US3795168A - Low-impact four-bar press - Google Patents
Low-impact four-bar press Download PDFInfo
- Publication number
- US3795168A US3795168A US00321009A US3795168DA US3795168A US 3795168 A US3795168 A US 3795168A US 00321009 A US00321009 A US 00321009A US 3795168D A US3795168D A US 3795168DA US 3795168 A US3795168 A US 3795168A
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- United States
- Prior art keywords
- axis
- press
- crank
- slide
- 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.)
- Expired - Lifetime
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Classifications
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- 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
- B30B1/10—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
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- 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
- Y10T74/1816—Crank, lever, toggle, and slide
-
- 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
- Y10T83/00—Cutting
- Y10T83/869—Means to drive or to guide tool
- Y10T83/8821—With simple rectilinear reciprocating motion only
- Y10T83/8827—Means to vary force on, or speed of, tool during stroke
-
- 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
- Y10T83/00—Cutting
- Y10T83/869—Means to drive or to guide tool
- Y10T83/8821—With simple rectilinear reciprocating motion only
- Y10T83/8841—Tool driver movable relative to tool support
- Y10T83/8843—Cam or eccentric revolving about fixed axis
Definitions
- third, lazy or constraining link is pivotally connected at one end thereof to the second link and at the other end thereof to the press frame at a point between the crank axis and the path of the slide.
- the arrangement of the several links is such as to provide desirable kinematic and dynamic characteristics by developing a particular coupler curve at the pivot point between the first and second links.
- PATENTED 74 SHEET 7 0F 7 LOW IMPACT PRESS AmmIOz: mxomkw VEO SLIDER -CRANK PRESS SLIDE VELO FIG.
- the present invention relates to the press art, and more particularly, to an improved mechanically driven press.
- the invention is particularly suited for metal punching and stamping operations and will be described with reference thereto. it will be appreciated, however, that the invention is capable of broader application and could be used for many other types of press operations.
- a majority of the mechanically driven presses in service today are used for metal-cutting operations such as punching or stamping, and for shallow metal drawing operations.
- the majority of these presses are rated between and 100 tons capacity and operate at a high speed and through relatively short strokes. Presses of this character generate considerable noise.
- 10 35 ton presses operating in a press room, punching steel will generate a noise level in excess of 90 decibefs.
- Such a noise level makes conversation impossible.
- high noise levels have deleterious effects on plant workers.
- recent studies have illustrated that continuous exposure to levels of noise generated by punching and stamping operations causes permanent hearing loss to press operators. Recently, federal legislation has established maximum permissible factory noise levels.
- the noise level which is objectionable results primarily from the metal cutting or stamping operation or other metal working operation which the press performs. It is known that the noise generated by a metal cutting or punching tool is proportional to the impact velocity of the tool against the metal workpiece. if the tool strikes the workpiece at a high velocity, much more noise is generated than when the tool strikes the workpiece at a low velocity. For example, a slow speed hydraulic press generates an insignificant noise level when producing a metal working operation. Such a press, however, is capable of making only a few strokes per minute while operating at a low velocity and, accordingly, a considerable loss in production results. Such a low production rate is basically unacceptable.
- a press drive which will cause the press slide to move relatively slowly through the metal working portion of the press stroke and extremely rapidly through the advance and return portions of the stroke.
- the drive should possess a high power transmission efficiency, as well as being simple and inexpensive to build, operate and maintain.
- Such a press drive advantageously reduces the press operation noise level and greatly reduces tool impact.
- the press user is provided with a safer plant environment for his press operators, and realizes increased profits from longer tool life.
- the present invention advantageously overcomes the disadvantages of high speed presses heretofore known, including the disadvantages specifically pointed out above, and in this respect provides a high speed press having mechanical drive linkage by which low noise level press operation and increased tool life are achieved.
- the drive linkage is capable of providing the desired velocity characteristics for the press while reducing torque requirements during the working portion of the stroke, in comparison with the torque requirements of conventional mechanical slider-crank driven presses.
- the drive linkage is adapted for use with punching and stamping presses of 10 to 200 tons capacity operating with any stroke or length that might be required by a customer.
