EP2934784A1

EP2934784A1 - Forming press

Info

Publication number: EP2934784A1
Application number: EP13818671.3A
Authority: EP
Inventors: Vaclav Hejplik; Patrick STICKER; Carsten Baumgartner
Original assignee: Uniflex Hydraulik GmbH
Current assignee: Uniflex Hydraulik GmbH
Priority date: 2012-12-21
Filing date: 2013-12-20
Publication date: 2015-10-28
Anticipated expiration: 2033-12-20
Also published as: WO2014095078A1; DE102012025134A1; EP2934784B1; US9314984B2; CN104884184A; US20150283775A1; CN104884184B

Abstract

The invention relates to a forming press, comprising a frame structure, a movable first tool carrier (8), a movable second tool carrier (9), a drive system, and a press controller that controls the drive system. A first drive unit (75) associated with the first tool carrier is designed as a fast-stroke unit, the first tool carrier can be mechanically locked in the closed position (8) thereof in relation to the frame structure by means of at least one position-changeable locking body (18), at least one piston-cylinder unit (30) associated with the second tool carrier (9) is designed as a high-pressure unit (48) at least for part of the motion of the second tool carrier in the direction of the first tool carrier (8), and a fluidic pressure booster is integrated into a feed line that connects the high-pressure unit (48) to the associated pressure fluid unit.

Description

forming press

The present invention relates to a fluidic forming press, in particular a radial press, with two tool carriers movable relative to one another along a working direction.

Such forming of workpieces serving presses are known in various designs. They differ from each other, for example, in terms of their intended use (e.g., radial press) and associated construction (e.g., yoke press), as well as the drive concept (e.g., hydraulic). Hydraulically driven yoke presses for the radial deformation of workpieces are known, for example, from DE 199 12 976 A1, DE 10 2009 057 726 A1, DE 4135465 A1 and US Pat. No. 4,854,031 A.

DE 10 2004 035 590 AI discloses a forming press with a movable up and down main plunger, which can be locked after the feed stroke with a fixed part of the press (in particular the lower crosshead) and in which a plunger, which serves the forming of the workpiece working stroke executes, and a blank holder (including associated drive cylinder) are added.

There is a need in the industry for increasingly efficient forming presses, i. Forming presses with one over the established state of the art

CONFIRMATION COPY Substantially further increased press force. As far as radial presses are concerned, this also depends, among other things, on the realization that the radial deformation of a workpiece - or, if necessary, a the joint transformation of two to be connected together

Workpieces - can produce high-strength connections in a radial forming press so that completely new areas of application (especially in connection technology) can be tapped.

The present invention is directed to provide a particularly efficient fluidic forming press in the sense of providing extremely high pressing forces, in particular a particularly powerful radial press for the radial forming of comparatively large-sized workpieces.

This problem is solved by the specified in claim 1 fluidic forming press. For the forming press according to the invention, which can be embodied in particular as a radial press, the following features are thus characteristic in combination and synergetic interaction with each other: The fluidic forming press comprises a frame structure, a first tool carrier movable along a working direction relative to the frame structure, one along the working direction relative to Frame structure movable second tool carrier, acting on the first and the second tool carrier drive system and the drive system controlling press control, wherein the drive system comprises a first drive unit associated with the first tool carrier and a second drive unit associated with the second tool carrier with at least one fluidic piston-cylinder unit, at least one at least latter pressurizing pressure fluid unit and preferably the admission controlling controlled by the press control valves. The at least one of the first tool carrier associated with the first drive unit is designed as Eilhub- unit by means of which the first tool carrier between a relative to the second tool carrier relatively remote home position and the second tool carrier relatively close closed position movable, ie to close the tool around the workpiece or to open. In its closed position, which relates to the second tool carrier, the first tool carrier can be locked mechanically relative to the frame structure by means of at least one positionally variable locking body. At least one of the second tool carrier associated, fluidic piston-cylinder unit is at least for a part of the movement of the second tool carrier in the direction of the (locked) first tool carrier, namely for a subsequent to a pre-pressing actual pressing (see below), as high-pressure Unit executed, which is operable with a lying substantially above the working pressure of the associated pressure fluid assembly operating pressure. In the high-pressure unit with the associated pressure fluid aggregate connecting feed line for this (at least) a fluidic pressure booster integ- riert. This is to be understood as meaning a component within which the pressure prevailing in the working fluid is raised from a first level to an upper second level. This is ideally done without the supply of external energy, in particular by pressure ratio in the inverse ratio of the surfaces of a stepped piston on the low pressure and the high pressure side.

The following explanation of the present invention is made solely for the sake of clarity through a preferred embodiment in which the drive system is hydraulically designed, wherein both the first and the second drive unit comprise hydraulic piston-cylinder units that run at least one pressure fluid unit as a hydraulic unit is, a hydraulic pressure booster is provided and the at least one first tool carrier associated with the first hydraulic piston-cylinder unit is designed as a maximum with the delivery pressure of the associated hydraulic unit operable low-pressure unit. From the focused on this embodiment explanation of the invention, however, even if this preferred development is apostrophized as a "invention" forming press, any restrictions of the invention to the corresponding embodiment can not be derived. In particular, for example, within the scope of the present invention given by claim 1, another embodiment of the first drive unit (eg as electrical spindle drive) into consideration.

