EP0228030B1 - Machine de forgeage - Google Patents

Machine de forgeage Download PDF

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Publication number
EP0228030B1
EP0228030B1 EP86117589A EP86117589A EP0228030B1 EP 0228030 B1 EP0228030 B1 EP 0228030B1 EP 86117589 A EP86117589 A EP 86117589A EP 86117589 A EP86117589 A EP 86117589A EP 0228030 B1 EP0228030 B1 EP 0228030B1
Authority
EP
European Patent Office
Prior art keywords
rams
piston
pistons
machine according
forging machine
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
EP86117589A
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German (de)
English (en)
Other versions
EP0228030A2 (fr
EP0228030A3 (en
Inventor
Heinz Schmoll
Peter Schubert
Hans Albert Schubert
Klaus Schulze
Heinrich Kutz
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.)
SMS Hasenclever GmbH
Original Assignee
SMS Hasenclever 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 SMS Hasenclever GmbH filed Critical SMS Hasenclever GmbH
Priority to AT86117589T priority Critical patent/ATE62838T1/de
Publication of EP0228030A2 publication Critical patent/EP0228030A2/fr
Publication of EP0228030A3 publication Critical patent/EP0228030A3/de
Application granted granted Critical
Publication of EP0228030B1 publication Critical patent/EP0228030B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J13/00—Details of machines for forging, pressing, or hammering
    • B21J13/02—Dies or mountings therefor
    • B21J13/03—Die mountings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J13/00—Details of machines for forging, pressing, or hammering
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/02—Special design or construction
    • B21J7/14—Forging machines working with several hammers