- a press including a frame, a slide reciprocable within the frame and mechanical drive means for imparting movement to the slide in a manner whereby the slide has a higher velocity during return and approach portions of the stroke and a lower velocity during the work performing portion of the stroke than high-speed mechanical presses heretofore known.
- the drive mechanism includes a first link pivotally connected at one end thereof to the press slide and pivotally connected at the other end thereof to one end of a second link having its other end pivotally interconnected with the press crank.
- a third link is pivotally connected at one end thereof to the press frame and at the other end thereof to the second link.
- the third link defines a lazy or constraining link, and the several links cooperate to impart reciprocable motion to the slide through the first link in response to rotation of the press crank 360.
- the link arrangement is such that the velocity of the slide is extremely low during the work performing portion of the press stroke and is relatively high during the return and approach portions of the stroke.
- the desired and advantageous velocities are achieved by a unique combination of the linkages which provides a unique output path which has a particular and advantageous relationship to the path followed by the slide of the press.
- the output path, or coupler curve is defined by tracing the path of travel of the pivot point between the first and second link components of the linkage assembly.
- a substantial reduction may be made in the size and strength of the crank and the gear drive therefor.
- the torque requirements of these components is reduced relative to presses heretofore known which are capable of operating at the same production rate.
- a press constructed in accordance with the present invention is economically compatible with high speed presses heretofore known and, at the same time, provides for a considerable reduction in noise level and an increase in tool life in comparison with such prior presses.
- the linkage system generates a coupler curve or path which allows the press slide and thus the tool carried thereby to move rapidly toward and away from the work during advance and return portions of the press stroke while providing for the tool to slow down considerably during the work performing portion of the stroke to achieve a low impact between the tool and workpiece.
- the press can operate at a high speed and maintain a desirable high production rate and, at the same time,
- Another object is the provision of a press of the character described having a high production rate and which generates lower noise levels than mechanical presses heretofore known having the same production rate.
- a further object is the provision of a press of the above character having a high production rate and in which the life of the press tool is longer than that of presses heretofore known having the same production rate.
- Yet another object of the present invention is the provision of a press of the above character in which the press tool is reciprocated at a high velocity during return and approach portions of the press stroke and at a low velocity during the work portion of the stroke, thus to provide for low impact forces between the press tool and workpiece.
- a further object of the present invention is the provision of a press having a drive arrangement which is especially suited for short stroke presses and creates an impact energy reduction during the work portion of the stroke of the slide of the press by providing for a slide velocity reduction during the work portion of the stroke.
- Still a further object of the invention is the provision of a mechanically driven press capable of producing relatively uniform slide forces throughout a comparatively short working stroke and under a constant crank torque.
- Yet another object is the provision of a press having a relatively low crank input torque requirement during the work portion of the press stroke.
- Yet another object is the provision of a mechanical press having a linkage system for driving the press slide, which linkage system generates a coupler curve providing for reduced slide velocity during the work portion of the press stroke and increased slide velocity during return and advance portions of the press stroke in a manner whereby the press can be operated at a high speed to provide a high production rate while maintaining a noise level considerably lower than and a tool life considerably longer than high-speed mechanical presses heretofore known.
- FIG. 1 is a plan view partially in section, illustrating a preferred embodiment of press structure in accordance with the present invention
- FIG. 2 is a front elevation, partially in section, of the press illustrated in FIG. 1, the section being taken along line 2--2 in FIG. 1;
- FIG. 3 is a side elevation, partially in section, of the press device, the section being taken along line 33 in FIG. 2;
- FIGS. 4-7 are schematic diagrams illustrating a drive linkage arrangement within the present invention at various points in a complete cycle of rotation of the crank component
- FIG. 8 is a schematic view illustrating the linkage shown in FIGS. 4'7 and illustrating the coupler curve or path generated thereby;
- FIG. 9 is a chart illustrating certain operating characteristics of the present invention.
- FIG. 10 is a chart illustrating other operating characterisitics of the present invention.
- FIG. 11 is an enlargement of a portion of the chart of FIG. 10.
- FIGS. 1-3 illustrate a low-impact 25-ton capacity press having a 3- inch stroke and a A inch working stroke.
- the press slide has a linear movement from top dead center to bottom dead center of three inches and the portion of the stroke within one quarter inch from bottom dead center is the working portion of the stroke.
