EP4135973B1 - Presse radiale - Google Patents

Presse radiale Download PDF

Info

Publication number
EP4135973B1
EP4135973B1 EP21751563.4A EP21751563A EP4135973B1 EP 4135973 B1 EP4135973 B1 EP 4135973B1 EP 21751563 A EP21751563 A EP 21751563A EP 4135973 B1 EP4135973 B1 EP 4135973B1
Authority
EP
European Patent Office
Prior art keywords
press
ring structure
radial
radial press
piston
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.)
Active
Application number
EP21751563.4A
Other languages
German (de)
English (en)
Other versions
EP4135973C0 (fr
EP4135973A1 (fr
Inventor
Vaclav Hejplik
Reiner Viehl
Carsten Baumgartner
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.)
Uniflex Hydraulik GmbH
Original Assignee
Uniflex Hydraulik GmbH
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 Uniflex Hydraulik GmbH filed Critical Uniflex Hydraulik GmbH
Publication of EP4135973A1 publication Critical patent/EP4135973A1/fr
Application granted granted Critical
Publication of EP4135973C0 publication Critical patent/EP4135973C0/fr
Publication of EP4135973B1 publication Critical patent/EP4135973B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B7/00—Presses characterised by a particular arrangement of the pressing members
    • B30B7/04—Presses characterised by a particular arrangement of the pressing members wherein pressing is effected in different directions simultaneously or in turn
    • 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
    • B30B1/007—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 using a fluid connection between the drive means and the press ram
    • 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
    • B30B1/40—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 wedge means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/062—Press plates
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/068—Drive connections, e.g. pivotal