For the below explained in detail preferred embodiment of the radial or other forming presses according to the invention thus the following features are characteristic in combination and synergetic interaction: The hydraulic forming press comprises a frame structure, along a working direction relative to the frame structure movable first tool carrier, one along the working direction relative to the frame structure movable second tool carrier, acting on the first and second tool carrier hydraulic drive system and the hydraulic drive system controlling press control, the hydraulic drive system to the individual tool carriers associated hydraulic piston-cylinder units, at least one of these hydraulic unit acting and preferably

Actuation controlling, actuated by a press control valves comprises. The at least one first tool carrier associated with the first hydraulic piston-cylinder unit is as a maximum with the

Delivery pressure of the associated hydraulic unit

operable low-pressure unit performed by means of which the first tool carrier (typically in "rapid traverse") between a relative to the second tool carrier remote basic position and a second tool carrier relatively close closed position is movable. In its closed position, the first tool carrier relative to the frame structure by means of at least one positionally variable locking body mechanically lockable. The at least one second piston-cylinder unit associated with the second tool carrier is designed as a high-pressure unit at least for a part of the movement of the second tool carrier in the direction of the (locked) first tool carrier, which means that it is substantially above the delivery pressure the associated hydraulic unit operating pressure is operable. In the high-pressure unit with the associated hydraulic unit connecting feed line for this purpose (at least) integrated a hydraulic pressure booster.

In the case of the hydraulic forming press according to the invention, both the first and the second tool carrier are moved along the working direction relative to the

Frame structure can be moved, the receiving space for the workpiece to be formed can be opened relatively wide. This is an essential aspect, for example, for those applications in which a complex workpiece is to be placed in the receiving space for the workpiece between the two tool carriers (or between the partial tools used therein). Also for laterally loaded radial presses (see below) is a correspondingly large stroke essential to provide between the two tool carriers a lateral insertion of the workpiece enabling clearance. In conjunction with the other characteristic of the inventive hydraulic forming press Unlike typical features of the prior art, however, such a large stroke of the two tool carriers relative to one another does not entail a limitation on the maximum pressing force. On the contrary: The hydraulic forming press according to the invention can provide far higher than previously realized pressing forces. This contributes significantly to the fact that the at least one of the second tool carrier associated with the second hydraulic piston-cylinder unit, by being assigned a arranged in the associated supply line hydraulic pressure booster is designed as a high pressure unit whose operating pressure substantially, typically by a multiple of the delivery pressure the associated hydraulic unit and the operating pressure of the at least one first tool carrier associated with the first hydraulic piston-cylinder unit. In this case, so that the at least one first hydraulic piston-cylinder unit, which essentially serves the rapid closing (and opening) of the press in the sense of an "idle stroke ¹¹ or" rapid traverse ", is not loaded with the correspondingly high full pressing force, the above-described mechanical, positive locking of the first tool carrier is provided relative to the frame structure by means of at least one lägeveränderbaren locking body.

By the second tool carrier for force pressing via a hydraulic pressure booster can be acted upon, needs the high hydraulic pressure, as he - in Interest of a particularly compact design of the forming press - small cross sections of the second piston-cylinder unit required for the required high pressing forces, not be provided by the hydraulic unit itself. Consequently, that hydraulic unit which serves to act on the at least one piston cylinder unit assigned to the first tool carrier can also be used for the high-pressure unit (in each case in phases via the pressure booster), so that as a result the forming press according to the invention can manage with a single hydraulic unit. This allows a comparatively simple design of the drive system even with, as stated, the highest performance data of the forming press according to the invention.

The statement according to which the first drive unit is assigned to the first tool carrier does not mean that the first drive unit necessarily acts between the first tool carrier and the frame structure. On the contrary, the first drive unit between the first and the second tool carrier acts particularly preferably, as explained in more detail below, so that the two tool carriers form a (as a whole replaceable) tool carrier unit connected to the first drive unit, to which preferably also a guide bracket counts, which ensures the leadership of the two tool carrier relative to each other along the working direction. Further advantages and favorable aspects of the present invention will become apparent from the following explanation of particularly favorable design features and the subsequent explanation of one in the drawing

illustrated particularly preferred Ausfuhrungsbei- game clearly.

A preferred development of the forming press according to the invention is characterized in that the cylinder of the at least one high-pressure unit is designed in a frame component which forms part of the frame structure and engages via lateral profiles in corresponding profiles of two side plates also associated with the frame structure. In this way, there is the possibility of a particularly compact design, which in turn is favorable in view of the extremely high operating forces, because this can optimally control deformations of the forming press during pressing. In addition, due to the load-bearing positive engagement of frame member and side plates supporting, i. in the direction of the forming press oriented screw largely or possibly. even completely avoided; and it results in addition to very favorable Kraftflussverläufen the possibility for a particularly simple installation. The - a form fit

effecting - interlocking, at least partially mutually corresponding lateral profiles of that frame member, in which the cylinder of the at least one high pressure unit is executed, and the side plates particularly preferably comprise, in addition to at least one load surface, which is substantially perpendicular to the working direction, at least one support surface which is offset therefrom. In particular, that support surface can run more or less at right angles to the respective load surface; their function consists primarily in the reception or support of moments which are induced in the side plates by the introduction of forces on the load surfaces, possibly also in the side plates and the said frame member in such an engagement to hold each other that the Load surfaces of side plates and frame member safely and permanently force-bearing abut each other. The mutually corresponding profiles of frame member and side plates are preferred, however, not necessarily as a positive profile (projection) on the frame member and negative profile (recess) executed on the side plates. The respective profile can extend continuously over the entire depth (transversely to the working direction) in the sense of an optimal force flow characteristic. In the cross section follow the

Profiles adjacent to the load surfaces preferably at least over a substantial part of an ellipse, which in turn is favorable in view of the force flow characteristic.

