Vibration damping device for a winding device of a cross-coil manufacturing textile machine

Description

[0001] The invention relates to a vibration damping device for a winding device of a textile machine producing cross-wound bobbins for reducing the vibrations occurring on the pivotably mounted bobbin frame during the winding operation of the textile machine.

[0002] In textile machines that produce packages, such as open-end rotor spinning machines or automatic package winders, there is always a risk of strong vibrations of the creel during winding. Particularly at the beginning of a package's travel and during the production of relatively hard packages, there is often a risk that the amplitude of the frame vibration will become so large that the winding process is significantly impaired, resulting in packages that are subsequently difficult to unwind and therefore unusable.

[0003] To prevent the production of such inferior cross-wound bobbins, the pivoting bobbin frames of the winding devices on conventional spinning or winding machines are usually equipped with a vibration dampening device. This means that the pivoting bobbin frame, which has two bobbin frame arms for freely rotating a cross-wound bobbin, is equipped with a dampening device designed to ensure that the vibrations of the bobbin frame, which are almost unavoidable during winding, are minimized as much as possible.

[0004] Such damping devices for pivotally mounted coil frames have been known for a long time and are described in the patent literature in various embodiments, some of them relatively extensively.

[0005] For example, vibration damping devices that feature a damping and lifting cylinder are state-of-the-art. Such damping and lifting cylinders comprise a pneumatically operated device for the defined lifting of a package held in the creel from its drive or support roller, as well as a hydraulically operated damping device. The damping device preferably uses oil as the damping medium. This means that by influencing the flow of the liquid damping medium, a reduction in the creel vibrations that occur during winding is achieved.

[0006] A vibration damping device designed in this way is described, for example, in the "AUTOCONER 238" manual from Schlafhorst on pages 01.3.9 and 01.3.11.

[0007] Similar vibration damping devices for the winding devices of textile machines producing cross-wound bobbins are also known from DE 41 21 780 A1, DE 195 34 333 A1, and DE 100 46 603 A1. This means that these patent applications also describe winding devices in which the damping devices for the bobbin frame are designed as hydraulic cylinders.

[0008] In DE 41 21 780 A1, for example, it is shown and described that in such hydraulic cylinders the pistons are each equipped with several openings through which the damping medium in the cylinder, for example hydraulic oil, flows when the coil frame vibrates, which leads to a damping of the vibrations of the coil frame.

[0009] The vibration damping device described in DE 100 46 603 A1 also operates with a similar hydraulic cylinder. However, in this known damping device, the damping medium of the hydraulic cylinder is a rheologically variable fluid, i.e., a fluid whose viscosity can be changed by means of a magnetic field generator. In these known damping cylinders, designed as hydraulic cylinders, a sealing ring is arranged between the lower and upper cylinder sections.

[0010] In addition, such damping cylinders feature a piston rod seal designed to prevent damping medium from escaping from the hydraulic cylinder. Although the sealing elements of these well-known damping cylinders have been continuously improved over time, there is always a risk of damping medium escaping with such hydraulically operated damping cylinders. This not only leads to contamination of the surrounding area and often to a not immediately noticeable deterioration in damping performance, but, in conjunction with the fiber dust that is almost unavoidable in textile factories, also poses a significant fire hazard.

[0011] In the past, various attempts have therefore been made to replace such hydraulically operating damping devices with damping devices that do not require a liquid damping medium.

[0012] For example, Swiss patent CH 374 003 describes a damping device comprising an energizable electromagnet that acts on an armature plate, which in turn is connected via a rod to the pivotally mounted coil frame to be damped. This means that in this known damping device, an electromagnet, which is known to contain an energizable coil, generates a force component that presses the ferromagnetic armature plate connected to the coil frame against a stationary abutment. In this known damping device, the damping behavior therefore results from the mechanical friction between the movably mounted armature plate and the stationary abutment.

[0013] A comparable, albeit contactless, electromagnetic damping device is also known from DE 100 12 005 B4. This damping device has a movable, electrically conductive component that is at least indirectly connected to the coil frame and arranged such that the component intersects the magnetic field of a stationary magnet system without contact. In this known damping device, the damping behavior is based on the generation of eddy currents in the electrically conductive component. In practice, however, it has been shown that both the damping devices according to CH-PS 374 003 and the damping devices according to DE 100 12 005 B4 have various disadvantages. In the case of damping devices based on the eddy current principle, for example, the force induced on the conductive component by the magnetic field of the magnet system was insufficient to achieve satisfactory damping.The damping devices described above were never able to prevail in practice.

