EP0648596A1 - Presse, en particulier presse à découper à grande vitesse - Google Patents

Presse, en particulier presse à découper à grande vitesse Download PDF

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Publication number
EP0648596A1
EP0648596A1 EP94115982A EP94115982A EP0648596A1 EP 0648596 A1 EP0648596 A1 EP 0648596A1 EP 94115982 A EP94115982 A EP 94115982A EP 94115982 A EP94115982 A EP 94115982A EP 0648596 A1 EP0648596 A1 EP 0648596A1
Authority
EP
European Patent Office
Prior art keywords
press
mass
lever
masses
frame
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
EP94115982A
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German (de)
English (en)
Other versions
EP0648596B1 (fr
Inventor
Hartmut Dexling
Gerhard Remmler
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.)
L Schuler GmbH
Original Assignee
L Schuler 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
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Application filed by L Schuler GmbH filed Critical L Schuler GmbH
Publication of EP0648596A1 publication Critical patent/EP0648596A1/fr
Application granted granted Critical
Publication of EP0648596B1 publication Critical patent/EP0648596B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0064—Counterbalancing means for movable press elements

Definitions

  • the invention relates to a press, in particular a high-speed cutting press according to the preamble of claim 1.
  • Balance weights serve as masses for balancing rotating mass forces during the operation of the press, for balancing oscillating and the like mass forces.
  • Presses of the generic type are known from DE 25 34 628 A1 and EP 0 546 265 with mass balancing mounted above the main drive shaft.
  • the second mass, formed by the respective press ram, is connected to the balancing mass by means of long, massive adjusting means. Dynamic mass force compensation of both masses with adaptation of the mass dynamics over the total stroke number range is not provided.
  • the object of the invention is to keep the vibrations occurring with increasing strokes and under the action of the cutting forces in presses of the generic type and thus increasing and thus reducing the load on the press and tool low.
  • the linearly moving masses are to be balanced with a synchronously adjustable counter mass, the plunger and counter mass being arranged closely above one another.
  • the lever system between the plunger and counter mass has a linear elastic behavior. There are favorable transmission angles between the two masses for each crank angle. This type of coupling of the masses allows the mass inertia of the counter mass to be fully used during the cutting process.
  • the frame of the press is largely kept free of mass forces. Coupling the bearing points of the compensation system for the plunger and counter mass in pairs leads to a short-circuiting of the bearing reactions on short paths.
  • Other components can be used. For example, it is possible to replace plain bearings with rolling bearings.
  • the product of stroke times mass can be at least approximately the same for both masses by choosing the leverage ratio.
  • the spring system can be used equally for both masses.
  • a further advantage here is that the adjustability of the spring constant compensates for the effects of a change in the number of strokes and that of the change in stroke.
  • the principle which works across the entire stroke rate range, relieves the drive of inertial forces.
  • the cutting energy is essentially taken from the kinetic energy of the ram and counterweights.
  • FIG. 1 The basic principle for adjusting the spring constants for use in high-speed presses according to FIG. 1 shows a linear spring 1, for example a torsion bar spring made from tempered steel or from a Cr-Ni-Mo alloy steel, which is press-fixed in the fixed point 2 and in a press-bearing-side pivot bearing 3 is stored.
  • a handlebar lever 4 is rigidly connected to the torsion bar spring 1 and can be acted upon by a tab 6 at an articulation point 5.
  • the flap 6 is articulated at the other end in a pivot point 7 by a lever 8.
  • this is to be regarded as a pivot point in the area close to the spring.
  • the lever 8 is mounted at the other end in its region close to the tappet in a pivot point 9.
  • the lever 8 is also mounted in a bearing 11 which can be moved manually or by a motor in the press frame 10 in the direction of the extent of the lever 8.
  • the bearing 11 is movable up to the area near the spring, articulation point 7, so that the lever length L2 of the lever 8 becomes zero and there are no deflection movements of the torsion bar spring 1 despite the movement of the articulation point 9 by the movement of the plunger 12.
  • Such a lever system enables the spring constants (ct) of the torsion bar spring to be adjusted even during operation of the press, for example when adjusting the stroke rate.
  • the spring constant (ct) of the torsion bar spring 1 gives the moment (Mt) acting in the end part 13 of the torsion bar spring 1.
  • the retroactive force (F) acting on the tappet 12 thus results from the moment divided by the product of Lh times i, where Lh corresponds to the length of the handlebar lever 4 connected to the torsion bar spring 1.
  • Fig. 2 shows a high-speed press with the press frame 10 and here four (times two) in fixed points 2 and pivot bearing points with 3 torsion bar springs 1.
  • the plunger 12 is only partially recognizable.
  • FIGs. 3A to 3C different possibilities for an adjustable articulation of the torsion bar spring 1 are shown.
  • a handlebar lever 4 is rigidly attached to the torsion bar spring 1 and is articulated in FIG. 3A via a tab 6 with a lever 8 is.
  • the lever 8 is articulated at the other end of the plunger 12.
  • the lever bearing point 11 is formed by a bearing which is adjustable in the longitudinal extent of the lever 8 in the press frame 10 and which has measures for pivoting the lever 8 therein.
  • Fig. 3B the handlebar lever 4 is pivotally connected directly to the lever 8. At the other end, the lever 8 is pivotally articulated on the plunger 12 via a tab 6.
  • 3C shows the possibility of the extended arrangement of the handlebar lever 4, lever 8 and bracket 6, the movement of the plunger 12 causing a deflection movement of the handlebar lever 4.
  • Lever 8 and the tab 6 slidably mounted therein remain aligned.
  • FIG. 4 could represent a section through the press shown in FIG. 2 in the area of the movement tapping on the tappet 12 for the articulation of four times two torsion bar springs 1.
  • the arrangements of the handlebar lever 4, lever 8 and bracket 6 correspond to those of FIG. 3B.
  • the adjustability of the bearings for the respective lever bearing point 11 of the levers 8 is carried out jointly via a motor-driven shaft 14, a worm wheel 16 placed on a spindle 15 provided with a right-left thread and threaded parts 17 in the displaceable backdrops 18 forming the bearing points 11.
  • the high-speed press with the press frame 10 in FIG. 5 has a plunger 19, the counter mass 20, a crank drive 21 articulated to a counter mass 20 and linear springs 2 fastened in fixed points 2 according to FIG. 4 to the balancing mass or counter mass 20 and plunger 19 second masses are guided linearly below the crank drive 21 to the press frame 10 and connected to one another via one or more link systems 22 with a pivot point 23 fixed to the frame and a link 24 mounted rotatably therein.
  • Each of the links 24 is in adjustable eccentric bearings 25 on the plunger 19 and stored in adjustable eccentric bearings 26 on the counterweights 20.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
EP94115982A 1993-10-14 1994-10-11 Presse, en particulier presse à découper à grande vitesse Expired - Lifetime EP0648596B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4335013A DE4335013A1 (de) 1993-10-14 1993-10-14 Presse, insbesondere schnellaufende Schneidpresse
DE4335013 1993-10-14