Definitions

  • the present invention relates, as stated in the preamble of claim 1, to a radial press with a first and a second ring structure extending around a press axis and a plurality of pressed bodies arranged between these around the press axis and slidably supported on the support surfaces assigned to the ring structures, the
  • the axial distance between the two ring structures can be changed by means of a hydraulic drive system, which comprises a plurality of hydraulic cylinder-piston units that are oriented parallel to the press axis and distributed around it, each of which has the cylinder with a first of the two ring structures and the piston rod are coupled to the second ring structure, and furthermore at least the support surfaces assigned to one of the two ring structures are oriented inclined to the press axis.
  • Radial presses of the generic type mentioned above are known in various designs (cf. for example DE 35 12 241 A1 , US 4,550,587 A , FR 2 341 093 A1 , US 2014/0331734 A1 and DE 36 11 253 C2 ) and in use (for example in the form of the “HM 200” radial press from Uniflex Hydraulik GmbH, Karben). They are equally compact and powerful and are characterized by several design-related advantages - especially compared to those of the yoke press design (see, for example, the "HM 325" radial press from Uniflex Hydraulik GmbH, Karben). This includes in particular that the press axis does not move during the pressing process shifted, which is particularly essential for automatic loading. Another advantage is the flexibility in terms of the number of compacts; if necessary, these can even be provided in an odd number.
  • the drive system comprises, in addition to the hydraulic cylinder-piston units that cause the (power) pressing, at least one further hydraulic cylinder-piston unit with a hydraulic working space with a smaller effective area, which is acted upon by the hydraulic pump of the drive system causes a rapid adjustment of the two ring structures, during which rapid adjustment the hydraulic cylinder-piston units used for power pressing are passively moved and fed from the tank in the suction mode (cf. for example DE 101 49 924 A1 concerning a non-generic hollow piston type radial press).
  • the geometry of the support surfaces of the at least one ring structure inclined to the press axis and the counter surfaces of the pressed bodies sliding on these are designed in a stepped manner, so that there are two different transmission ratios between the relative movement of the two ring structures to one another and the radial movement of the pressed bodies.
  • the present invention has set itself the task of providing a radial press of the generic type which, under practical conditions, is particularly suitable for forming particularly large workpieces with a particularly high pressing force and is superior to the prior art in such an application.
  • an electromechanical rapid adjustment drive comprising a plurality of actuators that function in parallel to one another and coordinate with one another.
  • an electromechanical rapid adjustment drive comprising a plurality of actuators that function in parallel to one another and coordinate with one another.
  • the high pressing forces to be sought here can be achieved with reasonable surface pressures between the support surfaces and the associated counter surfaces, which is important, among other things, from the point of view of the service life of the radial press.
  • the transition from closing the tool in rapid motion to power pressing is freely adjustable in adaptation to the respective workpiece. This enables optimized processes, which increases efficiency.
  • radial presses according to the invention are also superior to those in which the drive system, in addition to the hydraulic cylinder-piston units that effect the (power) pressing, comprises at least one further hydraulic cylinder-piston unit - which effects the rapid adjustment (see above).
  • the electromechanical rapid adjustment drive used according to the invention comprising several actuators - functionally parallel to one another and coordinated with one another - is characterized by a particularly high possible response capacity; it can react to internal process conditions much faster than a hydraulic high-speed drive.
  • the design of the radial press according to the invention allows, in particular, a sudden stopping of the movement of the two ring structures relative to one another in rapid motion, for example if one of the pressed bodies comes into contact with comes to the workpiece.
  • the tool can be closed in rapid motion at a higher speed (higher dynamics) and closer to the workpiece, without endangering the integrity of the respective workpiece, which allows cycle times to be shortened to increase efficiency .
  • the cylinder-piston units are designed as synchronous cylinders. This can, in a completely surprising way, contribute to substantially further improved advantageous properties of the radial press, namely to further increased dynamics. Because they are designed as synchronous cylinders, the cylinder-piston units of the drive unit are volume-neutral in rapid traverse; there is no volume difference to be fed from the tank. As a result, hydraulic fluid can only be “transferred” within the respective cylinder-piston unit from one working space to the other in rapid traverse. There is no need to suck in hydraulic fluid from the tank.
