MXPA00012980A - A high-speed rotary transfer device - Google Patents

Abstract

This invention provides a rotary transfer device (10) for transferring a material from one point to another point using a conjugate cam vehicle (21) and a transfer drive mechanism (28) therein to provide transfer speed ratios of between about 1x104:1, about 1:1, and/or about 1:1x104, and also from a stationary position to a specified speed and vice versa.

Description

I A HIGH-SPEED TRANSFER SWITCHING DEVICE FIELD OF THE INVENTION This invention provides a rotary transfer device for transferring material from one point to another point using a conjugate cam vehicle and a transfer drive mechanism thereon to provide transfer rate ratios of between approximately 1x104: 1, approximately 1 : 1, and / or approximately 1: 1x104, and also from a position M (3 stationary up to a specific speed and vice versa.

BACKGROUND OF THE INVENTION Items, such as disposable diapers, have usually been manufactured by a process where the discrete parts or components of different materials, such as leg elastics, waist elastics, tapes and other fasteners such as hook and loop materials or snaps, have been applied to a weft of the product continuously in movement of interconnected articles. Often, the speed at which the parties are fed into the process is not the same as the speed of the plot of the product itself. In this way, the speed of the parts must be changed to match the speed of the weft of the product to properly apply the parts without adversely affecting the process or the finished items. Various conventional methods have been known to those skilled in the art to change the speed of a part or a component of material so that it can be applied to a continuously moving web. For example, a method has been known as the sliding gap method or sliding cut. A web of material, which is traveling at a lower speed than the moving web, is fed to a blade and an anvil roller having a surface velocity equal to the speed of the moving web. As the material is cut into discrete parts, the vacuum in the anvil roller is activated to pull the parts of the material towards the surface of the anvil roller. Then the anvil roller takes the parts to the moving frame where the vacuum is released and the part is applied to the moving web, while both the parts and the moving web are carried at the same speed. Another method has used scallops to reduce the speed of the moving web to match the speed of the discrete material parts that are applied to the web. The moving plot is temporarily made to slow down at the speed of the parts with the excess portion of the moving plot festooning in festoons. The parts of the material are then applied to the moving frame while both the parts and the frame are traveling at the same speed. The festoons are then released allowing the moving plot to return to its original speed. Another method has been to use a sliding crank mechanism to achieve the speed change. The sliding crank mechanism uses arms or links concentrically mounted to receive the discrete parts of the material, increase the speed of the parts to equalize the speed of the moving web and apply the parts to the moving web. The sliding crank mechanism is a special case of a four-bar articulated system. Another method for changing the velocity of a discrete part before a moving frame is applied has used a cam-operated crank follower mechanism. The cam-operated crank follower mechanism comprises crank levers which are mounted on a rotating drive 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 that is mounted concentric with the center of rotation of the drive plate. The cam follower remains in contact with the fixed cam which is also mounted concentric with the center of rotation of the drive plate. As the drive plate rotates, the crank levers pivot as their cam followers follow the shape of the cam. Like the pivot of the crank levers, the levers of the follower cause the applicator device to accelerate or decelerate. An example of this method is described in U.S. Patent No. 4,610,751 issued September 9, 1986, to Eschler. Finally, another method for changing the speed of a discrete part before a moving frame is applied uses a displaced crank motion of a drive ring and the pivoting of the coupler arms to vary the effective driving radius of a segment of transfer material to provide variable speeds. More specifically, as the transfer segments rotate around their drive ring, they are able to move along their radial arm to effect changes in their speeds when picking up and transferring the elastic materials. An example of this method is described in U.S. Patent No. 5,716,478 issued on February 10, 1998 to Boothe, et al. Conventional methods, such as those described above, have exhibited several disadvantages. For example, as the discrete parts of the material are transferred, they are often subjected to a pulling action due to the surface velocity of the transfer medium used to transfer the parts that is greater than the speed of the parts. The drag action may result in undesirable lengthening or tearing of the parts. Also, some, if any, of conventional methods have the ability to achieve high-speed proportions claimed by the invention here; for example, the cutting and sliding method is one of said conventional method and also, it can not provide irregular shapes taken from one frame to another. Finally, several of the conventional methods can be very expensive and time-consuming to change as the size and speed of the discrete parts and the speed of the moving pattern change to coincide with different sizes of finished product. Consequently, an inexpensive and adaptable apparatus for receiving discrete parts traveling at a speed and applying the parts to a frame traveling at a different speed is desirable. Furthermore, it is desirable that the reception and application of the parts occur as long as the respective surface velocities are maintained substantially constant for a fixed duration. For example, it is desirable to apply the parts to the substrate web while the parts of the substrate web are traveling at substantially the same surface speed or at a similar speed. Such substantially constant rate retention allows precise control of the length and placement of the part on the substrate web especially if the part is fragile and / or elastic. Furthermore, it is desired here that the radius between the transfer axes and the center of the rotating drum remain constant.

