US3785282A - Mechanical press with toggle lever crank drive - Google Patents

Mechanical press with toggle lever crank drive Download PDF

Info

Publication number
US3785282A
US3785282A US00150982A US15097171A US3785282A US 3785282 A US3785282 A US 3785282A US 00150982 A US00150982 A US 00150982A US 15097171 A US15097171 A US 15097171A US 3785282 A US3785282 A US 3785282A
Authority
US
United States
Prior art keywords
arm
slide
press
eccentric
main shaft
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
US00150982A
Inventor
I Kamelander
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.)
ZDARSKE STROJIRNY A SLEVARNY
Original Assignee
ZDARSKE STROJIRNY A SLEVARNY
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 ZDARSKE STROJIRNY A SLEVARNY filed Critical ZDARSKE STROJIRNY A SLEVARNY
Application granted granted Critical
Publication of US3785282A publication Critical patent/US3785282A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • B30B1/268—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 using a toggle connection between driveshaft and press ram
    • 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
    • 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
    • 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
    • B30B1/263—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 work stroke adjustment means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating

Definitions

  • ABSTRACT 30 Foreign Application priority Data Drive mechanism for the slide of a mechanical press
  • the object of the invention is a press of the type in which a motor drives through gears, clutch and flywheel a rotating main shaft which imparts through a toggle lever connecting rod a reciprocating motion to the slide, the press having main drive means which imparts the motion to the top toggle lever substantially in the direction of the slide motion while auxiliary drive means is provided for simultaneously imparting a motion perpendicular to the direction of the slide motion.
  • the combination of these two actions results in a reciprocating rectilinear motion of the slide having as its main feature a sharp slow-down on its down-stroke, whereby the speed of impact of the tool on the material is reduced; if required, such speed may be even reduced to zero.
  • the present invention eliminates the drawbacks of the prior art and is characterized in that the main drive means is adjustable for varying the motion of the top toggle lever of the connecting rod, and the toggle joint is controlled by a linkage system including adjustable elements from an auxiliary eccentric.
  • FIG. 1 is a diagrammatic elevational view ofthe drive mechanism and the related elements of the machine
  • FIG. 2 is a view in vertical section along the line II--II in FIG. 1;
  • FIG. 3 is a view similar to FIG. 2 but showing a multiple slide embodiment of the invention
  • FIG. 4 illustrates examples of courses or cycles of slide strokes at reduced impact speeds
  • FIG. illustrates diagrammatically the situation when the mechanism is adjusted according to the curve a in FIG. 4 and the slide position is at s, (minimum speed at the moment of impact);
  • FIG. 6 illustrates diagrammatically the situation when the mechanism is adjusted according to the curve 0 in FIG. 4 (the slide being at top dead center).
  • an axle 2 on which there is arranged for rotation a crank wheel 3 with a solid main eccentric 4 and a solid auxiliary eccentric 16.
  • an adjustable eccentric 5 having on its one face adjacent to the crank wheel 3 teeth 6 engaging with corre sponding teeth on an eccentric sleeve 7, the two sets of teeth being pressed into mesh by a nut 8 on a thread 9 formed on the hub of the crank wheel 3.
  • the eccentric 4 may thus be adjusted angularly with respect to crank wheel 3 and thus with respect to eccentric 5 by loosening nut 8, turning parts 3 and 4 relative to each other, and then tightening nut 8.
  • An auxiliary eccentric is fixedly mounted on the hub of the crank wheel 3.
  • the two-arm lever 20 is swingable on a pin 22 fixed in the machine frame 1, and its second or lower arm is connected by a pin 23 to a link 24, the: length of which can be varied by adjustment of a threaded rod 25.
  • the link 24 is connected with the joint pin ll 1 of the toggle lever connecting rod.
  • the radially highest zone of the auxiliary eccentric is preferably angularly displaced in relation to the radially highest zone of the main eccentric by 2040 in the direction opposite to the direction of rotation of the crank wheel 3.
  • the crank wheel 3 is driven in a way known per se from a motor (not shown) through. a flywheel, a clutch and brake, and possibly an intermediate shaft to a pinion 27 meshing with a ring gear on the crank wheel 3.
  • FIG. 3 shows an example of embodiment of a triplicate mechanism according to the present invention.
  • the numerals 14a, 14b denote additional slides, the driving mechanism of each slide being the same as that above-described in the case of a simple slide.
  • the linkage system 16-25 straightens the toggle levers 10, 12 of the connecting rod and the eccentrics 4, 5 arrive at approximately their top dead center position.
  • the working portion of the slide motion now takes place in the following 90-1 10 of rotation of the crank wheel.
  • the toggle levers 10, 12 of the connecting rod form an elbow and move the pin 11 to the right in FIG. 1 out of the axis passing through the pins 2, 13, so that a reduced speed of the downwardly moving slide is maintained for a certain time.
  • the length of the working portion of the slide stroke is varied.
  • the adjustment of the slide block 19 and thus the lengthening or shortening of the one, upper arm of the two-arm lever 20 provides for variation of the total length of slide stroke.
  • the threaded rod adjusts the length of the link 24, and thereby adjusts the position of the pin 11 in relation to the slide motion as produced by eccentrics 4, 5, i.e. the value of the impact speed of the slide at the beginning of the stroke is adjusted.
  • FIG. 4 there are shown examples of courses or cycles of slide strokes for various relative adjustments of the length of the working portion of the slide stroke and the length of total slide stroke.
  • the curve denotes the course for maximum total stroke H, and maximum working portion of stroke p,.
  • the curve C shows the maximum total slide H and nearly minimum working portion of the stroke s
  • the curve d shows a nearly minimum total length of the stroke H and maximum working portion of the stroke 5
  • the curve e demonstrates minimum total length of the stroke H and nearly minimum working portion of the stroke s
  • a mechanical press having a reciprocable slide, a rotatable main shaft, means for driving the main shaft, a main drive means for reciprocating the slide toward and away from the main shaft, said main drive means comprising an eccentric mounted on the main shaft to be driven thereby, a toggle having links connected by a pivotal toggle joint drivingly connected between the eccentric and the slide auxiliary drive means imparting motion to the pivotal toggle joint between the toggle links in a direction substantially perpendicular to the motion of the slide, and means for adjusting said main drive means by varying the motion of the upper toggle link.
  • a press as claimed in claim 1, wherein said means for controlling the pivotal toggle joint comprises a linkage system including adjustable elements.
  • a press as claimed in claim 2, wherein said linkage system comprises a two-arm lever having a first arm adjustable in length, a cam driven by the main shaft, and a cam follower cooperating with the cam for driving said first arm.
  • a press as claimed in claim 3, wherein said first arm of the two-arm lever comprises a slide block and an adjusting screw.
  • a press as claimed in claim 3, wherein said linkage system comprises a link with length adjustment pivotally connected between the second arm of the two-arm lever and the pivotal toggle joint.
  • said linkage system comprises a two-arm lever having a first arm adjustable in length by a slide block and an adjusting screw, and a link with length adjustment by a threaded rod, said link being pivotally connected between the second arm of the two-arm lever and the pivotal toggle joint.
  • main drive means includes a combined eccentric comprising a second eccentric upon which said first-recited eccentric is mounted and with respect to which it is angularly

