EP0316475B1 - Presse, notamment pour fabriquer des articles pressés gardant leur format à partir de matières pulvérulentes - Google Patents

Presse, notamment pour fabriquer des articles pressés gardant leur format à partir de matières pulvérulentes Download PDF

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Publication number
EP0316475B1
EP0316475B1 EP87117037A EP87117037A EP0316475B1 EP 0316475 B1 EP0316475 B1 EP 0316475B1 EP 87117037 A EP87117037 A EP 87117037A EP 87117037 A EP87117037 A EP 87117037A EP 0316475 B1 EP0316475 B1 EP 0316475B1
Authority
EP
European Patent Office
Prior art keywords
press
lever
drive
arm
ram
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
EP87117037A
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German (de)
English (en)
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EP0316475A1 (fr
Inventor
Theodor Klein
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.)
Grabener Pressensysteme & Co KG GmbH
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Grabener Pressensysteme & Co KG 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.)
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Publication date
Application filed by Grabener Pressensysteme & Co KG GmbH filed Critical Grabener Pressensysteme & Co KG GmbH
Priority to ES87117037T priority Critical patent/ES2021684B3/es
Priority to AT87117037T priority patent/ATE61762T1/de
Priority to DE8787117037T priority patent/DE3768815D1/de
Priority to EP87117037A priority patent/EP0316475B1/fr
Priority to US07/272,733 priority patent/US4923382A/en
Priority to JP63290306A priority patent/JPH01162597A/ja
Publication of EP0316475A1 publication Critical patent/EP0316475A1/fr
Application granted granted Critical
Publication of EP0316475B1 publication Critical patent/EP0316475B1/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
    • B30B1/02—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 lever mechanism
    • B30B1/06—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 lever mechanism operated by cams, eccentrics, or cranks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/02—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space