BRIEF DESCRIPTION OF THE INVENTION Accordingly, the present invention provides a transfer device comprising a conjugate cam vehicle to achieve a rate ratio ranging from approximately 1x104: 1, approximately 1: 1, and / or approximately 1: 1x104 in the speed development or stationary at some speed and the transfer of materials around the device. This range of the speed ratio is achieved around a pair of pick-up and transfer points 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 central point, an outer perimeter, an internal perimeter, and irregularly shaped teeth which face inwards toward the central point. The conjugate cam may also comprise a second cam having a central point, an outer perimeter, an internal perimeter, and irregularly shaped teeth that face inwards toward the central point. The first cam and the second cam are positioned adjacent to each other to form a conjugate cam vehicle having a center, an outer perimeter, an internal perimeter and irregularly shaped teeth that face inwards toward the center. The conjugate cam vehicle is configured to provide substantially inconsistent acceleration around the irregularly shaped teeth such that the conjugate cam vehicle provides acceleration from about 0 ° to about 180 ° of the outer perimeter and a deceleration to from about 180 ° to about 360 ° of the outer perimeter. The transfer device also comprises a rotating transfer drive mechanism or transfer driver that collects and transfers the material. The transfer impeller is placed inside the conjugate cam and operates partially there inside. The transfer driver comprises a main drive shaft for driving the transfer drive mechanism which extends through the center of the conjugate cam. In addition, the transfer impeller comprises a rotary drum having a perimeter, a center, a first side, a second side opposite the first side. The rotating drum is attached to the main drive shaft at its center and rotates around it as the drive shaft rotates.

At least one transfer arrow is placed on and through the rotary drum adjacent to or near the perimeter of the drum. Each transfer arrow comprises a first end and a second end. The first end of each transfer arrow is positioned above the first side of the rotating drum and the second end of each rotary arrow is positioned below the second side of the rotating drum. Also, at least one transfer head is positioned around the first end and each transfer arrow above the first side of the rotary drum, each transfer head preferably but not necessarily being rotatable about each transfer shaft. A cam follower mechanism is placed around the second end of each transfer arrow below the second, side of the rotating drum. Each cam follower mechanism comprises a cam follower plate having a perimeter, a first side and a second side opposite the first side, and at least two cam followers fixed to each cam follower plate. At least one cam follower is fixed to the first side of the cam follower plate with the other cam followers which are fixed to the second side of the cam follower plate. Each cam follower mechanism is rotatable around a transfer arrow. The transfer drive adjusts at least partially within the camming vehicle whereby the cam followers move around the irregularly shaped teeth of the conjugate cam as the rotary transfer drive mechanism is rotated by the main drive arrow within the the conjugate cam BRIEF DESCRIPTION OF THE FIGURES Although the description concludes with the claims pointing out in a particular way and claiming differently the exposed matter that is considered as formant of the present invention, it is believed that the invention will be better understood from the following description taken in combination with the drawings that they accompany it, in which: Figure 1 is a perspective view of a rotary high-speed transfer device; Figure 2 is a side view of a high-speed rotary transfer device; Figure 3 is a plan view of the conjugate cam vehicle; Figure 4 is a plan view of the conjugate cam vehicle; Figure 5 is a plan view of the conjugate cam vehicle; Figure 6 is a plan view of the conjugate cam vehicle; Figure 7 is a plan view of the conjugate cam vehicle; Figure 8 is a plan view of the conjugate cam vehicle; Figure 9 is a plan view of the conjugate cam vehicle; Figure 10 is a plan view of the conjugate cam vehicle; Figure 11 is a graph related to the displacement of the planet or the followers of cam, velocity, and acceleration as compared to the angle of the drum.

