connected, on the one hand, to the spring element (9) elastically capable of buckling and bending and has, on the other hand, a mounting (46), e.g., a ring or an eyelet, for the mobile element (5), e.g., the warp thread.

The controllable actuator (11) acts on the spring element (9) and forces it to buckle elastically due to an axial compressive motion. The bar-shaped spring element (9) extends along the warp thread direction (k) and is clamped nonrotatably in mountings (13, 15) at both ends, and it undergoes a deformation during an axial compressive and pressure load in a symmetrical sinusoidal bending line according to Euler case 4 for metal bars subjected to buckling load.

The spring element (9) caused by the actuator (11) to oscillate undergoes deformation and alternatingly bulges in two opposite directions at right angles to the warp thread direction (k). The spring element (9) bulges and is tensioned in one direction during the compression stroke. It is again released during the load relief and return stroke and will bulge in the opposite direction during the next compression stroke. The snapping over about the stretched position of the spring element (9) is supported by the release motion and energy of the spring element. The next compression stroke immediately follows a release or the reaching of the stretched position. The spring element (9) does not preferably stop in the stretched position. It preferably also cannot become detached from the actuator (11) and released in an uncontrolled manner. The alternating bulges are usually indicated in the drawings by solid lines and broken lines. The stretched position is indicated by solid lines and both bulges by broken lines in the lowermost actuating device (1) in FIG. 1.

The lifter (7) is also moved by the alternating buckling deformations of the spring element (9) and are moved oscillatingly forward and backward or up and down in its axial direction. The lifter (7) is now directed essentially at right angles to the spring element (9) and to the warp thread direction (k). The lifter (7) is designed as a flat bar with a, for example, rectangular cross section, whose narrow side points in the warp thread direction (k). The lifter (7) preferably consists of metal. This may be stainless steel or another corrosion-resistant metal or even another suitable material. The mounting (46) is located at an end area, e.g., a lower end area of the lifter (7) and may be present as a single lifter or as a plurality of lifters.

In the area of the mounting (46), the lifter (7) has a local twisting (47). In the shedding machine (2) shown in FIG. 1, this makes it possible to arrange warp threads (k) at closely spaced locations and to bind them selectively to a row of lifters (51) extending along the warp thread direction (k). Another ring (52), an eyelet, a hook or the like may be arranged under the mounting (46), especially at the end of the lifter, and be used, e.g., to connect a tensioning or pulling device supporting the motion of the lifter.

The lifter (7) is coupled with its spring element capable of buckling and bending (9) via a connector (10), which will be explained in more detail below. During its oscillating longitudinal motions, the lifter (7) is guided in the straight direction by one or more lifter guides (44), which are designed, e.g., a guide rods and are arranged on the machine frame (4) of the shedding machine (2). The other components of the actuating device (1) are likewise arranged and supported on the machine frame (4).

The bar-shaped spring element (9) is designed as a spring assembly in the exemplary embodiments being shown and comprises a plurality of thin spring lamellae arranged in a layered manner with their broad sides on one another. The layered arrangement permits defined bulging deformations and bulging directions in a plane in parallel to the longitudinal axis of the lifter. The spring element (9) capable of buckling and bending consists at least partially of metal. The spring assembly has only metal lamellae in the exemplary embodiment being shown.

In the exemplary embodiments being shown, the spring element (9) is clamped nonrotatably in mountings (13, 15) at both ends and compressed by the actuator (11) on one side as well as axially. The clamping device (13) located opposite the actuator (11) may be arranged relatively stationarily in the machine frame (4). The other mounting (15) is arranged at the actuator (11) and is caused to perform oscillating motions forward and backward in the longitudinal direction of the spring element (9). Its stroke travel may be selected to be such that the spring element (9) is released at the end of its return stroke and assumes a straight stretched position.

According to FIGS. 1 and 2, the bulkier actuators (11) and the relatively thinner mountings (13) of the actuating devices (1) may be arranged in levels on alternating sides.

Alternating from one level to the next, the respective actuator is arranged once to the left and one to the right of the row of lifters (7). Space is saved and the density of levels is increased hereby.

