EP1687472B1 - Fadensteuervorrichtung für eine textilmaschine, insbesondere für eine fachbildevorrichtung - Google Patents

Fadensteuervorrichtung für eine textilmaschine, insbesondere für eine fachbildevorrichtung Download PDF

Info

Publication number
EP1687472B1
EP1687472B1 EP04797226A EP04797226A EP1687472B1 EP 1687472 B1 EP1687472 B1 EP 1687472B1 EP 04797226 A EP04797226 A EP 04797226A EP 04797226 A EP04797226 A EP 04797226A EP 1687472 B1 EP1687472 B1 EP 1687472B1
Authority
EP
European Patent Office
Prior art keywords
valve
control device
thread control
cylinder
valve seat
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.)
Active
Application number
EP04797226A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1687472A1 (de
Inventor
Erich Bühler
Bernhard Engesser
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.)
Textilma AG
Original Assignee
Textilma AG
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 Textilma AG filed Critical Textilma AG
Publication of EP1687472A1 publication Critical patent/EP1687472A1/de
Application granted granted Critical
Publication of EP1687472B1 publication Critical patent/EP1687472B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C13/00—Shedding mechanisms not otherwise provided for
    • D03C13/02—Shedding mechanisms not otherwise provided for with independent drive motors
    • D03C13/025—Shedding mechanisms not otherwise provided for with independent drive motors with independent frame drives
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C13/00—Shedding mechanisms not otherwise provided for
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C5/00—Cam or other direct-acting shedding mechanisms, i.e. operating heald frames without intervening power-supplying devices
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C5/00—Cam or other direct-acting shedding mechanisms, i.e. operating heald frames without intervening power-supplying devices
    • D03C5/02—Cam or other direct-acting shedding mechanisms, i.e. operating heald frames without intervening power-supplying devices operated by rotating cams
    • D03C5/04—Construction or shape of cams

