EP0168800B1 - Pneumatischer Schlagantrieb für Webschützen - Google Patents

Pneumatischer Schlagantrieb für Webschützen Download PDF

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Publication number
EP0168800B1
EP0168800B1 EP85108826A EP85108826A EP0168800B1 EP 0168800 B1 EP0168800 B1 EP 0168800B1 EP 85108826 A EP85108826 A EP 85108826A EP 85108826 A EP85108826 A EP 85108826A EP 0168800 B1 EP0168800 B1 EP 0168800B1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
chamber
shuttle
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP85108826A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0168800A3 (en
EP0168800A2 (de
Inventor
Pekka Ferdinand Alm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Herman Wangner GmbH and Co KG
Original Assignee
Herman Wangner GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Herman Wangner GmbH and Co KG filed Critical Herman Wangner GmbH and Co KG
Priority to AT85108826T priority Critical patent/ATE32756T1/de
Publication of EP0168800A2 publication Critical patent/EP0168800A2/de
Publication of EP0168800A3 publication Critical patent/EP0168800A3/de
Application granted granted Critical
Publication of EP0168800B1 publication Critical patent/EP0168800B1/de
Expired legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/24—Mechanisms for inserting shuttle in shed
    • D03D49/42—Mechanisms for inserting shuttle in shed whereby the shuttle is propelled by liquid or gas pressure

