GB2078351A - Device for conversion of centrifugal force to linear force - Google Patents

Abstract

A device (10) which converts centrifugal force to linear force comprises a pair of arms (12, 14) counter rotating about a common axle. One arm carries a mass in the form of two weights (114, 116) one of which is transferable to the other arm and back again at one hundred and eighty degree intervals where the arms pass each other as at points I and II. As a result the centrifugal force of the mass is converted to linear force which will move the device (10), for example in the direction of the arrow (172) along rails (18). Two of the devices (10) may be employed in tandem to create a steadier force in the direction of the arrow (172). <IMAGE>

Description

SPECIFICATION Device for conversion of centrifugal force to linear force and motion The present invention relates to a device for the conversion of centrifugal force to linear force and, therefore, linear motion.

In the past, various attempts have been put forward to reap the advantages of the powerful and easily-generated centrifugal force by effecting a transformation into a linear force. For example, these apparatuses have rotated mass members and shifted the centre of gravity relative to the axis of rotation. The result has been the development of a centrifugal force which is greater where the mass has shifted than in the remainder of the rotational cycle. In essense, the length of the radius of the arm has been changed. As is well known, the conservation of angular momentum would tend correspondingly to decrease the speed of the mass shifted. As an example of a successful machine of this type, reference is to be made to United States Patent No.

3,683,707 issued on August 15, 1972 to Robert Cook.

An efficient device for converting centrifugal force to a linear force for use in propelling vehicles such as automobiles, rail cars, and marine, aviation, and space carriers, is desirable and would find extensive use in the transportation industry.

The present invention achieves this goal by providing a device for conversion of centrifugal force to linear force and motion comprising a first arm adapted to rotate in a circular path about an axis to produce centrifugal force on the axis, a second arm adapted to rotate in a circular path about the axis of said first arm in a direction opposite to that of the first arm at a rotational speed equal to that of said first arm, a mass positioned at or near the end of said first arm, means for transferring a portion of said mass from the end of said first arm to the end of said second arm and vice versa at two selected points in the rotational path of said arms spaced by one hundred eighty degrees, thus producing an imbalanced centrifugal force on the axis during one hundred eighty degrees of the circular path of said first arm, and means for cancelling a component of the imbalanced centrifugal force.

A preferred embodiment utilizes a first rotating arm which moves about an axis of rotation. A pair of balanced weights rotates at the terminus of the arm in a plane perpendicular to the plane of the first arm.

A second arm counter-rotates about the same axis with respect to the first rotating arm and moves within a plane parallel to the plane of rotation of the first arm. A mechanism cooperative between the first and second arms permits the transfer of one of the balanced weights from the first arm to the second arm. At a selected point in the rotational path of both arms, one of the weights transfers, causing cancellation of the centrifugal force produced by the first rotating arm. The weight again transfers from the second arm to the first arm after one hundred and eighty degrees of circular travel of both arms. At this point, there is a centrifugal force bias in favour of the arm having the weights, which continues for another one hundred and eighty degrees of arcuate travel, when compared to the prior semi-circle travelled.In other words, the net result of the arm having the pair of weights is an imbalanced centrifugal force during half of the circular path of both arms.

The resultant imbalance may be transmitted into a linear uni-directional component of force by mounting both rotating arms on a rail or frictional wheel carriage.

The invention will be described further, by way of example, with reference to the accompanying drawings, in which: Figure 1 is a plan view of a preferred embodiment of the device of the invention, with the counter rotating arms thereof shown in phantom at the transfer points; Figure 2 is a sectional view taken along line 2-2 of Figure 1; Figure 3 is a fragmentary sectional view taken along line 3-3 of Figure 2; Figure 4 is a fragmentary sectional side elevational view of the mass transfer mechanism in the activated position; Figure 5 is a fragmentary sectional view taken along line 5-5 of Figure 4; Figure 6 is a fragmentary sectional view taken along line 6-6 of Figure 4; Figure 7 is a fragmentary side elevational view of the mass transfer mechanism in the deactivated position; Figure 8 is a fragmentary sectional view taken along line 8-8 of Figure 7;; Figure 9 is a fragmentary sectional view taken along line 9-9 of Figure 7; Figure 10 is a fragmentary sectional view taken along line 10-10 of Figure 7; Figure ii is a sectional view with parts cut away, showing a pair of devices in side-by-side connection; and Figure 12 is a schematic plan view showing the pair of devices in side-by-side connection, with the connecting leg in phantom lines.