Definitions

  • Forging machines are used for forging workpieces with a round, square, rectangular or similar cross-section that are emphasized along the longitudinal axis and are usually provided with four x-shaped rams with tools, which act radially on the workpiece and act radially on the workpiece.
  • the tools distributed around the workpiece which form a closed caliber at least in their stroke end position, allow for wide-free forming with correspondingly good forging.
  • the economic use of these forging machines requires a high degree of flexibility, which is why the workpieces should always be manufactured without a form bond between the tool and the workpiece. Accordingly, tools with a flat effective surface are used.
  • the cross section enclosed by the tools in the stroke end position results in a cross section with an edge length corresponding to the tool width.
  • the forging machine according to DE-C-325 985 has a caliber closed in all stroke positions, the tools of which are arranged in such a way that the side surface of one tool lies against the working surface of an adjacent tool.
  • the invention is based on this prior art.
  • the tools assigned to the plungers moving radially to the system axis are movable in the working plane at right angles to the axes of their plungers and are held in constant mutual contact by the force of each spring.
  • each tappet must move the tool adjacent to its work surface with one side surface against the friction and spring force resulting from the pressure of this tool on the workpiece, and also the friction between the side surface of its tool and the work surface of the other neighboring one Overcome tool, with the result of high power losses and high wear on the tools and tool guides of the ram.
  • the tool supports as handlebars with adjustable bearings on the tool supports in Area of the tools acting piston-cylinder units, the handlebars guide the tools so that they form an almost closed caliber in all stroke positions.
  • the tools of these forging machines make a movement transversely to the forging during their stroke from what is usually unfavorable for the forging process and leads to increased tool wear.
  • the caliber between the tools rotates with the handlebar movement and this rotation must be followed by the forging and the manipulator pliers guiding the forging.
  • the invention goes back to the state of the art given by DE-C-325 985 according to the preamble of claim 1.
  • the aim of the invention is to make transverse, oblique or oscillating movements of the tools and the resulting sliding movements between the tools and the Avoid workpiece, but maintain a closed caliber between the tools in the respective stroke end position over the entire working area.
  • the invention provides that piston-cylinder units are assigned as drive units, adjusting means for setting and displaying the stroke end positions of their working strokes, and that the tools are also supported with the tool offset in the working plane relative to the axis of the piston-cylinder units determining actuators are provided, and that the transverse adjustment of the tools takes place depending on the setting of the stroke end positions to such an extent that the tool edge formed by the working surface of a tool and its side surface facing the working surface of an adjacent tool by the same amount from the central axis of its pistons Cylinder units are offset, as the neighboring tool, which covers the side surface of the first tool with its working surface, approaches its piston-cylinder unit at the stroke end position set for the forging pass.
  • a caliber that is closed in all stroke positions is dispensed with, since it was recognized that it was sufficient if that Caliber is closed in the stroke end position corresponding to the respective forging dimension, which can be achieved according to the invention by the adjustability of the tools transversely to the drive units.
  • a tool adjustment is possible for a short time with the workpiece remaining in the caliber between the tools together with the stroke position adjustment for the subsequent forging pass.
  • piston-cylinder units are used only as drive units for separate plungers or the plungers themselves are designed as parts of the piston-cylinder units, it is advantageous that To dimension piston-cylinder units only for the working stroke and to provide the stroke position adjustment by means of special mechanical adjusting means, as is known per se for the purpose of minimizing the oil volume effective in the hydraulic drive and influencing the dynamic behavior of the forging machine.
  • cross pieces fitted with the tools in head pieces of the plunger in the working plane are adjustable at right angles to the plunger axis and can be fixed by releasable clamping elements relative to the head pieces, while adjusting devices for moving the cross pieces in the head pieces when the clamping elements are released between the Head pieces and cross pieces are arranged to act.
  • the drive and / or display devices for the actuating devices are expediently arranged on the ends of the plungers facing away from the head pieces and connected by coupling to the actuating devices, the couplings passing through the plungers or being arranged parallel to the plungers.
  • a space-saving arrangement results from the fact that the tappets are designed as parts (pistons or cylinders) of piston-cylinder units provided for the tappet drive. If the tappets are designed as pistons, it is advisable to connect the cylinders to the machine frame for direct guidance of the pistons and to adjust the stroke position by means of plugs which are adjustable in the cylinders and form the bottoms of the cylinders. If, on the other hand, the plungers are designed as cylinders, which are thus movably guided in the machine frame, the pistons must be provided for adjusting the stroke position by being arranged in the machine frame so as to be adjustable.
  • Both the pistons serving as plungers can be provided with shafts penetrating the plugs, and the cylinders serving as plungers can be provided with the shafts penetrating as pistons.
  • These shafts can be designed for the stroke limitation and the retraction of the pistons or cylinders (tappets) and can also be axially pierced so that, according to a further feature of the invention, they can accommodate the couplings for the geared connection of the adjusting devices with their drive and / or display devices .