In the exemplary embodiments being shown, the actuator (11) has a linearly guided slider (14) each with the mounting (15) for the spring element (9) and a driver (16) for the slider (14). The slider (14) has an elongated shape and performs an oscillating motion. This motion is directed in the warp thread direction (k) and along the longitudinal axis of the released spring element (9).

The spring element (9) may be held in a mounting (13, 15) in such a way that it is capable of performing yielding motions axially. As an alternative, the spring element (9) may be accommodated rigidly in a mounting (13, 15), and the mounting (13, 15) is arranged axially movably in the machine frame (4) or in the slider (14). Axial is defined here as the longitudinal axis of the released spring element (9). A restoring force may now act on the axially mobile mounting (13).

As is illustrated in the schematic view in FIG. 3, the spring element (9) may be axially supported in the mounting (15) at a support spring (25). As an alternative or in addition, a corresponding spring (25) may also be arranged at the other stationary mounting (13). In a variant of the embodiment shown, which variant is shown in FIGS. 2 and 13 through 15, the support spring (25) may act between a mounting (13, 15) and the external support thereof. The spring element (9) may be tensioned rigidly in the mounting (13, 15) in this case.

In the variant according to FIG. 2, the support spring (25) is arranged, e.g., as a buffer element, especially as a rubber buffer, between the mounting (13) guided axially movably and the machine frame (4). The guide may have a design similar to that of the slider (14).

FIGS. 13 through 15 show a variant of the mounting (13), which is held and guided axially movably in guides (17′) on the machine frame (4). The guides (17′) are located, e.g., on a supporting bar of the machine frame (4). The mounting (13) is fork-shaped and is designed, e.g., as a flat sheet metal part. The spring element (9) can be accommodated in the fork opening. The mounting (13) and the support spring (25) are connected to one another here and may have, e.g., a one-part design. The support spring (25) is shaped, e.g., as a leaf spring bent in a ring-shaped manner and is made integrally in one piece with the rear side of the mounting (13). The support spring (25) may be optionally elastically prestressed. It may have a closed ring shape or the openable variant shown, in which case one spring end (25′) is hung detachably and elastically on a mount (25″) of the mounting (13). The support spring (25) is, in addition, held and supported on the rear side on the machine frame (4) by means of a guide (17″).

The support spring (25) ensures uncoupling of the slider (14) from the current bulged position of the spring element (9). In a multiple arrangement of actuating devices (1), it compensates possible differences in the deformation of the spring elements (9) caused by deviations in material, dimensional tolerances, fatigue or other reasons. In addition, it facilitates the motion of the actuator when the spring element (9) comes relatively to a stop in its stretched position (closed shed) in case of a disturbance or for other reasons by creating space for the central passage through the opening prestressed spring leg. In addition, it absorbs shocks that enter the system due to disturbances.

The driver (16) is designed as a pusher in the exemplary embodiments being shown and preferably acts on the rear side of the slider (14), which side is located opposite the spring element (9). The pusher (16) is in a detachable driving connection with the slider (14). The driving connection may be a one-sided connection, especially a one-sided pressing or pushing connection. A driving connection that presses during the feed of the slider (14) and is optionally detached during the return stroke is preferably provided. The pusher (16) applies mainly forces of pressure on the slider (14) as a result. The restoring force of the spring element (9) keeps the slider (14) in steady contact with the pusher (16), which is also the case during the return stroke.

As an alternative, the release of the spring element (9) and the return stroke of the slider (14) may be supported by additional means. FIG. 16 shows such a variant of the actuator (1), in which a restoring element (54) acting on the slider (14) is arranged at the driver (16), especially at the pusher. This (restoring element) is designed, e.g., as a magnet, especially as a permanent magnet, and exerts, e.g., a pulling action on a rear-side boss (55) at the slider (14). In another variant, the restoring element (54) may be designed as an elastic mechanical pulling connection between the pusher (16) and the slider (14), which makes possible a temporary detachment of the driving connection. Furthermore, other design variants are possible. A restoring element may also exert a pushing action on the slider (14). It also does not have to have a connection to the driver (16) and may be supported, e.g., at the machine frame (4).

