EP0248917B1 - Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentrique - Google Patents

Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentrique Download PDF

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Publication number
EP0248917B1
EP0248917B1 EP86107769A EP86107769A EP0248917B1 EP 0248917 B1 EP0248917 B1 EP 0248917B1 EP 86107769 A EP86107769 A EP 86107769A EP 86107769 A EP86107769 A EP 86107769A EP 0248917 B1 EP0248917 B1 EP 0248917B1
Authority
EP
European Patent Office
Prior art keywords
eccentric
bush
eccentric shaft
shaft
eccentrics
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
EP86107769A
Other languages
German (de)
English (en)
Other versions
EP0248917A1 (fr
Inventor
Robert Czapka
Alfred Bareis
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.)
L Schuler GmbH
Original Assignee
L Schuler 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 L Schuler GmbH filed Critical L Schuler GmbH
Priority to DE8686107769T priority Critical patent/DE3677597D1/de
Priority to EP86107769A priority patent/EP0248917B1/fr
Priority to US07/057,358 priority patent/US4785732A/en
Priority to ES8701656A priority patent/ES2005247A6/es
Publication of EP0248917A1 publication Critical patent/EP0248917A1/fr
Application granted granted Critical
Publication of EP0248917B1 publication Critical patent/EP0248917B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/263—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks work stroke adjustment means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0064—Counterbalancing means for movable press elements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/211—Eccentric
    • Y10T74/2111—Plural, movable relative to each other [including ball[s]]
    • Y10T74/2112—Concentric

