EP4135973A1 - Presse radiale - Google Patents

Presse radiale

Info

Publication number
EP4135973A1
EP4135973A1 EP21751563.4A EP21751563A EP4135973A1 EP 4135973 A1 EP4135973 A1 EP 4135973A1 EP 21751563 A EP21751563 A EP 21751563A EP 4135973 A1 EP4135973 A1 EP 4135973A1
Authority
EP
European Patent Office
Prior art keywords
press according
ring structure
radial press
radial
cylinder
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.)
Granted
Application number
EP21751563.4A
Other languages
German (de)
English (en)
Other versions
EP4135973C0 (fr
EP4135973B1 (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

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 to a radial press with a first and a second ring structure extending around a pressing axis and a plurality of support surfaces arranged between them around the pressing axis and displaceably supported on the ring structures Press bodies, whereby 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 oriented parallel to the press axis and distributed around it, of which the cylinder is connected to a first of the both ring structures and the piston rod are coupled to the second ring structure, and wherein at least the one of the two ring structures associated support surfaces are oriented inclined to the pressing axis.
  • a hydraulic drive system which comprises a plurality of hydraulic cylinder-piston units oriented parallel to the press axis and distributed around it, of which the cylinder is connected to a first of the both ring structures and the piston rod are coupled to the second ring structure, and wherein at least the one of the two ring structures associated support
  • Radial presses of the aforementioned generic type are known in various configurations (see, for example, DE 35 12 241 A1, US Pat (For example in the form of the radial press “HM 200" from Uniflex Hydraulics 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 (cf . e.g. the "HM 325" radial press from Uniflex Hydraulic GmbH, Karben). This includes in particular that the pressing axis does not move during the pressing process relocated, which is particularly essential for automatic loading. Another advantage is the flexibility with regard to the number of compacts; these may even be provided in an odd number.
  • the drive system comprises, in addition to the hydraulic cylinder-piston units effecting the (power) pressing, at least one further hydraulic cylinder-piston unit with a hydraulic working chamber having a smaller effective area, which is acted upon by the hydraulic pump of the drive system causes rapid adjustment of the two ring structures, during which rapid adjustment the hydraulic cylinder-piston units used for power pressing are moved passively and are fed from the tank in suction operation (see, for example, DE 101 49 924 A1 relating to a non-generic Hollow Piston Type Radial Press ) .
  • 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 adjusters.
  • d. H through the implementation of an electromechanical rapid adjustment drive comprising several - functionally parallel to one another and coordinated - adjusters, by means of which the axial distance existing between the two ring structures is possible without the use of hydraulic components, in particular without active loading of the hydraulic cylinder-piston units
  • a number of serious advantages arise specifically for the application situation that is of interest here. So stand for other than this Radial presses with stepped geometry of the support and counter surfaces (see above) have the largest possible contact surface for power pressing.
  • the high pressing forces to be aimed for here can be realized with reasonable surface pressures between the support surfaces and the associated mating surfaces, which u . a. is significant from the point of view of the service life of the radial press.
  • the transition from closing the tool in rapid traverse to power pressing can be freely adjusted to suit the respective workpiece. This enables optimized process sequences, which is beneficial to ef fi ciency.
  • radial presses according to the invention are also superior to those in which the drive system comprises at least one additional hydraulic cylinder-piston unit which effects the rapid adjustment in addition to the hydraulic cylinder-piston units which effect the (power) pressing ( see above).
  • the electromechanical high-speed adjustment drive used according to the invention which comprises a plurality of adjusters—acting functionally parallel to one another and coordinated with one another—is distinguished by a particularly high possible reaction capacity; it can react to process-internal conditions far more quickly than a hydraulic high-speed drive.
  • the inventive design of the radial press allows the movement of the two ring structures to be stopped abruptly in relation to one another in rapid traverse, if, for example, one of the press bodies is in contact with the workpiece comes .
  • the tool can be closed in rapid traverse at a higher speed (higher dynamics) and closer to the workpiece without endangering the integrity of the respective workpiece, which means a reduction in efficiency that increases the cycle times allow .
  • the cylinder-piston units are designed as synchronous cylinders. Again, in a thoroughly surprising way, this is able to contribute to substantially further improved advantageous properties of the radial press, specifically to a further increased dynamic. Because of their design as synchronous cylinders, the cylinder-piston units of the drive unit are volume-neutral in rapid traverse; there is no difference in volume to be fed from the tank. Consequently, in rapid traverse alone, hydraulic fluid can be “transferred” within the respective cylinder-piston unit from one working chamber to the other. A suction of hydraulic fluid from the tank can be omitted.
  • each synchronous cylinder has a direct hydraulic short circuit of the two working chambers of the relevant double-rod cylinder is assigned enabling valve unit.
  • the hydraulic fluid is transferred within the respective cylinder-piston unit from one working area to the other in the shortest possible way. Losses can be minimized in this way, especially since it is possible to work with comparatively large flow cross sections.
  • the valve units are each arranged at the end on the associated piston rod having supply channels. So there is no need for piping.
