EP0211242A2 - Spring-coiling machine - Google Patents

Spring-coiling machine Download PDF

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Publication number
EP0211242A2
EP0211242A2 EP86109100A EP86109100A EP0211242A2 EP 0211242 A2 EP0211242 A2 EP 0211242A2 EP 86109100 A EP86109100 A EP 86109100A EP 86109100 A EP86109100 A EP 86109100A EP 0211242 A2 EP0211242 A2 EP 0211242A2
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EP
European Patent Office
Prior art keywords
wire
transport rollers
knife
crosses
drive
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Granted
Application number
EP86109100A
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German (de)
French (fr)
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EP0211242A3 (en
EP0211242B1 (en
Inventor
Max Frei
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SCHENKER MASCHINEN AG
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SCHENKER MASCHINEN AG
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Publication of EP0211242A3 publication Critical patent/EP0211242A3/en
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Publication of EP0211242B1 publication Critical patent/EP0211242B1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F3/00—Coiling wire into particular forms
    • B21F3/02—Coiling wire into particular forms helically

Definitions

  • the present invention relates to a spring winding machine with the wire feeding transport rollers which can be driven in the machine cycle, wherein the coiled springs are separated from the wire at the end of the winding process by a knife movable on a circular path which crosses the feed path of the wire.
  • a spring coiling machine is known on the market in which the wire is fed at a constant speed and the finished spring is cut off with a rotating knife in a flying cut without the wire feed being braked for this purpose.
  • the wire length of the spring is determined by the point in time at which a single-speed clutch is engaged, which sets the knife in the circular cutting movement and stops after one turn.
  • this single-speed clutch is subject to high wear and the limitation of the switching frequency also limits the production speed of the spring coiling machine. Since the transport rollers run at a constant rotational speed, there is a further disadvantage that the pitch tool has to perform a relatively fast movement in the case of compression springs with adjacent end windings. This also limits production output.
  • a device is known from DE-PS 1 267 653 in which the wire is advanced step by step.
  • the step drive required for this has a linearly movable back and forth drive element which drives the transport rollers via two oppositely acting one-way clutches.
  • the transport rollers are not driven by the same number of gears when the drive element is advanced as during the return.
  • a reversing gear is arranged in one of the two gear trains so that the pairs of feed rollers always have the same direction of rotation, regardless of the direction of movement of the drive element.
  • This known device therefore has a total play in the gear train to the transport rollers during the advance of the drive element, which is different from that during the return, which results in different wire feed lengths.
  • the object of the present invention is to improve a spring winding machine of the type mentioned at the outset in such a way that the machine output can be increased significantly.
  • this object is achieved in that the transport rollers are driven with a stepping drive for the gradual advancement of the wire, and that the knife crosses the advancement path at the end of a advancement step when the advancement speed is at least approximately zero.
  • the stepper drive has a linearly displaceable drive element which drives the transport rollers via two oppositely acting one-way clutches.
  • the drive element drives the one-way clutches on the input side isochronously but with the opposite direction of rotation and the single-way clutches drive the transport rollers on the output side via the same number of gears.
  • the invention has the advantage that the wire feed speed runs according to a rectified sinus curve and is therefore comparatively slow at the beginning and at the end of a half period of the machine cycle, and the rotational speed of the knife can thereby be relatively slow. This means that the knife can run in cycles, without switching by means of a single-speed clutch.
  • the pitch tool With compression springs with adjacent end windings, the pitch tool carries out the movements at the beginning and end of the wire feed. Since the speed of movement of the pitch tool is proportional to the wire feed speed, the speed of the pitch tool becomes relatively low with such springs, so that the production speed can also be relatively high for this reason.
  • the reference numerals 1 and 2 denote the transport rollers for feeding the wire 3.
  • the winding point 4 is further assigned an inclining tool 5 and a knife 6.
  • the transport rollers 1 and 2 are driven by a clock shaft 7 which is driven by a motor, not shown.
  • a pinion 15 or 14 meshes with each of the toothings 12, 13.
  • Each of these two pinions is connected in a rotationally fixed manner to the input side of a one-way clutch 17 or 16, which drives the shafts 19 and 18 on the output side, on each of which a gear wheel is fixed 21 or 20 sits.
  • the two gears 20 and 21 each mesh with a freely rotatable gear 22, to which a gear 23 is rotatably connected, which in turn meshes with a freely rotatable gear 24.
  • the transmission pinion 27 meshes with a pinion 28 which, together with the transport roller 1, is arranged in a rotationally fixed manner on a shaft 28 '.
  • the clock shaft 7 drives a shaft 31 via the gears 29 and 30, on which a cam 32 is seated in a rotationally fixed manner.
  • This actuates, twice per machine cycle, the incline tool 5 via a swivel lever arrangement 33.
  • two sprockets 36 and 37 are driven by the shaft 31 via a sprocket 34 and a chain 35, each of which is rotationally fixed on a shaft 38 and 39 and at the other end wear synchronously rotating crank disks 40 and 41, on the crank pin of which a knife holder 42 is mounted, to which the knife 6 is fastened.
  • the knife edge thus moves on a circular path, which it runs through twice per machine cycle.
  • the movement of the knife 6 is matched to the movement of the transport rollers 1 and 2 in such a way that it always assumes a cutting position when the toothed rack 11 assumes one of its two end positions or when the rotational speed of the transport rollers 1 and 2 is at least approximately zero.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Wire Processing (AREA)