- the press shown is comprised of a frame assembly A, a drive unit B, and a mechanical drive linkage assembly C.
- Frame assembly A may be of a variety of constructions and configurations, and in the preferred embodiment it is illustrated as a vertical frame comprising a base portion 10 supporting bed means 12, and an upper portion 14 housing drive unit B and drive linkage assembly C. More particularly, upper portion 14 of the frame assembly includes front wall 16 sidewalls l8 and 20 and intermediate walls 22 and 24 which are substantially parallel to front wall 16 and extend between and are welded or otherwise secured to sidewalls 18 and 20.
- the top of the press housing may be closed or open and, in the embodiment illustrated, the frame assembly is opened at the upper end thereof.
- Drive unit B is comprised of an electric motor 26, flywheel 28, main drive pinion 30 and main drive gear 32.
- Pinion 30 is keyed to a shaft 34 for rotation therewith, and shaft 34 extends through walls 22 and 24 and is supported for rotation relative thereto by suitable bearing means 36 and 38, respectively.
- Flywheel 28 is mounted on shaft 34 for rotation relative thereto and is adapted to be rotated by motor 26 through a pulley 40 attached to the motor shaft and a plurality of V-belts 42 disposed in grooves provided therefor in pulley 40 and flywheel 28. Flywheel 28 is adapted to be selectively coupled to shaft 34 to impart rotation thereto by a suitable clutch and brake mechanism 44 indicated generally by broken lines in FIG. 1.
- Pinion meshes with and drives main gear 32 in response to rotation of shaft 34.
- Main gear 32 is keyed to shaft portion 46 of a crank element indicated generally by the numeral 47 and which defines one of the components of the mechanical drive linkage assembly C.
- Shaft portion 46 extends through openings in walls 22 and 24 and is supported for rotation relative thereto by suitable bearing means 48 and respectively.
- motor 26 operates to drive flywheel 28 continuously and that brake and clutch mechanism 44 can be selectively actuated to couple flywheel 28 to shaft 34, thus to impart rotation to shaft 34 and drive pinion 30.
- Rotation of pinion 30 drives main drive gear 32 to impart rotation to shaft portion 46 of crank 47, whereby the crank is rotated about its axis 51 at a lesser speed than the rotation of pinion 30.
- crank 47 is, of course, dependent on the ratio of pinion 30 to main drive gear 32.
- the means for selectively controlling the brake and clutch mechanism 44 is not illustrated and may be comprised of any suitable means manually controlled by the press operator or automatically controlled in response to press operation.
- Crank 47 of the mechanical drive linkage assembly C includes shaft portion 46, mentioned above, and an axially aligned shaft portion 52 axially spaced from shaft portion 46 and interconnected therewith by a radially offset crank shaft portion 54 and crank arms 56.
- Each crank arm 56 has one end thereof integrally associated with shaft 46 or 52 and the other end thereof integrally associated with offset shaft portion 54.
- Shaft 52 extends through an opening in front wall 16 and is sup ported for rotation relative thereto by suitable bearing means 58.
- the outer end of shaft 52 may carry an indicator 59 which operates as a stroke indicator.
- the mechanical drive linkage further includes a connecting link 60 referred to herein as a drag link, and a pair of constraining links 61 and 62 disposed on opposite sides of connecting link 60.
- connecting link 60 is recessed to receive offset shaft portion 54 of the crank arm and is pivotally interconnected with shaft portion 54 by a cap 64 suitably attached to the link body.
- Suitable bearing means 65 are provided between shaft portion 54 and arm 60 and cap 64.
- the other end of connecting link 60 is provided with spaced apart leg portions 66 between which the upper end ofa slide arm 68 is disposed.
- Slide arm 68 is pivotally interconnected with legs 66 by means of a cylindrical pin 70 extending through the legs and through an opening in the arm defined by a recess in the arm and a cap 71 suitably attached to the arm.
- Suitable bearing means 72 are provided between pin 70 and each of the legs 66, and hearing means 74 is provided between pin 70 and arm 68 and cap 71.