Definitions

  • the invention relates to a device on a press with an eccentric shaft for adjusting the ram stroke by adjusting the resulting eccentricity of an eccentric and an eccentric bushing mounted thereon, on which a connecting rod is mounted, the eccentric bushing on the eccentric optionally being detachable and fixable in the direction of rotation by actuating means is, and wherein the detached eccentric bushing can be fixed on a part not rotating with the eccentric shaft and in this fixed state the eccentric shaft can be rotated for the purpose of adjusting the tappet stroke.
  • Such devices are known in numerous embodiments, for example from DE-A 25 34 626, DE-A 27 40 382, DE-A 34 21 184 and DE-U 81 27 545, both for presses with only one Connecting rods (single-point presses) than on those with multiple connecting rods (multi-point presses). All these known devices have in common that for the release and fixing of the eccentric bush on the eccentric acting actuating means are provided, such as internal, external and spur gears and claw rings. These actuating means all have the disadvantages that they can only be brought into engagement in stages due to the positive interlocking, the engagement cannot be completely free of play, and there is a risk of deflection during operation of the machine and with frequent actuation.
  • press bandages are known per se as releasable connections, for example from the DE specialist book “connecting elements” by Decker, Carl Hanser Verlag Kunststoff 1963, pp. 284/285.
  • these press braces only serve to connect the parts in a certain mutual position and to release them if necessary, for example when dismantling a machine.
  • a rolling bearing in which an intermediate ring supported with respect to these two bearing rings via rolling elements and with eccentrically located raceways for the rolling elements is provided between the outer and the inner bearing ring.
  • the eccentricity of the raceways of this intermediate ring can be changed in that the intermediate ring consists of two rings divided along a separating joint which is conical in the axial direction. These two rings can be easily joined and detached by means of a press fit by introducing pressure oil through a groove in the joint. The adjustment of the eccentricity of the running surfaces to one another that is made possible thereby serves to set a supported axle relative to a housing bore.
  • the first assembly of the press fit can take place either in the presence of a temperature difference between the eccentric sleeve and the eccentric or by pressurizing the cavity delimited by the cylindrical fitting surface in the eccentric sleeve.
  • An axial pressure oil line with at least one connecting line to the groove is expediently provided in the eccentric shaft, as a result of which the supply of pressure oil to the mating surfaces can be simplified.
  • the device on the eccentric shaft can have two rectified eccentrics of the same eccentricity with eccentric bushes of the same eccentricity mounted on them.
  • the required synchronism of the actuation can thus be easily achieved. If such a press is to be operated with a high number of strokes (high-speed press), mass balancing must generally be provided in the form of a balancing mass that can be moved in the opposite direction to the ram.
  • the eccentric shaft has at least one eccentric which diametrically opposes at least one other eccentric of the same eccentricity is directed, and that eccentric bushes of the same eccentricity are mounted on all eccentrics, or that the eccentric shaft has at least one eccentric which is diametrically opposed to at least one eccentric, and that the ratio of the eccentricities of the eccentric bushes to the eccentricities of the eccentrics for all eccentric / Eccentric bushing pairings is the same.
  • angular encoder disks are arranged coaxially on the eccentric shaft, at least one of which is non-rotatably connected to the eccentric shaft and at least one per eccentric bushing is rotatably mounted on the eccentric shaft and is non-rotatably connected to the associated eccentric bushing, and that each Angle encoder disk is assigned to at least one fixed contactless sensor.
  • an eccentric shaft 2 is mounted, which is provided with two rectilinear eccentrics 3 and a diametrically opposed eccentric 4, all of which have the same eccentricities.
  • Eccentric bushes 5, 6 are seated on the eccentrics 3, 4 and also have the same eccentricities.
  • Connecting rods 7 are mounted on the eccentric bushes 5 and are articulated on a tappet 9 at the other ends.
  • On the eccentric bush 6, a connecting rod 8 is mounted, which is articulated at the other end to a leveling mass 10.
  • a press fit is formed, which by supplying pressure oil through an axial pressure oil line 11 and connecting lines to a groove 12 in the mating surface of each eccentric 3, 4 is solvable.
  • a pressure oil source - not shown in the drawing - with a downstream valve is provided, which also enables the pressure oil line 11 to be relieved and the pressure oil to be drained off.
  • an angle encoder disk 13 is fastened coaxially and in a rotationally fixed manner, to which a sensor 14 which is fixed in space in the frame 1 is assigned.
  • three angle encoder disks 15 are rotatably mounted, each of which is rotatably connected to an eccentric sleeve 5, 6 in that the eccentric sleeve 5, 6 has a pin 16 projecting on one side, which engages in a slot 17 in the associated angle encoder disk 15 .
  • Each of the angle encoder disks 15 is assigned a contactless sensor 24 which is fixed in space in the frame 1.
  • each angle encoder disc 15 - shown in the drawing only in FIG. 2 for the angle encoder disc 15 assigned to the eccentric bushing 6 - has a recess 18 on the outer circumference, into which a bolt 19, which can be moved and controlled radially to the eccentric shaft 2, can engage, which can be engaged in the Frame 1 is slidably mounted.
  • Each bolt 19 has at its rear end, facing away from the associated recess 18, a nose 20 which interacts in each of the two end positions of the bolt 19 with one of two associated, contactless sensors 21, 22 which are fixed in space on the frame 1 .
  • the procedure is as follows. After the press has stopped, the eccentric shaft 2 with eccentrics 3, 4, eccentric bushes 5, 6 fixed thereon and associated angle encoder disks 13, 15 is rotated into an initial position at creep speed. This initial position corresponds to the plunger stroke that is still set and is determined in that in this initial position for the adjustment of the plunger stroke to be initiated, the bolts 19 can engage in the recesses 18 and initiators 23 provided on the angle encoder disks 15 face the assigned sensors 24. The reaching of this initial position is signaled by the sensors 24 and the eccentric shaft 2 is thus stopped by switching off the creep speed drive.
  • the bolts 19 are actuated radially inwards, which thereby engage in the recesses 18 and fix the angle encoder disks 15 and the eccentric bushes 5, 6 in the direction of rotation.
  • This state is reported by the radially inner sensors 21, which the lugs 20 on the bolt 19 face.
  • the eccentric shaft 2 with the eccentric tern 3, 4 rotated by the crawl speed drive according to the preselected ram stroke.
  • the angle of rotation path required for this or the absolute angle of rotation position required for this is detected by the angle encoder disk 13 and the associated sensor 14.
  • the correct angle of rotation position of the eccentric bushes 5, 6 on the eccentrics 3, 4 can be monitored by monitoring the synchronism of the occurrence of the signals at the sensors 24.
  • the correct rotational angle position of the eccentric bushes 5, 6 on the eccentrics 3, 4 can be restored by loosening the press fit, applying the bolts 19 radially inwards and rotating the eccentric shaft 2 until all bolts 19 in the recesses 18 engage, which can be indicated by the sensors 21. With this, the synchronism is restored; the bandages can be restored.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Claims (8)

