CA1172874A - Device for conversion of centrifugal force to linear force and motion - Google Patents
Device for conversion of centrifugal force to linear force and motionInfo
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- CA1172874A CA1172874A CA000366138A CA366138A CA1172874A CA 1172874 A CA1172874 A CA 1172874A CA 000366138 A CA000366138 A CA 000366138A CA 366138 A CA366138 A CA 366138A CA 1172874 A CA1172874 A CA 1172874A
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- pin
- axis
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Abstract
DEVICE FOR CONVERSION OF CENTRIFUGAL
FORCE TO LINEAR FORCE AND MOTION
A device to employ centrifugal force for use as linear motion utilizing a pair of counter rotating arms about a common axle. One arm contains a mass splitable and transferable to the other arm and back again at one hundred and eighty degree in-tervals. The device may include a surface travel system or two of such devices may be employed in tan-dem for any mode of travel.
FORCE TO LINEAR FORCE AND MOTION
A device to employ centrifugal force for use as linear motion utilizing a pair of counter rotating arms about a common axle. One arm contains a mass splitable and transferable to the other arm and back again at one hundred and eighty degree in-tervals. The device may include a surface travel system or two of such devices may be employed in tan-dem for any mode of travel.
Description
(1) BACKGROUND OF THE INVENTION
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 forth to reap the advantages of the power-ful and easily genera-ted centrifugal force by effecting a trasnformation into a linear force. For example, these apparatuses have rotated mass members and shifted the center of gravity relative to the axis of rotation. The result has been the development of a centrifugal force greater where the mass has shifted, than the remainder of the rotational cycle. In es-sence, the length of the radius of the arm has been changed. As is well known, the conservation of anyular momentum would tend to correspondingly decrease the speed of the mass shifted. As an example of a success-ful machine oE this type, reference is 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 iinear force for use in propell--ing vehicles such as automobiles, rail cars, and marine, avaiation, and space carriers, is desirable and would find extensive use in the transportaion industry.
The present invention achieves this goal by utilizing a first rotating arm which moves about an axis of rotation. A pair of balanced masses rotates h~
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 forth to reap the advantages of the power-ful and easily genera-ted centrifugal force by effecting a trasnformation into a linear force. For example, these apparatuses have rotated mass members and shifted the center of gravity relative to the axis of rotation. The result has been the development of a centrifugal force greater where the mass has shifted, than the remainder of the rotational cycle. In es-sence, the length of the radius of the arm has been changed. As is well known, the conservation of anyular momentum would tend to correspondingly decrease the speed of the mass shifted. As an example of a success-ful machine oE this type, reference is 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 iinear force for use in propell--ing vehicles such as automobiles, rail cars, and marine, avaiation, and space carriers, is desirable and would find extensive use in the transportaion industry.
The present invention achieves this goal by utilizing a first rotating arm which moves about an axis of rotation. A pair of balanced masses rotates h~
(2) . ~
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 co-operative 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 masses transfers causing cancellation of the centrifugal force produced by the first rotating arm. The mass again transfers from the second arm to the first arm after one hundred eight degrees of circular travel of both arms. At this point, -there is a centri~ugal force bias in favor of the arm having the masses which continues for another one hundred eighty degrees of arcuate travel, when compared to the prior semicircle traveled. In other words, the net result of the arm having the pair Oe masses 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,
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 co-operative 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 masses transfers causing cancellation of the centrifugal force produced by the first rotating arm. The mass again transfers from the second arm to the first arm after one hundred eight degrees of circular travel of both arms. At this point, -there is a centri~ugal force bias in favor of the arm having the masses which continues for another one hundred eighty degrees of arcuate travel, when compared to the prior semicircle traveled. In other words, the net result of the arm having the pair Oe masses 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,
(3) BRIEF DESCl~IPTION OF THE DRAWINGS
Figure i is a plan view of the device with the counter rotating arms 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 broken sectional view taken along line 3-3 of Figure 2, Figure 4 is a broken side elevational view of the mass transfer mechanism in the activated posi-tion.