The illustrated embodiment of the device of the invention is depicted in its entirety by the reference character 10. Figure 1 shows the device 10 which includes a first arm 12 and a second arm 14 which counter rotate with respect to one another about an axle 16, Figures 1 and 2. The circular paths of the arms 12 and 14 lie in parallel planes such that the arms are positioned in overlying alignment twice during the rotational cycle of both arms 12 and 14.

As shown by Figure 1, in partial phantom, the alignment of the two arms takes place one hundred and eighty degrees (180 ) apart and these positions are denoted as the "transfer points land 11", a fuller explanation of which will be hereinafter provided.

In the present embodiment, the device 10 is contemplated for use on a surface, but the device may be employed for any method of travel including travel in water, air and space media. As shown, the device 10 travels on a rail track 18 by the use of wheels 20 rotating about spindles 22 (Figure 2) that support a frame 24 via forks 26 which are fixed by being attached to the frame 24 and the spindles 22.

The frame 24 has axle 16 secured thereto by the use of a flange 28 by any suitable means, such as welding.

With reference to Figure 2, a driving shaft 30 is turned by the energy derived from any source of power (not shown). A block portion 32 and bearings 34 support the driving shaft 30 to allow smooth axial turning of the shaft 30, well known in the art. The shaft 30 includes a mitre gear 36 on its end nearest the axle 16, which gear 36 meshingly engages a bevel gear 38 integral with a bushing 40 which is free to slide about a bearing surface 52 circumferentially affixed to the axle 16. Flanges 42 and 44 are affixed to the second arm 14 such that rotation of the bushing 40 rotates the arm 14 about the axis of the axle 16. The upper end of the bushing 40 connects to a bevel gear 46 which meshingly engages a mitre gear 48. A stud 50 fixedly engages the axle 16 and a bearing 54 circumscribes the stud 50.The mitre gear 48 thus rotates about the fixed axis of the stud 50.

C-rings 56 and 58 prevent the movement of the stud 50 and the mitre gear 48.

A bevel gear 60 meshingly engages the mitre gear 48 and rotates in a direction opposite to the bevel gear 46. A flange 62, depicted as integral with the bevel gear 60, is affixed to the first arm 12 such that the arm 12 rotates oppositely to the arm 14.

One end of the first arm 12 includes a bearing mount 64 which circumferentially holds a shaft 66. A pin 68 positions the shaft 66 within the bearing mount 64, which has a seal 70. A mitre gear 72 is affixed to a shoulder 74 which surroundingly engages the shaft 66. The mitre gear 72 meshingly engages a bevel gear 76 and turns the shaft 66.

Flanges 78 and 80 join to hold the bevel gear 76 in a stationary position with respect to the mitre gear 72.

Stiffeners 82 and 84 strengthen the interconnection of the flanges 78 and 80 to the frame 24.

A universal joint 86 fixes the shaft 66 to a shaft 88 which extends through a bearing mount 90. A stub 92 is affixed to a base plate 94 which is secured to a bearing mount 90. The stub 92 extends through an arcuate slot 96 in the first arm 12, best depicted in Figure 3, the purpose of which will be described in detail as the specification continues. The lower end of the stub 92 is capped by a washer 98 and a nut 100. The stub 92 may move within the confines of the arcuate slot 96, subject to damping by a spring 124.

The shaft 88 engages a bearing 102 which fits within a hub 104 having wings 106 and 108. Bars 110 and 112 are affixed to the wings 106 and 108 respectivelyon one end and to weights 114and 116 on the otherend. The weights 114 and 116are preferably of equal size; mass and weight, therefore, balance one another when the shaft 88 rotates the bars 110 and 112 (which are of equal length) and the weights 114 and 116. The hub 104 also functions to damp oscillations upon the transfer of one of the weights, as will be discussed in detail hereinafter.

The second arm 14 has a U-shaped channel 118 between partitions 128 and 129 corresponding in the width dimension to the width of the weight 114 or 116. Openings 120 and 122 receive respective fingers (not shown) of the weight 114 or fingers of the weight 116 (only exemplary finger 130 is shown in Figure 4) dependent upon which weight is transferred from the arm 12to the arm 14.

A pin 132 rides on a cam follower 134 which travels a flexible circular cam track 136. This cam track 136 is supported by a plurality of blocks, including blocks 138, 140, 142 and 144. The block 140 includes an incline surface having a handle structure 148 attached thereto such that the circular track 136 may be lowered to the same level at block 140 as it is at block 138.

