EP1223027A2 - Transmission de puissance pour presse - Google Patents

Transmission de puissance pour presse Download PDF

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Publication number
EP1223027A2
EP1223027A2 EP01128165A EP01128165A EP1223027A2 EP 1223027 A2 EP1223027 A2 EP 1223027A2 EP 01128165 A EP01128165 A EP 01128165A EP 01128165 A EP01128165 A EP 01128165A EP 1223027 A2 EP1223027 A2 EP 1223027A2
Authority
EP
European Patent Office
Prior art keywords
pivotally connected
linking pieces
slide
linking
connection point
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
EP01128165A
Other languages
German (de)
English (en)
Other versions
EP1223027B1 (fr
EP1223027A3 (fr
Inventor
Akihiro Yoshida
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.)
Yamada Dobby Co Ltd
Original Assignee
Yamada Dobby Co Ltd
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 Yamada Dobby Co Ltd filed Critical Yamada Dobby Co Ltd
Publication of EP1223027A2 publication Critical patent/EP1223027A2/fr
Publication of EP1223027A3 publication Critical patent/EP1223027A3/fr
Application granted granted Critical
Publication of EP1223027B1 publication Critical patent/EP1223027B1/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
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B30B15/0035—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height using an adjustable connection between the press drive means and the press slide
    • 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
    • B30B1/10—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 toggle mechanism
    • B30B1/14—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 toggle mechanism operated by cams, eccentrics, or cranks
    • 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 present invention relates to a power transmission for a press machine provided with a slide and a balancing weight vertically spaced apart from each other.
  • a press machine provided with a slide and a balancing weight employing a toggle mechanism for a power transmission (e.g., Japanese Patent Appln. Public Disclosure No. 7-132400).
  • This press machine uses two sets of linkages to move the slide and the balancing weight as well as a position adjusting mechanism to make a stroke length of the slide variable.
  • This press machine has both linkages connected by a connector and uses long linking pieces pivotally supported on a frame, so that its structure is complicated.
  • An object of the present invention lies in simplifying the structure of the press machine having a balancing weight and capable of adjusting a stroke length of the slide.
  • the press machine comprises: a first and a second sliders disposed on a frame at a vertical interval from each other so as to move vertically; a connection for connecting the first slider with an eccentric portion of a crankshaft; a pair of first linking pieces pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with the first and the second sliders; a pair of second linking pieces pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with a slide and a balancing weight; and a position adjusting mechanism for adjusting the height position of the second slider in the vertical direction, one of the first linking pieces extending to the front end side more forward than a pivot connection point with the other to be pivotally connected with the second linking pieces.
  • Rotation of the crankshaft is transmitted to both first linking pieces by the connection to bend and extend the first linking pieces.
  • the bending and extending motion of the first linking pieces is transmitted to both second linking pieces by one of the first linking pieces to bend and extend the second linking pieces.
  • the linking piece pivotally connected with the frame can be dispensed with, which also dispenses with the pivot for the linking piece as well as the bracket, thereby simplifying the structure.
  • the pivot connection point of both second linking pieces may be a floating connection point not supported on the frame, and the slide as well as the balancing weight may be disposed on the frame immovably in the horizontal direction, and further, one of the second linking pieces may be pivotally connected with a plunger extending from the slide.
  • the position adjusting mechanism includes: a second slider disposed on the frame so as to move vertically; a disk-shaped rotor disposed on the frame so as to rotate about an axis extending in one direction and not to move in the one direction; and a rotating mechanism for rotating the rotor.
  • a second slider and the rotor has a female screw hole, while the other of the second slider and the rotor has a male screw portion screwed into the female screw hole.
  • the distance from the pivot connection point of both first linking pieces to the pivot connection point with the pivot connection point of the one of the second linking pieces and the slide can be equal to the distance from the pivot connection point of both first linking pieces to the pivot connection point with the other of the second linking pieces and the second slider.
  • the press machine further comprises: a pair of third linking pieces pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with the first and second sliders; a pair of fourth linking pieces pivotally connected with each other so as to bend and such that one and the other are respectively pivotally connected with the slide and the balancing weight.
  • Either one of the third linking pieces can be extended to the front end side more forward than the pivot connection point with the other to be pivotally connected with the fourth linking pieces.
  • the slide and the balancing weight are connected with the linkage at two positions, thereby stabilizing the movements of the slide and the balancing weight.
  • the frame preferably has a guide portion for regulating reciprocation of the balancing weight to the vertical direction. This also makes reciprocation of the balancing weight to the vertical direction, thereby stabilizing the vertical motion of the balancing weight.
  • Fig. 1 is a partially sectioned front elevation showing one embodiment of the press machine according to the present invention.
  • Fig. 2 is a partially enlarged sectional view of the power transmission and the balancer of the press machine in Fig. 1.
  • Fig. 3 is an enlarged sectional view taken along the line 3-3 in Fig. 1.
  • Fig. 4 is an enlarged sectional view taken along the line 4-4 in Fig. 1.
  • Fig. 5 is an enlarged sectional view taken along the line 5-5 in Fig. 1.
  • Fig. 6 is an enlarged sectional view taken along the line 6-6 in Fig. 1.
  • the press machine 10 comprises a lower frame 12 mounting a drag and an upper frame 14 supported on the lower frame 12.
  • a crankshaft 16 is supported on the upper frame 14 so as to rotate about a horizontally extending axis and receives rotation of a flywheel 18 shown in Fig. 3.
  • a so-called slide 20 supporting a cope is assembled into the lower end of a pair of plungers 22 extending through the lower end portion of the upper frame 14 so as to move vertically.
  • Both plungers 22 are extended upward in parallel from both end portions of the slide 20 and are reciprocated vertically by a power transmission 30 which converts rotation of the crankshaft 16 into vertical reciprocation. Thereby, the slide 20 is vertically reciprocated.
