JP2006176947A - Direct hydraulic servodrive for heald shaft - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heald shaft drive which can simply be controlled and give a large operation rate. <P>SOLUTION: The heald shaft drive comprises preferably hydraulic servodrive units (6, 7) flange-attached to the sides of a heald shaft (1). The hydraulic servodrive units (6, 7) comprise movement-measuring systems. The system sets the position of a desired heald shaft through their self position-adjusting circuits. Both the drive units (6, 7) are controlled with common guide signals generated from a common nominal value generator. This kind of direct driving gives a heald shaft drive which is mechanically strong, is little vibrated, and is used for highly flexible uses. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a drive for a loom heald shaft.

  In most of today's looms, heald shafts are used for shed formation. In shed formation, waving warp yarns from the warp surface is necessary to introduce the weft yarns to make the fabric. For this purpose, the warp is pulled through the heald. The healds are seated on the respective shaft plates by eyelets at the upper and lower ends. The upper and lower shaft plates are supported by a frame-like structure called a heald shaft which extends over the entire width of the knitted fabric to be produced and must be moved up and down continuously. Strict requirements are set for the relevant drive in terms of acceleration force to be applied and operating speed to be achieved.

  Patent Document 1 describes a piston / cylinder assembly in which a heald shaft is used as a drive unit. Each assembly has a cylinder in which a piston held movably is disposed. The piston is provided with a respective piston rod protruding from the cylinder at both ends at each end face. The upper piston rod is connected to the upper shaft rod of the heald shaft by traction means, while the lower piston rod is connected to the lower shaft rod of the heald shaft by another traction means.

  Such an arrangement faces difficulties at high operating speeds.

  A similar device is disclosed in Patent Document 2 (an application published without examination). The hydraulic or pneumatic cylinder used for the drive is mechanically controlled by a cam disk that operates the air supply valve.

  This arrangement cannot be employed to achieve higher operating speeds.

  U.S. Pat. No. 6,057,089 describes the operation of a heald shaft by a fluid cylinder. The piston rod is connected to the heald shaft from below and applies force to it. Each fluid cylinder only has one piston rod. The rod protrudes from the cylinder on one side and is connected to the heald shaft. When the reciprocating motion occurs, a swing load is applied to the piston rod in which the traction force and the pushing force alternate. There is a need for a rigid, especially torsion resistant piston rod design that increases the applied mass and limits the operating speed of the device with respect to pressure loading.

  Patent Document 4 proposes a direct drive of a heald shaft by a pressurized fluid. For this purpose, the upper and lower shaft rods are each I-beams. The web traverses the lateral groove of the elliptical tube where it is held sealed. The elliptical tube serves as a fluid cylinder with an extension formed in the web separating the upper and lower working chambers. By applying pressure to one or the other chamber, the entire heald shaft moves in one or the other direction.

  Such devices are based on a particular heald shaft structure and are often impractical.

  From Patent Document 5, it is known to drive an embroidery frame of an embroidery machine by a hydraulic motor directly connected to the embroidery frame. The hydraulic motor is controlled by a multi-directional control valve that is operated by an electric stepping motor.

  According to Patent Document 5, it is further known that a valve for controlling the hydraulic motor is provided in the adjustment circuit of the tracking device. This device generates an operation amount for setting an embroidery frame based on a comparison between standard and actual values. As a starting point, the desired movement is given in advance by an analog electrical quantity, such as a voltage, and the comparison between this nominal value and the actual value becomes a pulse that affects the electrohydraulic control valve. The hydraulic motor starts to move according to the magnitude and direction of this pulse, and then the required stop is initiated by a new comparison of standard and actual values. On the basis of this, it has been proposed to perform positioning of the embroidery frame by a hydraulic cylinder controlled by a stepping motor without adjusting the position in order to realize a higher operation speed.