[0014] Furthermore, winding devices for the workstations of textile machines producing cross-wound bobbins are also known from DE 26 06 859 A1, DE 10 2007 047 554 A1, and DE 199 24 390 A1. In these devices, the bobbin frame, which is pivotably mounted on the machine frame of the textile machine, is equipped with a damping device. These damping devices function as friction dampers, similar to the damping device known from Swiss Patent 374 003.

[0015] In the device according to DE 26 06 859 A1, for example, a movably mounted bobbin frame is equipped with a damped braking element that corresponds to a stationary counter-body. This means that the braking element has brake shoes that rest against a counter-body stationary on the machine frame of the textile machine.

[0016] A device equipped with a friction element for damping the vibrations occurring on the bobbin frame during the winding process of a cross-wound bobbin is also described in DE 10 2007 047 554 A1. In this damping device, a counter-body, also stationary on the machine frame of the textile machine, is subjected to a friction element that can be actuated by a pneumatic cylinder.

[0017] The damping device described in DE 199 24 390 A1 comprises a guide rod movably mounted on the bobbin frame, which corresponds to braking elements of a cylinder device mounted on the machine frame of the textile machine with limited movement. This means that the cylinder device contains, among other things, a movable, pneumatically actuated piston, which applies a braking element to the guide rod and thereby initiates a friction torque that dampens vibrations of the respective bobbin frame during winding.

[0018] Further vibration damping devices with the generic features of claim 1 are known, for example, from the documents DE 38 09 421 A1, DE 195 15 601 A1 and DE 198 53 316 A1.

[0019] As indicated above, the known damping devices have various disadvantages, which means that these damping devices can be improved.

[0020] Based on the aforementioned prior art, the object of the invention is to develop a vibration damper for a pivotably mounted bobbin frame of a winding device of a textile machine producing cross-wound bobbins, which is unproblematic both with regard to its susceptibility to contamination and ensures a relatively stable vibration-related state of the bobbin frame during the winding process.

[0021] This object is achieved according to the invention by a vibration damper having the features of claim 1.

[0022] Advantageous embodiments of the invention are the subject of the subclaims.

[0023] The vibration damper designed according to the invention not only has the advantage that its design as a mechanically operating friction damper eliminates the risk of contamination of the work area due to escaping damping medium, but also that the special, inventive design of the friction damper minimizes the problem of constant vibration-induced lifting of the cross-wound bobbin during the winding process. This means that the friction damper designed according to the invention generates direction-dependent frictional forces, whereby the frictional forces that act when the cross-wound bobbin is lifted in the reverse direction are significantly greater than the frictional forces that act when the cross-wound bobbin is lowered. The compact design of the friction damper also enables retrofitting of the damping device according to the invention at work areas of textile machines whose bobbin frames have previously been equipped with hydraulic damping cylinders.This means that in order to be able to use the friction dampers designed according to the invention advantageously, only a few minor modifications are required in the area of ​​the workstations of textile machines.

[0024] The friction damper has a brake rod which is mounted so that it can move relative to the damper housing of the vibration damper, a stationary first brake element and a movably mounted second brake element which can be adjusted to the brake rod by means of a support lever.

[0025] Such a design results in the friction damper having a locking and an idle direction. For this purpose, the support lever is arranged at an angle to the brake rod so that the second braking element is automatically pressed more strongly against the brake rod when the cheese attempts to lift from its associated bobbin drive drum. This means that if, during the winding process, the cheese resting on the bobbin drive drum and driven by friction begins to vibrate, for example due to a slight out-of-roundness, moments of force are immediately transferred to the bobbin frame. The moment of force attempting to lift the bobbin frame and thus also the housing of the vibration damper immediately causes greater pressure to be applied to the second braking element, resulting in a strong frictional moment.

[0026] At this point, the vibration damper operates in the so-called blocking direction.