The pusher (16) may have various designs, e.g., as an oscillating electric or fluidic linear drive. In the exemplary embodiments being shown, especially in FIGS. 1 through 3 and 7, the pusher (16) is designed as a rotator drive. It has an oscillating lever (28) with a shaft (29) and with an oscillating shaft drive (30). The oscillating lever (28) is mounted nonrotatably on the shaft (29) and is rotated thereby oscillatingly. A plurality of oscillating levers (28) may be arranged on a common shaft (29) and driven together. The shaft drive (30) may be, e.g., a controllable electric motor, a corresponding gear mechanism being optionally arranged for the oscillation between the motor and the shaft (29). As an alternative, a single actuator (11) or each actuator (11) may have an individual drive.

The driver (16), especially the preferred pusher (16), has a mobile transmission element, which is provided for the driving contact with the slider (14) and is preferably arranged and mounted rotatably. It may be mounted at the oscillating lever (28) in a corresponding shell-shaped bearing (32), and even though it can perform a rotary motion about its axis, it cannot become undesirably detached from the oscillating lever (28). The transmission element (31) preferably has a rounded shape at least in the contact area with the slider (14). The shape is circular in the exemplary embodiment, and the bearing (32) surrounds the transmission element (31) with an angle of more than 180°.

The rotatable mounting of the transmission device (31) has the advantage that the contact point with the slider (14) changes continuously due to the rotation and settling down or another undesired deformation possibly interfering with the function is avoided. The angular momentum arises from the transmission of the pivoting motion of the pusher (16) to the linear motion of the slider (14). The bearing (32) may be lubricated to support the rotation.

As is illustrated in FIG. 7, the transmission element (31) may have a rod-shaped design and may be designed, in particular, as a cylindrical bar and extend in parallel to the shaft (29). A plurality of actuators (11) may have a common transmission element (31), which interacts with a plurality of sliders (14). The transmission device (31), designed e.g., as a flexurally rigid push rod, requires only a few oscillating levers (28) located at spaced locations from one another in the axial direction for support and mounting, so that the design effort and the moved masses are markedly reduced. The transmission device (31) may consist of a material suitable for contact transmission and wear, e.g., a compression-resistant plastic. In a variant of the embodiment being shown, an individual actuator (11) or each actuator (11) may have a transmission device (31) of its own, which is optionally disk-shaped.

As is illustrated in FIGS. 2 through 6 and 16, the slider (14) has a preferably plate-like body (18). This has a contact joint (19), especially an elastic pressing arm, for the driving connection with the driver (16), especially the transmission element (31). The preferably shell-shaped contact joint (19) and the transmission element (31) of the pusher (16) have a mutually adapted and preferably rotationally symmetrical shape at the contact point. The contact joint (19) and the pressing arm are arranged at the rear end of the slider (14) and can be cut free from the body (18) by preparing slots. The pressing arm (19) has an elongated shape tapering towards the spring element (9), as a result of which it can perform oscillating pivoting motions and adapt itself to the kinematics of the pusher. The rotary motion of the pusher (16) can be converted hereby especially reliably and with little wear into the linear motion of the slider (14).

The slider (14) consists of a suitable, solid material, e.g., metal.

According to FIG. 16, the body (18) may have a boss (55) at the rear end facing the pusher (16). This boss (55) is arranged, e.g., under the pressing arm (19) and is bent downward. It interacts with the restoring element (54), which is, e.g., magnetic and is arranged under the transmission element (31) at the oscillating lever (28). The slider (14), at least its boss (55), may consist of a ferromagnetic material, e.g., steel.

The slider (14) and its body (18) are preferably aligned with its principal plane in parallel to the longitudinal axis of the lifter (7) and to the spring element (9). The body (18) is thin-walled and may be designed, e.g., as a strip of sheet metal. This design makes it possible to arrange sliders (14) close to one another, as is shown in FIGS. 6 and 7, in the weft thread direction (s) in a shedding machine (2). The above-mentioned pusher design with the push rod (31) is especially favorable for this.