DE 3120097 DE 1813411 United Kingdom Patent No. 591904 DE 1802118 DE 2452631

  It is therefore an object of the present invention to provide a heald shaft drive that can be easily controlled and provides a high operating speed.

  This object is achieved by a heald shaft drive as defined in claims 1 and 15.

  The heald shaft according to the invention as claimed in claim 1 has a double-acting hydraulic cylinder. The piston rod protrudes from the hydraulic cylinder on both sides. Both ends of the piston rod are directly connected to the heald shaft or indirectly connected by a hard intermediate carrier. Eventually, the prior art traction means that are usually used to convey the setting movement have become unnecessary. By connecting the upper and lower ends of the piston rod of the hydraulic drive directly to the heald shaft, compared to the hydraulic drive that has used a connecting chain with levers, brackets, etc. to establish the connection between the hydraulic drive and the heald shaft, There is an advantage that a higher operating speed can be obtained. The piston rod may be relatively thin. Thus, the mass inertia force associated with the hydraulic drive is minimized. A rigid connection, i.e. a statically determined connection between the end of the piston rod and the heald shaft, does not preclude the formation of a separation / connection position between the piston rod and the heald shaft. Anyway, there are no brackets with flexible or combined traction means, articulated supports and the like.

  In principle, the hydraulic cylinder is also arranged, for example, under the heald shaft, but is preferably arranged adjacent to the binder. Such an arrangement results in a short force transmission path and therefore the entire assembly becomes stiff accordingly and can be moved very dynamically. Preferably, both piston rods are exposed to pressure only, i.e. designed as extruded parts. Force transmission occurs in both piston rods of the cylinder only by pushing. The upper piston rod pushes the heald shaft upward during the upward stroke, while the lower piston rod accelerates the heald shaft downward during the downward stroke. Such an arrangement results in a particularly compact structure.

  According to a preferred embodiment, each hydraulic cylinder is arranged in both end binders of the heald shaft. The hydraulic cylinders are controlled synchronously and the heald shaft performs linear motion. For holding, at least in the case of a very wide heald shaft, one or more additional hydraulic drive units are provided. Such an additional drive unit is preferably arranged under the heald shaft and connected to the lower shaft rod. They are preferably arranged in a position where the shaft rods are connected to each other by an intermediate binder. Such an arrangement reduces the dynamic bending of the heald shaft.

  An adjacent heald shaft hydraulic cylinder is coupled to the cylinder block. This block is relatively thin and allows a compact, fast but quietly structured loom construction. The cylinder block of the hydraulic cylinder is preferably connected directly to the valve block so that the hydraulic pipe between the valve and the hydraulic cylinder is short and stiff. This arrangement results in reduced vibration as well as a direct connection of the end of the piston rod to the intermediate carrier or end binder. A better transmission behavior is obtained between the predetermined movement curve and the actual movement performed by the heald shaft. Furthermore, a high system pressure of, for example, 160 bar and a low volume flow of, for example, a cylinder of only 60 l / min are possible. More than 1000 bumps (pick) are realized per minute.

  In a preferred embodiment, the end of the piston rod is not directly connected to the end binder but via an intermediate carrier. The latter is a force that further guides the heald shaft and that is transmitted radially to the piston rod and serves to separate the hydraulic cylinder from the force generated by the heald shaft.

  The piston rod is connected to the movement measuring device directly or instead, for example, indirectly via an intermediate carrier. This device continuously measures the actual position of the heald shaft drive and applies the signal as an actual value to the adjustment circuit. The control device compares the actual value with the nominal value and controls the valves of the valve block so that the deviation is minimized. In this way, a real hydraulic servo drive is obtained. As a result, the heald shaft moves linearly in response to the guide signal. By means of a corresponding application of control signals, for example by computer control, virtually any movement curve is predetermined and obtained. For example, a motion curve is obtained in which the acceleration peak is minimized and therefore lower heald shaft vibrations are expected.