  • the power transmission 30 comprises: a connection 32 connected with the crankshaft 16; a pair of sliders 34 disposed on the upper frame 14 so as to reciprocate vertically and pivotally connected with the connection 32, i.e., so as to move pivotally; a pair of linkages 36 which are bended and extended synchronously with each other, following the reciprocation of the slider 34; a pair of linkages 38 which are made to individually correspond to the linkages 36 to be bended and extended, following the bending and extending motion of the corresponding linkages 36; a pair of sliders 40 disposed on the upper frame 14 so as to displace vertically and pivotally connected with both linkages 36; and a position adjusting mechanism 42 for adjusting the position of the sliders 40 in the vertical direction.
  • connection 32 is connected with an eccentric portion of the crankshaft 16 and is reciprocated vertically with rotation of the crankshaft 16.
  • the sliders 34, 40 are disposed in a guide portion 44 formed in the upper frame 14 so as to move vertically. Both sliders 34 are reciprocated vertically, following the reciprocation of the connection 32.
  • the sliders 40 are not reciprocated vertically by bending and extending motion of both linkages 36.
  • Each linkage 36 is provided with a pair of linking pieces 36a, 36b.
  • the linking pieces 36a, 36b of each linkage 36 are bendably connected with each other by a pivot 46 at the central portion of the linking piece 36a and the upper end portion of the linking piece 36b.
  • One linking piece 36a extends to the more downward side than the pivot connection point of the linking pieces 36a, 36b and is pivotally connected with the linkage 38 at the lower end portion.
  • One of the linking pieces 36a of both linkages 36 is pivotally connected with the connection 32 and the slider 34 at the upper end portion by a common pivot 48.
  • the other of the linking pieces 36b of both linkages 36 is pivotally connected with the slider 40 at the lower end portion by a common pivot 50.
  • the pivots 46, 48, 50 are set such that their pivotal points coincide with an axis 52 (see Fig. 2) extending vertically through the center of rotation of the crankshaft 16, but it is not always necessary to arrange the pivots 46, 48, 50 in such a manner.
  • the linking piece 36a of the linkage 36 is directly connected with the connection 32 and the slider 34, but it is possible to pivotally connect the connection 32 and the slider 34, and to connect the linking piece 36a of the linkage 36 with only one of the connection 32 and the slider 34.
  • Each linkage 38 is provided with a pair of linking pieces 38a, 38b.
  • the linking pieces 38a, 38b are bendably connected with each other at the lower end portion of the linking piece 38a and the upper end portion of the linking piece 38b by the pivot 54.
  • Both linking pieces 38a are connected at their upper end portion with a balancing weight 56 disposed on the upper frame 14 by a pivot 58 so as to move vertically.
  • Each linking piece 38b is pivotally connected at its lower end portion with the plunger 22 by a pivot 60.
  • Each linkage 38 is connected with the lower end portion of the linking piece 36a of the corresponding linkage 36 at the pivot connection point of both linking pieces 38a, 38b by the pivot 54.
  • the balancing weight 56 is disposed in a guide portion 62 formed on the upper frame 14 so as to move vertically and is positioned above the linkages 36, 38 and the crankshaft 16, thereby balancing unbalanced force attributable to vertical motion of the slide 20.
  • the position adjusting mechanism 42 is provided with: a forked bracket 70 pivotally connected with both linking pieces 36b and both sliders 40 by the pivot 50; a male screw 72 extending downward from the bracket 70; a worm wheel 74 screwed into the male screw 72; and a worm screw 76 meshed with the worm wheel 74.
  • the male screw 72 may be pivotally connected with both linking pieces 36b and both sliders 40.
  • the male screw 72 is connected with the bracket 70 so as not to rotate about the axis 52.
  • the worm wheel 74 is supported on support portions 78, 80 of the upper frame 14 so as to rotate about the axis 52 and not to move vertically.
  • the axis portion of the worm screw 76 rotatably extends through the upper frame 14 and has a sprocket 82 at an end portion (see Fig. 5).
  • the sprocket 82 is rotated by a rotating mechanism not shown such as an electric motor.
  • the sliders 34 are reciprocated in the same direction with vertical reciprocation of the connection 32, following rotation of the crankshaft 16.
  • the slider 40 is not moved unless the worm wheel 74 is rotated.
  • the pivot 48 acts as a movable side fulcrum of the linkage 36
  • the pivot 50 acts as a fixed side fulcrum of the linkage 36.
  • the linking pieces 38a and 38b are connected respectively with the balancing weight 56 and the plunger 22, the pivots 58, 60, together with the pivot 54, act as floating fulcrums not supported on the frame 14.
  • pivots 46, 48, 50, 54, 58 and 60 extend horizontally in parallel to the rotation axis of the crankshaft 16. Therefore, pivotal motion of members mutually connected by each pivot or members supported by each pivot is a motion about a horizontal axis.
  • both linkages 36 are bended and extended synchronously.
  • both linkages 38 are bended synchronously, as a result of which the slide 20 and the balancing weight 56 are synchronously reciprocated in the opposite directions.
  • the axis of the pivot 46 is at the midpoint between the axes of the pivots 48, 54 at both ends of the linking piece 36a, and the distance from the axis of the pivot 46 to the axis of the pivot 48 is the same as the distance between the axes of the linking pieces 44 at both ends of the linking piece 44. Consequently, when the slider 34 is reciprocated, the pivot 54 is horizontally reciprocated, and the pivots 58, 60 disposed in the linking pieces 38a, 38b connected by the pivot 54 are synchronously reciprocated upward and downward by the same amount in the opposite directions to each other. Therefore, the slide 20 and the balancing weight 56 are simultaneously reciprocated upward and downward by the same amount in the opposite directions to each other, thereby balancing the vertical movement of the slide 20 and the balancing weight 56.
  • Reciprocation of the slide 20 is restricted to the vertical direction because reciprocation of the plungers 22 is regulated to the vertical direction by the frame 14. Reciprocation of the balancing weight 56 is restricted to vertical reciprocation by the guide portion 62,
  • the position of the bottom dead center of the slide 20 may be adjusted by detecting it by an arbitrary detector, comparing the detected value with a predetermined reference value, and rotating the sprocket 82 so that the detected value can become the reference value.
  • the stroke length of the slide 20 can be set by rotating the sprocket 82 beforehand by a predetermined amount.
  • the present invention is not limited to the above embodiments.
  • the present invention can be variously modified without departing from its gist.
EP20010128165 2001-01-11 2001-11-27 Transmission de puissance pour presse Expired - Lifetime EP1223027B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001003266A JP2002205197A (ja) 2001-01-11 2001-01-11 プレス機の動力伝達装置
JP2001003266 2001-01-11

