WO2010012014A2 - Presse de formage de matériau - Google Patents

Presse de formage de matériau Download PDF

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Publication number
WO2010012014A2
WO2010012014A2 PCT/AT2009/000285 AT2009000285W WO2010012014A2 WO 2010012014 A2 WO2010012014 A2 WO 2010012014A2 AT 2009000285 W AT2009000285 W AT 2009000285W WO 2010012014 A2 WO2010012014 A2 WO 2010012014A2
Authority
WO
WIPO (PCT)
Prior art keywords
press
actuators
head piece
pressing direction
press according
Prior art date
Application number
PCT/AT2009/000285
Other languages
German (de)
English (en)
Other versions
WO2010012014A3 (fr
Inventor
Franz Ehrenleitner
Original Assignee
Franz Ehrenleitner
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
Priority claimed from AT13532008A external-priority patent/AT507110B1/de
Application filed by Franz Ehrenleitner filed Critical Franz Ehrenleitner
Priority to DE112009001795T priority Critical patent/DE112009001795A5/de
Publication of WO2010012014A2 publication Critical patent/WO2010012014A2/fr
Publication of WO2010012014A3 publication Critical patent/WO2010012014A3/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • B30B1/34—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure involving a plurality of plungers acting on the platen
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/044—Means preventing deflection of the frame, especially for C-frames
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/068—Drive connections, e.g. pivotal
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam

Definitions

  • the invention relates to a press for forming material with a table and a press ram (Bär), which is opposite to the table by means of a press drive up and down movable.
  • the power flow or power line through the press takes place in the "detour", that is, the force is passed from the base via the stator in the head piece and from there via the drives in the press ram.
  • the power circle is closed over the workpiece and the table.
  • Dead times are understood to be the times that pass for the movement of the head piece between the end of the pressing process and the top dead center and back again.
  • press a forming machine, hereinafter referred to as "press”, which does not have the mentioned disadvantages, at least in various embodiments, and does not require a higher investment cost than prior art presses.
  • the head piece is the movable platform of a parallel kinematic device whose fixed platform is stationary relative to the table.
  • actuators are provided instead of the head piece, the upright and the leg guides, which supply the pressing forces and absorb the moments and transverse forces which occur.
  • Actuators are in the parallel kinematics, as stated in the literature to the above overview, understood rod-shaped structures that are either variable in length and / or have a movable base and (in the technical sense) only on train and / or pressure, but not on bending or Torsion be claimed.
  • the principle possible rotary parallel kinematic devices are not considered here.
  • all components of the press are disassembled into frameworks, wherein the press ram is supported by such a framework. All this makes the following possible:
  • the individual components can be arranged with respect to the table in an optimal position for the supply and removal of the workpieces.
  • FIG. 9 shows the press according to FIG. 8 in the installed state
  • FIG. 10 shows a press line, ie FIG. IIa together with secondary figure IIb, an embodiment of the invention for better adjustment or distribution of the pressing forces, partly in section
  • FIG. FIGS. 15 to 17 show another development of the invention for increasing the clock rate
  • FIGS. 18 to 23 show various embodiments of the invention for equalizing the energy consumption
  • FIG. 24 shows an embodiment of an embodiment 25
  • Fig. 26 is a guide of Fig. 25 in detail
  • FIG. 24 shows an embodiment of an embodiment 25
  • Fig. 26 is a guide of Fig. 25 in detail
  • Fig. 27 is a side view of the press of Fig. 25, Fig. 28 the FIG
  • FIG. 30 shows the press from FIG. 29 from another direction
  • FIG. 32 shows the press from FIG. 31 in section A-A, including details
  • FIG. 33 to 39 a development of the invention for reducing the deflection of the tools: Figs. 33 to 35, purely schematically, three differently constructed presses and their
  • FIG. 36 shows a fiction, contemporary plunger in a perspective view
  • Fig. 37 shows a mechanical adjustment
  • Fig. 38 shows a press with plunger and table according to the embodiment in perspective view
  • Fig. 39 shows a variant in one View according to FIG. 38.
  • Fig. 1 shows a typical press 1 of the prior art in front view and plan view.
  • Four arranged at the corners of the table 5 vertical posts 2 each carry guides 3, where a head piece 4 can slide.
  • the head piece 4 is under the influence of a plunger 6, which also transmits the plunger force F (ultimately also the pressing force).
  • the relatively narrow access 7 from the front and 8 can be seen laterally.
  • FIG. 2 shows the deformation of a so-called single-column press under the pressing force in dotted lines;
  • FIG. Fig. 3 shows the corresponding deformation of a multi-jacketed press such as those shown in FIG. 1.
  • Fig. 4 shows, purely schematically, a press 101 according to the invention in a perspective view.
  • the table 105 is connected via a framework 109 and actuators 110 with a head piece 104 belonging to the framework 111.
  • the frameworks 109, 111 are designed statically determined, the rods are charged only to train or pressure, all deformations due to the pressing force are easy and accurate to calculate.
  • the nodes of the frameworks are commercial structures.
  • the six actuators 110 (statically determined design), which form the actual parallel kinematics, are divided into two groups in the illustrated embodiment, three actuators 112 are arranged practically exactly in the pressing direction and are therefore called main actuators, three further actuators 113, the secondary actuators, establish the static certainty, as explained in more detail below.
  • the points of attack of the actuators 110 are known in their training in the field of parallel kinematic, it is referred to the above-mentioned literature. In the description, for reasons of clarity, the points of attack on the table side are referred to as foot points and the points of attack on the side of the head piece as head points. Of course, the entire device is kinematically completely and dynamically virtually completely reversible.
  • the head piece 104 is, already to illustrate this, constructed completely analogous to the table.
  • three bearing stub 114 are provided.
  • FIG. 5 shows, in a nearly complete analogy to FIG. 4, a multi-stand press in which the same reference numerals have been used for parts acting in the same way.
  • Fig. 5 has eight actuators, is thus statically overdetermined. This can, as explained below, bring about various advantages. As if from a comparison of
  • FIGS. 8 and 9 the press of FIG. 5 in matching trim 1114 and with
  • Tool plates 115 once installed, shows: Around the table 115 is a substantially free space, the horizontal bars 116, which are the bases of the
  • FIG. 10 The advantageous situation in the use of such presses in a press line is shown in FIG. 10, from which the good accessibility to all presses and tables can be seen.
  • FIG. 10 The advantageous situation in the use of such presses in a press line is shown in FIG. 10, from which the good accessibility to all presses and tables can be seen.
  • FIG. 10 shows the advantageous situation in the use of such presses in a press line.
  • if necessary automatic tool change in the automotive industry is favored by the side, but also in other manufacturing maintenance and tool change is much easier.
  • FIG. 11 A comparison of Figs. 2 and 3 on the one hand with Figs. 6 and 7 on the other hand shows the significantly reduced deformation under the action of the pressing force, to which even by the framework (also the parallel kinematic is ultimately one) enabled easy and accurate calculation of the deformation comes that makes compensation possible.