- Constraining links 61 and 62 each have one end thereof pivotally interconnected with the press frame and the other end thereof'pivotally interconnected with connecting link 60. More particularly, one end-of constraining link 62 is pivotally associated with wall 22 of the press frame by means of a pin 76 projecting from wall 22, and the corresponding end of link '61 is pivotally associated with wall 16 of the press frame by apin 78 projecting from wall 16.
- 'Pins 7'6 and 78 are coaxial, and bearing means 80 and '8-1 are interposed between pins 76 and 78 and the corresponding link.
- each of the links 61 and 62 is pivotally associated with connecting link 60 by means of coaxially disposed pins 82 and 84 which project from link 60 through suitable openings in the corresponding constraining link.
- Suitable bearing means 86 and 88 are disposed between pins 82 and 84 and the corresponding constraining link.
- Slide arm 68 is associated at its lower end with a vertically reciprocable slide mechanism 90.
- Slide mechanism 90 includes a slide member 92 having guide bars 94 and 96 associated with guide way means 98 and 100 on front wall 16 and wall 22, respectively, which slide member guide bars and guide way means cooperate to guide slide member 92 during vertical movement thereof.
- the slide mechanism further includes a connecting member 102 having a cup-shaped upper end provided with socket defining components 104 and 106 which together cooperate with a ball component 108 on the lower end of arm 68 to define a ball and socket joint or pivot axis between arm 68 and slide 92.
- Connecting member 102 is rigidly fastened to slide 92 in any suitable manner.
- Ball 108 is adjustably mounted on slide arm 68 and in this respect may, for example, include a threaded shaft 110 adapted to project axially into arm 68 in threaded engagement with a threaded bore in arm 68.
- Ball 108 may be locked in an adjusted position thereof by any suitable means such as a split collar (not illustrated) and a cooperating threaded sleeve 112 which surrounds the collar and is threadedly associated with the lower end of arm 68.
- sleeve 112 cooperates with the underlying spilt collar to radially compress the collar about arm 68 to lock ball 108 against displacement relative to arm 68.
- the lower end .of the shaft portion 110 of ball 108 may be provided with tool pads 114 to facilitate adjustment of the ball by means of a wrench or the like.
- crankshaft axis 51 and the axes of constraining link pins 76 and 78 are parallel and spaced apart with the axes of pins 76 and 78 being disposed below the horizontal plane of the crank axis.
- the constraining link axis defined by the axes of pins 76 and 78 is disposed between slide path 116 and the crank axis. Rotation of the crank about its axis imparts, through the linkage mechanism, reciprocating movement to slide assembly 90 toward and away from press bed 12.
- Slide 92 of the slide assembly in use will be provided with a suitable tool such as apunch 93, for example.
- the particular four-bar linkage arrangement provides for the slide to have a low velocity during the work portion of the stroke thereof, whereby the tool 93 engages a workpiece supported on bed 12 with a low impact velocity during punching drawing or other work performed thereon.
- FIGS. 4-7 of the drawing diagramatically illustrate one embodiment of a drive linkage assembly adapted to be employed in a press having a three inch total stroke such as, for example, a press of the character illustrated in FIGS. 1-3.
- FIGS. 4-7 illustrate the linkage assembly as it passes through one complete cycle corresponding to rotation of the crank 360.
- the slide arm 120 defines a first link member having first and second end portions with the first end portion pivotally connected to a slide at a first axis A.
- the crank member 122 is rotatably mounted on the press frame at a second axis B and a second link member 124 has one end thereof pivotally connected to the crank arm at a third axis C and the other end thereof pivotally connected to the second end portion of slide arm link i20 at a fourth axis D.
- a third or constraining link member 126 has one end thereof pivotally connected to the press frame at a fifth axis E and the other end thereof pivotally connected to link 124 at a sixth axis F.
- the first axis A between line 120 and the slide is adapted to reciprocate along a path 128. It will be noted that fixed axis E between the constraining link 126 and the frame is disposed below fixed axis B between the crank arm and frame.