Definitions

  • the invention relates to a press which can be used, in particular, for producing dimensionally stable compacts from powdery materials, but which is also suitable for other uses, for example in the fields of plastics pressing technology, deep-drawing technology and stamping technology.
  • the subject of the invention is a press with a press frame, in which a press frame and a press table are provided as the main and leading axis, which are coupled to one another by a mechanical drive, primarily a toggle lever drive, and form a main press ram, and above is also provided with a lower plunger assigned to the press table as a pulling plunger and / or counter-pressing plunger, which can be actuated by a lever which is pivotally mounted in the press frame and can be moved by a mechanical drive, in particular a cam or cam drive.
  • the presses based on this development not only ensure that all of the cooperating press axes can always be perfectly reproduced, they can can also be operated with relatively high stroke rates. A high degree of dimensional stability of the entire press system is maintained with a permanently high level of functional reliability.
  • a press system has been created that can only be realized using an existing mechanical press, in particular a toggle press, by integrating an additional hydraulic press part.
  • flexible movement and drive options for the individual presses are achieved and, in addition, pressure-independent path control of the same is made possible.
  • the mechanical press part of the press is also assigned an additional lower plunger which can be actuated by a mechanical drive, namely preferably a cam or cam drive.
  • This lower plunger forms the so-called G-press axis, which makes it possible to work with the press either according to the so-called counter-pressing process or also according to the so-called pull-off process, in which case the lower plunger either forms the press counter-plunger or the press pulling plunger.
  • the invention aims at a press of the initially specified type to optimize the mechanical press part which actuates the ram and functionally in a structurally simple configuration.
  • the object of the invention is therefore to design the functional parts of the mechanical press part which actuates the lower plunger in such a way that it can be easily adapted to the respective needs and, if necessary, can also be retrofitted at any time for changing needs. So it depends on an assembly system for generic presses Specify which equipment and / or retrofit options ensure that the operation of the lower ram either only in the pull-off process or only in the counter-press process, but which also allow the alternate or alternative operation for the pull-off and the counter-press process.
  • the lever is a two-armed lever, one arm of which engages the lower plunger, while its other arm is articulated to an intermediate lever, which in turn is supported on a press frame Vibrating shaft sits, and that the vibrating shaft can be coupled via one or the other of two different gear trains with one and the same mechanical drive.
  • the advantage of this design according to the invention is that, in the simplest case, only the gear train required in each case is installed in the press between the mechanical drive and the lower plunger, in such a way that it either only the gear train for operating the lower plunger during the triggering process or only the gear train contains for the operation of the lower ram in the counter-pressing process. It is also possible to alternately install the two different gear trains in the press or to equip the press with both gear trains at the same time at any time, so that it can be used as desired for the triggering process or the counterpressing process. In the latter case, the oscillating shaft can then optionally and alternately be coupled with two different gear trains of the mechanical drive.
  • the two gear trains each consist of at least one that can be selectively coupled and uncoupled to the oscillating shaft Lever as well as at least from a rotating, driven cam or cam disc engaging there, all cam or cam discs sitting on a common drive shaft, which preferably also carries a drive crank for a toggle lever drive, which forms the actual drive for the main press ram.
  • Another important design measure according to the invention - according to claim 3 - is also that the effective length of the intermediate lever and / or the articulated arm of the two-armed lever is infinitely adjustable so that the stroke of the lower plunger can vary in a simple manner at any time leaves. It has proven useful if - according to claim 4 - the transmission ratio of the intermediate lever to the two-armed lever can be varied continuously over a range from 0 to 1: 2.5.
  • the invention proposes - according to claim 5 - that the connecting joint of the intermediate lever to the two-armed lever is seated in sliding blocks and is displaceable therein via a spindle actuator which is located on or in the second arm of the two-armed lever.
  • the angle lever of one gear train is kept in constant contact with the locking cam disc by a pressure medium cylinder, for example a hydraulic cylinder.