  • Racks connected to the cross pieces and pinions engaging in these and shafts connected to the pinions can be provided as adjusting devices, the shafts being guided through the central bores in the tappets or laterally along the tappets.
  • a precondition for a safe working method is that an unwanted displacement of the cross pieces in relation to the ram heads is excluded.
  • plunger heads and cross pieces are provided with corresponding grooves and strips inserted into the grooves and provided with teeth.
  • the pistons with the plungers are moved by the adjustment of the crosspieces in the case of piston-cylinder units arranged radially to the system axis for driving the plungers, the cylinders of which are arranged stationary in the machine frame Couplings that compensate for the tappets but transmit the axial forces from the pistons to the tappets.
  • a simple, reliably working coupling of the piston and tappet consists of a T or dovetail groove in the tappet end face, T or dovetail sliding pieces guided therein and pistons connected to the sliding pieces and of pistons guided in cylinder bores in a cross member over yoke pieces to exciting tie rods, the loading of the pistons being interrupted during the displacement of the cross pieces by the adjusting devices and the couplings thus being released.
  • the piston-cylinder units designed in connection with mechanical adjusting means, in particular screw drives for the stroke position adjustment form the further advantage that, together with a mechanical limitation of the working stroke, the mechanical fixing the stroke position so that the stroke end position and the setting of the tools can be precisely coordinated with each other using the cross pieces.
  • Automation of the forging process is possible if the lateral displacements of the crosspieces relative to the ram heads or the machine frame and the stroke end positions of the ram are measured and can be set as a function of a caliber dimension that has been entered and programmed via a process computer.
  • Figure 1 shows a first embodiment seen in an overall view in the direction of the system axis, for what Figure 1a shows a section with a different tool setting.
  • Figure 2 shows a section along the section line AA shown in Figure 5 3 shows a section along the section line BB entered in Figure 5 4 shows a section along the section line CC and entered in Figure 5
  • Figure 5 is a plan view of one of the four piston-cylinder units guiding a tappet with a tool.
  • a second embodiment is in Figure 6 shown in a section corresponding to Figure 2 for the first embodiment.
  • the workpiece 1 can be seen in its cross section, which traverses the length of the forging machine and is thereby stretched by the tools 2.
  • the tools 2 are cross-lock-like, that is to say offset according to the cross-section to be forged, and an adjacent tool 2 is arranged overlapping around the workpiece 1 with their working surface.
  • the respective center offset of the tools 2 determines the possible approximation of the tools 2 and thus the smallest cross section to be forged with a specific tool setting, which in turn determines the inner reversal points of the stroke movement of the tools 2, ie the stroke end positions of the respective stroke positions.
  • FIGS. 2 to 5 The details of the units formed from the tappets or pistons 3 and the cylinders 4 are shown in FIGS. 2 to 5.
  • the cylinders 4 are provided with flanges 8 and the frames 5 per cylinder 4 are provided with four eyes 9.
  • the tie rods 10 are also extended to spindles 13 with a threaded shaft 14.
  • Each cylinder 4 has a through bore which is closed on one side by a plug 15, which includes a seal 16.
  • the plug 15 is fixedly connected to a yoke plate 17, which are provided with four bores 18 for the passage of the spindles 13 to the tie rods 10.
  • the bores 18 are expanded to bearing bores in which nuts 20 provided on the outside with teeth 19 and on the inside with threads are rotatably supported and held by a split bearing plate 21.
  • the four nuts 20 of a yoke plate 17 are rotated together by a ring gear 22 which is rotatable with balls 23 on a bearing ring 24 centered and fastened on the yoke plate 17.
  • a plunger 3 formed from a piston 3 and also carrying the tool 2 is axially movable.
  • the piston 3 is provided with a round shaft 29 and at the transition from the piston 3 to the shaft 29 with a square section 30. Furthermore, the shaft 29 is provided with a collar 31 at its end.
  • the plug 15 is provided with a corresponding round and square bore in the region of the section 30, the square section 30 guiding the piston 3 in the corresponding square bore of the plug 15 against rotation.
  • the pressure medium space in the cylinder 4 between the piston 3 and the plug 15 is closed by the seals 32 and 33.
  • the axial movement of the piston 3 is limited, on the one hand, by its stop on the plug 15 and, on the other hand, by the collar 31 on the piston shaft 29, by the collar 31 striking the rear face 34 of the plug 15.
  • the collar 31 on the piston shaft 29 can be axially adjustable, whereby the stroke of the piston 3 limited by the stops is also adjustable.
  • the stroke position of the piston 3, however, is adjustable by the previously described adjustment of the yoke plate 17 by turning the nuts 20 on the threaded shafts 14 of the spindles 13.
  • the plug 15 is drilled out from the rear end face to a cylinder space 35.
  • piston-cylinder units 40 are arranged between the flange 8 of the cylinder 4 and the yoke plate 17, by means of which the constant contact of the threaded nuts 20 on the threaded shaft 14 is maintained in the working pressure direction in order to support the stopper 15 without play guarantee.
  • a protective jacket 41 is placed on the piston 3 and surrounds the cylinder 4 with little play on the outside (see in particular FIG. 3). Compressed air is blown into the protective jacket 41, which emerges at the annular gap 42 between the protective jacket 41 and the cylinder 4 and thus prevents the ingress of dirt into the space 43 covered by the protective jacket 4.
  • each tappet or piston 3 is connected on the head side to a tappet head 44.