The actuator (11) has, furthermore, a controllable locking device (33) for fixing the spring element (9) in a deformed buckled position or bulged position. The locking device (33) acts on the slider (14) and locks same in a feed position. The spring element (9) can be fixed in the buckled position for the duration of one or more actuator strokes. As a result, the lifter (7) and a shed (6) formed thereby remain in the desired position over a selectable duration. Locking is possible in one or both bulged positions of the spring element (9).

Due to the detachable driving connection, the driver (16) and the transmission device (31) can become detached from the locked slider (14) and move away during the return stroke. A possible restoring connection between the driver (16) and the slider (14) can now be detached. The driver (16) can continue to run continuously, and the driving connection is restored after the locking has been released.

The slider (14) has a stop (22, 23) for the meshing of a locking device (33) on at least one side. The stop (23, 23) may have various designs. In the embodiments being shown, it is formed by the edge of an indentation at the edge of the body. The stop edge (22, 23) may be adjoined in the feed direction by an elevated edge area (24) of the body (18), which is advantageous for the prestressing function of the locking device (33), which will be explained below.

The slider (14) has, on at least one side, another recess (20, 21) on the edge of the body as a free space for a locking element (36) of the locking device (33). The stops (22, 23) and the recesses (20, 21) are arranged on a longitudinal side of the body (18).

In the exemplary embodiments being shown, the slider has a stop (22, 23) each and another recess (20, 21) on two opposite sides or longitudinal sides, said stops (22, 23) and said recesses (20, 21) being arranged axially offset in the longitudinal direction of the slider (14). This makes possible the multifunctionality of the slider (14), which can be arranged such that it is rotated by 180° about its longitudinal axis. FIGS. 4 through 6 illustrate this design. In one position according to FIG. 4, the stop (22) and the recess (20) are located at the top and the other stop (23) along with the recess (21) are located at the bottom. The arrangement is reversed in FIG. 5. FIG. 6 shows the serial arrangement of the sliders (14) in the weft thread direction (s) with alternating direction.

This design is advantageous for an especially compact embodiment of the locking device (33) and the actuators (11). According to FIGS. 3 through 7, the locking device (33) has, for each actuator (11), an armature (34, 35) with a controllable drive (37) and with an end-side locking element (36), which is preferably designed as a cam. The armature (34, 35) transmits the forces and motions of the drive (37) to the locking element (36) possibly with step-up. The controllable drive (37) is preferably a piezo drive, which has a fast response characteristic, can perform fast and short motions with a strong force and has an especially compact design.

The locking element (36) performs, e.g., a rotatory feed motion directed at right angles to the principal plane and for feeding the slider (14). As an alternative, a translatory feed motion or a combination of rotatory and translatory feed motions is possible. In another variant, a feed motion of the locking element (36) may take place in the principal plane of the slider (14) and may have, e.g., a vertical or oblique direction.

The armature (34, 35) is designed, e.g., according to FIG. 6, as a pivoting lever with an oblique axis of rotation, on the longer lever arm of which, which is directed obliquely downward towards the slider (14), a cam (36) bent sharply downward is arranged at the end. The drive (37) acts on the other, shorter lever arm. The short strokes of a piezo drive are stepped up by the armature (34, 35) into a longer stroke of the cam. The oblique axis of rotation has a directional component along the warp thread direction (k), so that the cam (36) performs said feed motion directed at right angles to the slider (14).

In a shedding machine (2) with a plurality of actuating devices (1), the locking devices (33) present in a corresponding number can be combined into a selecting device (12) for the lifter-by-lifter selective shed control. The motions of the lifters and the bulging directions of the spring elements (9) in the shedding machine (2) can be controlled independently from one another by means of the locking device (33) and the selecting device (2). Desired Jacquard patterns can be set as a result exactly and with a very high resolution due to the close packing of lifters.

FIGS. 4 through 6 show further details of the locking device(s) (33). The armatures (34, 35) and their locking elements (36) are arranged one after another at spaced locations in the longitudinal direction of the sliders (14) and the released spring element (9).

