EP2113592B1 - Exzentermaschine mit Vorrichtung zur Fachgleichstellung - Google Patents

Exzentermaschine mit Vorrichtung zur Fachgleichstellung Download PDF

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Publication number
EP2113592B1
EP2113592B1 EP20080155491 EP08155491A EP2113592B1 EP 2113592 B1 EP2113592 B1 EP 2113592B1 EP 20080155491 EP20080155491 EP 20080155491 EP 08155491 A EP08155491 A EP 08155491A EP 2113592 B1 EP2113592 B1 EP 2113592B1
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EP
European Patent Office
Prior art keywords
cam
excenter
drive
adjusting device
adjusting
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 - Fee Related
Application number
EP20080155491
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German (de)
English (en)
French (fr)
Other versions
EP2113592A1 (de
Inventor
Bernhard Münster
Dr. Johannes Bruske
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.)
Groz Beckert KG
Original Assignee
Groz Beckert KG
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Filing date
Publication date
Application filed by Groz Beckert KG filed Critical Groz Beckert KG
Priority to EP20080155491 priority Critical patent/EP2113592B1/de
Priority to CN2009101378596A priority patent/CN101570908B/zh
Publication of EP2113592A1 publication Critical patent/EP2113592A1/de
Application granted granted Critical
Publication of EP2113592B1 publication Critical patent/EP2113592B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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