Abstract

Drive mechanism for the slide of a mechanical press, especially a toggle lever crank press. In the slide driving mechanism means are provided comprising two eccentrics adjustable relative to one another for continuously changing the slide speed during its stroke, especially its slowing down close before the tool comes into contact with the stock to be worked.

Description

United States Patent Kamelander Jan. 15, 1974 MECHANICAL PRESS WITH TOGGLE [56] References Cited LEVER CRANK DRIVE UNITED STATES PATENTS [75] Inventor; Ivan Kamelander, Brno, 2,280,587 4/1942 Klocke 74/38 Czechoslovakia 2,781,015 2/1957 Dehn et a]. 72/451 3,174,347 3/1965 Hecht 100/257 X [73] Assrgnee: Zdarske stro irny a slevarny, 3,426,635 2/1969 Nicklasson 74/38 X narodni podnik, Zdar nad Sazavou, Czechoslovakia Primary ExaminerHarvey C. Hornsby 22 d: 8 1971 Assistant ExaminerC. K. Moore 1 16 June Attorney--Arthur O. Klein [.21] Appl. No.: 150,982
[57] ABSTRACT 30 Foreign Application priority Data Drive mechanism for the slide of a mechanical press,
June [970 Czechoslovakia 704061 especially a toggle lever crank press. In the slide driving mechanism means are provided comprising two [521 U.S. c1 100/257 72/451 74/25 eccentrics adjustable relative amber [51] Int. Cl B30!) 5/00 tinuously changing the slide speed during its Stroke 58 Field of Search 160/257- 72/451- especially its 510mg befme comes into contact with the stock to be worked.
8 Claims, 6 Drawing Figures PATENTEDJMI 1 5 m4 SHEET 10F 3 INVENTOR VAN KAME LANDER 7642M (QIL U law I ATTORNEY memtnm 15 m4 SHEET 2 BF 3 @QQQ NOIISOd 30ns"H INVENTOR IVAN KAM LANDER ATTOR NEY MECHANICAL PRESS WITH TOGGLE LEVER CRANK DRIVE The present invention relates to crank driven toggle lever mechanical presses having reduced impact speed of the slide and thus of the tool on the workpiece.
The object of the invention is a press of the type in which a motor drives through gears, clutch and flywheel a rotating main shaft which imparts through a toggle lever connecting rod a reciprocating motion to the slide, the press having main drive means which imparts the motion to the top toggle lever substantially in the direction of the slide motion while auxiliary drive means is provided for simultaneously imparting a motion perpendicular to the direction of the slide motion. The combination of these two actions results in a reciprocating rectilinear motion of the slide having as its main feature a sharp slow-down on its down-stroke, whereby the speed of impact of the tool on the material is reduced; if required, such speed may be even reduced to zero.
The technological and economic advantages of this reduced impact speed are well-known, both from practice and in the literature.
There exists various mechanisms which realize the above-mentioned reduced impact speed of the tool on the material by the said combination of action on the toggle lever connecting rod, but they have a common drawback in that they do not have mechanical adjustable elements in the main drive means, nor do they have them in the auxiliary drive means. Such prior mechanisms are therefore designed for only a definite motion of the slide, i.e. they are suitable only for a certain operation, e.g. working upon material in a definite thickness range.
However, it is desirable in order to obtain good utilization of the machine, to provide the possibility of adjustment of other parameters of the slide motion:
a. impact and working speed b. length of working portion of stroke c. total stroke length d. lower dead point of slide.
The present invention eliminates the drawbacks of the prior art and is characterized in that the main drive means is adjustable for varying the motion of the top toggle lever of the connecting rod, and the toggle joint is controlled by a linkage system including adjustable elements from an auxiliary eccentric.
An example of embodiment of the present invention is shown in the accompanying drawings, in which:
FIG. 1 is a diagrammatic elevational view ofthe drive mechanism and the related elements of the machine;
FIG. 2 is a view in vertical section along the line II--II in FIG. 1;
FIG. 3 is a view similar to FIG. 2 but showing a multiple slide embodiment of the invention;
FIG. 4 illustrates examples of courses or cycles of slide strokes at reduced impact speeds;
