JP2002519267A - High-speed rotation transfer device - Google Patents

Abstract

(57) Abstract: The present invention provides a rotary transfer device (10) for transferring a substance from one point to another using a conjugate cam wheel (21) and a transfer drive mechanism (28). It provides a transport speed ratio between × 10 ⁴ : 1, approximately 1: 1 and / or approximately 1: 1 × 10 ⁴ and also from a stationary position to a specific speed and vice versa.

Description

DETAILED DESCRIPTION OF THE INVENTION

FIELD OF THE INVENTION The present invention provides a rotary transfer device for transferring a substance from one point to another using a conjugate cam wheel and a transfer drive mechanism, comprising approximately 1 × 10 ⁴ : 1, approximately 1.
: 1, and / or substantially 1: 1 × 10 feed speed ratio between ⁴ and also provides to a specific speed and vice versa from the rest position.

BACKGROUND OF THE INVENTION [0002] Manufactured generally by processing individual parts or components of different materials, such as leg elastics, waist elastics, tape, and other fasteners such as hooks and loops or snaps. Articles such as disposable diapers were applied to continuously move the product web of interconnected articles. often,
The speed of the parts fed into the process is not the same as the speed of the product web itself. Thus, in order to properly apply the part without adversely affecting the process or finished article, the speed of the part must be varied to match the speed of the product web.

[0003] Several different conventional methods of varying the speed of a part or component of a material are known in the art, as it can be applied to continuously moving the web. For example, one method is known as slip gap or slip cut. A web of material moving at a lower speed than the moving web is fed to a knife and an anvil roll having a surface speed equal to the speed of the moving web. When the material is cut into discrete parts, a vacuum is applied to the anvil roll to draw the parts of the material onto the surface of the anvil roll. The anvil roll then carries the part to the moving web where the vacuum is released, and the part is applied to the moving web while both the part and the moving web are moving at the same speed.

[0004] Other methods have utilized festoons to reduce the speed of the moving web to match the speed of the individual parts of the material to be applied to the web. The moving web is temporarily reduced to the speed of the part over the excess of the moving web gathering at the festoon. The material part is then applied to the moving web while both the part and the moving web are moving at the same speed. The festoon is then released to allow the moving web to return to its original speed.

[0005] To achieve speed changes, other methods utilize a slider-crank mechanism.
The slider-crank mechanism utilizes concentrically mounted arms or links to receive individual parts of the material, increasing the speed of the parts to match the speed of the moving web and applying the parts to the moving web. A slider-crank mechanism is a special case of a four bar link system.

Another method of changing the speed of an individual component before it is applied to a moving web is
A cam driven crank driven mechanism was used. The cam driven crank follower includes a crank lever mounted on a rotatable drive plate. Each crank lever includes a cam follower at one end and a follower lever connected to the other end. The other end of the driven lever is connected to an application device mounted concentrically with the center of the rotary driving plate. The cam follower also remains in contact with a stationary cam mounted concentric with the center of the rotating drive plate. As the drive plates rotate, the crank levers rotate as their cam followers according to the cam shape. When the crank lever rotates, the driven lever increases or decreases the speed of the application device. An example of this method is described in US Patent N issued to Eschler on September 9, 1986.
o. 4,610,751.

Finally, another method of changing the speed of the individual parts before it is applied to the moving web is to provide an offset crank movement of the drive ring and an effective drive of the mass transfer segment to provide a variable speed. The rotation of the connecting arm that changes the radius is used. Still more particularly, as the transfer segments rotate about their drive rings, they can move along their radial arms to effectively change their speed in picking up and transferring flexible material. It is. An example of this method is 1998 2
US Patent No. issued to Boothe et al. 5,716,478.

[0008] Conventional methods such as those described above have several disadvantages. For example, when individual parts of a substance are transferred, they are often tugging because the surface speed of the transfer means used to transfer the parts is greater than the speed of the parts.
) Easy to operate. The pulling action results in undesirable extension or tearing of the part. Also, if some of the conventional methods have the ability to achieve the high speed ratio claimed by the present invention, for example, if the cut and slip method is one such normal method, then Unable to provide irregular shapes taken from the web to others. Finally, some of the usual methods are very costly and time consuming to change as the dimensions and the speed of the individual parts and the speed of the moving web vary to match the various final product dimensions. Consume. As a result, there is a need for an inexpensive and adaptable apparatus that receives individual parts moving at one speed and applies the parts to a web moving at a different speed.

[0009] Furthermore, the receiving and adapting of the parts preferably takes place while the relative surface speed remains substantially constant for a fixed period of time. For example, it is preferable to apply the part to the material web while the part and the material web are moving at approximately the same surface speed, i.e., coincident speed. Substantially constant speed, if the part is brittle and / or flexible
In particular, it is believed to allow precise control of the length and placement of components on the material web.