  Coupled to the two drive units are their own positioning circuits, which preferably operate according to a joint predetermined value, but the other functions are independent of each other. For this purpose, each position adjustment circuit has its own movement sensor and its own adjustment amplifier. In addition, a monitoring unit is provided, which monitors the adjustment deviation of both adjustment circuits and emits a signal if the difference in adjustment deviation is excessive. The signal acts as a shutoff signal.

  Furthermore, the movement measuring device can be directly connected to the heald shaft and its position can be detected, for example, in an intermediate region. By this means, the heald shaft vibration is canceled out.

  The movement of the heald shaft is simply synchronized with the loom drive by synchronizing a given signal at the loom operating speed. In this way, fluctuations in the operating speed of the loom are automatically taken into account during machine start-up, machine stop or low speed operation.

  The details of other advantageous embodiments of the invention are the subject matter of the specification, drawings or claims.

  The drawings illustrate embodiments of the invention.

  FIG. 1 shows a group of heald shafts having a heald shaft 1. The heald shaft carries a heald (not shown) and serves as a shed formation in the loom. The heald shaft 1 has an upper shaft rod 2, a lower shaft rod 3, and end binders 4, 5 that form a rectangular frame with the upper and lower shaft rods 2, 3. The rectangular frame serves to accommodate a heald (not shown). Drive units 6 and 7 are provided to drive the heald shaft 1 and other heald shafts that are of substantially the same structure but cannot be considered separately. These units are connected to the end binders 4, 5 of the heald shaft 1 or the right or left ends 8, 9, 11, 12 of the shaft rods 2, 3, respectively.

  The drive units 6 and 7 are arranged in mirror image symmetry. They have the same, almost the same or similar structure and are only placed on the mirror image object. Therefore, the following description of the drive unit 6 applies to the drive unit 7 as well. The drive units 6, 7 serve to drive the heald shaft in the first position, but also serve as guides for them. See FIGS. 2 and 3 for this connection. The heald shafts are each relatively short (flat) relative to the longitudinal warp direction as can be seen in FIGS. For example, the heald shaft has a length of only 12 mm as measured in the longitudinal direction of the warp. The heald shafts abut against each other and are held at a small distance from each other by friction reducing spacers or riders. The end binder 4 (and thus also the end binder 5) has a guide groove 13 that extends vertically across a narrow side surface outside the end binder 4 on the side facing the drive unit 6 (and 7 respectively). The guide element 14 serves as a guide for the end binder 4 and the heald shaft 1. The guide element 14 is a lateral carrier from which a series of protrusions protrude. Each protrusion 15 extends into an associated guide groove 13 in each end binder 4 and thereby constitutes a vertical sliding guide.

  The guide element 14 is flanged to a side installation surface of the guide body 16 connected to the cylinder block 17. The guide body 16 has a rectangular basic shape. On the side facing the guide element 14, the guide body 16 has a series of vertical guide channels 18. This channel has, for example, a rectangular cross section as shown in the figure. As can be seen in particular from FIG. 5 and also from FIGS. 1, 3, 4 and 6, the guide channel 18 acts as a sliding guide for the guide bar 19. Each guide bar 19 forms a portion of a thread (carriage) 21 that is guided so as to move vertically in the guide channel 18. In this embodiment, the guide is of a sliding type, but it is understood that a rolling element guide such as a roller guide is also used.

  The guide bar 19 is coupled or coupled to the respective coupling members 22 and 23 at both the upper and lower end portions. The rigid connecting members 22 and 23 have connecting devices 24 and 25 on the surface facing the end binder 4. This connecting device is designed to establish a connection with the end binder 4 or the ends 8, 9, 11, 12 of the shaft rods 2,3. On the surface away from the connecting devices 24 and 25, the connecting members 22 and 23 have protrusions 26 and 27. The protrusions define a wide opening therebetween, and have flat surfaces that extend preferably parallel to each other. The cylinder block 17 is thus arranged in the opening area. The distance between the length of the guide bar 19 and the opposing flat surfaces of the protrusions 26, 27 is dimensioned so that the thread 21 performs a vertical stroke sufficient for shed formation in the guide body 16. In this embodiment, the distance is 150 mm, for example.

