KR100754106B1 - Thread control device for a textile machine in particular for a shedding device - Google Patents

Abstract

The invention relates to a thread control device for a textile machine, in particular, for a shedding device, with at least one thread guide body ( 31 ) which may be displaced in one displacement direction by means of a positive drive ( 35 ) and in the opposite direction by means of a non-positive, pneumnatic return device ( 36 ). Me return device ( 36 ) thus comprises a cylinder/piston unit ( 64,54 ), the cylinder chamber of which ( 52 ) is connected to a compressed gas source ( 60 ) by means of a valve ( 56 ). An improvement in control is achieved when the valve ( 56 ) comprises a first valve seat ( 72 ) connected to the cylinder chamber ( 52 ) and a second valve seat ( 76 ), between which a valve body ( 82 ), provided with at least one throttle point ( 80 ), may be displaced, pre-tensioned in the rest position by means of a spring ( 84 ) against the first valve seat ( 72 ), in which the throttle point ( 80 ) is ineffective and the valve body ( 82 ) blocks the communication with the compressed gas source ( 60 ) when the valve body ( 82 ) is in contact with the second valve seat ( 76 ).

Description

THREAD CONTROL DEVICE FOR A TEXTILE MACHINE IN PARTICULAR FOR A SHEDDING DEVICE

The present invention relates to a thread control device for a textile machine, in particular a shedding device, according to the preamble of claim 1.

Many thread control devices for textile machines are known. The most recent prior art according to WO 97/08373 discloses a thread control device designed as a drive and return device for a thread guide member. It is possible to move in one direction of movement by means of the drive device designed in the positive direction, and in the opposite direction of movement by means of the return device designed in the negative direction and air pressure, which operates in reverse with respect to the positive direction drive device. Do.

The pneumatic return device has a cylinder / piston assembly, the cylinder chamber of which is designed with a non-return valve connected to an excess pressure valve and a source of compressed gas. The gas pressure in the cylinder chamber is set in this case as a function of the textile machine operating state. For example, in the slow speed stage, the gas pressure is kept lower than in the high speed stage so that the electric motor can supply the necessary power to overcome the load resulting from the compression of the cylinder chamber. In the high speed stage, the electric motor delivers sufficient power so that the gas pressure can be further increased to prevent the roller on the cam disk of the positive direction drive device from being lifted off. The cylinder chamber can also be designed to have a manually actuated pressure relief valve to minimize the resistance that occurs as a result of compression in the cylinder chamber when the textile machine is installed.

The above solution has the disadvantage that the gas pressure in the cylinder chamber has to be adapted to the respective operating state. This requires a complex pressure control device that requires pressure reducing valves and opening valves to activate each cylinder chamber to set the gas pressure of the cylinder chamber. In addition, the complicated electronic control of the valves allows the cylinder chambers to be in each operating state. It is necessary to adjust the pressure inside.

In order to lubricate the cylinder / piston parts, for example, the oil drops onto the piston and enters the cylinder chamber due to hydrodynamic effects despite the permanent overpressure in the latter. Oil accumulated in the cylinder chamber can reduce the volume of air in the cylinder chamber to an indeterminate level, resulting in a higher uncomputable compression pressure in the chamber during operation, thereby continually stopping the operation of the seal control device. In extreme cases where a large portion of the cylinder chamber is filled with oil, the cylinder's movement is no longer possible, and further operation of the weaving machine will cause considerable damage.

Therefore, in an improved embodiment of the air pressure return device described in WO 97/08373, the valve is designed in such a way that oil separation is also possible in addition to the requirements of a stationary operation. In this case, the valve is operated at regular time intervals of a few seconds to drain the oil accumulated in the compression space. In order to avoid the roller being lifted off from the eccentric of the positive direction drive device, the rotational speed of the textile machine should be reduced during this operation (known as the attention cycle). At slow speeds, the valve is also opened so that the pressure in the cylinder chamber does not rise significantly above the supply pressure. The main motor can rotate at a low rotational speed, so that the required power of the motor, which is required for manual rotation on the hand wheel to be possible without extra effort, is therefore reduced.