- FIGS. 4-7 illustrate the positions of the various link components resulting from counterclockwise rotation of crank arm 122 360 in increments of 90. More particularly, when the linkage assembly is in the position illustrated in FIG. 4, slide arm axis A is in approximately the top dead center position thereof indicated A. As the crank arm rotates 90 counterclockwise to the position thereof illustrated in FIG. 5, slide arm axis A descends or advances toward the bottom dead center position thereof and after 90 rotation of the crank is positioned approximately at point A During rotation of the crank 90 from the position illustrated in FIG. 5 to the position illustrated in FIG. 6, slide arm axis A descends to the position A corresponding substantially to the bottom dead center position thereof.
- the angle which is designated Q in FIGS. ;7 be no less than 40 and preferably be at least 45 for all positions of the crank during 360 rotation thereof. Accordingly, in FIGS. 4-7, the angle Q is the angle between links 124 and 126, and in the press structure of FIGS. l-3 the angle between link 60 and links 61 and 62. If the angle Q is less than 40 at any time during rotation of the crank, linkage slam and excess vibration may develop under high speed press operation, both of which are highly undesirable. Maintenance of a minimum angle of 45, however, will facilitate mechanism balancing and permit attainment of the desired high press stroke rates.
- Coupler curve 130 is indicative of the velocity of the slide arm axis A during a 360 rotation of the crank and, accordingly, the velocity of the slide during the complete stroke of the slide.
- the coupler curve has a major axis 132 which is the longest distance between any two points within the curve. In a linkage mechanism within the present invention, the major axis extends transversely of the slide path 128 and generally perpendicular thereto. In FIG.
- crank arm 122 is designated in 20 increments and the corresponding path of pivot axis D is indicated along the coupler curve. It will be noted with regard to these position indicators that when the crank arm is rotating from approximately the 40 to approximately the 180 position thereof, that slide arm axis A is ascending, and that when the crank arm rotates from approximately the 180 position through approximately the 260 position that the slide arm axis A pases through the top dead center position thereof and begins to descend.
- the ascent of slide arm axis A is relatively rapid as is indicated by the coupler curve, and the descent occasioned by rotation of the crank arm to about the 260 position thereof is also reasonably rapid.
- the press is a 25 ton press having a total stroke of 3 inches and a working stroke of A inch.
- the press is adapted to operate at a continuous speed of 150 strokes per minute.
- the preferred lengths for the various linkage components are as follows:
- FIGS. 9, 10 and 11 are charts illustrating comparative requirements of a four-bar low-impact press made in accordance with the present invention and a mechanically driven slider-crank press having the same stroke and operated at the same number of strokes per minute, namely a 3-inch stroke and 150 strokes per minute.
- a slider-crank press has a crank torque requirement of better than 22 ton inches while the lower impact press of the present invention has a crank torque requirement of approximately 8.25 ton inches.
- the low impact press crank torque requirement is substantially below that of the slider-crank press.
- the chart in FIG. 10 illustrates the relative slide velocities of a slider-crank press and the low impact press of the present invention over the entire 3-inch stroke.
- the low-impact press has a higher velocity during the return and approach portions of the stroke and advantageously has a much lower velocity during the work portion of the stroke.
- the velocity relationship during the work portion of the stroke is better illustrated in FIG. 11 wherein the chart is an enlargement of the circled portion of the chart of FIG. 10. It will be seen in FIG. 11 that at the beginning of the work stroke the low-impact press has a slide velocity of approximately 5.5 inch per second while the slidercrank press has a slide velocity of more than 14 inches per second.
- the slide velocity of the low-impact press is continuously lower as the two presses being compared approach the bottom dead center positions of the slides.
- the following tabulation illustrates the decreases in slide velocity, impact energy and torque requirements of the low-impact press of the present invention when compared with the slider-crank press.
- the comparison is at increments of 1/32 inch during the inch work stroke illustrated in the charts of FIGS. 9, l and 1 1 for the two presses.
- a press including: a frame, a slide member carried by said frame for reciprocable movement along a path between first and second positions, drive means for reciprocating said slide member between said first and second positions, said drive means including a first link member having first and second end portions with the first end portion pivotally connected to said slide member, a crank member rotatably mounted in said frame, a connecting link member having opposite end portions pivotally connected respectively to said crank member and the second end portion of said first link member, and'a constraining link member having a first end portion pivotally connected to said frame intermediate said path and the axis of said crank and a second end portion pivotally connected to said connecting link member intermediate said opposite end portions thereof.
