EP1075931B1 - Presse excentrique - Google Patents

Presse excentrique Download PDF

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Publication number
EP1075931B1
EP1075931B1 EP20000115332 EP00115332A EP1075931B1 EP 1075931 B1 EP1075931 B1 EP 1075931B1 EP 20000115332 EP20000115332 EP 20000115332 EP 00115332 A EP00115332 A EP 00115332A EP 1075931 B1 EP1075931 B1 EP 1075931B1
Authority
EP
European Patent Office
Prior art keywords
gear
eccentric
press
shaft
differential
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20000115332
Other languages
German (de)
English (en)
Other versions
EP1075931A2 (fr
EP1075931A3 (fr
Inventor
Jürgen Hennig
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.)
Andritz Technology and Asset Management GmbH
Original Assignee
Andritz Technology and Asset Management 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 Andritz Technology and Asset Management GmbH filed Critical Andritz Technology and Asset Management GmbH
Publication of EP1075931A2 publication Critical patent/EP1075931A2/fr
Publication of EP1075931A3 publication Critical patent/EP1075931A3/fr
Application granted granted Critical
Publication of EP1075931B1 publication Critical patent/EP1075931B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/266—Drive systems for the cam, eccentric or crank axis

Definitions

  • the present invention relates to an eccentric press with an eccentric shaft and a drive, which is operatively connected via a countershaft transmission with the eccentric shaft.
  • Such eccentric press is for example from the DE 41 23 495 known.
  • the power of the drive motor is stored by means of a flywheel and transmitted via a countershaft gear on the eccentric shaft.
  • This countershaft transmission can be a single or multistage spur gear.
  • the eccentric shaft then drives the actual press ram in a known manner via a crank mechanism.
  • the countershaft gears are very bulky. Due to the parallel arranged shafts of the gear stages of the countershaft transmission also results in a large installation length perpendicular to the eccentric shaft.
  • the installation space required by the eccentric press requires a corresponding design of the machine halls. A reduction in the space required by the eccentric press is desirable in view of the costs caused by the large dimensions.
  • This solution is simple, and has the advantage that it can make the countershaft transmission of the eccentric much more compact. Due to the reduced dimensions of the countershaft transmission, the overall dimensions of the eccentric press can be reduced. In particular, transversely to the longitudinal extension of the eccentric shaft can be realized in this way a significant reduction in the dimensions. By the differential gear is still ensured that the force acting evenly on the two parallel-connected gear ratios. Uneven wear or stress, as would be the case with rigidly interconnected, parallel-connected ratio stages, can thereby be effectively avoided. Thus, despite the reduced dimensions, the life of the eccentric press can be maintained.
  • the eccentric shaft may have a spur gear with which both gear ratios are engaged.
  • a meshing engagement of both translation stages with one and the same spur gear of the eccentric shaft By using two toothed interventions, the spur gear of the eccentric shaft can be made significantly smaller. This also makes the eccentric press can be made more compact. Due to the differential nevertheless a uniform load through both translation stages. The spur gear is equally loaded by both gear ratios and uneven wear is avoided.
  • the drive follows on one side laterally next to the eccentrics.
  • the torque to be transmitted causes a torsion of the eccentric shaft.
  • This twist has different degrees of rotation of the eccentric result in different degrees of rotation angle cause a tilting of the press ram.
  • the countershaft transmission can be arranged centrally between the eccentrics. Then arise at both eccentrics angle of rotation of the same size and direction. A tilting of the press ram can be effectively avoided.
  • the differential gear can be a differential gear.
  • a differential gear can be made very compact.
  • Such a bevel gear differential gear allows a particularly compact design.
  • the countershaft transmission may comprise two parallel intermediate shafts each having a driven means arranged between the two transmission stages, both of which are operationally connected to the eccentric shaft.
  • a compact two-stage countershaft can be produced.
  • spur gears smaller diameter can be used, as would be the case with a single-stage countershaft transmission.
  • the output device has dome toothings which engage with corresponding dome toothings on the eccentric shaft and on the countershaft gearbox.
  • the gear ratios can be formed by preferably single-stage helical gear. Such a transmission is particularly easy to produce.