  • a guide groove 45 is machined, in which a cross piece 46 is slidably guided in the working plane transversely to the longitudinal axis of the workpiece.
  • the plunger 3 with its plunger heads 44 together with the cross pieces 46 form the tools 2 supporting supports.
  • grooves 47 are connected to the plunger head 44 strips 50 and in the grooves 48 connected to the cross piece 46 strips 51 are inserted, the strips 50 and 51 are provided on their facing surfaces with fine teeth 52 which are in engagement with each other.
  • a toothed rack 53 is inserted into the groove 49 and fastened in it.
  • a pinion 54 which is connected to one end of a shaft 55, engages in this toothed train 53.
  • the shaft 55 is rotatably mounted in a bearing bush 56 in the tappet head 44, passes through the tappet or piston 3 and piston shaft 29 in an axial bore 57 and is provided at its other end with a splined toothing 58 with which it engages in the correspondingly toothed bore a worm wheel 59 engages in a rotationally fixed but axially displaceable manner.
  • the worm wheel 59 and an associated worm shaft 60 are mounted in a gear housing 61 connected to the yoke plate 17 and can be driven by a drive (not shown).
  • clamping elements are provided which consist of a clamping bolt 62, a piston 63 and a nut 64 as the bundle of the clamping bolt 62 which surrounds the plunger head 44, the cross piece 46 and a spring 65.
  • the crosspiece 46 which is displaceable relative to the plunger head 44, is provided with slots 66 in the direction of displacement, in which two-part clamping blocks 67 can be displaced.
  • the springs 65 formed from a package of disc springs, which are supported in the plunger head 44, press against the pistons 63 of the clamping bolts 62 via collar bushings 68, so that the plunger head 44 and crosspiece 46 are braced against one another via the nuts 64 and clamping stones 67.
  • the crosspiece 46 By acting on the pistons 63 in the cylinders 69 connected to the plunger head 44, the crosspiece 46 is pushed by the plunger head 44 by the plunger head 44 so far that the teeth 52 on the pairs of strips 50, 51 come out of engagement, while the Cross piece 46 remains guided in the guide groove 45, for which purpose the guide groove 45 is held sufficiently deeper than the toothing 52 and the collar bushes 68 find a corresponding stroke limitation in the offset bores accommodating the spring assemblies 65.
  • the crosspiece 46 can then be adjusted relative to the plunger head 44 by means of the drive via the worm shaft 60, the worm wheel 59, the shaft 55, the pinion 54, and the toothed rack 53.
  • a valve (not shown) is opened, through which compressed air enters the closed gear housing 61 and from there through the bore 57 and branch bores 70 into the gap formed between the plunger head 44 and the crosspiece 46 which is being deposited, exits there and preventing dirt (sinter and the like) from entering the gap.
  • Tools 2 are interchangeably connected to cross piece 46.
  • the largest cross section (Q) to be forged is determined by the width of the tools 2, as shown in FIGS. 1 and 3 in dotted lines.
  • Smaller cross-sections such as the square cross-section (q) shown in full lines or a rectangular cross-section shown in FIG. 1a, require the crosspieces 46 to be displaced with the tools 2, so that the working surfaces of one tool 2 each have the unused tool width with the side surface each intersect an adjacent tool 2, the lateral offset (V) being half the difference between the full tool width and the used tool width.
  • the setting of the tools 2 to a specific cross-section must go hand in hand with the setting of the plunger or piston 3 to the specific cross-sectional dimension as the internal dimension of the stroke position by which the approximation of opposite tools 2 is determined.
  • the drives 28 for the stroke position adjustment and the drives via the worm shafts 60 for the lateral displacement (V) of the cross pieces 46 with the tools 2 are coupled to sensors for displaying the respective setting of the stroke position and the offset (V) (actual value). Automation can also take place via process computers via setpoint transmitters with predefined or preprogrammed setpoints; including mutual locking of mutually exclusive operations and settings.
  • the plungers are designed as cylinders 72, one of which is shown in FIG. 6.
  • the cylinders 72 are guided in the machine frame 73 in guide bushes 74 on the outside of round cylinders 72, with the guide bushes 74 taking the place of outside, non-circular flattened cylinders, guide plates of appropriate shape.
  • Each cylinder 72 forms a functional unit with a piston 75, the piston 75 being supported on a yoke plate 76.
  • the adjustment of the yoke plate 76 relative to the machine frame 73 is the same as that of the yoke plate 17 relative to the machine frame 5 in the first exemplary embodiment, the corresponding parts being identified identically, so that reference is made to their description in the first exemplary embodiment.
  • the piston 75 is designed as an annular piston and the cylinder 72 is accordingly provided with a shaft 77 which passes through the annular piston 75. At its end, the shaft 77 is provided with a traverse 78. On the yoke plate 76 with the piston 75, a plate 79 is placed, which is provided with cylinder bores 80. Pistons 81 in the cylinder bores 80 can be acted upon to retract the cylinder 72 and the working stroke of the cylinder 72 is limited on the one hand by the annular piston 75 and on the other hand by the pistons 81.
  • bushings 82a, b, and c are provided between the annular piston 75 and the cylinder 72 with a shaft 77, and sealing rings 82d and e are provided for sealing.
  • the design of the piston 75 as an annular piston and the shaft 77 offer the possibility of a tool adjustment through a bore 83 in the shaft 77.
  • a shaft 84 is provided which can be rotated and locked via a worm drive 85.
  • a pinion 84a connected to the shaft 84 is in engagement with a rack 86 in the cross piece 89.
  • the cross piece 89 carrying a tool 87 is fastened to a head piece 90 by means of clamping devices 88, the head piece 90 being connected to the Cylinder 72 is connected.
  • clamping devices 88 are released, the tool 87 can be adjusted transversely to the ram axis with its cross piece 89 on the head piece 90 in the working plane.