The greatest possible degree of compactness can be achieved if, according to another preferred development, the hydraulic pressure intensifier is also used is structurally integrated into the frame structure, that its cylinder is designed in the same frame member as the cylinder of the at least one high-pressure unit. The advantages set out above can be achieved particularly pronounced in this case. In addition, in this case the entire high-pressure area is "encapsulated" in a single component

arranged so that in particular the highest pressure exposed (exposed) line connections are avoided; and it requires in this case only shortest connection channels for the hydraulic fluid from the pressure booster to the at least one high pressure unit, which is also particularly advantageous because the forming press according to the invention - on the high pressure side - typically operates in a pressure range in which hydraulic oil is compressible. A minimal

Pressure oil volume therefore has considerable advantages in terms of the hydraulic rigidity of the drive system. Also from the point of view of a

Particularly compact design is advantageous if the hydraulic pressure booster is oriented with an axis perpendicular to the working direction of the forming press axis.

The aspects set forth above in connection with the positive connection between the side plates of the frame structure and that frame component, in which the cylinder of the at least one high-pressure unit is embodied, apply correspondingly to the at least one locking body on which the first tool carrier is pressed during force pressing supported. This means that preferably the at least one locking body engages positively in at least in its locking position via lateral profiles in corresponding profiles of two side plates associated with the frame structure. Particularly preferably, the profilings of the at least one locking body and each of the two side plates abut one another in each case on at least one load surface which is substantially perpendicular to the working direction. An additional support of the at least one locking body in the area of a support surface (for example on the first tool carrier) that is substantially perpendicular to the load surface and is offset therefrom acts against moments induced by off-axis force application. Again, it is true that the mutually corresponding profiles of locking body (s) and side plates are preferably designed as a positive profile (projection) on the / the locking body (s) and negative profile (recess) on the side plates and in cross section adjacent to the load surfaces preferably follow at least a substantial part of an ellipse.

Furthermore, it is particularly favorable if the at least one locking body is displaceable with a direction of movement perpendicular to the working direction. In this way, the pressing force exerted on the at least one locking body during force pressing via the workpiece and the first tool carrier does not result in a displacement component, so that the fixation of the locking body in its locking position can be realized with relatively little effort.

According to yet another preferred embodiment of the present invention, it is provided that two mutually mechanically coupled, a distance from one another compliant locking body are provided, wherein particularly preferably in the space between the two locking bodies, a guide bracket is provided for the first tool carrier. Again, this is a technical-constructive point of view, which allows a particularly compact design, with the advantages set out above. Said guide bracket is preferably fixedly connected to the second tool carrier.

Yet another preferred embodiment of the invention is characterized in that in addition to that supply line through which the high-pressure unit communicates with the hydraulic pressure booster, a further feed line is provided, via which the high-pressure unit, bypassing the hydraulic booster from an associated hydraulic unit can be acted upon. This makes it possible, after blocking the first tool carrier in the predetermined by the at least one locking body position the second tool carrier first, namely for a "pre-pressing" until the tool on the workpiece, directly, ie bypassing the To pressurize hydraulic booster from said hydraulic power unit. In this way, the full stroke of the hydraulic booster for the actual pressing, ie the power pressing remains available, so that a maximum pressing stroke is maintained for the force pressing. In this case, the drive system particularly preferably has a pressure sensor connected to the press control on the supply side associated with the second tool carrier, wherein during the movement of the second tool carrier in the direction of the first tool carrier as a function of the

Pressure signal a switching from the (direct) admission of the high-pressure unit via the second supply line to the admission of the high-pressure unit via the pressure booster takes place.

Is in the above-described sense one of the loading of the high-pressure unit, bypassing the hydraulic booster serving another

Provided supply line, it is particularly preferred in these a filling valve with high-pressure barrier function connected. The said high-pressure-resistant blocking function is particularly preferably via a

Poppet valve realized, wherein the closing body of the poppet valve can be hydraulically actuated namely by being in communication with an actuating piston, which in turn is part of a housed in the housing of the filling valve hydraulic piston-cylinder unit. By means of the latter, the closing body is advantageously both in the direction Closing and operable in the direction of opening the filling valve. The above-explained, a high-pressure-resistant blocking function having filling valve has in yet another preferred development on a mounted on the frame structure of the forming valve housing, wherein for fastening the valve housing prestressed expansion screws are provided and the sealing of the valve housing relative to the frame structure in the region of a clearance compensation by means of a radial seal he follows. This takes into account that at the extremely high pressures on which the forming press according to the invention is designed, relative movements of the valve housing and the frame structure are to be expected, with such relative movements of the valve housing relative to the frame structure in the case of the described seal by means of a radial seal in the area a clearance compensation even at the high pressure side prevailing extreme pressures (eg 3000 bar) ensures a reliable tightness.

According to yet another preferred development of the present invention, the at least one high-pressure unit is designed to be single-acting in the sense that it alone the running during the pre-pressing and power pressing movement of the second tool carrier in the direction of the first tool carrier (from the closed position in the pressing position) takes place, but not the re-dividing from the pressing position into the closed position. For the latter, ie for the movement of the second tool carrier away from the first tool carrier, a further, designed as a low-pressure unit hydraulic piston-cylinder unit is provided. On the other hand, such a separation of the function of prepressing / force pressing on the one hand and resetting on the other hand permits, due to the function-specific design of the components - a particularly compact design with the advantages already explained above. Particularly preferably, two high-pressure units are provided on the side of the second tool carrier, between which the low-pressure unit serving as the return is arranged. In this construction, not only for the second tool carrier results in a high degree of tilt stability, so that the function impairing tilting can be avoided; Rather, an introduction of the pressing force into the second tool carrier takes place via an arrangement of two high-pressure units at a distance from one another in an optimum manner for the subsequent force curve within the second tool carrier. In this way, the stresses within the second tool carrier are minimized, so that it can be dimensioned relatively small.

