EP0268681B1 - Presse a vis a double effet - Google Patents

Presse a vis a double effet Download PDF

Info

Publication number
EP0268681B1
EP0268681B1 EP86904989A EP86904989A EP0268681B1 EP 0268681 B1 EP0268681 B1 EP 0268681B1 EP 86904989 A EP86904989 A EP 86904989A EP 86904989 A EP86904989 A EP 86904989A EP 0268681 B1 EP0268681 B1 EP 0268681B1
Authority
EP
European Patent Office
Prior art keywords
screw
stop
spindle
slope
stops
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP86904989A
Other languages
German (de)
English (en)
Other versions
EP0268681A4 (fr
EP0268681A1 (fr
Inventor
Jury Alexandrovich Bocharov
Anatoly Vasilievich Safonov
Anatoly Petrovich Nosov
Jury Iosifovich Tamaris
Evgeny Semenovich Lunkov
Vladimir Ivanovich Myakinenkov
Igor Yakovlevich Perepechin
Leonid Izrailievich Rudman
Viktor Petrovich Salov
Igor Viktorovich Bovykin
Mark Moiseevich Zaidlin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
EXPERIMENTALNY NAUCHNO-ISSLEDOVATELSKY INSTITUT KUZNECHNO-PRESSOVOGO MASHINOSTROENIA 'ENIKMASH'
Moskovskoe Vysshee Tekhnicheskoe Uchilische Imeni N E Baumana
Original Assignee
EXPERIMENTALNY NAUCHNO-ISSLEDOVATELSKY INSTITUT KUZNECHNO-PRESSOVOGO MASHINOSTROENIA 'ENIKMASH'
Moskovskoe Vysshee Tekhnicheskoe Uchilische Imeni N E Baumana
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 EXPERIMENTALNY NAUCHNO-ISSLEDOVATELSKY INSTITUT KUZNECHNO-PRESSOVOGO MASHINOSTROENIA 'ENIKMASH', Moskovskoe Vysshee Tekhnicheskoe Uchilische Imeni N E Baumana filed Critical EXPERIMENTALNY NAUCHNO-ISSLEDOVATELSKY INSTITUT KUZNECHNO-PRESSOVOGO MASHINOSTROENIA 'ENIKMASH'
Publication of EP0268681A1 publication Critical patent/EP0268681A1/fr
Publication of EP0268681A4 publication Critical patent/EP0268681A4/fr
Application granted granted Critical
Publication of EP0268681B1 publication Critical patent/EP0268681B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/18—Drives for forging presses operated by making use of gearing mechanisms, e.g. levers, spindles, crankshafts, eccentrics, toggle-levers, rack bars
    • 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
    • B30B1/18—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 screw means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8841—Tool driver movable relative to tool support
    • Y10T83/8847—Screw actuated tool support