Definitions

  • the invention relates to a thread control device of a textile machine, in particular for a shedding device according to the preamble of claim 1.
  • Thread control devices for textile machines are known in large numbers.
  • the closest prior art according to the WO 97/08373 discloses a thread control device which is formed with a drive and a retraction device for a thread guide member.
  • the thread guide member is movable in a direction of movement by means of the form-fitting drive and in the opposite direction of movement by means of a frictional and pneumatically formed retraction device acting against the form-locking drive.
  • the pneumatic retraction device has a cylinder / piston unit whose cylinder chamber is designed with a pressure relief valve and a check valve which is connected to a compressed gas source. The gas pressure in the cylinder chamber is adjusted depending on the operating state of the textile machine.
  • the gas pressure is kept smaller than in a high-speed phase, so that the electric motor can provide the necessary power to overcome the resulting from the compression of the cylinder chamber load.
  • a high-speed phase of the electric motor provides sufficient power so that the gas pressure can be further increased to prevent lifting a roll on a cam of the positive drive.
  • the cylinder chamber may be configured with a manually operable pressure relief valve to minimize the resistance created by the compression of the cylinder chamber when setting up the textile machine.
  • a disadvantage of the above solution is that the gas pressure in the cylinder chamber must be adapted to a respective operating state. This requires a complex pressure control device for adjusting the gas pressure of the cylinder chamber, the pressure reducing valves and opening valves to control each cylinder chamber necessary. Moreover, a complex electronic control of the valves is necessary in order to adapt the pressure in the cylinder chambers to a respective operating state.
  • the valve is designed such that in addition to the requirements of stationary operation, an oil separation is possible.
  • the valve is actuated at regular time intervals for a few seconds to allow the accumulated in the compression chamber oil to drain. So that a lifting of the role of the eccentric of the positive drive is avoided, the speed of the textile machine during this process (so-called care cycle) must be reduced. It is also opened in the crawl, so that the pressure in the cylinder chamber does not rise significantly above the feed pressure. This reduces the required power of the motor, which is necessary so that the main motor can run around at low speeds and thus manual turning of the handwheel without too much effort is possible.
  • a disadvantage of the above solution is the great effort for electrical / pneumatic control of the valve.
  • the whole control of the pneumatic drive of the yarn control device therefore has a large number of components, such as check valves, pressure relief valves, pressure reducing valves, and electronic control units, which make the system more susceptible to disturbances.
  • the economy of the textile machine is alleviated by the repetitive lowering of the engine speed every 15 minutes to discharge the lubricating oil. Lowering the engine speed may also adversely affect web quality, for example, resulting in a slight change in the width of the manufactured web.
  • the object of the invention is to improve a yarn control device of the type mentioned.
  • the valve has a first associated with a cylinder chamber valve seat and a second valve seat, between which a provided with at least one throttle and biased against the first valve seat with a spring valve member is movable, wherein the throttle body is ineffective and the valve member communication with the compressed gas source locks when the valve member is present at the second valve seat, the valve can operate without external control in different operating conditions. Furthermore, a reliable separation of oil without lowering the speed, a reduction of the maximum compression pressure in the cylinder chamber at partial load, as well as lowering the compression pressure to feed pressure in crawl without additional measures provided by the autonomously operating valve.
  • valve In principle, various embodiments of the designed with two valve seats valve are conceivable.
  • Advantageous is an embodiment according to claims 2 and 3, wherein the housing has two parts, wherein the one part has the first valve seat at one end and the other is designed as a final part of the housing with the second valve seat and a passageway.
  • the valve therefore has the simplest possible structure, which allows cost-effective production and easy assembly of the valve.
  • the valve housing can basically have different shapes, advantageously a cylindrical design of the housing according to claim 4. This training allows a good guidance of the piston-like valve member in the housing.
  • the piston-like valve member may also be provided with a sealing ring to seal the cylinder chamber to the outside.
  • the valve may be arranged in a connecting line between the cylinder chamber and the feed pressure chamber.
  • a direct arrangement in the cylinder of the cylinder / piston assembly according to claim 6 is advantageous.
  • the valve can thus communicate directly with the cylinder chamber, and lubricating oil accumulated in the cylinder chamber can thus be fed through the valve into the supply pressure chamber in a short path. Accordingly, the end part of the valve is connected directly to the feed pressure chamber according to claim 8, in turn, to minimize the flow resistance and the flow path of the effluent oil.
  • the feed pressure chamber can in principle have any desired configuration.
  • Advantageous is an embodiment according to claims 9 to 12, which the feed pressure chamber is formed with an outlet for oil separation arranged at its bottom, and according to which a connection for compressed air can be arranged on a lateral wall at a distance from the bottom of the feed pressure chamber.
  • This arrangement of the compressed air connection and the oil separation outlet prevents accumulated oil in the supply pressure chamber from clogging the compressed air connection or flowing into a connection line of the compressed air connection.
