EP0847457A1

EP0847457A1 - Textile machine with driven thread guiding member

Info

Publication number: EP0847457A1
Application number: EP96926307A
Authority: EP
Inventors: Francisco Speich
Original assignee: Textilma AG
Current assignee: Textilma AG
Priority date: 1995-08-29
Filing date: 1996-08-19
Publication date: 1998-06-17
Anticipated expiration: 2016-08-19
Also published as: KR100415891B1; AU6694896A; RU2143019C1; EP0847457B1; ES2173304T3; US5947165A; KR19990022958A; WO1997008373A1; DE59609161D1; JP2007092272A; JP4199798B2; JPH11511211A; DE29513815U1; TR199800337T1

Abstract

The thread processing device (8) of a textile machine has at least one thread guiding device that moves a thread (4) back and forth between at least two positions (12, 14) by means of a thread guiding member (30, 32, 34). The thread guiding member may be moved in one direction by means of an interlocking drive (28) and in the opposite direction by a frictional engagement drive (36) that acts against the interlocking drive (28). The textile machine is substantially improved by designing the frictional engagement drive (36) as a pneumatic drive with an individual gas chamber (64) that contains a gas volume that may be compressed by the interlocking drive at the working frequency. The gas chamber communicates with a compressed gas source through a non-return valve.

Description

Textile fabrics for the manufacture of textile textile threads

Technical field

The invention relates to a textile machine for producing textile products from threads according to the preamble of claim 1.

State of the art

Textile machines are in large numbers, for example, as weaving machines (US Pat. No. 3,603,351, US Pat. No. 3,695,304, CH Pat. No. 531,588, EP Pat. No. 0,107,099, EP Pat. No. 0 325,547, EP-OS 0 363 311, DE-OS 31 20 097) or knitting machines (DE-A-27 58 421) are known.

For weaving, weaving machines contain thread processing devices which move the warp threads from a central shed position to a high or low position in order to open a shed into which a weft thread is inserted, which is then attached to a fabric edge by means of a reed. A wide variety of devices, such as shaft frames and individual strand controls, are used for the formation of shafts, and crank gear, cam disks, cam gear, dobby machines, jacquard machines or the like are used to drive them. A basic distinction is made between two types of drive, a positive drive, such as a crank mechanism, in which the drive is positive, that is to say positive, in both directions of movement. In the case of a negative drive, for example cam disks, cam gears, dobby machines, jacquard machines and the like, the drive is positive in one direction of movement, that is to say positive, and non-positive in the other direction of movement, that is to say negative, for example via tensile, pressure, or sheet - or torsion springs.

The disadvantage of a positive drive is that the bearing points are knocked out and play, particularly at high speeds. This leads on the one hand to a large noise development and on the other hand to inaccuracies and ultimately to the failure of the drive. Such a drive is not suitable for speeds above 2 * 000 revolutions / minute, for example.

In the case of a negative drive, of which the present invention belongs, the force-locking drive is carried out by means of tension, compression, leaf or torsion springs made of spring steel, rubber and synthetic elastomers. Since the positive drive always acts against the positive drive, problems arise at higher speeds. For example, resonance vibrations occur in many systems, which bring the drive parts out of control, ie the drive parts are no longer always in a preloaded state with respect to one another. This leads to greater noise, failure of the bearings, breakage of the springs and ultimately to a complete failure of the thread control. Steel springs are relatively long and heavy, which results in a low resonance speed. With rubber and elastane springs, the problems lie in the molecular friction of the material, which leads to high heating of the springs. Such high heating leads to premature aging and loss of spring properties, which in turn leads to a low resonance speed, inadequate spring properties and ultimately to their failure. It finally follows a drastic reduction in the degree of utilization, the utilization effect and the production output of such textile machines. It has been found that thread processing devices for forming a weaving machine using the following materials have clear limits, namely in the case of non-positive drives with:

Steel tension springs max. 1,500 revolutions / min.

Steel compression springs max. 2,000 revolutions / min.

Elastic extension springs max. 3,000 revolutions / min.

Elastane springs max. 2,500 revolutions / min.

In addition, such thread processing devices generally have a relatively large construction volume and cannot be adjusted to the operating conditions of the textile machines during operation.

From DE-AS 26 31 175 a loom of the type mentioned is known, in which the retraction for the healds of a jacquard machine is generated pneumatically. The healds are each connected to a piston / cylinder unit, the cylinders being connected to a common, large-volume gas chamber, so that a common retraction force is available for all healds and is constant over the entire retraction path of the heald. An individual pneumatic control of each heald is excluded.

