EP0549771A1 - Presse oscillante. - Google Patents

Presse oscillante.

Info

Publication number
EP0549771A1
EP0549771A1 EP92915796A EP92915796A EP0549771A1 EP 0549771 A1 EP0549771 A1 EP 0549771A1 EP 92915796 A EP92915796 A EP 92915796A EP 92915796 A EP92915796 A EP 92915796A EP 0549771 A1 EP0549771 A1 EP 0549771A1
Authority
EP
European Patent Office
Prior art keywords
wobble
die half
press according
die
mass
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
EP92915796A
Other languages
German (de)
English (en)
Other versions
EP0549771B1 (fr
Inventor
Walter Schlatter
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.)
Colcon Anstalt
Original Assignee
Colcon Anstalt
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 Colcon Anstalt filed Critical Colcon Anstalt
Publication of EP0549771A1 publication Critical patent/EP0549771A1/fr
Application granted granted Critical
Publication of EP0549771B1 publication Critical patent/EP0549771B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/02—Special design or construction
    • B21J9/025—Special design or construction with rolling or wobbling dies

Definitions

  • the invention relates to a wobble press with a first die half, which is driven to wobble with a drive with respect to a spatial axis about a pivot point, and with a second die half, which moves axially parallel relative to the first die half, the wobble drive having hydraulic working pistons with a regular, defined, pulsating flow of a hydraulic medium are supplied, and which in turn are connected to the first half of the die to generate a wobble movement.
  • the wobble drive having hydraulic working pistons with a regular, defined, pulsating flow of a hydraulic medium are supplied, and which in turn are connected to the first half of the die to generate a wobble movement.
  • Such a wobble press is known, for example, from CH 662 983, CH 666 857 or DE 1 652 653 and is used to manufacture solid parts made of metal or other solid materials, the part or workpiece being formed between two forming tool or die parts, and whereby, in contrast to the classic axially parallel pressing process, one tool half executes a rolling tumbling movement with respect to the other. Due to the partial contact of the upper tool with the material, the material can be made to flow with a significantly lower pressing force during the wobble movement, so that significantly larger degrees of deformation and a more precise shaping of the die contours can be achieved in one step.
  • the feed possible when handling results from the angle of inclination of the wobbling tool and is limited accordingly. The size of this feed then determines that for the total working stroke, i.e. for the desired upsetting height, the number of wobble rounds and, according to the wobble frequency, the deformation time.
  • the dome-shaped bearing of the wobbling tool must also absorb the entire pressing pressure.
  • the bearing pressure per unit area and thus the resulting work of friction increases significantly.
  • the frictional heat generated there must be removed from the bearing gap using a thin oil film.
  • the frictional heating which must be dissipated by the lubricant, also increases.
  • the narrow bearing gap limits the flow rate of the lubricant and coolant.
  • the invention sets itself the task of eliminating the stated disadvantages of the prior art and of creating a wobble press which permit continuous operation with an increased wobble frequency and a reduction in the forming time of a workpiece, in particular also in the half and warm ranges.
  • this object is achieved in that a countermass is connected to the first, tumbling driven die half, which is designed and arranged in such a way that its center of gravity is shifted by 180 on the opposite side of the pivot point as the center of gravity of the first die half , and that the product of their mass and their center of gravity distance from the pivot point of the wobble movement corresponds approximately to the product of the mass of the first half of the die and their center of gravity distance from the pivot point.
  • the compensation of the inertial forces of the wobbling tools can be achieved in that a displaceable mass is provided on the same side of the pivot point of the tool.
  • the invention is based on the knowledge that is apparently not taken into account in the prior art wobble presses that the disadvantages of the prior art can largely be remedied by compensating the centrifugal forces of the wobbling half of the die, so that the wobble press can be operated at an increased frequency .
  • frequencies of approximately 2400 rpm are achieved in continuous operation and the deformation time is reduced to approximately 1 to 1.5 seconds without disturbing vibrations.
  • This short forming time also allows the wobble pressing to be expanded into the area of hot forming without fear that the tools will wear out uneconomically due to the long contact time with the heated material and at the same time the material will cool prematurely during the forming process. It is particularly advantageous to ensure exact guidance of the two die halves, even with eccentric material distribution, in that a centering plate is non-positively connected to the first die half, which forms a practically play-free centering with the other die half.
  • the wobble drive of the first die half has at least three wobble pistons surrounding the wobble axis and acting on the die half, which periodically receive a cyclically varying amount of pressure medium from a multiple pump.
  • This cyclic variation is advantageously generated by two interacting axial piston pumps with rotating inclined swash plates, which act on a number of pump pistons which are connected to pressure medium lines, each with an associated swash piston.
  • Fig. 5 is a detailed view of the tool guide
  • the wobble press shown in FIG. 1 with a wobbly driven upper die half 1 and a lower die half 2 moved axially parallel and the workpiece 10 to be deformed arranged between the two die halves 1, 2 has a press frame 12 with built-in slide guides 15 and a press slide 8 , as well as a slide drive that can be moved hydraulically by a piston 9.
  • the press frame absorbs the counterforce to the press force generated by the press slide 8 or the hydraulic piston 9.
  • the press frame 12 or the slide guide 15 is formed by an upper cross member 7, a lower cross member 14 and a number of columns 13 arranged rotationally symmetrically about the press axis A. As shown in FIG. 2, four such columns 13 can be provided, for example.
  • a box frame can also be used, in which case a prismatic bed profile is advantageous.
  • the press slide 8 carries the fixed lower tool or die part 2 and is hydraulically pressed by the piston 9 against the tumbling upper die half 1 fastened in a tool holder 4.