  • each retraction device can have a separate feed pressure chamber.
  • valves 13 to 16 a particularly simple embodiment of the valve is described, while the valve may be arranged in conjunction with the claims 5 and 6 in a lower position of the cylinder chamber of the cylinder / piston unit.
  • a lower portion of the cylinder can serve as a housing for the valve.
  • the valve space can be advantageously limited by the cylinder inner surface, by a closing the cylinder chamber end part and by a valve member and are connected directly via a arranged on the cylinder wall connection with a compressed gas source.
  • a first valve seat for the valve member may be formed according to claim 14 on an annular stop.
  • a second valve seat may be formed on a sleeve part of the closure part. Moves the valve member against the second valve seat, the communication of the cylinder chamber is blocked with the source of pressurized gas and the throttle points on the valve member ineffective.
  • the valve is activated as soon as the pressure in the feed pressure chamber exceeds the switching pressure.
  • the latter depends both on the pressure of the feed pressure chamber and on the biasing force of the spring.
  • the biasing force can be adjusted, for example via a screw from the outside.
  • the maximum compression pressure of the valve is adjustable by means of the flow cross-section of the throttle point according to claim 19. If a higher compression pressure is required, the flow cross-section of the throttle point is reduced. Due to the smaller throttle area, the communication between the cylinder chamber and the compressed gas source is interrupted earlier, whereby a higher maximum compression pressure is achieved.
  • the switching pressure and the maximum compression pressure in the cylinder chamber can be adjusted in a simple manner.
  • the FIG. 1 shows a needle loom with a machine frame 2, in which a main drive shaft 4 is mounted, which drives at least one unsinged weft needle 6, a reed 7, a fabric take-off 8 and designed as a shank device 10 thread control device.
  • the needle loom comprises a warp beam frame 12 carrying warp beams 14, from which warp yarns 16 are fed to the shank device 10 which opens the warp yarns to a shed 18.
  • a weft yarn 24 of the weft needle 6 is fed from a yarn package 22, which introduces a weft yarn loop into the shed 18.
  • Successive weft loops can be tied with themselves or by means of a fishing thread 26 which is fed via a further yarn feeding device 28 of a knitting needle, not shown here, to bind a registered weft yarn loop and secure.
  • the Figures 2 shows the shaft device 10, in which a plurality of shaft frame 30 are connected to thread guide members 31 each by means of a link 32 on the one hand via a positive drive 35 with a cam drive 34 and on the other hand with a pneumatic retraction device 36.
  • the cam drive 34 has pivot lever 38, which cooperate at a drive point 40 with cam 42 of a camshaft 44. At the output point 46, the pivot lever 38 are articulated via joints 48 to the links 32.
  • the given by the joints 48 pivot axes extend at right angles to the plane defined by the shaft frame 30 levels.
  • the distances A of the pivot lever 38 of the drive points 40 to the respective pivot axes 50 are different between adjacent pivot levers, wherein the distances B of the output points 46 to the fixed pivot axes 50 are different, the whole such that the shaft frames are displaced by different lengths, to form a continuously widening and narrowing shed, like this FIG. 1 evident.
  • the pneumatic retraction device 36 is formed by a cylinder chamber 52, in which a piston 54 is displaceable, which is in communication with the handlebar 32 in order to compress the piston positively in the operating frequency of the cam drive 34.
  • the cylinder chamber 52 is connected to a valve 56.
  • the latter is preceded by a feed pressure chamber 58 via which a compressed gas source 60 is connected in order to maintain the gas pressure in the cylinder chamber 52 upright.
  • FIG. 3 and FIG. 4 show the pneumatic retraction device on a larger scale during a compression process.
  • the valve housing consists of two parts, a sleeve-like housing 70 having formed at one end of the first valve seat 72 which is connected to the cylinder chamber 52 and a closure member 74, the a second valve seat 76 and a passageway 78 has. The latter is connected to the feed pressure chamber 58. Between the valve seats provided with throttle bodies 80 valve member 82 is movably arranged.
  • valve member 82 In the initial state of FIG. 3 is the valve member 82 by means of the biasing force of a spring 84 against the first. Valve seat 72 biased so that the cylinder chamber 52 and the feed pressure chamber 58 communicating via the throttle bodies 80 in the valve member 82 and the passageway 78 of the closure member 74 communicating with each other. At high pressure in the cylinder chamber 52, the valve member 82 moves against the second valve seat 76 and interrupts the communication between the cylinder chamber 52 and the feed pressure chamber 58, as shown in FIG FIG. 4 is shown. In this position, the throttle bodies 80 are ineffective.
  • H stands for the stroke of the piston of the cylinder / piston unit with UT as bottom dead center and TDC as top dead center and PK for the pressure of the gas in the cylinder chamber.
  • PS represents the necessary switching pressure, so that the valve member switches from the first to the second valve seat, respectively from the second to the first valve seat.
  • the switching pressure PS can be divided into the feed pressure PD of the compressed gas source and the corresponding pressure PF of the spring force.
  • VZ represents the position of the locked and VO that of the valve communicating with the cylinder chamber via the throttle points.
  • the piston 54 moves in the cylinder 64 from top to bottom and displaces it in a first phase of air through the throttle valve 80 formed on the piston-like valve member 82 against the feed pressure chamber 58th
  • the pressure difference (PK-PD) above the valve member 82 increases until the switching force generated by the cylinder chamber pressure PK on the valve member 82 overcomes the biasing force of the spring 84 and the force on the valve member 82 generated by the feed pressure PD, and the valve member 82 against the second valve seat 76 presses.
