EP1091899A1 - Dispositif de transfert rotatif a grande vitesse - Google Patents

Dispositif de transfert rotatif a grande vitesse

Info

Publication number
EP1091899A1
EP1091899A1 EP99925238A EP99925238A EP1091899A1 EP 1091899 A1 EP1091899 A1 EP 1091899A1 EP 99925238 A EP99925238 A EP 99925238A EP 99925238 A EP99925238 A EP 99925238A EP 1091899 A1 EP1091899 A1 EP 1091899A1
Authority
EP
European Patent Office
Prior art keywords
cam
transfer
inches
conjugate
vehicle
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.)
Withdrawn
Application number
EP99925238A
Other languages
German (de)
English (en)
Inventor
Ronald Herbert Helton
Russell Pearce Bridges
John Frederick Droste
James Yu Hamilton
Maite Iraolagoitia
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.)
Procter and Gamble Co
Original Assignee
Procter and Gamble Co
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 Procter and Gamble Co filed Critical Procter and Gamble Co
Publication of EP1091899A1 publication Critical patent/EP1091899A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H5/00—Feeding articles separated from piles; Feeding articles to machines
    • B65H5/08—Feeding articles separated from piles; Feeding articles to machines by grippers, e.g. suction grippers
    • B65H5/12—Revolving grippers, e.g. mounted on arms, frames or cylinders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H29/00—Delivering or advancing articles from machines; Advancing articles to or into piles
    • B65H29/02—Delivering or advancing articles from machines; Advancing articles to or into piles by mechanical grippers engaging the leading edge only of the articles
    • B65H29/06—Delivering or advancing articles from machines; Advancing articles to or into piles by mechanical grippers engaging the leading edge only of the articles the grippers being carried by rotating members
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H29/00—Delivering or advancing articles from machines; Advancing articles to or into piles
    • B65H29/68—Reducing the speed of articles as they advance
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H3/00—Separating articles from piles
    • B65H3/42—Separating articles from piles by two or more separators mounted for movement with, or relative to, rotary or oscillating bodies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2403/00—Power transmission; Driving means
    • B65H2403/50—Driving mechanisms
    • B65H2403/51—Cam mechanisms
    • B65H2403/512—Cam mechanisms involving radial plate cam
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2403/00—Power transmission; Driving means
    • B65H2403/50—Driving mechanisms
    • B65H2403/54—Driving mechanisms other
    • B65H2403/543—Driving mechanisms other producing cycloids
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2513/00—Dynamic entities; Timing aspects
    • B65H2513/10—Speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2513/00—Dynamic entities; Timing aspects
    • B65H2513/20—Acceleration or deceleration

