EP0291714B1 - Procédé et dispositif pour la fabrication de corps de révolution à l'aide de formage par fluage - Google Patents

Procédé et dispositif pour la fabrication de corps de révolution à l'aide de formage par fluage Download PDF

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Publication number
EP0291714B1
EP0291714B1 EP88106349A EP88106349A EP0291714B1 EP 0291714 B1 EP0291714 B1 EP 0291714B1 EP 88106349 A EP88106349 A EP 88106349A EP 88106349 A EP88106349 A EP 88106349A EP 0291714 B1 EP0291714 B1 EP 0291714B1
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EP
European Patent Office
Prior art keywords
blank
blanks
respect
cylinder
tappets
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
EP88106349A
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German (de)
English (en)
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EP0291714A2 (fr
EP0291714A3 (fr
Inventor
Ludwig Balint
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Individual
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Individual
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Priority claimed from AT0334684A external-priority patent/AT381657B/de
Priority claimed from AT0334584A external-priority patent/AT382094B/de
Application filed by Individual filed Critical Individual
Priority claimed from EP85905045A external-priority patent/EP0198860B1/fr
Publication of EP0291714A2 publication Critical patent/EP0291714A2/fr
Publication of EP0291714A3 publication Critical patent/EP0291714A3/fr
Application granted granted Critical
Publication of EP0291714B1 publication Critical patent/EP0291714B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H1/00—Making articles shaped as bodies of revolution
    • B21H1/18—Making articles shaped as bodies of revolution cylinders, e.g. rolled transversely cross-rolling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H9/00—Feeding arrangements for rolling machines or apparatus manufacturing articles dealt with in this subclass

Definitions

  • the invention relates to a process for the production of rotating bodies with different diameters at their two ends or axial sections with different diameters, in which, when the blank is rotated about its longitudinal axis, a pressure exceeding the yield point of the material of the blank is locally applied to reduce the diameter of the blank , as well as a device for performing the method.
  • DE-OS 1 812 106 has disclosed a solution in which two rollers provided with profile ribs act on a blank.
  • the profile ribs of both rollers run out into the pointed surface of the roller in a pointed manner and have a cross section in their two end regions which corresponds exactly to the cross section of the groove to be produced.
  • feed ribs are also arranged on both rolls, which have two sections running perpendicular to the axis of the roll and between these sections a section running inclined to the axis. The latter pushes the rod material from which the rotary body is made into its position in which the corresponding groove is worked in during one revolution of the roller through its profile ribs.
  • a chisel also arranged on the rollers separates the rotary body thus produced from the bar material.
  • a solution was proposed by FR-PS 2 337 602 and DE-OS 19 10 549, in which a roller with a spirally arranged profile rib interacts with a smooth counter-pressure roller. There is also provided a short rib which acts as a chisel and runs perpendicular to the axis of the roller.
  • the rod material Due to the slope of the profile rib, the rod material is fed and the finished rotary body is cut off by the chisel.
  • the cross section of the running end area of the profile rib corresponds to the groove to be produced.
  • rollers provided with the profile ribs can only be used for the production of a certain rotating body.
  • a change, albeit small, to the body of revolution to be manufactured, e.g. a change in the axial extent of an area with a reduced diameter requires the production of new tools, i.e. new rollers.
  • the aim of the invention is to avoid this disadvantage and to propose a method and a device which allows a simple variation of the rotary bodies to be produced with little effort.
  • a pressure zone having a smaller dimension in the longitudinal direction of the blank compared to the axial extent of the region with a reduced diameter of the rotary body to be produced is moved in the axial direction of the blank during rotation thereof.
  • Another object of the invention is to propose a device for carrying out the method according to the invention.
  • the axis of rotation of the roller is inclined and cross each other in the course of the mutual relative movement and the feed device is formed by a guide for the blanks which is inclined with respect to the lines determined by the corresponding edges of the profile ribs resulting from the rotation of the roller when the roller rotates.