  • the high-speed adjustment drive includes a common servomotor that acts on all adjusters.
  • the adjusters are coordinated here mechanically, 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 accommodates the achievable manufacturing precision; for its part, it also promotes particularly high permissible dynamics in rapid traverse.
  • the rapid adjustment drive includes a self-locking gear.
  • a self-locking in the drive train between the (common) servomotor and the control is of great benefit when assembling the radial press and when carrying out maintenance work, especially in one standing construction of the radial press, d. H . vertically oriented pressing axis.
  • a separating clutch preferably an electromechanical separating clutch, is provided in the drive train of the high-speed adjustment drive and/or if the drive train of the high-speed adjustment drive has an input for manual operation.
  • adjusters are not directly connected to the two ring structures, but instead each act between the cylinder and the piston rod of a hydraulic cylinder-piston unit. In this way, the number of power-transmitting connections from drive components to the ring structures can be minimized.
  • the optimum integrity of the ring structures is consistent with their dimensional stability even under the highest loads and thus the avoidance of unnecessarily high masses.
  • the press bodies comprise base jaws and press jaws which can be fastened to them in an exchangeable manner.
  • a hydraulically actuable locking system can act between the base jaws and the pressing jaws. This is useful for large presses for minimal changeover times by automatically changing the press jaws.
  • the pressing 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 on the subsurface at a distance from it via a supporting structure. A space is thus created below the lower ring structure, into which a correspondingly large workpiece to be pressed can extend. It is also particularly favorable with such vertical radial presses according to the invention if the upper ring structure rests at least to the extent of a significant 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 one ring structure is supported.
  • spring elements e.g. gas springs
  • the unit - comprising the upper ring structure and the associated elements of the hydraulic cylinder-piston units - is more or less balanced via the spring elements, so that the hydraulic drive system and/or the express adjustment drive for opening the Tool to be provided forces 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 compacts 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 press bodies do not perform any axial movement when the tool is opened and closed, only a radial movement.
  • the radial press in the sense of a high flexibility of use (see above) of the radial press according to this development of the invention, it has a positive effect that a limitation of the working range (ie the maximum possible radial stroke of the press bodies), as is regularly the case with conventional radial presses by the return springs (ie given by their working area) does not exist for them.
  • the resetting of the compacts when the radial press is opened by the forced guidance of the compacts on both ring structures on both sides allows a larger working range of the radial press compared to the prior art.
  • the omission of the return springs conventionally arranged between the adjacent press bodies simplifies the assembly of the radial press.
  • the amount of pressing force available on the workpiece also benefits from the fact that the tool does not have to be closed against the restoring force of return springs.
  • the return springs In the case of such conventionally designed radial presses in which tilting moments and/or pull-out forces acting on the press body must be expected within the range of applications (see above), the return springs must be very provide large restoring forces. These cause a possible substantial reduction in the forming force that can be effectively applied to the workpiece.
  • the above-described double forced guidance of the pressing bodies on both sides can particularly preferably take place in each case via the pairs of guide grooves assigned to the pressing bodies and the ring structure in question and guide bodies engaging in these. It is particularly advantageous if the guide grooves are formed on the press bodies and/or if the guide bodies include guide rollers.
  • ring structure in no way implies that the structure in question is more or less round. Rather, it is crucial that the structure extends closed around a central opening.
  • the outer contour of the “ring structure” in question can also be approximated to a polygon, for example.
  • FIG. 1 the radial press in question in a perspective view at an angle from above
  • Fig. 2 from a similar perspective as in FIG. 1 the radial press shown in this in section
  • FIG. 3 shows a detail from FIG. 2 on an enlarged scale
  • FIG. 4 in a perspective view obliquely from above one of the eight hydraulic cylinder-piston units of the radial press shown in Figures 1-3 and
  • FIG. 5 one of the eight press bodies of the radial press according to FIGS. 1-3 without the associated cladding.
  • the radial press 1 illustrated in the drawing and designed for operation with a vertical pressing axis X comprises a first, lower ring structure 2 and a second, upper ring structure 3 . Both ring structures 2 , 3 extend around the pressing axis X .
  • the lower ring structure 2 is embodied as a stationary ring structure and is supported on the substrate via supports 4 .
  • the second, upper ring structure 3 can be raised and lowered by means of a hydraulic drive system, d. H . 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 (perforated in the center!) in that it has a bottom ring 6 and an essentially 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 one another.
  • the radial press comprises eight press bodies 8 arranged evenly around the press axis X, each of which can be slid - via assigned upper counter surfaces 9 and lower counter surfaces 10 - on an upper planar support surface 11 assigned to the upper ring structure 3 and one of the lower ring structure 2 associated lower level support surface 12 support.
