EP0499218B1 - Fadenbremse - Google Patents

Fadenbremse Download PDF

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Publication number
EP0499218B1
EP0499218B1 EP92102286A EP92102286A EP0499218B1 EP 0499218 B1 EP0499218 B1 EP 0499218B1 EP 92102286 A EP92102286 A EP 92102286A EP 92102286 A EP92102286 A EP 92102286A EP 0499218 B1 EP0499218 B1 EP 0499218B1
Authority
EP
European Patent Office
Prior art keywords
brake
thread
guiding element
thread brake
elements
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 - Lifetime
Application number
EP92102286A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0499218A1 (de
Inventor
Atila Horvath
Hermann Schmodde
Josef Fecker
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.)
Memminger IRO GmbH
Original Assignee
Memminger IRO GmbH
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 Memminger IRO GmbH filed Critical Memminger IRO GmbH
Publication of EP0499218A1 publication Critical patent/EP0499218A1/de
Application granted granted Critical
Publication of EP0499218B1 publication Critical patent/EP0499218B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D04—BRAIDING; LACE-MAKING; KNITTING; TRIMMINGS; NON-WOVEN FABRICS
    • D04B—KNITTING
    • D04B15/00—Details of, or auxiliary devices incorporated in, weft knitting machines, restricted to machines of this kind
    • D04B15/38—Devices for supplying, feeding, or guiding threads to needles
    • D04B15/44—Tensioning devices for individual threads
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H59/00—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators
    • B65H59/10—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators by devices acting on running material and not associated with supply or take-up devices
    • B65H59/20—Co-operating surfaces mounted for relative movement
    • B65H59/22—Co-operating surfaces mounted for relative movement and arranged to apply pressure to material
    • B65H59/225—Tension discs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2555/00—Actuating means
    • B65H2555/10—Actuating means linear
    • B65H2555/13—Actuating means linear magnetic, e.g. induction motors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/30—Handled filamentary material
    • B65H2701/31—Textiles threads or artificial strands of filaments