  • the lever of the second gear train is - according to claim 8 - a one-armed lever which protrudes into the effective area of a second drive cam disc and with this by a pressure medium cylinder, e.g. a hydraulic cylinder, is kept in constant contact.
  • Another important embodiment of the invention is - according to claim 9 - that the two-armed lever and the intermediate lever in the direction of a predetermined basic position by a pressure medium cylinder, e.g. a hydraulic cylinder, can be acted upon, and that in this basic position the coupling device between the oscillating shaft and the levers of the two gear trains sitting thereon can be engaged and disengaged.
  • a pressure medium cylinder e.g. a hydraulic cylinder
  • the coupling devices each consist of coupling drivers, which are non-rotatably wedged onto the oscillating shaft, and of coupling slides, which are guided on the levers in an adjustable manner transversely to their plane of movement and which are inserted by pressure medium cylinders, for example hydraulic cylinders. and can be disengaged.
  • the coupling driver has engagement holes, for example bushings, provided arms, while the clutch slider are formed by cross-section push pins.
  • these coupling slides or push pins of the coupling devices can be designed as overload protection devices, for example provided with predetermined breaking points.
  • the short arm of the two-armed lever articulates via a limitedly displaceable intermediate piece on a pressure piece, which in turn is guided in the lower tappet parallel to its direction of movement to a limited extent, with adjustment stops between the pressure piece and the lower plunger, via which the extent of the relative displacement can be changed.
  • an adjustment stop can be assigned to each end of the pressure piece, both adjustment stops being selectively activated by their own drive, e.g. an electromechanical drive.
  • the intermediate piece forms a carriage which can be shifted in height in the table console and which is provided with coupling elements for the lower tappet which can be engaged and disengaged in the transverse direction.
  • the lower plunger drive is associated with a hydraulic press part installed between the press frame and press table with at least one additional press axis, but preferably several additional press axes, in which the working movement is assigned to everyone Press axis of the hydraulic press part away and time-dependent on the working movement of the main and leading axis of the mechanical press part consisting of press frame and press table.
  • the press according to the invention makes a number of different functions of the lower plunger possible.
  • a trigger stroke can be set, which can be varied, for example, between 0 and 80 mm. Any necessary corrections to the height of the lower plunger can be made using an electromagnetic actuator on the extension piece.
  • a mechanical fixation of the lower plunger in the pressed position can also be brought about by the locking cam.
  • electromechanical adjustment of the lower plunger is possible on the one hand in its pressing position and on the other hand in its filling position.
  • the stroke of the lower plunger can be infinitely adjusted, for example over a range from 0 to 80 mm, and an electromechanical adjustment can be effected both for the pressing position and for the filling position.
  • the presses can be switched from the pull-off method to the counter-pressing method and vice versa.
  • the push pins of the coupling devices can be designed as overload protection devices, which prevent damage to other functional parts of the press.
  • cam disk of the gear train in question is easily replaceable on the drive shaft, so that the lifting movement of the lower plunger can be easily adapted to different needs.
  • All other functions of the press during the pull-off process such as lowering the press die, the electromechanical adjustment of the start of lowering, the upward provision of the lower plunger and the height adjustment of the upper connecting piece are preferably effected via the hydraulic press part of the press system.
  • All functions of the press can either be operated individually from a control panel, for example by pressing a button. However, they can also be set and operated automatically by a computer program using a tool code.
  • a hydromechanical press system 101 essentially only the mechanical press part is shown, which in turn has a toggle press 102.
  • the mechanical press part has a press frame 103 which carries a press table 104 and in which a press frame 105 is guided so that it can be raised and lowered relative to the press table 104.
  • the press table 105 is moved in the press frame 103 via a toggle lever system 106 which engages on the one hand via a joint 107 on the press frame 103 and on the other hand via a joint 108 on the press frame 105.
  • a push rod 110 is in drive connection with the knee joint 109 of the toggle lever system 106, which can be formed, for example, by the crank pin of a crank mechanism 111, which is accommodated in the press frame 103.
  • the push rod 110 is thereby moved by the drive in a fixed 360 ° travel-time curve in such a way that the toggle lever system 106 continuously carries out alternating movements between its extended position (FIG. 1) and a predetermined bent position.