Definitions

  • the invention relates to a pneumatic percussion drive for shooters, in which a piston in a cylinder is acted upon by a pressurized fluid and drives the shooter via a piston rod.
  • the supply of the pressure fluid from a reservoir into the cylinder is controlled by a main valve, which has a valve seat and a valve element and a valve guide in which the valve element is slidably mounted.
  • An auxiliary valve actuates the main valve by creating a pressure difference between the front and rear of the valve element.
  • Such a pneumatic percussion drive for web shooters is known from US Pat. No. 2,677,933.
  • the memory surrounds the cylinder in a ring, and the valve seat is formed by the open end of the cylinder, into which the front cylindrical end of the valve element can be inserted to close the main valve.
  • the pressure prevailing in the cylinder and the working pressure prevailing in the accumulator surrounding the cylinder act on the front of the valve element.
  • a high pressure can act on the back of the valve element by means of the auxiliary valve, which results in the closing of the main valve, or atmospheric pressure, which results in the opening of the main valve.
  • the main valve When the main valve is open, the compressed gas present in the reservoir flows into the cylinder and the Piston applied, which then drives the shooter via the piston rod.
  • a pneumatic impact drive is known from US Pat. No. 3,698,444, in which the piston drives the impact arm via a crank mechanism.
  • the supply of the pressure fluid from a reservoir into the cylinder is controlled by a magnetically operated main valve.
  • This impact drive is mechanically complex due to the crank mechanism.
  • the invention has for its object to provide a pneumatic percussion drive for shooters in which the piston can be acted upon with the full pressure present in the accumulator without major losses and within the shortest possible time and it is ensured that the piston assumes its starting position again.
  • the main valve is arranged between the memory and the cylinder chamber and the valve element is designed as a cap-shaped valve plate with a hollow rear side and has a valve stem which is displaceably mounted in the valve guide, the annular wall of the hollow rear side of the Valve plates are essentially fluid-tight on the outer circumference of the valve guide, so that a chamber is formed between the rear of the valve plate and the front of the valve guide, the volume of which changes with the valve plate movement and, when the main valve is closed, has its maximum volume such that the auxiliary element is in a continuous bore of the valve stem is slidably mounted and, depending on its position, connects the chamber either with the cylinder space or via the bore of the valve stem and the guide bore of the valve guide with the accumulator, the auxiliary valve when the main valve and Au are closed Starting position of the piston is pushed back by the piston and thereby connects the chamber to the cylinder chamber and that a control valve is provided for controlling the movement of the valve plate, which has a control opening, which
  • the valve seat is preferably conical and the valve disk is provided with a correspondingly conical ring region.
  • An O-ring can be inserted into a groove of the valve seat for sealing.
  • the auxiliary valve is preferably spindle-shaped, so it consists of a stem with a thickening with an O-ring in the middle, which rests against the inner wall of the longitudinal bore of the valve stem. From the chamber located on the back of the valve plate, connection openings open into the longitudinal bore of the valve stem. Depending on its position, the auxiliary valve gives the way back from these connection openings into the accumulator or after free in the front of the cylinder space. For better guidance and to limit the axial movement of the spindle in the longitudinal bore of the valve stem, there is a further thickening at the rear end of the stem, this thickening having longitudinal bores so that the connection between the connection openings and the memory is not impaired.
  • the valve guide has a central bore for guiding the hollow valve stem.
  • On the outer circumference of the valve guide lies the annular edge of the hollow rear of the valve plate, so that a chamber is formed between the valve guide and the rear of the valve plate.
  • the pressure in this chamber depends on the position of the auxiliary valve and contributes to the control of the main valve.
  • the control valve is connected to the accumulator and through the control opening to the front area of the valve seat, so that there is also a connection to the cylinder space even when the main valve is closed.
  • the control opening is selectively connectable to the memory or to a compressed gas source through the control valve, the gas with a relatively low excess pressure, the so-called brake pressure of z. B. 0.2 bar, or with a vacuum source of z. B. 0.2 bar negative pressure.
  • the memory is also constantly connected to a compressed gas source for the so-called working pressure, which is adjustable and z. B. 4 bar overpressure.
  • the terms "overpressure and" underpressure denote the pressure difference from the ambient pressure (atmospheric pressure).
  • the front of the cylinder chamber is vented to the surroundings, so that the front of the piston is pressurized by atmospheric pressure.
  • the pneumatic percussion drive is controlled in such a way that, in the initial position of the piston, the control opening of the control valve is connected to the negative pressure source, so that the piston is held in its initial position by the negative pressure. He presses the auxiliary valve to the rear so that negative pressure is also present at the connection openings of the chamber and there is also negative pressure in the chamber itself. The main valve is thus kept closed by the pressure difference.
  • the control opening of the control valve is connected to the accumulator by the control valve, so that working pressure is present on the front of the valve plate and on the piston. Since the pressure equalization takes place slowly through the relatively fine connection openings, there is initially still negative pressure in the chamber, while the working pressure is already applied to the front of the valve plate.
  • valve disk backwards i.e. that is, the main valve opens and the piston is driven forward by the pressurized gas under pressure, so that the shooter is knocked through the shed.
  • the auxiliary valve Due to its inertia, the auxiliary valve does not or only partially follows the movement of the valve plate, but remains in its position.
  • the application of pressure to the front of the valve plate via the control opening takes place only for a very short period of time of a fraction of a second and the main valve opens in about 0.1 seconds.
  • the piston only moves a few centimeters during this time. Due to the working pressure built up in the cylinder chamber, the piston is driven forward and the shooter is knocked off.
  • the control opening of the control valve is now connected to the brake pressure source. Since the brake pressure is significantly lower than the working pressure, the main valve now closes, i. H. the valve plate moves forward and lies against the valve seat. The auxiliary valve follows this movement because the same pressure difference is applied to it, so that the front end of the auxiliary valve now projects into the cylinder chamber.