FIG. illustrates diagrammatically the situation when the mechanism is adjusted according to the curve a in FIG. 4 and the slide position is at s, (minimum speed at the moment of impact); and
FIG. 6 illustrates diagrammatically the situation when the mechanism is adjusted according to the curve 0 in FIG. 4 (the slide being at top dead center).-
In the frame 1 of the press is fixedly mounted an axle 2 on which there is arranged for rotation a crank wheel 3 with a solid main eccentric 4 and a solid auxiliary eccentric 16. On the main eccentric 4 there is mounted an adjustable eccentric 5 having on its one face adjacent to the crank wheel 3 teeth 6 engaging with corre sponding teeth on an eccentric sleeve 7, the two sets of teeth being pressed into mesh by a nut 8 on a thread 9 formed on the hub of the crank wheel 3. The eccentric 4 may thus be adjusted angularly with respect to crank wheel 3 and thus with respect to eccentric 5 by loosening nut 8, turning parts 3 and 4 relative to each other, and then tightening nut 8.
On the adjustable eccentric 5 there hangs the upper toggle lever 10 of the connecting rod, lever 10 being connected by a joint pin 11 to the bottom toggle lever 12, which latter is attached by a pin 13 to a slide 14 which is movable within guides 15 on the frame 1.
An auxiliary eccentric is fixedly mounted on the hub of the crank wheel 3. On the auxiliary eccentric 16 there hangs an auxiliary pitman 17, pitman 17 being connected by a pin 18 to a slide block 19 movable within the slot of a first or upper arm of a two-arm or bell crank lever 20 by means of adjusting screw2l. The two-arm lever 20 is swingable on a pin 22 fixed in the machine frame 1, and its second or lower arm is connected by a pin 23 to a link 24, the: length of which can be varied by adjustment of a threaded rod 25. The link 24 is connected with the joint pin ll 1 of the toggle lever connecting rod. The radially highest zone of the auxiliary eccentric is preferably angularly displaced in relation to the radially highest zone of the main eccentric by 2040 in the direction opposite to the direction of rotation of the crank wheel 3.
The crank wheel 3 is driven in a way known per se from a motor (not shown) through. a flywheel, a clutch and brake, and possibly an intermediate shaft to a pinion 27 meshing with a ring gear on the crank wheel 3.
FIG. 3 shows an example of embodiment of a triplicate mechanism according to the present invention. The numerals 14a, 14b denote additional slides, the driving mechanism of each slide being the same as that above-described in the case of a simple slide.
The above-described mechanism functions as follows:
In the position shown in FIG. 1, the slide 14 is in its bottom dead position, the toggle lever connecting rod 10, 12 is straight, the eccentric 4 is at lower dead center, and the high point of the eccentric 16 is offset 20-40 with respect to eccentric 4 in the direction opposite the direction of rotation of the crank wheel.
When the crank wheel starts to rotate in the direction of the arrow in FIG. 1, the eccentrics 4, 5 lift the toggle lever 10 and the slide travels upwards. At the same time the eccentric 16 moves the pitman 17 to the right (FIG. 1) whereby through the two-arm lever 20 and the link 24 the pin 11 of the toggle lever is moved to the left in FIG. 1, out of the axis connecting the pins 2 and 13, thus forming an elbow" in the connecting rod and accelerating the upward movement of the slide. After rotation of the crank wheel 3, i.e. eccentrics 4, 5, by about the slide is in the top dead center position and starts to move downwards.
The linkage system 16-25 straightens the toggle levers 10, 12 of the connecting rod and the eccentrics 4, 5 arrive at approximately their top dead center position. The working portion of the slide motion now takes place in the following 90-1 10 of rotation of the crank wheel. At this time, the toggle levers 10, 12 of the connecting rod form an elbow and move the pin 11 to the right in FIG. 1 out of the axis passing through the pins 2, 13, so that a reduced speed of the downwardly moving slide is maintained for a certain time.
In the continuation of the downward movement of the slide, its speed increases again and has a course known for the standard crank mechanism, during which time the linkage system 16-25 returns the pin 11 back to the axis passing through the pins 2 and 13, i.e. straightens the elbow formed by toggle levers 10, 12 until they assume again the position in FIG. 1.