Abstract

Der Draht (3) wird von zwei Transportrollen (1, 2) zugeführt, die von einer Taktwelle (7) antreibbar sind. Die gewundenen Federn werden jeweils am Ende des Windevorganges durch ein auf einer Kreisbahn bewegbares Messer (6) abgetrennt, welches den Vorschubweg des Drahtes kreuzt. Zur Leistungssteigerung wird vorgeschlagen, dass die Transportrollen (1, 2) mit einem Schrittantrieb für den schrittweisen Vorschub des Drahtes angetrieben sind, und dass das Messer jeweils am Ende eines Vorschubschrittes den Vorschubweg kreuzt, wenn die Vorschubgeschwindigkeit mindestens näherungsweise Null ist.The wire (3) is fed by two transport rollers (1, 2) which can be driven by a clock shaft (7). The coiled springs are separated at the end of the winding process by a knife (6) which can be moved on a circular path and which crosses the feed path of the wire. To increase performance, it is proposed that the transport rollers (1, 2) are driven with a stepping drive for the gradual advancement of the wire, and that the knife crosses the advancement path at the end of each advancement step if the advancement speed is at least approximately zero.

Description

Die vorliegende Erfindung bezieht sich auf eine Federwindemaschine mit den Draht zuführenden Transportrollen, die im Maschinentakt antreibbar sind, wobei jeweils die gewundenen Federn am Ende des Winde­vorganges durch ein auf einer Kreisbahn bewegbares Messer, welches den Vorschubweg des Drahtes kreuzt, vom Draht abgetrennt werden.The present invention relates to a spring winding machine with the wire feeding transport rollers which can be driven in the machine cycle, wherein the coiled springs are separated from the wire at the end of the winding process by a knife movable on a circular path which crosses the feed path of the wire.

Auf dem Markt ist eine Federwindemaschine bekannt, bei der der Draht mit konstanter Geschwindigkeit vorgeschoben wird und das Abschneiden der fertigen Feder mit einem rotierenden Messer in fliegendem Schnitt erfolgt, ohne dass hierfür der Drahtvorschub gebremst würde. Die Drahtlänge der Feder wird bestimmt durch den Zeitpunkt des Einkuppelns einer Eintourenkupplung, die das Messer in die kreisförmige Schnittbewegung versetzt und nach einer Umdrehung wieder anhält. Bei hohen Produktionsleistungen ist diese Eintourenkupplung einem hohen Verschleiss unterworfen und durch ihre Begrenzung der Schaltfrequenz wird auch die Produktionsgeschwindigkeit der Federwinde­maschine eingeschränkt. Da die Transportrollen mit konstanter Drehgeschwindigkeit laufen, ergibt sich als weiterer Nachteil, dass das Steigungswerkzeug bei Druck­federn mit anliegenden Endwindungen eine relativ schnelle Bewegung ausführen muss. Auch hierdurch wird die Produktions­leistung begrenzt.A spring coiling machine is known on the market in which the wire is fed at a constant speed and the finished spring is cut off with a rotating knife in a flying cut without the wire feed being braked for this purpose. The wire length of the spring is determined by the point in time at which a single-speed clutch is engaged, which sets the knife in the circular cutting movement and stops after one turn. At high production rates, this single-speed clutch is subject to high wear and the limitation of the switching frequency also limits the production speed of the spring coiling machine. Since the transport rollers run at a constant rotational speed, there is a further disadvantage that the pitch tool has to perform a relatively fast movement in the case of compression springs with adjacent end windings. This also limits production output.