  The cylinder block 17 has a plurality of cylinder holes 28. The number matches the number of protrusions 15 and is equal to the number of threads 21. The cylinder holes 28 are arranged in two rows arranged in a zigzag manner or in more rows if necessary. Thus, as shown in this example, the diameter of each cylinder bore 28 is greater than the 12 mm heald shaft width. As can be seen from FIG. 5, the lengths of the protrusions 26, 27 of the thread 21 are sized so that both rows are bridged by the cylinder holes 28. The cylinder holes 28 extend parallel to the guide bars 19 and their guide channels 18. In each cylinder hole 28 a sealed vertically movable piston 29 is arranged. In this embodiment, it is sufficient if the piston 29 has a single seal.

  The piston 29 is connected to the piston rod 31. The rod extends through upper and lower working chambers 32, 33 separated by a piston 29. Further, the piston rod 31 extends through the closing members 34 and 35. These members are provided with through-holes 36, 37 suitable for this purpose and are arranged at the upper and lower parts of the cylinder block 17 to close the working chambers 32, 33, respectively. Preferably, respective hydrodynamic piston rod bearings are arranged in the through holes 36, 37. Such a bearing allows high speed of the piston rod. The sealing is preferably done by a contactless clearance seal that minimizes friction.

  The piston rod 31 has respective flat or very slightly convex end faces 38, 39 at both the upper and lower ends. The end face engages the flat surface of each protrusion 26, 27 without play. In this way, all movement of the piston 29 is transmitted directly to the sled 21.

  A valve block 41 having a switching valve 42 (a solenoid valve or a valve controlled by an electric motor) that is electrically controlled to pressurize or depressurize the working chambers 32 and 33 is flange-mounted on the cylinder block 17. Corresponding fluid channels 43, 44 are processed directly into the valve block 41. They may be connected directly to the cylinder block 17 or connected to the closing members 34, 35 by short connecting tubes 45, 46 as shown. At least one switching valve 42 is coupled to each piston 29, that is, each cylinder hole 28.

  A movement measuring device 47 is provided for accurate detection of the movement of the piston 29 and in particular the sled 21. The movement measuring device 47 has a scale display body 48. For example, the body is connected to the thread 21, moves together with the thread 21, and extends through the hole of the guide body 16. An associated sensor 49 (shown schematically in FIG. 7) is disposed on the guide body 16. The movement measurement device 47 distributes electrical, analog or digital measurement values representing the instantaneous movement position of the sled 21.

  FIG. 7 schematically shows the hydraulic system of the heald shaft drive 1 according to the present invention in an example in which the two hydraulic cylinders of the drive units 6, 7 drive the heald shaft 1. For identification purposes, elements of the drive unit 6 associated with the end binder 4 are labeled “a” and elements of the drive unit 7 associated with the end binder 5 are labeled “b”. Reference numbers without character codes apply to both drive units 6 and 7. The reference numbers introduced earlier are also used here.

  In order to control the hydraulic cylinders of the drive units 6, 7, a control device 51 having position adjusting circuits 52a, 52b is provided for the respective hydraulic cylinders of the drive units 6, 7. Both position adjustment circuits receive a predetermined value or nominal value from the nominal value generator 53. The generator is coupled to the loom via conductor 54 and receives a clock signal therefrom. This signal is a continuous or periodic signal and represents the operating speed of the loom. The nominal value generator 53 generates a guide signal that is preferably continuous in time as a standard signal. The guide signal is a time function describing the desired movement of the heald shaft 1. In the simplest case, it is considered the starting point where the nominal time function is equal to the desired heald shaft motion time function.