  • the press frame 105 runs through a precisely defined, relatively large stroke path relative to the press table 104.
  • a hydraulic press part 112 is adapted into the mechanical press part, which is designed as a toggle press 102, namely between the fixed press table 104 and the press frame 105 that can be raised and lowered, but is only partially shown in FIGS. 1 and 4.
  • the actual pressing tool 113 is also only hinted at in FIGS. 1 and 4.
  • the main press ram of the hydromechanical press system 101 is formed by the cooperation of the press table 104 and the press frame 105 of the toggle press 102 and is effective as the so-called main or leading axis - the so-called X axis - for the entire hydromechanical press system 101.
  • press axes of the hydromechanical press system 101 namely, for example, the so-called M press axis, the so-called Z press axis and the so-called Y press axis (which are not important for the object described here) can be formed by the hydraulic press part 112.
  • the G press axis works with a lower plunger 114, which can only be seen in FIGS. 1 and 4 of the drawing. It consists of a carriage 115, which can be displaced to a limited extent in the table bracket 103 as an intermediate piece, and a carriage 115 that can be inserted and disengaged in the transverse direction Coupling elements 116 for a vertical movement related extension piece 117 which leads up through the press table 104 so that it can cooperate with the pressing tool 113 or the like.
  • the slide 115 of the lower plunger 114 has a frame-like shape, a pressure piece 119 engaging in its frame opening, which is penetrated in the transverse direction by a bearing pin 120.
  • Sliders 121 sit on both ends of the pressure piece 119 on the ends of the bearing bolt 120.
  • a two-armed lever is pivotally supported on a vertical plane to a limited extent about a horizontal transverse axis 122, the short arm 124 of which is fork-shaped and, as can be seen from FIG. 4, with its two fork legs 124a and 124b past the pressure piece 119 into the Frame opening 118 of the slide 115 protrudes.
  • Both fork legs 124a and 124b of the short arm 124 have a link slot 126, in which one of the two sliding pieces 121, which are seated on the bearing pin 120, is accommodated in a longitudinally displaceable manner.
  • the long arm 125 of the two-armed lever 123 is also equipped with a link slot 127, which extends over most of its length and serves as a guide receptacle for a slide 128.
  • a hinge pin 129 is arranged so that it protrudes on opposite sides over the slider 128.
  • a slider 130a or 130b is articulated on each end of the hinge pin 129 and is slidably received in a link slot 131a or 131b.
  • These link slots 131a and 131b are each located on the inside of two cheeks 132a and 132b of an intermediate lever 133.
  • Both cheeks 132a and 132b of the intermediate lever 133 have an angled outline shape and are connected in one piece or in the same material to a bracket in the end region of their one angle leg by a cross piece 132c.
  • the slot slots 131a and 131b extend parallel to the longitudinal direction of the other angle leg of both cheeks 132a and 132b.
  • each cheek 132a and 132b of the intermediate lever 133, 134a and 134b connects in one piece and in a manner fixed against relative rotation, in such a way that the longitudinal central axes thereof not only align with one another, but also pass through the intersection of the two longitudinal central planes of the angle legs of both cheeks 132a and 132b. But also the longitudinal center plane of the slot slots 131a and 131b intersect the longitudinal axes of the two oscillating shafts 134a and 134b.
  • the intermediate lever 133 is connected via its link slots 131a and 131b and the two-armed lever 123 via the link slot 127 in its long arm 125 in an articulated drive connection, in such a way that any swinging movement of the intermediate lever 133 is inevitably transferred to the two-armed lever 123.
  • the transmission ratio of the transmission of movement from the intermediate lever 133 to the two-armed lever 123 can be varied, preferably over a range that includes the value 0 and up to a transmission ratio of 1: 2.5.
  • a spindle actuator 135, which is installed in the long arm 125 of the two-armed lever 123, and whose spindle acts on the slider 128 serves for the stepless adjustment or change of this transmission ratio. By actuating the spindle actuator 135, the sliding pieces 128 and 130a, 130b are moved together in the slot slots 127 and 131a, 131b, so that the transmission ratio changes in accordance with the respective sliding position.
  • the intermediate lever 133 can execute oscillating movements with its oscillating shafts 134a and 134b without any movement being transmitted to the two-armed lever 123.
  • the gear ratio is 0.
  • the intermediate lever 133 is held by its two oscillating shafts 134a and 134b in fixed bearings 137a and 137b of the press frame 103.
  • the oscillating shafts 134a and 134b protrude from both bearings 137a and 137b by a considerable amount.
  • arms 138a and 138b are non-rotatably wedged onto the oscillating shafts 134a and 134b, which can be used as a coupling driver in a manner to be described.