Publications (3)

Publication Number Publication Date
EP1223027A2 true EP1223027A2 (fr) 2002-07-17
EP1223027A3 EP1223027A3 (fr) 2003-01-15
EP1223027B1 EP1223027B1 (fr) 2007-01-10

Family

ID=18871630

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20010128165 Expired - Lifetime EP1223027B1 (fr) 2001-01-11 2001-11-27 Transmission de puissance pour presse

Country Status (3)

Country Link
EP (1) EP1223027B1 (fr)
JP (1) JP2002205197A (fr)
DE (1) DE60125904T2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1650015A1 (fr) * 2004-10-25 2006-04-26 Haulick + Roos GmbH Presse, presse de poinçonnage ou dispositif de formage
US10850466B2 (en) 2015-06-15 2020-12-01 Aida Engineering Ltd. Dynamic balance device for press machine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4313816B2 (ja) * 2006-12-27 2009-08-12 株式会社山田ドビー プレス機械
CN102555254B (zh) * 2012-02-29 2014-04-23 西安交通大学 一种高速压力机主传动机构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4630516A (en) * 1982-09-06 1986-12-23 Mabu-Pressen Maschinenfabrik Karl Burkard Kg Eccentric press
US4920782A (en) * 1987-02-03 1990-05-01 Bruderer Ag Press drive
JPH07132400A (ja) * 1993-11-11 1995-05-23 Yamada Dobby Co Ltd プレス機
US5687645A (en) * 1995-06-19 1997-11-18 Sankyo Seisakusho Co. Mechanical pressing machine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4630516A (en) * 1982-09-06 1986-12-23 Mabu-Pressen Maschinenfabrik Karl Burkard Kg Eccentric press
US4920782A (en) * 1987-02-03 1990-05-01 Bruderer Ag Press drive
JPH07132400A (ja) * 1993-11-11 1995-05-23 Yamada Dobby Co Ltd プレス機
US5687645A (en) * 1995-06-19 1997-11-18 Sankyo Seisakusho Co. Mechanical pressing machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 08, 29 September 1995 (1995-09-29) & JP 07 132400 A (YAMADA DOBBY CO LTD), 23 May 1995 (1995-05-23) *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1650015A1 (fr) * 2004-10-25 2006-04-26 Haulick + Roos GmbH Presse, presse de poinçonnage ou dispositif de formage
US10850466B2 (en) 2015-06-15 2020-12-01 Aida Engineering Ltd. Dynamic balance device for press machine

Also Published As

Publication number Publication date
DE60125904D1 (de) 2007-02-22
DE60125904T2 (de) 2007-07-05
EP1223027B1 (fr) 2007-01-10
EP1223027A3 (fr) 2003-01-15
JP2002205197A (ja) 2002-07-23

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