  • the intersecting profile ribs which run inclined to the axis of rotation of the roller, result in an inclined course of the imaginary line connecting the intersection points of the profile ribs with respect to the axis of rotation of the roller, as a result of which the blanks can be supplied and the finished rotary bodies removed in different planes, whereby by the course of the guide inclined to this line ensures the axial displacement of the blanks relative to the effective area determined by the crossover area of the profile ribs of the central roller and the counter pressure surface.
  • the counter-pressure surface is subdivided into segments which can be displaced radially with respect to the roller, there is also the advantage that the counter-pressure surface can be fed to the central roller as desired. This is possible due to the fact that the interacting profile ribs cross each other and therefore in In extreme cases, only along a surface line, but not touching the surface. In the latter case, infeed would lead to a gap which changes over the arc length of the segment.
  • the feed device is formed by a driving device which has at least one, but preferably two, rotating bodies spaced apart from one another in the axial direction of the central roller, in which plunger (s) are held displaceably in their longitudinal direction by means of a sliding block or the like engage in a circumferential control groove arranged in a stationary part of the device, plungers guided in two different rotating bodies being aligned axially to one another and essentially parallel to the axis of rotation of the roller, and the blanks can be clamped by at least one plunger, but preferably between two plungers.
  • control groove (s)
  • the control groove (s) with the exception of a supply and removal area for the blanks or the rotating bodies, run essentially parallel to one another, as a result of which particularly precise guidance is achieved and simple picking up of the blanks and delivery of the finished rotational body is made possible.
  • the end regions of the plungers are held rotatably about the longitudinal axis of the plungers, the end regions of the one plunger preferably being spring-loaded against the coaxially aligned plungers. This prevents friction between the end faces of the blanks and the plungers.
  • the resilient support of the end regions of the one plunger can prevent the blanks being machined from being pressed too strongly if they grow in their axial dimensions in one section due to the diameter reduction. It can also compensate for dimensional deviations in the blanks will.
  • the end regions of the plungers can be formed by inserts.
  • a sprocket connected to the central roller in a rotationally fixed manner is provided, in which gear transmissions which are connected in drive connection with support shafts arranged parallel to the tappets engage, the support shafts in which the tappets leading rotating bodies or rotatably connected to these rotating bodies.
  • FIG. 1A shows schematically the profile ribs 7 and 8 arranged on the counter pressure surface 1, which is divided into five segments 2, 3, 4, 5 and 6, of which the profile ribs 7 form the shoulder or shoulder 10 of the finished rotary body 9 v serves.
  • the profile rib 8 on the other hand, is used to form the groove 11 of the finished rotary body 9 v and has its greatest width and smallest height at the beginning of the counter-pressure surface 1 or at its limit to the input area for the blanks 9 to be machined.
  • the width of the profile rib 8 constantly decreases and its height to, where it ends in a shape that is opposite to the shape of the groove 10.
  • the central roller 12 shown in FIG. 1B runs in the space enclosed by the segments 2 to 6 of the counter pressure surface, but a common representation has been left out for reasons of better clarity.
  • the roller 12 is installed in such a way that when the roller 12 is positioned relative to the segments 2 to 6 of the counter-pressure surface 1 in which the beginnings of the profile ribs 7 and 8 are radially aligned, they are also at the same height.
  • FIG. 2 shows the interaction of the two groups of profile ribs 7 and 8 or 7 'and 8'.
  • Figure 2 shows the handling of the profile ribs 7 and 8 of the counter pressure surface 1 and the profile ribs 7 'and 8' of the roller 12.
  • the profile ribs 7 and 8 rise from left to right, whereas the profile ribs 7 'and 8' fall from left to right.
  • the roller 12 rotates in the direction of arrow 13 in FIG. 1B
  • the profile ribs 7 'and 8' are moved in the direction of arrow 13 in FIG. 2 with respect to the profile ribs 7 and 8.
  • the cross-sectional shape of the profile ribs 7 'and 8' changes in the same way as that of the profile ribs 7 and 8, ie the profile rib 7 'widens from cross-section x to cross-section x5 and the profile rib 8 'decreases in width against the area of its largest elevation.
  • the blanks 9 are guided parallel to the line 15 between two plungers 14, 14 '.