  • each synchronous cylinder has a direct one Hydraulic short circuit of the two working spaces of the relevant synchronous cylinder valve unit is assigned. This means that the hydraulic fluid within the respective cylinder-piston unit is transferred from one working space to the other using the shortest possible route. Losses can be minimized in this way, especially since comparatively large flow cross sections can be worked with. It is particularly advantageous if the valve units are each arranged at the ends of the assigned piston rod having supply channels. This means there is no need for piping.
  • the rapid adjustment drive comprises a common servo motor that acts on all adjusters.
  • the adjusters are coordinated mechanically, so to speak, in that branching gears are provided in the drive train from the common servo motor to the majority of the adjusters connected to it.
  • the forced coupling of the adjusters provided in this way not only improves the manufacturing precision that can be achieved; It also promotes particularly high permissible dynamics in rapid traverse.
  • the rapid adjustment drive comprises a self-locking gear.
  • Such self-locking in the drive train between the (common) servo motor and the adjusters is of great benefit when assembling the radial press and when carrying out maintenance work, especially when it comes to one standing design of the radial press, ie vertically oriented press axis.
  • a separating clutch preferably an electromechanical separating clutch, is provided in the drive train of the rapid adjustment drive and/or if the drive train of the rapid adjustment drive has an input used for manual operation.
  • adjusters are not connected directly to the two ring structures, but rather act between the cylinder and the piston rod of a hydraulic cylinder-piston unit. In this way, the number of force-transmitting connections of drive components to the ring structures can be minimized.
  • the optimal integrity of the ring structures ensures their dimensional stability even under the highest loads and thus avoids unnecessarily high masses.
  • the pressed bodies include base jaws and press jaws that can be attached to these in an interchangeable manner.
  • a hydraulically actuated locking system can act between the base jaws and the pressing jaws. This is useful in large presses for minimal changeover times by automatically changing the press jaws.
  • the press axis is oriented vertically, so that one of the ring structures is a lower ring structure and the other ring structure is an upper ring structure forms.
  • the lower ring structure is preferably supported via a support structure on the substrate at a distance from it. This creates a space below the lower ring structure into which a correspondingly large workpiece to be pressed can extend.
  • the upper ring structure is located at least to the extent of a substantial part of its own mass and that of the elements of the hydraulic cylinder-piston units assigned to it via spring elements (e.g. gas springs) on the lower ring structure supported.
  • the unit - comprising the upper ring structure and the elements of the hydraulic cylinder-piston units assigned to it - is more or less balanced via the spring elements, so that the hydraulic drive system and / or the rapid adjustment drive for opening the tool Forces to be provided are low.
  • the adjusters of the rapid adjustment drive see above
  • Yet another preferred development of the radial press according to the invention is characterized in that only the support surfaces assigned to one of the two ring structures are inclined to the press axis, while the support surfaces assigned to the other ring structure are oriented perpendicular to the press axis. In this way When the tool is closed and opened, there is no axial movement of the pressed bodies relative to the second-mentioned ring structure. If this is designed as a stationary ring structure (e.g. as a lower ring structure supported on the ground in the sense explained above), then the pressed bodies do not carry out any axial movement when opening and closing the tool, but only a radial movement.
  • the pressed bodies are positively guided relative to the two ring structures.
  • the pressed bodies are returned radially outwards by return springs when the radial press is opened, as is provided in the prior art, this is done according to this development of the invention by positively guiding the pressed bodies on the two ring structures; In other words, the position of the pressed bodies is clearly defined here by their positive guidance on the two ring structures. Return springs acting between the pressed bodies can be omitted.
  • Such positive guidance of the pressed bodies on the two ring structures is reflected in several significant practical advantages.
  • a double, two-sided positive guidance of the pressed bodies prevents them from tipping - particularly as a result of an axially acting load.
  • the resistance of the pressed bodies against tipping that can be achieved in this way makes the radial presses designed in this way suitable for the radial pressing of axially loaded workpieces.
  • This is again a crucial aspect, especially in connection with the processing of particularly large and/or heavy workpieces; because for these the radial deformation in radial presses with a vertically oriented press axis, i.e. H.