Presentation of the invention

The object of the invention is to provide a textile machine of the type mentioned at the outset which has improved properties.

According to the invention, the object is achieved by the characterizing features of claim 1. The fact that the thread guide member is assigned an individual gas volume results in significant improvements to the textile machine, which consist in particular in the individual control of each thread guide member. The retraction force can thus be individually adjusted to the needs of the respective thread guide member. This is particularly important since the thread guide members have different control paths and / or thread qualities to be controlled, to which the retraction force has to be adjusted in order to achieve optimal results. The novel design of the thread processing device means that textile machines such as weaving and knitting machines can achieve significantly higher speeds, for example up to 6 * 000 revolutions / min. possible, this at a greatly reduced noise level, that is to say reduced noise development. The high speeds are possible because the critical resonance vibrations are much higher due to the pneumatic design of the non-positive drive, namely in the range above 6,000 revolutions / min. Because the critical resonance vibrations are very high and higher than the desired speed range the maximum required retraction force can be reduced, which makes a lighter design possible. Furthermore, the number of moving parts and their size can be significantly reduced, which not only leads to a simpler, more compact design, but also lowers the production costs of such a textile machine and yet the service life of the textile machine is greater until the occurrence of intolerable wear. The pneumatic design of the non-positive drive also makes it possible in particular to adjust the force of the non-positive drive to the individual operating conditions, particularly during operation.

Advantageous embodiments of the textile machine are described in claims 2 to 13. In principle, it is possible to use any gas chamber whose gas volume can be compressed in the working frequency of the textile machine by means of the positive drive. For example, it is possible to connect the positive drive to a membrane of a gas chamber by means of a tappet, in order to compress the gas volume by pressing the membrane against the gas chamber and pulling it out. However, an embodiment according to claim 2 is more advantageous. The gas chamber can be on the side of the piston rod, but it is more advantageous if the gas chamber is arranged on the side of the cylinder facing away from the piston rod.

An embodiment of the textile machine according to claim 3 is advantageous. By venting the gas chamber when the textile machine is at a standstill, the thread control device or the thread can be brought into a starting position independently of the position of the positive-locking gear, for example a cam gear. This allows the threads to be drawn in more easily into the thread control device, which is particularly advantageous when the thread processing device is designed as a shedding device. The thread repair times and the changeover times of such a textile machine are thus greatly reduced.

An embodiment of the textile machine according to claim 4 is also advantageous, wherein the maximum pressure, for example in the event of excessive heating or the like, cannot be exceeded by an overpressure valve on the gas chamber.

An embodiment of the textile machine according to claim 5 and in particular in the development according to claim 6 is particularly advantageous, as a result of which the gas pressure in the gas chamber can be set as a function of the operating state of the textile machine. This enables a completely new operating mode for the Textile machine, the operating state of the textile machine being understood not only to mean the individual running phases such as standstill, start-up, fast running, creeper and manual operation, but in particular also the type of textile product to be produced, such as light or heavy goods, heavily patterned or little patterned Goods, and the type of threads used, such as fine, coarse threads, rubber threads, wrapped threads and threads made of various materials. It also follows from this that the individual components of the textile machine are only loaded to the extent that is directly necessary and that the energy requirement of the textile machine can always be adjusted to the minimum load requirement, as a result of which the production costs can be greatly reduced. This operating mode also enables manual operation for adjustment and repair work to be made easier due to the need to reduce the force of the non-positive drive. This leads to simplified handling, which greatly reduces changeover times and repair times. Advantageous operating conditions of the textile machine describe claims 7 to 10.

In certain cases, an embodiment of the textile machine according to claim 11 can also be advantageous, it being possible for the second gas chamber, which can support and / or counteract the function of the first gas chamber, not only to improve its function, but also if need be the resonance behavior of the pneumatic drive can be influenced positively. By means of the second gas chamber and the control device, a positive control of the thread processing device can at best be achieved if, for example, by applying a controllable positive pressure in the second gas chamber, a thread guiding element no longer follows the force-locking drive, for example a warp thread remains in the down position and thus has to be pressed ¬ tion of the textile product to be contributed. Claim 12 describes the configuration of the textile machine as a weaving machine, the shedding device being provided with a non-positive pneumatic drive. In the case of ribbon looms in particular, however, it is also conceivable for the drive of a weft insertion needle to be equipped with such a non-positive pneumatic drive.