  • the blank 9 is on its way from the cross section x to the cross section x5 between the roller 12 and the counter pressure surface 1 not only because of the increasing height along this path the profile ribs are exposed to a radially acting pressure but also to an axial pressure which acts on the shoulder 10 which is formed and which significantly favors and facilitates the flow of the material, in particular in the axial direction.
  • the intermediate product 9 corresponds to the deformation state of the blank 9, as is given at the border x1 between the segment 2 and the segment 3.
  • the intermediate product 9 ⁇ corresponds to the deformation state of the blank in cross section x2
  • the intermediate product 9′ ⁇ corresponds to the deformation state of the blank in cross section x3
  • the intermediate product 9 ′ v corresponds to the deformation state in cross section x4.
  • the blank is shaped to form the finished rotating body 9 v .
  • the profile ribs 8 and 8 'used to form the groove 11' run essentially parallel to the line 15 and thus parallel to the path which the blanks describe during their processing between the roller 12 and the counter-pressure surface 1.
  • the slight inclination of the line 15 to the profile ribs 8, 8 ' is caused by the length growth of the blank by the indentation of the groove.
  • the profile rib 8,8' can also be used to form a section of the rotary body 9 v to be produced with a smaller one Diameter can be used.
  • the blanks only need to be guided on a path that leads upward relative to the profile rib 8,8 ′, for example along the line 16 shown in broken lines in FIG. 2.
  • the pressure zones determined by the profile ribs 8,8 ′ would be opposite in the axial direction the blank are moved, whereas in the pressure zones determined by the profile ribs 7, 7 'and a guidance of the blanks according to line 15 in FIG. 2, only a limitation of the pressure zones is moved in the axial direction with respect to the blank.
  • Figure 3 shows schematically a device for performing the method according to the invention in vertical section, in particular the bearings and their installation is shown in simplified form are. For reasons of production technology and for reasons of simpler assembly, assemblies consisting of several parts are shown in part as one part.
  • the drive motor 20 drives a shaft 23 via a clutch 21, one half of which is connected to a flywheel 22. This is supported in the usual way via the roller bearings 24 and 25 in the housing 26 and is rotatably connected to a bevel gear 27 and a sprocket 29.
  • the bevel gear 27 meshes with a further bevel gear 28, which is connected in a rotationally fixed manner to a vertical main shaft 30.
  • the main shaft 30 is held by means of two tapered roller bearings 31 and 32 in a support cylinder 33 connected to the housing 26.
  • a first guide body 34 is placed on this support cylinder 33 and rigidly connected to it. Furthermore, a needle bearing 35 is arranged on the support cylinder 33, which is fixed in its axial position by the guide body 34 and a support flange 36 and rotatably supports a rotating body 37 provided with a sprocket 38.
  • This rotating body 37 or its sprocket 38 is connected via two chains 39 to sprockets 40, which are non-rotatably connected to the output shaft 41 of a gear 42.
  • This gear 42 is driven by two chains 44 and sprockets 43 from the shaft 23 or the sprockets 29 connected to it and held by a bracket 46 in the housing 26 '.
  • the rotating body 37 is connected to a further rotating body 47 via bolts 45 and is mounted on the main shaft 30 via a roller bearing 48.
  • These two rotating bodies 37 and 47 are also connected to one another via slotted guide sleeves 49, in which the plungers 14 ', or their guide heads 50, are guided axially displaceably.
  • These guide heads 50 engage with their rotatably held roller 51 in a control groove 52 arranged in the guide body 43.
  • the rotating body 47 is connected by means of supports 55 to a further rotating body 56 which, like the rotating body 47, is provided with sections of dovetail guides which extend in the tangential direction and which serve to receive sliding blocks which form parts of the driving device shown in FIGS. 8 to 10 are and will be explained later with reference to these figures. For reasons of better clarity, the corresponding reference numerals have not been entered in FIG. 3.
  • a chuck body 57 is rotatably arranged, onto which the roller 12 'with the profile ribs 7' and 8 'is pushed and held in a rotationally fixed manner by means of a tongue and groove connection.
  • a toothed ring 58 is screwed to the roller 12, from which the drive for the driving device is derived, as will be explained in more detail with reference to FIGS. 8 and 10.