  • the embodiment of the invention proposes to provide at certain points of the framework short-stroke cylinder 209, 211 (or the like, below), which, depending on the application, force or position controlled.
  • the position of the nodes of the truss can be calculated via the controller / software of the press and the difference to the optimum position of the tool can be corrected;
  • the force required at the point of control is either pre-set, e.g. in the finite element calculation of the pressing process, calculated and taken into account, or it is concluded on the basis of the first results from the finished workpiece and / or the data from sensors to necessary changes in the locally acting forces.
  • the press To be influenced by the press are: the period it takes the press to get between the upper break point and the first contact of the tool with the blank / sheet metal part (infeed motion), the period of time the press needs to perform the pressing operation (power stroke ) and the time needed for the press to move from the lower press point to the upper break point (free movement); In this case, feed movement and free movement together form the idle stroke.
  • the invention provides, as shown in FIGS. 12 to 14, in one embodiment, a press which combines mechanically effected and hydraulically effected movements with surprising results. It is also this variant of the invention for presses according to the prior art suitable, albeit with the restriction that in such presses compared to presses according to the invention very high dead loads (the posts 2, including all components and drives thereon) must be moved. For the static certainty of this variant, the above applies.
  • this shortening of the pressing cycle can be achieved in a first variant by a combination of vertical movements by movement of the foot points 302 of the (in this case exactly) vertically running actuators 112 of the main actuators 112. It is exploited according to the invention that the drives 301 for the mechanical lifting movement can be very small (weak), since they only during the feed movement and the free movement (does not have to be during the whole movement) must accelerate the masses of press ram and upper mold half but not participating in the power stroke.
  • the bases 302 of the main actuators 112 On the wings are the bases 302 of the main actuators 112, which are thus brought in the idle stroke quickly and synchronously with the rest, hydraulically effected movement, which takes place simultaneously, either in the upper rest position or in the position just before the power stroke.
  • the axes of the main actuators do not run parallel to the pressing direction, and generally not parallel to each other, except during the power stroke, due to the movement of their feet.
  • Actuators 14 which act as an actuator by thequaint Vietnamese pressebung and in their pressing action by the Mauaktuatoren, which are suitably designed as spindles supported.
  • spindles and even ropes with matching baffles and drives may be used instead of the rods, as long as the slave actuators provide movement of the header and the extraction of the ropes of the main actuators against gravity without their assistance.
  • the arrangement of the actuators does not necessarily have to be as shown, it can be chosen numerous other arrangements, in particular the favorable for the calculation of the movements 3-2-1 kinematics.
  • the head piece 104 In this attack at a common head on the movable platform, the head piece 104, three actuators, at another common head point two actuators and finally the sixth actuator by itself at a third Kop ⁇ unkt.
  • the advantages and the possible embodiments of this variant of the parallel kinematics are described in detail in the literature mentioned above and can be easily applied to presses by those skilled in the field of presses with knowledge of the invention.
  • FIG. 24 represents a press according to the parallel kinematics described above, further embodiments with reference to FIGS. 25 to 32 described.
  • FIG. 24 shows a press 600 having a table 605 and a head 604 connected together by generally vertically oriented main actuators 612 and other side-by-side slanted actuators 613.
  • the actuators are cylinder-piston units which are connected to the table 605 via a universal joint 620, respectively.
  • the system consists of four vertical and four oblique actuators and is thus overdetermined twice, once by a vertical actuator 612 and once by an oblique actuator 613.
  • the pressing force can be better distributed to the tool.
  • the pressing force can be dispensed with an expensive backlash-free storage of the actuators on the table and the headpiece by a control technology caused slight strain of the actuators, without having to take a geometric offset between the tool and workpiece in purchasing.
  • the part 602 of the head piece 604 which bears against the sliding guide 603 is not planed, but is cambered inwards, so that only a small bearing surface is created.
  • Corresponding effect could also be provided by differently shaped - inwardly or outwardly arched - guide support surfaces, e.g. spherical, cylindrical, etc., can be achieved.
  • the softness of the guide surface due to the shape can be increased by appropriate choice of material.
  • FIG. 27 and 28 show the press of FIG. 25 in a side view and in a section according to A-A, wherein the gimbal 620 of the cylinder base is highlighted at the table 605 closer.
  • the universal joint is oriented to allow rotation of the actuator about horizontal axes. Generally speaking, the universal joint allows rotations about axes that are normal to the effective direction of the respective actuator. The same applies to the cardan joints that connect the actuators with the head piece.
  • FIG. 29 shows a further variant of the invention in which, instead of the guides 603 from FIG.
  • At least one of the actuators 612a is firmly clamped to the table 605.
  • Another actuator 612b is secured with the table against pivoting about a horizontal axis while pivoting about the horizontal axis normal to it is possible.
  • These actuators 612a, 612b additionally assume the function of a guide and bind three degrees of freedom of the head piece or the attached tool, namely two translational in the horizontal plane and one against pivoting about the vertical axis.
  • the remaining actuators 612 are mounted like those of the example of FIG. 25 with a single universal joint 620 at the table.