Weiter ist aus der DE-PS 1 267 653 eine Vorrichtung bekannt, bei der der Draht schrittweise vorgeschoben wird. Der hierzu erforderliche Schrittantrieb weist ein geradlinig hin- und her verschiebbares Antriebselement auf, das über zwei ent­gegengesetzt wirkende Einwegkupplungen die Transportrollen antreibt.Furthermore, a device is known from DE-PS 1 267 653 in which the wire is advanced step by step. The step drive required for this has a linearly movable back and forth drive element which drives the transport rollers via two oppositely acting one-way clutches.

Bei dieser Federwindemaschine werden beim Vorlauf des Antriebselementes die Transportrollen nicht über die gleiche Anzahl Zahnräder angetrieben wie während des Rücklaufes. In einem der beiden Getriebezüge ist ein Umkehrzahnrad angeordnet, damit die Tansportrollenpaare unabhängig von der Bewegungsrichtung des Antriebselementes stets den gleichen Drehsinn haben. Da indessen zwischen zwei Zahn­rädern immer ein gewisses Betriebsspiel besteht, das sich innerhalb eines Getriebezuges mit dem Spiel der übrigen Zahnräder addiert, ergeben sich für Getriebezüge unter­schliedlicher Zahnradzahlen auch unterschiedliche Gesamt­spiele. Diese bekannte Vorrichtung hat daher im Getriebezug zu den Transportrollen beim Vorlauf des Antriebselementes ein Gesamtspiel, das verschieden von jenem beim Rücklauf ist, woraus unterschiedliche Drahteinzugslängen resultieren.In this spring coiling machine, the transport rollers are not driven by the same number of gears when the drive element is advanced as during the return. A reversing gear is arranged in one of the two gear trains so that the pairs of feed rollers always have the same direction of rotation, regardless of the direction of movement of the drive element. However, since there is always a certain operating clearance between two gearwheels, which is added to the clearance of the other gearwheels within a gear train, there are also different total backlashes for gear trains with different numbers of gears. This known device therefore has a total play in the gear train to the transport rollers during the advance of the drive element, which is different from that during the return, which results in different wire feed lengths.

Ein weiterer Nachteil dieser bekannten Vorrichtung besteht darin, dass das Abschneiden des Drahtes am Ende des Winde­vorganges im Stanzschnitt durch ein Messer erfolgt. Da dieser Schnitt kurzfristig in den Totpunkten des Antriebs­elementes zu erfolgen hat, sind der Arbeitsgeschwindigkeit dieser Vorrichtung Grenzen gesetzt.Another disadvantage of this known device is that the wire is cut off at the end of the winding process in a punch cut by a knife. There this cut must be made briefly in the dead center of the drive element, the working speed of this device is limited.

Die vorliegende Erfindung stellt sich die Aufgabe, eine Federwindemaschine der eingangs erwähnten Art derart zu verbessern, dass die Maschinenleistung wesentlich erhöht werden kann.The object of the present invention is to improve a spring winding machine of the type mentioned at the outset in such a way that the machine output can be increased significantly.

Erfindungsgemäss wird diese Aufgabe dadurch gelöst, dass die Transportrollen mit einem Schrittantrieb für den schritt­weisen Vorschub des Drahtes angetrieben sind, und dass das Messer jeweils am Ende eines Vorschubschrittes den Vorschub­weg kreuzt, wenn die Vorschubgeschwindigkeit mindestens näherungsweise Null ist.According to the invention, this object is achieved in that the transport rollers are driven with a stepping drive for the gradual advancement of the wire, and that the knife crosses the advancement path at the end of a advancement step when the advancement speed is at least approximately zero.