  • a sleeve 58 is pushed onto a shoulder of the main shaft 30 and connected to it in a rotationally fixed manner via a tongue and groove connection.
  • a rotary body 62 screwed to an internal ring gear 61 is mounted on this sleeve 59 via a roller bearing 60.
  • the internal ring gear 61 meshes with intermediate gear wheels 63, which in turn mesh with further gear wheels 64, which only serve to reverse the direction of rotation, and which, like the intermediate gear wheels 63, are rotatably held in a ring 66 arranged in the interior of another guide body 65 fixed to the housing .
  • the gears 64 in turn mesh with a ring gear arranged on the sleeve 59, which ensures the drive of the rotating body 62 via the gears 63 and 64 and the ring gear 61, which supports the guide body 65 via a roller bearing 60 '.
  • the rotating body 62 is connected via bolts 67 and a sleeve 68 to a ring 69 in which, like in the rotating body 62, bushes 53 in which the plungers 14 are rotatably and axially displaceably held are held.
  • the guide body 65 is formed in two parts and supports the main shaft 30 via a roller bearing 69 '. Furthermore, the Guide body 65 is provided with a control groove 70, in which, as shown in FIG. 6 on a larger scale, a rotatable roller 51, which is held in each stirring head 71 of the plunger 14, engages.
  • the pin 72 carrying the roller 51 engages, as shown in FIG. 6, with a shoulder in a circumferential groove 73 of the plunger 14, as a result of which the latter is held in the guide head 71 in a rotatable but axially non-displaceable manner.
  • the control groove 70 runs parallel to the control groove 52 of the guide body 34 over the largest part of the circumference of the guide body 65. Only in the input and output area explained with reference to FIG. 1A does this parallelism not exist and the two control grooves diverge in this area and again together.
  • the guide body 65 can be connected via a flange body 74 to a support arm 75, in which the main shaft 30 is supported in a slide bearing.
  • the support arm 75 is supported on a support column 76 which is fixed on the housing 26 '.
  • a spindle 77 is arranged, which is supported in its upper region by means of a centering ring 78 against the inner wall of the support column 76 and against a cylindrical bore 79 of the support arm 75.
  • the support arm 75 is clamped to the support column 76 by means of a nut 80.
  • the latter can be raised and pivoted, making it possible to disassemble the device in order to e.g. to replace the roller 12 with another one with differently shaped profile ribs in order to be able to produce other rotating bodies.
  • a circumferential link 92 is held via holding arms 91, which, as will be explained in more detail with reference to FIGS. 8 and 9, is provided for controlling the driving device.
  • the feed device for the blanks to be deformed which can be seen more clearly in FIG. 4, is designated in its entirety by 93 and is driven by the gear 42 via a chain wheel 94 and a chain 95.
  • the translation of the gear 42 and sprockets 40 and 38, as well as that of the gear formed by the ring gear 61 and the ring gear of the sleeve 59, as well as the gears 63 and 64 is selected so that the rotating body driven by these gears on that of the in these Rotary bodies held plungers 14, 14 'described path have half the peripheral speed of the shell of the roller bearing the profile ribs.
  • an oscillation generator 96 is screwed into the segment of the counter pressure surface 1, which sets the counter pressure surface in high-frequency vibrations and thereby facilitates the deformation of the blanks 9, which by means of a in FIG. 4 for better clarity Driver device, not shown, between the segments of the counter pressure surface 1 and the roller 12 are performed.
  • the feed device 93 has an inclined channel 97 which guides the blanks 9 to a star wheel 98.
  • This star wheel 98 transports the blanks to a further star wheel 99, a guide plate 100 being provided for transferring the blanks 9, which is fastened to the housing 26 'via a holder (not shown for reasons of clarity).
  • a magnet 103 is arranged in a horizontal plane different from the feed device. which leads the finished rotary body 9 v after their release through the plunger 14, 14 'in a further groove 104.
  • a switch 105 is installed in the trough 104, which makes it possible, by pushing in a baffle 106 by means of the piston-cylinder arrangement 107, to optionally pull out a rotary body, which then reaches a measuring device 109 via a trough 108.
