WO1988003448A1 - Procede et dispositif de transmission et d'entretien d'energie de deformation - Google Patents

Procede et dispositif de transmission et d'entretien d'energie de deformation Download PDF

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Publication number
WO1988003448A1
WO1988003448A1 PCT/DE1987/000504 DE8700504W WO8803448A1 WO 1988003448 A1 WO1988003448 A1 WO 1988003448A1 DE 8700504 W DE8700504 W DE 8700504W WO 8803448 A1 WO8803448 A1 WO 8803448A1
Authority
WO
WIPO (PCT)
Prior art keywords
support parts
support
mass
parts
tool support
Prior art date
Application number
PCT/DE1987/000504
Other languages
German (de)
English (en)
Inventor
Erich Goergens
Original Assignee
Erich Goergens
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Erich Goergens filed Critical Erich Goergens
Publication of WO1988003448A1 publication Critical patent/WO1988003448A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D15/00—Shearing machines or shearing devices cutting by blades which move parallel to themselves
    • B23D15/02—Shearing machines or shearing devices cutting by blades which move parallel to themselves having both upper and lower moving blades
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/34—Drives for hammers; Transmission means therefor for power hammers operating both the hammer and the anvil, so-called counter-tup
    • 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
    • B30B1/30—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 the pull of chains or ropes