Nach einer bevorzugten Ausführungsform ist vorgesehen, dass der Schrittantrieb ein geradlinig hin- und her verschieb­bares Antriebselement aufweist, das über zwei entgegen­gesetzt wirkende Einwegkupplungen die Transportwalzen an­treibt. Dabei treibt das Antriebselement die Einwegkupplungen eingangsseitig taktsynchron aber mit entgegengesetztem Drehsinn an und die Einzwegkupplungen treiben abtriebseitig je über die gleiche Anzahl Zahnräder die Transportrollen an. Daraus ergibt sich der Vorteil, dass während jeder Halbperiode eines Maschinentaktes eine Feder hergestellt werden kann, und dass sich das Getriebespiel minimal auf die Drahtlänge der Federn auswirkt.According to a preferred embodiment, it is provided that the stepper drive has a linearly displaceable drive element which drives the transport rollers via two oppositely acting one-way clutches. The drive element drives the one-way clutches on the input side isochronously but with the opposite direction of rotation and the single-way clutches drive the transport rollers on the output side via the same number of gears. This has the advantage that a spring can be produced during each half cycle of a machine cycle and that the gear play has a minimal effect on the wire length of the springs.

Die Erfindung hat den Vorteil, dass die Drahtvorschub­geschwindigkeit entsprechend einer gleichgerichteten Sinuskurve verläuft und dadurch zu Beginn und am Ende einer Halbperiode des Maschinentaktes vergleichsweise langsam ist und dadurch die Rotationsgeschwindigkeit des Messers relativ langsam sein kann. Dadurch kann das Messer takt­mässig umlaufen, ohne Schaltung mittels Eintouren-Kupplung.The invention has the advantage that the wire feed speed runs according to a rectified sinus curve and is therefore comparatively slow at the beginning and at the end of a half period of the machine cycle, and the rotational speed of the knife can thereby be relatively slow. This means that the knife can run in cycles, without switching by means of a single-speed clutch.

Bei Druckfedern mit anliegenden Endwindungen führt das Steigungswerkzeug die Bewegungen am Anfang und am Ende des Drahtvorschubes aus. Da die Bewegungsgeschwindigkeit des Steigungswerkzeuges proportional zur Drahtvorschubgeschwindig­keit ist, wird die Geschwindigkeit des Steigungswerkzeuges bei solchen Federn relativ klein, so dass auch aus diesem Grund die Produktionsgeschwindigkeit relativ hoch sein kann.With compression springs with adjacent end windings, the pitch tool carries out the movements at the beginning and end of the wire feed. Since the speed of movement of the pitch tool is proportional to the wire feed speed, the speed of the pitch tool becomes relatively low with such springs, so that the production speed can also be relatively high for this reason.

Anhand der beiliegenden schematischen, perspektivischen Darstellung wird die Erfindung beispielsweise erläutert.The invention is explained, for example, on the basis of the attached schematic, perspective representation.

In der Zeichnung bezeichnen die Hinweisziffern 1 und 2 die Transportrollen für den Vorschub des Drahtes 3. Der Winde­stelle 4 sind weiter ein Steigungswerkzeug 5 und ein Messer 6 zugeordnet. Der Antrieb der Transportrollen 1 und 2 erfolgt von einer Taktwelle 7, die durch einen nicht darge­stellten Motor angetrieben ist. Drehfest auf der Taktwelle 7 sitzt eine Kurbelscheibe 8 mit einem Kurbelzapfen 9, der in eine geradlinige Führung 10, senkrecht am Ende einer gerad­linig verschiebbar gelagerten Zahnstange 11 greift, die an ihrer Ober- und Unterseite je mit einer Zahnung 12 bzw. 13 versehen ist.In the drawing, the reference numerals 1 and 2 denote the transport rollers for feeding the wire 3. The winding point 4 is further assigned an inclining tool 5 and a knife 6. The transport rollers 1 and 2 are driven by a clock shaft 7 which is driven by a motor, not shown. A crank disk 8 with a crank pin 9, which engages in a rectilinear guide 10, perpendicularly at the end of a rectilinearly displaceable rack 11, sits on the clock shaft 7 in a rotationally fixed manner their top and bottom are each provided with teeth 12 and 13, respectively.