Unlike this, as stated above, applies to the at least one of the second tool carrier associated high-pressure unit, the at least one first hydraulic piston-cylinder unit is particularly preferably carried out double-acting, so that with her equally the first tool holder - in the sense of Closing the forming press - can be moved to the second tool carrier, as well as - in the sense of opening the forming press - away from the second tool carrier.

The foregoing discussion of the forming press of the present invention and the following discussion of a preferred embodiment are clearly illustrative of the broader advantages associated with the present invention, that is to say, the benefit of the present invention. can be achieved with the forming presses defined in the claims,

Namely, as far as the special performance of a radial press according to the present invention is concerned. In this case, the synergetic interactions of the cooperating, characteristic of the forming press according to the invention characteristics come into play. For applications in which not all the performance potential provided by the present invention is needed or exhausted, there is still a significant advantage over the prior art in the somewhat "slimmed down" implementation of the invention underlying knowledge. For example, with a reduced power requirement, embodiments of forming presses, in particular of radial presses, can be used, in which the fluid pressure booster associated with the second drive unit is dispensed with, although the construction remains unchanged. This is especially true when the aspect of compactness of the forming press in the specific application concerned has comparatively little importance, so that without serious detriment to the usability of the forming press for the application in question, the cross sections of the second drive unit can be increased.

In the following, the present invention will be explained in more detail with reference to a preferred exemplary embodiment illustrated in the drawing. It shows

Fig. 1 a guided perpendicular to the press axis

Vertical section through a executed according to the present invention radial press in its normal position,

Fig. 2 shows the radial press of Fig. 1 with the tool closed, i. fully lowered upper tool carrier,

3 with the radial press according to FIGS. 1 and 2 with mechanically locked upper tool carrier,

4 shows the radial press according to FIGS. 1 to 3 after a first part of the upward movement of the lower tool carrier,

Fig. 5 shows the radial press of Figs. 1 to 4 when the lower tool carrier is fully moved upwards, i. at the end of the pressing process,

Fig. 6, the radial press of FIGS. 1 to 5 am

End of the decompression phase,

7 shows the radial press according to FIGS. 1 to 6 after the complete lowering of the lower tool carrier, 8 after the unlocking of the upper tool carrier,

9 shows the radial press according to FIGS. 1 to 8 after the complete lifting of the upper tool carrier; continues to show

10 shows an enlarged vertical section through the part of the drive unit assigned to the lower tool carrier,

11 is a substantially schematic, guided in the plane of the press axis vertical section through a principle constructed in accordance with FIGS. 1 to 10 radial press,

Fig. 12 in the radial press of FIGS. 1 to

11 used valve unit in an enlarged view,

13 is a hydraulic circuit diagram of the radial press according to Figures 1 to 12 and

14 shows one of the radial press according to the figures 1 to

9 removed tool carrier unit together with inserted radial pressing tool.

The radial hydraulic press illustrated in FIGS. 1 to 12 serves for the radial deformation of a workpiece 1 relative to a press axis A. It comprises a frame structure 2 which essentially consists of four main components, namely two side plates 3, a lower frame component 4 and an upper one Bracket 5. The in the side plates 3 to the

Press axis A arranged around openings 6 extend up to the right in the drawing darge put edge 7 of the side plates 3 to allow lateral loading of the radial press; this explains the designation of this radial press concept (see DE 19940744 A1) as "C-press".

Between the two side plates 3 of the frame structure 2, two tool carriers are accommodated, namely an upper, first tool carrier 8 and a lower, second tool carrier 9, movable relative to this and one another along a working direction B which is perpendicular to the pressing axis A. The first tool holder 8 forms in the present press design a Oberj 10 och, the second tool carrier a lower yoke 11. The recorded in the Oberj och 10 and the lower yoke 11 tool comprises a total of eight pressing jaws 12, which at the Oberj och 10 and the lower yoke eleventh in the manner known as such - partially sliding - support, wherein two of the pressing jaws are designed to be divided in a known manner. The guide of the Oberj ochs 10 serves a recorded between the side plates 3 of the frame structure 2, with the lower yoke 11 firmly bonded guide bracket 13, on which the Oberj 10 o is slidably guided by a linear guide 14 slidably up and down. The Oberj 10 associated components of the linear guide 14 are not rigidly connected to the Oberj 10 here, but rather with the interposition of an elastomer body comprehensive Entkoppelungseinheit. In this way affect operation - within certain limits - occurring deformations not the reliability of the press.

The lower frame component 4 and the two side plates 3 engage in one another in a form-fitting manner via profilings 15 which essentially correspond to one another (cf., FIG. 11). In this case, the profiles 15 are designed so that the lower frame member 4 and each of the two side plates 3 not only abut on a substantially perpendicular to the working direction B load surface 16 in the direction of force to each other, but also at least one of them remote on the cooperating support surfaces 17 not only cause the engagement of side plates 3 and lower frame component 4 to be maintained; Based on the respective associated load surface 16, the support surfaces 17 additionally each cause a support torque C, which counteracts a deformation of the side plates 3 during pressing. The profiling 15 of the side plates 3 from the respective load surface 16 towards the full wall thickness (i.e., upwards in Fig. 11) is followed by avoiding too much discontinuity of an ellipse E followed by a transient slope S.