  The control device 51, ie the position adjustment circuits 52a, 52b, has analog or digital differential amplifiers 55a, 55b which receive a nominal value signal at the input and an actual value signal provided by sensors 49a, 49b at another input. . The generated differential signal is applied to the adjustment amplifiers 56a and 56b. The adjustment output signal serves to control the solenoid valves (solenoid valves) 42a and 42b. The solenoid valve is preferably a two-stage hydraulic pre-control servo valve with negative overlap and mechanical reset. Solenoid valves 42a and 42b are switching valves and block channels 43 and 44, or connect them to pressure source P in the same rotational direction or instead, or connect them to oil pan T. The pressure source P is preferably a constant pressure system with a pressure-regulating transfer pump and a constant pressure system with a hydraulic accumulator not shown to absorb volume flow peaks. Furthermore, an oil cooler is provided in order to eliminate heat loss that occurs as a result of energy loss.

  According to the improved embodiment, the nominal value generator is improved in the following respects. In other words, depending on the operating speed of the loom, for example, the temporal course of the nominal value can be deviated from the actually desired movement curve of the heald shaft. This relates to a definitive pre-determination of the nominal value in order to take into account the adjustment deviations that appear at the instantaneous working speed and to measure the actual nominal value of the moment. This is done so that the desired nominal value is actually obtained while taking into account the adjustment error (adjustment deviation) and the actual operating speed that appear in such a nominal value. Therefore, it can be said that the limit error generated depending on the speed by the regulator is added to the nominal value.

  The heald shaft drive operates as follows.

  The heald shaft 1 engages at least one coupling device 24 or two coupling devices 24, 25 in two end binders 4, 5 and is vertically guided vertically as prescribed. For this purpose, drive units 6, 7 having at least one hydraulic cylinder for each heald shaft are provided. In order to start the movement of the heald shaft, the control device 51 receives a guide signal, for example an electrical signal representing the angular position of the main shaft of the loom, via a conductor 54. In accordance with this signal, a nominal value generator 53 produces nominal values for the position adjustment circuits 52a, 52b that operate independently of each other in parallel. The regulators 56a and 56b in the position adjustment circuits 52a and 52b determine an existing deviation between the nominal value and the actual value measured by the sensors 49a and 49b, and apply a corresponding control signal to the electromagnetic valves 42a and 42b. The latter applies pressure to the working chambers 32a, 32b or 33a, 33b so that both pistons 29a, 29b move to the same desired vertical nominal position. Therefore, the piston rods 31a and 31b cause the sled 21 of the drive units 6 and 7 to move in synchronism with the desired position, thereby setting the heald shaft 1 at the desired position. During machine operation, the nominal value generator 53 constantly changes the nominal value. Thus, the pistons 29a, 29b constantly follow the nominal value signal, while the pistons are controlled by the piston adjustment circuits 52a, 52b at each instant. In this way, shed formation is performed by the controlled vertical movement of the heald shaft 1.

  In a preferred embodiment, the nominal value generator performs a small amplitude vertical vibration at both the upper and lower end positions of the heald shaft 1. These positions are considered stationary positions. Such vertical vibration prevents sudden changes in acceleration of the heald shaft that occur when the heald shaft is braked to zero speed and maintained at zero speed. In this way, such heald shaft vibrations in the upper and lower end regions of the stroke prevent wobble from appearing and thus avoid unintentional vibrations in the heald shaft.

  By driving the heald shaft directly without a transmission member, vibrations are reduced and drive motion is transmitted to the heald shaft 1 substantially without distortion. Limit errors caused by mass inertial and frictional forces and vibrations are minimized. Held shafts that swing in the upper and lower regions of the end position may be made to minimize acceleration. This reduces the load on the heald shaft and reduces the energy requirement. The stroke of the heald shaft can be adjusted. For example, the width of the shed opening can be adapted to a size suitable for a particular fabric. This is done by adapting the corresponding magnitude to the nominal value generator 53.