Claim 13 describes the configuration of the textile machine as a knitting machine, the non-positive pneumatic drive being assigned to a thread laying rod, in particular a weft thread laying rod. If a knitting machine contains several thread-laying rods, then such a force-locking pneumatic drive can be assigned to each thread-laying rod.

Air will generally be used as the gas. However, it is also conceivable that a particularly coordinated operating behavior can be achieved by using other gases.

Brief description of the drawings

Exemplary embodiments of the invention are described in more detail below with reference to the drawings, in which:

1 shows a weaving machine with a thread processing device for shed formation, with a warp thread in the raised position;

Figure 2 shows the loom of Figure 1 in

Lowering of a warp thread;

Figure 3 is a diagram of the dependence of

Gas pressure from the gas volume; Figure 4 shows the frictional pneumatic

Drive the shedding device of the weaving machine of Figures 1 and 2 with a pressurized gas source;

Figure 5 shows the diagram of the dependence of

Gas pressure from the operating state of the weaving machine;

Figure 6 shows the thread processing device of a knitting machine with a thread laying bar.

Ways of Carrying Out the Invention

FIGS. 1 and 2 describe a textile machine designed as a weaving machine, the basic structure of which corresponds, for example, to that of the weaving machine of US Pat. No. 3,603,351 or CH-PS 531,588 or EP-PS 0 107 099. The weaving machine contains a warp beam 2, from which warp threads 4 pass via a match beam 6 into the area of a thread processing device 8, which is designed as a shedding device to move the warp threads 4 from the high shed position 12 to the deep shed position 14 or from the deep shed position 14 to Deflect high position 12. As a result, a shed 16 is opened, into which a weft thread 18 is inserted and attached to a fabric edge 22 by means of a reed 20. The textile product 24 produced in this way, that is to say the fabric is drawn off via a goods take-off device 26.

The thread processing device 8 for producing the shed contains a thread control device 27 with a form-fitting drive 28 which, as the thread guide member, has a shaft frame 30 with a strand 32 and a strand eye 34 in Lower position moves, while a non-positive pneumatic drive 36 counteracts this and moves the shaft edge 30 into the high position.

The positive drive 28 contains a driven cam 38, with which an arm 40 of a two-armed lever 42 cooperates via a roller 44. The two-armed lever 42 is pivotally mounted on the machine frame 48 via a pivot point 46. The second arm 50 of the two-armed lever 42 interacts via a fork 52 with a cam 54 which is fastened to the shaft frame 30. A piston rod 56 of a piston-cylinder unit 58 of the non-positive pneumatic drive 36 also acts on this cam 54. The piston rod 56 is connected to a piston 60 which is guided up and down in a cylinder 62. On the side of the piston 60 facing away from the piston rod 56, the piston / cylinder unit forms a gas chamber 64, to which a pressure relief valve 66 for limiting the maximum pressure and a pressure gas source 70 are connected via a check valve 68. As can be seen in particular from FIG. 4, the gas chamber 64 can also be provided with a manually operated pressure relief valve 72. FIG. 1 shows the force-fitting pneumatic drive 36 with an expanded gas volume V _E at a pressure P _E in the gas chamber 64 when the shaft frame is in the high position. FIG. 2 shows the non-positive pneumatic drive 36 with compressed gas volume V _j ^ and the pressure P _j ^ when the shaft frame 30 is in the low position.

The diagram in FIG. 3 shows the dependency of the gas pressure P on the gas volume V and the corresponding position L of the piston 60 in the cylinder 62. If the piston is moved from the expanded position Lg to the compression position L _j r, this changes Gas volume V from the expanded state V _E to the compressed volume V _R , the gas pressure P _E from expanded state to the gas pressure P _{κ increases} in the compressed state. The diagram of FIG. 3 also shows the maximum pressure P _max indicated by the pressure relief valve 66, at which the pressure relief valve 66 opens. The force-fitting pneumatic drive 36 is expediently det ausgebil¬ so that the gas pressure P in the compressed state of the _κ Gas¬ chamber is: ^p κ -

'K

The gas pressure P _R is preferably:

P _κ ≤ 100 ^* P _E

4 shows the non-positive pneumatic drive 36 of FIGS. 1 and 2 in detail, wherein in particular the compressed gas source 70 also contains a control device 74 which is connected to a control device 76 of the weaving machine. The compressed gas source 70 contains a compressor 78 which supplies compressed gas, preferably air, to the control device 74. This contains various pressure reducing valves 80a-e, which correspond to the various operating states I-V of the weaving machine. The control unit 76 controls the opening valves 82 connected downstream of the pressure reducing valves 80a-e in order to connect the compressor 78 to the piston / cylinder unit 58 via the selected pressure reducing valve 80a-e.