Definitions

  • Process and device for transmitting or supporting deformation energy which is impulse-free or impulse-generating, from force, travel or energy-dependent drive units (12, 13, 14, 15, 16) in respect of resting or mov - ably supported bodies (4) by means of two thereby force-connected driv- ing or driven co-operating support parts (3a, 3b) which are directly or indirectly supported on support masses (1, 2) so as to be able to move in opposite directions and keep the support masses free from Impulses or which (while representing a part of same) do not achieve any lever action on these by the impulse.
  • the invention relates to a method for transferring or supporting force-free or force-generating deformation energy from drive units (12, 13, 14, 15, 16) in relation to bodies (4) supported at rest or in motion by means of two supporting parts (3a, 3a, 3b), which are supported directly or indirectly on the supporting mass (1, 2), movably and which keep the supporting mass free of force shocks, or which represent part of the same, do not achieve any leverage on these by way of the frictional connection.
  • the invention also relates to a device according to claim 11 for the transmission or support of power surge-free or power surge-generating deformation energy, in particular from hydraulically actuatable or an expanding mass representing force, displacement or energy-bound drive components (12, 13, 14, 15, 16) with respect to resting or Moving supported workpiece bodies (4) by means of two non-positively connected, driving or driven interacting tool support parts (3a, 3b), which are directly or indirectly supported on guide columns (2) or foundation-like support masses (1) or represent part of the same .
  • Such devices are known from the prior art as a press, forging hammer, bending machine, punch, guillotine shear or recoil-damping device.
  • a counterblow hammer forging hammer
  • the hydraulically actuated drive unit which generates a power surge is in each case arranged between a tool part and the machine frame, as a result of which the dynamic reaction forces of the power surge are transmitted to the machine frame with each work cycle.
  • the machine frame and adjacent surrounding structures are subjected to great loads and disturbing vibrations or gravity waves are generated or transported.
  • both the tools and the machine frames have to be made very solid in order to adequately support the deformation energy flowing there, which requires great expenditure and requires a limited construction.
  • the object of the invention is therefore to create a method for monitoring the reaction of the tools or support bodies which react with one another in a supported or unsupported manner.
  • the invention has for its object to provide a device for changing the shape of a workpiece or for supporting impulsive bodies of the type mentioned, in which the machine frame or the supporting device compared to that by the drive force or acceleration of the tools or support body, is isolated.
  • the drive units generating a power surge are non-positively connected exclusively via the tool support parts or only support elements which are trimmed thereon. Furthermore, in that, in the case of drive units which operate without a surge, only one of the tool support parts (3a, 3b) or any support elements (8,9,10,11) or workpiece body on the guide column (2) or the machine frame (1) is stored at rest or are trimmed.
  • the device is always in static equilibrium with the machine frame (1), while the drive units are always actively static or energetic equilibrium via the tool support parts.
  • counter-forces of the same size are converted into an active or passive static balance, ie there they continue to act with the same driving forces or are in their rest position due to their mass and bearing condition.
  • Machine frames (1) so insulated from deformation energy have the consequence that the device can be supported directly on any surrounding structures or foundations.
  • the invention has the advantage that such devices cannot generate or transport unwanted vibrations or gravity waves.
  • the support device or drive unit there is a particular advantage according to the invention in that no changes in position are forced, particularly in the case of mobile systems with power surge insulation.
  • advantageous solutions can also be achieved in vehicle construction. For example to change the centrifugal force in accelerated transport systems (such as tank trucks) as a curve stabilizer or collision protection.
  • the energetically isolated systems or devices according to the invention can therefore be further optimized particularly advantageously because they provide any degrees of freedom inside or outside the device. If the invention is used correctly, it will always be possible to isolate bodies, devices or systems which are energetically coupled according to the prior art and thus to open up further areas of application.
  • Fig. 1 shows a section through a first embodiment of the invention for the transmission of power-generating deformation energy
  • FIG. 2 shows a section through a second exemplary embodiment of the invention for supporting force-generating deformation energy of a drive unit (15)
  • FIG. 3 shows a section through a third exemplary embodiment of the invention for the transmission of power-generating deformation energy
  • Fig. 4 shows a section through a fourth exemplary embodiment
  • Fig. 5 shows a section through a fifth embodiment of the invention for the transmission of power-generating deformation energy with pendulum-like tool support parts
  • FIG. 6 shows a section through a sixth exemplary embodiment of the invention for the transmission of power-generating deformation energy as a detail of FIG. 5
  • FIG. 7 shows a section through a seventh exemplary embodiment of the invention for the transmission or support of force-generating forging change energy in the form of a transverse drive (16).
  • Fig. 8 shows a section through an eighth embodiment for the transmission of (the support of a drive unit (15)) only limited force-generating deformation energy.
  • Fig. 9 shows a section through a ninth exemplary embodiment for the transmission of preferably impact-free deformation energy with low support worlds.
  • the first exemplary embodiment is a device which is comparable to a counterblow hammer (known from the prior art).
  • the drive unit (12) is not supported here between the tool support part (3a, 3b) and the machine frame (1) but via a rope-like traction means (8) wrapping around the tool support parts (a3, 3b).
  • a machine frame in the true sense of the word is no longer required in a device for transmitting power-generating deformation energy for shaping or changing a workpiece body (4).
  • the device for shaping or changing the shape of a workpiece body (4) consists of two non-positive connections sig with the foundation (1) connected guide columns (2), which serve to guide two tool support parts (3a, 3b) along the column direction.
  • the tool support parts (3a, 3b) are each mounted on the guide column (2) with low friction.
  • One end of a piston-cylinder system (12) serving as a drive unit is coupled to a tool support part (3a, 3b).
  • the other end of the piston-cylinder system (12) acts against a further rope (8), which also serves as a traction device and endlessly loops around the tool support parts (3a, 3b).
  • the traction means is guided through bores in the tool parts (3a, 3b) and is additionally connected approximately in the middle between the tool support parts (3a, 3b) with a workpiece holder (10) which acts as a carrier for a workpiece body ( 4) serves.
  • additional centering rods (11) are provided, which prevent the tool movement from escaping from the direction specified by the guide column (2).
  • tool support parts (a3, 3b) and workpiece body (4) can be precisely aligned with one another.
  • the guide columns (2) take up the static weight of the tool support parts (3a, 3b) via the traction cables (6) and the deflection rollers (5) and transfer this to the foundation.
  • a pressure medium for example hydraulic oil
  • the piston-cylinder system is deflected and the two tool support parts (3a, 3b) move as a result sen towards each other along the direction given by the centering rods (11).