  • the clamping of the lifting cylinder is e.g. by supporting the lifting cylinder at the table by two cardan joints 620, 622 spaced vertically from one another.
  • Securing the other lifting cylinder against pivoting about a horizontal axis is e.g. by two vertically spaced joints 620, 623, one of which, 620, is a universal joint and the other a simple pivot 623 which allows rotation about a single horizontal axis.
  • the hinge 623 itself is movable in a horizontal direction, e.g. as part of a cylinder-piston guide. This translational movement is indicated in the figures with an arrow P, while the axis of rotation of the rotary joint is shown with a dashed line.
  • the details of these hinges are shown in FIG. 32, wherein the main illustration of FIG. 32 is a sectional view A-A of FIG. 31 (side view).
  • the other two actuators 612 of the total of four actuators are each connected to the table 605 only via a single universal joint 620.
  • This system with four actuators is simply overdetermined, namely by one of these simple mounted actuators.
  • these examples require at least three actuators.
  • at least three actuators are required whose bases (or head points) are not all arranged on a straight line.
  • the lifting cylinders described below which are designed in the form of long step cylinders, offer a particularly good guide ratio, so that the above-described function of the guide can be reliably taken over by the actuators.
  • the sliding guides of the cylinder must be adapted to the intended use.
  • Another aspect of the invention relates to the interaction of separate tool guides with the rest of the drive and possibly guide system.
  • Press tools usually have their own separate guide systems, which determine the position of the upper tool part (attached to the head piece) and the lower tool part (attached to the table).
  • This tool guide can now lead to undesirable stresses within the entire press, since they lead to a multiple over-determination of the system.
  • the invention proposes that, as soon as the upper and lower tool guide engage each other (this is done, for example, by chamfers, funnel-shaped tapers, rails, etc.), the (clamped or against pivoting securing) actuators 612a, 612b, which otherwise also assume the function of leadership to take their leadership. Through this unlocking the otherwise occurring over-determination is canceled, whereby tension and consequent wear on the tools can be prevented. This unlocking is particularly easy to perform in the variant shown in FIGS. 29, 30.
  • the invention is not limited to the Ausimileungsforrnen described.
  • ball joints can be used, or other joints or combinations thereof, which have the same effect in relation to the storage, clamping and securing described above. It is only important that the degrees of freedom of the head piece are restricted accordingly.
  • the lifting cylinders for the lifting force and the pressing force - master cylinder - must move the lifting ram (press ram) vertically and absorb the moments around the horizontal axes.
  • the lifting ram press ram
  • they must also provide the force for the pressing process (power stroke).
  • the cylinders only have to move their own masses. Therefore, it makes sense to use multi-chamber cylinder to provide more effective area and thus more force in the downward movement and to require less lift volume in the upward movement and thus to achieve higher speed. This is easily possible, in particular in presses according to the invention, since more height is available as a result of the specific arrangement of the cylinders than in presses according to the prior art.
  • FIGS. 15-17 Various cylinder-piston units that are suitable for accomplishing this task, often referred to simply as cylinders for the sake of simplicity, are shown in FIGS. 15-17. It is, as stated, to consider that in the inventive arrangement of the actuators by far the largest power requirement (load stroke) occurs during a small part of the pulling movement of the cylinder-piston units, whereas during most of the pulling movement and the entire Pressure movement only a much lower power requirement (idle, Eilhub) exists.
  • This cylinder 401 is much better suited for pressing than those used in the prior art, but still has disadvantages that are avoided by the cylinder 411 of FIG. 16:
  • this cylinder 411 with basically the same basic structure as in the cylinder 401, in which for similar components, the same reference numerals are used, Leerhubhuntn 408 and 413 are provided with greatly reduced cross-section and with a Leerhubkolben 414 of the piston rod 404 cooperatively.
  • This double-acting Leerhubzylinder can now cause all movements of the head piece 4 during the idle stroke and is either used during the load stroke to support or it will be the two chambers 407 and 413 short-circuited. It may be the Leerhubzylinder 408, 413, 414 optionally provided with its own oil circuit with its own pump, but it can also be supplied by the pump that supplies the load cylinder.
  • the cylinder 401 In order to drive the cross-sectional reduction of the Leerhubhuntn 408, 413 and thus the extension speed of the cylinder-piston unit 411 to the top, the cylinder 401 has a central rod 409 and the piston rod 404 is hollow at its free end and takes the central rod 409 sealingly. Since a dead volume 410 of variable volume is thereby formed inside the hollow piston rod 404, it must be connected to the environment by means of a vent line 412 for the purpose of pressure equalization. If, starting from the position of the piston rod 404 shown in FIG. 16, oil is applied to the idle stroke cylinder 408 and the piston rod 404 is extended, then according to the invention oil is forced out of the idle stroke chamber 413 to the pump without requiring a large supply vessel.
  • the working stroke (pulling movement) begins, which, as will be explained in detail below, first begins with the feed movement, which does not yet require a large force. Therefore, oil is forced into the Leerhubhunt 413 and presses the oil in the Leerhubhunt 408 through the now switched valves in the direction of the pump (which also includes a small reservoir for oil, possibly with a cooling and / or cleaning device), the movement takes place accordingly quickly. Similarly, oil is forced out of the empty chambers 407 directly into the draw chambers 402 by shorting the valves in the fluid lines (FIG. 23), that is, without passing through the pump or a reservoir (short circuit).
  • both tension chambers 402 are pressurized, the full force is available, of course at a correspondingly reduced speed.
