US3745865A - Cyclic variable speed drive - Google Patents

Cyclic variable speed drive Download PDF

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Publication number
US3745865A
US3745865A US3745865DA US3745865A US 3745865 A US3745865 A US 3745865A US 3745865D A US3745865D A US 3745865DA US 3745865 A US3745865 A US 3745865A
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United States
Prior art keywords
arm
rotor
axis
variable speed
roller
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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English (en)
Inventor
R Johnson
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Harris Corp
Original Assignee
Harris Intertype Corp
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Publication date
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Publication of US3745865A publication Critical patent/US3745865A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D36/00—Control arrangements specially adapted for machines for shearing or similar cutting, or for sawing, stock which the latter is travelling otherwise than in the direction of the cut
    • B23D36/0008—Control arrangements specially adapted for machines for shearing or similar cutting, or for sawing, stock which the latter is travelling otherwise than in the direction of the cut for machines with only one cutting, sawing, or shearing devices
    • B23D36/0033—Control arrangements specially adapted for machines for shearing or similar cutting, or for sawing, stock which the latter is travelling otherwise than in the direction of the cut for machines with only one cutting, sawing, or shearing devices for obtaining pieces of a predetermined length
    • B23D36/0041—Control arrangements specially adapted for machines for shearing or similar cutting, or for sawing, stock which the latter is travelling otherwise than in the direction of the cut for machines with only one cutting, sawing, or shearing devices for obtaining pieces of a predetermined length the tool moving continuously
    • 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
    • Y10T74/1836—Rotary to rotary
    • Y10T74/18408—Cranks, slidable connections
    • 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
    • Y10T83/465—Cutting motion of tool has component in direction of moving work
    • Y10T83/474—With work feed speed regulator
    • Y10T83/4743—With means to vary cyclically speed of work
    • 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
    • Y10T83/465—Cutting motion of tool has component in direction of moving work
    • Y10T83/4766—Orbital motion of cutting blade
    • Y10T83/4775—Tool speed varied within each orbital cycle