Definitions

  • This invention provides a rotary transfer device for transferring a material from one point to another point using a conjugate cam vehicle and a transfer drive mechanism therein to provide transfer speed ratios of between about lxl 0 4 : 1, about 1: 1, and/or about l : lxl0 4 , and also from a stationary position to a specified speed and vice versa.
  • Articles such as disposable diapers, generally have been manufactured by a process where discrete parts or components of different materials, such as leg elastic, waist elastic, tapes, and other fasteners such as hook and loop materials or snaps, have been applied to a continuously moving product web of interconnected articles.
  • discrete parts or components of different materials such as leg elastic, waist elastic, tapes, and other fasteners such as hook and loop materials or snaps.
  • the speed at which the parts are fed into the process is not the same as the speed of the product web itself.
  • the speed of the parts must be changed to match the speed of the product web to properly apply the parts without adversely affecting the process or the finished articles.
  • slip gap or slip cut method A web of material, which is traveling at a slower speed than the moving web, is fed into a knife and anvil roll having a surface speed equal to the speed of the moving web. As the material is cut into discrete parts, vacuum in the anvil roll is activated to draw the parts of material to the surface of the anvil roll. The anvil roll then carries the parts to the moving web where the vacuum is released and the parts are applied to the moving web while both the parts and the moving web are traveling at the same speed.
  • Another method has utilized festoons to reduce the speed of the moving web to match the speed of the discrete parts of material to be applied to the web.
  • the moving web is temporarily slowed down to the speed of the parts with the excess portion of the moving web gathering in festoons.
  • the parts of material are then applied to the moving web while both the parts and the web are traveling at the same speed.
  • the festoons are then released allowing the moving web to return to its original speed.
  • the slider-crank mechanism utilizes concentrically mounted arms or linkages to receive the discrete parts of material, increase the speed of the parts to match the speed of the moving web and apply the parts to the moving web.
  • the slider-crank mechanism is a special case of a four bar linkage system.
  • the cam actuated crank-follower mechanism comprises crank levers that are mounted on a rotatable driving plate. Each crank lever includes a cam follower on one end and a follower lever connected to the other end. The other end of the follower lever is connected to an applicator device which is mounted concentric with the driving plate's center of rotation.
  • the cam follower remains in contact with a fixed cam that is also mounted concentric with the driving plate's center of rotation.
  • the crank levers pivot as their cam followers follow the cam shape.
  • the follower levers cause the applicator devices to speed up or slow down.
  • An example of this method is described in U.S. Pat. No. 4,610,751 issued September 9, 1986, to Eschler.
  • the receiving and applying of the parts occurs while the respective surface speeds are maintained substantially constant for a fixed duration.
  • Such a substantially constant speed dwell allows precise control of the length and placement of the part on the substrate web especially if the part is fragile and/or elastic.
  • the present invention provides a transfer device comprising a conjugate cam vehicle for achieving a speed ratio ranging from about lxl0 4 :l, about 1 :1, and/or about l :lxl0 4 at pick-up or stationary at some speed and transfer of materials about the device.
  • This speed ratio range is achieved about a pair of points of pick-up and transfer spaced at least 10° and preferably at least 90° apart on the conjugate cam vehicle.
  • the conjugate cam vehicle comprises a first cam having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth faced inwardly toward the center point.
  • the conjugate cam also comprises a second cam having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth faced inwardly toward the center point.
  • the first cam and the second cam are positioned adjacent to one- another to form a conjugate cam vehicle having a center, an outer perimeter, an inner perimeter and irregularly shaped teeth faced inwardly toward the center.
  • the conjugate cam vehicle is configured to provide substantially inconstant acceleration about the irregularly shaped teeth such that the conjugate cam vehicle provides acceleration from between about 0° to about 180° of the outer perimeter and a deceleration from between about 180° to about 360° of the outer perimeter.
  • the transfer device also comprises a rotary transfer drive mechanism or transfer drive that picks up and transfers material.
  • the transfer drive is positioned within the conjugate cam and operates partially therein.
  • the transfer drive comprises a main drive shaft for driving the transfer drive mechanism which extends through the center of the conjugate cam.
  • the transfer drive comprises a rotatable drum having a perimeter, a center, a first side, and a second side opposed to the first side. The rotatable drum is attached to the main drive shaft at its center and rotates thereabout as the drive shaft rotates.
  • At least one transfer shaft is placed onto and through the rotatable drum adjacent to or near the drum perimeter.
  • Each transfer shaft comprises a first end and a second end. The first end of each transfer shaft is positioned above the first side of the rotatable drum and the second end of each rotatable shaft is positioned below the second side of the rotatable drum.