  • the rotating body 9 v is pushed with a piston 110 into a measuring position in which it rests against a stop 111 which can be pivoted by the piston-cylinder arrangement 112.
  • the measurement itself is carried out by means of an optical measuring head 113, which releases the measurement result in the form of electrical signals which are fed to a control device, not shown, for example a process computer.
  • the stepping motors 86 of the slides 81 are given corresponding control commands in order to adjust them accordingly. This enables compliance with very tight tolerances.
  • the bellows 111 is pivoted by the cylinder-piston arrangement 112 and the cylinder-piston arrangement 110 advances the already measured rotating body to the opening 114, through which it slides outwards via the groove 115.
  • Figure 7 shows the end regions of the plunger 14 and 14 'on an enlarged scale, these end regions being rotatable about the longitudinal axis of the plunger, the plunger 14 having an insert 116 screwed into its end face, in which a tip by means of a transverse bore 118 of the tip 117 penetrating pin 119, which also penetrates the walls of the insert 116.
  • the tip 117 is held axially displaceably in the insert 116 and is acted upon by a spring 120. Since the transverse bore 118 has a larger diameter than that Pin, there is a slight axial displacement of the tip 117 relative to the insert or its sleeve. This enables the compensation of small dimensional deviations of the blanks 9 and the compensation of the length growth of the blanks during the deformation by the profile ribs 7 and 8 or 7 'and 8' of the counter pressure surface 1 or the roller 12th
  • a sleeve 121 is screwed into which a sliding bush 122 is inserted and secured with an insert 123.
  • a tip 124 is held in this sliding bush 122, the collar of the tip being supported on a sliding ring 125, which in turn is supported on a shoulder of the sleeve 121.
  • the driver device is explained in more detail with reference to FIGS. 8, 9 and 10.
  • the rotating bodies 47 and 56 are provided in sections with tangentially extending, radially projecting dovetail guides 126.
  • Two sliding blocks 127 are slidably arranged on each of the sections of the dovetail guides.
  • the plungers 14 and 14 ' run between the approaches of the rotating body, while the support rollers 128 are rotatably mounted in the bores 129 of the sliding blocks 127.
  • the sliding blocks 127 held in different rotating bodies 47 and 56 are connected to one another via the pressure bodies 130, which are screwed to the sliding blocks 127.
  • the pressure bodies 130 are each controlled by a camshaft 131, the cylindrical lugs 132 of which pass through the bores 133 arranged in the radially projecting lugs of the rotary bodies 47 and 56 or are rotatably held therein.
  • the upper cylindrical lugs 132 are clamped in a control lever 134 in a rotationally fixed manner, the lugs 132 engaging in the bores 135, some of them Limit slot 136.
  • These control levers 134 slide along the fixed link 92 when the two rotating bodies 47, 56 are rotated.
  • This backdrop 92 essentially describes a circular arc over the arc area over which the counter pressure surface 1 extends.
  • the link 92 has a recess 137 which enables the control levers to pivot.
  • the support rollers 128 have a region which is provided with a rim, which comes into contact with the blanks 9 and drives them.
  • the support rollers are driven by the gear wheels 138, which are connected to the support rollers in a rotationally fixed manner.
  • These gears 138 mesh with intermediate gears 139, which are rotatably supported by a gear 138 in a holder 140, the intermediate gears 139 meshing with the ring gear 58, which is connected to the profile ribs 7 ', 8' carrying roller 12. Due to the speed difference between the ring gear 58 and the holders 140 which move due to the positive connection with the rotating bodies 47 and 56, which is provided by the support shafts 128, the idler gears 139 are rolled away and thus the support shafts are driven.
  • the brackets 140 that belong together are, as can be seen from FIG. 9, connected to one another with a bolt 141, the two brackets 140 being clamped together by two springs 142.
  • control levers 134 slide along the circular area of the link 92, these are deflected and the camshafts 131, which are connected to them in a rotationally fixed manner, press the pressure bodies 130 and the support shafts 128 held in the sliding blocks 127 against the tappets 14, 14 'and thus against the blanks 9 to be deformed.