  • a radial press that is suitable for pressing large workpieces can also be used to reliably form workpieces with dimensions that are significantly below the maximum dimension if the pressed bodies are adapted accordingly (e.g. by replacing replaceable pressing jaws; see below).
  • the positive guidance of the pressed bodies on both sides - when opening the radial press - reliably prevents the pressed bodies from being lifted off in the direction of the press axis from the support surfaces inclined relative to the press axis as a result of radially inwardly directed forces.
  • This development of the invention also provides a solution for - depending on the specific contour of the workpiece surface in the forming area and the material used, especially when forming large workpieces - there is a danger of precisely such forces (“extraction forces”) caused by the clamping of the pressed bodies on the workpiece surface, through which conventional radial presses equipped with return springs can be significantly damaged in extreme cases .
  • the double, bilateral positive guidance of the pressed bodies explained above can particularly preferably take place via pairs of guide grooves assigned to the pressed bodies and the relevant ring structure and guide bodies engaging in these. It is particularly advantageous if the guide grooves are designed on the pressed bodies and/or if the guide bodies comprise guide rollers.
  • ring structure in no way implies that the structure in question is more or less round. What is more important is that the structure extends closed around a central opening.
  • the outer contour of the relevant “ring structure” can also be approximated to a polygon, for example. However, it is particularly advantageous to have a contour that is at least very close to a circular shape, because of the distribution of stresses within the ring structures that comes close to ideal conditions and also the methods that can be used to produce them.
  • the radial press 1 illustrated in the drawing and designed for operation with a vertical press axis X comprises a first, lower ring structure 2 and a second, upper ring structure 3. Both ring structures 2, 3 extend around the press axis X.
  • the lower ring structure 2 is designed as a stationary ring structure and is supported on the ground via supports 4.
  • the second, upper ring structure 3 can be raised and lowered by means of a hydraulic drive system, ie the distance between the upper ring structure 3 and the lower ring structure 2 can be reduced and increased by means of the hydraulic drive system.
  • the lower ring structure has a pot-like basic shape (opened in the center!) in that it has a base ring 6 and a substantially cylindrical wall 7 projecting from it; it is dimensioned such that the lowered upper ring structure 3 enters the lower ring structure 2 in the sense that it and the cylindrical wall 7 of the lower ring structure 2 overlap each other.
  • the radial press comprises eight pressed bodies 8 which are arranged evenly around the press axis support flat support surface 12.
  • the upper support surfaces 11 are each designed on the surface of a replaceable upper sliding plate 13, and the lower support surfaces 12 are each designed on the surface of a replaceable lower sliding plate 14. While the lower support surfaces 12 (and the associated lower counter surfaces 10) are perpendicular to the press axis X stand, the upper support surfaces 11 (as well as the associated upper counter surfaces 9) are oriented inclined to the press axis X.
  • the upper support surfaces 11 represent “control surfaces” via which an axial movement of the upper ring structure 3 is converted into a radial movement of the pressed bodies 8.
  • the upper ring structure 3 thus forms a “control ring” 15.
  • the pressed bodies 8 include base jaws 16, on which the upper and lower counter surfaces 9 and 10 are designed, and press jaws 17 that can be interchangeably attached to the base jaws 16.
  • Each of the base jaws 16 - the extent of which is parallel to the press axis X is approximately twice as large as transversely this - is guided on the upper ring structure 3 via an upper positive guide 18 and on the lower ring structure 2 via a lower positive guide 19 in such a way that it is (at least essentially) free of play on the two assigned support surfaces 11 or 12 is held, that is, it cannot be withdrawn from them.
  • the upper positive guide 18 comprises two guide grooves 20, which are incorporated laterally on the relevant base jaw 16 and extend parallel to the upper counter surface 9, and guide bodies 21 which engage in this and are arranged on the upper ring structure 3 in the form of roller arrangements attached to an (upper) roller carrier 22 23.
  • the individual rollers are each mounted on a bolt designed as an adjusting eccentric.
  • sliding plates 27 which define a support surface are attached to the upper roller carriers 22, on which the base jaws 16 are supported via assigned counter surfaces 28.
  • At least one part of the pressed bodies 8 is assigned a displacement measuring device 29 (with a measuring direction parallel to the lower positive guides 19, i.e. radially oriented), by means of which the relative position of the relevant base jaw 16 in relation to the lower ring structure 2 can be detected.