In addition, it is desirable here that the radius between the transfer axis and the center of the rotatable drum remain constant.

SUMMARY OF THE INVENTION [0011] Accordingly, the present invention provides for stationary pickup and transfer of material at a certain velocity with respect to the device, in the order of approximately 1 × 10 ⁴ : 1, approximately 1: 1 and / or approximately 1: 1 × 10 ^4. A transfer device including a conjugate cam wheel that achieves a speed ratio in the range of This speed ratio range is achieved for a pair of pickup and transfer points spaced at least 10 degrees, and preferably at least 90 degrees, on a conjugate cam wheel.

The conjugate cam wheel includes a first cam having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth facing inward toward the center point. The conjugate cam also has a second point having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth facing inward toward the center point.
Including cam. The first and second cams are positioned proximate to each other to form a conjugate cam wheel having a center, an outer perimeter, an inner perimeter, and irregularly-shaped teeth facing inward toward the center.

The conjugate cam wheel has irregularly shaped teeth such that the conjugate cam wheel provides acceleration between approximately 0 degrees and approximately 180 degrees around the outer periphery and deceleration between approximately 180 degrees and approximately 360 degrees around the outside periphery. Is configured to provide a substantially non-constant acceleration with respect to

The transfer device also includes a rotary transfer drive mechanism, ie, a transfer drive for picking up and transferring substances. The transfer drive is located in the conjugate cam and operates locally therein. The transfer drive includes a main drive shaft that drives the transfer drive mechanism through the center of the conjugate cam. further,
The transfer drive includes a periphery, a center, a first side, and a second side opposite the first side. A rotatable drum is mounted at its center to the main drive shaft and rotates with respect to it as the drive shaft rotates.

[0015] At least one transfer shaft is provided on and through the rotatable drum around or near the drum. Each transfer axis includes a first end and a second end. A first end of each transfer shaft is positioned above a first side of the rotatable drum, and a second end of each rotatable shaft is positioned below a second side of the rotatable drum. In addition, at least one transfer head has a rotatable first drum.
Positioned about the first end of each transfer axis on the side, each transfer head is preferably, but not necessarily, rotatable about each transfer axis.

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 includes a cam follower plate having a perimeter, a first side and a second side opposite the first side, and at least two cam followers attached to each cam follower plate. At least one cam follower is attached to a first side of the cam follower plate and another cam follower is attached to a second side of the cam follower plate. Each cam follower mechanism is rotatable about one transfer axis.

The transfer drive is at least locally fitted in the conjugate cam wheel, so that when the rotary transfer drive is rotated by the main drive shaft in the conjugate cam, the cam follower will have the irregularly shaped teeth of the conjugate cam. Move about.

While the specification includes claims that particularly point out and distinctly claim the subject matter regarded as forming the invention, the invention will be better understood from the following description taken in conjunction with the accompanying drawings. I believe.

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for picking up and transferring substances with respect to a device of approximately 1 × 10 ^4.
The present invention provides a transfer device including a conjugate cam wheel that achieves a speed ratio in the range of 1: 1, approximately 1: 1 and / or approximately 1: 1 × 10 ⁴ . This speed ratio range is achieved for a pair of pick-up and transfer points that separate the conjugate cam wheels separately from the center of the vehicle by at least 10 degrees, preferably 45 degrees.

As shown in FIG. 1, the conjugate cam wheel 20 includes a first cam 21 having a center point, an outer periphery, an inner periphery, and irregularly shaped teeth 25 facing inward toward the center point. Conjugate cam wheel 20 also includes a second cam 22 having a center point, an outer perimeter, an inner perimeter, and irregularly shaped teeth facing inward toward the center point. First cam 21 and second cam 22
Are positioned adjacent to each other to form a conjugate cam wheel 20 having a shared and common center, outer perimeter, inner perimeter, and irregularly shaped teeth facing inward toward the center point.

The conjugate cam wheel 20 provides acceleration through the conjugate cam wheel 20 in a range of approximately 0 degrees to approximately 180 degrees around the outer periphery, and provides deceleration in a range of approximately 180 degrees to approximately 360 degrees around the outside periphery. The conjugate cam wheel 20 is formed to provide substantially non-constant acceleration for irregularly shaped teeth 25.