The various adjustments of the individual elements are:
By angularly adjusting the eccentric with respect to the crank wheel 3, the length of the working portion of the slide stroke is varied. The adjustment of the slide block 19 and thus the lengthening or shortening of the one, upper arm of the two-arm lever 20 provides for variation of the total length of slide stroke. The threaded rod adjusts the length of the link 24, and thereby adjusts the position of the pin 11 in relation to the slide motion as produced by eccentrics 4, 5, i.e. the value of the impact speed of the slide at the beginning of the stroke is adjusted.
By combining these adjustments, many variants of total slide stroke, length of working portion of stroke and speed of slide may be obtained to suit the operation in hand, i.e. one drive mechanism provides suitable conditions for operations requiring different parameters of the slide motion.
ln FIG. 4 there are shown examples of courses or cycles of slide strokes for various relative adjustments of the length of the working portion of the slide stroke and the length of total slide stroke. The curve denotes the course for maximum total stroke H, and maximum working portion of stroke p,. The curve C shows the maximum total slide H and nearly minimum working portion of the stroke s The curve d shows a nearly minimum total length of the stroke H and maximum working portion of the stroke 5 The curve e demonstrates minimum total length of the stroke H and nearly minimum working portion of the stroke s By shortening the link 24 it is possible to obtain a small reduction of both impact and working speed as shown by the curvefin FIG. 4 with the maximum total length of stroke H Although the invention is illustrated and described with reference to a plurality of preferred embodiments thereof, it is to be expressly understood that it is in no way limited to the disclosure of such a plurality of embodiments, but is capable of numerous modifications within the scope of the appended claims.
What is claimed is:
1. A mechanical press having a reciprocable slide, a rotatable main shaft, means for driving the main shaft, a main drive means for reciprocating the slide toward and away from the main shaft, said main drive means comprising an eccentric mounted on the main shaft to be driven thereby, a toggle having links connected by a pivotal toggle joint drivingly connected between the eccentric and the slide auxiliary drive means imparting motion to the pivotal toggle joint between the toggle links in a direction substantially perpendicular to the motion of the slide, and means for adjusting said main drive means by varying the motion of the upper toggle link.
2. A press as claimed in claim 1, wherein said means for controlling the pivotal toggle joint comprises a linkage system including adjustable elements.
3. A press as claimed in claim 2, wherein said linkage system comprises a two-arm lever having a first arm adjustable in length, a cam driven by the main shaft, and a cam follower cooperating with the cam for driving said first arm.
4. A press as claimed in claim 3, wherein said first arm of the two-arm lever comprises a slide block and an adjusting screw.
5. A press as claimed in claim 3, wherein said linkage system comprises a link with length adjustment pivotally connected between the second arm of the two-arm lever and the pivotal toggle joint.
6. A press as claimed in claim 2, wherein said linkage system comprises a two-arm lever having a first arm adjustable in length by a slide block and an adjusting screw, and a link with length adjustment by a threaded rod, said link being pivotally connected between the second arm of the two-arm lever and the pivotal toggle joint.
7. A press as claimed in claim 6, wherein said linkage system is driven by a cam driven from the main shaft and a pitman extending between said last-recited cam and the first arm of the two-arm lever.
8. A press as claimed in claim 1, wherein the main drive means includes a combined eccentric comprising a second eccentric upon which said first-recited eccentric is mounted and with respect to which it is angularly