Definitions

  • This invention relates to a cyclic variable speed drive and more particularly to a cyclic variable speed drive of the type employing slider crank mechanisms.
  • the device disclosed can be used on machines where it is desired to have a relatively simple means for midifying machine output speed when the input speed is constant.
  • a particular application for this variable speed drive is in industries where it is necessary to treat moving webs of material periodically.
  • a particular need is present in the paper and paperboard industry where webs of papers and paperboard are moved at relatively high speeds past treatment points.
  • the treatment points may comprise cutting, marking, stamping, punching or the like.
  • the speed of the moving web may be changed to suit conditions. Accordingly, it is necessary to have a suitable means for modifying the speed of the web treating device so that it can compensate to change the period for treatment of the web and cause the web contact tool to engage the web while moving at the same speed as the web.
  • my invention relates to a variable speed drive for converting a constant input motion of constant speed into an output motion of variable cyclic speed.
  • the input motion is utilized to drive a slider crank mechanism which may have its center of rotation varied in order to vary the period for treating the web.
  • the slider crank mechanism is connected by way of a second slider crank mechanism to a driven output shaft.
  • the output shaft has a speed which varies cyclically in accordance with the positioning of the first slider crank mechanism and the constant input speed.
  • the output shaft is connected to a tool which is used to treat the moving web.
  • a specific use for this invention is in a cut off mechanism of a paperboard corrugator wherein webs of paperboard moving at speeds up to about 800 fpm or more must be cut into sheets having legnths from about 22 inches up to about 240 inches.
  • the sheet length to be cut is changed, it is desirable to effect the change without slowing down the web since that can cause excessive waste. Even a loss of l feet of paperboard at every changeover results in an ultimate yearly loss of thousands of dollars.
  • one feature of this invention is the ability to quickly change over from one length of cut to another so as to reduce the waste occasioned by the changeover.
  • FIG. 1 is a schematic respective view showing the various components of the variable speed drive.
  • FIG. 2 is a sectional view taken through a housing supporting the variable speed drive.
  • FIG. 3 is a section view taken along the line 33 in FIG. 1.
  • FIG. 4 is a graph of sheet length versus offset.
  • variable speed drive 10 in a cutoff machine comprises an input drive shaft 12 which may run at constant speed. Thus, it may be driven from any suitable power source such as a synchronous motor 13 or the like which also drives the web to be cut.
  • the input motion of the drive shaft 12 is ultimately transmitted to output driven shaft 14 which is substantially parallel to the input drive shaft 12 but spaced therefrom.
  • the spur gear functions as the input driving member of the variable speed mechanism. To this extent, it is a relatively large gear having some of the characteristics of a flywheel promoting thereby smoother running of the machine.
  • a boss 20 is mounted on one of the faces of the spur gear 18 in spaced relation from its axis of rotation. The boss 20 supports a coupling member such as a stud 22 which rotatably supports a roller 24. Roller 24 drives rotating arm 26.
  • the rotating arm 26 includes an elongated portion 28 with an elongated radially directed slot 29 therein. Slot 29 has a length suitable for the sheet length range of the cutoff.
  • the rotating arm 26 also includes an outwardly directed porti0n 30. Portion 30 does not extend out as far as the elongated portion 28. However, it is preferred that portions 28 and 30 be diametrically opposed with respect to each other.
  • roller 24 will have a relatively large diameter compared with roller 36.
  • Portion. 28 of rotating arm 26 is tapered to reduce dynamic loads and inertial forces in the mechanism.
  • the reinforcement rib 27 has less mass at the outer free end of portion 28 which is where the bending moments and stresses are lowest in arm 26.
  • the rotating arm 26 is supported intermediate its ends for rotation by integral shaft 32 which may be mounted in a suitable journal block 34.
  • Outwardly extending portion 30 of arm 26 supports a coupling member such as stud 35 which has a roller 36 at its free end.
  • Roller 36 is received in an elongated radially disposed slot 38 in output crank rotor 40.
  • the output crank rotor 40 is fixed to aforementioned output shaft 14.
  • Portion 30 of arm 26 has a pocket 33 located between stud 35 and shaft 32. As illustrated in FIG. 3, pocket 33 is of substantial length and depth as compared with the length and thickness of portion 30. Pocket 33 decreases the twist in portion 30 of arm 26. Thus, pocket 33, by tending to concentrate stresses on the side edges of roller 36, shifts the shear center of portion 30 of arm 26 to a position outside the shear plane of arm 26 to a position adjacent the plane of rotor 40. This reduction in twist of arm 26 alleviates contact stresses between roller 36 and slot 38.
  • Roller 36 is preferably smaller than roller 24. When roller 24 is 5 inches in diameter, roller 36 may be 4 inches in diameter. Roller 36 is preferably crowned at its periphery to localize contact stresses in the central region of slot 38 in rotor 40 and the central plane of said roller 36. A suitable crown radius for roller 36 when it has a 4 inch diameter would be approximately 30 inches.
  • roller 24 and rotating arm 26 may be characterized as a first crank and slider mechanism.
  • Roller 36 and crank rotor 40 may be characterized as a second crank and slider mechanism.
  • the output shaft 14 drives a first output spur gear 42 which meshes with a second output spur gear 44.
  • Each of the gears has shafts 46 and 48 extending therefrom on which are supported their respective tools.
  • the tools 50 are shown to be cutting blades. However, it is apparent that they could be printing dies, punches or the like.
  • the input motion from drive shaft 12 is transmitted by way of pinion 16 and spur gear 18 to the first slider crank mechanism. That mechanism is connected to the second slider crank mechanism which in turn drives output shaft 14.
  • the velocity of the output shaft 14 with respect to its angular position depends upon the relative position of the longitudinal axis of shaft 32 with respect to the axis of output shaft 14.
  • the relative position of these two shafts is controlled by providing means for moving the aforementioned journal block 34.
  • suitable rails 49 or other constraining means are provided.
  • the journal block 34 may be provided with overhanging members 52 so that it is constrained for movement along the rails.