Definitions

  • the present invention relates to the field of mechanical engineering and in particular relates to a double-acting screw press.
  • This invention can most advantageously be used in drop forging, in particular when forging individual parts in closed double dies.
  • the invention can be used to manufacture precision parts of complex configuration from common and difficult-to-deform metals and alloys for gear pumps, gears, clutches, stepped rollers, T-pieces, cross pieces, gas turbine engines and fuel control devices, among others. used with success.
  • Workpieces are machined according to the hot-die press process in closed double dies by deforming cylindrical blanks during one stroke.
  • double-acting screw presses for forging in closed double dies when the outer tappet approaches the lower end position, the die halves collide elastically, causing the outer tappet to rebound together with the upper die, which leads to the opening of the joint between the die halves.
  • the inner tappet, with the tool attached to it begins to move downward at increased speed, deforming the blank between the die halves when the parting joint is open, causing the metal to spill out of the die cavity and thus usually Committee leads.
  • the screw press contains a frame with guides, a first spindle being rotatably accommodated along the longitudinal axis thereof.
  • One end of the spindle is kinematically connected to the tappets and the other end of the spindle is rigidly connected to a flywheel which is set in rotation by any known drive.
  • an outer plunger coaxial with the first spindle, which has two interconnected cavities.
  • An internal plunger is housed in one of them, namely in the lower cavity facing the tool, and in the other cavity there is a supporting element which represents the body of a nut which is in engagement with the first spindle.
  • the mother's body is rigidly connected to a hollow spindle, in the interior of which the first spindle is freely arranged.
  • the hollow spindle engages with a nut which is rigidly connected to the inner plunger.
  • a braking device for braking the outer tappet as it approaches the lower end position.
  • This braking device includes a traverse which is arranged in the guides mounted on the press frame so as to be displaceable along the longitudinal axis of the screw press, and at least two elastic elements which are rigidly attached to the frame above the outer plunger in its upper end position.
  • a threaded hole is made in the crossbeam.
  • the mother's body is facing the flywheel Side a screw thread that is opposite to the screw thread on the spindle. The threaded part of the nut body engages with the threaded hole in the crosshead.
  • the known construction of the double-acting screw press has a reduced efficiency because of the energy losses for overcoming the frictional forces that result in the threaded connection of the body of the mother with the cross-member when the outer plunger approaches its lower end position, when the inner plunger is displaced in order to carry out the deformation process and occur when the inner plunger returns to its original position with respect to the outer plunger.
  • the well-known screw press contains a frame Guides, wherein a spindle is rotatably supported along the longitudinal axis thereof.
  • a spindle is rotatably supported along the longitudinal axis thereof.
  • One end of the spindle facing the tool is kinematic with the tappets, but the other end of the spindle is rigidly connected to a flywheel which is set in rotation by any known drive.
  • an outer plunger is arranged concentrically to the spindle, which has two interconnected cavities.
  • An internal plunger is housed in one cavity facing the tool and in the other cavity is a load-bearing element which represents a body of a nut which is in engagement with the first spindle.
  • the mother's body is rigidly connected to a hollow spindle, in the interior of which the first spindle can be moved freely.
  • the hollow spindle engages another nut which is rigidly connected to the inner plunger.
  • On the outer wall of the mother's body two stops are attached symmetrically to its axis. The support surface of each of these stops has an inclination with respect to the longitudinal axis of the spindle which is opposite to the inclination of the helix of the first spindle.
  • a braking device is provided for braking the outer tappet as it approaches the lower end position.
  • This braking device contains two fixed crossbeams, each of which is rigidly connected to the frame and has at least two windows, a T-shaped groove being provided in the central part, and two movable crossbeams, each of which lies over one of the fixed crossbeams.
  • Each of the movable trusses is spaced from each of the fixed ones, which is adjusted by adjusting screws, and has a T-shaped groove in its central part.
  • a crossbar is attached, the lower end of which rests freely on the upper level of the outer tappet, while a stop is provided at the other end thereof, which is intended to interact with a movable bar.