  • the intermediate lever 133 can be driven by the oscillating shafts 134a and 134b by means of two different gear trains 139a and 139b, which have their main drive in common with the crank mechanism 111 for the toggle lever mechanism 106.
  • the gear train 139a shown on the left in FIG. 3 can also be seen in FIG. 1 of the drawing, while the gear train 139b shown on the right in FIG. 3 is further shown in FIG. 2.
  • the gear train 139a comprises a drive cam 140, which is non-rotatably wedged on the drive shaft of the crank drive, and a locking cam 141, which is also non-rotatably seated on this shaft, and an angle lever 142 which is on the left end portion of the left swing shaft 134a of the intermediate lever 133 is held, as can be seen in FIG. 3.
  • the angle lever carries a roller 144 at the free end of its arm 143a and a roller 145 at the free end of its arm 143b. While the roller 144 interacts with the cam contour of the drive cam 140, the roller 145 is the circumferential contour of the locking cam 141 assigned.
  • the angle lever 142 cannot transmit its movement to the intermediate lever 133. Rather, for this purpose it must be brought into engagement with the arm 138a serving as a clutch driver on the oscillating shaft 134a.
  • a push pin 146 serving as a clutch slide is used, which is seated in a guide housing 147 on the angle lever 142 and can be displaced with the aid of a pressure medium drive, namely in particular a hydraulic cylinder 148.
  • the thrust pin 146 In the retracted position of the thrust pin 146, the latter is disengaged from the coupling sleeve of the arm 138a so that the angle lever 142 can be moved freely about the oscillation axis 134a, whereby it can optionally be held in contact with the drive cam plate 140 by a pressure medium cylinder . However, if the push pin 146 is engaged, then the pivoting movement is transmitted to the oscillating shaft 134a via the arm 138a. The movement transmitted from the angle lever 142 to the oscillating shaft 134a then also occurs with the intermediate lever 133 and thereby also forcibly moves the two-armed lever 123.
  • the gear train 139b shown on the right-hand side of FIG. 3 has a drive cam plate 150 which is connected to the drive shaft for the crank mechanism 111 and which interacts with a lever 151 via a roller 152, as can be clearly seen in FIG. 2.
  • the lever 151 is suspended on the right end of the right oscillating shaft 134b, as can be seen easily from FIG. 3.
  • the suspension is normally provided to be relatively movable, i.e. the lever 151 can easily be angularly displaced relative to the oscillating shaft 134b as long as the push pin 154, which is guided in a guide housing 153 of the lever 151 as a coupling slide, is in its disengaged position shown in FIG. 3.
  • this push pin 154 is inserted axially into the coupling sleeve 156 of the arm 138b, which is non-rotatably wedged onto the oscillating shaft 134b by an actuator designed as a hydraulic cylinder 155, as is indicated by dash-dotted lines, then the movement of the lever 151 of the oscillating shaft 134b and over can these are transmitted to the intermediate lever 133.
  • a hydraulic cylinder 157 engages on the two-armed lever 123, which is supported on the press frame 103. He acts on the two-armed lever 123 in such a way that this and thus also the intermediate lever 133, on the one hand, is brought into a predetermined basic position with respect to the angle lever 142 and, on the other hand, with respect to the lever 151, in which at least the pushing-in bolts 146 and 155 can properly engage .
  • a hydraulic cylinder 158 is also supported on the press frame 103, the piston rod of which engages the lever 151 and pushes it in the direction toward the drive cam 150 keeps under tension.
  • the drive device for the lower plunger 114 of the mechanical press part does not in principle have to be equipped with the two drive trains 139a and 139b for the intermediate lever 133. Rather, it is also easily possible to provide either only the gear train 139a or only the gear train 139b. However, the gear train that is not available can be retrofitted into the press at any time, should this be necessary. It is also easily conceivable to remove the gear train contained in the press and instead to install the gear train that was not previously available.
  • a hydromechanical press system 101 which is to be operated both by the so-called pull-off method and by the so-called counter-press method, is expediently equipped with two gear trains 139a and 139b for the intermediate lever 133 from the outset.
  • the gear train 139a is intended for the operation of the hydromechanical press system 101 according to the so-called pull-off method, while the gear train 139b enables the operation of this hydromechanical press system 101 according to the counter-pressing method.
  • An upper adjustment stop 159 and a lower adjustment stop 160 are assigned to the pressure piece 119 in the frame opening 118 of the slide 115.
  • the upper adjustment stop 159 is actuated by an electromechanical drive 161, while the lower adjustment stop 160 can be actuated by a corresponding electromechanical adjustment drive 162.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)