  • the chamber is now at its maximum volume and there is working pressure in it, since the connection openings of the chamber are connected to the accumulator.
  • the level of the brake pressure is chosen so that the piston can intercept the incoming shooter within the piston stroke.
  • the piston grasps the auxiliary valve and pushes it backwards, as a result of which the connection openings of the chamber are connected to the cylinder chamber and the pressure in the chamber is reduced to the brake pressure. Since there is always working pressure on the outer circumference of the valve plate pointing backwards, the main valve is kept in its closed position.
  • the control opening of the control valve is connected to the vacuum source after the braking process has ended. If the piston has not reached its rear end position due to the braking of the shuttle, it is now pulled into this position by the negative pressure and held in it, since atmospheric pressure is present at the front of the piston. The negative pressure also spreads into the chamber through the connection openings.
  • the work cycle of the pneumatic percussion drive is now complete. To knock off the shooter, the control opening of the control valve is reconnected to the reservoir in the next work cycle.
  • the position into which the piston is pushed back by the kinetic energy of the shooter during interception is not precisely defined, since it depends on the friction of the piston within the cylinder and the speed of the shooter, which are both subject to fluctuations.
  • the piston is therefore only brought into its rear end position by the vacuum applied in the last working cycle. Therefore, in order to have the full piston stroke available as an acceleration path when knocking off the shooter
  • means are provided by which the shooter is carried along by the piston rod during the backward movement of the piston triggered by the negative pressure and is thus also brought into its rearward end position.
  • At the top of the piston rod there is z. B. a catch hook that is raised in the front end position of the piston and thereby releases the shooter.
  • the pneumatic percussion drive has a cylinder 1, a main valve 2, an accumulator 3 for gas under working pressure, an electrical control valve 4 and an auxiliary valve 5.
  • the cylinder 1 surrounds a cylinder space 6, in which a piston 7 and a piston rod 8 are mounted so that they can move back and forth.
  • the front end of the cylinder space 6 is open to the outside via an opening 9.
  • the piston rod engages with its front end on the shuttle 10 via a buffer 31, an embodiment of which is shown in FIGS. 6 to 8.
  • the main valve 2 also has a valve plate 12 with a valve stem 13 and an annular rim 14 and a valve guide 15.
  • the valve guide 15 has a cylindrical surface and is arranged coaxially to the cylinder 1 behind the valve seat 11. It has a central guide bore 16 in which the valve stem 13 is mounted.
  • the annular, axially rearwardly extending edge 14 of the valve plate 12 slides on the outside of the valve guide 15, so that a chamber 17 is formed between the front of the valve guide 15 and the rear of the valve plate 12.
  • the chamber 17 is closed to the outside and has only in the front region of the hollow valve stem 13 connecting openings 18 of z. B. 2 mm in diameter.
  • the valve stem 13 has a continuous axial bore 19 which opens at the rear into the guide bore 16 of the valve guide 15, which in turn leads to the accumulator 3, and which also opens into the cylinder space 6 at the front.
  • the valve plate 12 is displaceably guided on the valve guide 15, the volume of the chamber 17 changing when the valve plate 12 moves.
  • the main valve is closed, ie when the valve plate 12 is in contact with the valve seat 11, the volume of the chamber 17 is greatest, while the volume of the chamber is smallest when the main valve 2 is open and is practically zero.
  • To the rear connects to the main valve 2 of the memory 3, which can consist of a cylindrical space that is connected to a compressed gas source of, for. B. 4 bar pressure is connected.
  • the auxiliary valve 5 is slidably mounted in the bore 19 of the valve stem 13. It serves to connect the connection openings 18 of the chamber 17 either to the reservoir 3 or to the cylinder space 6.
  • the auxiliary valve 5 is spindle-shaped and consists of a shaft 20 with a disk-shaped thickening 21 with an O-ring in the middle of the shaft 20, which bears sealingly on the inner wall of the bore 19.
  • the movement of the auxiliary valve 5 is limited by suitable stops so that the disk-shaped thickening 21 is located in the front position of the auxiliary valve in front of the connection openings 18 and in the rear end position of the auxiliary valve 5 behind the connection openings 18, the stem 20 being in the front position something protrudes into the cylinder space 6.
  • the rear end of the shaft 20 can also be provided with a thickening 22, 22 axial channels 23 running through this thickening so that it has no shut-off effect.
  • Valve seat 11 and valve plate 12 have sealing surfaces that expand conically towards the rear.
  • an O-ring 25 is also inserted at the wide end in an annular groove 24, which serves for sealing.
  • a first line 26 opens into the conical sealing surface of the valve seat 11 behind the O-ring 25 and a second line 27 in front of the O-ring 25.
  • the first line 26 establishes a connection between the accumulator 3 and the control valve 4, while the second line 27 a control opening 28 connects to the control valve 4.
  • Both lines 26, 27 are arranged so that their ends are not closed by the valve plate 12 even in the closed position of the main valve. With the first line 26, this can be achieved in a simple manner in that it opens out at the wide end of the valve seat 11.
  • the second line 27 leads to the control opening 28, which is located at the narrow end of the valve seat 11, the transition from the valve seat 11 to the cylinder chamber 6 being somewhat rounded, so that the second line 27 via the control opening 28 even with the main valve 2 closed Cylinder chamber 6 communicates.
  • the control valve 4 is designed so that it can optionally perform three functions, namely firstly the first line 26 and to connect the second line 27 to each other, second to close the first line 26 and the second line 27 with a compressed gas source for the braking pressure of z. B. 0.2 bar overpressure and third to close the first line 26 and the second line 27 with a vacuum source of z. B. 0.2 bar negative pressure.
  • the impact drive described above works in three work cycles.
  • the main valve is closed, there is negative pressure on the second line 27 and the piston 7 is in its rear starting position and presses the auxiliary valve 5 backwards, so that the connection openings 18 are connected to the front of the valve plate 12 and in the chamber 17 is also under negative pressure.
  • This state is shown in Fig. 1. He is the starting position before the shooter is knocked off.
  • the auxiliary valve 5 does not change its position, or changes it only slightly, because of its inertia. that is, it moves forward relative to the valve plate 12.
  • the third work cycle begins.
  • the first line 26 is closed, and the second line 27 vents the working pressure through a line 29 until the desired brake pressure prevails, and is connected to a pressurized gas source that provides the brake pressure, which is relatively low and z. B. 0.2 bar overpressure.