Claims (8)

1. A mechanical press having a reciprocable slide, a rotatable main shaft, means for driving the main shaft, a main drive means for reciprocating the slide toward and away from the main shaft, said main drive means comprising an eccentric mounted on the main shaft to be driven thereby, a toggle having links connected by a pivotal toggle joint drivingly connected between the eccentric and the slide auxiliary drive means imparting motion to the pivotal toggle joint between the toggle links in a direction substantially perpendicular to the motion of the slide, and means for adjusting said main drive means by varying the motion of the upper toggle link.
2. A press as claimed in claim 1, wherein said means for controlling the pivotal toggle joint comprises a linkage system including adjustable elements.
3. A press as claimed in claim 2, wherein said linkage system comprises a two-arm lever having a first arm adjustable in length, a cam driven by the main shaft, and a cam follower cooperating with the cam for driving said first arm.
4. A press as claimed in claim 3, wherein said first arm of the two-arm lever comprises a slide block and an adjusting screw.
5. A press as claimed in claim 3, wherein said linkage system comprises a link with length adjustment pivotally connected between the second arm of the two-arm lever and the pivotal toggle joint.
6. A press as claimed in claim 2, wherein saId linkage system comprises a two-arm lever having a first arm adjustable in length by a slide block and an adjusting screw, and a link with length adjustment by a threaded rod, said link being pivotally connected between the second arm of the two-arm lever and the pivotal toggle joint.
7. A press as claimed in claim 6, wherein said linkage system is driven by a cam driven from the main shaft and a pitman extending between said last-recited cam and the first arm of the two-arm lever.
8. A press as claimed in claim 1, wherein the main drive means includes a combined eccentric comprising a second eccentric upon which said first-recited eccentric is mounted and with respect to which it is angularly adjustable.
US00150982A 1970-06-10 1971-06-08 Mechanical press with toggle lever crank drive Expired - Lifetime US3785282A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CS4061A CS148900B1 (en) 1970-06-10 1970-06-10

Publications (1)

Publication Number Publication Date
US3785282A true US3785282A (en) 1974-01-15

Family

ID=5382492

Family Applications (1)

Application Number Title Priority Date Filing Date
US00150982A Expired - Lifetime US3785282A (en) 1970-06-10 1971-06-08 Mechanical press with toggle lever crank drive

Country Status (6)

Country Link
US (1) US3785282A (en)
CH (1) CH537274A (en)
CS (1) CS148900B1 (en)
DE (1) DE2127289C3 (en)
FR (1) FR2097838A5 (en)
GB (1) GB1319391A (en)