  • the Leerhubzylinder 408, 413, 414 can support this movement or is shorted.
  • steps 4 + 5 pressurizing only one of the two chambers 402 during the power stroke (steps 4 + 5), which as with the feed movement, with the same oil flow to an increase (in this example, for example, to a doubling) of the pressing speed at deliberately reduced (about halved) Pressing force while the oil between the non-activated chambers is simply pushed back and forth (short-circuit operation).
  • This embodiment has the disadvantage that the Leerhubzylinder 408, 413, 414 because of the different cross-sections of the chambers 408 and 413 is no longer to build as a synchronous cylinder. Thus, an oil flow from and to an oil reservoir of only limited dimensions must be taken into account during the rapid stroke.
  • a further concern of the invention is the following: At simultaneous presses (eg heat press) the energy requirement at the same time (when all 5-6 presses simultaneously have to exercise the full pressing force in the working stroke), the highest required electrical maximum load from the power plants be made available, which means a considerable effort and leads to high energy consumption costs of the operator of such facilities.
  • the invention in an embodiment which is equally applicable to presses of any of the variants described above and to presses of the prior art, provides a new system of power supply and energy storage for presses.
  • a lifting cycle is now, as already stated above, starting from the top dead center of the press ram, starting from:
  • the idea according to the invention is now the use of a flywheel, which is set in rotation by a drive source (eg electric motor, hydraulic motor, etc.) which outputs a constant torque to the flywheel.
  • a controllable hydraulic pump (motor) now decreases power at this flywheel according to demand, which is appropriately translated into oil speed and oil pressure in the pump according to the desired speed of the press ram and the required pressing force.
  • energy is available during downhill travel and when braking and is delivered to the flywheel via the pump, which then operates as a motor.
  • energy is required and removed from the flywheel by means of the pump and delivered to the hydraulic cylinders.
  • FIGS. 18-23 show purely schematically (real arrangements are preferably with aligned shafts with shaft couplings without any teeth) and unrealistically arranged next to the drive cylinder-piston units, but clearly and vividly some embodiments of this further development of the invention; namely, FIGS. 18, 19 a simple variant, FIGS. 20, 21 an embodiment and FIGS. 22 and 23 a preferred variant.
  • Oil pump 504 drives by means of a hydraulic 503 with a cylinder-piston unit
  • the flywheel 502 has, for example, a 600 ton press
  • Cylinder-piston unit 401 corresponds to that of Fig. 15, the leadership of the individual
  • the hydraulic lines have no valves, the throttling when passing through valves and the associated destruction useful energy (pressure energy is converted into heat) is completely avoided, as the following examples show.
  • the circuit 505 is switched, the rear tension chamber 402 is then directly connected to the empty chamber 407, another connection with a reservoir creates the possibility of volume compensation in all directions; in the pressure chamber 403 oil is pressed, the front tension chamber 402 is the oil in it in the direction of the pump and is also in communication with the reservoir.
  • the front tension chamber 402 is the oil in it in the direction of the pump and is also in communication with the reservoir.
  • FIG. 22 and 23 shows an arrangement with a cylinder-piston unit 411 according to FIG. 16.
  • the idle stroke cylinder 408 is acted upon by the pump 506 and moves the piston rod; at the same time the counter chamber 413 is emptied, the pump 506 is required only a minimal reservoir; It may be a separate hydraulic circuit or connected to the load circuit (pump 504). In this load cycle with the pump 504, the traction chambers 402 are emptied, while the oil of the traction chambers 402 flows directly into the empty chambers 407; The load circuit also requires only a minimal reservoir, which it optionally shares with the Leerhubniklaufes.
  • the drive 501 permanently provides for the application of drive torque to the flywheel 502, at least as long as it is not switched off by a speed monitor.
  • the pump 504 and possibly the pump 506 power from the flywheel which reduces its speed.
  • power is also applied to the pump side, which can also be delivered to the flywheel by switching the pumps; which further saves energy.
  • flywheel press drive with separately switchable sub-cylinders in order to realize correspondingly higher speeds in the partial load range and the like, but it is always essential that through the inventive measures the flow of only partially open valves and the concomitant throttle loss completely or almost completely is avoided.
  • the measures according to the invention can be used advantageously without it being necessary to take the other measures;
  • the energy storage device according to the invention can be used for pressing of all kinds.
  • FIGS. 33 to 39 show an advantageous embodiment, which is advantageous in particular in parallel-kinematically constructed presses with actuators subjected to tension, as shown, since the overall height is not critical there:
  • Figs. 33 to 35 show, purely schematically, three differently constructed Mehrschreibrpressen, wherein the mutually corresponding parts, regardless of their different, depending on the type, training, provided with the same reference numerals.
  • 33 and 34 show multi-stand presses of conventional construction, with a press frame 710, a table 720 and a punch 730. During the operation, the upper and lower frame sections spread in a cushion, since the pressing forces are introduced substantially centrally.
  • FIG. 35 shows, analogously, the deformation of a press of a parallel kinematic construction, in which the press frame consists of actuators which are subjected almost exclusively to tension during the working process and thus are not subject to any deformation falling from their longitudinal axis and wherein the clamping plates 721, 731
  • the deformation takes place virtually inversely to that in the press according to FIG. 33.
  • the invention proposes to divide the plunger and / or the table, as already mentioned above, in the pressing direction.
  • Fig. 36 shows a possible embodiment of the invention with reference to a plunger 730.