  1. Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentriques (2) par réglage de l'excentricité résultant d'un excentrique (3, 4) et d'une douille excentrique (5, 6) portée par celui-ci au moyen de surfaces cylindriques de palier, douille sur laquelle est montée une bielle (7, 8), la douille excentrique (5, 6) pouvant être sélectivement bloquée sur l'excentrique (3, 4) ou libérée dans le sens de rotation grâce à des moyens de commande, et dans lequel la douille excentrique libérée (5,6) est agencée pour être fixée à un élément ne tournant pas avec l'arbre à excentriques (2) et, dans cette situation, l'arbre à excentriques (2) peut tourner pour régler la course du coulisseau, caractérisé en ce que les surfaces cylindriques de palier de la douille excentrique (5, 6) sur l'excentrique (3, 4) sont formées par des surfaces de contact ménagées sur ces deux éléments et entre lesquelles est réalisé, grâce à un surdimensionnement de l'excentrique (3, 4), un assemblage comprimé qui peut être libéré par introduction d'huile sous pression dans au moins une rainure (12) ménagée dans au moins une surface de contact.
  2. Dispositif selon la revendication 1, caractérisé en ce que l'assemblage comprimé entre la douille excentrique (5, 6) et l'excentrique (3, 4) est produit à l'aide d'une différence de température entre ces deux éléments.
  3. Dispositif selon la revendication 1, caractérisé en ce que l'assemblage comprimé entre la douille excentrique (5, 6) et l'excentrique (3, 4) est produit par application d'une pression hydraulique dans l'espace libre délimité par la surface cylindrique de contact dans la douille excentrique (5, 6).
  4. Dispositif selon la revendication 1, 2 ou 3, caractérisé en ce quel'arbre à excentriques (2) comporte un conduit axial (11) d'huile sous pression, ayant au moins un conduit de raccordement à ladite rainure (12).
  5. Dispositif selon la revendication 4, caractérisé en ce quel'arbre à excentriques (2) comporte deux excentriques (3) ayant des excentricités égales et de même direction et portant des douilles excentriques (5) ayant des excentricités égales.
  6. Dispositif selon la revendication 4 ou 5, caractérisé en ce que l'arbre à excentriques (2) comporte au moins un excentrique (3) dont l'excentricité est égale et diamétralement opposée à celle d'un autre excentrique (4), et en ce que tous les excentriques (3, 4) portent des douilles excentriques (5, 6) ayant des excentricités égales.
  7. Dispositif selon la revendication 4 ou 5, caractérisé en ce que l'arbre à excentriques (2) comporte au moins un excentrique dont l'excentricité est différente et diamétralement opposée à celle d'un autre excentrique, et en ce que le rapport entre les excentricités des douilles et celles des excentriques est le même dans toutes les paires formées par une douille et un excentrique.
  8. Dispositif selon l'une des revendications précédentes, caractérisé en ce que des disques indicateurs d'angle (13, 15) sont disposés coaxialement sur l'arbre à excentriques (2), parmi lesquels au moins un disque (13) est solidaire en rotation de l'arbre et au moins un disque (15) pour chaque douille excentrique (5, 6) est monté de manière rotative sur l'arbre (2) et est solidaire en rotation de la douille correspondante (5, 6), et en ce que chaque disque indicateur d'angle (13, 15) est associé à au moins un capteur sans contact (14, 24), disposé de manière stationnaire.
EP86107769A 1986-06-06 1986-06-06 Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentrique Expired - Lifetime EP0248917B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE8686107769T DE3677597D1 (de) 1986-06-06 1986-06-06 Vorrichtung an einer presse mit exzenterwelle zum verstellen des stoesselhubes.
EP86107769A EP0248917B1 (fr) 1986-06-06 1986-06-06 Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentrique
US07/057,358 US4785732A (en) 1986-06-06 1987-06-03 Push rod stroke adjustment device for a press
ES8701656A ES2005247A6 (es) 1986-06-06 1987-06-05 Dispositivo en una prensa con arbol de excentrica para regular lacarrera del portamachos