- a power press comprising a frame, a slide member carried by said frame for reciprocable movement along a substantially straight slide path between first and second positions relative to said frame, and a linkage drive means for reciprocating said slide member between said first and second positions
- said linkage drive means including a first link having first and second end portions with said first end portion pivotally connected to said slide at a first axis, a crank member rotatably mounted on said frame at a second axis, a second link having one end thereof pivotally connected to said crank member at a third axis spaced from said second axis and having the other end thereof pivotally connected to said second end portion of said first link at a fourth axis, and a third link having one end thereof pivotally connected to said frame at a fifth axis and the other end thereof pivotally connected to said second link at a sixth axis, said sixth axis being spaced from said third and fourth axes and being closer to said fourth axis than said third axis, said fourth axis
- a power press comprising a frame, a slide member carried by said frame for reciprocable movement along a generally straight path between first and second positions relative to said frame, and a linkage drive means for reciprocating said slide member between said first and second positions with a predetermined velocity-time relationship
- said linkage drive means including a first link member having first and second end portions with said first end portion pivotally connected to said slide at a first axis, a crank member rotatably mounted on said frame at a second axis, a second link member pivotally connected at one end thereof to said crank member at a third axis and pivotally connected to the second end portion of said first link member at a fourth axis, and a third link member having one end thereof pivotally connected to 'said frame at a fifth axis and a second end pivotally connected to said second link member at a sixth axis, said sixth axis being spaced from said third and fourth axes and being closer to said fourth axis than said third axis, said slide member moving from said one
- a power press comprising a frame, a slide member carried by said frame for reciprocable movement along a generally straight path the length of which defines a stroke and which stroke includes a return and advance portion and a working portion, and a linkage drive means for reciprocating said slide member through said return and advance portion and said working portion
- said linkage drive means including a first link member having one end thereof pivotally connected to said slide member, a crank member rotatably mounted on said frame and having a crank arm rotatable about the axis of said crank member, a second link member having one end thereof pivotally connected to the second end of said first link member and having the other end thereof pivotally connected to said crank arm on an axis spaced from said crank axis, and a constraining link member having one end thereof pivotally connected to said frame and the other end thereof pivotally connected to said link member at a point intermediate the opposite ends of said second link member, said slide member moving through said stroke thereof in response to rotation of said crank member 360, said constraining link member operating during rotation of said crank member to constrain
- a linkage drive means for reciprocating said slide member through said working portion at a low velocity to achieve low-impact force between a tool carried by said slide member and a workpiece engaged by said tool during said work portion of said stroke, said linkage drive means including a first link member having one end thereof pivotally connected to said slide member, a crank member rotatably mounted on said frame and having a crank arm rotatably 360 about the axis of said crank member, a second link member having one end thereof pivotally connected to the other end of said first link member and having the other end thereof pivotally connected to said crank arm on an axis spaced from said crank axis,
- constraining link member having one end thereof pivotally connected to said frame and the other end thereof pivotally connected to said second link member at a point intermediate the opposite ends of said second link member, said constraining link member operating during rotation of said crank member to constrain movement of said slide member through the stroke thereof so that said slide member moves through said work portion of said stroke at a low velocity to achieve low-impact force between said tool and workpiece.