Between the two side plates 3 are further - on both sides of the guide bracket 13 - two locking body 18 is arranged, which on the upper bracket. 5 the frame structure 2 along linear guides 19 are guided transversely to the direction B displaced. These two (mutually coupled) locking body 18 can by means of the hydraulic VerfahrZylinders 20 together, that is shifted synchronously in a lying above the Oberj ochs 10 locking position when the Oberjoch - by means of the associated first hydraulic piston-cylinder unit 21 - is lowered correspondingly far (see below). Thus, the upper 10 is mechanically locked relative to the frame structure 2 by means of the two position-adjustable locking body 18 in the sense that the (when pressing) from the lower yoke 11 on the workpiece 1 on the Oberj 10 exerted, substantially in the direction of Working direction B upward force is introduced via the two locking body 18 in the side plates 3. For this purpose, the upper part 10 lies in the region of upper end faces 22 on corresponding contact surfaces

23 of the two locking body 18 on; and the two locking bodies 18 engage - at least in their locking position - on lateral profiles

24 in corresponding profiles 25 of the side plates 3 a. The said profiling 24 or 25 of the locking body 18 and the respective associated side plate 3 are in each case at one on the working direction B substantially perpendicular load surface 26 to each other. Furthermore, the two side plates 3 are supported at the top by a support surface 27 perpendicular to the load surface 26 on the bracket 5; and the two locking bodies 18 are also supported on the inside-down support surfaces 28, which are provided on both sides of a disposed at the top of Oberj ochs 10 web 29.

The radial press also has a hydraulic drive system, which acts on the Oberj 10 and the lower yoke 11. This drive system comprises a first drive unit 75 in the form of the first associated with the Oberjoch 10, the movement relative to the lower yoke 11 (and thus relative to the frame structure) causing first hydraulic piston-cylinder unit 21, a second drive unit 76 in the form of three the lower yoke 11 associated, the movement of which relative to the frame structure 2 causing the second hydraulic piston-cylinder units 30, a hydraulic piston-cylinder units 21, 30 beaufschlagendes

Hydraulic unit 31 and said admission controlling valves. The - controlled by the press control - valves are housed in two valve and Verteilblöcken 32 and 33. Unlike the first piston-cylinder unit 21, which is designed to move the upper yoke 10 downwards and upwards double-acting and whose lower end is struck on the lower yoke 11, the three second piston-cylinder units 30 are single-acting, with two Press units 34 and arranged between these restoring unit 35 are provided. The cylinders 36 of the three second piston-cylinder units 30 are each made in the lower frame member 4; and the pistons 37 of the three second piston-cylinder Units 30 are connected to a mounting plate 38 for the lower yoke 11. In this case, in the region of the connection of the piston of the restoring unit 35 with the mounting plate 38 a compliance (in particular in the form of an elastomeric element) interposed, so that during operation of the press - within certain limits - resulting deformations can not lead to jamming. For the same reason, the piston press units 34 are "articulated" in the sense that certain tilting of the pistons in the associated cylinders are tolerated and the

Do not compromise operational safety. In the center plane defined by the press axis A, the mounting plate 38 is guided, moreover, by two guide pins X, which - again yielding - with the

Mounting plate 38 is connected and slidably received in corresponding guide holes of the lower frame member 4. The lower yoke 11 is constrained to the mounting plate 38 in the sense that it slides sideways on the surface of the mounting plate 38, i. transversely to the direction B is displaced. For this purpose, the surface of the mounting plate 38 is designed as a roller conveyor 39.

In the lower frame member 4 is further - oriented at right angles to the direction B - the high-pressure side cylinder 40 of a hydraulic

Differential pressure booster 41 housed, ie in the present case executed directly in the lower frame member 4. The low-pressure side piston 42 of the hydraulic Differential pressure booster 41 is sealingly guided in a cylinder housing 44 flanged to the lower frame component 4 by means of a screw flange 43. In the region of the screw flange 43 of the cylinder housing 44, a stiffening plate 45 is arranged, which rests with its peripheral edge on the inside of the threaded projection 46 of the cylinder housing 44. The high-pressure side cylinder 40 of the hydraulic pressure booster 41 communicates via a connecting channel 47 directly with the cylinders 36 of the two press units 34, which are connected in parallel with one another via the channel 57 and which thus constitute high-pressure units 48.

The cylinders 36 of the two high-pressure units 48 communicate with a further feed line 49, via which the high-pressure units 48 - during the first part of the pressing process, the "pre-pressing" until the pressing jaws 12 abut against the workpiece 1 or encounter considerable resistance - bypassing the

hydraulic booster 41 can be acted upon by the hydraulic unit 31. Between the hydraulic unit 31 and the high-pressure units 48, a filling valve 50 is connected in the second feed line 49, which has a high-pressure-resistant blocking function, which is realized by a present example, 3000 bar designed check valve 51. In that regard, the filling valve 50 actually represents a filling and shut-off valve. The filling valve 50 is designed as a seat valve with a hydraulic actuator. Tigbaren closing body 52, which communicates with an actuating piston 53 in conjunction, which in turn is part of a housed in the housing 54 of the filling valve 50 hydraulic piston-cylinder unit 55. The hydraulic piston-cylinder unit 55 which serves to actuate the closing body 52 of the filling valve 50 is also acted upon by the hydraulic unit 31 via the pilot valve 73 and the valve and distributor block 33 via pilot valves accommodated in the valve and distributor block 32.