  • This consists essentially of a holding part 733, framed in Fig. 36, and a tool holder 732, the (not visible) underside 731 represents the platen;
  • the adjusting devices, not shown, come at the adjustment points 734 provided for this purpose.
  • the holding part 733 has the task of holding the tool carrier 732 in position and biasing it, taking into account the expected pressing forces, so that the deformation of its clamping surface 731 remains minimal in the course of the pressing process.
  • the force is introduced via the four bearing points 735, which is particularly favorable for parallel kinematic presses, and a three-dimensional framework 737, which directs the introduced into the bearings 735 forces in the adjustment 734.
  • the bearings 735 are provided on wings 738, which also have connecting pieces 739 to the tool carrier 732.
  • five adjustment points 734 and thus adjusting devices are provided, a large-sized in the center and four smaller sized in the middle of each outer contour of the tool carrier 732.
  • the tool carrier 732 itself has a box shape, i. it consists of a lying in the normal plane to the pressing direction grid, which represents the track of the running in the pressing direction outer walls and the inner walls.
  • the grid construction with relatively high (in the pressing direction) walls 736 whose distance B is smaller than their height, one achieves a very light and thereby very rigid construction in the pressing direction.
  • the ability to choose the distance B small one reaches a whole set of clamping points for the tool, which are accurate and reliable in one plane.
  • the connecting pieces 739 are fastened to the corners of the tool carrier 732 and essentially absorb the tensile forces arising on the one hand from the weight and the inertia of the tool carrier and, on the other hand, from the tensile forces; the adjustment points 734 are only suitable for the transmission of pressures.
  • a punch 730 in other ways possible, so when used in a conventional press with central force introduction, of course, the location of the bearings 735 centrally above the support member 733, which then has more the shape of a truncated pyramid.
  • the tool carrier 732 is essentially to be constructed as shown, adaptations to the outline of the possible pressing surface and to the available height, which is already predetermined in existing presses, can be taken into account.
  • Fig. 37 shows the simplest of all possible adjusting 740, a correspondingly large-sized screw, which is screwed with its thread 741 in a correspondingly sized mating thread of the holding part 733 at the adjustment point 734 and fixed in the appropriate angular position.
  • FIG. 38 shows an exemplary embodiment of a parallel-kinematically constructed press with virtually identical design of table and ram, whereby both the investment and the storage for maintenance and spare parts can be significantly reduced, and what is the following to be executed:
  • the clamping plate 721 of the tool carrier 722 is brought into the desired position and prestressing, the tool 750 is fastened in a suitable manner on the clamping plate 721.
  • the pressing force is now applied by four actuators, namely hydraulic cylinder-piston units 711.
  • actuators namely hydraulic cylinder-piston units 711.
  • To increase the pressing force (while the hydraulic cylinder-piston unit 711 claimed to train) are axially connected in series piston and cylinder used, as can be seen from the guidance of the indicated hydraulic lines 712.
  • FIG. 39 A variant of the invention is shown in FIG. 39.
  • a tool carrier 732 is provided both in the table and in the plunger, which has a rectangular cross section and therefore with more, namely eight adjustment points 734 against the associated holding part 733 is biased.
  • the holding part is of course also provided with a rectangular outline and has a customized framework for power distribution. It can easily be seen from a comparison of Fig. 38 and Fig. 39 that it is not necessary to make the holding part noticeably higher or heavier at the larger pressing area than the smaller one, this is an advantage which the invention makes possible:
  • the deformation of the holding part 732 can be taken into account in the determination of the bias and thus does not matter, as long as only the strength itself is not affected.
  • a mass savings in the ram is achieved, which increases cubically with the linear dimensions of the plunger, which is surprisingly saved on investment costs, maintenance costs and energy enormously.
  • clamping plates 721, 731 are still to be stated that they can be made significantly thinner compared to the prior art (in a calculated example, about 120 mm instead of 310 mm), without causing an impermissible deformation occurs. This is due to the corresponding bias and the mechanical stability of the tool carrier 732.
  • FIGS. 38 and 39 show exemplary embodiments which can be modified in many ways.
  • the application of the pressing force P can be different take place and it can be done the guide of the punch with respect to the table in other ways.
  • the principle according to the invention of the desired and predetermined pretensioning of the clamping plates 721, 731 can also be applied to presses which are not force-determined but, for example, like the eccentric presses or toggle presses, determine away. This is clear to those skilled in the field of press construction and a corresponding application in the field of differently constructed presses brings no problems.
  • the tool holder does not have to have the illustrated box structure, but can be variously modified:
  • the outer walls which are only stabilized on the one hand by the inner walls, can be correspondingly thicker and therefore more stable, in order to reliably prevent bulging or kinking.
  • the initiation of the holding forces on the connecting pieces 39 can take place at locations other than shown, but the solution shown is optimal because of the good power flow directly into the wings 738 in most cases.
  • the drive as usual in conventional presses, attacks centrally (from above), think again; a likewise central attachment is then preferable.
  • the materials are known from the press construction materials and the skilled worker. When sizing, as already mentioned, because of the bias to be chosen within wide limits, without any disadvantage, a total deformation can be accepted, which makes a significant weight saving possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Press Drives And Press Lines (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Abstract