Abstract
Description
Claims (36)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US32100973A | 1973-01-04 | 1973-01-04 |
Publications (1)
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US3795168A true US3795168A (en) | 1974-03-05 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US00321009A Expired - Lifetime US3795168A (en) | 1973-01-04 | 1973-01-04 | Low-impact four-bar press |
Country Status (4)
Country | Link |
---|---|
US (1) | US3795168A (en) |
BR (1) | BR7400028D0 (en) |
ES (1) | ES422027A1 (en) |
ZA (1) | ZA739720B (en) |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
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US3919876A (en) * | 1974-11-11 | 1975-11-18 | Du Pont | Toggle press |
US4138904A (en) * | 1977-07-20 | 1979-02-13 | Verson Allsteel Press Company | Link drive mechanism for mechanical presses |
US5189922A (en) * | 1989-05-09 | 1993-03-02 | Parashikov Peter H | Force impulse generator |
FR2750625A1 (en) * | 1996-07-05 | 1998-01-09 | Jeandeaud Jean Claude | DEVICE FOR MOVING PART OF A MACHINE AND EXERCISING A FORCE AT THE END OF STROKE |
US5919015A (en) * | 1997-04-16 | 1999-07-06 | Utica Enterprises, Inc. | Mechanical drive for a blind spline broaching machine |
US20040016134A1 (en) * | 2001-12-03 | 2004-01-29 | Bednar Thomas Richard | Handle arrangement for a power tool |
USD487384S1 (en) | 2000-11-02 | 2004-03-09 | Milwaukee Electric Tool Corporation | Corded reciprocating saw |
US20040174345A1 (en) * | 2001-08-01 | 2004-09-09 | Microsoft Corporation | Correction of alignment and linearity errors in a stylus input system |
US20040231170A1 (en) * | 2000-11-02 | 2004-11-25 | Neitzell Roger Dean | Handle arrangement for a reciprocating saw |
US6826980B2 (en) | 2001-11-05 | 2004-12-07 | George Schmideg | Drive and control systems for high speed intermittent motion generations, control and applications |
US20050223569A1 (en) * | 2001-12-03 | 2005-10-13 | Milwaukee Electric Tool Corporation | Handle arrangement for a reciprocating saw |
US20060086219A1 (en) * | 1998-08-14 | 2006-04-27 | Milwaukee Electric Tool Corporation | Movable handle for a power tool |
US20100095537A1 (en) * | 2005-09-30 | 2010-04-22 | Serdynski David P | Tool and method of using same |
US8061043B2 (en) | 2006-11-15 | 2011-11-22 | Milwaukee Electric Tool Corporation | Power tool |
US9365007B2 (en) * | 2014-04-09 | 2016-06-14 | Metal Systems Technologies, LLC | Four-bar press with increased stroke rate and reduced press size |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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US2197391A (en) * | 1937-05-04 | 1940-04-16 | United Eng Foundry Co | Press and drive therefor |
US2562044A (en) * | 1949-03-12 | 1951-07-24 | Klocke William | High-speed mechanical power press |
US2600242A (en) * | 1948-08-24 | 1952-06-10 | May Otto Hermann | Toggle press |
-
1973
- 1973-01-04 US US00321009A patent/US3795168A/en not_active Expired - Lifetime
- 1973-12-28 ZA ZA739720A patent/ZA739720B/en unknown
-
1974
- 1974-01-04 BR BR28/74A patent/BR7400028D0/en unknown
- 1974-01-04 ES ES422027A patent/ES422027A1/en not_active Expired
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2197391A (en) * | 1937-05-04 | 1940-04-16 | United Eng Foundry Co | Press and drive therefor |
US2600242A (en) * | 1948-08-24 | 1952-06-10 | May Otto Hermann | Toggle press |
US2562044A (en) * | 1949-03-12 | 1951-07-24 | Klocke William | High-speed mechanical power press |
Cited By (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3919876A (en) * | 1974-11-11 | 1975-11-18 | Du Pont | Toggle press |
US4138904A (en) * | 1977-07-20 | 1979-02-13 | Verson Allsteel Press Company | Link drive mechanism for mechanical presses |
US5189922A (en) * | 1989-05-09 | 1993-03-02 | Parashikov Peter H | Force impulse generator |
FR2750625A1 (en) * | 1996-07-05 | 1998-01-09 | Jeandeaud Jean Claude | DEVICE FOR MOVING PART OF A MACHINE AND EXERCISING A FORCE AT THE END OF STROKE |
