EP0978332B1 - Multi-cylinder metal-extrusion press - Google Patents

Abstract

The invention relates to a metal extrusion press provided with two or more cylinders (32), the piston rods (33) of which are connected to the press pistons (31) and are connected to the counter beam (5) to the cylinder beam (1). In order to be able to run the press at high speed while idling and when retracting and to be able to cope with the large volume flows that occur, the cylinder part spaces (32H, 32R) according to EP 0 822 017 B1 are on both sides of the plunger (31) by short-circuit lines (41, 42) connectable. The object of the invention is to improve a metal extrusion press of this type by structurally simple, functional and stress-oriented training and assignment of its components. To achieve this object, the invention provides a combination of features in which, by the arrangement of packing elements (40) or spring-supported separating pistons in the cylinder subspaces (32H, 32R), beyond the effective surfaces of the plunger (31), storage spaces (32R) for receiving the Oil volumes displaced by the plunger (31) during their return stroke. In the case of packing bodies (40) connected to the plunger (31) between their plunger (31) and the cylinder end (38), these are provided with at least one radial freedom compensating for an angular deviation between the plunger axis and the cylinder axis. Together with a stationary arrangement of the cylinder spar (1) as a carrier of the fixed pressing tool (11), the effects of elastic deformations of the components, including the line connections of the pressure medium supply, are minimized under the operating load. <IMAGE>

Description

Metal extrusion presses are mostly designed as frame presses and consist of a cylinder spar, a counter spar, these tie rods connecting to a frame (Pillars) and one in the frame of one in the cylinder of the cylinder beam running plunger movable barrel. In the direct pressing process is one Die and a sensor for a block to be pressed on the counter beam supported, while a press die pressing out the block with the Barrel is moved by the piston. In the indirect pressing process is on the counter beam a die stamp supported while the transducer with a Sealing disc receives a block to be pressed and with the Barrel is moved by the plunger.

In order to achieve a high degree of utilization of the presses, the non-productive times have to be be minimized. Idling and retreat should therefore be as large as possible Speed. Here there are large volume flows between Cylinder and oil tank to cope with high flow speed, being turbulent flows and, as a result, air pockets in the oil and foam formation can occur, which must be countered by the fact that the oil lines as possible short and the cross sections of the oil lines and the valves kept large (low Δ p) and filters are also large. To keep the oil lines short can be oil tank, drive and control as close as possible to the press cylinder, at lying metal extrusion presses arranged above the press cylinder, which is true has the advantage of taking up little space, but is not always desirable.

With a distribution of two that is not absolutely necessary due to the size of the pressing force or more plungers and cylinders and by inserting the plungers with piston rods are provided in the place of the tie rods (columns) in the classic You have to join the frame design by connecting them to the counter beam one suitable for direct and indirect pressing Metal extrusion press reduces the structural effort of the classic design because this eliminates the need for a special spar and the overall length of the Press could be reduced accordingly (hydraulic presses and hydraulic fluid systems, Volume 3, Figs. 83 and 84, pages 93 to 95, by Ernst Müller, Springer-Verlag Berlin / Göttingen / Heidelberg, DE-PS 510 895), but this has Press type of the "frameless" design found no widespread use.

A "frameless" metal extrusion press has now become known from EP 0 822 017 B1, in which the coping with large volume flows is achieved in that the two or more plungers with their cylinders penetrating on both sides Provide piston rods of the same diameter and the piston rods on both sides are sealed off from the cylinders, so that cylinder subspaces on both sides same effective area, which by a to the working stroke by a switchable check valve closable short-circuit line are interconnected. For a quick return stroke and a fast forward run are with this press special piston-cylinder units are provided. Over which the cylinder subspaces short-circuit line connecting both sides of the plunger is a fast one Transition of the oil from one cylinder part to the other with little Flow resistance possible, with a corresponding dimensioning of the Short-circuit lines and the switchable check valves arranged in them without Difficulty can be met. It should be the flow rate Do not exceed 8 m / sec in the short-circuit line and 12 m / sec in the shut-off valve.