Figure 5 is a broken sectional view taken along line 5-5 of Figure 4.
Figure 6 is a broken elevational view taken along line 6-6 oE Figure 4.
Figure 7 is a broken side elevational view of the mass transfer mechanism .in the deactivated ~, position.
Fi.gure 8 is a broken sectional view taken along line 8-8 of Figure 7.
Figure 9 is a broken sectional view taken along line 9-9 of Figure 7.
Figure lQ is a broken sectional view taken along line 10-10 of Figure 7.
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(~) E'igure ll is a fragmentary sectional view showing a pair of devices in side-by-side eonnection.
Figure 12 is a schematic view showing a pair of devices in side-by-side conneetion, with the con-necting leg in phantom.
2~74 (5) _SCRIPTION OF THE PREFERRED EMBODIMENTS
With reference to the drawings, the device or apparatus as a whole is depicted in its entirety by 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 takès place one hundred and eighty degrees (180) apart and these positions are denoted as the "tranfer points I ancl II", a uller explanation of which will be hereinafter provided.
In the present embodiment, the device 10 is contemplated ~or use on a surface, but the device may be employecl for any method of travel includinq travel in water, air and space media. As shown, the device 10 travels on a rail track 18 by the use of wheels rotat-ing about spin~les 22 that support frame 24, via forks 26, which are fixed by being attached to frame 24 and spindle 22. The frame 24 secures to axle 16 by the use of flange 28 by any suitable means, such as welding.
With reference to Figure 2, driving sha.ft 30 turns by the energy derived from any source of power (not shown~. Block portion 32 and bearings 34 support shaft 30 to allow smooth axial turning of the shaft, ~'7~.,B~
(6) well known in the art. Shaft 30 includes a miter gear 36, on the end nearest axle 16, which meshingly engages bevel gear 38 integral with bushing 40, which is free to slide about the bearing surface 52 circum-ferentially affixed to axle 16. Flanges 42 and 44 affix to arm 14 such that the rotation of bushing 40 rotates arm 14 about the axis of axle 16. The upper end of bushing 40 connects to bevel gear 46 which meshingly engages miter gear 48. Stud 50 fixedly engages axle 16 and bearing 54 circumscribes the stud 50. Miter gear 48, thus rotates about the fixed axis of stud 50. C-rings 56 and 58 prevent the movement of stud 50 and miter gear 48.
Bevel gear 60 meshingly engages miter gear 48 and rotates in the direction opposite to bevel gear 46. Flange 62, depicted as integral with bevel gear 60, a~ixes to arm 12 such that arm 12 rotates opposite to arm 1~.
One end of arm 12 includes a bearing mount 64 which circumferentially h~olds shaft 66. Pin 68 positions shaft 66 within bearing 64 which has a seal 70. Miter gear 72 affixes to shoulder 74 which surroundingly engages shaft 66. Miter gear 72 meshingly engages bevel gear 76 and turns shaft 66.
Flanges 78 and 80 join to hold bevel gear in a sta-tionary posltion with res~ect to miter gear 72.
StifEeners 82 and 84 strengthen the interconnection of flanges 78 and 80 to the frame 24.
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37~a (7) Universal joint 86 affixes shaft 66 to shaft 88 which passes through bearing moun-t 90.
Stub 92 a~fixes to base plate 9~ which secures to bearing mount 90. Stub 92 passes through an arcuate slot 96 in arm 12, best depicted in Fiugre 3; the purpose of which will be described in detail as the specification continues. The lower end of stub 92 is capped by washer 98 and nut 100. S~ub 92 may travel within the confines of arcuate slot 96 subject to dampening by spring 124.
Shaft 98 engages bearing 102 which fits within hub 104 having wings 106 and 1~8. Bars 110 and 112 affix to wings 106 and 108 respectively on one end and to masses 114 and 116 on the other end.