They are arranged offset in relation to one another in the weft thread direction (s) in a shedding machine (2). The rear armatures (34) with their cams (36) interact each with the one of the respective stops (23) of the sliders (14) rotated correspondingly alternatingly. The front armatures (35) with the cams (36) interact with the other stops (22). The recesses (20, 21) belonging to the respective stops (22, 23) are used as a free space for the cam of the respective other armature (35, 34). As a result, the cams (36) can perform a significant lateral feed motion without colliding with the respective adjacent slider (14) or hindering this in its motions. The recesses (20, 21) have a corresponding and optionally different length for this. Due to the armatures (34, 35) forming a row in the weft thread direction (s) and the axial offset of the rows of armatures, sufficient space is created, besides, for the locking device (33) and the components thereof, especially the drives (37) thereof, despite the sliders being arranged close to one another.

The elevated edge areas (24) of the body (18) adjoining the respective stop (22, 23) may have a stop function for the prepositioning and prestressing of the locking device (33) and the locking elements (36) thereof. If a slider (14) that is being fed shall be locked, the locking element (36) is fed laterally by a pre-actuation of the corresponding locking device (33), and it will strike first said elevated edge area (24) and is pressed on here with a prestressing force. As soon as the respective corresponding stop (22, 23) passes beyond the locking element (36) at the end of the feed motion, this locking element can snap into the locking position behind the stop (22, 23) very quickly thanks to the prestress and lock the slider (14) at or in the vicinity of the dead center of the motion thereof. The position of the stops (22, 23) and of the locking elements (36) is correspondingly coordinated with this.

The locking preferably takes place at a short distance in front of the dead center in the direction of feed of the sliders (14), and the lateral indentation behind the stop (22, 23) has a corresponding length. As a result, the locking element (36) has enough time to assume its locked position, on the one hand On the other hand, there will be a sensing clearance and the slider (14) will have an oscillating motion during feed, because the driver (16) also meshes with the locked slider (14) at the end of its oscillating driving motions, so that this slider will oscillate between the locked position and the dead center position. In addition, the sensing clearance can be used to release the locking of the slider (14), so that the locking device (33) has enough time to reset the locking element (33).

According to FIGS. 3 through 5, the slider (14) is guided axially on the machine frame (4) by means of guides (17) during its linear motions. The slider (14) has a slot-like, outwardly expanding mounting (27) at its front end. This mounting may have bent guide edges (26), with which the spring element (9) can come into contact in the bulged position and at which it can possibly be supported.

The lifter (7) has the aforementioned connector (10) for mobile connection to the corresponding spring element (9). The connector (10) may act in the middle area of the spring element (9). The connector (10) is fastened to the lifter and is designed as a guide shoe (38) with a passage opening (40) for the spring element (9) passed through at right angles. This design is shown in FIGS. 7, 8, 11 and 12.

The passage opening (40) may have a ring-like shape closed all around according to FIGS. 11 and 12. It is defined, on the one hand, by the lifter (7) and, on the other hand, by one or two U-shaped webs (40′) of the connector (10), which are located opposite. The spring element (9) is guided and held as a result on all sides at the connector (10) in the axial direction.

In another variant, not shown, the passage opening (40) may be designed as a duct that has a U-shaped or C-shaped cross section and is closed on one side, the lateral duct opening being arranged on the side facing away from the lifter (7). This may be favorable for assembly, but the quality of guiding may possibly be reduced. In a variant of this, the lateral duct opening may be undercut and make it possible to snap in the spring element (9) laterally at a correspondingly spring-loaded connector (10). This improves the quality of guiding.

The connector (10) has a slide bearing (39) with bent, especially convex bearing cams (41) in the area of the passage opening (40). FIG. 12 shows this arrangement in a rear view with a view from the rear towards the lifter (7) and the connector (10) located in front. The passage opening (40) is defined by the bearing cams (41) at the top and at the bottom, by the lifter (7) in the rear and by said webs (40′) of the connector (10) on the front side.

The connector (10) may have, furthermore, a guide (42) for an adjacent lifter (7). This is advantageous for the arrangement of lifters (7) in a row in the weft thread direction (s) in a shedding machine (2). The guide (42) may be arranged on the front side of the connector (10) facing away from the lifter (7) and may have the shape of a guide groove directed along the lifter (7). FIG. 11 shows this arrangement in a front view towards the front side of the connector (10). The guide groove may be defined laterally by elevated webs, which have a convex arch favorable for guiding.