The transfer device 10 also includes a rotary transfer drive mechanism 28, ie, a transfer drive 28, that picks up and transfers material with respect to the device 10. A transfer drive 28 is located within and operates partially within the conjugate cam wheel 20. The transfer drive 28 includes a main drive shaft 32 that passes through the center of the conjugate cam wheel 20 to drive the transfer drive 28. In addition, the transfer drive 28 is
Includes a rotatable drum 30 having one side and a second side opposite the first side.
A rotatable drum 30 is mounted through its center to a main drive shaft 32 and rotates with respect to the drive shaft 32 as it rotates.

At least one transfer shaft 35 is installed adjacent to the periphery of the drum, ie through the rotatable drum 30. Each transfer shaft 35 includes a first end 35A (not shown) and a second end 35B (not shown). First end 3 of each transfer axis
5A is located on the first side surface 30A of the rotatable drum 30, and the
The two ends 35B are located below the second side surface 30B of the rotatable drum 30. Also, at least one transfer shaft 40 is positioned with respect to the first end 35A of each transfer shaft 35 on the first side 30A of the rotatable drum 30, and each transfer shaft 40 is not required but preferably has product sizing. Is rotatable about each transfer shaft 35 to accommodate.

Each of the transfer shafts on the first side surface 30 A of the drum 30 on which the cam follower mechanism 34 can rotate.
Positioned with respect to 35 first ends 35A. Each cam follower mechanism 34 is peripheral, first side 38
And a cam follower plate 38 having a second side surface 38 "opposite the first side surface 38 'and at least four cam followers 36 attached to each cam follower plate 38. At least two cam followers A joint 36 is attached to the first side 38 'of the cam follower plate 38 and includes at least two
Two cam followers 36 are attached to the second side 38 "of the cam follower plate 38. The cam follower plate
With respect to all the cam followers 36 on one side (either the first or second) of the other 38, the other cam followers located on the opposite side (either the first or the second) of the cam follower plate 38 There are 36. Each cam follower mechanism 34 is rotatable on one transfer shaft 35.

The transfer drive mechanism 28 is at least partially fitted in the conjugate cam wheel 20 so that when the transfer drive mechanism 28 is rotated by the main drive shaft 32 in the conjugate cam wheel 20, the cam follower 36 The cam wheel 20 moves with respect to the irregularly shaped teeth 25.

In practice, the first and second cams each include a small cam diameter ranging from approximately 3.0 inches to approximately 200 inches. Preferably, the small cam diameter ranges from about 22 inches to about 28 inches.
Also, the first and second cams each include a large cam diameter ranging from approximately 4.0 inches to approximately 260.0 inches. Preferably, the large cam diameter of the first and second cams is from about 30 inches to about 34
Range of inches. The small cam diameter is the diameter measured from the inside periphery of the conjugate cam (ie, from the tip of the cam teeth) to the center of the conjugate cam wheel 20. The large cam diameter is the diameter measured from the deepest point of the irregularly shaped tooth (ie, the bottom of the tooth) to the center of the conjugate cam wheel 20.

In addition, the outer diameter of the conjugate cam wheel 20 ranges from approximately 4.5 inches to approximately 180 inches. Preferably, the outer diameter of the conjugate cam wheel 20 ranges from approximately 35 inches to approximately 37 inches. The first and second cams each include a cam width ranging from approximately 0.25 inches to approximately 8 inches. Preferably, the cam width ranges from approximately 0.3125 inches to approximately 2.0 inches. 1st cam
21 and the second cam 22, and thus the conjugate cam wheel 20, are also each at approximately 0 degrees to approximately 10,000
Includes harmonic deviation in the 0 degree range. The term "harmonic deviation" as used herein refers to the cycle of the rotatable drum 30 due to harmonic changes in position, i.e., 36
The maximum rotation deviation of the planet per 0 degree rotation.

The rotatable drum 30 of the transfer device 10 includes a diameter ranging from about 2.5 inches to about 160 inches, and is preferably from about 15 inches to about 35 inches. The thickness of the rotatable drum 30 may range from approximately 0.25 inches to approximately 20 inches.

FIG. 1 shows a conjugate cam wheel 20, a cam follower 36, a cam follower plate 38, and a rotatable drum.
High-speed rotary transfer device 30 viewed from the back angle, that is, transfer device 10
FIG. Further, a main drive shaft 32 penetrating the transfer device 10 and the conjugate cam wheel 20 is shown. Recall that conjugate cam wheel 20 includes a first cam 21 and a second cam 22. Also shown is a transfer shaft 35 attached to the cam follower plate 38 at one end and to the transfer head 40 at the other end. FIG. 1 shows a preferred embodiment in which the transfer shaft 35 is mounted on a rotatable guide plate 42 such that the transfer shaft 35 is stabilized at their respective ends. The preferred movement of the transfer shaft 35 is that firstly when the cam follower 36 moves along the conjugated cam irregularly shaped teeth 25 of the first and second cams inside and outside the conjugate cam wheel 20, the transfer shaft Second, the transfer shaft 35 rotates about itself such that the transfer head 40 rotates about the transfer shaft 35.