  • a stop On the movable bar, on the side facing the mother's body, there is in its lower part a stop which is rotatable about its axis and is intended to interact with the stop which is located on the mother's body surface.
  • Elastic elements are housed in the windows of each fixed crossbeam, with which the movable crossbeam interacts via the plungers.
  • each bar moves freely together with the same until the upper stop cooperates with the movable crossmember.
  • the stops on the body of the mother interact with the lower ledge stops before the die halves are joined.
  • the upper ledge stops interact with the movable crossbeams, which compress the elastic elements via the plunger, creating resistance forces between the lower ledge stops and the nut body stops, the vectors of which are perpendicular to the plane of interaction of the stops.
  • the horizontal components of the resistive forces create a torque that forces the nut body to rotate.
  • This design of the braking device precludes a simultaneous interaction of the lower stop of each bar of the fixed crossmember with the corresponding stop on the nut body, which leads to the generation of bending moments in the threaded connections of the nut enclosed in the body with the spindle and the nut of the inner tappet with the hollow Spindle leads, ie Canting in the threads causes. The latter shortens the life of the screw press.
  • the invention has for its object to provide a double-acting screw press, in which the braking device of the outer tappet would ensure the compensation of angular velocities of the load-bearing elements and the spindle as it approached the lower end position, thereby eliminating the rebound of the outer tappet when the die forces were combined without reducing the performance and operational reliability of the screw press and reducing the efficiency of the same.
  • the object is achieved in that in the double-acting screw press, which has a frame with guides, a spindle being rotatably mounted along the longitudinal axis thereof, while in the frame guides, an outer tappet with guides for an inner tappet and with two is concentric with the spindle interconnected cavities, the inner plunger being in the one cavity facing the tool and the other being a supporting element with at least two symmetrical with respect to the axis of the first spindle and housed on the outer surface of the first stops, the support surface of each of which has an inclination with respect to the longitudinal axis of the spindle which is opposite to the inclination of the helix of the first spindle, which element engages with a first spindle which is in engagement with the first spindle Mother and rigidly connected to a hollow spindle, which comprises the first spindle and engages with a second nut rigidly mounted in the inner plunger, and a braking device for braking the outer plunger as it approaches the lower end position, which braking
  • This design of the screw press ensures minimal energy losses due to friction, because two second stops in the traverse are arranged with two first stops on the load-bearing element Stops only cooperate within a limited section, namely within the braking section of the outer plunger as it approaches the lower end position, which leads to an increase in the efficiency of the screw press according to the invention.
  • the attachment of the second stops on the plate ensures their simultaneous interaction with the stops on the supporting element, which precludes the generation of bending moments in the threaded connections of the nut of the supporting element with the spindle and the nut of the inner plunger with the hollow spindle, i.e. Tilting in the threads prevented.
  • the only plate provided in the braking device facilitates and accelerates the changeover of the screw press when changing the type of the parts to be manufactured, which leads to an increase in the performance of the screw press. Furthermore, the mounting of the third stops in the spindle press frame, namely in the stands thereof, increases the rigidity of the braking device, which prevents canting between the plate and the frame when the stops on the supporting element interact with the second stops when braking the outer tappet.
  • the arrangement of the plate on the upper end face of the outer tappet ensures the same an unimpeded displacement up to the upper or lower end position, which simplifies the construction of the screw press, its metal content and the dimensions are reduced.
  • the arrangement of the plate on the outer plunger shortens the plate stroke in the guides and reduces the dimensions of the same.
  • two profile surfaces forming a cam are to be provided, which interact with two spring-loaded push elements which are symmetrical with respect to the axis of the load-bearing element, each of them in guides on the plate surface is arranged, which is opposite to the surface in which it cooperates with the third stop, and has an inclined surface, which is intended to cooperate with the inclined surface of the third stop at the end of braking of the outer plunger.