Definitions

  • the invention relates to a thread brake with two, preferably disc or plate-shaped brake elements resiliently pressed against one another by load means, between which at least one thread to be braked can be carried out and which are mounted on a common bearing axis bearing means and are under the action of a device which sets them into oscillatory movements .
  • the brake disks or disks forming the brake elements are generally rotatably mounted on a guide pin which at one end has a thread on which an adjusting nut is attached is screwed on, which forms the abutment of a compression spring elastically pressing the two brake disks or plates.
  • lubricants adhering to the surface of the running thread paraffins, spool oil, etc.
  • deposits on the brake discs or plates, in which dirt particles and fluff are embedded with the result that a sticky, pasty Mass results that increasingly penetrates between the brake discs or plates.
  • the object of the invention is to remedy this and to create a thread brake of the type mentioned, which is characterized by an improved self-cleaning effect, i.e. the occurrence of undesirable deposits of lubricants etc. is effectively prevented and, at the same time, uniform thread braking is ensured over long operating periods.
  • Thread brake according to the invention characterized in that the braking elements can be set in oscillating movements by the oscillation generating device, said oscillating movements being mainly directed transversely to the bearing axis.
  • the brake elements are mounted on a guide element containing the bearing axis, the brake elements being able to be set in oscillatory movements together with the guide element.
  • the guide element can be rigid, for example as a cylindrical bolt.
  • the guide element is elastic at least in sections, which e.g. can be achieved in that the guide element is made of a corresponding plastic material.
  • the guide element is mounted elastically in mounting means, so that it receives the required mobility at its bearing point.
  • the braking elements themselves are advantageously mounted on the guide element with radial play, so that they can carry out a certain movement in the direction of vibration which is independent of the guide element.
  • practical experience has shown that with the conventional thread brakes of the type in question here, it is expedient that the oscillating movements have a frequency of approximately 40 to 500 Hz.
  • the excitation of the vibrations of the braking elements can be done in a variety of ways.
  • the structure of the facility used for this depends, among other things. also on the particular use of the thread brake and the drive means available at the place of use. It has proven to be advantageous if the oscillation generating device has a driven member which executes a reciprocating movement and which is coupled directly or indirectly to the brake elements.
  • the holding means in which the holding means participate in the oscillating movement of the braking elements, the holding means can be mounted directly on the link which executes the reciprocating movement, which results in a further simplification of the structural conditions.
  • the thread brake can be arranged on a thread delivery device having a rotating shaft, the member performing the reciprocating movement being coupled to the shaft via a gear mechanism producing this movement.
  • the shaft rotating in these thread delivery devices generally drives a thread delivery element, for example in the form of a thread storage roll, or a thread winding element. It is in turn driven by a drive source which, in the case of a circular knitting machine in practice, often consists of an endless toothed belt with which the shafts of the individual thread delivery devices are each coupled via a toothed belt pulley and which in turn is rotated synchronously with the needle cylinder.
  • embodiments of the thread brake are also advantageous in which the vibration generating device is designed to act directly on the brake elements, for example by acting on the circumference thereof.
  • the gear mechanism mentioned can be a cam mechanism with a cam element seated on the shaft, against the cam surface of which the reciprocating member is held in contact.
  • “Cam gears” are understood to mean all form-fitting gears that generate a vibratory movement, for example also eccentric gears etc.
  • the basic structure of the thread delivery device shown in FIGS. 1, 2 is known. It has a holder 1 which, for example, by means of a clamping screw 2 on a support ring indicated at 3. a circular knitting machine, can be fastened and in which a continuous shaft 4 is rotatably mounted, which has a vertical orientation when the holder 1 is mounted in the operating position.
  • the shaft 4 is connected at one end to a thread drum 5 arranged underneath the holder 1 and in the form of a rod cage; it carries at its upper end a toothed belt pulley 7 which can be coupled in a rotationally fixed manner via a coupling 6 and via which the thread drum 5 can be rotated from an endless toothed belt (not shown further).
  • a plate thread brake 8 is arranged, which has two identical, essentially disk-shaped brake plates 9, between which the thread indicated at 10 passes.