  • the distance measuring device 29 in question comprises a pin 30 connected to the base jaw 16 in question and projecting downwards therefrom with a sensor 31 arranged at the end thereof, which cooperates with an associated, radially extending measuring ruler 32 fixed to the lower ring structure 2.
  • Hydraulic drive system includes eight hydraulic cylinder-piston units 33 oriented parallel to the press axis
  • the hydraulic cylinder-piston units 33 - each arranged in a gap with the pressed bodies 8 - are designed as synchronous cylinders 34.
  • the cylinder 35 is firmly connected to the upper ring structure 3 (control ring 15) via an assigned flange 37 formed on the cylinder base 36.
  • the lower end 38 of the respective piston rod 39 extending through the cylinder 35 is, in contrast, firmly connected to the lower ring structure 2 (“support ring” 40).
  • each hydraulic cylinder-piston unit 33 within the respective cylinder 35, which is closed at the top by a pierced cover 41, two hydraulic working spaces A and B are defined, which are delimited from one another by the piston 42 which is firmly connected to the piston rod 39. These are supplied through the pierced piston rod 39.
  • a valve unit 45 is constructed on the upper end 43 of the piston rod 39 passing through the opening 44 of the cover 41 - or possibly on a mounting plate (see below) connected to it.
  • the two into the respective valve unit 45 integrated switching valves 49 which can be actuated via an electric actuator 48, allow switching between, on the one hand, fluidic communication between the two work spaces A and B with the pressure supply unit (via a passage connection between the connection a and the connection c and the connection b with the connection d ) and on the other hand a direct hydraulic short circuit of the two working spaces A and B via an internal bypass 50 that fluidly connects the connections c and d.
  • the two working spaces A and B are shut off from the pressure supply unit by means of the switching valves 49.
  • Said bypasses 50 are opened when a rapid adjustment of the two ring structures 2 and 3 relative to one another takes place by means of a rapid adjustment drive 51.
  • This is designed electromechanically and includes a drive unit 52, four adjusters 53 and a drive train 56 which connects the drive unit 52 to the four adjusters 53 and has shafts 54 and deflection gear 55.
  • Each of the four adjusters 53 (designed as a rack drive 57) is - between the cylinder 35 and the piston rod 39 acting - assigned to a hydraulic cylinder-piston unit 33.
  • a toothed wheel 58 which is fixed on the cover 41 of the respectively assigned hydraulic cylinder-piston unit 33 engages with a gear wheel which is rotatably mounted in a toothed drive housing 59.
  • the toothed drive housing 59 is constructed on a mounting plate 60, which in turn is connected to the end section of the piston rod 39 of the relevant hydraulic cylinder-piston unit protruding from the cover 41 33 is firmly connected.
  • four position measuring systems 61 are provided, each with a measuring ruler 62 fixed to the cover 41 of the associated hydraulic cylinder-piston unit 33 and a sensor 63 fixed to the relevant mounting plate 60.
  • the drive unit 52 which is also connected (at least indirectly) in a fixed position to the piston rod 39 of the relevant hydraulic cylinder-piston unit 33 and is in particular built on the valve unit 45 assigned to it, comprises a servomotor 64 with a flanged, self-locking planetary gear 65, an electromechanical separating clutch 66, one of the Manual operation input 67 and a transfer case 68 with two outputs 69, to which assigned shafts 54 of the drive train 56 are connected.
  • the unit consisting of the upper ring structure 3 and the eight cylinders 35 of the hydraulic cylinder-piston units 33 connected to it is supported on the lower ring structure 2 via spring elements 70 at least to the extent of a substantial part of its mass.
  • gas springs 71 extend between a lower articulation point 72 assigned to the lower ring structure 2 and an upper articulation point 73 assigned to the cover 41 of a hydraulic cylinder-piston unit 33.
  • the radial press 1 is protected by a cover 74 - hydraulically actuated locks are provided, which enable the eight base jaws 16 to be equipped automatically with a set of press jaws.
  • the locks each comprise a clamping unit 76 attached to the base jaw base body 75 with a pivotally driven claw, which pulls the respective pressing jaw 17 - resting on the reinforcement rail 77 of the base jaw base body 75 - radially outwards into its locking position defined by the stops 78 .
  • the locking comprises two hydraulic cylinders 79 arranged in pairs on the base jaw base body 75 with locking heads 80 attached to the respective piston rod, which press the relevant pressing jaw 17 into the assigned receptacle of the base jaw base body 75.
  • a mechanical spring 81 supports the respective hydraulic cylinder 79 and ensures that the relevant pressing jaw 17 is held on the respective base jaw 16 even without external energy, that is, it does not tip over due to its own weight.
  • the position of the locking heads 80 is detected by sensors 82, which are attached to the base jaw base body 75 via angles 83.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)