A disadvantage of this solution is the high cost of the electrical / air pressure activity of the valve. Therefore, the overall control of the pneumatic actuation of the seal control device is characterized by the use of non-return valves, overpressure valves, pressure reducing valves, And a large number of parts, such as an electronic control unit, which makes the system more susceptible to defects. Moreover, the efficiency of the textile machine is reduced as a result of repeated deceleration of the motor rotational speed to discharge the lubricating oil, which deceleration occurs every 15 minutes. In addition, this reduction in motor rotational speed can adversely affect the quality of the weave. For example, this may cause some variation in the width of the fabric fabric produced.

It is an object of the present invention to improve the yarn control device of the type mentioned earlier.

The set object is achieved by means of the features characterized in claim 1. The valve has a first valve seat and a second valve seat connected to the cylinder chamber, with at least one throttle point between them and provided by means of a spring. The valve is subject to external interference because the valve member, which is initially stressed against the one valve seat, is movable and the throttle point is deactivated and the valve member disconnects from the compressed gas source when the valve member faces the second valve seat. Can operate in various operating states without In addition, reliable oil separation is assured without further measurement by a valve operating independently, without reducing the rotational speed, decreasing the maximum compression pressure in the cylinder chamber under load and reducing the compression pressure from the slow speed to the supply pressure.

Useful matters of the invention are described in claims 2 to 19.

In principle, the most various embodiments of a valve designed with two valve seats can be devised. The requirement as claimed in claims 2 and 3, according to the housing having two parts of one part with the housing at the end of the first valve seat and the other part designed as the finish of the housing with the second valve seat and the passage duct is useful. . Therefore, the valve is as simple as possible, the production cost is low, and is a simple part.

In principle, there can be various forms of the valve housing, and the cylindrical design of the housing is useful according to claim 4, which improves the guide of the piston-type valve member in the housing. Moreover, the piston-type valve member may be provided with a sealing ring to seal the cylinder chamber to the outside. In a variant according to claim 4, it is useful to design the throttle points with throttle openings formed on the valve member. According to claim 5, it is also conceivable to design the valve member without a sealing ring, in which case the gap between the valve member and the housing wall can serve as a throttle point.

The valve may be arranged in line connecting the cylinder chamber and the supply pressure chamber. However, direct placement in the cylinder of the cylinder / piston part according to claim 6 is useful. In addition, according to claim 7, it is useful for the valve to be placed at the lowest point of the cylinder. Thus, the valve can be connected directly to the cylinder chamber, and lubricating oil accumulated in the cylinder chamber can flow along the short passage through the valve to the supply input chamber. Alternatively, the end of the valve also has a fluid resistance and It is preferred to connect directly to the supply pressure chamber according to claim 8 in order to minimize the fluid path.

In principle, the supply pressure chamber can be one of the desired designs. The supply pressure chamber can be designed as an oil separation outlet arranged at the bottom of the supply pressure chamber, and as a connection to the compressed air can be placed on the sidewall, away from the supply pressure chamber bottom, claim 9 The design as required in paragraphs 12 to 12 is useful. This arrangement of the compressed air connection and the oil separation outlet prevents the accumulated oil in the supply pressure chamber from blocking the compressed air connection or from flowing into the connection line of the compressed air connection. In principle, several return devices may have a separate supply pressure chamber. According to claim 12, however, it is useful to connect a plurality of return devices to one supply pressure chamber. A simple structure with only one connection to the compressed air and a simple structure with only one oil separation outlet for a plurality of return devices are possible.

In principle, according to the invention, many different designs of pneumatic return devices can be devised. In the claims 13 to 16, in connection with the claimed 5 and 6, a particularly simple design of the valve is described, in which the valve can be arranged at the lower point of the cylinder chamber of the cylinder / piston assembly. According to claim 13, the lower part of the cylinder can serve as a housing for the valve. The valve space may be usefully delimited by the cylinder inner surface, by a finish that closes the cylinder chamber, and by the valve member, and directly through the compressed gas source through a connection disposed on the cylinder wall. May be connected. According to claim 14, the first valve seat for the valve member may be formed as an annular stop. According to claim 15, the second valve seat may be formed as a sleeve portion of the finish. When the valve member moves toward the second valve seat, the connection with the cylinder chamber with the compressed gas source is broken and the throttle point on the valve member is deactivated. In addition, according to claim 16, it is particularly useful for arranging the oil separation outlet directly on the finish.