  • the plungers are designed as cylinders 91, as shown in FIGS. 7, 8 and 9.
  • Each cylinder 91 is guided in the machine frame 92.
  • double-acting pistons 93 are provided, which are connected to the yoke plates 95 via piston rods 94.
  • each cylinder 91 is closed off by a cover 96 towards the piston rod 94, the cover 96 also limiting the stroke of the cylinder 91 to the working stroke.
  • the stroke position is adjusted via the yoke plate 95 in a manner similar to that in the first and second exemplary embodiments.
  • the ring gear 22 can be driven and fixed by motors 28a via pinions 20a.
  • a tool adjustment by a centrally arranged shaft as in the first and second embodiment would be possible - for this purpose the piston 93 would have to be extended with a pin into a bore penetrating the bottom of the cylinder 91 and the cylinder 91 to 7, the tool adjustment is provided by two external shafts 97, which are mounted in bearings 98 fastened to the yoke plate 95 and follow the movement of the yoke plate 95.
  • a gear transmission 99 is placed on the yoke plate 95 and connects the shafts 97 driven by motors 102 via two intermediate gears 100 and gears 101.
  • the waves 97 are furthermore mounted in a head piece 103 to the cylinder 91 in bushes 104 and connected with pinions 105.
  • a cross piece 107 carrying the tool 106 which is guided in the head piece 103 and is detachably connected to the head piece 103 by a clamping device 108, is provided on both longitudinal sides with a toothing 109, in which the pinions 105 engage. When the clamping device 108 is released, the tool 106 can be adjusted with its cross piece 107 on the head piece 103 in the working plane transverse to the ram axis.
  • FIGS. 10 to 15 the boundaries of the largest and smallest cross section of a workpiece 111 to be forged can be seen from FIGS. 10 and 11.
  • the tools 112 are shown in the setting for the largest cross section to be forged in their outer stroke end position, that is to say in the fully open position and dotted in the setting for the smallest cross section to be forged in their inner stroke end position, that is to say with the caliber closed.
  • the tools 112 are carried by plungers 113, which are guided axially movably in cross pieces 114, while the cross pieces 114 are in turn guided in the working plane and at right angles to the axis of the plungers 113 in the machine frame 115.
  • the machine frame 115 is anchored to the foundation 117 with foot pieces 116.
  • the latter is provided with strips 118 and also with grooves 119 for receiving locking pieces 120.
  • the strips 118 and the strikers together form guide grooves in which the cross pieces 114 slide with strips 121 which are covered with wear plates.
  • Wedge pieces 122 are between the strips 121 and the strikers 120 are arranged.
  • the wedge pieces 122 are connected to spring-loaded tie rods and clamp the cross pieces 114 on their strips 121 in the guide grooves formed by the strips 118 and closing pieces 120, the wedge pieces 122 against the force of the springs of piston-cylinder units 123 for displacing the Cross pieces 114 can be solved.
  • the cross pieces 114 are displaced by spindle drives, consisting of spindles 124 and drive gears 125 with drive motors 126, the drive gears 125 being formed from the outside with worm teeth, which are rotated by worm shafts.
  • spindle drives consisting of spindles 124 and drive gears 125 with drive motors 126, the drive gears 125 being formed from the outside with worm teeth, which are rotated by worm shafts.
  • the plungers 113 have an I-shaped cross section and are guided in axially movable fashion in corresponding recesses 128 of the cross pieces 114 by plates 129, as can be seen in particular from FIGS. 11, 12 and 15.
  • the plunger 113 is driven by pistons 130 which are guided in cylinder 131.
  • the pistons 130 are provided with a collar 132 through which the stroke of the pistons 130 into the cylinder 131 is mechanically limited.
  • Each cylinder 131 is closed off by a cover 133 fastened to it with screws.
  • Each cover 133 is provided with a threaded pin 134, with which it is supported in a traverse 136 via a nut 135.
  • cylinders 141 are fastened, in which pistons 142 are guided, which act with their piston rods 143 via lugs 144 of the cylinders 131 on them, the cylinder covers 133 and the threaded pins 134 and the constant contact of the threaded pins 134 in the nuts 135 below Maintain exclusion of any game.
  • the piston 130 in the cylinder 131 is acted upon by an epee tube 145, which is attached to the cylinder cover 133 and is guided and sealed in the crossmember 136, and the pipeline 146.
  • the pistons 130 are provided with spherical pressure surfaces 147, with which they press onto the plunger 113 via pressure pans 148 which are likewise provided with spherical pressure surfaces.
  • the adjustability of the cross pieces 114 with the plungers 113 in the working plane at right angles to the plunger axis requires a coupling of the pistons 130 with the plungers 113 to compensate for this displacement.
  • the plungers 113 are connected to their end faces with two strips 149, so that there is a T-groove on the end face. T-shaped sliders 150 are inserted into this T-groove, which are connected to a ring 151 and, via this, to tie rods 152.
  • the tie rods 152 are passed through the cross member 136 and connected above the cross members 136 by yoke pieces 153.
  • the cross members 136 are provided with cylinder bores 154 in which pistons 155 are guided, which act on the tie rods 152 via the yoke pieces 153.
  • the pistons 155 When the pistons 155 are loaded, the T-shaped sliders 150 are clamped in the T-grooves between the strips 149, whereby the pistons 130 are connected to the plungers 113. At the same time, the pistons 155 serve as retraction pistons for the pistons 130. If the cross pieces 114 are to be adjusted with the plungers 113, the motor 126 must be actuated and at the same time the action on the pistons 155 is interrupted.
  • the setting of the tools 112 to a specific cross-section is accompanied by the setting of the plunger 113 with the pistons 130 and cylinder 131 to the corresponding stroke end position, which takes place above the motor 140.
  • the displacement of the associated tool 112 can be determined as the actual value via the worm shaft 124 as the encoder and can be set via the setpoint generator.