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a transfer device comprising a conjugate cam vehicle to achieve a rate ratio that varies from approximately 1x104: 1, approximately 1: 1, and / or approximately 1: 1x104 in the uptake and transfer of materials around the device. This range of the speed ratio is achieved around a pair of pick-up and transfer points separated at least 10 ° and preferably at least 45 ° apart on the conjugate cam vehicle from the center of the vehicle. As shown in Figure 1, the conjugate cam vehicle 20 comprises a first cam 21 having a central point, an outer perimeter, an internal perimeter and irregularly shaped teeth 25 that face inward towards the central point. The conjugate cam vehicle 20 also comprises a second cam 22 having a central point, an outer perimeter, an internal perimeter, and irregularly shaped teeth that face inward towards the central point. The first cam 21 and the second cam 22 are positioned adjacent to each other to form a conjugate cam vehicle 20 having a shared and common center, an outer perimeter, an internal perimeter and irregularly shaped teeth that face inwards towards the center. The conjugate cam vehicle 20 is configured to provide substantially non-constant acceleration around the irregularly shaped teeth 25 such that the conjugate cam vehicle 20 provides accelerations through the conjugate cam vehicle 20 ranging from about 0 ° to approximately 180 ° of the external perimeter and decelerations varying from about 180 ° to about 360 ° of the external perimeter. The transfer device 10 also comprises a rotary transfer drive 28 or transfer driver 28 which collects and transfers the material around the device 10. The transfer driver 28 is placed inside the conjugate cam vehicle 20 and operates partially therein therein. The transfer impeller 28 comprises a main drive shaft 32 for driving the transfer driver 28, which extends through the center of the conjugate cam vehicle 20. Further, the transfer driver 28 comprises a rotating drum 30 having a perimeter , a center, a first side and a second side opposite the first side. The rotary drum 30 is fixed to the main drive shaft 32 through its center and rotates around it as the drive shaft rotates 32. At least one transfer arrow 35 is placed on and through the rotating drum 30 adjacent to or near the perimeter of the drum. Each transfer arrow 35 comprises a first end 35A (not shown) and a second end 35B (not shown). The first end 35A of each transfer arrow is positioned above the first side 30A of the rotary drum 30 and the second end 35B of each rotating shaft 35 is positioned below the second side 30B of the rotating drum 30. AlsoAt least one transfer head 40 is placed around the first end 35A of each transfer arrow 35 above the first side 30A of the rotating drum 30, each transfer head 40, preferably but not necessarily, being rotatable about each transfer arrow 35 to adapt to changes in the size of the product. A cam follower mechanism 34 is positioned around the first end 35A of each transfer arrow 35 above the first side 30a of the rotating drum 30. Each cam follower mechanism 34 comprises a cam follower plate 38 having a perimeter, first side 38 'and a second side 38"opposite the first end 38', and at least four cam followers 36 fixed to each cam follower plate 38. At least two cam followers 36 are fixed to the first side 38 'of the plate 38 of the cam follower and at least two cam followers 36 are fixed to the second side 38"of the square 38 of the cam follower. For each cam follower 36 on one side (either the first or the second) of the cam follower plate 38 there is another cam follower 36 positioned on the opposite side (either the first or the second) of the plate 38 of the cam follower Each cam follower mechanism 34 is rotatable on a transfer shaft 35. The transfer drive mechanism 28 fits at least partially inside the conjugate cam vehicle 20, whereby the cam followers 36 move around the irregularly shaped teeth. of the conjugate cam vehicle 20 as the transfer drive 28 is rotated by the main drive shaft 32 within the conjugate cam vehicle 20. In practice, each of the first and second cams comprise a smaller cam diameter that varies from about 7.6 cm to about 508 cm. Preferably, the smaller diameters of the cam vary from about 55 cm to about 70 cm. Also, each of the first and second cams comprise a larger cam diameter ranging from about 10 cm to about 650 cm. Preferably, the larger cam diameters of the first and second cams vary from about 75 cm to about 85 cm. The smaller diameter of cam is that diameter measured from the internal perimeter of the conjugate cam (i.e., from the tips of the cam teeth) to the center of the conjugate cam vehicle 20. The larger cam diameter is that diameter measured from the deepest points of the irregularly shaped teeth (i.e., the lower part of the teeth) to the center of the conjugate cam vehicle 20. Additionally, the conjugate cam comprises an outer diameter ranging from approximately 11.40. cm to approximately 450 cm. Preferably, the outer diameters of the conjugate cam vehicle 20 range from about 87.5 cm to about 92.5 cm. Each of the first and second cams comprises a cam width ranging from about 0.64 cm to about 20 cm. Preferably, the cam widths vary from about 0.7937 cm to about 5.08 cm. The first cam 21 and the second cam 22, and in this way the conjugate cam vehicle 20, each also comprises a harmonic deviation ranging from about 0 ° to about 10,000 °. As used herein, the term "harmonic deviation" refers to the maximum rotational deviation of the planet by 30 cycles of the rotating drum, or 360 ° rotation, due to the harmonic change in position. The rotating drum 30 of the transfer device 10 comprises a diameter ranging from about 6.35 cm to about 400 cm, preferably from about 37.5 cm to about 87.5 cm. The thickness of the rotating drum 30 can vary from about 0.635 cm to about 50 cm. Figure 1 provides a perspective view of a high-speed rotary transfer device or transfer device 10 taken at an angle behind the conjugate cam vehicle., the cam followers 36, the cam follower plates 38 and the rotating drum 30. The main drive shaft 32 is also shown extending through the transfer device 10 and the conjugate cam vehicle 20. Recalling that the vehicle of The conjugate cam 20 is composed of a first cam 21 and a second cam 22. Also shown are the transfer arrows 35 fixed to the cam follower plates 38 at one end and fixed to the transfer heads 40 at the other end. Figure 1 shows a preferred embodiment wherein the transfer arrows 35 are fixed to a rotating guide plate 42 in such a way that the transfer arrows 35 are stabilized at each of their respective ends. The preferred movement of the transfer arrows 35 is that first, they rotate about the main drive shaft 32 as the cam followers 36 move along the irregularly-shaped teeth of the conjugate cam 25 of the first and second cams inside. or outside the conjugate cam vehicle 20 and second, the transfer arrows 35 themselves rotate so that the transfer heads 40 rotate around the transfer arrows 35. Figure 2 provides a side view of the transfer device. 