FIG. 5 now shows the pressure curve which the compressed gas source 70 feeds into the gas chamber 64 as a function of various operating phases of the weaving machine. In the article change phase I, the gas pressure P _j corresponds to the ambient pressure of the atmosphere, so it is practically zero. The gas pressure P- _j - _{j is} greatest in the start-up phase II and then drops to the gas pressure Pm in the high-speed phase III. from. If the webma Operated in the crawl gear phase IV, the gas pressure P _IV drops further. In the manual operating phase V, the gas pressure P _{v can be} equal to or less than the gas pressure P _{IV of} the creeper phase IV.

Normally, the non-positive pneumatic drive 36 only works against the positive drive 28, ie the cylinder 62 is open on the side facing the piston rod 56 and is under ambient pressure P _Q. A further embodiment is indicated by dash-dotted lines in FIG. 4, the side of the piston 60 opposite the gas chamber 64 also being provided with a gas chamber 84, ie being closed, and being connected to a pressure control device 86 which has a compressor 88. The pressure control device 86 can be designed such that this second gas chamber 84 supports and / or counteracts the function of the first gas chamber 64. This enables a more subtle adjustment and control of the non-positive pneumatic drive 36. The pressure control device can at most also be connected to the control device 76 of the weaving machine and configured so that the pressure in the second gas chamber 64 is periodically greater than the gas pressure in the first gas chamber 64, as a result of which the shaft frame 30 is held in the down position can and therefore no longer follows the positive drive 28. This enables a pattern-based control of the shaft frame.

FIG. 6 shows a thread processing device 90 of a knitting machine, for example a warp knitting machine, in particular a crochet galloon machine, the basic structure of which is evident, for example, from DE-OS 27 58 421. FIG. 6 shows a laying bar 92, for example for a weft thread, not shown in detail. The laying bar 92 is guided up and down in supports 94 and can be moved longitudinally and acts on one side with a form-fitting sigen drive 96 together, which has a driven rotating cam 98, which acts on a roller 100 which is fixed to a rocker arm 102. The rocker arm 102 is pivotally mounted on the machine frame 104 and, at its end facing away from the machine frame 104, interacts with the laying bar 92 via a coupling member 106. The coupling member 106 is connected on the one hand via a joint 110 to the rocker arm 102 and on the other hand via a second joint 108 to the laying bar 92, so that the latter can perform an up and down movement. The other end of the laying rod 92 is connected to a non-positive pneumatic drive 112, the laying rod 92 being designed as a piston 114 which is immersed in a cylinder 116 of a piston / cylinder unit 118. A gas chamber 120 is thus formed in the interior of the cylinder 116, to which, on the one hand, a pressure relief valve 122 and, on the other hand, a pressure gas source 126 are connected via a check valve 124. In the area of the gas chamber 120, the cylinder 116 can also be provided with a manually operable pressure relief valve analogous to the pressure relief valve 72 in FIG 130 cooperate to insert a weft thread, not shown, between at least two knitting needles 130. The displacement path can also run over two or more knitting needles.

The knitting machine according to FIG. 6 can be controlled according to analogous principles, such as the control of the weaving machine according to FIGS. 1 to 5. LIST OF REFERENCE NUMBERS