[0027] In a further advantageous embodiment, the vibration damper has a spring element that applies a force-locking action to the support lever, which is arranged at an angle with respect to the brake rod. The spring element is preferably designed as a compression spring, and the compressive force of the spring element is adjustable using an adjusting screw. Such a design ensures that the frictional force with which the brake elements rest against the brake rod in the assembled state can be adjusted in a defined manner. This means that the compressive force of the spring element can be used to influence the magnitude of the frictional force acting on the brake rod, thus ensuring that the support lever reliably operates in the locking direction when required.

[0028] According to the invention, the support lever is, on the one hand, connected to the second brake element with limited mobility and, on the other hand, supported in a guide of the damper housing via a guide and locking device. The guide and locking device is displaceably mounted in the preferably partially circular guide of the damper housing and can be positioned there in a defined manner. The advantageously arranged guide and locking device forms a pivot and support point for the support lever during operation. This means that by appropriately positioning the guide and locking device in the partially circular guide of the damper housing, the angle that the support lever assumes with respect to the brake rod can be adjusted and thus the contact pressure of the second brake element, which is largely responsible for the frictional torque, can be influenced.

[0029] In a further advantageous embodiment, the first and second brake elements are designed as identical components. This means that the first and second brake elements each have two through holes for fastening and a recess. A replaceable brake pad can be installed in each recess.

[0030] The use of identically designed brake elements has the advantage that the number of differently designed components is minimized and thus the manufacturing costs of the friction damper designed according to the invention can be kept relatively low. Equipping the brake elements with replaceable brake pads also enables proper, cost-effective operation of the friction damper according to the invention. If, for example, the operating personnel notices that a package is not running completely smoothly during the winding process, this may be due to a somewhat weakened damping behavior of a friction damper according to the invention. In such a case, the optimal friction conditions of the damping cylinder can be easily restored by simply replacing the brake pads.

[0031] The invention is explained in more detail below with reference to an embodiment shown in the drawings.

[0032] They show: Fig. 1 in side view, a work station of a textile machine producing cross-wound bobbins, in the embodiment of a cross-wound automatic bobbin winder, with a winding device whose bobbin frame is equipped with a friction damper designed according to the invention, Fig. 2 schematically on a somewhat larger scale, a winding device of a work station of a textile machine producing cross-wound bobbins, which is equipped with a friction damper designed according to the invention, Fig. 3 a friction damper designed according to the invention, in section, Fig. 4 a braking element of a friction damper designed according to the invention.

[0033] In Fig. 1A schematic side view of a workstation 2 of a textile machine producing cross-wound bobbins, in the exemplary embodiment of a cross-wound winding machine 1, is shown. As is known and therefore not explained in detail, at the workstations 2 of such textile machines 1, spinning bobbins 3, which were produced on ring spinning machines upstream in the production process and which contain only relatively little yarn material, are rewound into large-volume cross-wound bobbins 5.

[0034] Such cross-winding machines 1 often have a bobbin and tube transport system 6, in which transport plates 11 rotate, on which spinning bobbins 3 or empty tubes are arranged in a vertical orientation. This bobbin and tube transport system 6 is shown in the Fig. 1 only the cop feed section 24, the reversibly driven storage section 25, one of the cross transport sections 26 leading to the winding units 2 and the tube return section 27 are shown.

[0035] Finished cross-wound bobbins 5 are usually transferred to a machine-length cross-wound bobbin transport device 7 by means of an automatically operating service unit (not shown), preferably a cross-wound bobbin changer, and are transported from there to a bobbin loading station or the like arranged at the end of the machine.

[0036] The numerous, identical workstations 2 of such textile machines 1 each have various devices necessary for the proper operation of such a textile machine. For example, the workstations 2 each have a winding device 4, which has a bobbin frame 8, a bobbin drive roller 9, and a thread traversing device 10 for traversing the thread 16 running onto the winding bobbin. The bobbin frame 8 is mounted for limited movement about a pivot axis 12, which runs parallel to the rotation axis of a cheese 5. This means that the cheese 5, which is rotatably mounted in the bobbin frame 8, rests with its surface on the bobbin drive roller 9 during winding operation and is frictionally driven by the latter.In order to reduce the vibrations occurring during the winding process when the cheese 5 is unwound, a damping device 18 is also connected to the bobbin frame 8. This damping device has a friction damper 20 designed according to the invention, which, as will be explained below with reference to the . Fig. 3 explained in more detail, different friction forces are generated depending on the direction.