Claims (14)

  1. Presse radiale (1) avec une première et une deuxième structure annulaire (2, 3) s'étendant autour d'un axe de pressage (X) et plusieurs corps de pressage (8) disposés entre celles-ci autour de l'axe de pressage (X), s'appuyant pouvant se déplacer sur les surfaces d'appui (11, 12) attribuées aux structures annulaires (2, 3),
    sachant que la distance axiale des deux structures annulaires (2, 3) peut être modifiée entre elles au moyen d'un système d'entraînement hydraulique, lequel comprend une pluralité d'unités vérin-piston hydrauliques (33) orientées parallèlement à l'axe de pressage (X) et disposées réparties autour de celui-ci desquelles sont respectivement couplés le vérin (35) à une première des deux structures annulaires et la tige de piston (39) à la deuxième structure annulaire et sachant en plus qu'au moins les surfaces d'appui (11, 12) attribuées à une des deux structures annulaires (2, 3) sont orientées inclinées par rapport à l'axe de pressage (X),
    caractérisée en ce qu'
    un mécanisme de réglage rapide électromécanique (51) est prévu comprenant plusieurs régleurs (53) coordonnés entre eux, agissant de façon fonctionnelle parallèlement l'un par rapport à l'autre.
  2. Presse radiale selon la revendication 1, caractérisée en ce que les unités vérin-piston (33) sont exécutées sous la forme de vérins synchronisés (34).
  3. Presse radiale selon la revendication 2, caractérisée en ce qu'une unité de soupape (45) permettant un court-circuit hydraulique direct des deux espaces de travail (A, B) du vérin synchronisé (34) concerné est attribuée à chaque vérin synchronisé (34).
  4. Presse radiale selon la revendication 3, caractérisée en ce que les unités de soupape (45) sont respectivement disposées en extrémité sur la tige de piston (39) attribuée comportant des conduits d'alimentation (46, 47) .
  5. Presse radiale selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le mécanisme de réglage rapide (51) comprend un servomoteur (64) commun agissant sur tous les régleurs (53) .
  6. Presse radiale selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la commande de réglage rapide (51) comprend une transmission autobloquante.
  7. Presse radiale selon l'une quelconque des revendications 1 à 6, caractérisée en ce qu'un accouplement de séparation (66), de préférence un accouplement de séparation électromécanique, est prévu dans la chaîne cinématique (56) du mécanisme de réglage rapide (51).
  8. Presse radiale selon l'une quelconque des revendications 1 à 7, caractérisée en ce que la chaîne cinématique (56) du mécanisme de réglage rapide (51) comporte un accès (67) servant à l'actionnement manuel.
  9. Presse radiale selon l'une quelconque des revendications 1 à 8, caractérisée en ce que les régleurs (53) agissent respectivement entre le vérin (35) et la tige de piston (39) d'une unité vérin-piston hydraulique (33).
  10. Presse radiale selon l'une quelconque des revendications 1 à 9, caractérisée en ce que les corps de pressage (8) comprennent des mâchoires de base (16) et des mâchoires de pressage (17) pouvant être fixées et changées sur ceux-ci, sachant que l'extension des mâchoires de base (16) parallèlement à l'axe de pressage (X) est au moins deux fois plus grand que transversalement à celui-ci et/ou un système de verrouillage pouvant être actionné hydrauliquement agit entre les mâchoires de base (16) et les mâchoires de pressage (17).
  11. Presse radiale selon l'une quelconque des revendications 1 à 10, caractérisée en ce que seules les surfaces d'appui (11) attribuées à une des deux structures annulaires (2, 3) sont inclinées par rapport à l'axe de pressage (X), les surfaces d'appui (12) attribuées à l'autre structure annulaire sont par contre orientées perpendiculairement à l'axe de pressage (X), sachant de préférence que la structure annulaire (2) comportant les surfaces d'appui (12) orientées perpendiculairement à l'axe de pressage (X) est exécutée en tant que structure annulaire fixe (40) et un dispositif de mesure de course (29) avec une direction de mesure orientée radialement agit entre la structure annulaire fixe (40) et au moins un des corps de pressage (8).
  12. Presse radiale selon l'une quelconque des revendications 1 à 11, caractérisée en ce que l'axe de pressage (X) est orienté verticalement, sachant qu'une des structures annulaires forme une structure annulaire inférieure (2) et l'autre structure annulaire une structure annulaire supérieure ((3).
  13. Presse radiale selon la revendication 12, caractérisée en ce que la structure annulaire inférieure (2) s'appuie par le biais d'une structure porteuse (4) sur le fond à distance de celui-ci, sachant de préférence que la structure annulaire supérieure (3) s'appuie par le biais d'éléments à ressort (70) exécutés comme des ressorts pneumatiques (71) sur la structure annulaire inférieure (2) au moins dans la périphérie d'une partie essentielle de sa masse propre ainsi que de celle des éléments attribués à celle-ci des unités vérin-piston hydrauliques (33), lesquels agissent entre la structure annulaire inférieure (2) et les éléments des unités vérin-piston hydrauliques (33) attribués à la structure annulaire supérieure (3).
  14. Presse radiale selon l'une quelconque des revendications 1 à 13, caractérisée en ce que les corps de pressage (8) sont en guidage forcé par rapport aux deux structures annulaires (2, 3), sachant de préférence que le guidage forcé (18, 19) a lieu respectivement par le biais des corps de pressage (8) et de paires attribuées à la structure annulaire (2, 3) concernée de rainures de guidage (20, 24) réalisées sur les corps de pressage (8) et des corps de pressage (21) venant en prise dans celles-ci, lesquels comprennent respectivement des galets de guidage (23, 26) logés sur axe exécuté sous la forme d'un un excentrique de réglage.
EP21751563.4A 2020-08-11 2021-07-28 Presse radiale Active EP4135973B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020121143.0A DE102020121143B4 (de) 2020-08-11 2020-08-11 Radialpresse
PCT/EP2021/071137 WO2022033873A1 (fr) 2020-08-11 2021-07-28 Presse radiale