  • the wobbling movement of the upper die half 1 is generated by several, at least three, working pistons 5, 6, acting on a diameter of the tool holder 4 movable in a spherical cap 3, which are acted upon by a periodically sinusoidally pulsating quantity of oil, which is actuated by a hydraulic multiple pump 20 is generated with a number of pump pistons 25, 26.
  • This consists of two axial piston pumps 21 arranged in the same axial position transversely to the wobble axis,
  • the two pumps 21, 22 each of which is driven by an electric motor 31, 32 at a controllable speed.
  • the two pumps 21, 22 each work with a rotating swash plate that is dynamically balanced to avoid centrifugal forces
  • the swash plates 23, 24 cyclically move pump pistons 25 and 26, the number of which corresponds to the number of working pistons 5, 6.
  • one pump piston 25 of one pump 21 is fixedly connected to the pump piston 26 of the other pump 22 arranged in the same order by means of a hydraulic line 27 or 28, and this connecting line 27 or 28 is in turn rigid with the pressure line 29 or 30 of the associated working piston 5 or 6.
  • the flow rate of a pair of pump pistons 25, 26 increases from zero at angle 0 to a maximum at angle 180, and from there the amount of fluid is withdrawn again up to angle 360.
  • the working piston 5 connected via the lines 27, 28, 29, 30 directly to the pump pistons 25, 26 is copied this sinusoidal movement and transfers it to the wobbling tool, the stroke size depending on the ratio of the cross section of the pump piston to the cross section of the wobble piston. If the phase position of the swash plates is shifted relative to one another by appropriate control of the pump motors, the wobble stroke of the upper tool can be regulated continuously from the maximum with a 0 difference in the phase position of the two pumps to zero with a difference in the mutual phase position of 180.
  • the drive shafts 31, 32 of the swash plates are driven by separate motors, so that different forms of the wobbling unwinding of the upper tool 1 can be generated by mutually varying their speeds.
  • Fig. 6a shows an example of a star-shaped
  • Fig. 6b a spiral
  • Fig. 6c an approximately rectilinear movement in the selectable direction
  • Fig. 6d a circular wobble movement T with respect to the wobble axis A. Thanks to the small rotating masses and the electronic control on the Pump drive motors 31, 32 can program various such variants and can be carried out under load within one and the same deformation process.
  • the tool holder 4 is dome-shaped, so that the tumbling die half 1 is centered relative to the fixed die half 2.
  • the counterpressure of the lower die half 2 is not absorbed by the dome-shaped tool holder 4 or its guide 3, but by the hydraulic medium in the working cylinders 5, 6.
  • the lower die half 2 is arranged in the press chute 8, which can be moved by means of the piston 9.
  • a hydraulically actuated ejection piston 11 for the workpiece 10 is also provided in the piston 9.
  • the magnitude of these centrifugal forces Zo on the upper die half 1 is determined by the eccentricity Eo of the center of gravity S with respect to the axis A.
  • a counter mass G with a center of gravity offset by 180 is attached below the upper wobbling die half 1.
  • the eccentricity E and center of gravity S of the counterweight G are selected such that a centrifugal force Z of the same magnitude as the centrifugal force Z of the die half 1 results.
  • the product from the distance E of the center of gravity S of the counterweight G from the pivot point M is chosen to be as equal as possible to the corresponding product of the tumbling driven die half 1.
  • the compensation of the inertial forces of the wobbling tools can be achieved in that a displaceable mass is provided on the same side of the pivot point of the tool.
  • the described centrifugal force compensation allows a significant increase in the wobble frequency to values of up to approximately 2400 rpm and thus a reduction in the deformation time of a workpiece to the value customary in drop forging in mechanical presses, ie a substantial increase production output, as well as use even at elevated temperatures of around 800 to 1100, without excessive heating of the tools and without premature cooling of the workpiece.
  • the countermass G takes up as little space as possible and is easy to accommodate, it is advantageously formed from a material with a high specific weight, for example from lead, another heavy metal or from tungsten carbide.
  • the rigidity of the mutual guidance is of great importance for maintaining the central position of the two die halves, even in the case of workpieces with a strongly asymmetrical material distribution.
  • direct centering is provided according to the example according to FIG. 5.
  • a centering plate 17 is connected directly to the tool holder of the upper die half 1, which fits onto the outer diameter of the lower tool 2 practically without play and forms a rigid connection with it during the forming process.
  • the lower tool 2 is immersed in the centering plate 17 and, even with eccentric material distribution, ensures compliance with very narrow tolerances with regard to the axis offset, i.e. Even in the case of a non-rotationally symmetrical distribution of the material cross-section, the direct tool guidance ensures that the axes of the two tools match exactly.
  • the counterweight G serving to compensate the centrifugal force is in this case designed as a ring and rigidly connected to the tumbling upper tool 1 via a number of stud bolts 16. Openings or slots 18 of a suitable shape in the centering plate 17 enable the pendulum movement of the stud bolts 16.
  • the version with hydraulic drive described is particularly advantageous since there is no need for a highly loaded axial bearing which would only survive a short service life at high speeds. The smoothness is significantly improved and further increased speeds can be achieved in continuous operation.
  • the mutual movements of the two tools can easily be adapted to the technological requirements, and a circular, spiral, oscillating or pivoting movement can be effortlessly carried out as required realize, both the size of the tendency to wobble and the initiation of the various movement programs can be preprogrammed and controlled without delay.
  • the upsetting process can be started, for example, with the upper tool at rest and then brought to the desired wobble stroke without delay.
  • the warm hydraulic medium circulating between the pump and the working piston can be rinsed out and any leakage losses at the end of the pressing piston stroke can be compensated for by a suction valve.
  • the pressurized oil that heats up in the course of a press cycle can be recooled at the end of each cycle using a suitable oil cooler.