The connector (10) consists of a low-friction material, especially a plastic, which makes easy sliding of the spring element (9) and of the adjacent lifter (7) possible and which possibly also imparts elasticity on the connector (10). The adjacent lifter can oscillate unhindered in its longitudinal direction thanks to the axial guide (42).

As is illustrated in FIGS. 1 and 2, a plurality of actuating devices (1) may be arranged one on top of another and at spaced locations from one another in a shedding machine (2). The distance is selected to be such that the spring elements (9) can bulge out unhindered by one another. A plurality of lifters (7) may be arranged here in the warp thread direction (k) at closely spaced locations next to each other in a row (51) of lifters. Lifter guides (44) arranged as multiple lifter guides secure the distance and the pushing stability of the lifters (7). The lifters (7) have all essentially the same length, and the connectors (10) within one row (51) of lifters are arranged at different levels at the lifters (7). The connectors (10) are also offset laterally in relation to one another, and they act approximately centrally on their respective spring element (9). They may all point in the same direction. In addition, they are made so narrow that there is a lateral distance from the adjacent lifters (7). The actuators (11) of this upright row of actuating devices (1) are arranged alternatingly to the left and right of the row (51) of lifters.

According to FIG. 1, there are different distances between the lifter and the interlacing point (53) within the row (51) of lifters. To obtain uniform warp thread angles at the interlacing point (53), different lifter strokes are required corresponding to the particular distance between the lifters. This can be ensured by affecting the bulging characteristic of the spring elements (9), e.g., by selecting the length or tensioned length or the material of the spring elements (9), setting the stroke of the driver or the like. These may be individual or combined measures. The goal is to achieve essentially equal energies, forces and accelerations of the spring elements (9). The lifter (7) located closest to the interlacing point (53) belongs to the topmost actuating device (1) with the smallest bulge size. The actuating device (1) of the lifter (7) located farthest away can have the greatest bulge height and the lowermost position. This may also be reversed.

The actuating devices (1) and lifters (7) are arranged in a matrix in a shedding machine (2). A plurality of the above-described arrangements of actuating devices (1) and a row (51) of lifters are arranged for this in the weft thread direction (s) at closely packed locations.

The actuators (11) are all arranged on the same side of the lifters (7) in the actuating devices (1) located at the same level in the weft thread direction (s).

To increase the buckling stability of the lifters, the lifters (7) may be guided by the spring elements (9) between the levels. Another possibility is guiding in the individual levels in the horizontal direction by means of so-called pawls, which may consist of steel or plastic.

The lifters (7) may have, furthermore, at least one spacer (45) for the lifter (7) that is adjacent in the weft thread direction (s). FIGS. 8 and 9 show this design. The spacer (45) may be designed as an additional local twisting of the band- or bar-shaped lifter body that is located at a spaced location from the mounting (46). This section-by-section oblique positioning of a lifter area by, e.g., approx. 30° is preferably present at all lifters (7). During a relative motion of adjacent lifters (7), the spacer (45) ensures the kicking-off impulse when sliding onto a normal, flat lifter area, and prevents these lifters (7) from sticking to one another. The twisting (47) at the mounting (46) may also have this effect, which is optimized in the interaction of the twisting (47).

As is indicated in FIG. 1, the individual actuating device (1) has a sensor system(8), which senses and detects the lifter. The sensor system (8) is arranged at a spaced location from the warp thread (5) and is preferably located at the opposite end area (48) of the lifter (7). In a shedding machine (2) according to FIG. 1, all lifters (7) end essentially at the same height with uniform bulging of the spring elements (9). The sensor systems (8) can be integrated as a result in a compact sensor unit at the upper area of the machine frame (4). The sensor system (8) may have any desired design. It is designed to detect one or preferably more lifter positions, especially to upper and lower end positions according to the bulging as well as optionally intermediate positions. The sensor system (8) may have one or more sensor elements (50), which are associated each with an individual lifter (7). A contactless sensor system, preferably an optical sensor system or a field sensor system with Hall sensors, is preferably used. To establish the reliability of detection, it is favorable to define a sensing area (49) at the lifter (7), e.g., at the tip thereof, e.g., by shaping, the selection of the material or the like. The sensing area (49) may also be optimized for guiding and sealing purposes.