  • the holders 140 are also forced apart against the force of the springs 142. If one of the control levers 134 slides into the recess in the link, it can deflect and the springs 142 can press the support shafts 128 away from the tappets, which also causes the camshaft 131 to pivot a pivoting of the control lever 134 comes, which is held in contact with the link 92 by the springs 142.
  • the idler gears 139 run in two different horizontal planes and are rotatably mounted on axle stubs held in the respective holder 140 on one side.
  • the translation of the gears 58, 139, 138 and the support shaft 128, or the diameter of their rimmed area are matched to one another so that the peripheral speed of the rimmed area of the support shafts 128 and thus also that of the blanks 9 adjacent to them, equal to the peripheral speed of the Jacket of the roller 12 carrying the profile ribs.
  • the blanks 9 are set in motion by rolling on the stationary counter-pressure surface 1 and the casing of the roller 12, as indicated by the arrows in FIG. 10, but the blank can also slide during the deformation of the blank come on these surfaces. This is prevented by the additional drive of the blank by the support shafts, whereby, as can be seen from FIG. 10, the blank 9 is always supported and driven between the support shafts 128 held in adjacent pairs of holders 140.
  • the pressure bodies 130 have a groove facing the support shafts 128, which extends in the axial direction and is held in the roller body 144, which protrude beyond the outer edges of the groove 145. The friction between the support shafts and the pressure bodies 130 is thus largely avoided.
  • control grooves 52, 70 which determine the path of the blanks 9, run in the area covered by the counter pressure surface 1 corresponding to line 15 in Figure 1A or parallel to this. Outside of this area, the course of the control grooves has opposing bulges, the circumferential control grooves 52, 70 moving farther apart and approaching each other again, so that there is no clamping of the blanks 9 or 9 v in this area and the blanks in this area fed and the finished rotary body can be removed.
  • control grooves 52, 70 can have a course deviating from the line 15 in FIG. 1A in the area that is the same as the counterpressure surface 1 and may run parallel to line 16 or 17 in FIG. 2, for example. This depends on the shape of the rotary body to be manufactured 9 v and on the design of the profile ribs 7, 8; 7 ', 8'.
  • the counter pressure surface has a curvature corresponding to the roller 12.
  • this is by no means absolutely necessary.
  • a flat counter pressure surface can also be provided, over which the roller is moved, it being immaterial whether the counter pressure surface is moved with respect to the axis of the roller or is moved parallel to the counter pressure surface.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Forging (AREA)

Claims (7)

  1. Procédé de fabrication de pièces de révolution possédant à leurs deux extrémités des diamètres différents ou des segments axiaux présentant des diamètres différents, dans lequel, pendant qu'on fait tourner l'ébauche (9) autour de son axe longitudinal, une pression excédant la limite d'élasticité apparente de la matière de l'ébauche (9) est exercée localement pour réduire le diamètre de l'ébauche (9),
    caractérisé
    en ce qu'une zone de pression, qui présente une plus petite dimension dans la direction longitudinale de l'ébauche, comparativement à la dimension axiale de la région de diamètre réduit de la pièce de révolution (9V) à produire, se déplace dans la direction axiale de l'ébauche (9), sur la longueur de l'ébauche pendant sa rotation.
  2. Dispositif pour la mise en oeuvre du procédé selon la revendication 1, qui comprend un cylindre (12) qui coopère avec une surface de contre-pression (1) et peut se déplacer relativement à celle-ci, cependant qu'une nervure au profil en relief est prévue sur le cylindre et/ou sur la surface de contre-pression,
    caractérisé
    en ce que la ou les nervure(s) au profil (7,7') présente(nt) une largeur inférieure à la dimension axiale de la région de diamètre réduit de la pièce de révolution (9V) à fabriquer et que, pour agir sur les ébauches, il est prévu un dispositif d'avance (14, 14', 5é, 70) qui provoque à force un déplacement axial de l'ébauche (9) par rapport aux nervures (7, 7').