  • the brake pressure is significantly lower than the working pressure, so that there is a lower pressure on the front of the valve plate 12 than on the rear.
  • the valve plate 12 is thereby pushed against the valve seat 11, so that the main valve 2 closes.
  • the auxiliary valve 5 does not change its position relative to the valve plate 12, i. that is, it is also pushed forward so that the chamber 17 enlarges, in which the working pressure exists.
  • Fig. 3 This state is shown in Fig. 3, and once the main valve 2 is closed, the percussion drive is able to catch and slow down the returning shooter.
  • the shooter 10 is braked evenly by the pressure cushion in the cylinder space 6.
  • the required braking distance depends on the level of the braking pressure and the size of the control opening between the second line 27 and the cylinder space 6 and the size of the opening 9.
  • the braking distance is chosen as large as possible, i. that is, the brake pressure is as small as possible so that the piston 7 comes to a standstill when the shuttle 10 is braked near its left end position.
  • the first line 26 remains closed and the second line 27 with a negative pressure source, which is a negative pressure of z. B. 0.2 bar, connected.
  • This negative pressure in turn propagates through the control opening 28 into the cylinder chamber 6 and pulls the piston 7 completely into its left end position or starting position if it should not already have reached this by the braking process.
  • the piston 7 presses the auxiliary valve 5 backwards into the bore 19 of the valve stem 13, so that the connection openings 18 are now in communication with the cylinder chamber 6 and the negative pressure also propagates into the chamber 17.
  • the percussion drive is ready for the next hitting of the shooter 10.
  • the valve disk 12 Since there is negative pressure in the chamber 17 in this first working cycle, the valve disk 12 is kept closed only by the working pressure acting on the annular rim 14 and on the auxiliary valve 5.
  • the annular edge 14 should therefore have a sufficient area, the actual effective area resulting from the difference in diameter of the O-ring 25 and the valve guide 15.
  • the O-ring 25 can e.g. B. a diameter of 8.5 cm, the valve guide 15 has such a 6.3 cm and the auxiliary valve 5 has such a two centimeters.
  • the effective area is then approximately 29 cm 2 , so that a closing force of approximately 1200 N results at a working pressure of 4 bar.
  • the control valve 4 is operated by a pro grammage of the weaving machine shaft activated. Manual operation is also provided for single-shot operation. There is a vacuum valve between the control valve and the vacuum source, which is activated by the position sensor of the contactor box. There is also a brake valve between the control valve and the pressure source for the brake pressure, which is also activated by the position sensor of the contactor box. Since the timing of the programming of the control valve, the vacuum valve and the brake valve takes place in such a way that the pneumatic percussion drive essentially knocks off the shooter at the same time as a mechanical percussion drive, it is familiar to the person skilled in the art and is not described in more detail here.
  • the main valve 2 should be as short as possible and the area of the annular space formed between the valve seat 11 and the valve plate 12 when the main valve 2 is open, so that the flow resistance is as low as possible.
  • the gas should be able to flow from the reservoir 3 into the cylinder space 6 without too much change of direction.
  • FIG. 5 shows the details of a preferred embodiment.
  • 0-rings 40 are provided for sealing.
  • a sleeve seal 41 is provided in the interior of the annular edge 14 and a sleeve seal 42 is provided in the guide bore 16 in order to seal the chamber 17 as well as possible from the reservoir 3.
  • An O-ring 43 is fastened in a groove in the end face of the valve guide 15 and dampens the impact of the valve plate 12 on the valve guide 15.
  • the auxiliary valve 5 is guided in an annular insert 44, the inside diameter of which corresponds to the thickening 21 of the auxiliary valve 5 and which tapers at the front to the diameter of the stem 20, so that the latter is guided.
  • the rear end of the shaft 20 has a thickening 22 which slides in the bore 19 and has axial channels 23.
  • the front end position of the auxiliary valve 5 is defined by the abutment of the thickening 22 on the insert 44, an O-ring 45 being interposed and damping the impact.
  • a compression spring 46 is supported against a stepwise diameter widening of the bore 19 of the valve stem 13 that opens toward the rear. The other end of the compression spring 46 is seated on a guide pin 47 which is fastened to the rear end of the guide bore 16 by means of a snap ring 48.
  • the compression spring 46 is not essential for the function of the impact drive, but only facilitates assembly and gives the valve disk 15 a defined position in the depressurized state.
  • the front end of the compression spring 46 also serves as a stop for fixing the rear end position of the auxiliary valve 5, for which purpose an O-ring 49 is inserted between the thickening 22 and the compression spring 46.
  • Figures 6 to 8 show a device by which the front end of the piston rod 8 is firmly connected to the shuttle 10, as long as the piston 6 is not in its front end position, so that the piston 7 when it is in the first stroke by the in the cylinder space 6 prevailing negative pressure is pulled back, the shooter 10 takes.
  • This device consists of a catch hook 30, which is attached to the front end of the piston rod 8, wherein there is also a buffer 31 at the front end of the piston rod 8, which acts on the shuttle 10.
  • the catch hook 30 is articulated somewhat above the buffer 31 and engages in the recess 32, which is located in the archer and receives its rollers 33.
  • the front end of the catch hook 30 engages in this recess 32 at the bottom and is provided at the top with a slide roller 34 which runs along a rail 35 which is arranged parallel to and at a distance above the rifle track.
  • the rail 35 has a rubber pad 36, on which the sliding roller 34 travels along, so that the catch hook 30 is pressed elastically downward and cannot fall out of the recess 32 of the shuttle 10.
  • the catch hook 30 In the front end position of the percussion drive, the catch hook 30 must release the shooter 10 so that the latter can insert the weft thread into the shed. The catch hook 30 must therefore be raised in the front end position.
  • An advantage of the pneumatic impact drive consists in its relatively low noise level. While the noise development in a weaving machine for paper machine screens with a mechanical impact drive is approximately 90 dB (A), it can be reduced to approximately 82 dB (A) by using the pneumatic impact drive.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Details Of Valves (AREA)
  • Looms (AREA)
  • Actuator (AREA)
  • De-Stacking Of Articles (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Load-Engaging Elements For Cranes (AREA)
  • Soil Working Implements (AREA)
EP85108826A 1984-07-18 1985-07-15 Pneumatischer Schlagantrieb für Webschützen Expired EP0168800B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85108826T ATE32756T1 (de) 1984-07-18 1985-07-15 Pneumatischer schlagantrieb fuer webschuetzen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3426534 1984-07-18
DE3426534A DE3426534A1 (de) 1984-07-18 1984-07-18 Pneumatischer schlagantrieb fuer webschuetzen