A disadvantage of the "frameless" metal extrusion press according to the prior art is that their counter spars are stationary and the heavier cylinder spars are arranged displaceably, so that the masses to be moved are correspondingly large are, and that the supply of pressure medium to the cylinders with their plunger over whose piston rods, in the case of the older state of the art, via the Piston rods under compressive force must take place.

With the plungers with their cylinders penetrating on both sides, against the Cylinder-sealed piston rods according to EP 0 822 017 B1 each have three Sealing and guide points. Cylinder beam and counter beam can be relative are designed to be rigid, but their bending can be done under the pressing force do not rule out entirely and their bending is transferred to that of the frameless metal extrusion presses to replace the piston rods, so that another disadvantage is the high lateral forces in the sealing and Leadership positions.

Starting from "frameless" metal extrusion presses in the preamble of the claim 1 in detail outlined design, the object of the invention is a structurally simple, functional and stress-oriented training and To achieve the allocation of their components. The invention provides a solution to this problem the combination of features forming the characterizing part of claim 1 or claim 2 before, which is common that by the assignment of packing (Claim 1) or spring-supported separating piston (claim 2) to the plunger storage spaces in the cylinder subspaces beyond the effective surfaces of the ram to accommodate the oil volumes displaced by the plungers during their return stroke exist, the packing connected to the plunger (claim 1) between their plunger and the cylinder end with at least one Compensate for angular deviations between the ram axis and the cylinder axis radial freedom are provided. Together with the fixed arrangement of the Cylinder bars as a carrier of the stationary press tool are the effects the elastic deformation of the components including the pipe connections the pressure medium supply is minimized under the operating load.

According to the invention between the ram, packing, cylinder and cylinder end Radial freedom to be provided can be achieved with a cover that closes the cylinder penetrating filler and seal provided between cover and filler for example, by connecting the packing with the ball joint Plunger, or caused, for example, that the seal in the Cover is kept limited radially movable.

An advantageous solution with regard to the overall length of the metal extrusion press results by arranged as a packing between the plunger and the cylinder cover, with these end-connected telescopic tubes are provided, the middle Outside diameter corresponds to the diameter of the piston rods of the ram. A particular structural advantage is an apprenticeship, in which after another Feature of the invention, the first inner telescopic member of a plunger and Piston rod extending pin is formed, and after another, further Feature of the invention, the last outer telescopic member from one in the cylinder cover inserted pipe section formed and the cylinder cover as Hood is formed, the tube and the cavity of the hood taken together one corresponding to the insertion depth of the penultimate telescopic member Have depth.

The drawings show exemplary embodiments of the invention.

Figur 1

in einer teilweise geschnittenen Ansicht rechtwinklig zur Hauptachse "x-x" der Metallstrangpresse und dazu in Schnitten quer zur Hauptachse "x-x" nach den in der Figur 1 eingetragenen Schnittlinien in

Figur 2

nach Schnittlinie II-II, in

Figur 3

nach Schnittlinie III-III, in

Figur 4

nach Schnittlinie IV-IV, in

Figur 5

nach Schnittlinie V-V, in

Figur 6

nach Schnittlinie VI-VI dargestellt.

Figur 7

zeigt eine Abwandlung des ersten Ausführungsbeispiels in einem Ausschnitt "A" der Figur 1 und in

Figur 8

eine weitere Abwandlung des ersten Ausführungsbeispiels im Ausschnitt "A" der Figur 1.

Figur 9

zeigt eine besonders vorteilhafte Abwandlung des ersten Ausführungsbeispiels im Ausschnitt "A" der Figur 1 in größerem Maßstab.

Figur 10

zeigt ein zweites Ausführungsbeispiel in einem dem Ausschnitt "A" der Figur 1 entsprechenden Ausschnitt.

A first embodiment is shown in

Figure 1

in a partially sectioned view perpendicular to the main axis "xx" of the metal extrusion press and also in sections transverse to the main axis "xx" according to the cutting lines in FIG

Figure 2

according to section line II-II, in

Figure 3

according to section line III-III, in

Figure 4

according to section line IV-IV, in

Figure 5

according to section line VV, in

Figure 6

shown along section line VI-VI.