L'invention concerne une presse de formage de matériau, comportant une table (5) et une tête (4) munie d'un coulisseau pouvant être animé d'un mouvement de monte et baisse par rapport à la table au moyen d'un système d'entraînement de presse dans le sens de pression. L'invention se caractérise en ce que la pièce de tête (4) est la plateforme mobile d'un dispositif à cinématique parallèle (101), dont la plateforme fixe est stationnaire par rapport à la table (5). Des modes de réalisation de l'invention concernent l'agencement des actionneurs (112, 113) du dispositif à cinématique parallèle (101), leur mode de réalisation, une application d'un volant réduisant les pics d'énergie ainsi que le fonctionnement particulier d'une telle presse et un mode de réalisation de la table ou du coulisseau de la presse.
PCT/AT2009/000285 2008-07-30 2009-07-23 Presse de formage de matériau WO2010012014A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009001795T DE112009001795A5 (de) 2008-07-30 2009-07-23 Presse zum Umformen von Material

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
ATA1181/2008 2008-07-30
AT11812008 2008-07-30
AT13532008A AT507110B1 (de) 2008-07-30 2008-08-29 Presse zum umformen von material
ATA1353/2008 2008-08-29
ATA1571/2008 2008-10-07
AT15712008A AT507111B1 (de) 2008-07-30 2008-10-07 Presse