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  • Mechanical Engineering (AREA)
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Claims (18)

  1. Machine à forger comportant des outils (2; 87; 106; 112) disposés en X dans un plan de travail situé perpendiculairement à l'axe du système et déplaçables radialement à l'axe du système à chaque fois par une unité d'entraînement (3, 4; 72, 75; 91, 93; 130, 131) par l'intermédiaire d'un support formé à claque fois par un coulisseau (3; 72; 91; 113) et par une pièce en croix (46; 89; 107; 114), les outils (2; 87; 106; 112) qui, dans leur position de fin de course proche du centre, forment un calibre fermé étant agencés, par l'intermédiaire des supports, avec possibilité de déplacement dans le plan de travail, transversalement à leur direction de travail, et chaque outil (2; 87; 106; 112) ayant la partie de sa surface de travail excédant la dimension du calibre recouverte par une surface latérale d'un outil voisin (2; 87; 106; 112) et recouvrant lui-même, par l'une de ses surfaces latérales, la partie de la surface de travail de l'autre outil voisin (2; 87; 106; 112) excédant la dimension du calibre,
    caractérisée
    par le fait qu'à des unités cylindre-piston (3, 4; 72, 75; 91, 93; 130, 131) en tant qu'unités d'entraînement sont conjugués des moyens positionneurs (14, 19-28; 134; 135) pour le réglage et l'indication des positions de fin de leurs courses de travail, par le fait que les supports des outils (2; 87; 106; 112) sont munis de dispositifs positionneurs (53-60; 84-86; 97, 99-102, 105, 109; 124-126) qui fixent le déport d'outil dans le plan de travail, transversalement à l'axe des unités cylindre-piston (3, 4; 72, 75; 91, 93; 130, 131), et par le fait que le déplacement transversal des outils en fonction du réglage des positions de fin de course s'effectue avec une ampleur telle que l'arête d'outil formée par la surface de travail d'un outil (2; 87; 106; 112) et par sa surface latérale tournée vers la surface de travail d'un outil voisin (2; 87; 106; 112) soit déportée transversalement hors de l'axe central de son unité cylindre-piston (3, 4; 72, 75; 91, 93; 130, 131), d'une valeur identique à celle dont l'outil voisin (2; 87; 106; 112), recouvrant par sa surface de travail la surface latérale du premier outil, s'approche de l'axe du système lors de la position de fin de course, réglée pour le parcours de forgeage, de son unité cylindre-piston (3, 4; 72, 75; 91, 93; 130, 131).
  2. Machine à forger selon revendication 1,
    caractérisée
    par le fait que des pièces en croix (46; 89; 107) équipées d'outils (2; 87; 106) sont guidées dans des têtes de travail (44; 90; 103) des coulisseaux (3; 72; 91), avec possibilité de déplacement dans le plan de travail, perpendiculairement à l'axe des coulisseaux, et peuvent être immobilisées vis-à-vis des pièces de tête (44; 90; 103) par des éléments de serrage relâchables (62-69; 88; 108), tandis que des dispositifs positionneurs (53-60; 84-86; 97-109) pour le déplacement des pièces en croix (46; 89; 107) dans les pièces de tête (44; 90; 103) lorsque les éléments de serrage (62-69; 88;108) sont desserrés, sont agencés de manière à opérer entre les pièces de tête (44; 90; 103) et les pièces en croix (46; 89; 107).
  3. Machine à forger selon revendication 2,
    caractérisée
    par le fait que des dispositifs d'entraînement et/ou d'indication pour les dispositifs positionneurs (53-60; 84-86; 97-109) sont agencés sur les extrémités des coulisseaux (3; 72; 91) éloignées des pièces de tête (44; 90; 103), et des organes d'accouplement (55; 84; 97) sont prévus entre ceux-ci, traversent les coulisseaux (3; 72;) ou sont agencés parallèlement aux coulisseaux (91).
  4. Machine à forger selon revendication 1, 2 ou 3,
    caractérisée
    par le fait que les coulisseaux sont réalisés en tant que pistons (3) et guidés dans des cylindres (4) liés au cadre de la machine (6), et le changement de position de levée s'effectue par des bouchons (15) déplaçables dans les cylindres (4) dont ils forment les fonds.
  5. Machine à forger selon revendication 4,
    caractérisée
    par le fait que les pistons (3) servant de coulisseaux sont munis de tiges (29) traversant les bouchons percés (15).
  6. Machine à forger selon revendication 1, 2 ou 3,
    caractérisée
    par le fait que les coulisseaux sont réalisés en tant que cylindres (72; 91) tandis que les pistons (75; 93) sont agencés avec possibilité de modification de position, sur le cadre (73; 92) de la machine, aux fins du réglage de position de levée.
  7. Machine à forger selon revendication 6,
    caractérisée
    par le fait que les cylindres (72) munis de tiges intérieures (77) sont des cylindres annulaires qui, par leurs tiges (77) traversent les pistons (75) percés en tant que pistons annulaires.
  8. Machine à forger selon revendication 5 ou 7,
    caractérisée
    par le fait que les tiges (29; 77) des pistons (3) ou cylindres (72) prévus en tant que coulisseaux (3; 72) sont percées axialement et reçoivent dans ces perçages (57; 83) les organes d'accouplement (55; 84) pour relier fonctionnellement les dispositifs positionneurs à leurs dispositifs d'entraînement et/ou d'indication.
  9. Machine à forger selon revendication 3 ou 8,
    caractérisée
    par le fait que les dispositifs positionneurs sont constitués par des crémailléres (53; 86; 109) liées aux pièces en croix (46; 89; 107), crémaillères dans lesquelles engrènent des pignons (54; 85; 105), et par le fait qu'il est prévu, en tant qu'organes d'accouplement (55; 84; 97), des arbres (55; 84; 97) liés aux pignons (54; 84a; 105), les arbres (55; 84; 97) passant par les trous centraux (57; 83) dans les coulisseaux (3; 72), ou latéralement le long des coulisseaux (91).
  10. Machine à forger selon l'une des revendications 2 à 9,
    caractérisée
    par le fait que des têtes de coulisseau (44; 90; 103) et des pièces en croix (46; 89; 107) sont mutuellement liées positivement lorsque les éléments de serrage sont fermés (62-69; 88; 108), du fait des dentures fines (52) mutuellement en prise, excluant le déplacement mutuel.
  11. Machine à forger selon revendication 10,
    caractérisée
    par le fait que les têtes de coulisseau (44; 90; 103) et les pièces en croix (46; 89; 107) sont munies de rainures correspondantes (47, 48) et de barrettes (50, 51) munies des dentures (52) et insérées dans les rainures.
  12. Machine à forger selon l'une des revendications 2 à 11,
    caractérisée
    par le fait qu'il est prévu, en tant qu'éléments de serrage, des boulons de serrage connus en soi (62), lesquels sont munis de collets (63, 64) arrêtant la pièce en croix (46), la tête de coulisseau (44) et un ressort (65), le collet (63) aménagé en tant que piston (63), surjacent au ressort (65), étant sollicité contre la force du ressort (65) et par conséquent de manière à relâcher le serrage, la sollicitation du piston (63) et le relâchement des éléments de serrage commandant en même temps un déverrouillage des entraînements (60, 28) pour le déplacement des pièces en croix (46) par rapport aux têtes de coulisseau (44) et pour le changement de position de levée.
  13. Machine à forger selon l'une des revendications 2 à 12,
    caractérisée
    par le fait qu'avec le desserrage des éléments de serrage (62-69) par sollicitation du piston (63) une soupape est ouverte qui laisse passer de l'air comprimé par l'interstice s'établissant entre pièce en croix (46) et tête de coulisseau (44) et empêche toute entrée de souillure dans l'interstice.
  14. Machine à forger selon revendication 1,
    caractérisée
    par le fait que les pièces en croix (114) sont guidées dans le cadre (115) de la machine, avec possibilité de changement de position dans le plan d'entraînement, Perpendiculairement à l'axe du coulisseau, et peuvent être immobilisées par rapport au cadre (115) de la machine par des éléments de serrage relâchables (122, 123), les dispositifs positionneurs (124-126) pour le déplacement des pièces en croix (114) dans le cadre de la machine (115) lorsque les dispositifs de serrage (124-126) sont relâchés étant agencés de manière à agir entre le cadre (115) de la machine et les pièces en croix (114), et les coulisseaux (113) équipés des outils (112) étant guidés avec possibilité de mouvement axial dans les pièces en croix (114), et étant liés chacun à une unité d'entraînement (130, 131).
  15. Machine à forger selon revendication 14,
    caractérisée
    par le fait que des unités cylindre-piston (130, 131) agencées radialement à l'axe du système sont prévues pour l'entraînement des coulisseaux (113), leurs cylindres (131) étant agencés fixes dans le cadre (115) de la machine, tandis que les pistons (130) sont liés aux coulisseaux (113) par des accouplements compensant le déplacement des pièces en croix (114) avec les coulisseaux (113) mais transmettant néanmoins les forces axiales des pistons (130) aux coulisseaux (113).
  16. Machine à forger selon revendication 15,
    caractérisée
    par le fait que les accouplements agencés entre les pistons (130) et coulisseaux (113) consistent chacun en une rainure en forme de T ou de queue d'aronde (149) dans la surface frontale du coulisseau, en pièces de glissement (150) en forme de T ou de queue d'aronde qui y sont guidées, et en tiges de traction (152) à tendre par l'intermédiaire de pièces transversales (153), par des pistons (155) guidés dans la traverse (136) dans des alésages cylindriques, ces tiges étant liées aux pièces de glissement (150), la sollicitation des pistons (155) étant interrompue pendant le déplacement des pièces en croix (114) par les dispositifs positionneurs (124-126), et les accouplements étant alors relâchés.
  17. Machine à forger selon l'une des revendications précédentes,
    caractérisée
    par l'utilisation d'un entraînement hydraulique connu en soi, dimensionné simplement pour la course de travail, au moyen d'unités cylindre-piston (3, 4; 72, 75; 91, 93; 131, 132), avec limitation mécanique de la course (31; 81; 96; 132) et des moyens positionneurs mécaniques, notamment des mécanismes à broche (14, 20; 134, 135) pour le réglage, déterminant la position de levée et la position de fin de course, des unités cylindre-piston (3, 4; 72, 75; 91, 93; 131, 132) en fonction de la position d'outil prédéterminée par le calibre considéré.
  18. Installation de forgeage selon l'une des revendications précédentes,
    caractérisée
    par le fait que les déplacements latéraux des pièces en croix (46; 89; 107, 114) par rapport aux têtes des coulisseaux (44; 72; 103), ou encore par rapport au cadre de la machine (135), et les positions de fin de course des coulisseaux (3; 72; 91; 113), sont mesurés et réglés en fonction d'une dimension de calibre introduite à chaque fois ou programmée par l'intermédiaire d'un calculateur de processus.
EP86117589A 1986-01-02 1986-12-17 Machine de forgeage Expired - Lifetime EP0228030B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86117589T ATE62838T1 (de) 1986-01-02 1986-12-17 Schmiedemaschine.