The actuating device (1) may have a suitable control (not shown), which is connected to the actuator (11), the locking device (33) and the sensor system (8). In case of a multiple arrangement of actuating devices (1) in a shedding machine (2), these controls may be integrated in a machine control, which also actuates the selecting device (12). This may be an internal or external control. Furthermore, it is possible that a higher-level control is present for a multiple arrangement of shedding machines (2). In a Jacquard machine (2), the pattern specifications are read into the control and outputted to the selecting device (12) for the selective control of the lifters by specific locking

The respective control can monitor the function of the actuating device(s) (1) permanently and during each stroke of the lifter. It can be determined by means of the sensor system (8) whether the lifter (7) is moving in the specified manner and whether it assumes the specified position. The locking device (33) and the selecting device (12) can also be monitored for correct function on the basis of the lifter position. Lifter errors and disturbances can be recognized in time by the control, especially in case of a high-resolution sensor system (8), and the actuating device(s) (1) can be stopped, if necessary, to avoid weaving errors.

An actuating device (1) and also a shedding machine (2) can be referenced at start-up, and the lifter(s) (7) is/are brought into a specified position. The actuator or the actuators (11) are switched on for this and the lifter(s) (7) is/are fixed in the desired position with the corresponding locking device (33).

Various modifications of the embodiments shown and described are possible.

As an alternative, the shedding machine (2) or Jacquard machine may be arranged under a power loom or, in another variant, above and under a power loom (3), in which case the arrangement shown in FIG. 1 can be correspondingly turned over or split and partially turned over. The shedding can be supported by tensioning or pulling devices additionally acting on the lifters (7).

The design of the actuator (11) and especially the driver (16) may be modified. The drive kinematics for the slider (14) for the compressive load of the spring element (9) may be varied by applying a combination instead of compressive forces and pulling forces.

Furthermore, the features of the above-described exemplary embodiments may be combined with one another or replaced as desired. The features of claims 2, 3, 4, 7, 24, 29 and 32 for the above-mentioned independent aspects of the invention may each be combined with the preamble of claim 1 to characterize the corresponding invention.

The actuating device (1) may be used for purposes other than for the shedding described in a Jacquard machine (2). The mobile element (5) may correspondingly be designed in another manner. The directions indicated for the warp thread direction and the weft thread direction (k, s) will change correspondingly.

Furthermore, a plurality of actuating devices (1) with their lifters (7) may operate synchronously and act on a common mobile element (5). This may be, e.g., the shaft frame of a shaft machine. In addition, there are any other fields of use in textile machines or in other industrial areas. The mountings (46) at the lifters (7) may have a corresponding design for this, e.g., they may be designed, e.g., as hooks, swivel joints, screw or riveted connections, magnets or the like.

In one variant of the above-described actuating device (1) and shedding machine (2), a bilateral action of the actuator on the ends of a spring element (9), which ends are tensioned nonrotatably, is possible, as this is described, e.g., in WO 2006/114199 A1. Individual above-described components or all the above-described components of the actuating device (1), especially the slider (14), the locking device (33), the driver (16), the connector (10), the spacer (45) and the sensor system (8) may be used in any desired combination in such a variant. For example, sliders (14) with a respective mounting (15) and optionally with a support spring (25) are arranged at each spring element (9) at both ends in this case.

In another variant, the actuating device (1) according to DE 43 35 620 A1 or DE 296 18 765 U1 may be designed with an actuating device tensioned in an articulated manner on both sides and with an actuator located on one side or on both sides. One or more of the above-described components of the actuating device (1), especially the driver (16), the connector (10), the spacer (45) and the sensor system (8), may likewise be used in his variant.

While specific embodiments of the invention have been shown and described in detail to illustrate the application of the principles of the invention, it will be understood that the invention may be embodied otherwise without departing from such principles.