  • the throttle point 80 of the valve member 82 is no longer effective.
  • the cylinder chamber pressure PK increases sharply during the compression process in the cylinder chamber 52 and reaches its maximum at the bottom dead center UT.
  • the valve member 80 moves from the second to the first valve seat 76 as soon as the spring force exceeds the force generated by the pressure difference (PK-PD) on the valve member 80.
  • the feed pressure PD sets in the cylinder chamber. Moreover, any accumulated oil in the cylinder chamber 52 can now drain through the passageway 78.
  • the outflowing oil is blown out by the displaced into the feed pressure chamber 58 air and flows in an outlet formed at a bottom 86 of the feed pressure chamber 88 for oil separation.
  • a connection 90 for compressed air is arranged on a side wall 92 of the feed pressure chamber, thus preventing further backflow of the oil.
  • FIG. 5 and FIG. 6 show a further embodiment of a pneumatic retraction device on a larger scale during a compression process.
  • the piston 54 in turn in a top dead center 66 and FIG. 6 the piston 54 at a bottom dead center 68 in the cylinder 64 after the compression of the cylinder chamber 52.
  • a valve 56a is in turn disposed directly at a lowermost point of the cylinder 64.
  • the wall of the cylinder serves as a valve housing and a valve chamber 94 is bounded by the wall of the cylinder 64, a closure member 64a closing the cylinder 64 and a piston-like valve member 82a.
  • a trained as a ring stop 71 is disposed directly in the interior of the cylinder 64 of the cylinder / piston unit and serves as an ester valve seat 72a for the piston-like valve member 82a.
  • the latter is in turn biased against the first valve seat 72a by a spring 84a.
  • the spring 84a is supported on the end part 74a closing off the cylinder, which has an inner sleeve part 96 for guiding the spring 84a and whose free end also serves as a second valve seat 76a for the valve member 82a. If the latter abuts against the second valve seat 76a, throttling point 80a formed in the valve member 82a becomes ineffective.
  • connection 90a arranged on the cylinder for a compressed gas source 60 is blocked by means of the valve member 82a.
  • An oil discharge outlet 88a formed on the end part 74a can drain oil accumulated in the cylinder chamber 52.
  • valve member 82a In the initial state of FIG. 5 the valve member 82a is biased by the biasing force of the spring 84a against the first valve seat 72a, so that the cylinder chamber 52 with a compressed gas source via the throttle bodies 80a in Valve member 82a are in communication. At high pressure in the cylinder chamber 52, the valve member 82 a moves against the second valve seat 76 a and interrupts the communication between the cylinder chamber 52 and the compressed gas source 60 by blocking the port 90 a disposed in the cylinder wall, as shown in FIG FIG. 6 is shown. In this position, the throttle bodies 80a are ineffective.
  • connection 90a for compressed air is arranged on a wall 100 of the cylinder at a distance from the bottom of the closure part, and thus prevents further backflow of the oil.
  • FIG. 7a, 7b and 7c are the pressure and piston curves of the inventive retraction device over two load cycles in creeper for a speed of 800 rev / min ( Figure 7a ), for part load at 1000 rpm ( FIG. 7b ) and for full load at 4000 rpm ( FIG. 7c ).
  • the cylinder chamber pressure PK reaches the required switching pressure PS during one cycle, whereupon the valve blocks the communication of the compressed gas source with the cylinder chamber and the compression begins in the closed cylinder chamber.
  • the compression in the cylinder chamber reaches its maximum at a bottom dead center UT.
  • Upon subsequent expansion of the cylinder chamber pressure PK falls again below the switching pressure PS.
  • the cylinder chamber is now again in communication with the source of compressed gas and upon reaching a top dead center OT of the piston is again in the cylinder chamber feed pressure PD a.
  • the required switching pressure PS is reached earlier (FIG. 7c) than at lower operating speeds.
  • the compression therefore takes place over a larger stroke and consequently the maximum compression pressure reaches a higher value than at lower operating speeds.
  • the necessary switching pressure PS is reached, whereupon the valve restores the communication of the cylinder chamber with the compressed gas source.
  • the maximum compression pressure is a direct function of the speed of the machine, i. at higher speeds, the maximum compression pressure also increases. This is advantageous both for economical operation of the machine, as well as for proper operation of the positive drive.
  • valve By opening the valve once per cycle, a continuous flow of the accumulated in the cylinder chamber lubricating oil. For a safe and steady operation of the system is possible without any maintenance cycles to remove the lubricating oil from the cylinder chamber.
  • the above-described tasks and requirements for the valve are autonomous, ie without any external control.
  • By dimensioning the spring force, the throttle cross-section and the valve member outer diameter or the valve seat diameter are given the autonomous control functions of the valve.
  • the retraction device for a Fanden horrinvorraum described here thus fulfills a variety of requirements autonomously and at the same time has a minimal technical effort.
  • the retraction device is therefore particularly inexpensive to manufacture and largely maintenance and trouble-free in operation due to their simple structure.
  • the inventive thread control device can also be used for a single thread control, for example for a jacquard machine, further in a weft thread device for presenting individual weft threads.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Looms (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Actuator (AREA)
  • Sewing Machines And Sewing (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Lift Valve (AREA)
EP04797226A 2003-11-28 2004-11-05 Fadensteuervorrichtung für eine textilmaschine, insbesondere für eine fachbildevorrichtung Active EP1687472B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH20342003 2003-11-28
PCT/CH2004/000669 WO2005052233A1 (de) 2003-11-28 2004-11-05 Fadensteuervorrichtung für eine textilmaschine, insbesondere für eine fachbildevorrichtung