Mit jeder der Zahnungen 12, 13 kämmt je ein Ritzel 15 bzw. 14. Jedes dieser beiden Ritzel ist je drehfest mit der Eingangsseite einer Freilaufkupplung 17 bzw. 16 verbunden, welche abtriebseitig die Wellen 19 bzw. 18 antreiben, auf denen fest je ein Zahnrad 21 bzw. 20 sitzt. Die beiden Zahnräder 20 und 21 kämmen je mit einem frei drehbar gelagerten Zahnrad 22, mit dem drehfest ein Zahnrad 23 verbunden ist, das seinerseits mit einem frei drehbar gelagerten Zahnrad 24 kämmt. Dieses wiederum kämmt mit einem Ritzel 25, das zusammen mit der Transportrolle 2 und einem Uebertragungsritzel 27 drehfest auf der Welle 26 sitzt. Das Uebertragungsritzel 27 kämmt mit einem Ritzel 28, das zusammen mit der Transportrolle 1 drehfest auf einer Welle 28' angeordnet ist.A pinion 15 or 14 meshes with each of the toothings 12, 13. Each of these two pinions is connected in a rotationally fixed manner to the input side of a one-way clutch 17 or 16, which drives the shafts 19 and 18 on the output side, on each of which a gear wheel is fixed 21 or 20 sits. The two gears 20 and 21 each mesh with a freely rotatable gear 22, to which a gear 23 is rotatably connected, which in turn meshes with a freely rotatable gear 24. This in turn meshes with a pinion 25 which, together with the transport roller 2 and a transmission pinion 27, sits on the shaft 26 in a rotationally fixed manner. The transmission pinion 27 meshes with a pinion 28 which, together with the transport roller 1, is arranged in a rotationally fixed manner on a shaft 28 '.

Im Uebersetzungsverhältnis 1 : 2 treibt die Taktwelle 7 über die Zahnräder 29 und 30 eine Welle 31, auf der drehfest eine Kurvenscheibe 32 sitzt. Diese betätigt, je Maschinen­takt zweimal, das Steigungswerkzeug 5 über eine Schwenk­hebel-Anordnung 33. Weiter werden von der Welle 31 über ein Kettenrad 34 und eine Kette 35 zwei Kettenräder 36 und 37 angetrieben, welche drehfest je auf einer Welle 38 bzw. 39 sitzen und am anderen Ende synchronumlaufende Kurbelscheiben 40 bzw. 41 tragen, an deren Kurbelzapfen ein Messerhalter 42 gelagert ist, an dem das Messer 6 befestigt wird. Im Betriebszustand bewegt sich die Messerschneide somit auf einer kreisförmigen Bahn, die sie je Maschinentakt zweimal durchläuft. Die Bewegung des Messers 6 ist derart auf die Bewegung der Transportrollen 1 und 2 abgestimmt, dass es immer dann eine Schneidposition einnimmt, wenn die Zahn­stange 11 eine ihrer beiden Endlagen einnimmt bzw. wenn die Umlaufgeschwindigkeit der Transportrollen 1 und 2 mindestens näherungsweise Null ist.In the gear ratio 1: 2, the clock shaft 7 drives a shaft 31 via the gears 29 and 30, on which a cam 32 is seated in a rotationally fixed manner. This actuates, twice per machine cycle, the incline tool 5 via a swivel lever arrangement 33. Furthermore, two sprockets 36 and 37 are driven by the shaft 31 via a sprocket 34 and a chain 35, each of which is rotationally fixed on a shaft 38 and 39 and at the other end wear synchronously rotating crank disks 40 and 41, on the crank pin of which a knife holder 42 is mounted, to which the knife 6 is fastened. in the Operating state, the knife edge thus moves on a circular path, which it runs through twice per machine cycle. The movement of the knife 6 is matched to the movement of the transport rollers 1 and 2 in such a way that it always assumes a cutting position when the toothed rack 11 assumes one of its two end positions or when the rotational speed of the transport rollers 1 and 2 is at least approximately zero.

Claims (4)