[0037] As in Fig. 1 As indicated, the bobbin drive roller 9 is driven individually by an electric motor 15, which is connected to a workstation computer 28 via a control line. The drive 14 of the thread traversing device 10, which preferably has a finger thread guide 13 that traverses the thread 16 running onto the winding bobbin during winding operation, is also connected via a control line to the workstation computer 28, which in turn is connected to the central control unit 30 of the package winder 1 via a bus system 29.

[0038] The workstations 2 of such cross-winding machines 1 generally also each have a thread connecting device 21, for example a pneumatic splicer, a gripper tube 22 for handling the bobbin thread and a suction nozzle 17 with which the upper thread which has run onto the cross-wound bobbin 5 after a winding interruption can be picked up and inserted into the thread connecting device 21.

[0039] The Fig. 2 shows schematically and on a somewhat larger scale a winding device 4 of a work station 2 of a textile machine 1 producing cross-wound bobbins with a vibration damping device 18 designed according to the invention. As indicated, the vibration damping device 18 has a friction damper 20, the damper housing 31 of which is connected to the bobbin frame 8 via a first bearing rod 19 and is thus movable therewith.

[0040] As can be seen, the brake rod 32 of the friction damper 18 is also connected to a stationary bearing point 33 of the work station 2 via a second bearing rod 23.

[0041] The Fig. 3 The friction damper 20 of the vibration damping device 18, shown in section and in detail, designed according to the invention, has a damper housing 31 provided with a connecting thread 34 at the top. A first bearing rod 19 can be secured in this connecting thread 34, with which the damper housing 31 is connected to the coil frame 8 in the assembled state. Arranged within the damping housing 31 is a brake rod 32, which is connected to a stationary bearing point 33 via a second bearing rod 23. The damper housing 31 is mounted so as to be displaceable relative to the brake rod 32.

[0042] As can also be seen, two identically designed brake elements 39, 41 are non-positively connected to the brake rod 32. The first brake element 39 is fixed in the damping housing 31, for example via screw bolts 40, while the second brake element 41 is movably mounted in the damper housing 31. This means that the damping housing 31 has a partially circular guide 35 in which a guide and locking device 36 is arranged so that it can be moved and, if necessary, positioned as required. The guide and locking device 36 forms a pivot and support point 37 for a support lever 38. The support lever 38 is in turn arranged at an angle with respect to the brake rod 32 and is also connected to the second brake element 41 with limited movement.As shown, the support lever 38 is further acted upon by a spring element, preferably a compression spring 42, the effective compressive force of which can be predetermined by means of an adjusting screw 43.

[0043] The Fig. 4 shows one of the identically designed brake elements 39, 41.

[0044] The brake elements 39, 41 each have two through-holes 44 for securing the brake elements as needed, as well as a recess 45 for securely receiving a replaceable brake pad 46. This means that the first brake element 39 can be fixed in place in the damper housing 31 by means of screw bolts 40 that pass through the through-holes 44. A replaceable brake pad 46 can be installed in each of the recesses 45, i.e., a brake pad 46 that can be easily replaced as needed. Function of a friction damper designed according to the invention:

[0045] During the winding operation, the winding frame 8 is constantly set into vibration by the cross-wound bobbin 5 resting on the bobbin drive drum 9 and driven by friction, i.e. the slightly unevenly running cross-wound bobbin 5 repeatedly lifts slightly off the bobbin drive drum 9.

[0046] These vibrations are transmitted via the first bearing rod 19 to the damper housing 31 of the friction damper 20, whose brake rod 32 is stationary connected to a bearing point 33 via the second bearing rod 23. This means that each time the cheese 5 is lifted from its associated bobbin drive drum 9, the damper housing 31 is also subjected to a lifting torque, which is counteracted by the brake elements 39, 41, which are frictionally connected to the brake rod 32.

[0047] In the friction damper 20 designed according to the invention, when the cheese 5 is lifted off, the damper housing 31 of the friction damper 20 designed according to the invention is acted upon in such a way that the angularly arranged support lever 38, as indicated by the arrow 48, is subjected to a torque which exerts an additional moment on the braking element 41, with the result that the braking force of the braking elements 39, 41 predetermined by the compression spring 42 is significantly increased and thus the upward oscillation of the bobbin frame 8 is greatly reduced or almost prevented.