  • the thread path extends from a thread spool, not shown, through a thread eyelet 11 attached to the holder 1, a knot catcher 12, the thread brake 8 to a thread inlet eyelet 14 attached to the holder 1 via an angle piece 13, from which the thread 10 onto the Thread drum 5 runs on which it forms a storage roll 15 and from which it runs to the thread consumption point via a thread outlet eyelet 16 also provided on the holder 1.
  • Thread breakers connected, each about a horizontal pivot axis Thread sensor arms 17, 18 pivotably mounted on the holder 1 monitor the thread running on the inlet and outlet sides of the thread drum 5.
  • the thread brake 8 as can also be seen in particular from FIG. 3, has a guide pin 19 which forms a guide element and is fastened at one end to holding means in the form of a winding piece 20 by means of a nut 21.
  • the nut 21 is screwed onto a threaded part 22 of the guide pin 19, on which, on the side facing away from the angle piece 20, an intermediate bushing 23 made of ceramic is pushed, which at one end rests against an annular shoulder on the guide pin 19 and at the other end via an annular washer 24 of larger diameter supports the elbow 20.
  • the two brake actuators 9 are easily rotatable and axially displaceable with a certain radial play by means of plastic bushings 25.
  • the thread brake 8 described in this way can be set in operation with its brake actuators 9, the guide pin 19 and the angle piece 20 forming the holding means, the amplitudes of which are directed mainly at right angles to the common bearing axis 29 of the two brake actuators 9 formed by the guide pin 19.
  • a vibration generating device is present, which is shown in FIG. 3 as a whole is designated by 30 and with which the thread brake 8 is directly connected.
  • the vibration generating device 30 has a reciprocating link in the form of a push rod 31 which is axially displaceable but non-rotatably mounted in a bearing bush 32, which in turn is inserted into the associated end wall of the holder designed as a housing.
  • the bearing bush 32 simultaneously holds the angle piece 13 carrying the inlet eyelet 14; it is provided with a radial pin 33 which engages in a corresponding longitudinal groove 34 in the push rod 31 and prevents it from rotating.
  • the thread brake 8 is screwed onto the push rod 31 at one end by means of a nut 35 via the angle piece 20; it carries two lock nuts 36 which are screwed on in the area between the angle piece 20 and the bearing bush 32 and which form an adjustable stop for limiting the reciprocating stroke movement of the push rod 31.
  • the push rod 31 is driven from the shaft 4 via a cam gear 37, which has a cam element in the form of a three-surface cam plate 38, which is non-rotatably mounted on the shaft 4 and against whose cam surface the push rod 31 is supported with the interposition of a wear cap 39 arranged on the end face is, a return spring 40 arranged between the wear cap 39 and the bearing bush 32 biasing the push rod 31 in the direction of the cam plate 38, such that the push rod 31 over the Wear cap 39 is held in permanent engagement with the cam surface of the cam 38.
  • a cam gear 37 which has a cam element in the form of a three-surface cam plate 38, which is non-rotatably mounted on the shaft 4 and against whose cam surface the push rod 31 is supported with the interposition of a wear cap 39 arranged on the end face is, a return spring 40 arranged between the wear cap 39 and the bearing bush 32 biasing the push rod 31 in the direction of the cam plate 38, such that the push rod 31 over the Wear cap 39 is held in permanent engagement with the cam
  • the shaft 4 rotates at a speed of approximately 400 to approximately 4000 rpm and, depending on the number of cam surfaces on the cam plate 38, generates a reciprocating oscillating movement of the push rod 31, which takes into account the Natural frequency of the entire moving arrangement is generally in the range from 45 to 150 Hz.
  • This oscillatory movement is transmitted via the angle piece 20 to the thread brake 8, with the result that the brake actuators 9, which are mounted on the intermediate bush 23 for a limited amount of free movement, carry out a constant vibration movement, the amplitudes of which are mainly directed transversely to the bearing axis 29. Since, as can be seen from FIG. 1, the thread 10 passes eccentrically between the brake actuators 9, these are set in rotation while the thread is running, which, together with the described vibration transmitted via the push rod 31, results in an effective self-cleaning of the thread brake 8.
  • the thread brake 8 is fastened directly to the push rod 31 via the angle piece 20, without a further connection to the holder 1 of the thread delivery device being present.
  • the guide pin 19 is mounted on the housing 1 by means of a bearing bracket 41 which is rigidly connected to the latter and which contains, for example, a vulcanized-in, annular, rubber-elastic bearing part 42, with which the guide pin 19 is screwed in such a way that it is elastically movably mounted in its bearing point.
  • a pressure bush 43 is slidably placed, against the outer circumferential surface of which the rounded, correspondingly elongated push rod 31 bears.