Masses 114 and 116 are preferably o~ equal size; mass and weight, therefore, balance one another when shaEt 88 rotates bars 110 and 112 (which are ecIual length) and the mas~es 114 and 116. The hub 104 also func-tions to dampen oscillations upon the transfer of one of the weights, as will be discussed in detail herein-a~ter. Arm 14 has a U-shaped channel 118 between par-titions 128 and 129 corresponding in the width dimen-sion to the width of mass 114 or 116. Opening 120 and 122 receive the fingers (not shown) of mass 11~ or the fingers ~f mass 116 (only exemplar finger 130 shown) dependent upon which mass is transferred from arm 12 to arm 14.
(8) Pin 132 rides on cam follower 134 which travels a flexible c1rcular cam on -track 136. Cam track 136 is supported by a plurality o~ blocks, including blocks 138, 140, 142, and 144. Bl~c~ok 140 includes an incline surface having a handle structure 144 thereattached, such that the circular ~rack 136 may be lowered to the same level at block 140 as it is at block 138.
The mechanism involved in the actual trans-fer of one of the masses 114 or 116 may be more clear-ly explained by Flgures 4 - 10. As an example, mass 116 may be employed, as depicted in phantom on Figure 2, as the transferred mass. Figure 4, showing ~he mechanism in the activated position, includes bar 112 haviny a plate 150 which fits into arcuate channel 152.
Bar 112 affixes to plate 150. The combination is capa-ble of holding weight 116 while revolving about hub 104. ~s depicted by Fi~ure 5, the pin, when elevated by the track 136, runs through partially V-shaped channel 154, The mass 116 includes two equal portions 156 and 158, each portion respectively enclosed by caps 160 and 162, having a slidable relationship therebe-tween. Finger 130 of mass portion 158 slides within openings 164 and into slot 120 when the mass 116 trans-fers from arm 12 to arm 14. Spring means 166 urges mass member 158 away from slot 120 while the movement ~2.,~
(9) of pin 132 in channel 154 urges mass member 158 toward slot 120. Mass portion 156 also lncludes a finger, spring means, and opening arrangement (not shown) identical to mass portion 158 such as finger 130, spring means 166, and opening 16~, for use wi-th opening 122 (Figure 2).
Pin 132 includes a slot 168 and a key 170 in :
arm 14 to prevent rotation of the pin 132 in the ver-tical plane during transfer of the mass 116. Mass 114 contains the same mechanism as mass 116 for the purposes of the transfer, from arm 12 to arm 14, and the masses be substituted freely to perform the trans-fer function to evenly distribute wear and tear and the like.
In operation, the device 1.0 has two counter rotating arms 12 and 14 that are synchronized to ver tically align at two positions within their ro~ation-al cycles, where either mass 114 or 116 transfers to and from the first arm 12. As heretofore explained, mass 116 has been arbitrarily chosen, but proper cali-bration may employ mass 114 in the transfer mechanism herein described.
Power from a source drives driving shaft 30 which turns miter gear 36 and bevel gear 38. Arm 14 affixed to bushing 40 rotates in a plane substantially hori~ontal to the axis of driving shaft 30. Bevel gear 46 turns mi-ter gear 48 which spins bevel gear 60.
~7~,~7~
(10~
Arm 12 attached to flange 62, integral with be~el gear 60, rotates in a plane parallel to the plane of arm 14 and in an opposite direction to the path of rotation of arm 14 through gearing arrangements arms 12 and 14 vertically align at "transfer point I and II", shown on Figure 1.
Miter gear 72 and bevel gear 76 rotate shaft 88 and turns massess 114 and 116 in a vertical plane as arm 12 rotates in a horizontal plane. At transfer point I, depicted in Figure 2, the mass 116 fits be-tween partitions 128 and 129, shown in phantom, of arm 14~ At this point, the mass 116 and end of arm 14 has no relative motion therebetween. Just prior to that point, pin 132 enters channel 154 because of the rise in track 136 and spreads portions 156 and 158 apart.