  • the double-acting screw press designed according to the invention is intended for die forging precision parts of complicated configuration made of common and difficult-to-deform metals and alloys, for example of gear wheels, couplings, T-pieces, cross pieces, etc. in closed double dies.
  • the screw press contains a frame 1 (FIG. 1) with guides 2, a spindle 3 being rotatably mounted along the longitudinal axis thereof. One end of the spindle 3 is rigidly connected to a flywheel 4, which is set in rotation by any known drive.
  • a thrust bearing 6 and a thrust bearing 7 are present, in which the spindle 3 rotates.
  • the guides 2 are arranged on stands 8 of the frame 1.
  • An external plunger 9 is slidably arranged in these guides and has two interconnected cavities 10 and 11.
  • An inner plunger 13 is accommodated in the cavity 10 facing a tool 12, and in the cavity 11 there is a part of a load-bearing element which is a bimetallic nut 14, namely its threaded part 15 made of bronze and its body 16 made of steel or cast iron is made, which mother is engaged with the spindle 3.
  • the lower end of the spindle 3 is freely guided through a through bore 17 of a hollow spindle 18 which is rigidly connected to the body 16 of the nut 14.
  • the hollow spindle 18 engages with a second nut 19 rigidly attached in the inner tappet 13 and is supported with its flange 18a on a track pin 20 which is rigid with the outer tappet 9 connected is.
  • a thrust bearing 21 is provided on the flange 18a of the hollow spindle 18.
  • a braking device 23 is provided for braking the outer plunger 9 as it approaches the lower end position.
  • the brake device 23 mentioned contains a plate 24 which has a continuous central bore 25 which surrounds the body 16 of the nut 14 and runs coaxially with the spindle 3, and two crossbeams 2b which are kinematically connected to the plate 24.
  • spring-loaded thrust elements 28 are arranged in guides 27, which are symmetrical with respect to the axis of the body 16 of the nut 14.
  • each of the stops 30 is rotatably arranged in the crossmember 26 and interacts with this first stop 22 via one of its end faces, which is designed to be inclined and whose angle of inclination ⁇ 2 corresponds to the angle of inclination ⁇ 2 of the surface of the first stop 22, while using its other End face via a track bearing 32, the cross member 26, set screws 33 and a disc 34 cooperate with two elastic elements 31.
  • Each of the crossbeams 26 is supported on the upper surface of the outer plunger 9 by means of second set screws 35.
  • the plate 24 (FIG. 3) can be moved along the spindle axis, for which purpose it is provided with two ribs 36, each of which is accommodated in a guide 37 fastened to the outer plunger 9.
  • the stands 8 (Fig. 1) of the frame 1 of the screw press contain stops 38 (Fig. 4) to limit the displacement of the plate 24 (Fig. 1) as the outer plunger 9 approaches the lower end position and stops 39 (Fig. 4) Prevention of displacement of the outer plunger 9 in the upward direction until the moment when the inner plunger 13 (FIG. 1) assumes its upper end position.
  • Each of the push elements 28 has, on the side opposite to the interaction with the cam, an inclined surface 41 which is provided for cooperation with the stop 39 (FIG. 4).
  • Each of the push elements 28 has an interior 42 in which a spring 43 is accommodated which is connected at one end to the pushing element and at its other end presses against a pin 44 pressed into the plate 24.
  • the screw press works in the following way.
  • the outer plunger 9 (FIG. 1) and the hollow spindle 18, nut 14 connected to it and plate 24 raised to the upper end position.
  • the inner plunger 13 assumes an upper end position with respect to the outer plunger 9, here the push elements 28 (FIG. 2) are pressed against the profile surfaces 40 of the cam, the first stops 22 (FIG. 1) press with their inclined surfaces against the upper one Part of the second stops 30, but with their lower end faces via the thrust bearing 32, cross members 26, set screws 33 and the second set screws 35 against the outer plunger 9.
  • the flywheel 4 and the spindle 3 connected to it begin to rotate at high speed, and the spindle 3 unscrews the nut 14 by turning its body 16, the hollow spindle 18, the inner plunger 13 and the outer plunger 9 with the plate 24 attached to the same and the push elements 28 connected to the same, the guide sleeves 29, the second stops 30, the cross members 26, the elastic elements 31 and the set screws 33 and 35 are displaced in the downward direction .
  • the body 16 of the nut 14 does not rotate during this downward descent stroke because it is braked (the brake is not shown).
  • the joint movement of the outer plunger 9 and the plate 24 continues until the latter touches the stops 38 (FIG. 4), whereupon the plate 24 comes to a standstill and remains immobile.
  • the outer plunger 9 (FIG. 1) does not reach its lower end position, it is an amount ⁇ away from it and therefore continues its downward movement.
  • the amount ⁇ is regulated with the aid of the second set screws 35, which are adjusted after the set screws 33 have been set, which determine the end position of the body 16 of the nut 14 before starting work.