10. In an alternative embodiment, the retainer plates 15 (not shown) can secure the device 10 to the ground or some other structure while the transfer device 10 is in operation. As shown in Figure 1, the main arrow of ^ O drive 32 is shown here extending through the device 10 and being connected to the rotary drum 30 and to the rotating guide plate 42. The transfer arrows 35 are shown in separate relationship with respect to the main drive shaft 32. Figures 3 to 5 provide top plan views of the conjugate cam vehicle 20, the rotating drum 30, one end of the main drive shaft. 32, the plates of the cam follower 38 and the cam followers 36 fixed thereto and moving around the irregularly formed teeth 25 of the conjugate cam vehicle 20. In these views, the frontmost cam is the second cam 22 and the first cam 21, although not shown there, would be placed behind the second cam 22. Figure 3 provides a modality where three cam followers 36 are placed on either side of the cam follower plate 38 giving a total of six cam followers 36 placed on each cam follower plate, three of which are not seen in this view. The shape and shape of the cam teeth 25 in Figure 3 provide a suitable profile of the cam through which the followers can travel (by rotation) through the conjugate cams to meet the designed requirements of transfer speed and pickup speed. It is noted here that the cam followers 36 freely rotate about either a rotating or stationary arrow 52 (not shown) that connects each cam follower to its resident cam follower plate. By the term "cam profile" herein is meant the structure and shape of the cam teeth 25 of each cam in the conjugate cam vehicle 20. In another embodiment of the present, 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 there) are also fixed to the first side 38 '(not shown) of the cam follower plate 38 making a total of eight cam followers placed on each cam follower plate As in the embodiment of Figure 3, the cam profile shown in Figure 4 was constructed to meet the design criteria (eg, speed) of the transfer device 10 operating inside 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 a were I made you another. For example, in Figure 5 the transfer head 40 is shown to be in contact with a source A, conceivable for either the transfer or pickup of a material. In practice, the transfer heads 40 will always be aligned with the source A as they rotate around the transfer arrows 35 which instead rotate around the main drive shaft 32. Preferably, each transfer head 40 is independently rotatable around its transfer arrow 35. Figure 6 provides a plan view of the conjugate cam which shows the first cam 21 and the second cam 22. Also, four plates of the cam follower 38 are shown with the cam followers 36. in the same. The shaded cam followers 36 represent those cam followers which are placed 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 follower plate of the cam follower. cam 38. Eight cam followers 36 are shown for each cam follower plate 38. Additionally, each cam follower plate 38 has a rotating transfer head 40 positioned therein As shown, each transfer head 40 will follow the rotation path 50 shown by the heads 40 located on each transfer shaft 35. Also as shown, the path 50 for the transfer heads 40 develops from the design of the conjugate cam vehicle 20 and the speed requirements for capturing and transferring a material around the conjugate cam vehicle 20 from a point around the vehicle 20 to another point around the vehicle 20. In the flattened or bulb portion of the "formed drop" path, the transfer heads 40 move in their slowest rotation around the conjugate cam vehicle 20. As the transfer heads 40 make their way back to the area of transfer / capture A, they begin to travel with a higher rotational speed until they reach the transfer / capture area A, the point or the area of their higher velocity. Note, all of these speeds will correspond to the speeds of the material that is captured and transferred; that is, when the transfer heads 40 collect and supply the materials, the surface of the heads will be moved at substantially the same speed as the collection and transfer sources. Also note that the closer the irregularly shaped teeth are, the faster the transfer heads will travel 40. Correspondingly, the greatest extent of the teeth 25 are, the less the heads will travel. In general, the velocity of the main drive shaft 32 remains constant. Figure 7 shows a plan view of a "cloverleaf" configuration ie the trajectory of the transfer heads 40 around the conjugate cam and in a view of the conjugate cam vehicle 20 from the rear part of the cam the second cam 22. Where the teeth of the conjugate cam 25 are smaller and closer together, the transfer heads 40 are moving in their fastest manner. Correspondingly, wherein the teeth of the conjugate cam vehicle 20 are in their widest and most widely spaced manner, the transfer heads 40 are moving in their slowest manner. The "clover leaf" path of the transfer heads 40, as in the "drop" path configuration, results from the calculations to determine the number of revolutions of the transfer head by the revolutions of the drum. The trajectory of "clover leaf" is related to the speed, and the orientation of the materials of capture and transfer from one point to the other point. It is noted here that a person skilled in the art can construct various types of trajectories of the transfer head 40 to suit his design criteria. Therefore, any trajectory design falls within the scope of the present invention. The transfer device can achieve transfer times that vary from less than one millisecond to about 10 seconds between a point or points of capture. In one embodiment here, one pair of cam followers are fixed to the first side of the cam follower plate and the other pair of the cam followers is fixed to the second side of the cam follower plate. Preferably, each cam follower is equidistantly or proportionally positioned from the other cam followers on the cam follower plate. In another embodiment here, each mechanism of the cam follower comprises at least three cam followers positioned equidistantly apart around the perimeter of the cam follower plate 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 rotating drum can take any number of forms by the preferences and needs of the designer. For example, the rotating drum may be in the form of a circle, cross, star, bar, triangle, or any shape that could be useful for the operation of the device described herein.