The valve is activated as soon as the pressure in the supply pressure chamber has passed the switching pressure. The latter depends both on the pressure of the supply pressure chamber and the initial stress of the spring. The requirements of claims 17 and 18 are, for example, as the initial stress can be set externally through the screw, useful.

According to claim 19, the maximum compression pressure of the valve can be set by the fluid cross section of the throttle point. If a higher compression pressure is required, the flow fluid cross section at the throttle point is reduced. With smaller throttle regions, the linkage between the cylinder chamber and the compressed gas source breaks faster, resulting in a higher maximum compression pressure. .

Due to the variant according to claims 17 to 19, the switching pressure and the maximum compression pressure in the cylinder chamber can be set in a simple manner.

With respect to the needle-type ribbon weaving machine, embodiments of the thread control device of the present invention are described in more detail by the figures and are as follows;

1 shows a needle-shaped ribbon weaving machine from the side;

Figure 2 shows an inlet device with a pneumatic return device in a plane perpendicular to the direction of movement of the warp yarns;

3 shows a more detailed and larger view of the pneumatic return device shown in FIG. 2 in its default position;

4 shows the pneumatic return device shown in FIG. 3 in the compressed position;

5 is a larger illustration of another embodiment of the pneumatic return device;

6 shows the pneumatic return device shown in FIG. 5 in a compressed position;

7a shows the pressure and piston profile of an air pressure return device according to the invention at slow speed;

7b shows the pressure and piston profile of the pneumatic return device under partial load; and

7c shows the pressure and piston profile of the pneumatic return device under full load.

※ Explanation of code for main part of drawing

2: machine stand 56a: valve

4 main drive shaft 58 supply pressure chamber

6: weft needle 60: compressed gas source

7: lead 64: cylinder

8: fabric winding machine 66: top dead center

10: inlet device 68: bottom dead center

12: warp beam stand 70: housing

14: warp beam 71: stop

16: warp yarn 72: first valve seat

18: shed 72a: first valve seat

20: thread feed device 74: finish

22: thread bobbin 74a: finish

24: weft 76: second valve seat

26: single chamber 76a: second valve seat

28: thread supply device 78: passage duct

30: Inlet 80: Throttle Point

31: seal guide member 80a: throttle point

32: link 82: valve member

34: cam drive 82a: valve member

35: positive direction drive device 84: spring

36: return device 84a: spring

38: pivot lever 86: lower

40: driving point 88: outlet

42: cam 88a: outlet

44: camshaft 90: connection

46: output point 90a: connection portion

48: junction 92: wall

50: pivot axis 94: valve space

52 cylinder chamber 96 sleeve portion

54: piston 98: lower

56: valve 100: wall

 FIG. 1, although not shown in detail, is equipped with a main drive shaft 4, a lid 7, a fabric winder 8 and an inlet device 10 that drive at least one weft needle 6. A ribbon weaving machine with a machine stand 2 is shown. The ribbon weaving machine stand has a warp beam stand 12 with warp beams 14, which are fed to the inlet device 10 with the warp yarns forming the shed 18 open. Due to the thread feeder 20, the weft 24 is fed from the thread bobbin 22 to the weft needle 6, which feeds from the weft loop to the shed 18. Although not shown in detail, in order to bind and secure the inserted weft loops, successive weft loops may be bundled by themselves, and the single thread 26 fed to the knitting needle through the thread feeding device 28 thereon. Might be tied up.

2 shows the inlet apparatus 10. The plurality of inlets 30 having the seal guide members 31 are connected by a link 32 to a cam drive 34 on one side via a positive direction drive device 35 and a pneumatic return device on the other side. Is connected in each case. Cam drive 34 has pivotal levers 38 that cooperate with drive point 40 with cams 42 of camshaft 44. At the output point 46, the pivot lever 38 follows the links 32 via the junctions 48. The pivot axes defined by the junctions 48 move perpendicular to the planes spanned by the inlets 30. The distance A of the pivot levers 38 of the driving points 40 from the respective pivot axes 50 is different between the neighboring pivot levers, and the output points 46 from the fixed pivot axes 50. The distance B is also different, and as shown in FIG. 1, the inlets are generally changed to ranges of different sizes to form a continuously widening and narrowing shed. The pneumatic return device 36 is formed by the cylinder chamber 52, and the piston 54 connected to the link 32 moves to reliably compress the piston at the number of times the cam drive 34 is actuated. The cylinder chamber 52 is connected to the valve 56. In order to maintain the gas pressure in the cylinder chamber 52, the latter is preceded through a supply pressure chamber 58 connected to the compressed gas source 60.