Publications (2)

Publication Number Publication Date
EP1687472A1 EP1687472A1 (de) 2006-08-09
EP1687472B1 true EP1687472B1 (de) 2010-01-20

Family

ID=34624412

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04797226A Active EP1687472B1 (de) 2003-11-28 2004-11-05 Fadensteuervorrichtung für eine textilmaschine, insbesondere für eine fachbildevorrichtung

Country Status (11)

Country Link
US (1) US20070119142A1 (ko)
EP (1) EP1687472B1 (ko)
JP (1) JP4617314B2 (ko)
KR (1) KR100754106B1 (ko)
CN (1) CN1886540B (ko)
AT (1) ATE455885T1 (ko)
BR (1) BRPI0416975B1 (ko)
DE (1) DE502004010685D1 (ko)
ES (1) ES2337470T3 (ko)
HK (1) HK1094812A1 (ko)
WO (1) WO2005052233A1 (ko)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2019158B1 (en) * 2007-07-26 2010-01-27 Luigi Omodeo Zorini Needle loom
DE102008046326A1 (de) * 2008-08-29 2010-03-04 Picanol N.V. Verfahren und Vorrichtung zum Beobachten eines Bewegungsverlaufs einer Webmaschine
CN101922076B (zh) * 2009-06-12 2012-08-15 赵斯伟 织机开口装置
WO2012163571A2 (de) * 2011-06-01 2012-12-06 Textilma Ag Schaftwebmaschine und entsprechendes webverfahren
CN103132213A (zh) * 2011-12-02 2013-06-05 江南大学 一种小样织机双气缸控制剑杆的快速引纬方法
DE102013101988A1 (de) * 2013-02-28 2014-08-28 Maschinenfabrik Rieter Ag Spinnstelle zur Herstellung eines Garns
EP3018244B1 (de) * 2014-11-04 2017-03-15 Karl Mayer Textilmaschinenfabrik GmbH Legebarrenanordnung einer Kettenwirkmaschine
CN104727001B (zh) * 2015-04-20 2016-09-07 江苏工程职业技术学院 一种缂丝半自动小样机装置
EP3141642A1 (de) * 2015-09-10 2017-03-15 Textilma Ag Webmaschine zur herstellung von webgut mit eingearbeiteten wirk- oder legefäden
CN105350139B (zh) * 2015-11-13 2017-06-30 浙江嘉欣丝绸股份有限公司 一种磁控气压式大提花开口控制装置及控制方法
EP3257983A1 (de) * 2016-06-15 2017-12-20 Textilma Ag Nadelbandwebmaschine und entsprechendes webverfahren
CN111334914B (zh) * 2020-04-24 2021-12-28 博优技术纺织品(威海)有限公司 一种织机的共轭凸轮开口装置及其纺织方法