The mechanism involved in the actual transfer of one ofthe weights 114 or 116 may be more clearly explained by Figures 4 to 10. As an example, the weight 116 may be employed, as depicted in phantom lines in Figure 2, as the transferred weight.

Figure 4, showing the mechanism in the activated position, includes the bar 112 having a having a plate 150 which fits into an arcuate channel 152. The bar 112 is affixed to the plate 150. This combination is capable of holding the weight 116 while revolving aboutthe hub 104. As depicted by Figure 5, the pin 132, when elevated bythetrack 136, runs through a partialiy V-shaped channel 154.

The weight 116 includes two equal portions 156 and 158, each said portion respectively being enclosed by caps 160 and 162 having a slidable relationship therebetween. The finger 130 of the weight portion 158 slides within openings 164 and into the opening 120 when the weight 116 transfers from the arm 12 to the arm 14. Spring means 166 urges the weight portion 158 away from the opening 120 while the movement of the pin 132 in the channel 154 urges the weight portion 158 towards the opening 120. The weight portion 156 also includes a finger, spring means, and opening arrangement (not shown) identical to those of the weight portion 158, that is to say the finger 130, the spring means 166 and the opening 164, for use with the opening 122 (Figure 2).

The pin 132 includes a slot 168 and a key 170 in the second arm 14 to prevent rotation of the pin 132 in the vertical plane during transfer of the weight 116.

The weight 114 contains the same mechanism as the weight 116 for the purpose of transfer from the arm 12 to the arm 14, and to permit the weights be substituted freely to perform the transfer function, thereby evenly to distribute wear and tear.

In operation, the device 10 has the two arms 12 and 14 counter-rotating and synchronized to align vertically at two positions within their rotational cycles, where either the weight 114 or the weight 116 transfers to and from the first arm 12. As heretofore explained, the weight 116 has been arbitrarily chosen, but proper calibration may employ the weight 114 in the transfer mechanism herein described.

Power from a source drives the driving shaft 30 which turns the mitre gear 36 and the bevel gear 38.

The second arm 14 affixed to the bushing 40 rotates in a plane substantially horizontal to the axis of the driving shaft 30. The bevel gear 46 turns the mitre gear 48 which rotates the bevel gear 60. The first arm 12, attached to the flange 62 integral with the bevel gear 60, rotates in a plane parallel to the plane of the second arm 14 and in an opposite direction to the path of rotation of the arm 14 through gearing arrangements the arms 12 and 14 vertically align at the transfer points I and II shown in Figure 1.

The mitre gear 72 and the bevel gear 76 rotate the shaft 88 and turn the weights 114 and 116 in a vertical plane as the arm 12 rotates in a horizontal plane. At the transfer point I, depicted in Figure 2, the weight 116 fits between the partitions 128 and 129, shown in phantom of the arm 14. At this point, the weight 116 and the end of the arm 14 has no relative motion there-between. Just prior to that point, the pin 132 enters the channel 154 because of the rise in the cam track 136 and spreads the weight portions 156 and 158 apart. Fingers, corresponding to the exemplary finger 130, enter the openings 120 and 122, and the bar 112 with its affixed plate 150 rotates out of the arcuate channel 152. Thus, the weight 116 has been transferred to the arm 14, Figures 4to 6.

The arm 12 continues its rotation with only the weight 114forone hundred and eighty degrees to the transfer point II. It should be noted that the hub 104 preferably damps any oscillating motion pro duced bytheweight 114On the arm 12 by being of a weight equal to the combined weight of the weights 114 and 116. Likewise, the partitions 128 and 129 should be equal in weight to the hub 104 such that the sum of the weight of the weight 116 and partitions 128 and 129 equals the sum of the hub 104 and the weight 114. Thus, the device 10 is balanced during the portion of the cycle of the arm 12 between the transfer points I and II.

With reference to Figure 3, the stub 92 bears on the spring 124 such that any oscillation force of the weight 114 on the arm 12 is damped in one direction to help smooth the motion of the arm 12 as it rotates.

When the transfer point II is reached, the transfer mechanism reverses, Figures 7 to 10. The pin 132 lowers from the channel 154 because of the position of the track 134. Fingers, corresponding to the example 130, withdraw from the openings 120 and 122. The plate 150 engages the portions 158 and 160, Figure 9, and the weight 114 again rotates on the bar 112 with the weight 1 16., The mechanical components of the device 10 may be sealed in a vacuum with the shaft 30 and the handle structure 148 extending therethrough to reduce the effect of air friction on the rotating arms 12and 14.