3 and 4 show a larger view of the air pressure return device during compression. In this case, FIG. 3 shows the piston 54 at the top dead center 66 and FIG. 4 shows the piston 54 at the bottom dead center 68 of the cylinder 64 after compression. . The valve housing is formed at one end and has a housing 70 such as a sleeve having a first valve seat 72 connected to the cylinder chamber 52, and a finish having a second valve seat 76 and a passage duct 78. In the section 74, there are two parts. The latter is connected to the supply pressure chamber 58. The valve member 82 provided with the throttle points 80 is arranged to be movable between the valve seats.

In the initial state shown in FIG. 3, the valve member 82 receives an initial stress against the first valve seat 72 by an initial stress of the spring 84, so that the cylinder chamber 52 and the supply pressure chamber ( 58 becomes a connection to each other via throttle points 80 in the passage duct 78 of the valve member 82 and the finish portion 74. As shown in FIG. 4, when the cylinder chamber 52 is at high pressure, the valve member 82 moves against the second valve seat 76, and the connection between the cylinder chamber 52 and the supply pressure chamber 58 is performed. Is blocked. Throttle points 80 are not active at this position.

The compression / expansion activity of the cylinder / piston part is described below with reference to FIGS. 3 and 4 and described in relation to the graphs of FIGS. 7A, 7B and 7C. In the latter, the bottom dead center is represented by UT, the top dead center is represented by OT, H represents the stroke of the piston of the cylinder / piston part, and PK represents the pressure of the gas in the cylinder chamber. PS expresses the necessary switching pressure so that the valve member can switch from the first valve seat to the second valve seat or from the second valve seat to the first valve seat. The switching pressure PS may be divided into the supply pressure PD of the compressed gas source and the pressure PF corresponding to the spring force. In this case VZ shows the position of the shutoff valve, and VO shows the position of the valve leading to the cylinder chamber through the throttle points.

First, in the cylinder 64, the piston 54 moves from top to bottom opposite the supply pressure chamber 58, and at the same time in the first phase, the piston 54 is formed of a valve member 82 such as a piston. It moves the air through the throttle points 80. As the speed of the piston increases, the switching force generated by the cylinder chamber pressure PK on the valve member 82 is applied to the valve member 82 generated by the stress of the spring 84 and the supply pressure PD. The pressure difference (PK-PD) through the valve member 82 rises until it overcomes the force against and presses the valve member 82 against the second valve seat 76. The valve member 82 then rises. Throttle point 80 is no longer active. Thus, with piston 54 moving further toward valve 56, cylinder chamber pressure PK rises rapidly during compression activity of cylinder chamber 52 ， Maximum at bottom dead center (UT). In the expanded phase, the valve member 80 is provided with the first valve seat 72 at the second valve seat at the moment when the spring force exceeds the force generated on the valve member 80 as a result of the pressure difference PK-PD. Move to At the end of the expansion phase, a supply pressure PD corresponding to the top dead center 66 of the piston is established in the cylinder chamber. Furthermore, any oil accumulated in the cylinder chamber 52 is then passed through the passage duct 78. During the next compression activity, the outflowing oil is stopped by the air moving into the supply pressure chamber 58 and exits the oil separation outlet 88 formed in the lower portion 86 of the supply pressure chamber. A connection 90 to the compressed air is disposed on the side wall 92 of the supply pressure chamber, preventing further oil backflow.