  The heald shaft drive according to the invention preferably has hydraulic servo drive units 6, 7 that are flanged on the side of the heald shaft 1. The hydraulic servo drive units 6 and 7 have a movement measurement system for setting a desired heald shaft position by means of respective position adjustment circuits. Both drive units 6, 7 are controlled by a common guide signal emitted by a common nominal value generator. This type of direct drive results in a heald shaft drive that is more mechanically stiff, has less vibration, and is very flexible in application.

FIG. 5 is a simplified perspective view of a heald shaft drive associated with a group of heald shafts. It is a top view of the heald shaft of FIG. FIG. 3 is a detailed view of FIG. 2 at different scales. FIG. 2 is a perspective view of a heald shaft drive on one side of the heald shaft of FIG. 1. FIG. 5 is a longitudinal sectional view of the heald shaft drive according to FIG. 4. 6 is a plan view of the heald shaft drive of FIGS. 4 and 5. FIG. It is the schematic of the control apparatus for controlling a held shaft drive.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Held shaft 2,3 Upper shaft rod, Lower shaft rod 4,5 End binder 6,7 Drive unit 8,9,11,12 End 13 Guide groove 14 Guide element 15 Protrusion 16 Guide body 17 Cylinder block, cylinder Body 18 Guide channel 19 Guide bar 21 Thread, intermediate carrier 22, 23 Connecting member 24, 25 Connecting device 26, 27 Protrusion 28 Cylinder hole 29 Piston 31 Piston rod 32, 33 Operating chamber 34, 35 Closing member 36, 37 Through hole 38, 39 End face 41 Valve block 42 Solenoid valve (switching valve)
43, 44 Fluid channel 45, 46 Connecting pipe 47 Movement measurement device 48 Scale display body 49 Sensor 51 Control device 52 Position adjustment circuit 53 Nominal value generator 54 Conductor 55 Differential amplifier 56 Adjustment amplifier P Pressure source T Oil pan

Claims (28)