  3. Dispositif selon la revendication 2,
    caractérisé
    en ce que la ou les nervure(s) au profil (7) prévue(s) sur le cylindre central (12) et la ou les nervure(s) au profil (7) prévue(s) sur la surface de contre-pression (1), laquelle est de préférence divisée en plusieurs segments (2,2,4,5,6) réglables radialement par rapport au cylindre, s'étendent dans une direction inclinée sur l'axe de rotation du cylindre (12) et se croisent mutuellement au cours du mouvement relatif mutuel, et il est prévu un guidage agissant sur les ébauches (9) qui s'étend dans une direction inclinée par rapport aux lignes définies par les points d'intersection qui sont formés par les arêtes mutuellement correspondantes des nervures (7, 7') pendant la rotation du cylindre (12).
  4. Dispositif selon une des revendications 2 et 3, caractérisé
    en ce que le dispositif d'avance est constitué par un dispositif entraîneur qui présente au moins un corps tournant, mais de préférence deux corps tournants (37, 47 ; 62, 69) espacés l'un de l'autre dans la direction axiale du cylindre central (12), dans lequel ou dans lesquels sont montés des poussoirs (14, 14') mobiles en translation longitudinale, qui sont engagés au moyen d'un galet ou équivalent dans une rainure de commande circonférentielle (52, 70) disposée dans une partie fixe du dispositif, les poussoirs (14, 14') guidés dans deux corps tournants (34, 47 ; 62, 69) différents étant orientés axialement l'un par rapport à l'autre et sensiblement parallèlement à l'axe de rotation du cylindre (12), et les ébauches pouvant être bloquées par au moins un poussoir (14, 14') mais de préférence entre deux poussoirs (1', 14').
  5. Dispositif selon la revendication 4,
    caractérisé
    en ce qu'au moins les régions terminales des poussoirs (14, 14') qui sont dirigés l'une vers l'autre sont montées mobiles en rotation autour de l'axe longitudinal des poussoirs (14, 14'), les régions terminales d'un poussoir (14) étant sollicitées élastiquement vers les poussoirs (14') orientés coaxialement.
  6. Dispositif selon la revendication 2,
    caractérisé
    en ce que, pour le dispositif entraineur, il est prévu une couronne dentée (58) reliée solidairement en rotation au cylindre central (12), et dans laquelle engrènent des mécanismes à roues dentées (139, 138) qui sont en liaison d'entraînement avec des arbres d'appui (128) disposés parallèlement aux poussoirs (14, 14'), les arbres d'appui (128) étant montés dans les corps tournants qui guident les poussoirs ou dans des corps tournants (47, 56) reliés solidairement en rotation à ces poussoirs.
  7. Dispositif selon la revendication 4,
    caractérisé en ce que,
    les rainures de commande (52, 70) s'étendent sensiblement parallèlement entre elles, à l'exception d'une région d'amenée des ébauches (9) ou d'évacuation des pièces de révolution (9V).
EP88106349A 1984-10-19 1985-10-15 Procédé et dispositif pour la fabrication de corps de révolution à l'aide de formage par fluage Expired - Lifetime EP0291714B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
AT0334684A AT381657B (de) 1984-10-19 1984-10-19 Verfahren und vorrichtung zur herstellung von rotationskoerpern durch fliessumformung
AT0334584A AT382094B (de) 1984-10-19 1984-10-19 Verfahren und vorrichtung zur herstellung von rotationskoerpern durch fliessumformung
AT3345/84 1984-10-19
AT3346/84 1984-10-19
EP85905045A EP0198860B1 (fr) 1984-10-19 1985-10-15 Procede et installation pour fabriquer des corps de revolution par deformation plastique

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EP85905045.2 Division 1985-10-15

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EP0291714A2 EP0291714A2 (fr) 1988-11-23
EP0291714A3 EP0291714A3 (fr) 1992-06-03
EP0291714B1 true EP0291714B1 (fr) 1994-07-06

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CN111412554A (zh) * 2020-04-29 2020-07-14 宁波奥克斯电气股份有限公司 网罩及空调器

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AT291160B (de) * 1966-12-16 1971-07-12 Lajos Dipl Ing Balint Verfahren und Maschine zur Herstellung von Rotationsformkörpern durch Walzen

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EP0291714A2 (fr) 1988-11-23
EP0291714A3 (fr) 1992-06-03

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