[0048] During the subsequent downward oscillation of the creel 8, which is opposite to the so-called locking direction of the friction damper 20, the damper housing 31 is also acted upon in the direction of the spool drive drum 9, with the result that the angularly arranged support lever 38, as indicated by arrow 47, is acted upon in such a way that no additional torque is exerted on the second brake element 41. The braking force exerted by the brake elements 39, 41 on the brake rod 32 is thereby significantly reduced, and the creel 8 can swing back into a position in which the cheese 5 rolls properly again on the spool drive drum 9.

[0049] As can be seen and already indicated above, the vibration damper device 18 with the friction damper 20 designed according to the invention is very compact and can therefore also be retrofitted to textile machines that have already been delivered, i.e., to textile machines that have previously been equipped with damping cylinders, which are often somewhat problematic due to their hydraulic damping medium. Due to their compact design, the use of the friction damper 20 according to the invention does not cause any obstructions to possible service units. List of reference symbols 1 Cross-winding machine 25 Storage section 2 workplace 26 Cross transport route 3 Spinheads 27 Sleeve return line 4 winding device 28 Workplace calculator 5 cross-wound bobbin 29 bus system 6 Cop and tube transport device 30 Central control unit 31 Damper housing 7 Cross-wound bobbin transport device 32 brake rod 8 spool frame 33 stationary storage location 9 Coil drive drum 34 Connection thread 10 Thread traversing device 35 part-circular guide 11 Transport plate 36 Guide and locking device 12 Swivel axis 13 Finger thread guide 37 Pivot and support point 14 drive 38 Support lever 15 electric motor 39 first brake element 16 thread 40 screw bolts 17 suction nozzle 41 second brake element 18 Damping device 42 compression spring 19 first bearing rod7 43 Adjusting screw 20 Friction damper 44 Through hole 21 Thread connecting device 45 recess 22 gripper tube 46 brake pad 23 second bearing rod 47 Arrow 24 Cops feed line 48 Arrow

Claims

1. Vibration damping device (18) for a winding device (4) of a textile machine (1) that produces cross-wound packages (5), the vibration damping device (18) being provided for reducing the vibrations that occur at the pivotably mounted package cradle (8) during the winding operation of the textile machine (1), wherein the vibration damper is in the form of a friction damper (20) which has friction forces of different intensity depending on the working direction, the friction forces effective as the cross-wound package (5) lifts off during the winding operation being greater than the friction forces effective during the return movement of the cross-wound package (5), wherein the friction damper (20) has a braking rod (32), which is mounted for sliding relative to the damper housing (31) of the friction damper (20), a stationary first braking element (39), and a movably mounted second braking element (41), which can be placed against the braking rod (31) by means of a movable support lever (38), characterized in that one end of the support lever (38) is connected to the second braking element (41) such that limited movement is allowed, while the other end is supported in a guide (35) of the damper housing (31) by means of a guiding and arresting device (36).

2. Vibration damping device (18) according to claim 1, characterized in that a spring element (42) is provided, which acts, in frictional contact, on the support lever (38), the support lever (38) being arranged at angle to the braking rod (31).

3. Vibration damping device (18) according to claim 2, characterized in that the spring element is in the form of a compression spring (42), the effective compressive force of which can be set in a defined manner by means of an adjustment screw (43).

4. Vibration damping device (18) according to one of the preceding claims, characterized in that the guiding and arresting device (36) forms a pivoting and support point (37) for the support lever (38) and is mounted in the guide (35) of the damper housing (31) such that the guiding and arresting device (36) can be slid therein and can be positioned therein in a defined manner.

5. Vibration damping device (18) according to one of the claims 1 to 4, characterized in that the guide (35) is part-circular-shaped.

6. Vibration damping device (18) according to one of the preceding claims, characterized in that the first braking element (39) and the second braking element (41) are identical.

7. Vibration damping device (18) according to claim 6, characterized in that the braking elements (39, 41) are each equipped with through-bores (40) for fastening and with a recess (45) for an exchangeable brake lining (46).