Claims (17)

  1. Presse, notamment destinée à la fabrication de pièces moulées à dimensions exactes à partir de matériaux pulvérulents, comportant un châssis de presse (103) dans lequel sont agencées un cadre de presse (105) et une table de presse (104) en tant que axe principal et de guidage, qui sont accouplés l'un à l'autre par un organe d'entraînement mécanique, notamment un organe d'entraînement à genouillère (106) de façon à effectuer des mouvements concomitants et qui forment un coulisseau principal, et un coulisseau inférieur (114) associé à la table de presse (104) et servant de coulisseau d'éjection et/ou de contre-pression, qui est actionnable par un levier (123) logé de manière pivotable dans le châssis de presse (103) et déplaçable à l'aide d'un organe d'entraînement mécanique (111), particulièrement un entraînement à came , caractérisée en ce que le levier consiste en un levier à deux branches (123) dont l'une des branches (124) agit sur le coulisseau inférieur (114) alors que l'autre branche (125) est reliée de façon articulée (122) à un levier intermédiaire (133) qui est agencé à son tour sur un arbre oscillant (134a, 134b) logé dans le châssis de presse (103), et en ce que l'arbre oscillant (134a, 134b) est accouplable à un seul et même organe d'entraînement mécanique (111) via l'un (139a) ou l'autre (139b) de deux trains d'engrenages.
  2. Presse selon la revendication 1 caractérisée en ce que les deux trains d'engrenages (139a et 139b) sont prévus simultanément et sont accouplables au choix d'un côté ou de l'autre à l'arbre oscillant (134a, 134b), en ce que les deux trains d'engrenages consistent chacun en un levier (142 ou 151) sélectivement accouplable à l'arbre oscillant (134a ou 134b) ou découplable de celui-ci ainsi qu'en au moins une canne (140 ou 150) entraînée en rotation agissant sur celui-ci, les cames (140 et 150) étant logées sur un arbre d'entraînement commun (111) qui comporte de préférence aussi, simultanément, un vilebrequin pour un entraînement à genouillère (106) qui constitue l'entraînement du coulisseau principal.
  3. Presse selon l'une des revendications 1 et 2 caractérisée en ce que la longueur efficace du levier intermédiaire (133) et/ou de la branche (125) du levier à deux branches (123) qui y est articulée est réglable de façon continue.
  4. Presse selon l'une des revendications 1 à 3 caractérisée en ce que le rapport de transmission de levier intermédiaire (133) au levier à deux branches (123) est réglable de façon continue sur une zone allant de 0 à 1:2,5.
  5. Presse selon l'une des revendications 1 à 4 caractérisée en ce que la liaison articulée (129) du levier intermédiaire (133) au levier à deux branches (123) est logée dans des coulisses (127; 131a,131b) de celui-ci et y est déplaçable à l'aide d'un organe d'entraînement à broche (135) qui est agencé à la deuxième branche (125) du levier à deux branches (123) ou dans celle-ci.
  6. Presse selon l'une des revendications 1 à 5 caractérisée en ce que le levier de l'un des trains d'engrenages (139a) est un levier coudé (142) dont l'un des bras (143a) est associé à une came d'entraînement (140) sur l'arbre d'entraînement (111), alors que l'autre bras (143b) s'étend dans la zone angulaire d'une came de blocage (141) également logée sur l'arbre d'entraînement (111).
  7. Presse selon l'une des revendications 1 à 6 caractérisée en ce que le bras (143a) du levier coudé (142) est continuellement maintenu en contact avec la came d'entraînement (140) par un vérin, par exemple un vérin hydraulique.
  8. Presse selon l'une des revendications 1 à 7 caractérisée en ce que le levier (151) du deuxième train d'engrenages (139b) consiste en un levier à un seul bras qui s'étend dans la zone efficace d'une deuxième came d'entraînement (150) et est maintenu continuellement en contact avec celle ci à l'aide d'un vérin (158), par exemple un vérin hydraulique.
  9. Presse selon l'une des revendications 1 à 8 caractérisée en ce que le levier à deux bras (123) et le levier intermédiaire (133) sont actionnables, en direction d'une position de départ prédéterminée, par un vérin (157), par exemple un vérin hydraulique, et en ce que, dans cette position de départ, les dispositifs d'accouplement (146 à 149 ou 153 à 156) sont rétractables et repoussables entre l'arbre oscillant (134a, 134b) ainsi que les leviers qui y sont logés (142 et 151) des deux trains d'engrenages (139a et 139b).