Rotational displacement and harmonic deviation The rotational displacement is the amount of rotation of the dead center top point (t.d.c.) on the transfer head relative to the drum radius, which passes through the center of the head (Figure 6). The upper dead center point here means that point (or area) on a transfer head that contacts the material along or adjacent to the transfer or collection points adjacent to the conjugate cam. The rotational displacement is measured by the angular rotation of the upper dead center point from the radius of the drum passing through the center of the transfer head 40. The profile of the cam is driven by the required harmonic deflection. The greater harmonic deviation, the higher speeds will be at various points around the conjugate cam vehicle 20, and specifically at the pick-up and / or transfer points around the conjugate cam vehicle 20. The harmonic deflection is the amount of rotational displacement of the point upper central dead over half revolution around the conjugate cam, that is 180 ° from a point halfway between the transfer and collection points up to a point of 180 ° from that point 90 ° to 270 ° in the cam further, the harmonic deviation dictates how slowly or quickly the transfer head will rotate around the transfer arrows 35 at the pick-up and transfer points around the conjugate cam vehicle 20. In this way the harmonic deflection is said to drive the cam profile or determining the shape, height and contour of the teeth 25 of the conjugate cam vehicle 20. As shown in Figure 6, the 180 ° revolution around the conjugate cam starts from 0 ° (a pick-up or transfer point). ) and goes up to 180 ° (another point of transfer or capture). Obviously if the collection point is set at 180 °, then the transfer point for the particular profile shown in Figure 6 will be located at the 180 ° point. It is noted here that the capture and transfer points do not have to be 180 ° apart. More specifically, depending on the size of a material to be captured, the transfer point may be less than or greater than 180 °. For example, a discrete separation length of the component and an interconnected separation length of the article at about 20 inches to about 1 inch, respectively, in one embodiment here, will have a range between the transfer points at approximately 166 ° + 5 °. . In an alternative embodiment here, a material having a length of about 1 inch that is transferred to a product having a length of about 15 inches will have transfer points around the vehicle of the conjugate cam which vary from about 131 ° + 5 °. Likewise, a material that has a length of approximately 3 inches that will be transferred to a product that has a length of approximately 15 inches will have an interval between the transfer points of approximately 130 ° + 5. In practice, the cam followers will move around the conjugate cams in certain prescribed configurations. Each of these configurations is created based on several specific criteria for each transfer device design. For example, Figure 6 shows a conjugate cam vehicle 20 and cam followers 36 that move around the conjugate cam in a "drop" configuration. This prescribed configuration is determined by various factors including the speed of the transfer device moving within the cam, the number of cam followers used, and the profile of the teeth of the conjugate cam vehicle 20. When designing the transfer device, all of these factors combine to produce the "drop" configuration or the travel path of the transfer heads 40. Figure 7 shows another configuration called "cloverleaf". As the "drop", the "trefoil leaf" is determined by the speed of the transfer device that moves within the cam, the number of cam followers used, and the profile of the teeth of the conjugate cam. In an example, the lower number of head revolutions per revolutions to 360 ° of the drum produces the smaller movement of the cam followers around the conjugate cam. In the "drop" configuration, the transfer head rotates less times within a 360 ° revolution of the rotating drum. In general, the lower revolutions of the transfer head within a revolution of the 360 ° drum result in the smaller teeth being constructed, machined or carved into the conjugate cam. Such a design would usually result in the least contact stress applied to the conjugate cam as a whole and on the teeth specifically. Also, less force would be placed on the cam followers. This can result in greater product reliability when capturing and transferring materials around the conjugate cam. Figures 8, 9 and 10 provide illustrations with respect to the use of the invention for a range of sizes of interconnected articles 202, 206 and a range of discrete component sizes 201, 205. The interconnected articles 202, 206 may be, for example, uncut or un-peeled articles within a frame. In one example, this weft can make a diaper weave or that of any of the known absorbent articles. The discrete components 201, 205 may be component parts such as tape tabs, waist features and other types of commonly known elements applied to sanitary napkins. The range of the separation lengths of the discrete components 201, 205 that the transfer device 10 is capable of applying and the range of the separation lengths of the interconnected articles 202, 206 over which the discrete components will be applied are determined by the conjugate cam vehicle 200. The maximum separation length of the discrete component and the maximum separation length of the connected article have been established prior to the design of the conjugate cam vehicle 200. The transfer device 10 is capable of applying the discrete components having a separation length equal to or less than the maximum separation length of the discrete component and capable of applying the discrete components on the interconnected articles having a separation length equal to or less than the maximum separation length of the connected article. Referring now to Figures 8, 9 and 10, in practice, when it becomes necessary to either apply a discrete component whose size does not equal the maximum separation length of the discrete component or apply a discrete component to a interconnected article of which its size is not equal to the maximum separation length of the connected article, or the distance between similar points of adjacent parts of the product, adjustments must be made to the transfer device 10.