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3929000A (en) * 1973-11-15 1975-12-30 Bruno Kralowetz High-speed short-stroke forging press
US4008525A (en) * 1976-04-19 1977-02-22 Ball Brothers Service Corporation Apparatus for processing ware
US4079632A (en) * 1975-08-14 1978-03-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Mechanism for driving the nipper shaft of a comber
US4156387A (en) * 1974-09-03 1979-05-29 Bruderer Ag Apparatus for mass compensation at a machine driven by a crank drive
US4785732A (en) * 1986-06-06 1988-11-22 L. Schuler Gmbh Push rod stroke adjustment device for a press
US4791830A (en) * 1986-02-17 1988-12-20 Mitsubishi Jukogyo Kabushiki Kaisha Balancer of reciprocating machine
US4858835A (en) * 1987-11-26 1989-08-22 Axis S.P.A. Equipment for the actuation of needles for the realization of electric motors field windings
WO1990009762A1 (en) * 1989-02-22 1990-09-07 Physical Sciences Inc. Acoustic impact delivery catheter with end cap
US4967586A (en) * 1988-07-23 1990-11-06 Gebr. Hilgeland Gmbh And Co. Upsetting press for upsetting or swaging wire segments of predetermined lengths into balls or the like
US5246447A (en) * 1989-02-22 1993-09-21 Physical Sciences, Inc. Impact lithotripsy
DE4308475A1 (en) * 1993-03-17 1994-09-22 Pressen Engineering Essen Gmbh Drive for the plunger of a cutting press or metal-forming machine tool
EP0718091A1 (en) * 1994-12-23 1996-06-26 SCHULER PRESSEN GmbH & Co. Coin press
US6012321A (en) * 1995-04-12 2000-01-11 Murata Kikai Kabushiki Kaisha Driving device for a pressing machine
EP0972630A2 (en) * 1998-07-17 2000-01-19 Kabushiki Kaisha Yamada Dobby Press machine
US6164147A (en) * 1999-02-05 2000-12-26 The Minster Machine Company Adjustable link motion press
US6311612B1 (en) 1999-07-12 2001-11-06 The Minster Machine Company Link adjustment member
US20020104364A1 (en) * 2000-12-29 2002-08-08 Juergen Fahrenbach Press having a slide
US6564668B1 (en) * 1998-11-13 2003-05-20 Colombo Fillippetti S.P.A. Small sized driver mechanism with double spherical cam, for mechanical automatons
US6708609B1 (en) 1999-07-29 2004-03-23 Schuler Pressen Gmbh & Co. Kg Press product line
US20040168502A1 (en) * 2003-03-01 2004-09-02 Wolfgang Niemann Toggle press
US20110083568A1 (en) * 2008-06-18 2011-04-14 Fahrenbach Juergen Direct drive for a press
US20130247698A1 (en) * 2012-03-23 2013-09-26 Schuler Pressen Gmbh Press drive with several modes of operating a press and method for operating a press drive
WO2014063841A1 (en) * 2012-10-25 2014-05-01 Modus One Gmbh Drive apparatus
CN104647789A (en) * 2015-02-26 2015-05-27 江苏扬力集团有限公司 Transmission structure of multi-connecting-rod mechanical press
EP2998107A1 (en) * 2014-08-15 2016-03-23 Georg Maschinentechnik GmbH & Co. KG Press drive for a forming device
US20160347017A1 (en) * 2015-05-29 2016-12-01 Andritz Ag Device for compacting stacked sheets or pulp slabs
US20160347016A1 (en) * 2015-05-29 2016-12-01 Andritz Ag Device for compacting pulp flocks
CN106827610A (en) * 2017-04-17 2017-06-13 扬力集团股份有限公司 A kind of big stroke transmission mechanism of multi-link lever press
US20210372507A1 (en) * 2017-12-08 2021-12-02 Bes Isletme Arge Ve Muhendislik Cozumleri Sanayi Ticaret Limited Sirketi Variable displacement mechanism output movement of which can be lowered to zero stroke
IT202100013343A1 (en) * 2021-05-24 2022-11-24 Jofa S R L ELECTRIC PRESS FOR THE CHARACTERIZATION OF VEHICLE SHOCK ABSORBERS