  • the reciprocating oscillation movement of the push rod 31 is thus transmitted directly to the guide pin 19 and the brake plate 9, while the rigid bearing bracket 41 itself remains vibration-free.
  • the guide pin 19 and the brake actuators 9 execute an oscillation movement which is mainly directed transversely to the bearing axis 29, but which also contains longitudinal components due to the tilting movement resulting with the pivot point in the bearing point.
  • the described embodiments both according to FIG. 3 and according to FIG. 4 could also be modified in such a way that the guide pin 19 itself is made of an elastic material, for example a suitable plastic material, and can therefore perform a bending vibration.
  • the rubber-elastic bearing element 42 in FIG. 4 could possibly be dispensed with.
  • FIG. 5 differs from that according to FIG. 4 in that the vibration generating device 30 is designed to act directly on the brake actuator 9.
  • the push rod 31 is arranged with its axis lying in the center plane between the two brake actuators 9.
  • it carries an approximately frustoconical drive member 430 which has a flat base surface 44 approximately parallel to the bearing axis 29, the longitudinal extent of which is dimensioned in the direction of the bearing axis 29 such that it overlaps the two brake actuators 9 on both sides in the manner shown in FIG.
  • the brake actuators 9 are mounted on the intermediate bush 23 with radial play, their radial distance from the base surface 44 of the drive element 43 being dimensioned such that the drive element 43 periodically engages the circumference of the brake actuator 9 during the reciprocating movement of the push rod 31 and thus set them into oscillatory movements, the amplitudes of which are directed essentially at right angles to the bearing axis 29.
  • the guide pin 19 is rigidly screwed to the bracket 41 in this case. Basically, however, embodiments are also conceivable in which the guide pin 19 is mounted via a rubber-elastic bearing part 42 according to FIG. 3. In addition, the guide pin 29 can optionally also consist of an elastic material.
  • the compression spring 26 can also be replaced by other loading means, for example an electromagnet or means under the influence of gravity. Examples of this will be explained below with reference to the embodiments according to FIGS. 6 to 11.
  • the two brake actuators 9 are placed on an elongated guide element in the form of the guide pin 19 containing the common bearing axis 29, in the embodiments according to FIGS. 6 to 14 there is a guide element 190 used, which makes it possible to dispense with a continuous guide pin 19.
  • the guide bolts 19 are omitted in the embodiments described with reference to FIGS. 6 to 14, as mentioned.
  • the central area of the brake actuator 9 is rather exposed, so that no fluff can accumulate there.
  • the guide element 190 for the two brake actuators 9 arranged concentrically to one another with a common bearing axis 29 is in turn placed directly on the push rod 31 of the vibration generator 30 (see FIG. 3).
  • the guide element 190 is partially formed around the two brake actuators 9 in the circumferential direction over an angular range of approximately 300 °. It consists of two half-shell bearing elements 50, which are essentially in the form of part-circular Brackets are formed which are arranged at an axial distance from one another (FIG. 7) and parallel to one another.
  • the two bearing elements 50 are formed at one end on a mounting block 51 which is screwed onto the push rod 31.
  • Each of the bow-shaped bearing elements 50 carries three integrally formed, radially inwardly projecting bearing projections 52, 53, 54, which are distributed along the circumference at approximately equal angular intervals and of which the bearing projection 53 lies approximately in the extension of the axial direction of the push rod 31.
  • the bearing projections 52 to 54 form, as can be seen from FIG. 7, discrete, locally limited, lateral support points for the two brake actuators 9, so that these are held captively in the guide element 190.
  • Radially, the two brake actuators 9 are supported on their circumference at two bearing points 55, 56 which are arranged in the region of the bearing projections 53, 54.
  • the guide element 190 is usually made of plastic material; it has radial clearances 61 between the bearing projections 52 to 54 in the manner shown in FIG. 6, which extend over most of the circumference of the brake disks 9 and are thus also conducive to easy fluff removal.
  • a transverse pin 62 which is arranged laterally next to and parallel to the common bearing axis 29 and runs on an integrally formed holding arm 63 of the thread guide element 190, runs through the opening 59 of the brake actuator 9.
  • the cross pin 62 is made of ceramic material and has the task of preventing the thread 10 from accidentally jumping out of the area between the brake actuators 9.
  • a likewise axially parallel thread deflecting pin 64 is provided in the area of the lower bearing projection 54, which deflects the thread 10 when leaving the thread brake 8 in the manner shown in FIG. 6 towards the thread inlet eyelet 14.
  • the thread deflecting pin 64 is also made of ceramic material.