  • at least one transfer head is positioned about the first end of each transfer shaft above the first side of the rotatable drum, each transfer head preferably but not necessarily being rotatable about each transfer shaft.
  • a cam follower mechanism is positioned about the second end of each transfer shaft below the second side of the rotatable drum.
  • Each cam follower mechanism comprises a cam follower plate having a perimeter, a first side and a second side opposed to the first side, and at least two cam followers attached to each cam follower plate. At least one cam follower is attached to the first side of the cam follower plate with the other cam followers being attached to the second side of the cam follower plate.
  • Each cam follower mechanism is rotatable about one transfer shaft.
  • the transfer drive mechanism fits at least partially within the conjugate cam vehicle whereby the cam followers move about the irregularly shaped teeth of the conjugate cam as the rotary transfer drive mechanism is rotated by the main drive shaft within the conjugate cam.
  • Fig. 1 is a perspective view of the high-speed rotary transfer device
  • Fig. 2 is a side view of the high-speed rotary transfer device
  • Fig. 3 is a plan view of the conjugate cam vehicle
  • Fig. 4 is a plan view of the conjugate cam vehicle
  • Fig. 5 is a plan view of the conjugate cam vehicle
  • Fig. 6 is a plan view of the conjugate cam vehicle
  • Fig. 7 is a plan view of the conjugate cam vehicle
  • Fig. 8 is a plan view of the conjugate cam vehicle
  • Fig. 9 is a plan view of the conjugate cam vehicle
  • Fig. 10 is a plan view of the conjugate cam vehicle
  • Fig. 11 is a graph relating the planet or cam followers displacement, velocity, and acceleration as compared to the drum angle.
  • Fig. 12 is .
  • the present invention provides a transfer device that comprises a conjugate cam vehicle for achieving a speed ratio ranging from about lxl0 4 :l, about 1:1, and/or about lxlO 4 at pick-up and transfer of materials about the device.
  • This speed ratio range is achieved about a pair of points of pick-up and transfer spaced at least 10° and preferably at least 45° apart on the conjugate cam vehicle from the center of the vehicle.
  • the conjugate cam vehicle 20 comprises a first cam 21 having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth 25 faced inwardly toward the center point.
  • the conjugate cam vehicle 20 also comprises a second cam 22 having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth faced inwardly toward the center point.
  • the first cam 21 and the second cam 22 are positioned adjacent to one-another to form a conjugate cam vehicle 20 having a shared and common center, outer perimeter, inner perimeter and irregularly shaped teeth faced inwardly toward the center.
  • the conjugate cam vehicle 20 is configured to provide substantially inconstant acceleration about the irregularly shaped teeth 25 such that the conjugate cam vehicle 20 provides accelerations through the conjugate cam vehicle 20 ranging from between about 0° to about 180° of the outer perimeter and decelerations ranging from between about 180° to about 360° of the outer perimeter.
  • the transfer device 10 also comprises a rotary transfer drive mechanism 28 or transfer drive 28 that picks up and transfers material about the device 10.
  • the transfer drive 28 is positioned within the conjugate cam vehicle 20 and operates partially therein.
  • the transfer drive 28 comprises a main drive shaft 32 for driving the transfer drive 28 which extends through the center of the conjugate cam vehicle 20.
  • the transfer drive 28 comprises a rotatable drum 30 having a perimeter, a center, a first side, and a second side opposed to the first side.
  • the rotatable drum 30 is attached to the main drive shaft 32 through its center and rotates thereabout as the drive shaft 32 rotates.
  • At least one transfer shaft 35 is placed onto and through the rotatable drum 30 adjacent to or near the drum perimeter.
  • Each transfer shaft 35 comprises a first end 35 A (not shown) and a second end 35B (not shown).
  • the first end 35 A of each transfer shaft is positioned above the first side 30A of the rotatable drum 30 and the second end 35B of each rotatable shaft 35 is positioned below the second side 30B of the rotatable drum 30.
  • at least one transfer head 40 is positioned about the first end 35 A of each transfer shaft 35 above the first side 30A of the rotatable drum 30, each transfer head 40, preferably but not necessarily, being rotatable about each transfer shaft 35 to accommodate product size changes.
  • a cam follower mechanism 34 is positioned about the first end 35A of each transfer shaft 35 above the first side 30a of the rotatable drum 30.
  • Each cam follower mechanism 34 comprises a cam follower plate 38 having a perimeter, a first side 38' and a second side 38" opposed to the first side 38', and at least four cam followers 36 attached to each cam follower plate 38.
  • At least two cam follower 36 are attached to the first side 38' of the cam follower plate 38 and at least two cam followers 36 are attached to the second side 38" of the cam follower plate 38.
  • cam follower 36 For every one cam follower 36 on one side (either first or second) of the cam follower plate 38 there is another cam follower 36 positioned on the opposite side (either first or second) of the cam follower plate 38
  • Each cam follower mechanism 34 is rotatable on one transfer shaft 35.
  • the transfer drive mechanism 28 fits at least partially within the conjugate cam vehicle 20 whereby the cam followers 36 move about the irregularly shaped teeth 25 of the conjugate cam vehicle 20 as the transfer drive mechanism 28 is rotated by the main drive shaft 32 within the conjugate cam vehicle 20.
  • first and second cams each comprise a minor cam diameter ranging from about 3.0 inches to about 200 inches.
  • the minor cam diameters range from about 22 inches to about 28 inches.
