EP3738757A1 - Machine de presse et procédé de travail à la presse - Google Patents

Machine de presse et procédé de travail à la presse Download PDF

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Publication number
EP3738757A1
EP3738757A1 EP19738962.0A EP19738962A EP3738757A1 EP 3738757 A1 EP3738757 A1 EP 3738757A1 EP 19738962 A EP19738962 A EP 19738962A EP 3738757 A1 EP3738757 A1 EP 3738757A1
Authority
EP
European Patent Office
Prior art keywords
striker
ram
press machine
eccentric shaft
link
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
EP19738962.0A
Other languages
German (de)
English (en)
Other versions
EP3738757A4 (fr
EP3738757B1 (fr
Inventor
Keiji Kawamoto
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.)
Amada Co Ltd
Original Assignee
Amada 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 Amada Co Ltd filed Critical Amada Co Ltd
Publication of EP3738757A1 publication Critical patent/EP3738757A1/fr
Publication of EP3738757A4 publication Critical patent/EP3738757A4/fr
Application granted granted Critical
Publication of EP3738757B1 publication Critical patent/EP3738757B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/002—Drive of the tools
    • 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
    • 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

Definitions

  • the present invention relates to a press a machine and to a method for press working.
  • a ram moves downward from a top dead center toward a bottom dead center and then moves upward from the bottom dead center toward the top dead center.
  • press working e.g. punching
  • a sheet-shaped workpiece by an upper tool as a punch and a lower tool as a die
  • an eccentric shaft is rotated positively and negatively by using a servo motor as a drive source.
  • a ram is moved in vertical reciprocating motions.
  • the eccentric shaft is not rotated continuously in a constant rotational direction, but rotated in reciprocating rotations within a predetermined range of a rotational angle.
  • speeding-up of the vertical motions of the ram can be achieved.
  • a ram is moved vertically by rotating an eccentric shaft positively and negatively with a rotational angle range (reciprocating rotating angle: operational angle range) about 40° - 60°.
  • a stroke of the ram by rotating the eccentric shaft positively and negatively in a vicinity of the rotational angle 180° is smaller than a stroke of the ram by rotating the eccentric shaft positively and negatively in a vicinity of the rotational angle 90° (270°).
  • the rotational angle range of the ram can be made smaller in the vicinity of the rotational angle 90° (270°), and thereby high-speed working can be realized.
  • a stroke position of the ram in the vicinity of the rotational angle 90° (270°) is higher than that in the vicinity of the rotational angle 180°, so that punching may become impossible.
  • An object of the present invention is to provide a press machine and a method for press working by which press working can be done even when reciprocating rotations of an eccentric shaft are done in a vicinity of a rotational angle 90° (or 270°) of the eccentric shaft.
  • an aspect of the present invention provides a press machine in which a ram is moved vertically by rotations of an eccentric shaft, the machine comprising: a vertically movable striker provided in a striker housing provided beneath the ram, wherein the striker is capable of being fixed at a lift-up position and a lift-down position.
  • a configuration for rotating an eccentric shaft (crank shaft) by using a servo motor as a drive source (e.g. see the Patent Documents 1 and 2).
  • a servo motor as a drive source
  • reciprocating rotations of the eccentric shaft can be done with a desired range of a rotational angle.
  • a top dead center position of the eccentric shaft is denoted as a rotational angle 0°
  • a bottom dead center position thereof is denoted as 180°.
  • the eccentric shaft is rotated positively and negatively in turns (rotated reciprocatingly) with a rotational angle 90° - 180° (or 180° - 270°). Since the eccentric shaft is not rotated by 360°, high-speed press working (e.g. nibbling) can be achieved.
  • a vertically movable ram 1 and a rotational angle of an eccentric shaft (not shown in the drawings) in a press machine (not shown in the drawings) is shown in Fig. 1 schematically.
  • a stroke S for punching (nibbling) a sheet-shaped workpiece W by striking a striker 3 of the ram 1 against a punch 5 as an upper tool requires a rotational angle range ⁇ 1.