  • the thread path is selected by appropriate arrangement of the thread eyelet 11 of the cross pin 62 and the thread deflecting pin 64 such that the between the Brake actuator 9 incoming thread 10 (in Fig. 6 left) runs in at a distance next to the common bearing axis 29 and exits between them in the area of the lower bearing point 56.
  • a torque is frictionally applied to the two brake actuators 9 by the running thread 10, which acts in the same direction of rotation, indicated by arrow 59, as the torque that frictionally engages the brake discs 9 from the vibration generator 30 via the push rod 31 is transmitted.
  • the compression spring 26 is also omitted.
  • the two brake actuators 9 are pressed axially against one another by magnetic forces.
  • ring-shaped, counter-pole permanent magnets 65 are glued onto the brake disks 9 made of non-magnetic material, which axially press the two brake disks 9 (FIG. 7), which are approximately shell-shaped in cross section, against one another with a predetermined force.
  • the embodiment according to FIG. 8 corresponds to the embodiment of the thread brake 8 described above with reference to FIGS. 6, 7 in all parts, with the exception that the transverse pin 62 in the through openings 59 on the other, the right side of the common bearing axis 29 is misplaced.
  • the thread 10 carried out off-center between the brake actuators 9 thus exerts a torque on the brake actuators 9 in the run, the direction of which is indicated by the arrow 58a and opposite to the direction of this torque in the embodiment according to FIG. 6.
  • the transverse pin 62 can also be dispensed with.
  • Corresponding embodiments of the thread brake 8 are illustrated in FIGS. 9 to 14:
  • FIG. 9 essentially corresponds to the embodiments according to FIGS. 6,8; Identical parts are given the same reference symbols and are not explained again.
  • the thread 10 running in from the circumference between the brake actuators 9 is led out through the opening 59 on one side out of the space between the two brake actuators 9; it then goes on the outside of the guide element 190 via the thread deflecting pin 64 to the thread inlet eyelet 14.
  • a brake actuator 9a is fixedly arranged on the mounting block 51 of the guide element 190 assigned to it.
  • the guide element 190 is provided with a projecting, integrally formed projection 66, to which the annular brake disc 9a is attached.
  • This brake disc 9a is provided at a point lying outside the thread travel path shown in FIGS. 10, 11 with a V-shaped thread insertion slot 67 leading from the circumference into the opening 59.
  • the other brake actuator 9 is, like in the embodiments according to FIGS. 6 to 9, freely rotatable on its circumference.
  • the two bearing points are again designated 55, 56.
  • the lateral support takes place via the projections 52, 53, 54.
  • the threading process takes place in such a way that the thread 10 is pulled beyond the knot catcher 12 and a thread limiting hook 120 assigned to it into the area below the thread brake 8 and then without releasing it radially from the side (in FIG. 7, right) between the two bearing elements 50 between the two brake discs 9, 9a.
  • the thread 10 is about Thread insertion opening 67 is led laterally out of the central opening 59 of the fixed brake disc 9a and then threaded through the thread eyelet 14.
  • the thread 10 thus leaves the opening 59 in the manner shown in FIG. 10, wherein it runs over its correspondingly rounded edge.
  • the latter preferably consists of ceramic or a correspondingly wear-resistant coated material.
  • a fixed brake actuator 9a is also provided, similar to the embodiment according to FIGS. 10, 11 is formed with the thread insertion slot 67, which is arranged outside the thread path (see Fig. 12, 13).
  • the fixed brake actuator 9a is ring-shaped with a continuous central opening 59.
  • the threading process for the thread 10 takes place in the manner described with reference to FIGS. 10, 11.
  • the second rotatably mounted brake actuator 9 is not provided with a central opening 59, but rather is closed in the center (see FIG. 14).
  • the brake actuator 9 carries an integrally formed, cylindrical bearing extension 68 containing the common bearing axis 29, by means of which it is freely rotatably supported on an arm-like support 69 with play.
  • the carrier 69 is in turn supported at the other end by a bearing fork 70 against the mounting block 51 of the guide element 190. It is under the action of a compression spring 71 which is placed on a threaded bolt 72 inserted into the mounting block 51 and the pretension of which can be appropriately adjusted in a known manner by means of a control nut 73.
  • the control nut 72 By adjusting the control nut 72 accordingly, the braking force exerted by the brake actuators 9, 9a on the continuous thread 10 can be adjusted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Braking Arrangements (AREA)
  • Knitting Machines (AREA)
  • Transmission Devices (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Clamps And Clips (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
EP92102286A 1991-02-15 1992-02-12 Fadenbremse Expired - Lifetime EP0499218B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4104663A DE4104663C1 (zh) 1991-02-15 1991-02-15
DE4104663 1991-02-15