  • the first and second cams each comprise a major cam diameter ranging from about 4.0 inches to about 260.0 inches.
  • the major cam diameters of the first and second cams range from about 30 inches to about 34 inches.
  • the minor cam diameter is that diameter measured from the inner perimeter of the conjugate cam (i.e., from the tips of the cam teeth) to the center of the conjugate cam vehicle 20.
  • the major cam diameter is that diameter measured from the deepest points of the irregularly shaped teeth (i.e., the bottom of the teeth) to the center of the conjugate cam vehicle 20.
  • the conjugate cam comprises 20 an outer diameter ranging from about 4.5 inches to about 180 inches.
  • the outer diameters of the conjugate cam vehicle 20 range from about 35 inches to about 37 inches.
  • the first and second cams each comprise a cam width ranging from about 0. 25 inches to about 8 inches.
  • the cam widths range from about 0.3125 inches to about 2.0 inches.
  • the first cam 21 and second cam 22, and thus the conjugate cam vehicle 20, also each comprise a harmonic deviation ranging from about 0° to about 10,000°.
  • harmonic deviation refers to the maximum rotational deviation of the planet per rotatable drum 30 cycle, or 360° rotation, due to the harmonic change in position.
  • the rotatable drum 30 of the transfer device 10 comprise a diameter ranging from about 2.5 inches to about 160 inches, preferably from about 15 inches to about 35 inches.
  • the thickness of the rotatable drum 30 may range from about 0.25 inches to about 20 inches.
  • Figure 1 provides a perspective view of the high-speed rotary transfer device or transfer device 10 taken at an angle behind the conjugate cam vehicle 20, the cam followers 36, the cam follower plates 38 and the rotatable drum 30. Also shown is the main drive shaft 32 extending through the transfer device 10 and the conjugate cam vehicle 20. Recall that the conjugate cam vehicle 20 is comprised of a first cam 21 and a second cam 22. Also shown are the transfer shafts 35 attached to the cam follower plates 38 at one end and attached to the transfer heads 40 at the other end. Fig. 1 shows a preferred embodiment wherein the transfer shafts 35 are attached to a rotatable guide plate 42 such that the transfer shafts 35 are stabilized at each of their respective ends.
  • the preferred motion of the transfer shafts 35 is that first, they rotate about the main drive shaft 32 as the cam followers 36 move along the conjugate cam's irregularly shaped teeth 25 of the first and second cams within and without of the conjugate cam vehicle 20 and second, the transfer shafts 35 themselves rotate such that the transfer heads 40 rotate about the transfer shafts 35.
  • Figure 2 provides a side view of the transfer device 10.
  • holding plates 15 may secure the device 10 to the ground or to some other structure while the transfer device 10 is in operation.
  • the main drive shaft 32 is shown herein extending through the device 10 and being connected to the rotatable drum 30 and the rotatable guide plate 42. Transfer shafts 35 are shown in spaced relationship to the main drive shaft 32.
  • Figures 3-5 provide top plan views of the conjugate cam vehicle 20, the rotatable drum 30, one end of the main drive shaft 32 the cam follower plates 38 and the cam followers 36 attached thereto and moving about the irregularly-shaped teeth 25 of the conjugate cam vehicle 20.
  • the front most cam is the second cam 22 and the first cam 21, although not shown here, would be positioned behind the second cam 22.
  • Fig. 3 provides an embodiment wherein three cam followers 36 are positioned on either side of the cam follower plate 38 giving a total of six cam followers 36 positioned onto each cam follower plate, three of which are not seen in this view.
  • cam profile it is meant herein the structure and shape of the cam teeth 25 of each cam in the conjugate cam vehicle 20.
  • Fig. 4 shows four cam followers 36 on the second side 38" of the cam follower plate 38. Therefore, four other cam followers 36 (not shown herein) are also attached to the first side 38' (not shown) of the cam follower plate 38 making a total of eight cam followers positioned onto each cam follower plate.
  • the cam profile shown in Fig. 4 was constructed to meet the design criteria (e.g., speed) of the transfer device 10 operating within the conjugate cam vehicle 20.
  • Figure 5 provides an additional component to that of Figure 4, the transfer head 40.
  • the transfer heads 40 herein are used to transfer a material from one source to another.
  • the transfer head 40 is shown to be contacting a source A, conceivably for either transfer or pick-up of a material.
  • the transfer heads 40 will always be aligned with the source A as they are rotated about transfer shafts 35 which in turn rotate about the main drive shaft 32.
  • each transfer head 40 is independently rotatable about its transfer shaft 35.
  • Figure 6 provides a plan view of the conjugate cam which shows the first cam 21 and the second cam 22. Also, four cam follower plates 38 with the cam followers 36 thereon are shown. The shaded cam followers 36 represent those cam followers which are positioned on the second side 38" of the cam follower plate 38. The unshaded cam followers 36 are positioned on the first side 38' of the cam follower plate 38. Eight cam followers 36 for each cam follower plate 38 are shown. Additionally, each cam follower plate 38 has a rotatable transfer head 40 positioned thereon. As shown, each transfer head 40 will follow the path of rotation 50 shown by the heads 40 located on each transfer shaft 35. As is also shown, the path 50 for the transfer heads 40 develops from the design of the conjugate cam vehicle 20 and the speed requirements for the pick-up and transfer of a material about the conjugate cam vehicle 20 from one point about the vehicle 20 to another point about the vehicle 20.