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4107973A (en) * 1977-08-04 1978-08-22 Gulf & Western Manufacturing Company Press drive mechanism
DE4130004A1 (en) * 1991-09-10 1993-03-11 Erfurt Umformtechnik Gmbh DRIVE FOR THE PUSHER OF MECHANICAL PRESSES
DE19846951A1 (en) * 1998-10-12 2000-04-20 Strip S D O O Podjetje Za Svet Press with elbow lever drive has triangular guide rod connected to crank drive at one end and fitted with drive arm and support arm spaced from each other at other end and adjustable in length between elbow joint and crank drive
DE19935655B4 (en) * 1999-07-29 2005-09-08 Schuler Pressen Gmbh & Co. Kg Press series with attachment gear
DE102012102527B4 (en) 2012-03-23 2014-10-09 Schuler Pressen Gmbh Press drive with several working areas

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2280587A (en) * 1941-03-20 1942-04-21 Bliss E W Co Press
US2781015A (en) * 1952-06-11 1957-02-12 Cleveland Crane Eng Draw press
US3174347A (en) * 1961-04-20 1965-03-23 May Pressenbau Ltd Toggle lever system
US3426635A (en) * 1965-08-27 1969-02-11 Pullmax Ab Arrangement in sheet metal working machines,particularly nibbling machines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2280587A (en) * 1941-03-20 1942-04-21 Bliss E W Co Press
US2781015A (en) * 1952-06-11 1957-02-12 Cleveland Crane Eng Draw press
US3174347A (en) * 1961-04-20 1965-03-23 May Pressenbau Ltd Toggle lever system
US3426635A (en) * 1965-08-27 1969-02-11 Pullmax Ab Arrangement in sheet metal working machines,particularly nibbling machines

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3929000A (en) * 1973-11-15 1975-12-30 Bruno Kralowetz High-speed short-stroke forging press
US4156387A (en) * 1974-09-03 1979-05-29 Bruderer Ag Apparatus for mass compensation at a machine driven by a crank drive
US4079632A (en) * 1975-08-14 1978-03-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Mechanism for driving the nipper shaft of a comber
US4008525A (en) * 1976-04-19 1977-02-22 Ball Brothers Service Corporation Apparatus for processing ware
US4791830A (en) * 1986-02-17 1988-12-20 Mitsubishi Jukogyo Kabushiki Kaisha Balancer of reciprocating machine
US4785732A (en) * 1986-06-06 1988-11-22 L. Schuler Gmbh Push rod stroke adjustment device for a press
US4858835A (en) * 1987-11-26 1989-08-22 Axis S.P.A. Equipment for the actuation of needles for the realization of electric motors field windings
US4967586A (en) * 1988-07-23 1990-11-06 Gebr. Hilgeland Gmbh And Co. Upsetting press for upsetting or swaging wire segments of predetermined lengths into balls or the like
US5246447A (en) * 1989-02-22 1993-09-21 Physical Sciences, Inc. Impact lithotripsy
WO1990009762A1 (en) * 1989-02-22 1990-09-07 Physical Sciences Inc. Acoustic impact delivery catheter with end cap
DE4308475A1 (en) * 1993-03-17 1994-09-22 Pressen Engineering Essen Gmbh Drive for the plunger of a cutting press or metal-forming machine tool
EP0718091A1 (en) * 1994-12-23 1996-06-26 SCHULER PRESSEN GmbH & Co. Coin press
US6012321A (en) * 1995-04-12 2000-01-11 Murata Kikai Kabushiki Kaisha Driving device for a pressing machine
EP0972630A2 (en) * 1998-07-17 2000-01-19 Kabushiki Kaisha Yamada Dobby Press machine
EP0972630A3 (en) * 1998-07-17 2000-04-26 Kabushiki Kaisha Yamada Dobby Press machine
US6148720A (en) * 1998-07-17 2000-11-21 Kabushiki Kaisha Yamada Dobby Press machine
US6564668B1 (en) * 1998-11-13 2003-05-20 Colombo Fillippetti S.P.A. Small sized driver mechanism with double spherical cam, for mechanical automatons
US6164147A (en) * 1999-02-05 2000-12-26 The Minster Machine Company Adjustable link motion press
GB2346339B (en) * 1999-02-05 2003-08-27 Minster Machine Co Adjustable drive mechanism
US6606941B2 (en) 1999-07-12 2003-08-19 Minster Machine Company, The Method of altering the drive mechanism of a mechanical press
US6311612B1 (en) 1999-07-12 2001-11-06 The Minster Machine Company Link adjustment member
US6708609B1 (en) 1999-07-29 2004-03-23 Schuler Pressen Gmbh & Co. Kg Press product line
US6860198B2 (en) * 2000-12-29 2005-03-01 Schuler Pressen Gmbh & Co. Press having a slide
US20020104364A1 (en) * 2000-12-29 2002-08-08 Juergen Fahrenbach Press having a slide
US20040168502A1 (en) * 2003-03-01 2004-09-02 Wolfgang Niemann Toggle press
US7011019B2 (en) * 2003-03-01 2006-03-14 Reinhold Schulte Toggle press
US20110083568A1 (en) * 2008-06-18 2011-04-14 Fahrenbach Juergen Direct drive for a press
US8776682B2 (en) * 2008-06-18 2014-07-15 Schuler Pressen Gmbh & Co. Kg Direct drive for a press
US9770879B2 (en) * 2012-03-23 2017-09-26 Schuler Pressen Gmbh Press drive with several modes of operating a press and method for operating a press drive
US20130247698A1 (en) * 2012-03-23 2013-09-26 Schuler Pressen Gmbh Press drive with several modes of operating a press and method for operating a press drive
WO2014063841A1 (en) * 2012-10-25 2014-05-01 Modus One Gmbh Drive apparatus
EP2998107A1 (en) * 2014-08-15 2016-03-23 Georg Maschinentechnik GmbH & Co. KG Press drive for a forming device
CN104647789A (en) * 2015-02-26 2015-05-27 江苏扬力集团有限公司 Transmission structure of multi-connecting-rod mechanical press
US20160347016A1 (en) * 2015-05-29 2016-12-01 Andritz Ag Device for compacting pulp flocks
CN106182870A (en) * 2015-05-29 2016-12-07 安德里特斯公开股份有限公司 For the device by the heap lamination compacting of slurry
CN106182871A (en) * 2015-05-29 2016-12-07 安德里特斯公开股份有限公司 For the device by slurry wadding compacting
US20160347017A1 (en) * 2015-05-29 2016-12-01 Andritz Ag Device for compacting stacked sheets or pulp slabs
CN106827610A (en) * 2017-04-17 2017-06-13 扬力集团股份有限公司 A kind of big stroke transmission mechanism of multi-link lever press
US20210372507A1 (en) * 2017-12-08 2021-12-02 Bes Isletme Arge Ve Muhendislik Cozumleri Sanayi Ticaret Limited Sirketi Variable displacement mechanism output movement of which can be lowered to zero stroke
IT202100013343A1 (en) * 2021-05-24 2022-11-24 Jofa S R L ELECTRIC PRESS FOR THE CHARACTERIZATION OF VEHICLE SHOCK ABSORBERS