1. Federwindemaschine mit den Draht (3) zuführenden Transportrollen (1, 2), die von einer Taktwelle (7) antreibbar sind, wobei jeweils die gewundenen Federn am Ende des Windevorganges durch ein auf einer Kreisbahn bewegbares Messer (6), welches den Vorschubweg des Drahtes kreuzt, vom Draht (3) abgetrennt werden, dadurch gekenn­zeichnet, dass die Transportrollen (1, 2) mit einem Schritt­antrieb für den schrittweisen Vorschub des Drahtes angetrieben sind, und dass das Messer jeweils am Ende eines Vorschub­schrittes den Vorschubweg kreuzt, wenn die Vorschubgeschwindig­keit mindestens näherungsweise Null ist.1. Spring winding machine with the wire (3) feeding transport rollers (1, 2), which can be driven by a clock shaft (7), each of the coiled springs at the end of the winding process by a knife (6) movable on a circular path, which the feed path of the wire crosses, are separated from the wire (3), characterized in that the transport rollers (1, 2) are driven by a step drive for the gradual advancement of the wire, and that the knife crosses the feed path at the end of a feed step when the Feed rate is at least approximately zero. 2. Federwindemaschine nach Anspruch 1, dadurch gekennzeichnet, dass der Schrittantrieb ein gerad­linig hin- und her verschiebbares Antriebselement (11) auf­weist, das über zwei entgegengesetzt wirkende Einwegkupp­lungen (16, 17) die Transportwalzen (1, 2) antriebt.2. Spring winding machine according to claim 1, characterized in that the stepping drive has a linearly reciprocating drive element (11) which drives the transport rollers (1, 2) via two oppositely acting one-way clutches (16, 17). 3. Federwindemaschine nach Anspruch 2, dadurch gekennzeichnet, dass das Antriebselement (11) die Einwegkupplungen (16, 17) eingangsseitig taktsynchron aber mit entgegengesetztem Drehsinn antreibt und dass die Einweg­kupplungen abtriebseitig je über die gleiche Anzahl Zahnräder (21 bis 25 bzw. 20, 22 bis 25) die Transportrollen (1, 2) antreiben.3. Spring winding machine according to claim 2, characterized in that the drive element (11) drives the one-way clutches (16, 17) on the input side isochronously but with the opposite direction of rotation and that the one-way clutches on the output side each have the same number of gear wheels (21 to 25 or 20, 22 to 25) drive the transport rollers (1, 2). 4. Federwindemaschine nach einem der Ansprüche 2 bis 3, dadurch gekennzeichnet, dass das Messer (6) jeweils den Vorschubweg kreuzt, wenn das Anstriebselement (11) sich in einer seiner Endlagen befindet.4. Spring winding machine according to one of claims 2 to 3, characterized in that the knife (6) crosses the feed path when the drive element (11) is in one of its end positions.
EP86109100A 1985-08-08 1986-07-03 Spring-coiling machine Expired - Lifetime EP0211242B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3390/85A CH669342A5 (en) 1985-08-08 1985-08-08
CH3390/85 1985-08-08

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EP0211242A2 true EP0211242A2 (en) 1987-02-25
EP0211242A3 EP0211242A3 (en) 1989-03-08
EP0211242B1 EP0211242B1 (en) 1991-03-27

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EP86109100A Expired - Lifetime EP0211242B1 (en) 1985-08-08 1986-07-03 Spring-coiling machine

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US (1) US4779438A (en)
EP (1) EP0211242B1 (en)
JP (1) JP2571216B2 (en)
CH (1) CH669342A5 (en)
DE (1) DE3678354D1 (en)

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DE4040659C1 (en) * 1990-12-19 1992-02-20 Wafios Maschinenfabrik Gmbh & Co Kg, 7410 Reutlingen, De Metal spring coiling machine - incorporates wire feed, coiling tools and cutter
DE4138896A1 (en) * 1990-12-19 1992-07-02 Wafios Maschinen Wagner Spring coiling machine - has alternative crank and cam mechanisms to give rotary or straight cut

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JPH0214818Y2 (en) * 1986-06-12 1990-04-23
JPH0729164B2 (en) * 1993-01-27 1995-04-05 株式会社板屋製作所 Spring manufacturing equipment
US5444905A (en) * 1994-03-14 1995-08-29 Simmons Company Apparatus for manufacturing mattresses and box springs
JP2939472B1 (en) * 1998-08-21 1999-08-25 株式会社板屋製作所 Spring manufacturing equipment
JP3026793B2 (en) * 1998-08-21 2000-03-27 株式会社板屋製作所 Spring manufacturing device and tool selection device
CN107309367B (en) * 2017-07-28 2019-04-16 中国科学院沈阳自动化研究所 A kind of fixed length wire wind

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4040659C1 (en) * 1990-12-19 1992-02-20 Wafios Maschinenfabrik Gmbh & Co Kg, 7410 Reutlingen, De Metal spring coiling machine - incorporates wire feed, coiling tools and cutter
DE4138896A1 (en) * 1990-12-19 1992-07-02 Wafios Maschinen Wagner Spring coiling machine - has alternative crank and cam mechanisms to give rotary or straight cut

Also Published As

Publication number Publication date
JPS6234638A (en) 1987-02-14
EP0211242A3 (en) 1989-03-08
JP2571216B2 (en) 1997-01-16
DE3678354D1 (en) 1991-05-02
CH669342A5 (en) 1989-03-15
EP0211242B1 (en) 1991-03-27
US4779438A (en) 1988-10-25

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