  • the transfer heads 40 are moving at their slowest rotation about the conjugate cam vehicle 20. As the transfer heads 40 make their way back up to transfer/pick-up area A, they are beginning to travel with greater rotational speed until they reach transfer/pick-up area A, the point or area of their greatest speed. Note, all of these speeds will correspond to the speeds of material to be picked up and transferred; i.e., when the transfer heads 40 pick-up and deliver materials, the heads surface will be moving at substantially the same speed as the pick-up and transfer sources. Also note that the closer that the irregularly-shaped teeth 25 are, the faster the transfer heads 40 will travel. Correspondingly, the more spread-out the teeth 25 are, the slower the heads will travel. Generally, the speed of the main drive shaft 32 remains constant.
  • Fig. 7 shows a plan view of a "cloverleaf configuration; i.e., the path of the transfer heads 40 about the conjugate cam and at a look at the conjugate cam vehicle 20 from behind the second cam 22.
  • the transfer heads 40 are moving at their fastest.
  • the transfer heads 40 are moving at their slowest.
  • the "cloverleaf path of the transfer heads 40 results from calculations determining the number of transfer head revolutions per drum revolutions.
  • the "cloverleaf path relates to the speed, and the orientation of the pick-up and transfer of materials from one point to another point. It is noted herein that one skilled in the art can construct various types of transfer head paths 50 to suit her design criteria. Any such path design therefore falls within the scope of the invention herein.
  • the transfer device may achieve times of transfer ranging from less than one millisecond to about 10 seconds between a point or points of pick-up.
  • each cam follower is positioned equidistant or proportionately from the other cam followers on the cam follower plate.
  • each cam follower mechanism comprises at least three cam followers placed equidistant apart about the cam follower plate perimeter on the first side of the cam follower plate and also at least three cam followers placed equidistant on the second side of the cam follower plate.
  • the rotatable drum may take-on any number of shapes per the designer's preferences and needs.
  • the rotatable drum may be in the shape of a circle, cross, star, bar, triangle or whatever shape might be useful for the operation of the device described herein.
  • Rotational displacement is the amount of rotation of the top dead center (t.d.c.) point on the transfer head relative to the radius of the drum which passes through the center of the head (Fig. 6).
  • top dead center point it is meant herein that point (or area) on a transfer head that contacts material along or adjacent to the transfer or pick-up points adjacent to the conjugate cam.
  • Rotational displacement is measured by the angular rotation of the top dead center point from the radius of the drum passing through the center of the transfer head 40.
  • the cam profile is driven by the harmonic deviation required.
  • Harmonic deviation is the amount of rotational displacement of top dead center point over one-half revolution about the conjugate cam, i.e., 180° from a point midway between the transfer and pick-up points to a point 180° from that point 90° to 270° on the cam.
  • harmonic deviation dictates how slowly or quickly the transfer head will spin about the transfer shafts 35 at the pick-up and transfer points about the conjugate cam vehicle 20. In this way harmonic deviation is said to drive the cam profile or determine the shape, height and contour of the teeth 25 of the conjugate cam vehicle 20.
  • the 180° revolution about the conjugate cam begins from 0° (a point of pick-up or transfer) and goes to 180° ( another point of transfer or pick-up).
  • the transfer point for the particular profile shown in Fig. 6 will be located at the 180° point.
  • the points of pick-up and transfer do not have to be 180° apart. More specifically, depending upon the size of a material to be picked-up, the transfer point may be less than or greater than 180°.
  • a discrete component pitch length and an interconnected article pitch length at about 20 inches at about 1 inch, respectively will, in one embodiment herein, have a range between transfer points at about 166° ⁇ 5°.
  • a material having a length at about 1 inch which is transferred to a product having a length at about 15 inches will have transfer points about the conjugate cam vehicle ranging from about 131° ⁇ 5°.
  • a material having a length at about 3 inches which is transferred to a product having a length at about 15 inches will have range between transfer points of about 130° ⁇ 5.
  • the cam followers will move about the conjugate cams in certain prescribed configurations.
  • Each of these configurations is created based upon various criteria specific to each transfer device design.
  • Fig. 6 shows a conjugate cam vehicle 20 and cam followers 36 moving about the conjugate cam in a "teardrop" configuration.
  • This prescribed configuration is determined by various factors which include the speed of the transfer device moving within the cam, the number of cam followers used, and the teeth profile of the conjugate cam vehicle 20. In designing the transfer device, all of these factors combine to produce the "teardrop" configuration or path of travel of the transfer heads 40.
  • Fig. 7 shows another configuration called the "cloverleaf.
  • the "cloverleaf is determined by the speed of the transfer device moving within the cam, the number of cam followers used, and the teeth profile of conjugate cam. In one example, the fewer the number of head revolutions per 360° revolutions of the drum produces less motion of the cam followers about the conjugate cam.