Figure 7

shows a modification of the first embodiment in a section "A" of Figure 1 and in

Figure 8

a further modification of the first embodiment in section "A" of Figure 1.

Figure 9

shows a particularly advantageous modification of the first embodiment in section "A" of Figure 1 on a larger scale.

Figure 10

shows a second embodiment in a section corresponding to section "A" of Figure 1.

The metal extrusion press of the embodiment shown in Figures 1 to 6 consists of a cylinder spar 1 and a base frame firmly connected to it 2, which is provided on the top with guide beads 3 for guiding a block sensor 4 and a running / counter beam 5. With the block sensor 4 and the For this purpose, spars 5 are connected to actuating devices 6 which are mounted on sliding plates 7 Wear running shoes 9 lying on or against sliding plates 8. About the Adjustment devices 6 are the block sensor 4 and the walking beam 5 on the Main axis "x-x" of the press can be aligned.

The cylinder bar 1 is provided with a tool guide 10 for receiving exchangeable Tools 11. The tool support plate 12 has an opening 13 and the cylinder spar 1 is provided with a through opening 14 for the tool 11 shaped strand. In the cylinder spar 1 there is a shaft 15 via a lever 16 by a piston-cylinder unit 17 pivotally mounted, one on the end face of the tool 11 carries pivotable shearing knife 18 with which completed pressing process, the baling residue from the strand and from the tool 11 separated can be. Furthermore, piston-cylinder units 19 are in the cylinder spar 1 used, the piston rods 20 of the displacement of the block sensor 4 and the pressure on the tool 11 serve.

Firmly connected to the base frame 2 or in this with the block sensor 4 A block loader 21 can be displaced parallel to the main axis x-x by means of piston-cylinder units 22 can be pivoted about an axis 23 as soon as or as long as it is sufficient There is a distance between the block sensor 4 and the walking beam 5. The Barrel 5 is connected to a piston-cylinder unit 24 about an axis 25 pivotable bracket 26 provided for inserting a block in the Main axis x-x is pivoted out so that a bore 27 is exposed in the spar 5, by means of the piston rod 28 of a piston-cylinder unit 29 from Block loader 21 in the main axis x-x introduced block in the bore of the Block pickup 4 can be pushed. After a block has broken in, the piston rod 28 is withdrawn and overlaps in time herewith the block loader 21 swung out and with the direct pressing process a press die 30 provided support arm 26 pivoted into the main axis x-x When the shear knife 18 is pivoted out, the pickup holder 4 is connected to the Pickup by appropriately loading the piston-cylinder units 19 pressed against the tool 11.

The pressing of a block is carried out by pressurizing the ram 31 in cylinders 32 held by the cylinder spar 1, for which purpose the piston rods 33 Plunger 31 reach into the barrel 5 and are connected to it. The Pistons 31 with their piston rods 33 are hollow drilled over part of their length Dip cylinder bores 34 into plungers 35, which attach to cylinders 32 supporting covers 36. The action on the plunger 35 takes place through the plunger 35 through holes 37, which the Plunger 31 and with them on the piston rods 33 of the barrel 5 in the Move back to the starting position. By means of the piston-cylinder units 19 Pick-up holder 4 removed from the tool 11 and the press residue exposed, which then by pivoting the shear knife 18 from the tool 11 and the end of the strand is separated in the tool 11. This overlaps with the Support arm 26 swung out with the punch 30 and the one with a following Block loaded block loader 21 swung in. On the base frame 2 are about one Bridge piece 38 piston-cylinder units 39 supported, the pistons can be acted upon are in order to be able to move the walking beam 5 in the idle stroke / rapid traverse.