  • an equivalent stroke S in a vicinity of a rotational angle 90° (90° includable) requires a rotational angle range ⁇ 2.
  • a length of the striker 3 of the ram 1 is short by a length L in order to strike the punch 5.
  • a striking force of the striker 3 is weak in the vicinity of the rotational angle 90° (or 270°), and thereby a thickness of a workpiece W capable of being punched is small.
  • a press machine is configured to be capable of coping with the above-mentioned both cases.
  • a striker assy (configurations in and around the striker 3) in the press machine according to the present embodiment will be explained with reference to Figs. 2 to 6 .
  • configurations other than the striker assy are equivalent to whole configurations of a known press machine, and thereby their detailed explanations are omitted.
  • the configurations other than the striker assy are disclosed in the above-mentioned Patent Documents 1 and 2. Namely, the striker assy shown in Figs. 2 to 6 is attached to a bottom face 1L of the vertically movable ram 1 that is held by a ram guide, and the ram 1 is moved vertically by an eccentric shaft 1E via a connecting rod 1C. The eccentric shaft 1E is rotated reciprocatingly by a servo motor 1S.
  • Fig. 2 to Fig. 5 show the striker assy in a state where the striker 3 is lifted up with respect to a striker housing 9.
  • Fig. 3 and Fig. 4 shown is a state where an upper face 3U of the striker 3 contacts with the bottom face 1L of the ram 1 (lift-up position) .
  • Fig. 2 and Fig. 5 show a state where the striker 3 positions almost at the lift-up position.
  • Fig. 6 and Fig. 7 show a state where the striker 3 is lifted down (lift-down position).
  • an X-axis, a Y-axis and a Z-axis are defines as shown in the drawings. Further, Fig.
  • FIG. 5 shows a cross-sectional plane, with respect to an after-explained sync-motion mechanism (link mechanism) 15, including a sync-motion member (sync-motion shaft) 31, a (center) hinge pin 37A (37B) and a (second) hinge pin 47A (47B), and shows a cross-sectional plane, with respect to an after-explained operational rod (a piston rod 21 and a slide rod 25), including their center axises.
  • link mechanism sync-motion mechanism
  • a pair of brackets 6 facing to each other in a Y-axis direction is provided on the bottom face of the ram 1 that is moved vertically due to the rotations of the eccentric shaft (only one of the brackets 6 is shown in Figs. 2 and 3 ).
  • the paired brackets 6 are connected integrally with each other by a connecting member 7 extending in the Y-axis direction.
  • a box-shaped striker housing 9 is attached integrally to the connecting member 7.
  • the striker 3 is provided in the striker housing 9 so as to be movable vertically.
  • the sync-motion mechanism 15 is provided for synchronizing the vertical motion of the striker 3 with the entrance/removal motion of the pressure-receive plates 11 and 13 with respect to the gap between the upper face 3U and the bottom face 1L.
  • the striker 3 is held in a vertical pass-through hole 17 (see Fig. 4 ) formed in the striker housing 9 so as to be capable of moving vertically.
  • An actuator 19 for operating the sync-motion mechanism 15 is provided on one side of the striker housing 9 (one side in the X-axis direction).
  • the actuator 19 in the present embodiment is a fluid pressure cylinder such as an air cylinder, it may be configured by another type actuator, such as an electromagnetic solenoid, a rotary motor and a linear motor.
  • the actuator 19 includes a piston rod 21 movable reciprocatingly in the X-axis direction.
  • One end of a slide rod 25 is jointed integrally with a distal end of the piston rod 21 by a joint member 23 such as a joint screw.
  • An operational rod is configured of the piston rod 21 and the slide rod 25.
  • the slide rod 25 (operational rod) passes through an elongated hole 27 formed in the striker 3 so as to be long in a vertical direction.
  • the elongated hole 27 passes through the striker 3 in the X-axis direction. Therefore, the slide rod 25 is slidable in the X-axis direction with respect to the striker 3, and the striker 3 is slidable in a Z-axis direction with respect to the slide rod 25.
  • the other end of the slide rod 25 is slidably supported by a penetrating hole (first guide hole) 29 formed in the X-axis direction in the striker housing 9 (see Fig. 4 ).
  • first guide hole 29 formed in the X-axis direction in the striker housing 9 (see Fig. 4 ).
  • the striker 3 is vertically movable with respect to the striker housing 9 regardless of the existence of the slide rod 25.