Fingers, shown by exemplar finger 130, enter openings 120 and 122, and bar 112 with affixed plate 150 ro-tates out of arcuate channel 152. q'hus, mass 116 has been transferrecl to arrn 14, Fiyures 4 - 6.
Arm 12 continues its rotation with only mass 114 for one hundred and eighty degrees to "transfer point II". It should be noted that hub 104 preferably dampens the oscillating motion proudced by mass 114 on the arm 12 by belng of a weight equal to the com-bined weight of masses 11~ and 116. Likewise, parti-tions 128 and 129 should be equal in weight to hub 104, such that the sum of the weight of masses 116 and p~rtitions 128 and 129 equals the sum of the ~7~7~
(11) weight hub 104 and 114. Thus, the device 10 is balanced during the portion of the cycle of arm 12 between the "transfer points I and II".
With~ reference to Figure 3, the stub 92 bears on spring 124 such that the oscillation force of mass 114 on arm 12 is dampened in one direction -to help smooth the motion of arm 12 as it rotatesO
When "transfer point II" is reached, the transfer mechanism reverses, Figures 7-10~ Pin 132 lowers from channel 154 because of the position of track 134. Fingers, shown by exemplar 130 remove from openings 120 and 122. Plate 150 engages portions 158 and 160, Fiugre 9, and mass 11~ again rotates on bar 112 with mass 116.
The mechanical components of device 10 may be sealed in a vacuum with shaft 30 ancl handle structure 1~8 extending therethrough to reduce the effect o~ air fri~tion on the rotatiny arms.
When arm 12 includes both masses 114 and 116 axle 16 received a force along arm 12. This specifi-cally occurs counterclockwise between "transfer point II" and "transfer point I". This linear force may be broken into two component forces, one in the direction of the arrow 172 and the other in a force horizontally disposed. The horizontal force, a deflecting force, is absorbed by the rigidity of rail track 18. Thus, device 10 moves along track 18 in the direction of the ':
~7~7~
(12) arxow 172. It should be noted that a plurality of pairs of arms identical to arms 12 and 14 may be placed on axle 16 to create a steady orce in the direction of arrow 172.
~he device 10 alone will produce a pulse force during the time arm 12 travels from transfer point II to transfer point I. The transferring mechanism may be deactivated by pulling handle mechanism 148 and therefore the lower portion of block 140. The sliding of the upper and lower portions of block 140 on surface 146, lower arm txack 136 such that pin 132 does not enter channel 154 and trans:Ee:rring of mass 116 does not occur. Similarly, the ra'sing of track 136 one hundred and eight degrees :Erom block 146 would travel in a direction opposite to arrow 1'72. In other words, raising the track 136 to activate pin 132 opposite block 140 would brake device 10 moving in the direction oE arrow 172 or cause device 10, at rest, to move in a direction opposi~e to arrow 172.
Device 10 may be used with an identical device to eliminate the need for rail track 18 and its equivalent.
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(13) 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 trans-fer point I on the first device and transfer point II
on the second device, Fiyures 11 and 12.
Figure i is a plan view of the device with the counter rotating arms 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 broken sectional view taken along line 3-3 of Figure 2, Figure 4 is a broken side elevational view of the mass transfer mechanism in the activated posi-tion.
Figure 5 is a broken sectional view taken along line 5-5 of Figure 4.
Figure 6 is a broken elevational view taken along line 6-6 oE Figure 4.
Figure 7 is a broken side elevational view of the mass transfer mechanism .in the deactivated ~, position.
Fi.gure 8 is a broken sectional view taken along line 8-8 of Figure 7.
Figure 9 is a broken sectional view taken along line 9-9 of Figure 7.
Figure lQ is a broken sectional view taken along line 10-10 of Figure 7.
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(~) E'igure ll is a fragmentary sectional view showing a pair of devices in side-by-side eonnection.
Figure 12 is a schematic view showing a pair of devices in side-by-side conneetion, with the con-necting leg in phantom.