Landscapes

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

Abstract

Dans une presse oscillante comportant une première moitié de matrice (1) oscillante et une deuxième moitié de matrice (2) se déplaçant parallèlement à l'axe de la presse, le mouvement oscillant est produit par plusieurs pistons de travail (5) venant cycliquement en contact avec la moitié de matrice oscillante (1) et agissant hydrauliquement. La suppression des forces centrifuges au moyen d'un contrepoids (G) relié à la moitié de matrice oscillante (1), le guidage précis des moitiés de matrice (1, 2) au moyen d'un disque de centrage (17) et la suppression de la nécessité d'un entraînement mécanique grâce à l'utilisation d'une pompe à pistons multiples (20) et d'une commande hydraulique des pistons de travail (5) permettent de diminuer les forces de rotation, les vibrations, les frottements et les dégagements de chaleur parasites de telle manière qu'il soit possible d'atteindre des fréquences d'oscillation sensiblement plus élevées et des temps d'usinage plus courts avec des moyens moins importants, tout en conservant l'effet d'oscillation géométrique grâce à une fréquence d'oscillation élevée et de contrôler facilement et rapidement l'ampleur et la forme du mouvement oscillant, même pendant le fonctionnement, de manière qu'il soit possible de présélectionner un programme de pressage.
EP92915796A 1991-07-22 1992-07-22 Presse oscillante Expired - Lifetime EP0549771B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH2214/91 1991-07-22
CH2214/91A CH685105A5 (de) 1991-07-22 1991-07-22 Taumelpresse.
PCT/CH1992/000151 WO1993001906A1 (fr) 1991-07-22 1992-07-22 Presse oscillante