Applications Claiming Priority (12)

Application Number Priority Date Filing Date Title
DE3600018 1986-01-02
DE3600018 1986-01-02
DE3600178 1986-01-07
DE3600178 1986-01-07
DE3600690 1986-01-13
DE3600690 1986-01-13
DE3627843 1986-08-16
DE3627843 1986-08-16
DE3630170 1986-09-04
DE3630170 1986-09-04
DE3631439 1986-09-16
DE3631439 1986-09-16

Publications (3)

Publication Number Publication Date
EP0228030A2 EP0228030A2 (fr) 1987-07-08
EP0228030A3 EP0228030A3 (en) 1988-09-07
EP0228030B1 true EP0228030B1 (fr) 1991-04-24

Family

ID=27544414

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86117589A Expired - Lifetime EP0228030B1 (fr) 1986-01-02 1986-12-17 Machine de forgeage

Country Status (4)

Country Link
US (1) US4796456A (fr)
EP (1) EP0228030B1 (fr)
JP (1) JPH08273B2 (fr)
DE (1) DE3678918D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0260546A3 (en) * 1986-09-16 1988-09-07 Sms Hasenclever Maschinenfabrik Gmbh Forging machine
EP0549825A1 (fr) * 1991-12-30 1993-07-07 SMS Hasenclever GmbH Machine à forger
US5313816A (en) * 1991-12-30 1994-05-24 Sms Hasenclever Gmbh Forging machine with stroke adjustment means
US5582059A (en) * 1993-12-16 1996-12-10 Schubert; Peter Forging machine
DE102005012297B4 (de) * 2005-03-17 2007-06-14 Sms Meer Gmbh Schmiedemaschine
DE102017214961A1 (de) * 2017-03-22 2018-09-27 Sms Group Gmbh Radial-Schmiedeanlage