2~74 (5) _SCRIPTION OF THE PREFERRED EMBODIMENTS
With reference to the drawings, the device or apparatus as a whole is depicted in its entirety by 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 takès place one hundred and eighty degrees (180) apart and these positions are denoted as the "tranfer points I ancl II", a uller explanation of which will be hereinafter provided.
In the present embodiment, the device 10 is contemplated ~or use on a surface, but the device may be employecl for any method of travel includinq travel in water, air and space media. As shown, the device 10 travels on a rail track 18 by the use of wheels rotat-ing about spin~les 22 that support frame 24, via forks 26, which are fixed by being attached to frame 24 and spindle 22. The frame 24 secures to axle 16 by the use of flange 28 by any suitable means, such as welding.
With reference to Figure 2, driving sha.ft 30 turns by the energy derived from any source of power (not shown~. Block portion 32 and bearings 34 support shaft 30 to allow smooth axial turning of the shaft, ~'7~.,B~
(6) well known in the art. Shaft 30 includes a miter gear 36, on the end nearest axle 16, which meshingly engages bevel gear 38 integral with bushing 40, which is free to slide about the bearing surface 52 circum-ferentially affixed to axle 16. Flanges 42 and 44 affix to arm 14 such that the rotation of bushing 40 rotates arm 14 about the axis of axle 16. The upper end of bushing 40 connects to bevel gear 46 which meshingly engages miter gear 48. Stud 50 fixedly engages axle 16 and bearing 54 circumscribes the stud 50. Miter gear 48, thus rotates about the fixed axis of stud 50. C-rings 56 and 58 prevent the movement of stud 50 and miter gear 48.
Bevel gear 60 meshingly engages miter gear 48 and rotates in the direction opposite to bevel gear 46. Flange 62, depicted as integral with bevel gear 60, a~ixes to arm 12 such that arm 12 rotates opposite to arm 1~.
One end of arm 12 includes a bearing mount 64 which circumferentially h~olds shaft 66. Pin 68 positions shaft 66 within bearing 64 which has a seal 70. Miter gear 72 affixes to shoulder 74 which surroundingly engages shaft 66. Miter gear 72 meshingly engages bevel gear 76 and turns shaft 66.
Flanges 78 and 80 join to hold bevel gear in a sta-tionary posltion with res~ect to miter gear 72.
StifEeners 82 and 84 strengthen the interconnection of flanges 78 and 80 to the frame 24.
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37~a (7) Universal joint 86 affixes shaft 66 to shaft 88 which passes through bearing moun-t 90.
Stub 92 a~fixes to base plate 9~ which secures to bearing mount 90. Stub 92 passes through an arcuate slot 96 in arm 12, best depicted in Fiugre 3; the purpose of which will be described in detail as the specification continues. The lower end of stub 92 is capped by washer 98 and nut 100. S~ub 92 may travel within the confines of arcuate slot 96 subject to dampening by spring 124.
Shaft 98 engages bearing 102 which fits within hub 104 having wings 106 and 1~8. Bars 110 and 112 affix to wings 106 and 108 respectively on one end and to masses 114 and 116 on the other end.
Masses 114 and 116 are preferably o~ equal size; mass and weight, therefore, balance one another when shaEt 88 rotates bars 110 and 112 (which are ecIual length) and the mas~es 114 and 116. The hub 104 also func-tions to dampen oscillations upon the transfer of one of the weights, as will be discussed in detail herein-a~ter. Arm 14 has a U-shaped channel 118 between par-titions 128 and 129 corresponding in the width dimen-sion to the width of mass 114 or 116. Opening 120 and 122 receive the fingers (not shown) of mass 11~ or the fingers ~f mass 116 (only exemplar finger 130 shown) dependent upon which mass is transferred from arm 12 to arm 14.
(8) Pin 132 rides on cam follower 134 which travels a flexible c1rcular cam on -track 136. Cam track 136 is supported by a plurality o~ blocks, including blocks 138, 140, 142, and 144. Bl~c~ok 140 includes an incline surface having a handle structure 144 thereattached, such that the circular ~rack 136 may be lowered to the same level at block 140 as it is at block 138.