Publications (2)

Publication Number Publication Date
EP0549771A1 true EP0549771A1 (fr) 1993-07-07
EP0549771B1 EP0549771B1 (fr) 1995-05-24

Family

ID=4228530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92915796A Expired - Lifetime EP0549771B1 (fr) 1991-07-22 1992-07-22 Presse oscillante

Country Status (7)

Country Link
US (1) US5398536A (fr)
EP (1) EP0549771B1 (fr)
JP (1) JPH06505438A (fr)
CH (1) CH685105A5 (fr)
DE (1) DE59202341D1 (fr)
PL (1) PL298505A1 (fr)
WO (1) WO1993001906A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5615569A (en) * 1991-07-22 1997-04-01 Colcon Anstalt Wobble press
DE19637839C1 (de) * 1996-09-17 1997-10-30 Ford Werke Ag Verfahren zur Herstellung von Gelenkaußenteilen von Gleichlaufgelenken
DE19753949C2 (de) * 1997-12-05 1999-12-02 Doege Eckart Flexible Umformpresse mit steuerbarer nichtlinearer Stößelbewegung
JP3039863B1 (ja) * 1998-12-25 2000-05-08 不二精工株式会社 ロッキングプレス装置
DE19915758A1 (de) * 1999-04-08 2000-10-12 Hirschvogel Umformtechnik Gmbh Verfahren zum Herstellen eines Taumelstempels
DE10017462C2 (de) * 2000-04-07 2003-06-18 Fraunhofer Ges Forschung Taumelpresse
US20040180197A1 (en) * 2003-03-13 2004-09-16 Everaerts Albert I. Closure systems with self-adhering adhesives, and articles
US20070044530A1 (en) * 2005-08-24 2007-03-01 Ball Corporation Apparatus and Method for Flanging a Neck of a Container
DE102011001672B4 (de) 2011-03-30 2013-09-05 Langenstein & Schemann Gmbh Vorrichtung zum Umformen von Werkstücken
DE102011002066B4 (de) 2011-04-14 2016-02-04 Langenstein & Schemann Gmbh Taumellager für eine Vorrichtung zum Taumeln von Werkstücken
CN102284611A (zh) * 2011-06-14 2011-12-21 北京机电研究所 实现不过中心点的螺旋线运动轨迹的摆头装置
CN102284610A (zh) * 2011-06-14 2011-12-21 北京机电研究所 实现椭圆运动轨迹的摆头装置
DE102012016926A1 (de) * 2012-08-27 2014-02-27 Volkswagen Aktiengesellschaft Umformverfahren und ein nach diesem Umformverfahren hergestelltes Formteil
CN104014795B (zh) * 2014-06-18 2015-11-04 安平县德益金属复合材料有限公司 制备铁铜双金属密封螺母用摆辗模具及该螺母的制备方法

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
JPS52848A (en) * 1975-06-24 1977-01-06 Eidai Co Ltd Process for manufacturing a particle board
SU810339A1 (ru) * 1979-04-09 1981-03-07 Предприятие П/Я Р-6205 Устройство дл штамповки деталей
CH662983A5 (de) * 1984-04-21 1987-11-13 Heinrich Schmid Maschinen Und Taumelpresse.
CH666857A5 (de) * 1984-11-27 1988-08-31 Heinrich Schmid Maschinen Und Taumelpresse.
JPH01284452A (ja) * 1988-05-07 1989-11-15 Sumitomo Heavy Ind Ltd 揺動鍛造機
JPH01317650A (ja) * 1988-06-20 1989-12-22 Sumitomo Heavy Ind Ltd 揺動鍛造機
JPH02137637A (ja) * 1988-11-18 1990-05-25 Brother Ind Ltd 塑性加工方法及びその装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9301906A1 *

Also Published As

Publication number Publication date
JPH06505438A (ja) 1994-06-23
WO1993001906A1 (fr) 1993-02-04
PL298505A1 (en) 1994-01-10
CH685105A5 (de) 1995-03-31
EP0549771B1 (fr) 1995-05-24
US5398536A (en) 1995-03-21
DE59202341D1 (de) 1995-06-29

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