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4143175A1 (de) * 1991-12-30 1993-07-01 Hasenclever Maschf Sms Schmiedemaschine
ATE122941T1 (de) * 1993-12-16 1995-06-15 Hasenclever Maschf Sms Schmiedemaschine.
JPH07121429B2 (ja) * 1993-12-16 1995-12-25 エス エム エス ハーゼンクレヴァー ゲゼルシャフト ミット ベシュレンクテル ハフツング 鍛造機
EP0653258B1 (fr) * 1993-12-16 1995-05-24 SMS HASENCLEVER GmbH Machine à forger
DE4444493A1 (de) * 1993-12-16 1995-06-22 Hasenclever Maschf Sms Schmiedemaschine
US5842267A (en) * 1994-12-30 1998-12-01 Black & Decker, Inc. Method and apparatus for forming parts of a predetermined shape from a continuous stock material
US6290439B1 (en) 1994-12-30 2001-09-18 Black & Decker, Inc. Method and apparatus for forming parts from a continuous stock material and associated forge
AT404441B (de) * 1996-09-17 1998-11-25 Gfm Holding Ag Schmiedemaschine
EP1005933A1 (fr) * 1998-09-22 2000-06-07 SMS EUMUCO GmbH Machine de forgeage à poinçons multiples
JP2000197942A (ja) * 1998-10-30 2000-07-18 Toyota Motor Corp 鍛造加工解析方法およびその実行プログラムを記録した媒体
US20070271990A1 (en) * 2006-05-26 2007-11-29 Young Thomas M Shutter-Type Crimper
CN105650053A (zh) * 2014-11-28 2016-06-08 富泰华工业（深圳）有限公司 气缸
CN107838355B (zh) * 2017-11-02 2019-05-24 太原科技大学 一种用蜗杆轴向运动调速与制动的径向锻造操作机
CN107876682B (zh) * 2017-11-02 2019-05-28 太原科技大学 一种用于径向锻造操作机的传动和制动装置
CN110548827B (zh) * 2018-05-31 2021-11-12 宝武特种冶金有限公司 一种提高镍基耐蚀合金锻坯成材率的锻造方法
IT201900012960A1 (it) * 2019-07-26 2021-01-26 Mecolpress S P A Apparecchiatura per lo stampaggio di materiali.

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DE64549C (de) * Frau M. GAWRON in Stettin Reibscheibenkupplung mit Bremse
DE325985C (de) 1918-12-25 1920-09-22 Carl A Achterfeldt Schmiedemaschine mit drei oder mehr in einer Ebene zentral wirkenden Arbeitsbacken
DE449558C (de) * 1926-05-07 1927-09-15 Johannes Ingrisch Dipl Ing Presse zur Verdichtung oder Querschnittsaenderung von Koerpern aus Metall oder anderen Stoffen
DE1050154B (de) * 1956-03-19 1959-02-05 Champigny Seine Rene Etienne Bujon (Frankreich) Hämmermaschine zum Herstellen von Profilstäben
DE1094075B (de) * 1959-02-04 1960-12-01 Fertigungstechnik Und Maschb G Schmiedemaschine zum Vierkantschmieden
DE1271513B (de) * 1962-05-30 1968-06-27 Stevens & Bullivant Ltd Haemmermaschine mit einem umlaufenden Schwungrad
DE1953867U (de) 1966-09-30 1967-01-19 Sack Gmbh Maschf Schmiedemaschine.
DE1301790B (de) 1966-09-30 1969-08-28 Sack Gmbh Maschf Schmiedemaschine
AT292963B (de) 1968-11-08 1971-09-27 Stefan Sowitsch & Co Ing Gleitfangvorrichtung für Fahrstühle
DE1812169A1 (de) * 1968-12-02 1970-06-18 Sack Gmbh Maschf Schmiedemaschine
DE1908361A1 (de) * 1969-02-20 1970-09-10 Sack Gmbh Maschf Schmiedemaschine
DE1908362A1 (de) * 1969-02-20 1970-09-10 Sack Gmbh Maschf Schmiedemaschine mit verstellbaren Schmiedesaetteln
DE1953123A1 (de) * 1969-10-22 1971-04-29 Horst Schenk Werkzeug fuer Schmiedemaschine
DE1963979A1 (de) * 1969-12-20 1971-06-24 Demag Hydraulik Gmbh Hydraulische Schmiedemaschine fuer das Warmschmieden stab- und stangenfoermiger Werkstuecke
JPS5417196B2 (fr) * 1972-08-31 1979-06-28
AT329349B (de) * 1973-11-15 1976-05-10 Gfm Fertigungstechnik Schnellaufende kurzhub-schmiedepresse
SE423604B (sv) 1978-04-18 1982-05-17 Hakan Sallander Anordning for fastspenning av ett tvadelat verktyg i en maskin sasom en press eller liknande
JPS62229946A (ja) * 1986-03-31 1987-10-08 Toshiba Corp ドライエツチング装置

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0260546A3 (en) * 1986-09-16 1988-09-07 Sms Hasenclever Maschinenfabrik Gmbh Forging machine
EP0549825A1 (fr) * 1991-12-30 1993-07-07 SMS Hasenclever GmbH Machine à forger
US5313816A (en) * 1991-12-30 1994-05-24 Sms Hasenclever Gmbh Forging machine with stroke adjustment means
US5582059A (en) * 1993-12-16 1996-12-10 Schubert; Peter Forging machine
DE102005012297B4 (de) * 2005-03-17 2007-06-14 Sms Meer Gmbh Schmiedemaschine
DE102017214961A1 (de) * 2017-03-22 2018-09-27 Sms Group Gmbh Radial-Schmiedeanlage
DE102017214961B4 (de) * 2017-03-22 2021-06-10 Sms Group Gmbh Radial-Schmiedeanlage

Also Published As

Publication number Publication date
DE3678918D1 (de) 1991-05-29
US4796456A (en) 1989-01-10
JPS63238940A (ja) 1988-10-05
EP0228030A2 (fr) 1987-07-08
JPH08273B2 (ja) 1996-01-10
EP0228030A3 (en) 1988-09-07

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