  • flywheel acts on the differential shaft of the differential gear. Then the energy of the flywheel can be centrally introduced into the differential gear. It may also prove beneficial if the drive is via the differential shaft. Then flywheel and drive can be combined.
  • Fig. 1 shows a schematic representation of the eccentric press 1.
  • the eccentric press 1 has a housing 2, which has a gear housing 2a and a press head piece 2b, wherein an eccentric shaft 3 is rotatably mounted in bearings 4 in the gear housing 2a and in the press head 2b.
  • the eccentric shaft 3 is formed in several parts with two lateral eccentric sections 5 and 6, each having eccentric 7 and 8, on each of which connecting rods 9 and 10 are rotatably mounted.
  • the connecting rods 9 and 10 are connected in a known manner with a ram, not shown, which is guided in the press head piece 26 of the housing 2 vertically slidably movable.
  • a gear housing 2a mounted in the drive section 11, which also has a centrally approximately between the connecting rods 9 and 10 arranged spur gear 12 which is rotatably connected to the drive section 11.
  • the drive section 11 is connected via clutches 13 and 14 with the two eccentric sections 5 and 6, respectively.
  • the clutches 13 and 14 consist of coupling sleeves 15, and 16 and coupling wheels 21, 22 and 23, 24th
  • the coupling sleeves 15, 16 have internal teeth 17, 18 and 19, 20, respectively.
  • the coupling wheels 21, 22, 23, 24 have corresponding external teeth.
  • the clutch wheels 21, 23 are each rotatably connected to the associated eccentric sections 5, 6.
  • the clutch wheels 22, 24 are rotatably connected to the drive section 11.
  • two parallel intermediate shafts 25 and 25 ' are also rotatably mounted in bearings 26 and 26'.
  • the spur gear 27 and 27 ' is mounted approximately centrally on the intermediate shaft 25 and 25'.
  • two spur gears 28 and 29 rotationally fixed, but offset in the axial direction on the intermediate shafts 25, and 25' attached.
  • the spur gear 28 is rotationally fixed on the intermediate shaft 25 and the spur gear 29 on the intermediate shaft 25 '.
  • a differential gear 30 is provided.
  • the differential gear 30 has a rotatably mounted on a differential shaft 31 planet carrier 32.
  • the differential shaft 31 is rotatably mounted in bearings 33 and 34 in the housing 2.
  • ring gears 39 and 40 are rotatably mounted, which are respectively in engagement with the bevel gears 37 and 38 in a manner known in differential gear.
  • the ring gears 39 and 40 are each rotatably connected with spur gears 41 and 42, which in turn mesh in the respective associated spur gears 28 and 29.
  • the eccentric press also has a clutch 46 and a flywheel 47.
  • the flywheel 47 is rotatably supported on the differential shaft 31. When engaged, the clutch 46 rotatably connects the differential shaft 31 to the flywheel 47.
  • a brake 48 is provided on the opposite side of the clutch 46.
  • the differential shaft 31 is rotatably connected to the transmission housing 2a.
  • Clutch 46 and brake 48 are always operated alternately.
  • the eccentric press 1 has a drive, which is formed by an electric drive motor 49.
  • a rotatably mounted on the output shaft of the drive motor pulley 50 drives the flywheel 47 via a belt 51 at.
  • the drive via drive motor 49, wherein the power of the drive motor via the pulley 50 is applied to the belt 51 and the flywheel 48.
  • the clutch 46 is in the engaged state, so that the power is transmitted to the differential shaft 31.
  • the drive power is transmitted to the planet carrier 32 with the bevel gears 37 and 38.
  • the power split takes place on the two ring gears 39 and 40, and the spur gears 41 and 42, which are rotatably connected to the associated ring gears 39 and 40.
  • the spur gears 41 and 42 the drive power through the transmission stages 44 and 45, and the spur gears 28 and 29 are transmitted to the intermediate shafts 25 and 25 'and transmitted from there via the spur gears 27 and 27' to the spur gear 12.
  • the eccentrics 7 and 8 then transfer the power to the associated connecting rods 9 and 10.
  • the connecting rods 9 and 10 are then used to drive the press ram (not shown).
  • the eccentric press according to the invention it is possible to make the countershaft transmission over conventional eccentric presses extremely compact. By connecting two translation stages 44 and 45 in parallel, much smaller spur gears can be used. Also, using two parallel intermediate shafts allows a special compact design of the eccentric press. At the same time prevents due to the differential gear that uneven wear of the gear ratios 44 and 45 occurs. By the differential gear 30, the power of the drive motor is always evenly distributed on both gear ratios 44 and 45. Due to the central drive of the eccentric shaft 3, the angle of rotation for the two eccentrics 7 and 8 relative to the spur gear 12 is substantially equal, so that a misalignment of the press ram, not shown, is prevented.