The mechanism involved in the actual trans-fer of one of the masses 114 or 116 may be more clear-ly explained by Flgures 4 - 10. As an example, mass 116 may be employed, as depicted in phantom on Figure 2, as the transferred mass. Figure 4, showing ~he mechanism in the activated position, includes bar 112 haviny a plate 150 which fits into arcuate channel 152.
Bar 112 affixes to plate 150. The combination is capa-ble of holding weight 116 while revolving about hub 104. ~s depicted by Fi~ure 5, the pin, when elevated by the track 136, runs through partially V-shaped channel 154, The mass 116 includes two equal portions 156 and 158, each portion respectively enclosed by caps 160 and 162, having a slidable relationship therebe-tween. Finger 130 of mass portion 158 slides within openings 164 and into slot 120 when the mass 116 trans-fers from arm 12 to arm 14. Spring means 166 urges mass member 158 away from slot 120 while the movement ~2.,~
(9) of pin 132 in channel 154 urges mass member 158 toward slot 120. Mass portion 156 also lncludes a finger, spring means, and opening arrangement (not shown) identical to mass portion 158 such as finger 130, spring means 166, and opening 16~, for use wi-th opening 122 (Figure 2).
Pin 132 includes a slot 168 and a key 170 in :
arm 14 to prevent rotation of the pin 132 in the ver-tical plane during transfer of the mass 116. Mass 114 contains the same mechanism as mass 116 for the purposes of the transfer, from arm 12 to arm 14, and the masses be substituted freely to perform the trans-fer function to evenly distribute wear and tear and the like.
In operation, the device 1.0 has two counter rotating arms 12 and 14 that are synchronized to ver tically align at two positions within their ro~ation-al cycles, where either mass 114 or 116 transfers to and from the first arm 12. As heretofore explained, mass 116 has been arbitrarily chosen, but proper cali-bration may employ mass 114 in the transfer mechanism herein described.
Power from a source drives driving shaft 30 which turns miter gear 36 and bevel gear 38. Arm 14 affixed to bushing 40 rotates in a plane substantially hori~ontal to the axis of driving shaft 30. Bevel gear 46 turns mi-ter gear 48 which spins bevel gear 60.
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(10~
Arm 12 attached to flange 62, integral with be~el gear 60, rotates in a plane parallel to the plane of arm 14 and in an opposite direction to the path of rotation of arm 14 through gearing arrangements arms 12 and 14 vertically align at "transfer point I and II", shown on Figure 1.
Miter gear 72 and bevel gear 76 rotate shaft 88 and turns massess 114 and 116 in a vertical plane as arm 12 rotates in a horizontal plane. At transfer point I, depicted in Figure 2, the mass 116 fits be-tween partitions 128 and 129, shown in phantom, of arm 14~ At this point, the mass 116 and end of arm 14 has no relative motion therebetween. Just prior to that point, pin 132 enters channel 154 because of the rise in track 136 and spreads portions 156 and 158 apart.
Fingers, shown by exemplar finger 130, enter openings 120 and 122, and bar 112 with affixed plate 150 ro-tates out of arcuate channel 152. q'hus, mass 116 has been transferrecl to arrn 14, Fiyures 4 - 6.
Arm 12 continues its rotation with only mass 114 for one hundred and eighty degrees to "transfer point II". It should be noted that hub 104 preferably dampens the oscillating motion proudced by mass 114 on the arm 12 by belng of a weight equal to the com-bined weight of masses 11~ and 116. Likewise, parti-tions 128 and 129 should be equal in weight to hub 104, such that the sum of the weight of masses 116 and p~rtitions 128 and 129 equals the sum of the ~7~7~
(11) weight hub 104 and 114. Thus, the device 10 is balanced during the portion of the cycle of arm 12 between the "transfer points I and II".