When the arm 12 includes both weights 114 and 116, the axle 16 receives a force along the arm 12.

This specifically occurs counterclockwise between the transfer point II and the transfer point I. This linear force may be resolved into two component forces, one in the direction of arrow 172 (Figure 1) and the other in a horizontally-disposed direction.

The horizontal force, which is a deflecting force, is absorbed by rigidity of the rail track 18. Thus, the device 10 moves along the track 18 in the direction of the arrow 172. It should be noted that a plurality of pairs of arms identical to the arms 12 and 14 may be provided on the axle 16 to create a steady force in the direction of the arrow 172.

The device 10 alone will produce a pulse force during the time the arm 12 travels from the transfer point II to the transfer point I. The transferring mechanism may be deactivated by pulling the handle mechanism 148 and therefore the lower portion of the block 140. The sliding of the upper and lower portions of the block 140 on surface 146 serves to lower the cam track 136 such that the pin 132 does not enter the channel 154 and transferring of the weight 116 does not occur. Similarly, the raising of the track 136 at a position one hundred and eighty degrees from the block 140 would reverse the transfer mechanism such that the device 10 would travel in a direction opposite to the arrow 172.In other words, raising of the track 136 to activate the pin 132 opposite the block 140 would brake the device 10 when it is moving in the direction of the arrow 172 or will cause the device 10, when at rest, to start moving in a direction opposite to the arrow 172.

The device 10 may be used with an identical said device to eliminate the need for the rail track 18 or its equivalent. Applicant hereby incorporates, by reference, the specification of his United States Patent No. 3,683,707 issued August 15, 1972, wherein applicant describes the cancellation of horizontal forces. In particular, column 8, lines 9-38, describes the resolution of force in the Y axis and cancellation of the forces in the X axis.

By analogy, a set of devices identical to device 10 may be placed together, preferably side-by-side, with a leg 174 connecting identical axles 16 such that identical arms 12 are located at the transfer point Ion the first device and transfer point II on the second device, Figures 11 and 12.

Claims (8)

1. A device for conversion of centrifugal force to linear force and motion comprising a first arm adapted to rotate in a circular path about an axis to produce centrifugal force on the axis, a second arm adapted to rotate in a circular path about the axis of said first arm in a direction opposite to that of the first arm at a rotational speed equal to that of said first arm, a mass positioned at or near the end of said first arm, means for transferring a portion of said mass from the end of said first arm to the end of said second arm and vice versa at two selected points in the rotational path of said arms spaced by one hundred eighty degrees, thus producing an imbalanced centrifugal force on the axis during one hundred eighty degrees of the circular path of said first arm, and means for cancelling a component of the imbalanced centrifugal force.

2. A device as claimed in Claim 1 in which the mass comprises a first weight and a second equivalent weight located respectively on a first and second bar equidistant from the end of said first arm, at least one of said weights being detachably connected to the corresponding bar for transfer to the second arm, and said weights rotating in a plane substantially perpendicular to the planes of rotation of the first and second arms.

3. A device as claimed in Claim 2 in which the second arm includes a pair of partitions having a pair of opposed slots, the transferable weight having a pair of movable fingers engageable in said pair of slots during transfer of the said weight from the first arm to the second arm, these fingers being retractable for transfer of said weight from the first arm to the second arm.

4. A device as claimed in Claim 3 in which the second arm includes a cam operated pin, a portion of which is insertable in a channel within the transferable weight, insertion of the pin causing engagement of the pair of movable fingers into the pair of opposed slots and detachment of the bar from the transferable weight, retraction of the pin from the channel causing retraction of the fingers and attachment of the bar.

5. A device as claimed in Claim 4 in which the cam operated pin includes a cam follower at the end opposite the insertable portion of said pin, said cam follower engaging a surface of a cam track which causes said pin to enter in and retract from said channel.

6. A device as claimed in any preceding claim in which transfer of a portion of the mass takes place where there is no relative motion between said mass portion and the second arm.

7. An assemblyforconversion of centrifugal force to linear force and motion comprising a pair of devices as claimed in any preceding claim, with a connecting leg rigidly attached to the axes of rotation of each of said devices, the linear direction of movement of the assembly being in a direction perpendicular to axis of said leg.

8. A device for conversion of centrifugal force to linear force and motion substantially as hereinbefore described with reference to and illustrated in the accompanying drawings.