Family Cites Families (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE17298E (en) * 1929-05-21 Compressor
US1728824A (en) * 1927-05-03 1929-09-17 Firm Maschinenfabrik Carl Zang Drive for dobby and jacquard looms
US2072180A (en) * 1933-11-13 1937-03-02 Packard Motor Car Co Internal combustion engine
US2425676A (en) * 1943-10-18 1947-08-12 Hindle Thomas Hydraulic shedding means
NL251171A (ko) * 1959-06-03 1900-01-01
US3270836A (en) * 1964-02-06 1966-09-06 Morgan Construction Co Pressurized lubricating system
CH448923A (de) * 1965-12-15 1967-12-15 Sulzer Ag Webmaschine
US3587251A (en) * 1969-03-11 1971-06-28 Santoni & C Spa Device for the operation of members in circular machines for stockings,socks and the like
GB1315628A (en) 1971-03-02 1973-05-02 Bonas Machine Co Shedding motion
CS157292B1 (ko) * 1972-01-20 1974-09-16
CH620253A5 (ko) * 1977-04-14 1980-11-14 Sulzer Ag
US4444292A (en) * 1981-08-12 1984-04-24 Standard Oil Company (Indiana) Method and apparatus for lubricating a machine
US4566498A (en) * 1983-01-24 1986-01-28 Williams Gilmer A Reed control mechanism for terry loom
DE3442204A1 (de) * 1984-08-27 1986-03-06 Klöcker-Entwicklungs-GmbH, 4280 Borken Vorrichtung zur bildung einer dreherkante
US4693282A (en) * 1986-04-22 1987-09-15 Leonard Campbell Lubricating system for a weaving machine
DE4116163A1 (de) * 1991-03-13 1992-09-17 Textilma Ag Fachbildevorrichtung fuer eine textilmaschine
US5329913A (en) * 1991-03-26 1994-07-19 Yamaha Hatsudoki Kabushiki Kaisha Oil vapor separator system for the engine of a gas heat pump air conditioner
IT1252804B (it) * 1991-09-24 1995-06-28 Tcnotessile Centro Ricerche S Dispositivo per la movimentazione dei fili di ordito
US5711615A (en) * 1993-03-18 1998-01-27 Barmag Ag Antifriction bearing
DE9307391U1 (de) * 1993-04-26 1993-09-30 Textilma Ag, Hergiswil Fachbildevorrichtung für eine Webmaschine
SE501893C2 (sv) * 1993-10-14 1995-06-12 Svenska Rotor Maskiner Ab Skruvkompressor med variabla axialbalanseringsorgan
DE29513815U1 (de) * 1995-08-29 1995-10-19 Textilma Ag, Hergiswil Textilmaschine zur Herstellung von Textilerzeugnissen aus Fäden
WO1997011215A1 (de) * 1995-09-21 1997-03-27 Textilma Ag Vorrichtung zur wahlweisen steuerung einer oszillierenden querbewegung eines fadens, insbesondere eines kettfadens einer webmaschine
BE1010014A3 (nl) * 1996-02-09 1997-11-04 Picanol Nv Kanteninrichting voor een weefmachine.
JPH10153170A (ja) * 1996-11-25 1998-06-09 Sanden Corp 斜板式圧縮機のピストン
DE29716100U1 (de) * 1997-09-08 1997-10-30 Textilma Ag, Hergiswil Fadensteuervorrichtung
DE19939131A1 (de) * 1999-08-18 2001-03-08 Zexel Gmbh Axialkolbentriebwerk mit einem stufenlos verstellbaren Kolbenhub
JP4431912B2 (ja) * 1999-09-09 2010-03-17 株式会社ヴァレオサーマルシステムズ 斜板式圧縮機
JP3538137B2 (ja) * 2000-10-23 2004-06-14 津田駒工業株式会社 織機における開口装置
US6622824B2 (en) * 2001-03-07 2003-09-23 Daniel H. Roehrborn Lubrication supply system for a machine
US6877494B2 (en) * 2002-07-12 2005-04-12 Pearson Motor Company Limited Lightweight four-stroke engine
BE1015048A4 (nl) * 2002-07-19 2004-09-07 Wiele Michel Van De Nv Inrichting voor het bevestigen van terugtrekveren in een harnas van een jacquardweefmachine.
JP2004052150A (ja) * 2002-07-19 2004-02-19 Tsudakoma Corp 織機の往復運動装置
TWI303679B (en) * 2003-06-12 2008-12-01 Textilma Ag Loom
JP4244866B2 (ja) * 2004-06-04 2009-03-25 日産自動車株式会社 ディーゼルエンジンのオイル希釈検出装置及び制御装置
JP2006291751A (ja) * 2005-04-06 2006-10-26 Toyota Industries Corp ピストン式圧縮機