The valve housing 54 of the filling valve 50 is attached by means of prestressed expansion screws 56 to the frame structure 2 of the forming press. The sealing of the valve housing 54 relative to the frame structure 2 takes place (on both sides) in the area of the outer peripheral surface 58 of a sleeve-like projection 59 of an adapter 60 attached to the valve housing 54, on which a sealing ring 61 rests. This is a reliable tightness even with a certain game, which is unavoidable under the action of high pressures on the closing body 52 and thereby caused expansion of the expansion screws 56, guaranteed.

The hydraulic drive system is further designed and adapted to be used for a temperature control of the hydraulic fluid and / or the press. In order to allow the hydraulic fluid to circulate within the radial press for this purpose, the piston rod 62 of the hydraulic pressure Strengthens 41 on a longitudinal bore 63, which is the end face, ie limited in the region of the high-pressure side piston 64 by a present on 3.000 bar designed check valve 65. At the opposite end of the longitudinal bore 63 communicates via a connecting bore 66 with the piston rod working space 67 of the hydraulic pressure booster 41. 41 check valves 68 are also provided in the low pressure side piston 42 of the hydraulic pressure booster 41, which for a flow direction from the piston rod working chamber 67 of the hydraulic pressure booster 41st open to the piston working space 69. Other Durchströ- mung- or hydraulic oil circulation concepts that serve the temperature of the press or the hydraulic oil are possible in a corresponding manner.

The operation of the radial press shown is as follows (see Figures 1-9):

In Fig. 1, the press is ready for the insertion of the workpiece 1 to be pressed (see Fig. 1). The movable parts, ie in particular the lower yoke 11, the Oberj 10, the locking body 18 and the piston unit of the hydraulic pressure booster 41 assume their basic or initial position. If required for a temperature control of the press and / or the hydraulic fluid, the latter can circulate in this phase. In this case, for example (see FIG. 13), the hydraulic unit 31 flows through the pressure regulator 73, the distribution and valve block 33 and the distributor and valve unit. tilblock 32 - in the piston rod working space 67 of the hydraulic pressure booster 41 fed hydraulic fluid from there on the one hand - via the connecting bore 66 and the longitudinal bore 63 of the

Piston rod 62 and the high-pressure side cylinder 40 of the hydraulic pressure intensifier 41 - the cylinder 36 of the high pressure units 48 and flows through the - open to this - filling valve 50 to the valve and Verteilblock 33 and from there into the tank T back; On the other hand, hydraulic fluid fed into the piston rod working space 67 of the hydraulic pressure booster 41 flows through the hydraulic fluid in the low pressure side piston 42 of the hydraulic pressure booster 41

arranged check valves 68, the Kolbenarbeits- space 69 and the valve and distribution block 33 back to the tank T.

For radial deformation of the arranged in the receiving space 70 of the press workpiece 1, the first hydraulic piston-cylinder unit 21 is acted upon by the hydraulic unit 31 via the valve and distributor blocks 33 and 32 in the sense that the top yoke 10 downward toward the lower yoke 11 is moved, until the tool closes, ie until the press jaw sections 71 of the split press jaws associated with the two part tools abut one another (compare FIG. 2). In this position, the press jaw system is in the closed, for the actual

Pressing condition prepared. Now (see Fig. 3) the hydraulic piston-cylinder unit (ie, the movement cylinder 20) serving the method of the two locking bodies 18 is acted upon by the hydraulic unit 31 via the valve and distributor blocks 33 and 32 in the sense that the two Locking body 18 are moved over the Oberj 10 och. There is in this phase a small gap 72 between the upper end surfaces 22 of the Oberj ochs 10 and the corresponding abutment surfaces 23 of the two locking body 18. This gap 72 allows the said sliding movement of the locking body 18 via the upper yoke 10 regardless of that when raised to the locking bodies 18 abutting Oberj och 10 is blocked by cooperating locking elements such displacement.

In the next step (see Fig. 4), the cylinders 36 of the two high-pressure units 48 are acted upon by the hydraulic unit 31 via the valve and distribution block 33 and the open filling valve 50 in the sense that the lower yoke 11 is raised, so far until the further compressed pressing jaw system abuts against the workpiece 1 ("prepressing") and the tool carrier unit (including the tool received therein) comprising the first tool carrier 8 and the second tool carrier 9 until the upper jaw 10 abuts against the two locking bodies 18 in FIG Area of mutually corresponding surfaces is raised. The first piston-cylinder unit 21 is switched to its floating position in this phase. One - connected to the press control - pressure sensor (or pressure switch) determines the thereby adjusting (sudden) pressure increase in the hydraulic drive system and triggers a switch from the application of the high pressure units 48 via the filling valve 50 and the other feed line 49 to the application of high pressure Units 48 via the hydraulic pressure booster 41. For this purpose, the filling valve 50 is closed by corresponding loading of the piston-cylinder unit 55 assigned to the closing body 52 by the hydraulic unit 31 via the valve and distributor blocks 33 and 32.

In the following (see Fig. 5) takes place via an action on the piston working chamber 69 of the hydraulic pressure booster 41 by the hydraulic unit 31 via the valve and Verteilblock 33 a pressing of hydraulic fluid into the cylinder 36 of the high pressure units 48 under high pressure from the cylinder 40 of the hydraulic booster 41 by its high-pressure side piston 64. This is the process of the actual high-pressure power pressing. This high-pressure force pressing takes place until reaching the pressing dimension. Also in this phase, the first piston-cylinder unit 21 is switched to its floating position.