WO1998001244A1 (en) * | 1996-07-05 | 1998-01-15 | Jeandeaud Jean Claude | Device for moving part of a machine and for exerting a force at the end of its stroke |
US5919015A (en) * | 1997-04-16 | 1999-07-06 | Utica Enterprises, Inc. | Mechanical drive for a blind spline broaching machine |
US7497152B2 (en) | 1998-08-14 | 2009-03-03 | Milwaukee Electric Tool Corporation | Movable handle for a power tool |
US20060086219A1 (en) * | 1998-08-14 | 2006-04-27 | Milwaukee Electric Tool Corporation | Movable handle for a power tool |
US7308764B2 (en) | 1998-08-14 | 2007-12-18 | Milwaukee Electric Tool Corporation | Power tool with movable handle |
US7191526B2 (en) | 1998-08-14 | 2007-03-20 | Milwaukee Electric Tool Corporation | Movable handle for a power tool |
US20060174498A1 (en) * | 1998-08-14 | 2006-08-10 | Zeiler Jeffrey M | Movable handle for a power tool |
US20060117921A1 (en) * | 1998-08-14 | 2006-06-08 | Zeiler Jeffrey M | Movable handle for a power tool |
US20060117579A1 (en) * | 1998-08-14 | 2006-06-08 | Zeiler Jeffrey M | Movable handle for a power tool |
US20060117920A1 (en) * | 1998-08-14 | 2006-06-08 | Zeiler Jeffrey M | Movable handle for a power tool |
US20060107535A1 (en) * | 1998-08-14 | 2006-05-25 | Milwaukee Electric Tool Corporation | Movable handle for a power tool |
USD487384S1 (en) | 2000-11-02 | 2004-03-09 | Milwaukee Electric Tool Corporation | Corded reciprocating saw |
US20040231170A1 (en) * | 2000-11-02 | 2004-11-25 | Neitzell Roger Dean | Handle arrangement for a reciprocating saw |
US20040174345A1 (en) * | 2001-08-01 | 2004-09-09 | Microsoft Corporation | Correction of alignment and linearity errors in a stylus input system |
US6826980B2 (en) | 2001-11-05 | 2004-12-07 | George Schmideg | Drive and control systems for high speed intermittent motion generations, control and applications |
US20050223569A1 (en) * | 2001-12-03 | 2005-10-13 | Milwaukee Electric Tool Corporation | Handle arrangement for a reciprocating saw |
US20050000097A2 (en) * | 2001-12-03 | 2005-01-06 | Thomas Bednar | Handle arrangement for a power tool |
US20040187322A2 (en) * | 2001-12-03 | 2004-09-30 | Thomas Bednar | Handle arrangement for a power tool |
US20040117992A2 (en) * | 2001-12-03 | 2004-06-24 | Thomas Bednar | Handle arrangement for a power tool |
US20040016134A1 (en) * | 2001-12-03 | 2004-01-29 | Bednar Thomas Richard | Handle arrangement for a power tool |
US20100095537A1 (en) * | 2005-09-30 | 2010-04-22 | Serdynski David P | Tool and method of using same |
US8061043B2 (en) | 2006-11-15 | 2011-11-22 | Milwaukee Electric Tool Corporation | Power tool |
US8640346B2 (en) | 2006-11-15 | 2014-02-04 | Milwaukee Electric Tool Corporation | Power tool |
US9365007B2 (en) * | 2014-04-09 | 2016-06-14 | Metal Systems Technologies, LLC | Four-bar press with increased stroke rate and reduced press size |
Also Published As
Publication number | Publication date |
---|---|
ZA739720B (en) | 1974-11-27 |
BR7400028D0 (en) | 1974-08-15 |
ES422027A1 (en) | 1976-04-16 |
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Legal Events
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AS | Assignment |
Owner name: E.W. BLISS COMPANY, INC.,, DELAWARE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GULF & WESTERN INDUSTRIAL PRODUCTS COMPANY A CORP OF DE;REEL/FRAME:004204/0264 Effective date: 19831110 Owner name: E.W. BLISS COMPANY, INC., DE. A CORP OF DE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:GULF & WESTERN INDUSTRIAL PRODUCTS COMPANY A CORP OF DE;REEL/FRAME:004204/0264 Effective date: 19831110 |
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Owner name: BARCLAYS AMERICAN/BUSINESS CREDIT, INC., CONNECTIC Free format text: SECURITY INTEREST;ASSIGNOR:E.W. BLISS COMPANY;REEL/FRAME:005880/0330 Effective date: 19880915 |
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Owner name: SHAWMUT CAPITAL CORPORATION, CONNECTICUT Free format text: SALE/TRANSFER OF SECURITY INTEREST TO A NEW SECURED PARTY;ASSIGNOR:BARCLAYS BUSINESS CREDIT, INC.;REEL/FRAME:007644/0215 Effective date: 19950130 |