Publications (2)

Publication Number Publication Date
EP0648596A1 true EP0648596A1 (fr) 1995-04-19
EP0648596B1 EP0648596B1 (fr) 1998-08-05

Family

ID=6500127

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94115982A Expired - Lifetime EP0648596B1 (fr) 1993-10-14 1994-10-11 Presse, en particulier presse à découper à grande vitesse

Country Status (2)

Country Link
EP (1) EP0648596B1 (fr)
DE (2) DE4335013A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6055903A (en) * 1997-12-12 2000-05-02 Bruderer Ag Press, specifically punch press

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1047925A (fr) * 1950-07-25 1953-12-17 Karl Eugen Fischer Fa Dispositif d'équilibrage des machines
DE2534626A1 (de) * 1974-09-03 1976-03-11 Bruderer Ag Vorrichtung fuer den massenausgleich bei mittels kurbeltrieb angetriebenen maschinen
DE3332173A1 (de) * 1982-09-06 1984-03-08 Mabu-Pressen Maschinenfabrik Karl Burkard KG, 6370 Oberursel Exzenterpresse
US4791830A (en) * 1986-02-17 1988-12-20 Mitsubishi Jukogyo Kabushiki Kaisha Balancer of reciprocating machine
JPH02229700A (ja) * 1989-03-02 1990-09-12 Sankyo Seisakusho:Kk 機械式プレスの動的平衡装置
EP0546265A1 (fr) * 1991-12-11 1993-06-16 Bruderer Ag Presse polyçonneuse à arbre unique

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1047925A (fr) * 1950-07-25 1953-12-17 Karl Eugen Fischer Fa Dispositif d'équilibrage des machines
DE2534626A1 (de) * 1974-09-03 1976-03-11 Bruderer Ag Vorrichtung fuer den massenausgleich bei mittels kurbeltrieb angetriebenen maschinen
DE3332173A1 (de) * 1982-09-06 1984-03-08 Mabu-Pressen Maschinenfabrik Karl Burkard KG, 6370 Oberursel Exzenterpresse
US4791830A (en) * 1986-02-17 1988-12-20 Mitsubishi Jukogyo Kabushiki Kaisha Balancer of reciprocating machine
JPH02229700A (ja) * 1989-03-02 1990-09-12 Sankyo Seisakusho:Kk 機械式プレスの動的平衡装置
EP0546265A1 (fr) * 1991-12-11 1993-06-16 Bruderer Ag Presse polyçonneuse à arbre unique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 14, no. 540 (M - 1053) 29 November 1990 (1990-11-29) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6055903A (en) * 1997-12-12 2000-05-02 Bruderer Ag Press, specifically punch press

Also Published As

Publication number Publication date
DE59406604D1 (de) 1998-09-10
DE4335013A1 (de) 1995-04-20
EP0648596B1 (fr) 1998-08-05

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