  • the transfer head rotates fewer times within one 360° revolution of the rotatable drum. Generally, fewer transfer head revolutions within one 360° drum revolution results in fewer teeth being built, machined or carved into the conjugate cam. Such a design would generally result in less contact stress being applied to the conjugate cam as a whole and on the teeth specifically. Also, less forces would be placed on the cam followers. This can result in greater product reliability in pick-up and transfer of materials about the conjugate cam.
  • Figures 8, 9, and 10 provide illustrations regarding use of the invention for a range of sizes of interconnected articles 202, 206 and a range of sizes of discrete components 201, 205.
  • Interconnected articles 202, 206 may be, for example, uncut or unreleased articles within a web. In one example, this web could be a diaper web or that of any of the known absorbent articles.
  • the discrete components 201, 205 may be component parts like tape tabs, waist features and other types of known elements commonly applied to sanitary napkins.
  • the range of pitch lengths of discrete components 201, 205 which the transfer device 10 is capable of applying and the range of pitch lengths of interconnected articles 202, 206 on which the discrete components will be applied is determined by the conjugate cam vehicle 200.
  • the maximum discrete component pitch length and maximum interconnected article pitch length have been set forth prior to the design of the conjugate cam vehicle 200.
  • the transfer device 10 is able to apply discrete components having a pitch length equal to or less than the maximum discrete component pitch length and is able to apply the discrete components onto interconnected articles having a pitch length equal to or less than the maximum interconnected article pitch length.
  • top dead center head radius it is meant herein the distance between the top dead center of the pick-up head surface and the center of the pick-up head shaft.
  • the new pick-up heads must be phase rotationally aligned to match their placement with the interconnected articles 202, 206.
  • Anvil roll 203 must be adjusted in position and rotational phase to align with the pick-up heads 208.
  • the vertical position and machine direction phasing of the interconnected articles 202, 206 must be adjusted to be aligned with the pick-up heads 208.
  • the supply rate of interconnected articles is equal to the number of heads on the drum 209 per every one revolution of said drum.
  • supply rate it is meant herein the rate at which one interconnected article 202, 206 is delivered to the point of transfer, i.e., pick-up head 208.
  • the rotational speed of the anvil roll is such that the discrete components 205 are supplied at a rate of one discrete component per one interconnected article.
  • the description can be broken down into several concepts that can be understood individually more easily.
  • the invention can be thought of as two wheels in space that spin in opposite directions. One is the main drum. The other is one of the planets. The total number of planets is not of concern here because if one planet can be modeled correctly then modeling the others is simply a matter of copying the first.
  • the following three examples explain the two essential concepts to the design of the cam, Planet Speed Factor and Harmonic Deviation.
  • Example Two Again the drum spins at constant velocity.
  • the planet has no initial rotational velocity, but begins accelerating up to some rotational speed, slows back to zero velocity, accelerates in the opposite direction up to the same rotational speed in the opposite direction, and then slows back to zero velocity. This cycle repeats for every revolution of the drum.
  • the Planet Speed Factor is 0 because the planet makes no cumulative revolutions.
  • the Harmonic Deviation is at some value, not zero. This example illustrates that Harmonic Deviation is the amount of rotation the planet experiences from rotational stopping point to rotational stopping point.
  • Example Three Combine Example One and Example Two.
  • the drum spins at constant velocity.
  • the planet begins at twice the rotational velocity of the drum in the opposite direction. It accelerates to some speed and then returns to the two times speed, then decelerates to some slower speed (without reversing), and returns to the two times speed.
  • Speed Factor is 2 and Harmonic Deviation is some value.
  • Fig. 11 shows a graph of planet rotational displacement, velocity, and acceleration.
  • the planet is placed on the edge of and in the same plane as the drum. At this point in the discussion the drum and planet motion have been described.
  • the next step is to track a point on the edge of the planet, representing the center of a cam follower.
  • the total number of cam followers is not of concern here because if one follower can be modeled correctly then modeling the others is simply a matter of copying the first as with the planets. The path that this point will trace will be one of the cam follower paths.
  • Planet Speed Factor Qualitatively, the amount of change in rotational speed of planet as drum makes constant rotation.
  • follower shift 45° for follower one, 135° for follower two, 225° for follower three, and 315° for follower four.
  • Fig. 12 shows the cam paths 55 (four) which can be used to fabricate the cam itself. Note that this is only one of two cams, a conjugate pair. In fact, second cam 22 is showing.
  • the first cam 21 is created by shifting the four followers 36 by 45°, half the spacing of the followers 36 to create four new paths 55.
  • adding 45° to each of the follower shift values 0°, 90°, 180°, & 270° will give new values of 45°, 135°, 225°, & 315° which will yield four new pairs of equations. While particular embodiments of the present invention have been illustrated and described, it would be obvious to those skilled in the art that various other changes and modifications can be made without departing from the spirit and scope of the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)