FIG. 2 provides a side view of the transfer device 10. In an alternative embodiment,
While the transfer device 10 is in operation, a retaining plate 15 (not shown) may secure the device 10 to the ground or some other structure. As shown in FIG. 1, the main drive shaft
32 indicates that it penetrates the device 10 and is connected to the rotatable drum 30 and the rotatable guide plate 42. The transfer shaft 35 is shown separated from the main drive shaft 32.

FIG. 3-5 shows the upper surface of the conjugate cam wheel 20, one end of the main drive shaft 32, the cam follower plate 38 and the cam follower 36 attached thereto and moving with respect to the irregularly shaped teeth 25 of the conjugate cam wheel 20. Provide a diagram. In these figures, the foremost cam is the second cam 22, not shown here, but the first cam 21 is located behind the second cam 22. FIG. 3 illustrates that three cam followers 36 are located on either side of a cam follower plate 38 providing a total of six cam followers 36 located on each cam follower plate, three of which are shown in FIG. An embodiment not shown in the figure is provided. The shape and profile of the cam teeth 25 in FIG. 3 provide a suitable cam profile in which the follower moves (by rotation) through the conjugate cam to meet the designed transport and pickup speed requirements. It is noted here that the cam followers 36 rotate freely about either rotatable or stationary axes 52 (not shown) connecting each cam follower to its underlying cam follower plate. The term "cam profile" here refers to the structure and shape of the cam teeth 25 of each cam in the conjugate cam wheel 20.

In another embodiment, FIG. 4 illustrates four cam followers 3 on a second side 38 ″ of a cam follower plate 38.
Shows 6. Therefore, four other cam followers 36 (not shown) are also attached to the first side 38 '(not shown) of the cam follower plate 38, a total of which is located on each cam follower plate. Eight cam followers are provided. As in the embodiment of FIG.
The cam profile shown in FIG. 1 is configured to meet the design criteria (eg, speed) of the transfer device 10 operating in the conjugate cam wheel 20.

FIG. 5 provides additional components of the transfer head 40 to that of FIG.
Here, the transfer head 40 is used to transfer material from one source to another. For example, in FIG. 5, the transfer head 40 indicates that it is in contact with the source A, possibly for either transferring or picking up material. In fact, the transfer heads 40 will always be aligned with the source A when they are rotated about the transfer axis 35, which rotates about the main drive axis 32. Preferably, each transfer head 40 is independently rotatable about its transfer axis 35.

FIG. 6 provides a plan view of the conjugate cam showing the first cam 21 and the second cam 22. Also shown are four cam follower plates 38 having a cam follower 36 thereon. The hatched cam followers 36 represent those cam followers located on the second side 38 "of the cam follower plate 38. The unshaded cam followers 36 are the first side 38 of the cam follower plate 38. The eight cam followers 36 of each cam follower plate 38 are shown.In addition, each cam follower plate 38 has a rotatable transfer head 40 positioned thereon. As such, each transfer head 40 will follow the path of rotation 50 indicated by the head 40 located on each transfer shaft 35. Also, as shown, the path 50 of the transfer head 40 will And from one point around the car 20 to another point around the car 20 from the speed requirements for material pickup and transfer for the conjugate cam wheel 20.

In the stretched or bulbous part of the formed “water drop” path,
The transfer heads 40 are moving at their slowest rotation with respect to the conjugate cam wheel 20. When transfer heads 40 are returned in their path to transfer / pickup area A, they are beginning to move at a high rotational speed until they reach transfer / pickup area A, at which point their maximum speed at area A Becomes All of these speeds correspond to the speed of the material being picked up and transferred, i.e., when the transfer head 40 picks up and delivers the material, the head surface will be moving at approximately the same speed as the pickup and transfer source. It should be noted. In addition, the closer the irregular shape of the teeth 25 is to the transfer head
It should be noted that the 40 moves faster. Correspondingly, the longer teeth 25 slow down the movement of the head. In general, the speed of the main drive shaft 32 remains constant.

FIG. 7 shows a transfer head for a “cloverleaf” configuration, ie, a conjugate cam.
FIG. 5 is a plan view of the conjugate cam wheel 20 viewed from a path 40 and a second cam 22 behind. Where the conjugate cam teeth 25 are smallest and closest to each other, the transfer heads 40 are moving at their highest speed. Correspondingly, the transfer heads 40 are moving at their lowest speed where the teeth of the conjugate cam wheel 20 are at their widest and most distant. As in the "drop" path configuration, the "cloverleaf" path of the transfer head 40 results from a calculation that determines the number of transfer head rotations per drum rotation. The "cloverleaf" path relates to speed and the direction of material pick-up and transfer from one point to another. It is noted here that those skilled in the art can configure various types of transfer head paths 50 to adapt to the design criteria. Any such path design therefore falls within the scope of the present invention.