  • the set screws are then tightened in any known manner (in the drawing not shown) locked.
  • the first stops 22 act on the elastic elements 31 via the second stops 30, cross members 26, first set screws 33 and washers 34. There is a force F (Fig. 5), which resists the displacement of the first stops 22 and the parts connected to them _ the body 16 of the nut 14, the hollow spindle 18, the outer plunger 9 and the inner plunger 13 and is normal to the plane of contact of the first stops 22 and the second stops 30.
  • F2 F3 ⁇ tg ⁇ 2, where ⁇ is the angle of inclination of the end face of each of the first stops 22 to the horizontal plane, which is the same as the angle of inclination of the end face of each of the second stops 30.
  • the torques M1 and M2 are directed in the direction of rotation of the spindle 3 and generate a total torque M, which drives the nut 14 to an ever faster rotation in the direction of rotation of the spindle 3.
  • M M1 + M2
  • the angular velocity of the nut 14 can also be determined by solving the following equation of motion
  • R1 and ⁇ 1 are predetermined, and R2 is determined constructively, then applies;
  • the braking process of the outer plunger 9 is composed of two stages. In the first stage, when the rotational speed of the nut 14 is low, the compression of the elastic elements 31 takes place with the accumulation of the potential energy of the elastic deformation of the elastic elements 31. In the second stage, the nut 14 is accelerated and the plunger 9 is braked due to the stored potential energy of the elastic elements 31, which is converted into the kinetic energy of the rotation of the nut 14.
  • the braking distance ⁇ of the outer tappet 9 is predetermined in such a way that during the braking stroke of the outer tappet 9 when the potential is completely released Energy of elastic deformation of the elastic elements 31 for accelerating the nut 14, the angular velocity ⁇ 2 (Fig. 6) of the nut 14, the angular velocity ⁇ 1 of the spindle 3 is the same.
  • the displacement speed of the inner plunger 13 is 13 where h2 means the thread pitch of the hollow spindle 18.
  • the body 16 of the nut 14 rotates at an angle at which the cam profile surfaces 40, which are attached to the body 16 in a controllable manner (not shown in the drawing), act on the push elements 28 with inclined surfaces, as a result of which they are forced to act to move in the radial direction up to the contact with the inclined surfaces of the stop 39.
  • the cam profile surfaces 40 come into contact with the abutment elements 28 on a surface of a constant radius, so that the abutment elements 28 do not make any displacements.
  • the working tool 12 meets the workpiece (not shown in the drawing), and a deformation stroke takes place until the energy of the moving parts has completely transferred to the deformation work on the workpiece.
  • the body 16 of the nut 14 comes to a standstill, the drive, the flywheel 4 and the spindle 3 are reversed in the direction opposite to the angle of rotation of the body 16 during the working stroke.
  • the movement of the outer plunger in the upward direction is only possible in the case when the body 16 of the nut 14 has been rotated in the direction of rotation of the spindle 3 up to a position of the cam profile surfaces 40 which ensure the displacement of the push elements 28 towards the center.
  • the rotation of the body 16 enables the inner plunger 13 to be raised into the upper end position with respect to the outer plunger 9, the first stops 22 coming into contact with the inclined surfaces of the second stops 30 via their inclined surfaces. Then the body 16 of the nut 14 comes to a standstill and the moving parts are raised to the upper end position.
  • the drive is switched off and the brake of the flywheel 4 (not shown in the drawing, is switched off when the "downward stroke" working cycle is switched on).
  • the work cycle has ended.
  • the construction of the double-acting screw press proposed according to the invention ensures the specified workflow, i.e. a bumpless connection of the working tool and the successive movement of the inner plunger in the upper end position with respect to the outer plunger and the subsequent joint movement of the two plungers in the upward direction after the deformation stroke has ended.
  • This makes it possible to expand the technological possibilities of the equipment, to ensure the production of high-quality parts and to reduce the loads on the elements of the die and the screw press, but to increase their service life.
  • the construction of the screw press makes it possible to simplify its construction and operation, because this specialized equipment for forging in closed double dies under conditions of series and small series production is determined, which is characterized by frequent changing of the technological equipment and changing the device for bumplessly connecting the jaws and for successively moving the inner plunger with respect to the outer plunger.