  • a sync-motion member 31 that penetrates the striker housing 9 in the Y-axis direction is attached integrally to a distal end of the slide rod 25.
  • a through hole 33 orthogonally crossing the penetrating hole 29 is formed in the striker housing 9 so as to be long in the X-axis direction.
  • the through hole 33 passes through the striker housing 9 in the Y-axis direction.
  • the sync-motion member 31 is movable in the X-direction within the through hole 33. Both ends of the sync-motion member 31 extending in the Y-axis direction pivotally coupled with one ends of the sync-motion links 35A and 35B, respectively.
  • a link mechanism including the sync-motion link 35A of the sync-motion mechanism 15 is provided symmetrically (with respect to an XY plane including a center axis of the slide rod 25) on the opposite side of the striker housing 9 in the Y-axis direction, and the opposite-side link mechanism includes the sync-motion link 35B.
  • Component elements of the paired link mechanisms of the sync-motion mechanism 15 are differentiated from each other by being labeled with suffixes A and B, and only one of the link mechanisms (with the suffix A) will be explained hereinafter. But, the other of the link mechanisms (with the suffix B) also configured symmetrically and operates symmetrically.
  • a (center) hinge pin 37A penetrating the striker housing 9 in the Y-axis direction toward the vertical pass-through hole 17 is disposed on one side of the striker 3 in the Y-axis direction. Threads are formed on a distal end of the hinge pin 37A, and screw-fitted with the striker 3 in the vertical pass-through hole 17.
  • the hinge pin 37A passes through a through hole (second guide hole) 39A formed on a side face of the striker housing 9 so as to be long in the vertical direction, and is movable vertically in the through hole 39A.
  • the hinge pin 37A pivotally supports the center of a link (center link) 41A so as to allow a rotational motion thereof.
  • One end of a (first) intermediate link 43A is pivotally coupled with one end of the link 41A via a (first) hinge pin 45A.
  • the other end of the intermediate link 43A is pivotally coupled with the other end of the sync-motion link 35A via a (second) hinge pin 47A.
  • the other end of the link 41A is pivotally coupled with a (first) connecting bracket 51A via a (third) hinge pin 49A.
  • the connecting bracket 51A is attached integrally to a bottom face of an end of the (first) pressure-receive plate 11.
  • a (scissors) link 53A is disposed on an inner side of the link 41A in the Y-axis direction.
  • a base end of the link 53A is pivotally supported by the hinge pin 37A.
  • a distal end of the link 53A is pivotally coupled with a (second) connecting bracket 57A via a (fourth) hinge pin 55A.
  • the connecting bracket 57A is attached integrally to the (second) pressure-receive plate 13.
  • a (second) intermediate link 59A whose both ends are pivotally coupled respectively with the hinge pins 47A and 55A is provided between the hinge pin 47A and the hinge pin 55A.
  • An axis distance between the hinge pin 45A and the hinge pin 47A are equal to an axis distance between the hinge pin 47A and the hinge pin 55A (see Fig. 3 ).
  • the sync-motion member 31 When the piston rod 21 of the actuator 19 is protruded by being moved leftward as shown Fig. 7 from the lift-up state of the striker 3 shown in Fig. 3 and Fig. 4 , the sync-motion member 31 is also moved leftward in an integrated manner.
  • the sync-motion link 35A When the sync-motion member 31 is moved leftward, the sync-motion link 35A is moved leftward from the position shown in Fig. 3 to the position shown in Fig. 6 .
  • the link 41A is rotated clockwise about the hinge pin 37A via the intermediate link 43A.
  • the pressure-receive plate 11 is move rightward.
  • displacement of the pressure-receive plate 11 in the vertical direction is restricted by the upper face of the striker housing 9 and the bottom face 1L of the ram 1.
  • the hinge pin 37A moves downward by being guided by the through hole 39A extending in the vertical direction concurrently while the pressure-receive plate 11 is moved rightward. Since the hinge pin 37A is fixed with the striker 3, the striker 3 also moves downward ( Fig 4 to Fig. 7 ). When the hinge pin 37A moves downward, the pressure-receive plate 13 is moved leftward via the link 53A and the intermediate link 59A.