Definitions

  • the invention relates to an eccentric machine for driving at least one weaving shank of a weaving machine, preferably for driving a plurality of heddle shafts.
  • Eccentric machines are used to drive healds, which are used in looms for shedding.
  • Each eccentric machine has a number of wings, which serve as outputs for the heald frames.
  • the eccentric derives the swinging motion of the rocker from the rotational movement of an input shaft. For this purpose, it has a number of cams and cam followers, which couple via a linkage with the wings.
  • This eccentric also has a Exzenterverstell Surprise on, if necessary, to transfer the heald frames to a zero position.
  • This zero position is a position in which all heddles have the same height. This is also referred to as a shaft equalization.
  • the Exzenterverstell Marie serves to adjust the game between cam followers and cams. At maximum play, the cam followers lift off the cam discs and abut against a stop, whereby all shafts go into the said compartment equalization. All shafts are approximately in zero position and the warp threads are maximally relieved.
  • the compartment equalization is for maintenance work, e.g. Changing the dishes and correcting faults is necessary and also relieves the warp threads of machine downtime.
  • the adjusting eccentric is provided with an arm which carries a threaded nut at its end. This engages with a motor driven spindle.
  • the motor unit is itself rotatably mounted about an axis in order to follow the circular arc movement of the spindle nut can.
  • the variable displacement motor must be hung swinging.
  • the adjustment of the eccentric is limited to an angle which is less than 180 °. In addition to the large number of moving parts and bearings, a high-torque and therefore large drive motor must be used because the gear ratios achievable with a threaded spindle are limited.
  • the rack is driven by a suitable drive.
  • a suitable drive This can for example be an electric motor with a Spindelhubgetriebe.
  • Other linear drives, such as electric linear motors or hydraulic linear drives are also used.
  • the combination of a rotating electric motor with Spindelhubgetriebe for driving the rack is considered particularly advantageous.
  • a rotating electric motor with Spindelhubgetriebe for driving the rack With a correspondingly low thread pitch and long thread engagement, high reductions and correspondingly large actuating forces can be achieved at low drive torques achieve.
  • the achievable driving forces are greater than in worm gears with screws of the same pitch because of the possible in principle long and around the entire circumference of the spindle threaded engagement.
  • a stepper motor, synchronous motor, asynchronous motor, DC motor can be used, the rotor is connected directly or via a gear to the threaded spindle.
  • the eccentric adjustment device comprises one or more eccentrics for all shaft drives.
  • all the rockers sit on a common shaft, which is adjustable by the adjusting eccentric in their relative position to the cams.
  • the adjustment of the Exzenterverstell annoying by a gear transmission has the advantage that the rotational movement of the eccentric can be adjusted by any angle.
  • the angle adjustment is limited only by the length of the rack. With a correspondingly long trained rack, the eccentric can be rotated by 180 degrees or more. Thus, the eccentricity can be fully exploited.
  • FIG. 1 is an eccentric 1 illustrated, which is used to drive not illustrated heddle shafts of a loom.
  • the eccentric 1 has at least one rocker 2, but preferably a plurality of wings 2a to 2g, which serve as outputs.
  • the wings 2a to 2g protrude from the in FIG. 1 missing housing and are driven back and forth.
  • This is rotatably mounted in the machine frame 4 of the eccentric and optionally drives via a bevel gear 5 and other gear means a pivot drive 6 for the wings 2a to 2g.
  • Such a pivot drive is exemplary in FIG. 2 as well as in FIG. 3 illustrated.
  • the description of the "rocker 2" applies equally and is representative of all the wings 2a to 2g, unless expressly noted differences.
  • Each rocker 2 (2a to 2g) are associated in the preferred embodiment, one or two cams 7, 8, which are rotationally driven by the main shaft 3.
  • the cam discs 7, 8 are cam followers 9, 10, for example in the form of rollers 11, 12, assigned, which are in each case with the circumference of the associated cam 7, 8 in abutment.
  • the cam followers 9, 10 are held on a rocker 13.
  • the cam tracks defined by the outer peripheries of the cams 7, 8 are preferably matched to one another such that the rollers 11, 12 effect a pivoting of the rocker 13 during one revolution of the cams 7, 8 coupled to each other in a rotationally fixed manner, wherein they are continually in contact with the cams 7 , 8 remain.
  • the rocker 13 can, as FIG. 2 shows, be rigidly connected to the rocker 2.
  • the rocker 13 can be indirectly connected for example via a link 14 or other power transmission means with the rocker 2, as it FIG. 3 suggests.
  • the part-turn actuators of the various Swing 2a to 2g are preferably constructed basically the same, they can cause different pivoting movements of the wings 2a to 2g.
  • the rocker 13 forms an element which is pivotally mounted about a pivot center 15.
  • the pivot center 15 is the center axis of a pivot bearing 16, which is indicated only symbolically in the figures and can be designed both as a sliding bearing and as a rolling bearing.
  • the pivot bearing 16 is mounted eccentrically in the machine frame 4, whereby a Exzenterverstell sensible 17 is formed.
  • a rotary body 18 which is rotatable about its central axis 19.
  • the pivot center 15 shifts, as in FIG. 2 indicated by two small curved arrows.
  • the rotary body 18 thus forms an eccentric.
  • FIG. 3 As a result, the pivoting center 15 of the rocker 13 can be moved away from and toward the cam disks 7, 8.
  • FIGS. 4 to 6 illustrate various variants of the training of the Exzenterverstell issued 17.
  • the various wings 2a to 2g each on its own eccentric 20a to 20g, which are interconnected by a shaft 21. This corresponds in its function to the rotary body 18. It is rotatable about the axis 19.
  • the rotary body 18 or the shaft 21 is non-positively or materially connected to a first adjusting means 22.
  • This first adjusting means 22 interacts with a second adjustment means 23 in a form-fitting manner.
  • the second adjusting means 23 is connected via a gear to a drive 26.
  • the transmission can, for example, the rotational movement of the drive 26 convert into a linear movement of the second adjusting means 23.
  • the rotary body 18 and the shaft 21 is connected to a gear 22a or only with a gear segment, as in FIG. 2 is illustrated by the dashed representation of a portion of the gear 22a.
  • the gear 22a meshes with a rack 23a.
  • the gear 22a is a spur gear with straight teeth.
  • the rack 23a is slidably mounted in corresponding linear bearings 24, 25, which may be formed, for example, as plain bearings, ie longitudinally in a tangential direction to the gear 22a. It is secured against rotation in a suitable manner.
  • the rack 23a is connected via a Spindelhubgetriebe with a drive 26 in the form of a motor.
  • the Spindelhubgetriebe can be formed, for example, by the rack 23amit provided with a threaded bore 27.
  • a threaded spindle 28 engages in threaded bore 27, wherein the motor 26 is fixedly mounted in the machine frame 4.
  • the motor 26, the threaded spindle 28 and the rack 23 a form a linear adjusting drive 29 for the Exzenterverstell issued 17th
  • the rotary body 18 and the shaft 21 is connected to the pivot member 22b.
  • the pivot member 22b has a receiving device 34 in its end region away from the center of rotation.
  • this recording device 34 formed in the form of a slotted guide or recess. This embodiment is not part of the invention.
  • This recess 34 receives an extension 35 of the guide element 23b.
  • This extension 34 is connected to the guide element 23b and may for example have the shape of a pin.
  • the pivot member 22b thus cooperates with the guide element 23b.
  • the guide element 23b is slidably mounted in corresponding linear bearings 24, 25, which may for example be designed as slide bearings, ie longitudinally in a tangential direction to the pivot member 22b.
  • the guide element 23b is connected via a screw jack with a drive 26 in the form of a motor.
  • the screw jack for example, be formed by the guide member 23 b is provided with a threaded bore 27.
  • a threaded spindle 28 engages in threaded bore 27, wherein the drive 26 is fixedly mounted in the machine frame 4.
  • the drive 26, the threaded spindle 28 and the guide element 23b form a linear adjustment drive 29 for the Exzenterverstell issued 17th
  • the eccentric machine 1 described so far works as follows:
  • the eccentric adjusting device 17 is rotated by means of the linear adjusting drive 29 in such a position that the pivot center 15 is relatively close to the cams 7, 8.
  • the cam followers 9, 10 are in constant engagement with the curves of the cams 7, 8.
  • Turning the cams 7, 8 follows a reciprocating pivotal movement of the rocker 13. Accordingly, all swing 2a to 2g perform each by the law of motion of the associated Cams fixed oscillating or pivoting movement.
  • the motor 26 is set in motion. This rotates the threaded spindle 28 and thereby displaces the rack 23a in a longitudinal direction.
  • the rack 23a thereby rotates the gear (or gear segment) 22 and with this the rotary body 18 and the shaft 21.
  • all the eccentrics 20a to 20g are rotated synchronously in a direction in which the pivot center 15 of the cams 7, 8 away.
  • the cam followers 9, 10 are thus out of engagement with the cams 7, 8.
  • the wings 2 (2a to 2g) are thus no longer fixed by the cams 7, 8 in their pivoting position. They lean against a stop. This puts them in the same subject area.
  • FIG. 6 shows, it is also possible to support the wings 2a to 2g on a shaft 20 ', which is supported at its two ends in each case by an eccentric 20a, 20b.
  • eccentric 20a, 20b are mounted in the machine frame 4 concentric with each other about an axis 19 rotatably.
  • Both eccentrics 20a, 20b are rotatable synchronously with each other. They can be interconnected or provided with their own adjustment drives.
  • the linear adjustment drive is formed by the motor 26, the lead screw 28, the rack 23a, which meshes with the gear 22a or sector gear.
  • FIG. 7 illustrates a modified linear adjustment 29 in the form of a linear motor 30.
  • This includes a stator 31 and a rotor 32.
  • the (electric) linear motor 30 may be formed, for example, as a linear stepping motor. Its rotor 32 may include corresponding permanent magnets.
  • the slider 32 may also be connected directly to the rack 23a. This arrangement allows particularly fast adjusting movements.
  • a separate locking device 33 may be provided to lock the rack 23a in a predetermined axial position.
  • the locking device 33 can act as shown on the rack 23a or alternatively directly on the Exzenterverstell Road 17 to lock the eccentric 20 to the body 18 and the shaft 21 rotatably.
  • the eccentric machine according to the invention with the improved Exzenterverstell Stein 17 overcomes the inherent disadvantages of the prior art by the eccentric, the rotary body 18, which determines the pivot center 15 of the rocker 2 and the rocker 13 is provided with a toothing with a rack 23 a interacts.
  • the rack 23a rotates by its longitudinal movement of the eccentric 18 and thus adjusts the play between the cams 7, 8 and the cam followers 9, 10 a.
  • the rack 23a can receive its longitudinal movement from a drive motor 26 whose Rotary movement is converted by the threaded spindle 28 in a longitudinal movement of the rack 23a.
  • the rack 23a can also be driven directly by a linear motor 30. This structure allows a sufficiently high reduction so that a space-saving motor 26 can be used with low power.
  • the drive unit does not have to be stored in a movable way. Overall, fewer parts and bearings are required than in the prior art.
  • a sander 2 (2a-2g) Swing 3 main shaft 4 machine frame 5 angle gear 6 Rotary actuator 7, 8 cams 9, 10 Cam follower means 11, 12 roll 13 Element, rocker 14 handlebars 15 pivoting center 16 pivot bearing 17 eccentric adjustment 18 Rotary body, eccentric 19 axis 20, 20a, 20b eccentric 20c eccentrically mounted shaft 21 wave 22 adjusting, 22a Gear / gear segment 22b pivot member 23 adjustment 23a rack 23b guide element 24, 25 linear bearings 26 Drive, engine 27 threaded hole 28 screw 29 Linear adjustment 30 linear motor 31 stator 32 runner 33 Locking device 34 recording device 35 Extension, pin