To minimize the idle times in the operation of the metal extrusion press, it is necessary Return stroke and the idle stroke of the press at the highest possible speeds drive while coping with large volume flows, what about creating equally large stroke volume in the cylinders on both sides of the main plunger and a possibility for switchable connections of the two-sided cylinder subspaces 32H and 32R is reached. The free, the active surfaces of the plunger For this purpose, cylinder subspaces 32R facing away are provided with packing elements which form the free cylinder subspaces 32R to approximately the same size effective areas as that of Limit plunger 31, and the plunger 31 are with several through holes 41 provided, via which the cylinder sections 32H and 32R on both sides of the Plunger 31 via switchable arranged in the through holes 41 Check valves 42 (two-way cartridge valves according to DIN 24342, also as logic or Cartride valves known) are connected.

In the exemplary embodiment according to FIGS. 1 to 6, the packing is from several telescopic links 40/1, 40/2, 40/3, 40/4 composite telescopic tubes 40 formed, the first telescopic member 40/1 with the associated Main press piston 31 with piston rod 33 and its last telescopic member 40/4 with the cover 36, which closes the associated cylinder 32, the average diameter of the telescopic members 40/1, 40/2, 40/3 and 40/4 the Diameter of the piston rod 33 corresponds. The connection of the telescopic links 40/1, 40/2, 40/3 and 40/4 with each other leaves a slight angular deviation of their Center axes to each other, so that a radial freedom between plunger 31st and cylinder end 36 is given by which an angular deviation between the Axes of the cylinder 32 and the axes of the plunger 31 are balanced can. With 43a is the pressure medium supply line to act on the plunger 31 in Cylinder 32 to the working stroke of the press, with 43b the pressure medium supply to Actuation of the plunger 35 in the cylinder bore 34 for the return stroke of the Press, with 44 a derivation of fluid leakage from the telescopic tube 40 and at 45 a pressure medium compensation line for volume differences between the Cylinder sub-spaces designated 32H and 32R, whereby via the pressure medium compensation line 34 during the press stroke, the amount of oil displaced from the cylinder part space 32R in an oil tank is derived.

In the modification of the embodiment shown in FIG Figures 1 to 6 are inserted into the cylinder spar 1 cylinder 46, the plunger 47 are provided, the piston rods 48 of which are connected to the counter beam 5. With each plunger 47 a filler 49 is connected via a ball joint 50. The Packing bodies 49, which have the same outer diameter as the piston rods 48, penetrate the sealing the cylinder 46, provided with sealing rings 51 Cover 52. The ball joints 50 give radial freedom with which one Angular deviation between the cylinder axis and the ram axis is compensated.

In a further modification shown in FIG. 8, the cylinder spar 1 Cylinder 53 used, which are provided with plungers 54, the piston rods 55th are connected to the counter beam 5. The plunger 54 are with threaded pin 56th provided on the packing 57 of the same outer diameter as the piston rods 55 are attached. The fillers 57 penetrate the cylinders 53 that close off Lid 58. For sealing against the cylinder 53 is on the filler 57 Sealing ring 59 is placed which is provided with radial clearance to cover 58 and has a flange 60 with which the sealing ring 59 between the cover 58 and a cap ring 61 is axially held and sealed.

A structurally particularly advantageous modification is shown in FIG the cylinder 62 inserted into the cylinder spar 1 shows one with a piston rod 63 connected plunger 64 receives. The cylinder 62 is closed from a cover 65 which is provided with a hood 66. Inserted in the lid 65 and held by the hood 66 is an outer telescopic tubular member 67/1 Telescopic tube 67, which has two further telescopic tube members 67/2 and 67/3, the latter sealingly axially displaceable on a pin 68 of the piston rod 63 is. The pin 68 forms together with the telescopic tube members 67/1, 67/2 and 67/3 a packing, which is located on the back to the active surface of the plunger 64 Cylinder subspace 62R on a corresponding to the effective surface of the plunger 64 Effective area is restricted. The plunger 64 has a plurality of through bores 69 provided, in which controllable check valves 70 are arranged, which open one Connect the cylinder sections 62H and 62R and make a quick one Exchange of the two-sided volumes in rapid traverse or when the press returns allow, while the check valves 70 are closed for the press stroke. The control of the shut-off valve 70 takes place via a pilot valve 71, which is shown in FIG Switch position shown via a control line 72, an epee tube 73, which in a bore 74 in the piston rod 63 and the pin 68 dips and via a Branch line 75 acts on the valve lifter 76 of the check valve 70 and in Closing position brings and holds. The blocking valve 70 is acted upon by the line 72a, via which the pilot valve 71 to a separate oil supply from a Control oil circuit is connected. When switching the pilot valve 71 Control line 72, the epee tube 73, the branch line 75 and thus the valve lifter 76 depressurized, so that the closing valve 70 in both flow directions can open. To compensate for small volume differences between the cylinder subspaces 62H and 62R is the cylinder compartment 62R to one Expansion tank 77a connected. The interior of the telescopic tube 67 is with a vent 78 and a termination 79 for leak oil. The construction of the plunger 64 to the press stroke is carried out by the pumps 80 and the branch line 81 in cylinder 62. The corresponding amount of oil in cylinder chamber 62R is determined by the Control block 77 led to the tank. The epee tube 73 is in this embodiment only as part of the control line for actuating the check valve 70 provided and the return stroke is via double-acting piston-cylinder units causes, corresponding to the piston-cylinder units 39 in the embodiment are arranged according to Figure 1.