  • the upper support surfaces 11 are each designed on the surface of an exchangeable upper slide plate 13 , and the lower support surfaces 12 each on the surface of an exchangeable lower slide plate 14 . While the lower support surfaces 12 (and the associated lower mating surfaces 10) are perpendicular to the pressing axis X, the upper supporting surfaces 11 (and the associated upper mating surfaces 9) are oriented inclined to the pressing 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 compact 8 .
  • the upper ring structure 3 thus forms a "control ring" 15 .
  • the press bodies 8 comprise base jaws 16, on which the upper and lower mating surfaces 9 and 10, and press jaws 17 that can be attached to the base jaws 16 in an exchangeable manner.
  • Each of the base jaws 16 - whose extent parallel to the pressing axis X is about twice as large as transversely to it - is guided on the upper ring structure 3 via an upper restricted guide 18 and on the lower ring structure 2 via a lower restricted guide 19 in such a way that it (at least essentially) no play on the two assigned support surfaces 11 or . 12 is held, i . H . cannot be withdrawn from these .
  • the upper restricted guide 18 comprises two guide grooves 20 worked into the side of the base jaw 16 in question, extending parallel to the upper counter surface 9, and guide bodies 21, which engage in these grooves and are arranged on the upper ring structure 3, in the form of on an (upper) roller carrier 22 mounted roller assemblies 23 .
  • the individual rollers are each mounted on a bolt designed as an adjusting eccentric.
  • sliding plates 27 each defining a support surface are attached to the upper roller carriers 22 and on which the base jaws 16 are supported via associated mating surfaces 28 .
  • At least one part of the press body 8 is assigned a path measuring device 29 (with a measuring direction parallel to the lower forced guides 19, i .e . radially oriented measuring direction), 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 displacement measuring device 29 in question comprises a pin 30 connected to the base jaw 16 in question and protruding downwards from the latter, with a sensor 31 arranged on the end thereof, which cooperates with an associated, radially extending measuring ruler 32 fixed to the lower ring structure 2 .
  • the hydraulic drive system includes eight hydraulic cylinder-piston units 33 oriented parallel to the press axis X and a pressure supply unit (not shown, of conventional design) with a tank, a motor-pump unit and a controller.
  • the hydraulic cylinder-piston units 33 are designed as double-rod cylinders 34 - each of which is arranged with a gap in relation to the press bodies 8 .
  • the cylinder 35 is in each case firmly connected to the upper ring structure 3 (control ring 15) via an associated flange 37 formed on the cylinder base 36 .
  • the lower end 38 of the respective piston rod 39 extending through the cylinder 35 is firmly connected to the lower ring structure 2 (“support ring” 40).
  • each hydraulic cylinder-piston unit 33 two hydraulic working spaces A and B are defined within the respective cylinder 35, which is closed at the top by a pierced cover 41. These are supplied through the pierced piston rod 39 .
  • a valve unit 45 is installed, if necessary on a mounting plate connected to it (see below). This has four connections a, b, c, d each; It communicates with the pressure supply unit via two of these (ports a and b), while the other two ports c and d are connected to the two work spaces A and B supplying, within the piston rod 39 extending supply channels 46 and 46 respectively. 47 communicate .
  • the two in 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 working chambers A and B and the pressure supply unit (via a flow connection between port a and port c and between port b and port d) and on the other hand a direct hydraulic short-circuit of the two working chambers A and B via an internal bypass 50 fluidically connecting the connections c and d to one another.
  • the two working chambers A and B are shut off from the pressure supply unit by means of the switching valves 49 .
  • Said bypasses 50 are opened when 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 comprises a drive unit 52 , four adjusters 53 and a drive train 56 which connects the drive unit 52 to the four control elements 53 and has shafts 54 and deflection gears 55 .
  • Each of the four adjusters 53 (designed as a rack and pinion drive 57) is assigned to a hydraulic cylinder-piston unit 33, acting between the cylinder 35 and the piston rod 39.
  • a gear wheel which is rotatably mounted in a pinion housing 59, is in engagement with a toothed rack 58 fixed to the cover 41 of the respective associated hydraulic cylinder-piston unit 33.
  • the rack and pinion 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 that projects out of the cover 41.
  • Piston unit 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 (at least indirectly) fixed in position to the piston rod 39 of the relevant hydraulic cylinder-piston unit 33 and is mounted in particular 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, a input 67 serving for manual operation and a transfer case 68 with two outputs 69 to which associated 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 respective lower pivot point 72 associated with the lower ring structure 2 and an upper pivot point 73 associated with the cover 41 of a hydraulic cylinder-piston unit 33 .
  • each protected by a panel 74 - hydraulically actuated locks are provided, which allow automated loading of the eight base jaws 16 with a set of press jaws.
  • the locks each comprise a clamping unit 76 attached to the base jaw body 75 with a pivotally driven claw which presses the respective press jaw 17 - resting on the reinforcement rail 77 of the base jaw body 75 - radially outwards into its defined by the stops 78 locking position pulls .
  • the locking mechanism comprises two hydraulic cylinders 79 arranged in pairs on the base jaw body 75 with locking heads 80 attached to the respective piston rod, which press the press jaw 17 in question into the associated receptacle of the base jaw body 75 .
  • a mechanical spring 81 supports the hydraulic cylinder 79 in question and ensures that the pressing jaw 17 in question is held on the respective base jaw 16 even without external energy, d. H . does not tip over due to its own weight.
  • the position of the locking heads 80 is detected by means of sensors 82 which are attached to the base body 75 via brackets 83 .