Specifically, the displacement of the cam, the fixed rotational position of the conjugate cam vehicle 200 must be adjusted. The pick-up heads 208 (Figure 8) should be replaced with a new pick-up head 210 to match the shape of the new discrete components 205 and having a new top dead center head radius. By the term "head radius of the upper dead center" is here meant the distance between the upper dead center of the surface of the pick-up head and the center of the arrow of the pick-up head. The new pick-up heads must be rotationally aligned phases to match their placement with the interconnected articles 202, 206. The anvil roll 203 must be adjusted in position and the rotational phase to align with the pick-up heads 208. The vertical position and the machine direction phase of the interconnected items 2, 202, 206 must be adjusted to be aligned with the pick-up heads 208. It is usually desirable that the delivery speed of the interconnected articles be equal to the number of heads on the drum 209 for each revolution of said drum. By the term "delivery rate" is meant the speed at which an interconnected article 202, 206 is delivered to the transfer point, ie, the pick-up head 208. It is also commonly desirable that the speed of rotation of the Anvil roll is such that the discrete components 205 are supplied at a speed of a discrete component by an interconnected article. To create a cam that produces the rotating motion of a planet that is attached to a drum that rotates at a fixed speed, it is only necessary to describe the trajectories of the centers of the cam followers that mount along the cam. Each cam follower on the planet will have its own unique trajectory that will travel through once for each revolution of the drum. By using a cutting device with the same diameter as the cam followers, these same trajectories can be used to manufacture the cam. Therefore, the task of defining the cam profile becomes a matter of mathematically describing the trajectories of the followers and therefore the cam cutters that will create the profile. A pair of equations for each follower trajectory must be found and a list of coordinates for each trajectory must be created, these being the outputs of the equations giving some step of increase of the rotation of the drum.