5 and 6 show a further design of the pneumatic return device during compression activity. In this case, FIG. 5 again shows the piston 54 at the top dead center 66, and FIG. 6 shows the piston 54 of the bottom dead center 68 at the cylinder 64 after compression of the cylinder chamber 52. The valve 56a is repositioned directly at the lowest point of the cylinder 64. The wall of the cylinder serves in this case as the valve housing, and the valve space 94 is the wall of the cylinder 64, the cylinder ( It is delimited by the closing portion 74a closing 64 and the wall of the valve member 82a such as a piston. A stop 71 designed as a ring is placed directly in the cylinder 64 of the cylinder / piston part and It serves as a first valve seat 72a for a valve member 82a such as a piston. The latter is supported by a closing portion 74a that closes the cylinder, has an inner sleeve 96 that guides the spring 84a, and is free to act as a second valve seat 76a with respect to the valve member 82a. It also has an end. When the latter comes opposite to the second valve seat 76a, the throttle points 80a formed in the valve member 82a are inactive. Likewise, in this position, the connecting portion 90a disposed in the cylinder for the compressed gas source 60 is blocked by the valve member 82a. Oil accumulated in the cylinder chamber 52 may flow out through the oil separation outlet 88a formed as the finish portion 74a.

In the initial state shown in FIG. 5, the valve member 82a is applied to the stress force of the spring such that the cylinder chamber 52 is connected to the compressed gas source through the throttle points 80a at the valve member 82a. It is compressed to face the first valve seat. When the cylinder chamber 52 is high pressure, as shown in FIG. 6, the valve member 82a moves against the second valve seat 76a and is disposed on the cylinder chamber 52 and the cylinder wall. Blocking the connection 90a breaks the connection between the compressed gas source 60. Throttle points 80a are not active at this position.

At the end of the expansion phase, the supply pressure is established in the cylinder chamber 52. Thereafter, any oil accumulated in the cylinder chamber 52 can flow out through the throttle points 80a into the valve space 94. During the next compression activity, the outflowing oil is moved to the valve space 94. It is blocked by air and flows out of the oil separation outlet 88a formed as the lower portion 98 in the closing portion 74a. The connection 90a to the compressed air is arranged on the wall 100 of the cylinder away from the bottom of the closure, preventing further backflow of oil.

In accordance with the present invention, FIGS. 7A, 7B and 7C show a slow load at a speed of 800 rev / min (Figure 7a), a partial load at 1000 rev / min (Figure 7b), and 4000 rev / min (Figure 7c). In full load, we are concerned with two load cycles.

For example, at a slow speed of 800 rev / min (Fig. 7a), the cylinder pressure (PK) is continuous so that the cylinder pressure (PK) does not reach the switching pressure (PS) necessary to break the connection between the cylinder chamber and the compressed gas source. Pressure compensation occurs through the throttle points of the valve member. Therefore, the pressure in the cylinder chamber PK is always in the order of the supply pressure PD. The motor load caused by the driving of the air pressure is lowered, the motor load causes the motor to run quietly, and in particular the driving In the case of switching off, the thread control device is moved manually, for example for the purpose of setting up and repairing.

Under partial load at 1000 rev / min (Figure 7b), after the cylinder chamber pressure PK reaches the required switching pressure PS during the cycle, the valve breaks the connection between the cylinder chamber and the compressed gas source, Compression begins in the cylinder chamber. At the bottom dead center (UT), the compression of the cylinder chamber reaches its maximum. During subsequent expansion, the cylinder chamber pressure PK again falls below the switching pressure PS. Then, the cylinder chamber is once again connected to the compressed gas source, and when the top dead center point OT of the piston is reached, the supply pressure PD is once again made in the cylinder chamber. The compression pressure of the cylinder chamber prevents the roller from being lifted off at both drive eccentrics in high speed operation.

Under full load at 4000 rev / min, the switching pressure (PS) is faster than at low speed (Figure 7c). Therefore, compression takes place over a larger stroke, so that the maximum compression pressure reaches a higher value than in low speed operation. During subsequent expansion, after the required switching pressure PS is brought back, the valve is connected to the cylinder chamber and the compressed gas source. To recover. The maximum compression pressure is a direct function of the machine speed, i.e. at high speeds, the maximum compression pressure also increases. This is an advantage of both the efficient operation of the machine and the satisfactory function of the positive direction drive.