  10. Presse selon l'une des revendications 1 à 9 caractérisée en ce que les dispositifs d'accouplement (146 à 149 ou 153 à 156) consistent chacun en des organes d'entraînement (138a, 138b) agencés par clavette de façon fixe en rotation sur l'arbre oscillant (134 a, 134b) ainsi qu'en des organes poussoirs (146, 154) agencés sur les leviers (142 et 152) de façon réglable transversalement par rapport au plan de mouvement de ceux-ci, les organes poussoirs étant rétractables et repoussables à l'aide de vérins (148, 155), par exemple des vérins hydrauliques.
  11. Presse selon l'une des revendications 1 à 10 caractérisée en ce que les organes d'entraînement (138a et 138b) consistent en des bras munis de douilles d'accouplement (149, 156), tandis que les poussoirs sont constitués par des chevilles (146, 154) de même section transversale.
  12. Presse selon l'une des revendications 1 à 11 caractérisée en ce que les organes poussoirs ou chevilles (146, 154) des organes d'accouplement forment des sécurités de surcharge, et sont par exemple munis de sections destinées à la rupture.
  13. Presse selon l'une des revendications 1 à 12 caractérisée en ce que le bras court (124) du levier à deux bras (123) agit via une pièce de glissement déplaçable de façon limitée (121) de manière articulée, sur une pièce de pression (119) qui est à son tour menée de manière limitativement coulissable dans le coulisseau inférieur (114) parallèlement à la direction de mouvement de celui-ci, des butées réglables (159,160) étant logéesentre la pièce de pression (119) et le coulisseau inférieur (114) et permettant le réglage de la mesure du mouvement.
  14. Presse selon l'une des revendications 1 à 13 caractérisée en ce qu'une butée réglable (159,160) est associée à chaque extrémité de la pièce de pression (119) et en ce que les deux butées réglables (159,160) sont actionnables séparément par un moyen d'entraînement propre, par exemple un moyen d'entraînement électromagnétique (161,162).
  15. Presse selon l'une des revendications 1 à 14 caractérisée en ce que la pièce de glissement constitue un chariot (115) qui est réglable en hauteur dans la console de table (103) et qui est muni d'éléments d'accouplement (116) rétractables et repoussables selon une direction transversale, pour le coulisseau inférieur (117).
  16. Presse selon l'une des revendications 1 à 15 caractérisée en ce que le coulisseau inférieur est associé a une partie de presse hydraulique (112) agencée entre le cadre de presse (105) et la table de presse (104) et comportant au moins un axe de presse supplémentaire, de préférence plusieurs axes de presse supplémentaires (axe M, axe Z et axe Y), le mouvement de travail de chaque axe de presse de la partie hydraulique (112) étant commandable et réglable en fonction de la course et du temps du mouvement de travail de l'axe principal (axe X) de la partie mécanique (102) de la presse, constituée par le cadre de presse (105) et la table de presse (104).
  17. Presse selon l'une des revendications 1 à 16 caractérisée par la commande forcée de l'un des trains d'engrenages (139a) sur une zone angulaire de la came qui correspond à la position du poinçon supérieur dans la position de point mort bas de l'axe X.
EP87117037A 1987-11-19 1987-11-19 Presse, notamment pour fabriquer des articles pressés gardant leur format à partir de matières pulvérulentes Expired - Lifetime EP0316475B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES87117037T ES2021684B3 (es) 1987-11-19 1987-11-19 Prensa para fabricar sobre todo piezas prensadas de materiales en polvo
AT87117037T ATE61762T1 (de) 1987-11-19 1987-11-19 Presse, insbesondere zum herstellen masshaltiger presslinge aus pulverfoermigen werkstoffen.
DE8787117037T DE3768815D1 (de) 1987-11-19 1987-11-19 Presse, insbesondere zum herstellen masshaltiger presslinge aus pulverfoermigen werkstoffen.
EP87117037A EP0316475B1 (fr) 1987-11-19 1987-11-19 Presse, notamment pour fabriquer des articles pressés gardant leur format à partir de matières pulvérulentes
US07/272,733 US4923382A (en) 1987-11-19 1988-11-17 Press for producing precision parts from powdered material
JP63290306A JPH01162597A (ja) 1987-11-19 1988-11-18 プレス