With~ reference to Figure 3, the stub 92 bears on spring 124 such that the oscillation force of mass 114 on arm 12 is dampened in one direction -to help smooth the motion of arm 12 as it rotatesO
When "transfer point II" is reached, the transfer mechanism reverses, Figures 7-10~ Pin 132 lowers from channel 154 because of the position of track 134. Fingers, shown by exemplar 130 remove from openings 120 and 122. Plate 150 engages portions 158 and 160, Fiugre 9, and mass 11~ again rotates on bar 112 with mass 116.
The mechanical components of device 10 may be sealed in a vacuum with shaft 30 ancl handle structure 1~8 extending therethrough to reduce the effect o~ air fri~tion on the rotatiny arms.
When arm 12 includes both masses 114 and 116 axle 16 received a force along arm 12. This specifi-cally occurs counterclockwise between "transfer point II" and "transfer point I". This linear force may be broken into two component forces, one in the direction of the arrow 172 and the other in a force horizontally disposed. The horizontal force, a deflecting force, is absorbed by the rigidity of rail track 18. Thus, device 10 moves along track 18 in the direction of the ':
~7~7~
(12) arxow 172. It should be noted that a plurality of pairs of arms identical to arms 12 and 14 may be placed on axle 16 to create a steady orce in the direction of arrow 172.
~he device 10 alone will produce a pulse force during the time arm 12 travels from transfer point II to transfer point I. The transferring mechanism may be deactivated by pulling handle mechanism 148 and therefore the lower portion of block 140. The sliding of the upper and lower portions of block 140 on surface 146, lower arm txack 136 such that pin 132 does not enter channel 154 and trans:Ee:rring of mass 116 does not occur. Similarly, the ra'sing of track 136 one hundred and eight degrees :Erom block 146 would travel in a direction opposite to arrow 1'72. In other words, raising the track 136 to activate pin 132 opposite block 140 would brake device 10 moving in the direction oE arrow 172 or cause device 10, at rest, to move in a direction opposi~e to arrow 172.
Device 10 may be used with an identical device to eliminate the need for rail track 18 and its equivalent.
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(13) 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 trans-fer point I on the first device and transfer point II
on the second device, Fiyures 11 and 12.
Claims (11)
1. A device for the conversion of centrifugal force to linear force and motion comprising:
a. first arm rotating in a circular path about an axis producing centrifugal force on the axis;
b. a second arm rotating in a circular path about the axis of said first arm in a direction opposite to said first arm at a rotational speed equal to said first arm;
c. mass positioned at the end of said first arm;
d. means for transferring a portion of said mass from the end of said first arm to the end of the second arm and vice versa at two selected points in the rota-tional path of said arms spaced by one hundred eighty deg-rees, thus producing an imbalanced centrifugal force on the axis during one hundred eighty degrees of the circular path of said first arm;
e. means for cancelling a component of the im-balanced centrifugal force.
a. first arm rotating in a circular path about an axis producing centrifugal force on the axis;
b. a second arm rotating in a circular path about the axis of said first arm in a direction opposite to said first arm at a rotational speed equal to said first arm;
c. mass positioned at the end of said first arm;
d. means for transferring a portion of said mass from the end of said first arm to the end of the second arm and vice versa at two selected points in the rota-tional path of said arms spaced by one hundred eighty deg-rees, thus producing an imbalanced centrifugal force on the axis during one hundred eighty degrees of the circular path of said first arm;
e. means for cancelling a component of the im-balanced centrifugal force.
2. the device of Claim 1 in which said mass positioned at the end of said first arm comprises a first mass and a second equivalent mass, each mass located respectively on a first and second bar equidistant from the end of said first arm, at least one of said masses detachably connected to the corresponding bar (15) for transfer to said second arm, said masses rotating in a plane substantially perpendicular to the planes of rotation of said first and second arms.
3. The device of Claim 2 in which said second arm includes a pair of partitions having a pair of opposed slots, said transferable mass having a pair of moveable fingers insertable in said pair of slots during transfer of said mass from said first arm to said to said second arm and said fingers being retractable during transfer of said mass from said first arm to said second arm.