 A valve opened once per cycle results in a continuous outflow of lubricant accumulated in the cylinder chamber. Thus, reliable and continuous operation of the mechanism is possible without the multiple durations of removing lubricant from the cylinder chamber. The work and requirements for the valves described above occur independently, ie there is no external activity. The spring force, the throttle cross section, and the dimensions of the valve member outer diameter or valve stem diameter can serve as independent control functions of the valve.

Thus, the return device described herein for a real control device independently fills a number of requirements and enables the least expense at the same time in technical conditions. Therefore, in particular, in terms of cost-efficiency, the return device can be produced well, and because of its simple structure, continuous operation is free during operation and without defects.

According to the invention, the control device may also be used for the control of individual yarns, for example a jacquard machine in the weft device for the supply of individual wefts.

Claims (19)

At least one seal guide member movable in one direction of movement by means of the drive device 35 designed in the positive direction and in the opposite direction of movement by means of the return device 36 designed by air pressure in the negative direction ( 31, the latter having a cylinder / piston assembly 64, 54, whose cylinder chamber 52 is connected to a source of compressed gas 60 through valves 56, 56a. As a thread control device for The valves 56, 56a may include a first valve seat 72, 72a and a second valve seat 76, 76a connected to the cylinder chamber 52, and at least one throttle point 80 moving between them. 80a is provided with valve members 82, 82a, which are initially stressed against the first valve seats 72, 72a by means of springs 84, 84a in a basic position, The throttle points 80, 80a are deactivated and the valve members 82, 82a are depressed when the valve members 82, 82a are opposed to the second valve seats 76, 76a. Seal control device, characterized in that for disconnecting. The seal control device according to claim 1, wherein the valve has a housing (70) at one end where the first valve seat (72) is formed. The seal control device according to claim 2, wherein the second valve seat (76) is formed on a finish portion (74) designed as a passage duct (78). 4. Seal control device according to claim 2 or 3, characterized in that the housing (70) is designed in a cylindrical shape, in which a piston-type valve member (82) is guided and sealed against the housing wall. The seal control device according to claim 2 or 3, characterized in that the gap between the valve member (82) and the housing wall of the valve (56) is used as a throttle point. The seal control device according to claim 1 or 2, wherein the valve (56, 56a) is arranged in the cylinder chamber (52). The seal control device according to claim 1 or 2, wherein the valve (56, 56a) is disposed at the lowest point of the cylinder (64). 4. Seal control device according to claim 3, characterized in that the closure (74) of the valve (56) is directly connected to a supply pressure chamber (58). 9. The seal control apparatus as claimed in claim 8, wherein the supply pressure chamber (58) has an oil separation outlet (88) for oil coming out of the cylinder chamber (52). 10. The seal control apparatus according to claim 9, wherein the oil separation outlet (88) is disposed on a lower portion (86) of the supply pressure chamber (58). 12. The seal control apparatus according to claim 10, wherein a connection portion (90) for compressed air is arranged on the side wall (92) of said supply pressure chamber from said lower portion (86) of said supply pressure chamber (58). . 9. Seal control device according to claim 8, characterized in that the supply pressure chamber (58) of at least one return device (36) is used as supply pressure and oil outflow device. A seal control device according to claim 1, characterized in that the lower part of the cylinder (64) serves as a valve housing and has a connection (90a) to the compressed gas source (60). 14. The seal control according to claim 13, characterized in that the annular stop (71) is arranged inside the cylinder (64) and designed as the first valve seat (72a) connected to the cylinder chamber (52). Device. 15. The cylinder (64) of claim 14 wherein the cylinder (64) is closed by a finish (74a), the finish (74a) has a sleeve portion (96), and the free end of the sleeve portion (96) is the second portion. Seal control device which acts as a valve seat (76a). 16. The seal control device according to claim 15, wherein an oil separation outlet (88a) is disposed on the finish portion (74a). The seal control device according to claim 1, wherein the switching pressure (PS) of the valve (56, 56a) can be set by a change in the initial stress of the spring (84, 84a). 18. The seal control apparatus according to claim 17, wherein the initial stress of the spring (84, 84a) can be set externally. The seal control apparatus according to claim 1, wherein the maximum compression pressure (PK) in the cylinder chamber (52) can be set by means of the fluid cross section of the throttle point (80, 80a).

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