Also Published As

Publication number Publication date
CH537274A (en) 1973-05-31
DE2127289A1 (en) 1971-12-16
CS148900B1 (en) 1973-05-24
GB1319391A (en) 1973-06-06
FR2097838A5 (en) 1972-03-03
DE2127289B2 (en) 1974-04-25
DE2127289C3 (en) 1974-11-21

Similar Documents

Publication Publication Date Title
US3785282A (en) Mechanical press with toggle lever crank drive
US4032018A (en) Workpiece transfer mechanism
US3162232A (en) Multiple depth control for power press brakes
US6012370A (en) Toggle type punch driving system
US3855839A (en) Drive linkage for double action press
CN206551517U (en) A kind of two point double action press device
US2693955A (en) Control unit for stock feed
US3695090A (en) Mechanical double-action press of link mechanism type
US2268242A (en) Rapid punch press
US3570300A (en) Apparatus for ejecting articles in cold forming presses or the like
US3099180A (en) Feed roll release means for power presses
US2783996A (en) Feed roll drive and brake mechanism therefor for presses of the punch and blanking type
US3822603A (en) Slide driving linkage for metal forming press
US1561770A (en) Draw press for sheet metal
US1322533A (en) candee
EP0635320B1 (en) Pressure pad for single-acting presses in particular for mechanical and transfer presses
US3714848A (en) Cutting apparatus for tissue-like material
US2659906A (en) Heading and like machine
US2790541A (en) High speed nailmaker feed mechanism
SU564977A1 (en) Hydraulic press control system
US2887145A (en) Offsetting press
US2522747A (en) Press
DE2742041A1 (en) Workpiece ejector for metal forming press - has two to one step up drive to allow more time for workpiece removal
US451224A (en) Drawing or stamping press
KR20170127825A (en) Driving apparatus of double knuckle press