Landscapes

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

Claims (10)

  1. Presse à excentrique avec au moins un arbre à excentrique (3) pourvu d'un entraînement (49) qui est en relation fonctionnelle avec l'arbre à excentrique grâce à une transmission intermédiaire (43), caractérisée en ce que la transmission intermédiaire comporte un engrenage compensateur (30) à l'aide duquel la puissance de l'entraînement peut être répartie sur deux niveaux de transmission (44, 45) de la transmission intermédiaire qui sont montés en parallèle.
  2. Presse à excentrique selon la revendication 1, caractérisée en ce que l'arbre à excentrique comporte une roue droite (12) avec laquelle les deux niveaux de transmission s'engrènent.
  3. Presse à excentrique selon la revendication 1 ou 2, caractérisée en ce que l'arbre à excentrique comporte au moins deux excentriques et la transmission intermédiaire transmet la puissance d'entraînement entre les deux excentriques à l'arbre à excentrique.
  4. Presse à excentrique selon l'une des revendications précédentes, caractérisée en ce que la roue droite de l'arbre à excentrique est disposée à peu près à mi-distance entre les excentriques.
  5. Presse à excentrique selon l'une des revendications précédentes, caractérisée en ce que l'engrenage compensateur est constitué par un différentiel.
  6. Presse à excentrique selon la revendication 5, caractérisée en ce que l'engrenage compensateur est constitué par un différentiel conique.
  7. Presse à excentrique selon l'une des revendications précédentes, caractérisée en ce que la transmission intermédiaire comporte deux arbres intermédiaires parallèles (25, 25') qui ont chacun un dispositif de sortie (27, 27') disposé entre les deux niveaux de transmission et en relation fonctionnelle avec l'arbre à excentrique.
  8. Presse à excentrique selon la revendication 7, caractérisée en ce que chaque dispositif de sortie est constitué par une roue droite (27) qui s'engrène avec la roue droite de l'arbre à excentrique.
  9. Presse à excentrique selon l'une des revendications précédentes, caractérisée en ce que les niveaux de transmission sont formés par des engrenages droits de préférence à un niveau.
  10. Presse à excentrique selon l'une des revendications précédentes, caractérisée en ce que le volant agit sur l'arbre différentiel (31) du différentiel.
EP20000115332 1999-08-13 2000-07-14 Presse excentrique Expired - Lifetime EP1075931B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19938450 1999-08-13
DE1999138450 DE19938450C2 (de) 1999-08-13 1999-08-13 Exzenterpresse

Publications (3)

Publication Number Publication Date
EP1075931A2 EP1075931A2 (fr) 2001-02-14
EP1075931A3 EP1075931A3 (fr) 2002-11-13
EP1075931B1 true EP1075931B1 (fr) 2009-08-26

Family

ID=7918320

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000115332 Expired - Lifetime EP1075931B1 (fr) 1999-08-13 2000-07-14 Presse excentrique

Country Status (3)

Country Link
EP (1) EP1075931B1 (fr)
DE (2) DE19938450C2 (fr)
ES (1) ES2329966T3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4014461B2 (ja) * 2002-07-10 2007-11-28 アイダエンジニアリング株式会社 機械プレスの駆動装置
CN108943792A (zh) * 2018-09-05 2018-12-07 山东迈特力重机有限公司 一种双联凸轮传动机构

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2881880A (en) * 1956-09-19 1959-04-14 Niagara Machine & Tool Works Power press drive mechanism
AT270324B (de) * 1967-02-15 1969-04-25 Simmering Graz Pauker Ag Zahnradgetriebe mit Leistungsverzweigung
GB1279607A (en) * 1968-10-04 1972-06-28 Modern Wheel Drive Ltd Improvements relating to gear drives
US3559498A (en) * 1969-03-26 1971-02-02 Kennedy Van Saun Co Floating pinion mounting for reduction gear units
GB1236519A (en) * 1969-10-23 1971-06-23 Teru Hayashi A power transmission gear system
DE2739596A1 (de) * 1977-08-31 1979-03-08 Mannesmann Ag Getriebe, insbesondere schiffsgetriebe
DD295589A5 (de) * 1990-07-25 1991-11-07 Umformtechnik Erfurt Gmbh,De Einrichtung zur Nutzbremsung an Exzenter- oder Kurbelpressen

Also Published As

Publication number Publication date
EP1075931A2 (fr) 2001-02-14
DE19938450C2 (de) 2001-11-08
ES2329966T3 (es) 2009-12-03
DE19938450A1 (de) 2001-03-01
DE50015729D1 (de) 2009-10-08
EP1075931A3 (fr) 2002-11-13

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