After pressing, a decompression phase takes place (see Fig. 6) in order to compress the hydraulic fluid compressed at the existing extreme pressure conditions (eg at 3,000 bar to approximately 80% of the initial volume). tet) at least substantially to the pressure level of the incompressibility or even further (to relax more or less on the tank pressure). This relaxation of the high-pressure side clamped hydraulic fluid is effected by a (via the relevant valves of the valve and distributor blocks 33 and 32) controlled movement of the piston unit of the hydraulic pressure booster 41st

Following this (see Fig. 7) is - by appropriate control of the valves of the valve and distributor blocks 32 and 33 - the existing on the low pressure side of the hydraulic pressure booster 41 hydraulic fluid locked, whereby the piston unit of the hydraulic pressure booster 41 is blocked, the filling valve 50 and the reset unit 35 is acted upon from the hydraulic unit 31. As a result, the lower yoke 11 is moved downwards, specifically until it assumes its maximally lowered position ("initial position" according to FIG. 1). It already follows because of its own weight Oberj 10 so that this lifts off from the locking bodies 18, so that the two locking body 18 are released. During this phase, hydraulic fluid is displaced from the high-pressure units 48 via the filling valve 50 into the tank T. In order to support the joint lowering of the entire, still closed tool carrier unit, the first piston-cylinder unit 21 may possibly be locked in this phase. Next (see Fig. 8), the two locking bodies 18 are moved into their initial or basic position by corresponding action of the moving unit 20, so that (see Fig. 9) subsequently - by acting on the first piston-cylinder unit 21st - The tool is opened and the upper yoke 10 is moved further up, until reaching the

Initial position. The finished pressed workpiece can be removed from the opened tool. The provision of the piston unit of the hydraulic pressure booster 41 in its initial position completes the cycle; For this purpose - with continued loading of the reset unit 35 and with appropriate control of the associated valves - an action on the high pressure side of the hydraulic Duckverstärkers 41 from the hydraulic unit 31 via the filling valve 50 and the cylinder 36 of the high pressure units 48. Hydraulic fluid from the piston working chamber 69 of the hydraulic Pressure amplifier 41 is doing over the

Valve block 33 displaced into the tank T. This provision of the piston unit of the hydraulic booster 41, however, can also be initiated sooner, namely as soon as the lower yoke 11 is lowered to its initial position (see above).

For Fig. 11, reference should be made to the schematic character. Thus, the radial press is simplified in several ways. In particular, the high-pressure unit 48 and the support of the lower yoke 11 are shown roughly simplified. FIG. 14 illustrates the possibility of the entire unit consisting of the first tool carrier 8 or the upper 10, the second tool carrier 9 and the lower yoke 11, the guide console 13 fixed to the lower yoke and the between the lower yoke 11 and the upper joch 10 extending - first piston-cylinder unit 21 (including recorded between the two tool carriers pressing tool) to remove from the frame structure of the radial press, for example, to convert the presses from one pressing task to another. The removal of the unit to be removed from the press and the positioning of the unit to be accommodated in the press is facilitated by the arrangement of the roller conveyor 39 on the mounting plate 38.

By way of precaution, it should be pointed out in conclusion that the directions used such as "top", "bottom" and the like may not be interpreted in the sense that this expresses a particular orientation of the press in use. Rather, the press, as is the case, for example, when connecting the pipe sections of a laid on the floor fluid line (eg a pipeline), also hanging with downward facing opening for the "lateral" inserting a workpiece are used (see Suspension eyelets 74), in which case the working direction B is not vertical, but rather horizontal. In that regard, the said directions are solely to refer to the orientation of the radial press shown concretely in the drawing. By the way, as a precautionary measure, it should be pointed out that individual figures may differ from each other with regard to specific details which, however, are wholly irrelevant to the nature of the present invention specified in the claims. Such discrepancies, since they do not affect the invention as such, are not significant and therefore remain uncommented.

Claims

claims

1. fluidic forming press, in particular radial press, with a frame structure, one along a

Working direction (B) relative to the frame structure movable first tool carrier (8), along the working direction (B) relative to the frame structure movable second tool carrier (9), acting on the first and the second tool carrier drive system, which one of the first

Tool carrier (8) associated with the first drive unit (75) and a second tool carrier (9)

associated second drive unit (76) with

at least one fluidic piston-cylinder unit (30), at least one at least the latter

pressurizing pressure fluid aggregate and - preferably

- The admission-controlling valves comprises, and controlling the drive system

Press control, with the following features:

- The at least one of the first tool carrier (8) associated with the first drive unit (75) is designed as Ehp-unit, by means of which the first tool carrier (8) between a relative to the second tool carrier (9) relatively remote home position and a second

Tool carrier relatively close closed position is movable;

- in its closed position is the first

Tool carrier (8) relative to the frame structure by means of at least one positionally variable locking body (18) mechanically

lockable; - At least one of the second tool carrier (9) associated with fluidic piston-cylinder unit

(30) is at least for a part of the movement of the second tool carrier in the direction of the first tool carrier (8) as a high-pressure unit

(48) executed, which is operable with a substantially above the working pressure of the associated pressure fluid unit operating pressure lying;

- In the high-pressure unit (48) with the

associated pressurized fluid aggregate

Feed line is integrated a fluidic pressure booster.