Also Published As

Publication number Publication date
KR20060088566A (ko) 2006-08-04
JP2007512441A (ja) 2007-05-17
JP4617314B2 (ja) 2011-01-26
KR100754106B1 (ko) 2007-08-31
EP1687472A1 (de) 2006-08-09
US20070119142A1 (en) 2007-05-31
BRPI0416975B1 (pt) 2014-12-23
CN1886540B (zh) 2011-01-12
ES2337470T3 (es) 2010-04-26
ATE455885T1 (de) 2010-02-15
CN1886540A (zh) 2006-12-27
BRPI0416975A (pt) 2007-02-21
DE502004010685D1 (de) 2010-03-11
WO2005052233A1 (de) 2005-06-09
HK1094812A1 (en) 2007-04-13

Similar Documents

Publication Publication Date Title
EP1394303B1 (de) Drosselventil für Druckluft oder dergleichen und seine Verwendung in einer Webmaschine
EP3394454B1 (de) Ventil, insbesondere 4/2-wegeschieberventil
EP1687472B1 (de) Fadensteuervorrichtung für eine textilmaschine, insbesondere für eine fachbildevorrichtung
DE69123764T2 (de) Vorrichtung für endlagedämpfung und geschwindigkeitsregelung der bewegung eines kolbens in einem druckmittelzylinder
DE2231217C2 (de) Hydraulische Steuervorrichtung zur lastunabhängigen Steuerung von hydraulisch betriebenen Einrichtungen
EP0761854B1 (de) Texturiermaschine mit pneumatischem Fadenanleger
DE1945844B2 (de) Vorrichtung zur Kompensation der durch das bewegte Walzgerüst von Rohrkaltwalzwerken hervorgerufenen Massenträgheitskräfte
DE1650267C3 (de) Hydraulische Vorrichtung zur Steuerung des Druckmittelflusses zu einem einen doppelt und einen einfachwirkenden Hydrozylinder aufweisenden hydraulischen System
CH681825A5 (ko)
DE19711594A1 (de) Vorrichtung zur Führung und Lagerung eines Greifertragorganes in Webmaschinen
CH641324A5 (de) Vorrichtung zur regelung des unterdruckes in einem unterdruckleitungssystem, insbesondere fuer melkanlagen.
DE2151837C2 (de) Hydraulische Steuervorrichtung für die lastunabhängige Druchflußregulierung zu einem Verbraucher
DE2248656A1 (de) Pneumatisch arbeitende vorrichtung zum anheben und absenken der kettfaeden bei webstuehlen
EP3770444B1 (de) Anordnung mit einem pneumatischen oder hydraulischen kolbenstangenzylinder
DE102022117745A1 (de) Vorrichtung und System zur Steuerung einer Bewegung eines Objekts
DE2238213A1 (de) Steuerung fuer hoehenveraenderliche arbeitsbuehnen
DE719561C (de) Leistungsregler
DE3836401A1 (de) Hydraulischer linearantrieb
DE10115916B4 (de) Wendestange für eine Materialbahn
EP3585720B1 (de) Fangzylinder für ein lasthebemittel sowie lasthebemittel mit einem fangzylinder
DE1600799C (de) Hydraulische Zu- und Abflußsteuerung für eine hydraulische Steuerkammer eines Ventils
DE1064770B (de) Durchflussventil mit Hilfsventilsteuerung
DE1178625B (de) Druckregeleinrichtung fuer eine Pumpe
DE1157517B (de) Verfahren und Vorrichtung zum Steuern der Geschwindigkeit von hydraulisch bewegten Ringbaenken oder Spindelbaenken bzw. Spulenbaenken an Feinspinnmaschinen oder Zwirnmaschinen bzw. Vorspinnmaschinen
DE177815C (ko)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20060323

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LU MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: SCHMAUDER & PARTNER AG PATENT- UND MARKENANWAELTE

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502004010685

Country of ref document: DE

Date of ref document: 20100311

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2337470

Country of ref document: ES

Kind code of ref document: T3

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20100120

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100520

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100520

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100421

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100420

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

26N No opposition filed

Effective date: 20101021

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100120

BERE Be: lapsed

Owner name: TEXTILMA A.G.

Effective date: 20101130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101130

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20101105

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101105

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20120110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101106

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 455885

Country of ref document: AT

Kind code of ref document: T

Effective date: 20101105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101105

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100721

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20161121

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20161110

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171130

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171130

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20201124

Year of fee payment: 17

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211105

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20231121

Year of fee payment: 20