Abstract

Presse à vis à double effet dans laquelle le mécanisme (23) de freinage de la coulisse extérieure (9) lors de son approche de la position inférieure extrême, est montée sur la face extrême de ladite coulisse. Le mécanisme (23) comporte une plaque (24) pourvue d'un dispositif permettant le déplacement le long de l'axe longitudinal de la vis (3), quatre éléments élastiques (31) montés sur la plaque (24), dont deux sont reliés, par une traverse (26), à une deuxième butée (30). Cette dernière est montée de façon rotative dans la traverse (26) et coopère, par sa face, avec la face extrême d'une première butée (22). De plus, la presse est équipée d'une troisième butée, reliée de manière rigide au cadre (1) et qui coopère avec la plaque (24) lorsque la coulisse externe (9) approche de sa position inférieure extrême.

Claims (3)

1. Presse à vis à double action, comportant un bâti (1) avec des guidages (2), une première vis (3) mobile en rotation étant montée suivant l'axe longitudinal dudit bâti et un coulisseau extérieur (9) pourvu des guidages pour un coulisseau intérieur (13) et de deux cavités (10, 11) communiquant entre elles, étant disposé dans les guidages (2) du bâti (1) concentriquement à la première vis (3), le coulisseau intérieur (13) étant logé dans l'une (10) de ces cavités orientée vers l'outil (12), tandis que l'autre cavité abrite un élément porteur muni d'au moins deux premières butées (22) disposées symétriquement par rapport à l'axe de la première vis (3) et montées sur sa surface extérieure, la surface d'appui de chacune desdites butées ayant une inclinaison par rapport à l'axe longitudinal de la vis (3) inverse à l'inclinaison de l'hélice de la première vis (3), ledit élément étant solidaire d'un premier écrou (14) accouplé à la première vis (3) et à une vis creuse (18) entourant la première vis (3) et entrant en prise avec un deuxième écrou (19), monté rigidement dans le coulisseau intérieur (13) et un mécanisme de freinage (23) pour le freinage du coulisseau extérieur (9) à son approche de la position extrême inférieure, ledit mécanisme étant lié cinématiquement à l'élément porteur, caractérisée en ce que le mécanisme de freinage (23) est disposé sur la face frontale du coulisseau extérieur (9), orientée vers les premières butées (22) et comporte un plateau (24), disposé coaxialement à la vis (3) muni d'un trou débouchant (25) dans lequel est logé l'élément porteur et est pourvu d'un dispositif de déplacement suivant l'axe longitudinal de la première vis (3) sur lequel sont montés des éléments élastiques (31), une paire desdits éléments étant liée cinématiquement à une deuxième butée (30), montée mobile en rotation dans la traverse (26) et coopérant par sa face frontale avec la première butée (22), ladite face frontale étant inclinée, et son angle d'inclinaison coïncidant avec l'angle d'inclinaison de la surface de la première butée (22) en ce qu'on a de plus prévu des troisièmes butées (38, 39), liées rigidement au bâti (1) et coopérant avec le plateau (24) lorsque le coulisseau extérieur (9) se rapproche de la position inférieure extrême.
2. Presse à vis à double action selon la revendication 1, caractérisée en ce que deux surfaces profilées (40) formant une came sont prévues sur la surface extérieure de l'élément porteur qui coopèrent avec deux poussoirs (28) à ressort disposés symétriquement par rapport à l'axe de l'élément porteur, montés, chacun dans des guidages (27) sur la surface du plateau (24), opposée à la surface coopérant avec la troisième butée (39) et ayant une surface inclinée (41) destinée à coopérer avec la surface inclinée d'une troisième butée (38) à la fin du processus de freinage du coulisseau extérieur (9).
3. Presse à vis à double action selon les revendications 1, 2, prises séparément ou en combinaison, caractérisée en ce que l'angle d'inclinaison (α₂) de la face frontale de la deuxième butée (30) coïncidant avec l'angle d'inclinaison (α₂) de la surface d'appui de la première butée (22) et inverse à l'inclinaison de l'hélice de la première vis (3) est déterminé par la relation suivante:
Figure imgb0019
 où:
R₁ est le rayon moyen du filetage de la vis;
R₂ est la distance entre l'axe de la vis et l'axe de la deuxième butée;
α₁ est l'angle d'inclinaison de l'hélice sur le diamètre moyen du filetage de la vis.
EP86904989A 1986-05-29 1986-05-29 Presse a vis a double effet Expired - Lifetime EP0268681B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SU1986/000054 WO1987007210A1 (fr) 1986-05-29 1986-05-29 Presse a vis a double effet

Publications (3)

Publication Number Publication Date
EP0268681A1 EP0268681A1 (fr) 1988-06-01
EP0268681A4 EP0268681A4 (fr) 1989-01-18
EP0268681B1 true EP0268681B1 (fr) 1991-04-03

Family

ID=21617005

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86904989A Expired - Lifetime EP0268681B1 (fr) 1986-05-29 1986-05-29 Presse a vis a double effet

Country Status (6)

Country Link
US (1) US4881399A (fr)
EP (1) EP0268681B1 (fr)
JP (1) JPS63503445A (fr)
DE (1) DE3678582D1 (fr)
HU (1) HU202150B (fr)
WO (1) WO1987007210A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2660784B2 (ja) * 1992-08-07 1997-10-08 月島機械株式会社 複数移動部材の駆動装置
US5609081A (en) * 1995-03-30 1997-03-11 Lin; Shoei C. Portable round-tube cutter
EP1600224A1 (fr) * 2004-05-27 2005-11-30 Trumpf Werkzeugmaschinen GmbH + Co. KG Machine avec mécanisme de levage pour travailler une pièce avec un outil
GB201016930D0 (en) * 2010-10-07 2010-11-24 Ishida Europ Ltd Lifting apparatus
CN103252436B (zh) * 2012-02-20 2016-02-03 青岛东方神力机械有限公司 电动双螺旋压力机
CN203391364U (zh) * 2012-04-13 2014-01-15 会田工程技术有限公司 用于机械压力机的滑动件运动控制设备
CN114516192B (zh) * 2022-03-04 2022-11-04 无锡职业技术学院 一种机电一体式旋转下压装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU617280A1 (ru) * 1976-11-03 1978-07-30 Московское Высшее Техническое Училище Имени Н.Э.Баумана Винтовой пресс двойного действи
SU658005A1 (ru) * 1977-03-29 1979-04-25 Московское Ордена Ленина И Ордена Трудового Красного Знамени Высшее Техническое Училище Им. Баумана Винтовой пресс двойного действи
SU620397A1 (ru) * 1977-05-04 1978-08-25 Московское Ордена Ленина И Трудового Красного Знамени Высшее Техническое Училище Им.Н.Э.Баумана Винтовой пресс
SU706173A1 (ru) * 1978-07-25 1979-12-30 Завод-Втуз При Московском Автомобильном Заводе Им. И.А.Лихачева Гидравлический пресс
SU854740A1 (ru) * 1979-10-26 1981-08-15 Московское Ордена Ленина И Ордена Трудового Красного Знамени Высшее Техническое Училище Им. Н.Э.Баумана Винтовой пресс двойного действи
SU1027056A1 (ru) * 1981-10-29 1983-07-07 Московское Ордена Ленина, Ордена Октябрьской Революции И Ордена Трудового Красного Знамени Высшее Техническое Училище Им. Н.Э.Баумана Винтовой пресс двойного действи
SU1147593A1 (ru) * 1983-05-30 1985-03-30 МВТУ им.Н.Э.Баумана Винтовой пресс двойного действи
DE3425332A1 (de) * 1984-07-10 1986-01-16 SMS Hasenclever Maschinenfabrik GmbH, 4000 Düsseldorf Spindelpresse