To help in writing the mathematics involved with the invention, the description can be broken down into several concepts that can be more easily understood individually. The invention can be taught as two wheels in space that move in opposite directions. One is the main drum. The other is one of the planets. The total number of planets is of no interest here because if one planet can not be modeled correctly then modeling the others is simply a matter of copying the first one. The following three examples explain the two essential concepts for the design of the cam, the planet's velocity factor and the harmonic deviation.

EXAMPLES Example one: The drum moves at constant speed. The planet moves at a constant speed and at twice the rotational speed of the drum in the opposite direction. In this example, the planet's velocity factor is 2. The harmonic deviation is 0 because there is no change in the velocity of the planet.

Example two: Again the drum moves at constant speed. The planet has no initial rotational velocity, but begins to accelerate to some rotational velocity, reduces velocity to the velocity of zero, accelerates in the opposite direction to the same rotational velocity in the opposite direction, and then decelerates to the velocity of zero. This cycle is repeated for each revolution of the drum. In this example, the planet's velocity factor is 0 because the planet does not make cumulative revolutions. The harmonic deviation is at some value, not zero. This example illustrates that the harmonic deviation is the amount of rotation that the planet experiences from the point of rotational stop to the point of rotational stop.

Example three: Example one and example two combined. The drum moves at a constant speed. The planet begins at twice the rotational speed of the drum in the opposite direction. It accelerates at some speed and then returns to twice the speed, then decelerates at some slower speed (without inverting), and returns at twice the speed. The velocity factor 2 and the harmonic deviation is some value. Figure 11 shows a graph of the planet's rotational displacement, velocity and acceleration. The planet is placed on the edge of and on the same plane as the drum. At this point in the discussion the movement of the drum and the planet have been described. The next step is to follow a point on the edge of the planet, representing the center of a cam follower. The total number of cam followers is of no interest here because if a follower can not be modeled correctly then the modeling of the others is simply a matter of copying the former as with the planets. The trajectory that will trace this point will be one of the trajectories of the cam follower. The pair of equations that give the position of the cam follower, especially the angle and distance from the center of the drum, for any given drum angle is dependent on a series of five fixed variables. The names and definitions for these variables follow: Drum radius - Distance from the center of the drum to the center of the planet. Planet radius - Distance from the center of the planet to the center of the cam follower. Planet speed factor - Average rotational speed of the planet divided by the speed of the drum.

Harmonic deviation - Mathematically, the largest amount of rotational displacement of the planet that you will experience from the constant rotation defined by the planet's velocity factor. Qualitatively, the amount of change in the rotation speed of the planet according to the drum makes the rotation constant. Tracker Displacement - Position of each follower on your planet. In a planet configuration of four followers, the tracking of the follower equals 0 ° for one follower, 90 ° for two followers, 180 ° for three followers, and 270 ° for four followers. For the conjugate cam, the tracking of the follower equals 45 ° for one follower, 135 ° for two followers, 225 ° for three followers, and 315 ° for four followers. Figure 12 shows the cam paths 55 (four) that can be used to manufacture the cam itself. Note that this is only one of two cams, a conjugate pair. In fact, the second cam 22 is shown. The first cam 21 is created by moving four followers 36 by 45 °, half of the split of the followers 36 to create four new trajectories 55. For a follower of four by cam design, adding 45 ° to each of the follower displacement values 0 °, 90 °, 180 °, and 270 °, will give new values of 45 °, 135 °, 225 ° and 315 ° which will produce new four pairs of equations. Although the 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.