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Transmission Devices (AREA)
EP20080155491 2008-04-30 2008-04-30 Exzentermaschine mit Vorrichtung zur Fachgleichstellung Expired - Fee Related EP2113592B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20080155491 EP2113592B1 (de) 2008-04-30 2008-04-30 Exzentermaschine mit Vorrichtung zur Fachgleichstellung
CN2009101378596A CN101570908B (zh) 2008-04-30 2009-04-29 具有梭口协调装置的偏心多臂机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20080155491 EP2113592B1 (de) 2008-04-30 2008-04-30 Exzentermaschine mit Vorrichtung zur Fachgleichstellung

Publications (2)

Publication Number Publication Date
EP2113592A1 EP2113592A1 (de) 2009-11-04
EP2113592B1 true EP2113592B1 (de) 2013-05-08

Family

ID=40083689

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20080155491 Expired - Fee Related EP2113592B1 (de) 2008-04-30 2008-04-30 Exzentermaschine mit Vorrichtung zur Fachgleichstellung

Country Status (2)

Country Link
EP (1) EP2113592B1 (zh)
CN (1) CN101570908B (zh)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH594082A5 (zh) 1975-07-10 1977-12-30 Albatex Ag
JPH0721584Y2 (ja) * 1990-03-19 1995-05-17 株式会社豊田自動織機製作所 織機のヘルドフレームのレベリング装置
FR2868090B1 (fr) 2004-03-29 2006-05-26 Staubli Faverges Sca Dispositif de nivelage, mecanique d'armure a came incorporant un tel dispositif et metier a tisser d'une telle mecanique

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Publication number Publication date
EP2113592A1 (de) 2009-11-04
CN101570908B (zh) 2012-06-20
CN101570908A (zh) 2009-11-04

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