4. The device of Claim 3 in which said second arm includes a cam operated pin, a portion of which is insertable in a channel within said transferable mass, said insertion of said pin causing insertion of said pair of moveable fingers in said pair of opposed slots and detachment of said bar from said transferable mass and retraction of said pin pin said channel causes retraction of said fingers and attachment of said bar.
5. The device of Claim 4 in which said cam operated pin includes a cam follower at the end opposite the insertable portion of said pin and a cam track, said cam follower engaging the surfacd of said cam track , said cam track causing said pin to insert in and retract from said channel.
6. The device of Claim 1 in which the transfer of a portion of said mass takes place where there is no (16) relative motion between said mass portion and said second arm.
7. The device of Claim 6 in which said mass positioned at the end of said first arm comprises a first mass and a second equivalent mass, each mass located respectively on a first and second bar equidistant from the end of said first arm, at least one of said masses detachably connected to the corresponding bar for transfer to said second arm, said masses rotating in a plane substantially perpendicular to the planes of rotation of said first and second arms.
8. The device of Claim 7 in which said second arm includes a pair of partitions having a pair of opposed slots, said transferable mass having a pair of moveable fingers insertable in said pair of slots during transfer of said mass from said first arm to said second arm and said fingers being retractable during transfer of said mass from said first arm to said second arm.
9. The device of Claim 8 in which said second arm includes a cam operated pin, a portion of which is insertable in a channel within said transferable mass, said insertion of said pin causing insertion of said pair of moveable fingers in said pair of opposed slots and detachment of said bar from said transferable mass and retraction of said pin from said channel causes retraction of said fingers and attachment of said bar.
(17)
(17)
10. The device of Claim 9 in which said cam operated pin includes a cam follower at the end opposite the insertable portion of said pin and a cam track, said cam follower engaging the surface of said cam track, said cam track causing said pin to insert in and retract from said channel.
11. A device for conversion of centrifugal force to linear force andmotion comprising a pair of apparatuses, each having:
a. first arm rotating in a circular path about an axis producing centrifugal force on the axis;
b. a second arm rotating in a circular path about the axis of said first arm in a direction oppo-site to said first arm at a rotational speed equal to said first arm;
c. mass positioned at the end of said first arm;
d. 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;
e. and a connecting leg rigidly attached to the axis of rotation of each of said apparatuses, the linear direction of movement of said device being in a direction perpendicular to axis of said leg.
a. first arm rotating in a circular path about an axis producing centrifugal force on the axis;
b. a second arm rotating in a circular path about the axis of said first arm in a direction oppo-site to said first arm at a rotational speed equal to said first arm;
c. mass positioned at the end of said first arm;
d. 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;
e. and a connecting leg rigidly attached to the axis of rotation of each of said apparatuses, the linear direction of movement of said device being in a direction perpendicular to axis of said leg.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000366138A CA1172874A (en) | 1980-12-04 | 1980-12-04 | Device for conversion of centrifugal force to linear force and motion |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000366138A CA1172874A (en) | 1980-12-04 | 1980-12-04 | Device for conversion of centrifugal force to linear force and motion |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1172874A true CA1172874A (en) | 1984-08-21 |
Family
ID=4118634
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000366138A Expired CA1172874A (en) | 1980-12-04 | 1980-12-04 | Device for conversion of centrifugal force to linear force and motion |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1172874A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115096644A (en) * | 2022-06-28 | 2022-09-23 | 山东省煤田地质局第三勘探队 | Geological exploration data acquisition device |
-
1980
- 1980-12-04 CA CA000366138A patent/CA1172874A/en not_active Expired
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115096644A (en) * | 2022-06-28 | 2022-09-23 | 山东省煤田地质局第三勘探队 | Geological exploration data acquisition device |
| CN115096644B (en) * | 2022-06-28 | 2023-01-13 | 山东省煤田地质局第三勘探队 | Geological exploration data acquisition device |
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