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP86107769A EP0248917B1 (fr) 1986-06-06 1986-06-06 Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentrique

Publications (2)

Publication Number Publication Date
EP0248917A1 EP0248917A1 (fr) 1987-12-16
EP0248917B1 true EP0248917B1 (fr) 1991-02-20

Family

ID=8195176

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86107769A Expired - Lifetime EP0248917B1 (fr) 1986-06-06 1986-06-06 Dispositif de réglage de la course du coulisseau dans une presse à arbre à excentrique

Country Status (4)

Country Link
US (1) US4785732A (fr)
EP (1) EP0248917B1 (fr)
DE (1) DE3677597D1 (fr)
ES (1) ES2005247A6 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4130031A1 (de) * 1991-09-10 1993-03-18 Graebener Theodor Pressensyst Hub-verstellvorrichtungen fuer exzenterwellen
DE4219405A1 (de) * 1992-06-13 1993-12-16 Hensel Eisenwerk Exzenterpresse mit veränderbarem Stößelhub
DE19746180B4 (de) * 1997-02-07 2008-10-16 The Minster Machine Company, Minster Werkzeug und Verfahren zum Einstellen der exzentrischen zeitlichen Position bei Kurbelwellen mit einstellbarem Hub

Families Citing this family (24)

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Publication number Priority date Publication date Assignee Title
CH672173A5 (fr) * 1986-04-28 1989-10-31 Bruderer Ag
EP0250871B1 (fr) * 1986-06-30 1990-08-08 Aida Engineering Ltd. Dispositif pour le réglage de la course dans les presses
CH677336A5 (fr) * 1988-08-31 1991-05-15 Bruderer Ag
CA2037500A1 (fr) * 1990-03-05 1991-09-06 Masakatsu Shiga Appareil permettant d'ajuster la course du chariot d'une presse
US5109766B1 (en) * 1990-10-31 1994-03-22 Minster Machine Co Adjustable stroke punch press
US5136875A (en) * 1991-03-08 1992-08-11 The Minster Machine Company Single reciprocating dynamic balancer for a double action stamping press
DE4132976C2 (de) * 1991-10-04 2003-04-17 Schuler Pressen Gmbh & Co Vorrichtung an einer Presse zum Verstellen der Hübe eines Arbeitsstößels und einer Gegenschwingmasse
DE4201095A1 (de) * 1992-01-17 1993-07-22 Raster Maschinen Gmbh Synchron verstellbarer dynamischer massenausgleich an exzenterpressen oder -stanzen mit automatischer hubverstellung
US5398601A (en) * 1993-04-20 1995-03-21 The Minster Machine Company Press shutheight adjustment in motion mechanism
US5345861A (en) * 1993-04-20 1994-09-13 The Minater Machine Company Press adjustment screw mechanism
US5349902A (en) * 1993-04-20 1994-09-27 The Minster Machine Company Press shutheight adjustment mechanism
US5446955A (en) * 1993-10-08 1995-09-05 Mitsubishi Heavy Industries America, Inc. Mold height extension method
DE19645464B4 (de) * 1995-11-13 2006-12-07 The Minster Machine Co., Minster Mechanische Presse
US5865070A (en) * 1996-10-28 1999-02-02 The Minster Machine Company Adjustable stroke connection
DE19810405A1 (de) * 1998-03-11 1999-09-16 Schuler Pressen Gmbh & Co Exzenterpresse mit geregelter Hauptwellenpositionierung
DE19810406A1 (de) * 1998-03-11 1999-09-16 Schuler Pressen Gmbh & Co Exzenterpresse mit variabler Stößelbewegung
JP2001300798A (ja) * 2000-04-25 2001-10-30 Aida Eng Ltd プレス機械のストローク調節装置
US6676323B2 (en) * 2000-12-29 2004-01-13 The Minster Machine Company Adjustable clamping device in a mechanical press
US6647869B2 (en) * 2002-04-02 2003-11-18 The Minster Machine Company Positive lock for infinite adjustable stroke mechanism
ITMI20031783A1 (it) * 2003-09-18 2005-03-19 Donato Manera Dispositivo per regolare la corsa di una pressa meccanica e metodo per regolare detta corsa mediante detto dispositivo
EP1764882B1 (fr) * 2005-09-19 2008-07-16 komax Holding AG Presse à sertissage
US8025346B2 (en) * 2006-12-15 2011-09-27 Caterpillar Inc. Machine component configuration for enhanced press fit and press fit coupling method
CN104960234B (zh) * 2015-07-28 2016-08-03 济南精创模具技术开发有限公司 生物质成型机偏心轮安装轴
CN111055529A (zh) * 2019-12-31 2020-04-24 宁波精达成形装备股份有限公司 一种带动平衡机构的压力机