  • This movement takes place through the rigid coupling of the drive unit with the two tool support parts (3a, 3b) in such a way that when the tool support parts (3a, 3b) strike the workpiece body (4) which is held by the workpiece holder (10) in the Middle is held.
  • the pulse triggered by this is recorded in the tool support parts or by the workpiece body (4). Since the frictional connection does not take place via bearings connected to the machine frame, this does not have to absorb the reaction force that occurs during impact. Rather, in this arrangement, in each operating state of the device, only the weight forces of the tool support parts (3a, 3b) are transmitted to the guide columns (2) via the deflection rollers (5).
  • the workpiece holder (10) can also be supported in the manner shown in dashed lines, analogously to the tool support parts (3a, 3b) with traction means (6) and ballast mass (17).
  • the compensating mass (18), which is mounted in a pendulum-like manner, can be positioned or designed as desired while maintaining the function, or e.g. Have guide runners.
  • the second exemplary embodiment shown in FIG. 2 differs from the first in that the tool support parts (3a, 3b) are coupled virtually from the inside by a drive unit (15) in the form of an expanding mass (4), for example a plastic mass.
  • a drive unit in the form of an expanding mass (4), for example a plastic mass.
  • the tool support parts (3a, 3b) are set in opposite directions, which can be counter-positively coupled by means of the drive units (12) and traction means (8) shown in dashed lines (as in FIG. 1).
  • the opening travel or the filling quantity can be determined via force-dependent, movable or rigid stops (3c) on traction means (6).
  • the traction means (6) between them becomes a traction means (3d) which is additionally subjected to tension in the equilibrium.
  • the tool support part has an overlapping (enveloping the tool support part (3b)), leading and support-limiting body shape.
  • the centering rods (11) or guide columns (2) were replaced by a partially rod-like traction device (6 or 3d) which are only guided at any point on a support mass (1).
  • the deflection roller (5) is mounted with its axis of rotation (7) directly on any supporting mass (1).
  • a spring-like tension element (8) between the tool support part (3a) and the stop (3c) ensures, among other things. For a reset to the starting position.
  • FIG. 2 differs significantly from FIG. 1 with the same function, but in its application purpose.
  • the support mass (1) is a supporting or supporting mobile device, this can be kept immovable according to the invention, while between the tool support parts (3a, 3b) a force surge due to expansion of a dashed line, from the opening completely or partially escaping workpiece body (4) is generated.
  • First the tool support part (3) is accelerated, which also applies to (3a) via traction means (3d, 6) and deflection roller (5). If the tool supporting parts (3a, 3b) have a sufficiently inert mass, the drive energy would be completely converted into potential energy over a corresponding distance.
  • the spring (8) on (3d) absorbs or stores the required restoring energy or is designed for additional damping of the tool support part movement.
  • existing kinetic energy would result in the tool support parts (3a, 3b) colliding over the stop (3c) and in this way, in (3d) building equal counter-forces into equilibrium.
  • the predominant force of the spring (8) causes the tool support parts to be returned to the starting position.
  • recoil forces can be supported, absorbed or converted into potential energy by acting on the drive units (12) shown in broken lines by means of the traction means (8) interacting with them in a force-fitting manner.
  • the collision can also take place via the frame-like tool support part (3a).
  • the isolation of the power surge has a particularly advantageous effect on the device, not least because the additional degrees of freedom mean that fewer undesirable reactions in the interaction of the coupled components are possible.
  • action reaction
  • degrees of freedom mean that there is no obstacle in their direction of action and consequently no reaction can take place.
  • the fourth application example according to Flg. 4 differs from the third only in that traction means (6) is guided as in Fig. 1 or Fig. 2 and two pistons as tool support parts (3a, 3b) are coupled therewith. It follows from this that the one-piece cylinder each has the function of a tool support part (3a, 3b) and therefore two workpiece bodies (4) are used simultaneously.
  • Fig. 5 shows a fifth embodiment of the invention, which differs from the previous one in that, despite the power-generating drive unit (12), the tool support parts (3a, 3b), as a relatively large mass, directly on the support mass (1) (but rotatable ) are stored.
  • the three axes of rotation (7 and 7a) provide this device with the required degrees of freedom for a reaction-free function with respect to the support mass (1) in the direction of the force action.
  • arbitrarily shaped support bodies (5) could also be used, which means that then no division of the tool support body into two parts (3a, 3b) would be defined.
  • Fig. 6 shows a detailed solution to Fig. 5 for storing a relatively heavy mass or a tool support part (3a, 3b) or support part (5) on a support mass (1) over at least the required angle (alpha max.) To to avoid undesirable reactions on the support mass (1).
  • the seventh exemplary embodiment shown in FIG. 7 shows a transverse drive (16).
  • Deviating here is the drive unit (12), which is arranged transversely to the direction of movement of the tool support parts (a3, 3b) and which can be rotatably connected at any point to the articulation points (9a) of the obliquely or horizontally articulated articulated rods (9). It is optional how many rods (9) are arranged in which direction to deflect, but the drive unit (as in this example) must be arranged between oppositely deflecting joint rods.
  • the version shown in dashed lines can also be used, the frame-like traction means (8) also being able to be realized from jointed rods (9).
  • This cross drive is particularly characterized by the reliable, parallel guidance and support function. Its use enables the highest precision of the workpiece body (4) produced in such devices.
  • Fig. 8 shows an eighth embodiment, which differs from the first in that the tool support parts (3a, 3b) instead of traction means (6) and deflection rollers (5) directly on the guide column (2) non-positively with equally large counterforces or are supported via drive unit (12).
  • a load caused by a power-generating method depends on the acceptance of a correspondingly increasing discharge of structure-borne noise via the guide column.
  • an equivalent function relating to the support can only be achieved if absolutely synchronous operation of the two tool support parts (3a, 3b) is ensured and the tensile load between the drive units, which does not have a displaceable effect, is not a criterion.
  • the ninth exemplary embodiment according to FIG. 9 is the only one largely tied to power surge-free procedures, which, however, can be compensated for with increasing span and number and synchronous loading of all drive units (also shown in dashed lines). That is, in the most favorable case (with very large distances between the guide columns (2)), this device can be regarded as almost equivalent to all the others (FIGS. 1 to 8).
  • the deflection that increases with the span is also advantageously compensated for by drive units (12) via traction means (8) because a relatively favorable loading of the tool support parts (3a, 3b) is achieved. Nevertheless, the device according to FIG. 9 appears unsuitable for use in mobile support masses (1). Compared to the forming machines of a similar design known from the prior art (such as hydraulic presses), however, the advantage clearly lies in dispensing with a machine frame or in the fact that tools of almost unlimited size (lightweight construction) can be produced, stabilized and used economically.
  • any further configurations can be achieved according to the invention, additional areas of application can be opened up and additional advantages can be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