Figure 10 shows a second embodiment in a detail, while in remaining of this embodiment that shown in Figures 1 to 6 Embodiment corresponds, wherein FIG. 10 is one of the cylinder spars 1 inserted cylinder 82 shows that receives a plunger 84 with piston rod 83. The cylinder 82 is closed by a cover 85 on which a Epee tube or plunger 86 supports, which or the sealing in a bore 87th immersed. In the cylinder 82 and on the epee tube or the plunger 86 is after sealed inside and outside a separating piston 88, the port 89 below Standing gas pressure follows the plunger 84 at a distance that the oil volume corresponds to that between the cylinder part space 82H and the cylinder part space 82R on the return stroke of the plunger 84 or on the outward stroke of the plunger 84 in Rapid traverse via through holes 90 with switchable check valves 91 in Plunger 84 changes, the separating piston 88 executes a stroke that leads to the stroke of the plunger 84 in the area ratio of the main and rear Prepress piston ring surfaces (main side = ring surface in the cylinder part space 82H, rear side = Ring area in the cylinder sub-space 82R) is inversely proportional. The press stroke The amount of oil displaced from the cylinder part space 82R is fed through an epee pipe 92 and a line 93 provided with a pressure relief valve in the oil tank derived.

Claims (12)

1. Multicylinder metal extrusion press, the press pistons (31; 47; 54; 64) of which, which are guided in the cylinders (32; 46; 53; 62) of a cylinder cross member (1) are connected by way of their piston rods (33; 48; 55; 63) with a counter cross beam (5) and in which the cylinder cross member (1) and the counter cross member (5) are movable relative to one another for the pressing process by loading of the press pistons (31; 47; 54; 64) and thus the tools (11, 30) supported by the cylinder cross member (1) on the one hand and the counter cross member (5) on the other hand, namely die with ingot receiver and press ram in direct pressing and die ram and ingot receiver with lock piece in indirect pressing, wherein the cylinder partial spaces (32H, 37R; 62H, 62R) separated relative to one another by the press pistons (31; 47; 54; 64) are connectible together by a valve (42; 70) opening in the return stroke of the press and separate piston-cylinder units are provided for the return stroke and the forward stroke in rapid transit, characterised in that the cylinder cross member (1) is arranged to be stationary and is constructed as a support of the fixed press tool (11), i.e. the die in direct pressing and die ram in indirect pressing, and that the press pistons (31; 47; 54; 64) arranged in the cylinders (32; 46; 53; 62) of the cylinder cross member (1) are connected on the side opposite their work surface with respective filler bodies (40; 49; 57; 67) which limit the free cylinder space (32R, 62R) to an effective area corresponding with the effective area of the press piston (31; 42; 54; 64) and which bridge over the spacing between the press pistons (31; 47; 54; 64) and the cylinder closures (36; 52; 58; 65) in the form of a cap or annular cap, and that the filler bodies (40; 49; 57; 67) are linked with at least one radial freedom, which compensates for an angular deviation between cylinder axis and press piston axis, between press piston (31; 47; 54; 64) and cylinder closure (36; 52; 58; 67).
2. Multicylinder metal extrusion press, the press pistons (84) of which, which are guided in the cylinders (82) of a cylinder cross member (1), are connected by way of their piston rods (83) with a counter cross beam (5) and in which the cylinder cross member (1) and the counter cross member (5) are movable relative to one another for the pressing process by loading of the press pistons (84) and thus the tools (11, 30) supported by the cylinder cross member (1) on the one hand and the counter cross member (5) on the other hand, namely die with ingot receiver and press ram in direct pressing and die ram and ingot receiver with lock