Publications (3)

Publication Number Publication Date
EP4135973A1 EP4135973A1 (fr) 2023-02-22
EP4135973C0 EP4135973C0 (fr) 2024-01-10
EP4135973B1 true EP4135973B1 (fr) 2024-01-10

Family

ID=77226809

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21751563.4A Active EP4135973B1 (fr) 2020-08-11 2021-07-28 Presse radiale

Country Status (5)

Country Link
US (1) US20230116737A1 (fr)
EP (1) EP4135973B1 (fr)
CN (1) CN115835952B (fr)
DE (1) DE102020121143B4 (fr)
WO (1) WO2022033873A1 (fr)

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2341093A1 (fr) 1976-02-13 1977-09-09 Anoflex Flexibles Machine a sertir des embouts sur des tuyauteries souples
DE2715188A1 (de) * 1977-04-05 1978-10-12 Smg Sueddeutsche Maschinenbau Presse mit einem arbeitshub vorgeschaltetem leerhub
DE3221758A1 (de) * 1982-06-09 1983-12-15 Hartmann & Lämmle GmbH & Co KG, 7255 Rutesheim Hydraulische antriebsvorrichtung
US4550587A (en) 1983-12-15 1985-11-05 The Goodyear Tire & Rubber Company Heavy duty hose crimper
DE3512241A1 (de) 1985-04-03 1986-10-16 Peter Dipl Ing Schroeck Radialpresse
DE3611253A1 (de) 1986-04-04 1987-10-08 Peter Dipl Ing Schroeck Radialpresse
DE29824688U1 (de) 1998-04-22 2002-08-01 Uniflex-Hydraulik GmbH, 61184 Karben Radialpresse
DE19817882B4 (de) * 1998-04-22 2005-08-18 Uniflex-Hydraulik Gmbh Radialpresse
AT410707B (de) * 2000-05-12 2003-07-25 Steyr Werner Waelzlager Und In Vorrichtung zum anklemmen eines hydraulikschlauches an eine schlaucharmatur mit einer presse
ITBS20010040U1 (it) * 2001-04-23 2002-10-23 Op Srl Pressa radiale per la raccordatura di tubi flessibili oleodinamici
DE10149924A1 (de) * 2001-10-10 2003-04-30 Uniflex Hydraulik Gmbh Radialpresse
EP1745869A3 (fr) * 2005-07-22 2008-04-23 Peter Dipl.-Ing. Schröck Presse radiale pour le sertissage de corps creux à symétrie de révolution
DE102005041487A1 (de) 2005-08-30 2007-04-05 Ekf Werkzeug Und Maschinenbau Gmbh Radialpresse
DE102009057726A1 (de) * 2009-12-10 2011-06-16 Uniflex-Hydraulik Gmbh Radialpresse
PL2420332T3 (pl) * 2010-08-20 2013-05-31 Op Srl Chwytak do trzymania narzędzi prasy promieniowej
DE102011015654A1 (de) * 2011-03-31 2012-10-04 Uniflex-Hydraulik Gmbh Radialpresse
AU2013251238B2 (en) 2012-11-01 2018-05-17 Betaswage Pty Ltd Indexing die shoes in a swage press
DE102012025134A1 (de) * 2012-12-21 2014-06-26 Uniflex-Hydraulik Gmbh Umformpresse
CN103170565B (zh) * 2013-03-07 2014-11-05 西安交通大学 一种无油泵交流伺服电机直驱式行程控制增压型液压机
CN103978724B (zh) * 2014-05-23 2016-07-06 南京理工大学 模块化压力机装模高度调节装置
DE102014008613A1 (de) * 2014-06-06 2015-12-17 Uniflex-Hydraulik Gmbh Radialpresse
DE102016102275A1 (de) * 2016-02-10 2017-08-10 Uniflex-Hydraulik Gmbh Radialpresse
DE102016106650B4 (de) * 2016-04-12 2021-09-16 Uniflex-Hydraulik Gmbh Radialpresse