Procédé et dispositif de transmission et d'entretien d'énergie de déformation libre d'impulsions ou engendrant des impulsions à partir d'unités d'entraînement (12, 13, 14, 15, 16) dépendant d'une force, d'une course ou d'une énergie, par rapport à des corps (4) au repos ou supportés de manière mobile au moyen de deux parties support (3a, 3b) à entraînement ou entraînées qui coopèrent et sont ainsi fixées par liaison de force, lesdites parties étant supportées directement ou indirectement sur des masses support (1, 2) de manière à pouvoir se déplacer dans des directions opposées et garder les masses support.
PCT/DE1987/000504 1986-11-14 1987-11-10 Procede et dispositif de transmission et d'entretien d'energie de deformation WO1988003448A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3638999 1986-11-14
DEP3638999.4 1986-11-14
DEP3700277.5 1987-01-07
DE3700277 1987-01-07

Publications (1)

Publication Number Publication Date
WO1988003448A1 true WO1988003448A1 (fr) 1988-05-19

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PCT/DE1987/000504 WO1988003448A1 (fr) 1986-11-14 1987-11-10 Procede et dispositif de transmission et d'entretien d'energie de deformation

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WO (1) WO1988003448A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU617996B2 (en) * 1987-04-03 1991-12-12 Amgen, Inc. Novel proteolytic enzymes
EP0511504A2 (fr) * 1991-04-01 1992-11-04 The Dow Chemical Company Presse de moulage pour moules séparables

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2863343A (en) * 1954-04-15 1958-12-09 Schloemann Ag Counterblow hammers
US3329003A (en) * 1963-11-05 1967-07-04 Nat Res Dev Impulse-forming and like machines
GB1413364A (en) * 1973-06-14 1975-11-12 Inst Gidrodinamiki Sibirskogo Counterstroke hammer
DE3417712A1 (de) * 1984-05-12 1985-11-14 Andreas 8077 Reichertshofen Pöhl Buch-presse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2863343A (en) * 1954-04-15 1958-12-09 Schloemann Ag Counterblow hammers
US3329003A (en) * 1963-11-05 1967-07-04 Nat Res Dev Impulse-forming and like machines
GB1413364A (en) * 1973-06-14 1975-11-12 Inst Gidrodinamiki Sibirskogo Counterstroke hammer
DE3417712A1 (de) * 1984-05-12 1985-11-14 Andreas 8077 Reichertshofen Pöhl Buch-presse

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU617996B2 (en) * 1987-04-03 1991-12-12 Amgen, Inc. Novel proteolytic enzymes
EP0511504A2 (fr) * 1991-04-01 1992-11-04 The Dow Chemical Company Presse de moulage pour moules séparables
EP0511504A3 (en) * 1991-04-01 1993-01-13 The Dow Chemical Company Molding press for multiple molds
US5234332A (en) * 1991-04-01 1993-08-10 The Dow Chemical Company Molding process for multiple molds

Also Published As

Publication number Publication date
AU8170987A (en) 1988-06-01

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