Claims (13)

1. A transfer device for transferring articles, characterized in that: a conjugate cam vehicle to achieve a speed ratio ranging from approximately 1: 1 to approximately 1: 1X1010, around a pair of separate points at least 45 ° apart in the vehicle of conjugate cam, the conjugate cam vehicle comprising a first cam having a central point, an outer perimeter, an internal perimeter, and irregularly shaped teeth that face inwards toward the central point, a second cam having a central point, a outer perimeter, an internal perimeter, and irregularly shaped teeth that face inward towards the central point, the first cam and the second cam being placed adjacent to each other to form a conjugate cam vehicle having a central point, an outer perimeter, an internal perimeter and irregularly shaped teeth that face inwards toward the central point, the vehicle being conjugate cam configured to provide substantially discontinuous acceleration about the teeth irregularly shaped such that the conjugate cam vehicle is configured to provide acceleration from about 0 ° to about 180 ° of the outer perimeter and a deceleration of between about 180 ° to approximately 360 ° of the outer perimeter, the transfer drive providing multiple contact points in the pickup and transfer of the material and operating with the conjugate cam vehicle comprising a main drive shaft for driving the transfer drive, a rotating drum having a perimeter, a center, a first side and a second side opposite the first side, the rotating drum being fixed to the main drive shaft through the center and rotating around it, at least two arrows of transfer this When placed opposite each other on and through the rotary drum adjacent the perimeter of the drum, each transfer arrow comprises a first end and a second end, the first end of each transfer arrow being positioned above the first side of the rotating drum and the second end of each rotary arrow being positioned below the second side of the rotating drum, at least one transfer head being positioned around the first end of each transfer arrow above the first side of the rotary drum, each rotary transfer head being around each transfer arrow, and a mechanism of the cam follower positioned around the second end of each transfer arrow under the second side of the rotating drum, each mechanism of the cam follower comprising a cam follower plate having a perimeter, a first side and a second side opposite the first lad or, at least two cam followers fixed to each cam follower plate, at least one cam follower being fixed to the first side of the cam follower plate and at least the other cam follower being attached to the second cam follower. side of the cam follower plate, with each mechanism of the cam follower being rotatable about a transfer shaft, the transfer drive adjusting at least partially within the cam cam conjugate such that the cam followers adjust within and they move around the irregularly shaped teeth of the conjugate cam.

The transfer device according to claim 1, wherein each of the first cam and the second cam comprises a smaller cam diameter ranging from about 15.24 cm to about 127 cm and preferably from about 55.88 cm to about 71.12 cm.

3. The transfer device in accordance with the claim 1, wherein each of the first cam and the second cam comprises a greater diameter of cam ranging from about 20.32 cm to about 162.56 cm and preferably from about 76.2 cm to about 86.36 cm.

4. The transfer device according to claim 1, wherein each of the first cam and the second cam comprises an outer diameter ranging from approximately 22.86 cm to approximately 182.88 cm and preferably from approximately 88.9 cm to approximately 93.98 cm.

The transfer device according to claim 1, wherein each of the first cam and the second cam comprises a cam width ranging from about 0.7937 cm to about 6.35 cm and preferably from about 0.635 cm to about 5.08 cm .

The transfer device according to claim 1, wherein the first cam and the second cam each comprise a harmonic deviation ranging from about 100 ° to about 230 °.

The transfer device according to claim 1, wherein the speed ratio varies from about 1: 1 to about 35: 1.

The transfer device according to claim 1, wherein the rotating drum comprises a diameter ranging from about 63.5 cm to about 71.12 cm.

9. The transfer device in accordance with the claim 1, wherein the rotating drum comprises a thickness ranging from about 5.08 cm to about 12.7 cm.

The transfer device according to claim 1, wherein the transfer drive achieves a transfer time ranging from about 0 milliseconds to about 10 seconds.

11. The transfer device according to claim 1, wherein a pair of cam followers are fixed to the first side and the second side of the cam follower plate, each cam follower of each pair being positioned 80 ° from the other cam follower in the pair.

12. The transfer device in accordance with the claim 1, wherein each cam follower mechanism comprises at least three cam followers positioned equidistantly apart around the perimeter of the cam follower plate on the first side of the cam follower plate and at least three cam followers positioned equidistant around the perimeter of the cam follower plate on the second side of the cam follower plate. The transfer device according to claim 1, wherein the rotating drum comprises a circular shape, a cross shape, a star shape, or a bar shape.