The transfer device achieves a transfer time in the range of less than 1 millisecond to 10 seconds between pickup points.

In one embodiment herein, one pair of cam followers is attached to a first side of the cam follower plate, and another pair of cam followers is attached to a second side of the cam follower plate. . Preferably, each cam follower is positioned equidistant or balanced from the other cam followers of the cam follower plate. Here, in another embodiment, each cam follower mechanism comprises at least three cam followers equidistant about the periphery of the cam follower plate on the first side of the cam follower plate; At least three cam followers equidistantly disposed on the second side.

The rotatable drum can take any number of forms depending on the preferences and needs of the designer. For example, the rotatable drum can be a circle, cross, star, bar, triangle, or any shape useful for operation of the devices described herein.

Rotation Displacement and Harmonic Deviation Rotation displacement is the amount of rotation of the top dead center (tdc) of the transfer head with respect to the radius of the drum passing through the center of the head (FIG. 6). Top dead center here means the point (or area) of the transfer head that contacts the material along or adjacent the transfer or pickup point adjacent to the conjugate cam. The rotational displacement is measured by the angular rotation of the top dead center from the radius of the drum passing through the center of the transfer head 40.

The cam profile is driven by the required harmonic deviation. The high harmonic deviation is
The speed is high at various points with respect to the conjugate cam wheel 20, especially at the pick-up and / or transfer points with respect to the conjugate cam wheel 20. Harmonic deviation is the amount of rotational displacement of the top dead center that is more than one-half relative to the conjugate cam, ie, 18 minutes from the midpoint between the transfer and pickup points.
0 degrees, the point of the cam is 180 degrees from 90 degrees to 270 degrees. In addition, the harmonic deviation dictates how slowly or quickly the transfer head rotates about the transfer axis 35 in pick-up and transfer with respect to the conjugate cam wheel 20. In this way, it can be said that the harmonic deviation manipulates the cam profile and determines the shape, height and contour of the teeth 25 of the conjugate cam wheel 20.

As shown in FIG. 6, the 180 degree rotation for the conjugate cam begins at 0 degrees (pickup or transfer point) and proceeds to 180 degrees (transfer or other point of pickup).
Clearly, if the pick-up point is set at 180 degrees, the transfer point for the particular profile shown in FIG. 6 would be located at the 180 degree point. It should be noted that the pickup and transfer points do not have to be 180 degrees apart. Depending on the size of the material to be picked up, the transfer point may be smaller or larger than 180 degrees. For example, if the individual component pitch lengths and the interconnected article pitch lengths are approximately 20 inches and 1 inch, respectively, then in one embodiment, the range between the transfer points has 166 degrees ± 5 degrees. Here in an alternative embodiment,
A material having a length of approximately 1 inch transferred to a product having a length of approximately 15 inches will have a transfer point in the range of approximately 131 ° ± 5 ° with respect to the conjugate cam wheel. Similarly, abbreviations
Approximately 1 substance having a length of approximately 3 inches transferred to a product having a length of 15 inches
It has a range between the transfer points of 30 degrees ± 5 degrees.

In practice, the cam follower moves with respect to the conjugate cam in a certain defined shape. Each of these shapes is made according to various standard specifications for each transfer device design. For example, FIG. 6 shows the conjugate cam wheel 20 and cam follower 36 moving in a "drop-drop" configuration with respect to the conjugate cam. This defined shape depends on the speed of the transfer device moving in the cam, the number of cam followers used, and the conjugate cam wheel 20.
It is determined by various factors, including the tooth profile. In the design of the transfer device, all of these factors combine to create a “drop of water” shape, ie, a path of movement for the transfer head 40.

FIG. 7 shows another shape called “clover leaf”. Like "drop", "cloverleaf" is determined by the speed of the transfer device moving within the cam, the number of cam followers used, and the tooth profile of the conjugate cam.

In one embodiment, a smaller number of head rotations for a 360 degree rotation of the drum produces less movement of the cam follower with respect to the conjugate cam. In the "drop" configuration, the transfer head rotates several times within one 360 degree rotation of the rotatable drum. Generally, less transfer head rotation within one 360 degree drum rotation is assembled into the conjugate cam, resulting in several machined or bent teeth. Such designs generally result in small contact stresses being applied to the conjugate cam as a whole and especially as teeth. Also, a small force is applied to the cam follower. This can result in greater product reliability in picking up and transferring material with respect to the conjugate cam.