  • the paired pressure-receive plates 11 and 13 move so that they are made closer to each other from both sides in the X-axis direction to be positioned above the striker 3 that is moved downward by the sync-motion mechanism 15, and thereby contact with the upper face 3U of the striker 3. That is, the paired pressure-receive plates 11 and 13 can enter a gap between the bottom face 1L of the ram 1 and the upper face 3U of the striker 3 from the opposite sides, respectively.
  • a pair of sloped surfaces 3S is formed at an upper portion of the striker 3 in order to assist the movements of the pressure-receive plates 11 and 13 and the lift-down of the striker 3 even if the paired pressure-receive plates 11 and 13 contact with the striker 3 while they moves. In this manner, the pressure-receive plates 11 and 13 can be set quickly above the striker 3.
  • the paired pressure-receive plates 11 and 13 are positioned between the upper face 3U of the striker 3 and the bottom face 1L of the ram 1 to keep the striker 3 in the lift-down state.
  • the hinge pin 37A moves upward by being guided by the through hole 39A extending in the vertical direction. Since the hinge pin 37A is fixed with the striker 3, the striker 3 also moves upward ( Fig. 7 to Fig. 4 ).
  • the paired pressure-receive plates 11 and 13 are also moved by the sync-motion mechanism 15 so as to be made distanced from each other. Namely, the paired pressure-receive plates 11 and 13 can be removed from the gap between the bottom face 1L of the ram 1 and the upper face 3U of the striker 3 toward the opposite both sides, respectively. As the result, they are made returned into the initial state shown in Fig. 3 and Fig. 4 .
  • the link 41A and the link 53A configure a sort of cross-link, and rotate in opposite directions to each other about the hinge pin 37A. Due to their rotation, the paired pressure-receive plates 11 and 13 move in synchronization with each other so as to be made closer to each other or to be made distanced from each other.
  • the sync-motion link 35A and the intermediate links 43A and 59A and so on (including the sync-motion member 31 and the hinge pins) configure a transferring link for transferring strokes (reciprocating motions) of the operational rod (the piston rod 21 and the slide rod 25) to the cross-link (the link 41A and 53A and the hinge pin 37A).
  • the striker 3 of the ram 1 can be set at the two positions, the lift-up position and the lift-down position, with respect to the striker housing 9.
  • the height difference between the lift-up position and the lift-down position can be brought by the height of the pressure-receive plates 11 and 13, and this difference corresponds to the length L in Fig. 1 .
  • the length L may be determined according to specification of the press machine or the punching force of a workpiece as a work object. Therefore, it is possible to cope with press working in which an eccentric shaft is rotated positively and negatively with a rotational angle 90° - 180° (or 180° - 270°). In addition, it is possible to cope with press working in which an eccentric shaft is rotated positively and negatively with a rotational angle range set in a vicinity of a rotational angle 90° (or 270°) (90° (or 270°) includable).
  • a hold mechanism for holding the striker 3 at the lift-up position and the lift-down position is configured by the paired pressure-receive plates 11 and 13, the sync-motion mechanism 15 for synchronizing the pressure-receive plates 11 and 13 with the striker 3, the actuator 19 and the operational rod (the piston rod 21 and the slide rod 25).
  • the sync-motion mechanism 15 is configured by the pair of the link mechanisms in the present embodiment, only a single link mechanism may be provided as long as its operation doesn't cause a failure.
  • high-speed press working can be done by rotating the eccentric shaft positively and negatively with a rotational angle range set in a vicinity of a rotational angle 90° (270°).
  • the thick sheet material can be pressed (punched) by rotating the eccentric shaft positively and negatively with a rotational angle range set in a vicinity of a rotational angle 180° (180° includable).
  • the present invention may be defines as follows.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Punching Or Piercing (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Control Of Presses (AREA)
EP19738962.0A 2018-01-11 2019-01-10 Machine de presse et procédé de travail à la presse Active EP3738757B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018002471A JP6550481B2 (ja) 2018-01-11 2018-01-11 プレス機械及びプレス加工方法
PCT/JP2019/000450 WO2019139064A1 (fr) 2018-01-11 2019-01-10 Machine de presse et procédé de travail à la presse