Publications (2)

Publication Number Publication Date
EP0499218A1 EP0499218A1 (de) 1992-08-19
EP0499218B1 true EP0499218B1 (de) 1994-11-30

Family

ID=6425112

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92102286A Expired - Lifetime EP0499218B1 (de) 1991-02-15 1992-02-12 Fadenbremse

Country Status (22)

Country Link
US (1) US5343983A (zh)
EP (1) EP0499218B1 (zh)
JP (1) JPH0790984B2 (zh)
KR (1) KR970009384B1 (zh)
CN (1) CN1026884C (zh)
BR (1) BR9204772A (zh)
CA (1) CA2076752C (zh)
CZ (1) CZ280298B6 (zh)
DE (2) DE4104663C1 (zh)
EG (1) EG19529A (zh)
ES (1) ES2065081T3 (zh)
HK (1) HK48895A (zh)
MX (1) MX9200657A (zh)
MY (1) MY108137A (zh)
PH (1) PH31514A (zh)
RO (1) RO109628B1 (zh)
RU (1) RU2070863C1 (zh)
SG (1) SG30559G (zh)
SK (1) SK281015B6 (zh)
TR (1) TR25972A (zh)
UA (1) UA25896C2 (zh)
WO (1) WO1992014670A1 (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6089491A (en) * 1997-08-01 2000-07-18 Sipra Patententwicklungs - U. Beteiligungsgesellschaft Mbh Yarn delivery device and drive wheel suitable for this purpose
DE102011053824B3 (de) * 2011-09-21 2012-10-04 Memminger-Iro Gmbh Fadenliefergerät zur Zufuhr eines Fadens zu einer Textilmaschine
DE102012103534A1 (de) 2011-09-21 2013-03-21 Memminger-Iro Gmbh Vorrichtung zur Zufuhr eines Fadens zu einer Textilmaschine

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DE4301507C2 (de) * 1993-01-21 1995-01-26 Memminger Iro Gmbh Fadenbremse
DE4409450C2 (de) * 1994-03-18 1996-12-05 Memminger Iro Gmbh Fadenbremseinrichtung
SE504096C2 (sv) * 1995-03-02 1996-11-11 F & N Mekanik Ab Garngripare för garnmatningssystem i vävstolar
DE19531579C1 (de) * 1995-08-28 1997-01-23 Barth Tex Instr & Software Gmb Fadenbremse
DE19720795A1 (de) * 1997-05-16 1998-11-19 Sipra Patent Beteiligung Fadenbremse und damit ausgerüstete Textilmaschine und Fadenliefervorrichtung
DE19919122A1 (de) * 1999-04-27 2000-11-02 Iro Patent Ag Baar Aktuator und Fadenbremse mit einem Aktuator
DE10006599A1 (de) * 2000-02-15 2001-08-23 Memminger Iro Gmbh Friktionsfournisseur mit Vibrationsanregung
US6439488B1 (en) 2000-11-27 2002-08-27 Bobby Hunter Tensioning device for circular knitting machine
DE10345369A1 (de) 2003-09-26 2005-05-12 Sipra Patent Beteiligung Fadenbremse und damit ausgerüstete Textilmaschine und Fadenliefervorrichtung
CN102707097B (zh) * 2011-03-28 2015-08-19 国家电网公司 带有磁吸式连接装置的试验线夹
CH706263A1 (de) * 2012-03-21 2013-09-30 Uster Technologies Ag Tellerfadenbremse mit Reinigungseinrichtung.
CH706264A1 (de) * 2012-03-21 2013-09-30 Uster Technologies Ag Tellerfadenbremse.
CN102677383A (zh) * 2012-06-08 2012-09-19 慈溪太阳洲纺织科技有限公司 一种针织输纱机
CN106149187B (zh) * 2016-08-03 2019-06-21 广州美名纺织科技有限公司 一种用于针织大圆机的滚轮式夹纱器
CN106637644B (zh) * 2017-03-16 2022-09-16 泉州精准机械有限公司 一种防缠纱张力调节的送纱器
CN108987098B (zh) * 2018-08-31 2023-12-12 公元股份有限公司 一种卧式绕线机
CN109487426B (zh) * 2018-11-02 2024-04-12 南京曼星忆知科技有限公司 一种全电脑织袜机
CN110054023A (zh) * 2019-05-24 2019-07-26 晋江市万晋自动化设备有限公司 一种独立恒张力弹性线材控制装置
CN111286846B (zh) * 2020-04-15 2021-04-16 扬州市郭氏精密机械制造有限公司 一种织布用纱夹
EP4101965A1 (de) * 2021-06-11 2022-12-14 KARL MAYER STOLL R&D GmbH Fadenbremse