piece in indirect pressing, wherein the cylinder partial spaces (84H, 84R) separated relative to one another by the press pistons (84) are connectible together by a valve (91) opening in the return stroke of the press and separate piston-cylinder units are provided for the return stroke and the forward stroke in rapid transit, characterised in that the cylinder cross member (1) is arranged to be stationary and is constructed as a support of the fixed press tool (11), i.e. the die in direct pressing and die ram in indirect pressing, and that separating pistons (88) are arranged in the cylinders (82) to be standing under gas pressure / spring pressure on the side remote from the work surface of the press pistons (84), travel after the press pistons (84) in their return stroke and form between themselves and the press pistons (84) reservoirs (82R) for reception of the oil volume displaced by the press pistons (84).
3. Multicylinder press according to claim 1, characterised in that the filler bodies are formed by telescopic tubes (40; 67) which are arranged between press pistons (31; 64) and cylinder closure caps (36; 33) and connected at the ends therewith and the mean outer diameter of which corresponds with the diameter of the piston rod (33; 63) of the press piston (31; 64).
4. Multicylinder press according to claim 3, characterised in that the first, inner telescope element is constructed as a spigot (68) prolonging the piston (64) and piston rod (63).
5. Multicylinder press according to claim 3 or 4, characterised in that the last, outer telescope element (67/1) is constructed as a pipe piece inserted into the cylinder closure cap and the cylinder closure cap (65) is constructed as a hood (66), wherein the pipe piece (67/1) and the cavity of the hood (66) taken together have a depth corresponding to the depth of pushing in of the penultimate telescope element (67/2).
6. Multicylinder press according to one of claims 3 to 5, characterised in that the internal spaces of the telescope tubes (40; 67) are provided with drains (44; 79) to the oil collecting container.
7. Multicylinder press according to one of claims 3 to 6, characterised in that the caps (36) closing the cylinders (31) each support a respective centrally arranged plunger piston (35), and the press pistons (31) together with their piston rods (33) are provided with cylindrical bores (34) into which the plunger pistons (34) penetrate and are loadable for the return stroke of the press.
8. Multicylinder press according to claim 7, characterised in that the pressure means feed for the loading of the plunger pistons (3) is effected by a bore (37) longitudinally extending through the plunger pistons (35).
9. Multicylinder press according to one of claims 3 to 6, characterised in that the caps (36) closing the cylinders (62) each support a respective centrally arranged telescopic pipe (73), and the press pistons (64) together with their piston rods (63) are provided with cylindrical bores (74) into which the telescopic pipes (73) serving as control lines for controlling the switchable blocking valves (70) in drive sealingly penetrate.
10. Multicylinder press according to claim 1, characterised in that the filler body (49) extends through the cap (52) dosing the cylinder (46), a seal (51) is provided between cap (52) and filler body (49) and the filler body (49) is connected with the piston (47) by spherical joint (50).
11. Multicylinder press according to claim 1, characterised in that the filler body (57) extends through the cap (58) dosing the cylinder (53), a seal (59) is provided between cap (58) and filler body (57) and the seal (49) is retained in the cap (58) to be capable of limited radial movement.
12. Multicylinder press according to one of claims 1 or 3, characterised in that outer annular spaces (32R; 62R) surrounding the filler bodies (40; 67) are connected with the oil collecting chamber by way of compensating ducts (45; 77).

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