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP87117037A EP0316475B1 (fr) 1987-11-19 1987-11-19 Presse, notamment pour fabriquer des articles pressés gardant leur format à partir de matières pulvérulentes

Publications (2)

Publication Number Publication Date
EP0316475A1 EP0316475A1 (fr) 1989-05-24
EP0316475B1 true EP0316475B1 (fr) 1991-03-20

Family

ID=8197459

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87117037A Expired - Lifetime EP0316475B1 (fr) 1987-11-19 1987-11-19 Presse, notamment pour fabriquer des articles pressés gardant leur format à partir de matières pulvérulentes

Country Status (6)

Country Link
US (1) US4923382A (fr)
EP (1) EP0316475B1 (fr)
JP (1) JPH01162597A (fr)
AT (1) ATE61762T1 (fr)
DE (1) DE3768815D1 (fr)
ES (1) ES2021684B3 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995014567A1 (fr) * 1993-11-24 1995-06-01 Stackpole Limited Filiere double pour piece a contre-depouille
WO1995014568A1 (fr) * 1993-11-24 1995-06-01 Stackpole Limited Matrice double a mise en phase
US5580586A (en) * 1994-03-17 1996-12-03 Tamagawa Machinery Co., Ltd. Die control speed rate conversion device for powder mold press
US6165400A (en) * 1996-05-09 2000-12-26 Stackpole Limited Compacted-powder opposed twin-helical gears and method
US6440357B1 (en) 1996-05-09 2002-08-27 Stackpole Limited Compacted-powder opposed twin-helical gears and method
CN1074983C (zh) * 1998-04-16 2001-11-21 朱锦忠 粉末成型压机
CN1089675C (zh) * 1999-05-13 2002-08-28 吴素珍 粉末成型压机的加压机构
GB2360825B (en) * 2000-03-30 2004-11-17 Formflo Ltd Gear wheels roll formed from powder metal blanks
CN1322972C (zh) * 2003-12-17 2007-06-27 朱锦忠 粉末成型压机的顶压加压机构
CN100467262C (zh) * 2005-04-11 2009-03-11 朱锦忠 粉末成型压机的顶压凸轮装置
DE102007011489A1 (de) * 2007-03-07 2008-09-11 Kiefel Gmbh Überlastsicherung, Antriebsstrang mit einer derartigen Überlastsicherung, Vorrichtung zum Herstellen und/oder Bearbeiten eines Werkstückes sowie Verfahren zum Aufbringen von Arbeitskräften
CN101927580B (zh) * 2009-06-19 2013-03-27 扬州锻压机床股份有限公司 一种粉末成型机

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Publication number Priority date Publication date Assignee Title
DE120177C (fr) *
US2867844A (en) * 1954-01-18 1959-01-13 Baldwin Lima Hamilton Corp Press for molding powdered material
GB1141114A (en) * 1966-04-08 1969-01-29 Pramet Zd Y Praskove Metalurgi Improvements in and relating to mechanical presses
DE1627942C3 (de) * 1967-09-27 1974-03-07 Mannesmann-Meer Ag, 4050 Moenchengladbach Steuerung der Bewegung der Matrize einer mechanischen Pulver-Formpresse
US3545045A (en) * 1968-09-04 1970-12-08 Paul Vinson Powder compacting subpress
US3687586A (en) * 1970-04-22 1972-08-29 Tamagawa Kikai Kinzoku Kk Powder-forming press
ZA715429B (en) * 1970-09-10 1972-04-26 Olivetti & Co Spa A device for moulding parts to be sintered
GB1361684A (en) * 1970-09-22 1974-07-30 Olivetti & Co Spa Device for moulding sinterin blanks
US3826599A (en) * 1972-06-01 1974-07-30 Wolverine Pentronix Adjusting mechanism and process for powder compacting press
DE2424802C3 (de) * 1974-05-22 1978-08-31 Gebr. Netzsch, Maschinenfabrik Gmbh & Co, 8672 Selb Presse zum Herstellen von Formungen aus pulverförmigen oder körnigen Werkstoffen
US4166716A (en) * 1977-05-20 1979-09-04 Ptx-Pentronix, Inc. Mechanical toggle and fluid actuated ram for powder compacting press
ATE55086T1 (de) * 1987-05-07 1990-08-15 Graebener Theodor Pressensyst Presse, insbesondere zum herstellen masshaltiger presslinge aus pulverfoermigen werkstoffen, und verfahren zum betrieb einer solchen presse.
ATE61761T1 (de) * 1987-09-02 1991-04-15 Graebener Theodor Pressensyst Presse, insbesondere zum herstellen masshaltiger presslinge aus pulverfoermigen werkstoffen.

Also Published As

Publication number Publication date
DE3768815D1 (de) 1991-04-25
US4923382A (en) 1990-05-08
ATE61762T1 (de) 1991-04-15
JPH01162597A (ja) 1989-06-27
EP0316475A1 (fr) 1989-05-24
JPH0460759B2 (fr) 1992-09-28
ES2021684B3 (es) 1991-11-16

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