FIGS. 8, 9, and 10 provide diagrams that are considered use of the invention for the size ranges of the interconnected articles 202, 206, and the size ranges of the individual components 201, 205. The interconnected articles 202, 206 can be, for example, articles that are not cut into the web, ie, are not pulled apart. By way of example, the web may be a diaper web or any web of known absorbent articles. The individual components 201, 205 are components such as tape tabs, waist neck features and other types of known components commonly applied to sanitary napkins.

The range of the pitch length of the individual components 201, 205 to which the transfer device 10 is applicable and the range of the pitch length of the interconnecting articles 202, 206 to which the individual components are applied are determined by the conjugate cam wheel 200. It is determined. The maximum individual component pitch length and the maximum interconnected article pitch length are indicated prior to the design of the conjugate cam wheel 200. The transfer device 10 can be applied to individual components having a pitch length equal to or less than the maximum individual component pitch length, and transfer the individual components to an interconnected article having a pitch length equal to or less than the maximum interconnected article pitch length. Allows you to apply.

Referring to FIGS. 8, 9 and 10, in practice, the size is applied to an individual component whose size is not equal to the maximum individual component pitch length, or the size is applied to the maximum interconnected article pitch length , Or when it is necessary to apply individual components to interconnected articles that are not equal to the distance between similar points on adjacent product parts.
Will be adjusted. In particular, the cam shift and the fixed rotating part of the conjugate cam wheel 200 must be adjusted. Pickup head 208 (FIG. 8) conforms to the shape of new discrete component 205 and must be replaced with a new pickup head 210 having a new top dead center head radius. The term "top dead center head radius" as used herein means the distance between the top dead center of the pickup head surface and the center of the pickup head axis. The new pickup head must be phase rotated to match the interconnected articles 202, 206 and their replacement. The position and rotation phase of the anvil roll 203 must be adjusted so as to align with the pickup head 208. The vertical position and machine direction indicating the phase of the interconnected articles 202, 206 are
Must be adjusted to align with 8.

It is usually preferred that the feed rate of the interconnected article be equal to the number of heads of the drum 209 for each revolution of the drum. The term “feed rate” is used herein to refer to one interconnected article 20.
2, 206 means the point of transfer, that is, the rate of delivery to the pickup head 208. It is also usually preferred that the rotational speed of the anvil roll is such that the individual components 205 are supplied at a rate of one individual component per interconnected article.

In order to create a cam that produces a rotating motion of a planet attached to a drum rotating at a fixed speed, it is only necessary to describe the path of the center of the cam follower traveling along the cam. . Each cam follower of the planet will have its own unique path it will travel once for each revolution of the drum. By using a cutting device having the same diameter as the cam follower, these same paths can be used to manufacture the cam. Therefore, the task of defining a cam profile will mathematically describe the path of the camcutter that makes up the follower and the profile. A pair of equations for each follower path is found, and a list of alignments for each path is created, which are the outputs of the equations given some incremental steps of drum rotation.

For the purpose of describing the mathematical formulas involved in the invention, the description may be analyzed into several concepts that can be more easily understood individually. The invention is based on two spaced apart rotations in opposite directions.
Can be considered as one wheel. One is the main drum. The other is one planet.
If one planet can be accurately modeled, the total number of planets is not relevant here, since the other model is simply to make the first copy. The following three examples illustrate two concepts essential to cam design: planetary speed coefficient and harmonic deviation.

Examples Example 1: The drum rotates at a constant speed. The planet rotates in the opposite direction at a constant speed and twice the rotation speed of the drum. In this example, the planet speed coefficient is 2. Since there is no change in the planetary speed, the harmonic deviation is zero.

Example 2: Again the drum rotates at a constant speed. The planet begins to accelerate to a certain rotational speed rather than the initial rotational speed, returns to zero speed, accelerates in the opposite direction to the same rotational speed in the opposite direction, and then returns to zero speed. This cycle repeats with each rotation of the drum. In this example, since the planets do not make cumulative turns, the planet speed coefficient is 0.
It is. Harmonic deviation is a value, not zero. This example shows that harmonic deviation is the amount of rotation that the planet experiences from a spin stop to a spin stop.

Example 3: Examples 1 and 2 are combined. The drum rotates at a constant speed. The planet starts in the opposite direction at twice the rotation speed of the drum. It accelerates to a certain speed, returns to double speed, then decelerates to a lower speed (without reversing) and returns to double speed. The speed coefficient is 2, and the harmonic deviation is a certain value. FIG. 11 shows graphs of planetary rotation transition, velocity, and acceleration.