Publications (3)

Publication Number Publication Date
EP3738757A1 true EP3738757A1 (fr) 2020-11-18
EP3738757A4 EP3738757A4 (fr) 2021-03-24
EP3738757B1 EP3738757B1 (fr) 2022-05-18

Family

ID=67219765

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19738962.0A Active EP3738757B1 (fr) 2018-01-11 2019-01-10 Machine de presse et procédé de travail à la presse

Country Status (3)

Country Link
EP (1) EP3738757B1 (fr)
JP (1) JP6550481B2 (fr)
WO (1) WO2019139064A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115318481B (zh) * 2022-10-12 2023-02-03 常州铭赛机器人科技股份有限公司 一种高精度压电喷雾阀的控制方法

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU977194A1 (ru) * 1980-12-22 1982-11-30 Воронежское Производственное Объединение По Выпуску Кузнечно-Прессового Оборудования Им.М.И.Калинина Пресс безмуфтового включени
SU1425093A1 (ru) * 1986-08-19 1988-09-23 Я. Н. Яковишин, С. Н. Яковишин, П. П. Яковишина и Н. Н. Яковишин Вертикальна кузнечно-прессова машина
US5131303A (en) * 1991-08-12 1992-07-21 Wilson Tool International Punch assembly
JP2000024729A (ja) * 1998-07-10 2000-01-25 Amada Co Ltd 打ち抜き装置
JP2002045995A (ja) * 2000-08-07 2002-02-12 Amada Eng Center Co Ltd プレス加工装置
JP2003340599A (ja) * 2002-05-27 2003-12-02 Tamagawa Seiki Co Ltd プレス機械の上死点停止制御方法及び装置
JP3802513B2 (ja) 2002-06-18 2006-07-26 株式会社アマダ プレス機械の連続加工システム
JP4360793B2 (ja) * 2002-10-01 2009-11-11 株式会社アマダ パンチプレスによる打抜き加工方法及びパンチプレス
JP2007185667A (ja) 2006-01-11 2007-07-26 Amada Co Ltd パンチプレス機および同機を用いた高速ニブリング加工方法
DE102007012638A1 (de) * 2007-03-16 2008-09-18 Heidelberger Druckmaschinen Ag Bogenstanz- und -prägemaschine
JP2018002471A (ja) 2016-07-08 2018-01-11 秀子 江尻 テープカッター

Also Published As

Publication number Publication date
JP2019118952A (ja) 2019-07-22
WO2019139064A1 (fr) 2019-07-18
JP6550481B2 (ja) 2019-07-24
EP3738757A4 (fr) 2021-03-24
EP3738757B1 (fr) 2022-05-18

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