Forming press according to claim 1, characterized

characterized in that it is a hydraulic

Drive system comprises, wherein the first and the second drive unit (75; 76) comprise hydraulic piston-cylinder units (21; 30), the at least one pressure fluid unit is designed as a hydraulic unit (31), as a fluidic pressure booster, a hydraulic pressure booster (41) is provided is and at least one of the first tool carrier (8) associated with the first hydraulic piston-cylinder unit (21) is designed as a maximum with the delivery pressure of the associated hydraulic unit (31) operable low-pressure unit.

Forming press according to claim 2, characterized

in that a cylinder (36) of the

at least one high-pressure unit (48) in a frame member (4) is formed, which forms part of the frame structure and on the side

Profiling (15) in corresponding

Profiles (15) of two also the Frame structure associated side plates (3)

engages.

4. forming press according to claim 3, characterized

characterized in that each other

corresponding profiles (15) of

Frame member (4) and side plates (3) as a positive profile (projection) on the frame member (4) and negative profile (recess) on the side plates (3) are executed.

5. forming press according to claim 3 or claim 4,

characterized in that the profiles (15) in the cross-section adjacent to load surfaces (16, 26) at least over a substantial part of an ellipse follow.

6. forming press according to one of claims 3 to 5,

characterized in that the profilings (15) of the frame member (4) and each of the two

Side plates (3) each at one on the

Working direction (B) substantially perpendicular to the load surface (16) and at least one thereof remote support surface (17) abut each other.

7. forming press according to claim 5 or claim 6,

characterized in that also the hydraulic pressure booster (41) so structurally in the

Frame structure is integrated, that its cylinder (40) in the frame member (4) is executed.

8. forming press according to one of claims 2 to 7, characterized in that the hydraulic

Duck amplifier (41) is oriented with an axis perpendicular to the working axis (B).

9. forming press according to one of claims 2 to 8,

characterized in that the at least one locking body (18) at least in its

Locking position via lateral profiles (24) engages in corresponding profiles (25) of the frame structure.

10. forming press according to claim 9, characterized

in that the profilings (24; 25) of the at least one locking body (18) and of the frame structure bear against one another on a load surface (26) which is substantially perpendicular to the working direction (B).

11. Forming press according to one of claims 2 to 10,

characterized in that the at least one locking body (18) with a on the

Working direction (B) vertical

Movement direction is displaced.

12. Forming press according to one of claims 2 to 11,

characterized in that two spaced apart locking body (18) are provided.

13. forming press according to claim 12, characterized

characterized in that in the intermediate space between the two locking bodies (18) has a

Guide console (13) for the first tool carrier (8) is provided.

14. forming press according to claim 13, characterized in that the first tool carrier (8) by means of a linear guide (14) on the

Guide console (13) is guided, wherein the first tool carrier (8) associated components of the linear guide (14) with the first tool carrier with the interposition of an elastic

Entkoppelungseinheit are connected.

15. Forming press according to claim 13 or claim 14,

characterized in that the guide bracket (13) is fixedly connected to the second tool carrier (9) and the at least one first hydraulic piston-cylinder unit (21) acts between the first and second tool carriers (8; 9) the two tool carriers, the

Guide console and the at least one first hydraulic piston-cylinder unit comprehensive complete tool carrier unit of the frame structure can be removed.

16. Forming press according to one of claims 2 to 15,

characterized in that another

Supply line (49) is provided, via which the high-pressure unit (48), bypassing the

Hydraulic pressure booster (41) by an associated hydraulic unit (31) can be acted upon.

17. forming press according to claim 16, characterized

in that the drive system is assigned to the second tool carrier (9)

Supply side one with the press control connected during the movement of the second tool carrier (9) in the direction of the first tool carrier (8) in response to the pressure signal, a switching from the application of the high-pressure unit (48) via the second feed line (49) the

Actuation of the high-pressure unit via the hydraulic pressure booster (41) takes place.

18. Forming press according to claim 16 or claim 17,

characterized in that in the second

Feed line (49) a filling valve (50) with

high-pressure barrier function is switched.

19. Forming press according to claim 18, characterized

characterized in that the filling valve (50) as

Seat valve is executed with a hydraulically actuated closing body (52), which with a

Actuating piston (53) is in communication, which in turn is part of a in a valve housing (54) of the filling valve (50) accommodated hydraulic piston-cylinder unit (55).

20. Forming press according to claim 18 or claim 19,

characterized in that the filling valve (50) on the frame structure of the forming press

having attached valve housing (54), wherein biased for fastening the valve housing

Expansion screws (56) are provided and the

Sealing of the valve housing against the

Frame structure in the field of clearance compensation by means of a radial seal (61).

21. Forming press according to one of claims 2 to 20, characterized in that the at least one high-pressure unit (48) designed to be single-acting and that the second tool carrier (9) for the movement away from the first tool carrier (8) has a reset unit (35 ) in the form of another, designed as a low-pressure unit hydraulic

Piston-cylinder unit (30) is assigned.

22. forming press according to claim 21, characterized

characterized in that two high pressure units (48) are provided, between which the low pressure unit is arranged.

23. Forming press according to one of claims 2 to 22,

characterized in that the at least one first hydraulic piston-cylinder unit (21) is double-acting.

24. Forming press according to one of claims 2 to 23,

characterized in that all hydraulic piston-cylinder units (21; 30) from exactly one hydraulic unit (31) can be acted upon.

25. Forming press according to one of claims 2 to 24,

characterized in that it is designed as a laterally loadable radial press that the between the tool carriers (8; 9) arranged receiving space (70) for the workpiece (1) via a lateral opening is accessible.