Landscapes

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

Abstract

Dans une presse radiale ayant une première et une seconde structure annulaire (2, 3) qui s'étendent autour d'un axe de presse et qui comportent une pluralité d'éléments de pression (8), qui sont disposés autour de l'axe de presse et sont supportés en translation sur des surfaces de support associées aux structures annulaires (2 ; 3), la distance axiale des deux structures annulaires (2 ; 3) l'une par rapport à l'autre peut être modifiée au moyen d'un système d'entraînement hydraulique qui comprend une pluralité d'unités cylindre-piston hydrauliques (33) orientées parallèlement à l'axe de presse et réparties autour de l'axe de presse, le cylindre (35) de chaque unité cylindre-piston (33) étant accouplé à une première des deux structures annulaires et la tige de piston (39) de chaque unité cylindre-piston étant accouplée à la seconde structure annulaire. Au moins les surfaces de support associées à l'une des deux structures annulaires (2 ; 3) sont orientées selon une inclinaison par rapport à l'axe de presse. Est également décrit un entraînement de réglage rapide électromécanique (51) comprenant une pluralité de dispositifs de réglage (53).
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 true EP4135973A1 (fr) 2023-02-22
EP4135973C0 EP4135973C0 (fr) 2024-01-10
EP4135973B1 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) US12441074B2 (fr)
EP (1) EP4135973B1 (fr)
CN (1) CN115835952B (fr)
DE (1) DE102020121143B4 (fr)
WO (1) WO2022033873A1 (fr)

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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
DE19817882B4 (de) * 1998-04-22 2005-08-18 Uniflex-Hydraulik Gmbh Radialpresse
DE29824688U1 (de) 1998-04-22 2002-08-01 Uniflex-Hydraulik GmbH, 61184 Karben 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
US9283613B2 (en) 2012-11-01 2016-03-15 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
CN115835952A (zh) 2023-03-21
US12441074B2 (en) 2025-10-14
US20230116737A1 (en) 2023-04-13
WO2022033873A1 (fr) 2022-02-17
DE102020121143A1 (de) 2022-02-17
CN115835952B (zh) 2024-06-21
EP4135973C0 (fr) 2024-01-10
DE102020121143B4 (de) 2022-03-10
EP4135973B1 (fr) 2024-01-10

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