  • a threaded shaft 54 is utilized for effecting displacement of the journal block and shaft 32 relative to the axis of output shaft 14.
  • variable speed mechanism is shown supported in a housing 60.
  • the housing may be mounted adjacent to a running web of material so that the tools 50 will be disposed transversely of it.
  • the principal supporting structure for the variable speed drive comprises a bearing collar 62 which is supported on the front wall 64 of the housing.
  • Main drive spur gear 18 is supported by suitable bearings 65 on the outer wall of the bearing collar 62.
  • Output shaft 14 is supported concentrically within the bearing collar 62 while crank rotor 40 is fixed thereto by an elongated sleeve 66.
  • crank rotor 40 and the main drive spur gear 18 are all mounted for rotation about a common axis.
  • Rotating arm 26 is fixed to journal block 34 by shaft 32.
  • the journal block is mounted for movement along rails 49 within the housing.
  • Threaded shaft 54 is rotated by way of a suitable motor connected to gear 68 disposed outside the housing.
  • gear 68 moves shaft 32 and arm 26 relative to the aforementioned axis of rotor 40.
  • the motor connected to gear 68 should be a reversible motor and may be a stepper pulse motor 67 whereby a predetermined number of pulses will accurately move journal block 34 a predetermined distance.
  • Spur gear 42 is supported on output shaft 14 which is supported near the spur gear by suitable bearings 69.
  • Spur gear 42 drives spur gear 44 which is supported by bearings 70.
  • Each of the spur gears 42 and 44 supports driven shafts 46 and 48 on which the tool for treating the web of moving material can be mounted. At their opposite ends, each of the shafts 46 and 48 support spur gears 72 and 74 which are supported by hearings in a housing 76. Thus, there is positive drive between the upper and lower shafts 46 and 48 and the tools supported thereby.
  • the subject drive is comprised of a minimum number of moving parts each of which is relatively lightweight and of simple construction.
  • the cyclic drive is in its zero position and the velocities of shafts 46 and 48 are constant.
  • the zero position corresponds to a sheet length of 34 inches.
  • Block 34 will engage limit stops which establish the allowable limits for the position of rotating arm 26.
  • the distance of travel for shaft 32 from its position for processing minimum sheet lengths of 22 inches to its position for processing maximum sheet lengths of 240 inches is relatively short, such as 7% inches.
  • FIG. 4 there is illustrated a graph of sheet length in inches versus offset in inches.
  • the word offset refers to the distance between the axes of shafts l4 and 32.
  • the graph of FIG. 4 is based on the formula:
  • e is the offset in inches
  • R is the distance in inches between the longitudinal axes of shaft 32 and roller 36
  • SL designates the sheet length in inches which corresponds to the period of the tool connected to shaft 14.
  • the numeral 34 represents the circumference of the tool path in inches.
  • 34 in said formula would represent the length of the sheet in I inches which is cut when the mechanism is in its zero position of uniform motion and the velocities of shafts 46 and 48 are constant. The circumference of the path of the tool 50 is then equal to the length of the sheet cutoff.
  • the distance between the longitudinal axes of shaft 32 and roller 36 equals th distance between the longitudinal axes of shaft 14 and roller 24.
  • the graph illustrated in FIG. 4 is based on R being 10 inches.
  • variable speed drive may be used for stamping, cutting, punching, or printing of moving webs.
  • the above-described mechanism causes the tools 50 to cyclically increase and decrease speed so that the tools are at web speed when the tools engage thee web.
  • a cyclic variable speed drive comprising a first axis of rotation, a drive input member supported for rotation about said first axis of rotation, first means defining another axis of rotation, an arm, said am being mounted on said first means for rotation about said other axis, said arm including a first portion having an elongated radial slot and a second portion directed in substantially the opposite direction from said slot, driven output means, said driven output means axis being coaxial with said first axis of rotation, a rotor, said rotor being connected to said driven output means to drive it about said first axis of rotation, said rotor including an elongated radially directed slot, first and second elongated coupling members disposed in substantially parallel relation to said first axis of rotation, said first coupling member having one end fixed to said drive input member and having a roller on its other end rotatably received in said first arm slot for rotating said arm, said second elongated coupling member having one end fixed to said arm second portion and having its other end rot
  • variable speed drive in accordance with claim 1 wherein said rotor and arm are tapered so as to have less mass at one free end thereof, and said second coupling member having a crown roller disposed in the slot on said rotor.
  • a variable speed drive in accordance with claim 1 including first and second cutting blades mounted on shafts, gear means coupling said shafts, the shaft for said first blade being connected to said driven output means.
  • a cyclic variable speed drive comprising an output shaft rotatable about its longitudinal axis to drive a tool, a rotor fixed to said output shaft so that rotation of said rotor causes said output shaft to rotate, means for cyclically driving said rotor, said means including a support shaft rotatable about an axis parallel to said output shaft, an elongated arm fixedly connected intermediate its ends on said support shaft for rotation about the axis of said shaft, one end portion of said arm being coupled to said rotor by a coupling member constrained for radial movement on said arm, the other end portion of said am being tapered toward the free end thereof and having a radially disposed slot therein, a roller means constrained for movement in said slot, said driving means being operative to cause said roller to rotate said arm about said support shaft, motor means for moving the axis of rotation of said support shaft from a zero position where it is coaxial with the longitudinal axis of said output shaft to maximum and minimum offset positions on opposite sides of the zero position, and the distance between
  • variable speed device as defined in claim 6 wherein said am has a pocket on said one end portion between said coupling member and said shaft, said pocket being on a side face of said arm remote from said rotor and having a depth greater than one-half the thickness of said one end portion.
  • a variable speed device in accordance with claim 6 wherein a crowned roller is supported by said coupling member, said rotor having a slot receiving said crowned roller and being rotatably driven thereby.
  • a variable speed drive in accordance with claim 6 wherein the offset between the axes of said shafts is defined by:

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Transmission Devices (AREA)
US3745865D 1971-08-09 1971-08-09 Cyclic variable speed drive Expired - Lifetime US3745865A (en)

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US17018371A 1971-08-09 1971-08-09

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US3745865D Expired - Lifetime US3745865A (en) 1971-08-09 1971-08-09 Cyclic variable speed drive

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US (1) US3745865A (nl)
JP (1) JPS4827162A (nl)
CA (1) CA964081A (nl)
DE (1) DE2236692A1 (nl)
FR (1) FR2149756A5 (nl)
GB (1) GB1371410A (nl)
IT (1) IT964898B (nl)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3962942A (en) * 1974-11-29 1976-06-15 Molins Machine Company, Inc. Cutoff mechanism
US4098173A (en) * 1977-04-22 1978-07-04 Jamestown Container Corporation Automatic compensating register
US4186614A (en) * 1978-08-07 1980-02-05 Hamlin Fred A Force and distance multiplying oblique leverage transmission
US4201102A (en) * 1977-11-04 1980-05-06 Hauni-Werke Korber & Co., Kg Apparatus for subdividing running webs into sections of varying length
US4255998A (en) * 1977-11-03 1981-03-17 Hauni-Werke Korber & Co. Kg Apparatus for cutting paper webs or the like
US4360354A (en) * 1978-07-17 1982-11-23 The Deritend Engineering Co. Ltd. Machine for the treatment of web material
US4507994A (en) * 1978-04-10 1985-04-02 Jagenberg Ag Device for monitoring a cylinder-piston assembly
US5465648A (en) * 1995-01-04 1995-11-14 Cy; Chiou C. Cylinder having a piston assembly capable of stopping once when having moved up and down every time

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5635568Y2 (nl) * 1975-09-23 1981-08-21
GB2444165A (en) * 2006-11-23 2008-05-28 Applied Engine Technology Ltd A transmission with rectilinear drive mechanisms in series
GB2523072B (en) * 2013-12-05 2020-04-29 John Vowles Roger Variable output speed system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2957450A (en) * 1956-12-04 1960-10-25 American Mach & Foundry Filter tip machine
US3286536A (en) * 1963-03-07 1966-11-22 Philips Corp Driving mechanisms more particularly for the movement of picture films
US3613471A (en) * 1969-10-20 1971-10-19 S & S Corrugated Paper Mach Counterbalancing means for cutoff knives
US3659398A (en) * 1970-11-02 1972-05-02 Battle Creek Packaging Machine Film feed and cutter for fold-over wrapping machine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2957450A (en) * 1956-12-04 1960-10-25 American Mach & Foundry Filter tip machine
US3286536A (en) * 1963-03-07 1966-11-22 Philips Corp Driving mechanisms more particularly for the movement of picture films
US3613471A (en) * 1969-10-20 1971-10-19 S & S Corrugated Paper Mach Counterbalancing means for cutoff knives
US3659398A (en) * 1970-11-02 1972-05-02 Battle Creek Packaging Machine Film feed and cutter for fold-over wrapping machine

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3962942A (en) * 1974-11-29 1976-06-15 Molins Machine Company, Inc. Cutoff mechanism
US4098173A (en) * 1977-04-22 1978-07-04 Jamestown Container Corporation Automatic compensating register
US4255998A (en) * 1977-11-03 1981-03-17 Hauni-Werke Korber & Co. Kg Apparatus for cutting paper webs or the like
US4201102A (en) * 1977-11-04 1980-05-06 Hauni-Werke Korber & Co., Kg Apparatus for subdividing running webs into sections of varying length
US4507994A (en) * 1978-04-10 1985-04-02 Jagenberg Ag Device for monitoring a cylinder-piston assembly
US4360354A (en) * 1978-07-17 1982-11-23 The Deritend Engineering Co. Ltd. Machine for the treatment of web material
US4617850A (en) * 1978-07-17 1986-10-21 Dec (Realisations) Limited Machine for the treatment web material
US4186614A (en) * 1978-08-07 1980-02-05 Hamlin Fred A Force and distance multiplying oblique leverage transmission
US5465648A (en) * 1995-01-04 1995-11-14 Cy; Chiou C. Cylinder having a piston assembly capable of stopping once when having moved up and down every time

Also Published As

Publication number Publication date
JPS4827162A (nl) 1973-04-10
GB1371410A (en) 1974-10-23
IT964898B (it) 1974-01-31
FR2149756A5 (nl) 1973-03-30
DE2236692A1 (de) 1973-02-22
CA964081A (en) 1975-03-11

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