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DE2758334C2 (de) * 1977-12-27 1986-04-17 W. Schlafhorst & Co, 4050 Mönchengladbach Fadenbremse
CH636578A5 (de) * 1977-12-27 1983-06-15 Schlafhorst & Co W Fadenbremse.
US4209881A (en) * 1978-03-21 1980-07-01 Phillips Petroleum Company Knitting intermittently drawn yarns
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DE3029509A1 (de) * 1980-08-04 1982-03-25 Gütermann & Co, 7809 Gutach Fadenbremse
JPH0252864A (ja) * 1988-08-17 1990-02-22 Tsudakoma Corp 繊維機械における糸張力調整装置
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6089491A (en) * 1997-08-01 2000-07-18 Sipra Patententwicklungs - U. Beteiligungsgesellschaft Mbh Yarn delivery device and drive wheel suitable for this purpose
DE102011053824B3 (de) * 2011-09-21 2012-10-04 Memminger-Iro Gmbh Fadenliefergerät zur Zufuhr eines Fadens zu einer Textilmaschine
DE102012103534A1 (de) 2011-09-21 2013-03-21 Memminger-Iro Gmbh Vorrichtung zur Zufuhr eines Fadens zu einer Textilmaschine
WO2013041349A1 (de) 2011-09-21 2013-03-28 Memminger-Iro Gmbh Fadenliefergerät zur zufuhr eines fadens zu einer textilmaschine

Also Published As

Publication number Publication date
CZ280298B6 (cs) 1995-12-13
TR25972A (tr) 1993-11-01
EP0499218A1 (de) 1992-08-19
HK48895A (en) 1995-04-07
MX9200657A (es) 1992-08-01
BR9204772A (pt) 1993-07-06
JPH06502613A (ja) 1994-03-24
US5343983A (en) 1994-09-06
JPH0790984B2 (ja) 1995-10-04
CN1026884C (zh) 1994-12-07
CA2076752A1 (en) 1992-08-16
CS44892A3 (en) 1992-10-14
RU2070863C1 (ru) 1996-12-27
DE59200816D1 (de) 1995-01-12
KR970009384B1 (ko) 1997-06-12
SK281015B6 (sk) 2000-10-09
CN1064845A (zh) 1992-09-30
RO109628B1 (ro) 1995-04-28
UA25896C2 (uk) 1999-02-26
DE4104663C1 (zh) 1992-08-13
ES2065081T3 (es) 1995-02-01
MY108137A (en) 1996-08-15
SG30559G (en) 1995-09-18
EG19529A (en) 1995-07-27
CA2076752C (en) 1998-04-21
PH31514A (en) 1998-11-03
WO1992014670A1 (de) 1992-09-03

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