Publications (2)

Publication Number Publication Date
WO2010012014A2 true WO2010012014A2 (fr) 2010-02-04
WO2010012014A3 WO2010012014A3 (fr) 2010-04-22

Family

ID=41258895

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT2009/000285 WO2010012014A2 (fr) 2008-07-30 2009-07-23 Presse de formage de matériau

Country Status (2)

Country Link
AT (1) AT507111B1 (fr)
WO (1) WO2010012014A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012130364A1 (fr) * 2011-04-01 2012-10-04 Uniflex-Hydraulik Gmbh Presse radiale
WO2013008022A3 (fr) * 2011-07-14 2013-05-16 Subsea 7 (Uk Service Company) Limited Améliorations se rapportant à la pose de canalisations
WO2019057230A3 (fr) * 2017-09-21 2019-09-06 Kiefel Gmbh Machine de matriçage, un système d'adaptation d'outil de matriçage, outil de matriçage, procédé d'adaptation d'une machine de matriçage, procédé d'adaptation de machine de matriçage, procédé de fonctionnement d'une machine de matriçage et utilisation d'un outil de matriçage inférieur

Citations (10)

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FR2329438A1 (fr) * 1975-10-27 1977-05-27 Moules Mecaniques Precision Perfectionnements aux presses a presenter
US4063453A (en) * 1977-03-03 1977-12-20 Mts Systems Corporation Adjustable space frame for testing machine
WO1987003535A1 (fr) * 1985-12-12 1987-06-18 Unto Ahoste Presse pour mise en balles
FR2600932A3 (fr) * 1986-07-03 1988-01-08 Inoplast Sa Perfectionnements aux presses de moulage, notamment par compression de materiaux composites ou autres
DE3802266A1 (de) * 1988-01-27 1989-08-10 Doege Eckart Presse
US4873923A (en) * 1986-05-16 1989-10-17 Manning Douglas E Hydraulic press platon support
DE19753949A1 (de) * 1997-12-05 1999-09-02 Doege Flexible Umformpresse mit steuerbarer nichtlinearer Stößelbewegung
DE10017462A1 (de) * 2000-04-07 2001-10-18 Fraunhofer Ges Forschung Taumelpresse
WO2003059581A1 (fr) * 2002-01-16 2003-07-24 Abb Ab Robot industriel
US20080047651A1 (en) * 2006-08-25 2008-02-28 Adp Engineering Co., Ltd. Substrate bonding apparatus having alignment unit and method of aligning substrates using the same

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DE3116379A1 (de) * 1979-12-14 1982-12-23 Bison-Werke Bähre & Greten GmbH & Co KG, 3257 Springe Heizplattenpresse
US4615857A (en) * 1984-11-30 1986-10-07 Motorola, Inc. Encapsulation means and method for reducing flash
DE4415577B4 (de) * 1994-05-03 2007-02-22 Müller Weingarten AG Einrichtung zur Kompensation bzw. gezielten Einstellung von Durchbiegungen in Pressen der Umformtechnik
ITTV20060198A1 (it) * 2006-11-03 2008-05-04 Inglass Spa Struttura portante ausiliaria per presse e pressa per la produzione di manufatti in materiale plastico provvista di tale struttura.

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2329438A1 (fr) * 1975-10-27 1977-05-27 Moules Mecaniques Precision Perfectionnements aux presses a presenter
US4063453A (en) * 1977-03-03 1977-12-20 Mts Systems Corporation Adjustable space frame for testing machine
WO1987003535A1 (fr) * 1985-12-12 1987-06-18 Unto Ahoste Presse pour mise en balles
US4873923A (en) * 1986-05-16 1989-10-17 Manning Douglas E Hydraulic press platon support
FR2600932A3 (fr) * 1986-07-03 1988-01-08 Inoplast Sa Perfectionnements aux presses de moulage, notamment par compression de materiaux composites ou autres
DE3802266A1 (de) * 1988-01-27 1989-08-10 Doege Eckart Presse
DE19753949A1 (de) * 1997-12-05 1999-09-02 Doege Flexible Umformpresse mit steuerbarer nichtlinearer Stößelbewegung
DE10017462A1 (de) * 2000-04-07 2001-10-18 Fraunhofer Ges Forschung Taumelpresse
WO2003059581A1 (fr) * 2002-01-16 2003-07-24 Abb Ab Robot industriel
US20080047651A1 (en) * 2006-08-25 2008-02-28 Adp Engineering Co., Ltd. Substrate bonding apparatus having alignment unit and method of aligning substrates using the same

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012130364A1 (fr) * 2011-04-01 2012-10-04 Uniflex-Hydraulik Gmbh Presse radiale
WO2013008022A3 (fr) * 2011-07-14 2013-05-16 Subsea 7 (Uk Service Company) Limited Améliorations se rapportant à la pose de canalisations
CN103842702A (zh) * 2011-07-14 2014-06-04 萨博赛7有限公司 涉及管敷设的改进
US9200728B2 (en) 2011-07-14 2015-12-01 Subsea 7 Limited Pipelaying
US9719613B2 (en) 2011-07-14 2017-08-01 Subsea 7 Limited Pipelaying
WO2019057230A3 (fr) * 2017-09-21 2019-09-06 Kiefel Gmbh Machine de matriçage, un système d'adaptation d'outil de matriçage, outil de matriçage, procédé d'adaptation d'une machine de matriçage, procédé d'adaptation de machine de matriçage, procédé de fonctionnement d'une machine de matriçage et utilisation d'un outil de matriçage inférieur

Also Published As

Publication number Publication date
WO2010012014A3 (fr) 2010-04-22
AT507111B1 (de) 2012-04-15
AT507111A1 (de) 2010-02-15

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