Note: Descriptions are shown in the official language in which they were submitted.
374
(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
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(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,
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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,
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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
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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.
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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
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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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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
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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
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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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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.