Also Published As

Publication number Publication date
US4881399A (en) 1989-11-21
HU202150B (en) 1991-02-28
HUT49073A (en) 1989-08-28
EP0268681A4 (fr) 1989-01-18
DE3678582D1 (de) 1991-05-08
JPS63503445A (ja) 1988-12-15
WO1987007210A1 (fr) 1987-12-03
EP0268681A1 (fr) 1988-06-01

Similar Documents

Publication Publication Date Title
DE102007051894A1 (de) Freigabemechanismus und mit diesem versehenen Richtvorrichtung
EP0765735A1 (fr) Presse poinçonneuse à genouillère
DD256610A7 (de) Automat fuer hydroplastische bearbeitung von stirnraedern
DE2415549B2 (de) Vorrichtung für die spanlose Kaltverformung eines Rohlings
EP0268681B1 (fr) Presse a vis a double effet
DE102011054063B4 (de) Antriebsvorrichtung für ein Stützteil zum Abstützen eines Werkstücks
EP0724953B1 (fr) Poinçonneuse avec espace allongé pour le montage de poinçons
DE1627678B1 (de) Vorrichtung zum überwiegenden Kaltpressen aussen hinterschnittener, vorgepresster Zwischenoresslinge
DE3327258C2 (fr)
DE2810273C2 (de) Vorrichtung zur Regelung der Vorschubgeschwindigkeit des Dorns in einem kontinuierlichen, mit gehaltenem Dorn arbeitenden Walzwerk
EP0739663A2 (fr) Machine pour former des pièces
EP0761338B1 (fr) Procédé et dispositif pour la fabrication d'articles profilés
DE3323428C2 (fr)
DE2748235A1 (de) Gesenkschmiedepresse
DE102006023721B3 (de) Schmiedevorrichtung
EP3024646B1 (fr) Module de force et système de pressage modulaire
EP3448594B1 (fr) Presse-transfert pourvue d'un serre-flan en c
EP1345715B1 (fr) Presse a forger dotee d'un dispositif de reglage situe cote matrice
DE3429490A1 (de) Schmiedemaschine mit geschlossenem gesenk
EP0283532B1 (fr) Presse à couper et déformer à entraînement à genouillère hydro-mécanique
DE2525052C3 (de) Einrichtung zur Steuerung von Schnellpressen
WO1999054122A1 (fr) Presse radiale
DE2834697C2 (de) Hydraulische Spindelpresse zum Gesenkschmieden
DE19614574A1 (de) Antriebsvorrichtung für eine Presse
EP0912843B1 (fr) Mecanisme articule

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19880120

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

A4 Supplementary search report drawn up and despatched

Effective date: 19890118

17Q First examination report despatched

Effective date: 19900608

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 3678582

Country of ref document: DE

Date of ref document: 19910508

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19910520

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19910522

Year of fee payment: 6

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19910628

Year of fee payment: 6

ITF It: translation for a ep patent filed

Owner name: MODIANO & ASSOCIATI S.R.L.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19920529

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19920529

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19930129

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19930202

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050529