Abstract

Cette invention concerne un dispositif de transfert rotatif (10) qui permet de transférer une matière d'un point à un autre, et qui comprend, à cette fin, un véhicule (21) à came et contre-came ainsi qu'un mécanisme (28) d'actionnement et de transfert. On obtient ainsi des rapports de vitesse de transfert qui varient environ entre 1x104:1, 1:1 et/ou 1:1x104, et qui permettent également de passer d'une position stationnaire à une vitesse prédéterminée, et vice-versa.
EP99925238A 1998-06-30 1999-06-24 Dispositif de transfert rotatif a grande vitesse Withdrawn EP1091899A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US10737698A 1998-06-30 1998-06-30
US107376 1998-06-30
PCT/IB1999/001184 WO2000000419A1 (fr) 1998-06-30 1999-06-24 Dispositif de transfert rotatif a grande vitesse

Publications (1)

Publication Number Publication Date
EP1091899A1 true EP1091899A1 (fr) 2001-04-18

Family

ID=22316321

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99925238A Withdrawn EP1091899A1 (fr) 1998-06-30 1999-06-24 Dispositif de transfert rotatif a grande vitesse

Country Status (5)

Country Link
EP (1) EP1091899A1 (fr)
JP (1) JP2002519267A (fr)
AU (1) AU4160999A (fr)
CA (1) CA2335176A1 (fr)
WO (1) WO2000000419A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6942086B2 (en) 2002-11-22 2005-09-13 The Procter & Gamble Company Transfer apparatus for transferring a workpiece from a moving anvil to a moving carrier
JP6719069B2 (ja) * 2016-02-04 2020-07-08 シブヤマシナリー株式会社 物品受渡し装置
JP7029055B2 (ja) * 2018-02-22 2022-03-03 澁谷工業株式会社 物品積層装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2437986B1 (fr) * 1978-10-06 1985-06-21 Jagenberg Werke Ag Machine a etiqueter pour objets et en particulier pour bouteilles
US4596545A (en) * 1982-07-06 1986-06-24 R. A. Jones & Co. Inc. Orbital feeder
DE3476049D1 (en) 1983-10-21 1989-02-16 Hartmann Paul Ag Device for successively removing and applying tags from and to spaced regions on a web of material
IT1279950B1 (it) * 1995-06-14 1997-12-23 Gd Spa Metodo per l'alimentazione in continuo di elementi di incarto in foglio ad una macchina operatrice
US5716478A (en) 1995-10-17 1998-02-10 Kimberly-Clark Worldwide, Inc. Apparatus and method for applying discrete parts onto a moving web

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0000419A1 *

Also Published As

Publication number Publication date
JP2002519267A (ja) 2002-07-02
AU4160999A (en) 2000-01-17
CA2335176A1 (fr) 2000-01-06
WO2000000419A1 (fr) 2000-01-06

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