The planets are located on the edge of the drum and on the same plane. Drum and planetary movements were described in this regard in this discussion.

The next step is to track the edge of the planet about the center of the cam follower. If one follower is modeled correctly, the total number of cam followers is irrelevant, as the other model is to make an initial copy simply as a planet. The path that this point tracks is one cam follower path.

A pair of equations giving the position of the cam follower, ie, the angle and distance from the center of the drum for a given drum angle, depend on a set of five fixed variables. The names and definitions of these variables are as follows: Drum radius-the distance from the center of the drum to the center of the planet. Planet radius-the distance from the center of the planet to the center of the cam follower. Planetary speed factor-the average rotational speed of the planet divided by the speed of the drum. Harmonic Deviation-Mathematically, the maximum amount of rotational displacement a planet experiences from a constant rotation defined by a planetary speed coefficient, qualitatively, the change in the rotational speed of the planet when the drum is at a constant rotation. Follower Shift-the position of each follower on the planet. In the four follower planet configuration, the follower shift is equal to 0 degrees for follower 1, equal to 90 degrees for follower 2, equal to 180 degrees for follower 3, and equal to 270 degrees for follower 4. For the conjugate cam, the follower shift is equal to 45 degrees for follower 1, 135 degrees for follower 2, 225 degrees for follower 3, and 315 degrees for follower 4.

FIG. 12 shows cam paths (four) that can be used to manufacture the cam itself.
It should be noted that this is only one of the two cam, conjugate pairs. In fact, the second cam 22 is shown. The first cam 21 is driven 3 to create four new paths 55
It is made by shifting the four followers 36 by half a spacing of sixty-five degrees. For the four followers for the cam design, adding 45 degrees to each of the follower shift values 0, 90, 180, and 270 gives a new value of 4 that yields four new pairs of equations.
Gives 5, 135, 225, and 315 degrees.

While particular embodiments of the present invention have been shown and described, it will be apparent to those skilled in the art that other changes and modifications can be made without departing from the spirit and scope of the invention.

[Brief description of the drawings]

FIG. 1 is a perspective view of a high-speed rotation transfer device.

FIG. 2 is a side view of the high-speed rotation transfer device.

FIG. 3 is a plan view of the conjugate cam wheel.

FIG. 4 is a plan view of the conjugate cam wheel.

FIG. 5 is a plan view of the conjugate cam wheel.

FIG. 6 is a plan view of the conjugate cam wheel.

FIG. 7 is a plan view of the conjugate cam wheel.

FIG. 8 is a plan view of the conjugate cam wheel.

FIG. 9 is a plan view of the conjugate cam wheel.

FIG. 10 is a plan view of the conjugate cam wheel.

FIG. 11 is a graph of planet or cam follower displacement, speed, and acceleration versus drum angle.

FIG. 12 is a plan view showing a cam path of the conjugate cam wheel.

[Explanation of symbols]

10 ... transfer device 15 ... holding plate 20 ... conjugate cam wheel 21 ... cam 22 ... cam
25 ... Cam tooth 28 ... Rotary transfer drive mechanism 30 ... Drum 30A ... Side 30B
… Side surface 32… main drive shaft 34… cam follower mechanism 35… transfer shaft 35A… end
35B ... End 36 ... Cam follower 38 ... Side 38 ... Cam follower plate 40 ... Transfer shaft 40 ... Transfer head 42 ... Guide plate 50 ... Transfer head path
52 ... shaft 55 ... path 200 ... conjugate cam wheel 201.205 ... individual components 202.206 ... interconnected articles 203 ... anvil roll 208 ... pickup head 209 ... drum

──────────────────────────────────────────────────続 き Continuation of front page (81) Designated country EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, IT, LU, MC, NL, PT, SE ), OA (BF, BJ, CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, GM, KE, LS, MW, SD, SL, SZ, UG, ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AL, AM, AT, AU, AZ, BA, BB, BG, BR , BY, CA, CH, CN, CU, CZ, DE, DK, EE, ES, FI, GB, GD, GE, GH, GM, HR, HU, ID, IL, IN, IS , JP, KE, KG, KP, KR, KZ, LC, LK, LR, LS, LT, LU, LV, MD, MG, MK, MN, MW, MX, NO, NZ, PL, PT, RO, RU, SD, SE, SG, SI, SK, SL, TJ, TM, TR, TT, UA, UG, UZ, VN, YU, ZA, ZW (71) Applicant ONE PROCTER & GANBLE PLAZA, CINCINNATI, OHIO, UNITED STATES OF AMERICA (72) Inventor Bridges, Russell Perth United States, 45230 Cincinnati, Bennett Wood Court, Ohio 696 (72) Inventor Droste, John Frederick United States, 45242 Cincinnati, Ohio, Linfield Drive 9541 (72) Inventor Hamilton, James Yu United States, Sandhegar Place 499, Cincinnati, Ohio 499 (72) Inventor Illago Lagoitia, Mayite, Venezuela, 1080 Caracas, Avenida Principal de la Tahona, P.H. 3, Residencia Las Tapias (no address) ) F-term (reference) 3F101 CA12 CC29 CD01 CE15