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GB554328A (en) * 1942-06-24 1943-06-29 Thos W Ward Ltd Improvements in and relating to power presses
BE570085A (fr) * 1957-09-13
US3358591A (en) * 1965-10-23 1967-12-19 Textron Inc Press
CS148900B1 (fr) * 1970-06-10 1973-05-24
CH541734A (de) * 1971-08-04 1973-09-15 Maschb Ing O Klammer Einrichtung zur stufenlosen Verstellung des Hubes einer auf einer Exzenterwelle gelagerten Pleuelstange
US4156387A (en) * 1974-09-03 1979-05-29 Bruderer Ag Apparatus for mass compensation at a machine driven by a crank drive
CH581281A5 (fr) * 1974-09-03 1976-10-29 Bruderer Ag
DE2542070A1 (de) * 1975-09-20 1977-03-31 Skf Kugellagerfabriken Gmbh Waelzlager
DE2740382C2 (de) * 1977-09-08 1987-01-29 L. Schuler GmbH, 7320 Göppingen Vorrichtung für die Einstellung des Hubes einer Exzenterpresse
DE2855579A1 (de) * 1978-12-22 1980-07-03 Grensing Gmbh Waelz- oder gleitlager
DE3121007C2 (de) * 1980-07-07 1985-07-25 Delmag-Maschinenfabrik Reinhold Dornfeld Gmbh + Co, 7300 Esslingen Kurbelantriebsvorrichtung für Bodenverdichtungsgeräte
DE8127545U1 (de) * 1981-09-19 1983-04-14 Maschinenfabrik Weingarten Ag, 7987 Weingarten Vollautomatische Verstellung des Stösselhubes bei Doppelständerpressen mit zwei auf Exzenterbüchsen einer Exzenterwelle hintereinander angeordneten Pleuel
DE3408662A1 (de) * 1984-03-09 1985-09-19 Haulick + Roos Werkzeugmaschinen GmbH, 7530 Pforzheim Vorrichtung zum veraendern des stoesselhubes an einer exzenterpresse
DE3421184C2 (de) * 1984-06-07 1986-11-20 Unidor GmbH, 7534 Birkenfeld Verfahren zur Hubverstellung an Exzenterpressen

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4130031A1 (de) * 1991-09-10 1993-03-18 Graebener Theodor Pressensyst Hub-verstellvorrichtungen fuer exzenterwellen
DE4219405A1 (de) * 1992-06-13 1993-12-16 Hensel Eisenwerk Exzenterpresse mit veränderbarem Stößelhub
DE19746180B4 (de) * 1997-02-07 2008-10-16 The Minster Machine Company, Minster Werkzeug und Verfahren zum Einstellen der exzentrischen zeitlichen Position bei Kurbelwellen mit einstellbarem Hub

Also Published As

Publication number Publication date
EP0248917A1 (fr) 1987-12-16
DE3677597D1 (de) 1991-03-28
US4785732A (en) 1988-11-22
ES2005247A6 (es) 1989-03-01

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