At least one double-acting hydraulic cylinder comprising a cylinder body (17) having an upper closing member (34) and a lower closing member (35);
A cylinder hole provided in the hydraulic cylinder, which is held so that the piston (29) can move, and a piston rod (31) connected to the piston (29)
A heald shaft drive for the lodge heald shaft (1) with
Each closing member (34, 35) has a through hole (36, 37),
The piston rod has an upper end extending through the through hole (36) of the upper closing member (34) and a lower end extending through the through hole (37) of the lower closing member (35);
A heald shaft drive in which both ends are connected to the heald shaft (1) either directly or via an intermediate carrier (21).   2. Held shaft drive according to claim 1, characterized in that the hydraulic cylinder is arranged adjacent to the side of the end binder (4, 5) of the heald shaft (1).   2. Held shaft drive according to claim 1, characterized in that a hydraulic cylinder is arranged on the heald shaft (1) adjacent to the sides of both end binders (4, 5).   The heald shaft drive according to claim 1, characterized in that a plurality of hydraulic cylinders are integrated into the cylinder block (17) to drive the plurality of heald shafts.   2. Held shaft drive according to claim 1, characterized in that a hydraulic cylinder is connected to a valve block (41) having an electrically controllable valve (42) for controlling the pressurization of the piston (29).   The intermediate carrier (21) is a sled held so as to be movable in the guide direction by a guide device (18, 19), the guide direction coinciding with the direction of movement of the piston (29). Held shaft drive as described in.   2. Held shaft drive according to claim 1, characterized in that the intermediate carrier (21) comprises at least one coupling device (24) for attachment to the heald shaft (1).   2. The intermediate carrier (21) according to claim 1, characterized in that it comprises at least one coupling device (24) for attachment to the end binder (4, 5) of the heald shaft (1). Held shaft drive.   7. Guide device (18, 19) comprising at least one guide element (15) for guiding the end binder (4, 5) of the heald shaft (1). Held shaft drive.   2. Held shaft drive according to claim 1, characterized in that the piston rod (31) is connected to a movement measuring device (47) which emits a signal corresponding to the actual position of the piston rod (31).   11. Held shaft drive according to claim 10, characterized in that the movement measuring device (47) is connected to an intermediate carrier (21), an end binder (4, 5) or a heald shaft (1).   11. Held shaft drive according to claim 10, characterized in that the movement measuring device (47) and the valve block (41) are connected to a control device (51) for controlling the heald shaft drive.   The control device (51) is a position adjustment device (52) for adjusting the position of the actual heald shaft corresponding to a given time-varying signal, and for each hydraulic cylinder its own position adjustment. 13. Held shaft drive according to claim 12, characterized in that a circuit (52a, 52b) is provided.   14. A heald shaft drive according to claim 13, wherein the given signal is synchronized with the operating speed of the loom. At least one double-acting hydraulic cylinder having a cylinder body (17) with at least one closing member (34) having a through-hole (36);
A piston (29) held movably in the cylinder bore (28) of the hydraulic cylinder;
A piston rod (31) connected to the piston (29), having an end passing through the through hole (36) of the closing member (34) and connected to the heald shaft (1);
A movement measuring device (47) emitting a signal corresponding to the actual position of the piston rod (31);
A valve block (41) for controlling the pressurization of the piston (29), and a control device (51) connected to the valve block (41) and the movement measuring device (47) for controlling the hold shaft drive
A heald shaft drive for the lodge heald shaft (1).   16. Held shaft drive according to claim 15, characterized in that the control device (51) is a position adjusting device (52) for adjusting the actual position of the heald shaft corresponding to a given signal which varies over time. .   The heald shaft drive of claim 16, wherein the given signal is synchronized with the operating speed of the loom.   16. A heald shaft drive according to claim 15, characterized in that the hydraulic cylinder is arranged adjacent to the side of the end binder (4, 5) of the heald shaft (1).   16. A heald shaft drive according to claim 15, characterized in that a plurality of hydraulic cylinders are integrated in the cylinder block (17) in order to drive a plurality of heald shafts.   16. Held shaft drive according to claim 15, characterized in that a hydraulic cylinder is arranged on the heald shaft (1) adjacent to the sides of both end binders (4, 5).   The cylinder body (17) has an upper closing member (34) and a lower closing member (35), and each closing member (34, 35) has a respective through hole (36, 37). 16. A heald shaft drive according to claim 15, characterized in that: The piston rod (31) connected to the piston (29) passes through the upper end extending through the through hole (36) of the upper closing member (34) and the through hole (37) of the lower closing member (35). And has a lower end extending
The heald shaft drive according to claim 21, characterized in that both ends are respectively connected to the heald shaft (1) directly or via an intermediate carrier (21).   23. A heald shaft drive according to claim 22, characterized in that the end of the piston rod (31) is rigidly connected to the heald shaft (1) or the intermediate carrier (21).   The intermediate carrier (21) is a sled held so as to be movable in the guide direction by a guide device (18, 19), the guide direction being coincident with the movement direction of the piston (29). Held shaft drive as described in.   23. A heald shaft drive according to claim 22, characterized in that the intermediate carrier (21) comprises at least one coupling device (24) for attachment to the heald shaft (1).   23. The intermediate carrier (21) according to claim 22, characterized in that it comprises at least one coupling device (24) for attachment to the end binder (4, 5) of the heald shaft (1). Held shaft drive.   25. The guide device according to claim 24, characterized in that the guide device (18, 19) comprises at least one guide element (15) for guiding the end binder (4, 5) of the heald shaft (1). Held shaft drive.   16. Held shaft drive according to claim 15, characterized in that the movement measuring device is connected to an intermediate carrier (21), an end binder (4) or a heald shaft (1).

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