Publications (3)

Publication Number Publication Date
EP0168800A2 EP0168800A2 (de) 1986-01-22
EP0168800A3 EP0168800A3 (en) 1986-08-06
EP0168800B1 true EP0168800B1 (de) 1988-03-02

Family

ID=6240986

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85108826A Expired EP0168800B1 (de) 1984-07-18 1985-07-15 Pneumatischer Schlagantrieb für Webschützen

Country Status (6)

Country Link
US (1) US4602660A (pt)
EP (1) EP0168800B1 (pt)
AT (1) ATE32756T1 (pt)
BR (1) BR8503405A (pt)
DE (2) DE3426534A1 (pt)
ES (1) ES288006Y (pt)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6481723B1 (en) * 2001-03-30 2002-11-19 Lam Research Corporation Lift pin impact management
EP1777330A1 (de) * 2005-10-01 2007-04-25 Markus Farner Verfahren zur Abstützung eines Schussfadenführungselements

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2677933A (en) * 1949-05-13 1954-05-11 Pneumatic Loom Dev Corp Pneumatic shuttle actuating means
DE1218368B (de) * 1957-05-04 1966-06-02 Emil Jaeger K G Hydraulische Schuetzenschlagvorrichtung fuer Webstuehle
AT265157B (de) * 1965-09-10 1968-09-25 Elitex Zavody Textilniho Vorrichtung zum Einschlagen des Greiferschützens auf Greiferwebstühlen
GB1291881A (en) * 1969-08-23 1972-10-04 Hindle Son And Company Ltd Pneumatic picking motion for a loom
US3902530A (en) * 1972-07-24 1975-09-02 Crompton & Knowles Corp Projectile picking means for a pneumatic loom
CS179720B1 (en) * 1975-10-10 1977-11-30 Vladimir Svaty Piston rod controlling device
US4082118A (en) * 1976-10-20 1978-04-04 Crompton & Knowles Corporation Pneumatic picking mechanism for looms
SE415040B (sv) * 1977-11-14 1980-09-01 Aelmhults Bruk Ab Hydraulisk drivanordning for en skyttel

Also Published As

Publication number Publication date
BR8503405A (pt) 1986-04-08
EP0168800A3 (en) 1986-08-06
DE3426534A1 (de) 1986-01-23
US4602660A (en) 1986-07-29
ES288006U (es) 1986-01-01
EP0168800A2 (de) 1986-01-22
DE3561753D1 (en) 1988-04-07
ATE32756T1 (de) 1988-03-15
ES288006Y (es) 1986-08-01

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