Claims (13)

[Claims] 1. A conjugate cam wheel that achieves a speed ratio in the range of 1: 1 to 1: 1 × 10 ⁴ for a pair of points separated by at least 45 degrees on the conjugate cam wheel, A first cam having a center point, outer perimeter, inner perimeter, and irregularly shaped teeth facing inward toward the center point, and a center cam, outer perimeter, inner perimeter, and inward facing toward the center point A second cam having irregularly shaped teeth, wherein the first cam and the second cam have irregularly shaped teeth facing inward toward the center point, the outer perimeter, the inner perimeter and the center point. The conjugate cam wheel is positioned close to each other to form a car, and the conjugate cam wheel accelerates between about 0 ° and about 180 ° around the outside and decelerates between about 180 ° and about 360 ° around the outside. Provides substantially discontinuous acceleration for irregularly shaped teeth configured to provide A transfer drive mechanism that provides a plurality of points of contact in picking up and transferring the substance and that operates with the conjugate cam wheel; a main drive shaft that drives the transfer drive mechanism; A rotatable drum having a second side opposed to one side and attached to and rotating about a main drive shaft passing through the center; and a drum opposing and penetrating the rotatable drum. At least two transfer shafts disposed proximate to the periphery, each transfer shaft including a first end and a second end, wherein the first end of each transfer shaft is positioned on a first side of the rotatable drum. And a second end of each rotatable shaft is located below a second side of the rotatable drum, and a first end of each transfer shaft above the first side of the rotatable drum. At least one transfer head positioned about the end and rotatable about each transfer axis, and a cam follower positioned about the second end of each transfer axis below the second side of the rotatable drum A knot mechanism,
Each cam follower mechanism includes a periphery, a cam follower plate having a first side and a second side opposite to the first side, at least two cam followers attached to each cam follower plate,
At least one cam follower is attached to a first side of the cam follower plate, and at least another cam follower is attached to a second side of the cam follower plate, and each cam follower mechanism includes one transfer shaft. A cam follower mechanism rotatable about the conjugate cam wheel so that the cam follower fits within the conjugate cam wheel and moves with respect to the irregularly shaped teeth of the conjugate cam. Fit,
A transfer device for transferring articles, characterized in that: 2. The method according to claim 1, wherein the first cam and the second cam are each about 6.0 inches to about 50 inches,
2. The transfer device of claim 1 including a small cam diameter preferably in the range of about 22 inches to about 28 inches. 3. The first and second cams each include a large cam diameter ranging from about 8.0 inches to about 64.0 inches, preferably from about 30 inches to about 34 inches.
Transfer equipment. 4. The transfer device of claim 1 wherein the first and second cams each include an outer diameter in a range from about 9 inches to about 72 inches, preferably from about 35 inches to about 37 inches. 5. The transfer device of claim 1, wherein the first cam and the second cam each include a cam width ranging from about 0.3125 inches to about 2.5 inches, preferably from about 0.25 inches to about 2.0 inches. 6. The transfer device of claim 1, wherein the first cam and the second cam each include a harmonic deviation in the range of approximately 100 degrees to 230 degrees. 7. The transfer device according to claim 1, wherein the speed ratio ranges from approximately 1: 1 to approximately 35: 1. 8. The transfer device of claim 1, wherein the rotatable drum includes a diameter that ranges from approximately 25 inches to approximately 28 inches. 9. The transfer device of claim 1, wherein the rotatable drum includes a thickness ranging from about 2 inches to about 5 inches. 10. The transfer device according to claim 1, wherein the transfer drive mechanism achieves a transfer time in a range of approximately 0 milliseconds to 10 seconds. 11. A pair of cam followers are attached to the first and second sides of the cam follower plate, each of the pairs of cam followers positioned 180 degrees from the other cam followers in the pair. The transfer drive mechanism according to claim 1, wherein 12. A cam follower mechanism wherein at least three cam followers are equidistantly spaced about the cam follower plate about a first side of the cam follower plate, and around a second side of the cam follower plate. At least 3 equidistantly spaced with respect to the cam follower plate
The transfer device of claim 1 including two cam followers. 13. The transfer device of claim 1, wherein the rotatable drum comprises a circle, a cross, a star, or a bar.