P _Q ambient pressure

P _Q gas pressure of the compressed gas source

P _E gas pressure in the expanded state

P _κ gas pressure in the compressed state

P _j Gas pressure in the article change phase

PJJ gas pressure in the start-up phase

PJJJ gas pressure in the high-speed phase

P _jV gas pressure in the creeper _phase

P _v Gas pressure in the manual operating phase ^p max roaximal gas pressure

V _E gas volume in the expanded state

V _R gas volume in the compressed state

2 warp beam

4 warp threads

6 match tree

8 thread processing device

12 superscript

14 subscript

16 shed

18 weft

20 reed

22 goods edge

24 textile product

26 Goods take-off device

27 Thread control device

28 positive drive 30 shaft frame

32 strands

34 stranded eye

36 non-positive pneumatic drive

38 cam Arm two-armed lever

role

pivot point

Machine frame

poor

fork

cam

Piston rod

Piston / cylinder unit

piston

cylinder

Gas chamber

Pressure relief valve

check valve

Pressurized gas source

Pressure relief valve

control device

control unit

Compressor a-e pressure reducing valve

Opening valve

Gas chamber

Pressure control device

compressor

Thread processing device

Laying bar

Carrier positive drive

Cam 0 roller 2 rocker arm 4 machine frame 6 coupling link 8 joint 110 joint

112 non-positive pneumatic drive

114 pistons

116 cylinders

118 piston / cylinder unit

120 gas chamber

122 pressure relief valve

124 check valve

126 compressed gas source

128 thread guides

130 knitting needle

Claims

PATENT CLAIMS

1. Textile machine for producing textile products from threads, with a thread processing device (8, 90) which has at least one thread control device (27) which moves at least one thread back and forth over at least two positions by means of a thread guide member (34, 128), wherein the thread guide member can be moved in one direction of movement by means of a positive drive (28, 96) and in the opposite direction of movement by means of a force-fitting pneumatic drive (36, 112) acting against the positive drive, characterized in that the pneumatic drive for the thread guide by the has positive drive (28,96) in the working frequency compressible gas volume in an individual gas chamber (64,120).

2. Textile machine according to claim 1, characterized in that the pneumatic drive (36, 112) has a piston / cylin der unit (58, 118) which contains a piston (60, 114) which on the one hand delimits a cylinder chamber forming the gas chamber (64, 120) and which on the other hand, it is coupled to the positive drive (28, 96) via a piston rod (56, 92).

3. Textile machine according to claim 1 or 2, characterized in that an actuatable pressure relief valve (72) is connected to the gas chamber (64, 120).

4. Textile machine according to one of claims 1 to 3, characterized in that a pressure relief valve is connected to the gas chamber (64, 120).

5. Textile machine according to one of claims 1 to 4, characterized in that the gas chamber (64, 120), preferably via a check valve (68, 124), is connected to a compressed gas source (70, 126).

Textile machine according to claim 5, characterized in that the compressed gas source (70, 126) has a control device (74), which is preferably connected to a control unit (76) of the textile machine, with which the gas pressure (P) in the gas chamber (64, 120) is dependent is adjustable from the operating state of the textile machine.

7. Textile machine according to claim 6, characterized in that the control device (74) is designed such that the gas pressure (P) in the gas chamber (64) is adjustable as follows:

Gas pressure P _j in an article change phase I of the textile machine, which corresponds to the ambient pressure P _Q ;

Gas pressure P-J-J in a start-up phase II, which is at least as high as the gas pressure PJJJ in the high-speed phase;

- Gas pressure PJU in a high-speed phase III, which is less than or equal to the gas pressure PJJ of the start-up phase II; Gas pressure P _IV in a crawl gear phase IV, which is lower than the gas pressure PJJJ of the high-speed phase III; and

Gas pressure P _v in a manual operating phase V, which is equal to or less than the gas pressure P _{IV of} the creeper phase.

8. Textile machine according to one of claims 5 to 7, characterized in that it is designed such that the gas pressure (P _E ) with expanded gas in the gas chamber (64) corresponds to the gas pressure (PQ) of the compressed gas source (70).

9. Textile machine according to claim 8, characterized in that it is designed such that the gas pressure (P _jζ ) in the gas chamber (64) in the compressed final state corresponds to the following formula:

^• EV _τ

^P K -

'K

in which:

P _E = gas pressure of the expanded gas volume of the gas chamber

V _E = volume of gas in the gas chamber in the expanded state

^V K ⁼ volume of gas in the gas chamber in the compressed final state

10. Textile machine according to claim 9, characterized in that it is designed such that the gas pressure (PR) in the compressed final state:

^p κ ^ 100 E

11. Textile machine according to one of claims 2 to 10, characterized in that the cylinder part (62) located on the second side of the piston (60) is designed as a gas chamber (84) and is connected to a pressure control device (86) such that the gas pressure (P) in the second gas chamber (84) supports and / or counteracts the function of the first gas chamber (64).

12. Textile machine according to one of claims 1 to 11, characterized in that it is designed as a weaving machine, at least the shedding device being provided with a non-positive pneumatic drive (36).

13. Textile machine according to one of claims 1 to 11, characterized in that it is designed as a knitting machine, preferably as a warp knitting machine, at least one thread laying rod (92), preferably a weft thread laying rod, being provided with a non-positive pneumatic drive (112).