Also Published As

Publication number Publication date
DE102020121143A1 (de) 2022-02-17
EP4135973C0 (fr) 2024-01-10
US20230116737A1 (en) 2023-04-13
EP4135973A1 (fr) 2023-02-22
WO2022033873A1 (fr) 2022-02-17
CN115835952B (zh) 2024-06-21
CN115835952A (zh) 2023-03-21
DE102020121143B4 (de) 2022-03-10

Similar Documents

Publication Publication Date Title
EP2509725B1 (fr) Presse radiale
EP3442784B1 (fr) Presse radiale
AT509239B1 (de) Antriebsvorrichtung für eine biegepresse
DE102007051894A1 (de) Freigabemechanismus und mit diesem versehenen Richtvorrichtung
DE102012209077A1 (de) Spanneinrichtung zum Einspannen eines stabartigen Werkstücks und Werkzeugmaschine damit
DE102006019207B4 (de) Antriebssystem einer Mehrstößel-Umformpresse
AT507110B1 (de) Presse zum umformen von material
EP4135973B1 (fr) Presse radiale
EP4132777B1 (fr) Presse radiale
AT509907B1 (de) Schliesseinheit für eine spritzgiessmaschine
EP3024646B1 (fr) Module de force et système de pressage modulaire
EP0051121B1 (fr) Machine de fluotournage
DE3323428C2 (fr)
DE102004006126A1 (de) Presse mit verriegeltem Stößel
EP3448594B1 (fr) Presse-transfert pourvue d'un serre-flan en c
EP0002032A1 (fr) Procédé et dispositif de fabrication de poulies multigorges
WO2014001198A1 (fr) Machine de forage profond, adaptateur et procédé de forage profond
EP0659501B1 (fr) Machine à forger
DE19607257C2 (de) Hydraulische Blechformpresse
DE202006013430U1 (de) Vorrichtung zur Übertragung der Zuhaltekräfte bei Spritzgiessformen
DE19809371A1 (de) Kupplung zur Verbindung von Werkstückgreifern mit einer Handhabungseinrichtung
EP1344585A2 (fr) Dispositif d'emboutissage profond hydroélastique
EP4337400A1 (fr) Procédé de formage à chaud d'un lingot de forge coulé à l'aide d'un dispositif de forgeage
DE4444497A1 (de) Schmiedemaschine
CH616208A5 (en) Axial piston pump whose hydraulic-fluid flow can be regulated by means of suction valve control, and use thereof in a hydraulic drive of a plate-bending press.

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

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

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20221118

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref document number: 502021002455

Country of ref document: DE

Ref country code: DE

Ref legal event code: R079

Free format text: PREVIOUS MAIN CLASS: B30B0015160000

Ipc: B30B0001400000

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230529

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: B30B 7/04 20060101ALI20230706BHEP

Ipc: B30B 1/40 20060101AFI20230706BHEP

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
INTG Intention to grant announced

Effective date: 20230804

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502021002455

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

U01 Request for unitary effect filed

Effective date: 20240201

P04 Withdrawal of opt-out of the competence of the unified patent court (upc) registered

Effective date: 20240206

U07 Unitary effect registered

Designated state(s): AT BE BG DE DK EE FI FR IT LT LU LV MT NL PT SE SI

Effective date: 20240209

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

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240510

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240411

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

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240410

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240110

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240110