INFINITELY VARIABLE TRANSMISSION WITH UNIFORM INPUT-TO-OUTPUT RATIO THAT IS NON-DEPENDENT ON FRICTION

TRANSMISSION A VARIATION INFINIE A RAPPORT ENTREE-SORTIE UNIFORME QUI N'EST PAS DEPENDANTE DU FROTTEMENT

English Abstract

The present disclosure is an infinitely variable transmission that is non-dependent on friction. It can be used in high torque applications, offering a steady and uniform output for a steady and uniform input. Since it allows a co-axial input and output, by using a planetary gear system the output can be made continuous from forward to reverse. It uses a "scotch-yoke" mechanism to convert rotational motion to a linear reciprocating motion. The linear distance of this reciprocating motion - "stroke" is changed by altering the crankpin location of the scotch -yoke mechanism. This reciprocating motion is converted to a rocking motion by using a "rack and pinion" and later converted to a unidirectional motion via a One- Way-Bearing. Sets of Geneva wheel system are used to achieve a steady and uniform output, along with gear systems employing a simple mechanism to change the ratio between the input and output of the transmission.

French Abstract

La présente invention est une transmission à variation infinie qui n'est pas dépendante du frottement. Elle peut être utilisée dans des applications à couple élevé, offrant une sortie stable et uniforme pour une entrée stable et uniforme. Comme elle permet une entrée et une sortie coaxiales, à l'aide d'un système d'engrenage planétaire, la sortie peut être rendue continue de l'avant vers l'arrière. Elle utilise un mécanisme "bielle-manivelle" pour convertir un mouvement de rotation en un mouvement de va-et-vient linéaire. La distance linéaire de ce mouvement de va-et-vient - "course" - est changée par modification de l'emplacement du maneton du mécanisme bielle-manivelle. Ce mouvement de va-et-vient est converti en un mouvement de balancement par une "crémaillère" et converti ultérieurement en un mouvement unidirectionnel par un palier unidirectionnel. Des ensembles de système à croix de malte sont utilisés pour obtenir une sortie stable et uniforme, conjointement avec des systèmes d'engrenage employant un mécanisme simple pour modifier le rapport entre l'entrée et la sortie de la transmission.

Claims

1
CLAIMS:
1. An infinitely variable transmission comprising:
one or more driving Geneva pin wheels mounted on an input shaft, operably
connected to one or more
driven Geneva slot wheels each operably connected to rotate an input disk of a
scotch yoke mechanism,
causing a crank pin of the scotch yoke mechanism, placed at an offset distance
to an axis of rotation of the
input disk where the offset distance can be altered from 0 to a real value
using an external force, to revolve
around the axis of rotation of the input disk, which reciprocates one or more
racks, which are restricted to only
move along the rack's pitch line and each rack rocks a pinion comprising a one
way bearing that is mounted
on a hollow output shaft that is co-axially placed with the input shaft,
wherein the input shaft passes
completely through the output shaft.
2. An infinitely variable transmission comprising:
A) at least one scotch yoke module comprising:
a. a crank pin revolving around
b. a notched input shaft, at an offset distance between a longitudinal
axes of the crank pin and
the auxiliary input shaft that remain parallel to each other, and the offset
distance that can
be altered when the crank pin is co-axial to the auxiliary input shaft from
zero to a non-zero
real number by displacing the crank pin along a radial slot of
c. an input disk rigidly mounted on the input shaft, by
B) a crank pin displacement mechanism comprising:
a. a sliding collar disposed co-axially with the auxiliary input shaft with a
feature preventing
relative angular displacement while allowing relative translation,
b. a link assembly comprising
i. a link pivoting the crank pin through the notch
ii. a crank pin pivot pin on one end and pivoting the sliding collar about
iii. a sliding collar pivot pin on another end of the link,
c. at least one thrust bearing that is co-axially placed in contact with the
sliding collar, such that
an external force applied on the thrust bearing causing an axial displacement
of the thrust
bearing along with the sliding collar with respect to the auxiliary input
shaft, alters the offset
distance by moving the crank pin along the radial slot of the input disk,
d. a slotted rack holder comprising one or more racks, which is restricted to
only move along a
direction of the longitudinal axis of the one or more racks, and a crank pin
slot for receiving
the crank pin, with a longitudinal axis of the crank pin slot orthogonal to
the one or more
racks,
C) at least one angular velocity module comprising:

2
a. an input shaft,
b. one or more driving Geneva pin wheels mounted on the input shaft and
driving
c. at least one driven Geneva slot wheel each rotating the input shaft
D) at least one rectifier module comprising:
a. a pinion engaged with the rack, and mounted on
b. a pinion shaft through
c. a computer-controlled clutch, a one-way clutch or a ratchet mechanism
arranged such that a uniform rotation of the driving Geneva pin wheel via the
input shaft, causes a non-
uniform angular velocity of the input shaft via the driven Geneva slot wheel
and the planetary gear system,
causing the crank pin to reciprocate the rack substantially along a
longitudinal direction of the rack at a
substantially constant velocity and slowing down briefly during direction
reversal and accelerating to the
constant velocity, where a magnitude of the reciprocation is proportional to
the offset distance of the crank pin
and the auxiliary input shaft, and this reciprocation of the rack causes an
alternating rotation of the pinion and
this alternating rotation of the pinion is converted to a unidirectional
rotation of the pinion shaft via the
computer-controlled clutch, the one-way clutch or the ratchet mechanism.
3. The infinitely variable transmission of claim 2, wherein the feature
preventing relative angular displacement
while allowing relative translation between the sliding collar and the
auxiliary input shaft is further defined as
one of the co-axially placed sliding collar or the auxiliary input shaft
having a non-circular cross section and
the other of the sliding collar and the auxiliary input shaft having a non-
circular orifice matching the non-
circular cross section.
4. Currently Amended) A infinitely variable transmission comprising:
A) at least one scotch yoke module comprising:
a)a crank pin perpendicularly mounted on
b)a crank pin collar having a non-circular orifice and sliding on
c)a co-axial crank pin collar shaft having a matching non-circular cross-
section, and the crank
pin collar shaft is mounted perpendicularly on
d) a notched auxiliary input shaft, such that a longitudinal axis of the crank
pin is coplanar and
parallel and at an offset distance to the longitudinal axes of the auxiliary
input shaft,
wherein the offset distance can be altered by displacing the crank pin by
e) a crank pin displacement mechanism comprising:
i. a sliding collar disposed co-axially with the auxiliary
input shaft, wherein one of the
sliding collar and the auxiliary input shaft has a non-circular cross-section
and another
of the sliding collar and the auxiliary input shaft has a matching non-
circular orifice,

3
such that the sliding collar and the auxiliary input shaft rotate
synchronously with each
other while having the ability to slide axially relative to each other,
ii. a link assembly comprising
a) a link pivoting on the sliding collar and the crank pin collar through
the notch
b) a sliding collar pivot pin on one end of the link and pivoting the crank
pin collar
with
c) a crank pin collar pivot pin on another end
f) at least one thrust bearing that is co-axially placed in contact with
the sliding collar, such
that an external force applied on the thrust bearing causes an axial
displacement of the
thrust bearing and the sliding collar with respect to the auxiliary input
shaft, which alters
the offset distance by moving the crank pin collar together with the crank pin
along the
crank pin collar shaft,
g) a slotted rack holder comprising one or more racks, which is restricted to
only move
along a direction of a longitudinal axis of the one or more racks, and a crank
pin slot for
receiving the crank pin, with a longitudinal axis of the crank pin slot
orthogonal to the one
or more racks,
B) at least one angular velocity module comprising:
a) an input shaft,
b) at least one driving Geneva pin wheel mounted on the input shaft and
driving
c) at least one driven Geneva slot wheel mounted co-axially on the
auxiliary input shaft, at a
fixed orientation to the axis of the crank pin shaft and
C) at least one rectifier module comprising:
a) a pinion engaged with the one or more racks, and mounted on
b) a pinion shaft through
c) a computer-controlled clutch, a one-way bearing, or a ratchet mechanism;
arranged such that a uniform rotation of the driving Geneva pin wheel via the
input shaft, causes a non--
uniform angular velocity of the auxiliary input shaft via the driven Geneva
slot wheel, causing the crank pin to
revolve the auxiliary input shaft reciprocating the one or more racks
substantially along a longitudinal direction
of the one or more racks at a substantially constant velocity and slowing down
briefly during direction reversal
and accelerating to the constant velocity, where a magnitude of the
reciprocation is propodional to the offset
distance of the crank pin and the auxiliary input shaft, and this
reciprocation of the rack causes an alternating
rotation of the pinion and the rotation of the pinion is converted to a
unidirectional rotation of an output gear,
or output sprocket mounted on the pinion shaft via the computer controlled
clutch, the one way bearing or the
ratchet mechanism.

4
5. The infinitely variable transmission of claim 2, wherein rotation ratio of
driving Geneva pin wheel of the
driven Geneva slot wheel, when expressed using Cartesian coordinates (X1, Y1)
and (X2, Y2) respectively, as
a function of angle 19 are
where 4,(9) is a solution to a piece-wise differential equation
<IMG>
function of any linear or nonlinear curve connecting points
<IMG>
<IMG>
ki if 0,i < < 02i,
function of any linear or nonlinear curve connecting points (02i3O)to
(03i,¨ki)
if 02i < 0 < 03.
¨ki if 03. < 0 < 04i,
function of any linear or nonlinear curve connecting points (94i, 0) to
<IMG>
or
<IMG>
function of any linear or nonlinear curve connecting points (0,i,ki)to (92,
¨ki)
if 01i < <192i,
¨ki if 02i < O < 03i,
function of any linear or nonlinear curve connecting points (03i,¨ki) to
(04i,ki)
<IMG>
where boundary conditions are

<IMG>
where
CTR is a center to center distance of the driving Geneva pin wheel and the
driven Geneva slot wheel,
0 is an angular displacement of the driving Geneva pinwheel;
(1) is an angular displacement of the driven Geneva slot wheel;
i refers to an i-th revolution the input disk from 0 to N*n-1 with a 1st
rotation being i=0;
N is a number of times the input disk rotates when the driven Geneva pin wheel
rotates once;
n is a number of times the driven Geneva slot wheel rotates when the driving
Geneva slot wheel once;
regions where the piece-wise function for the rack velocity is constant are
functional regions and regions
where the piece-wise function for the rack velocity is not constant are non-
functional regions which can be
linear or non-linear functions of 0;
191i,192i, 193i, 194i are specific angular positions of the driving Geneva pin
wheel, the values of which are
solved for using a solution to the piece-wise differential equation;
(1,2, (1,3, (1,4 are specific angular positions of the driven Geneva slot
wheel corresponding to angular
positions 191i,192i093i094i of the driving Geneva pin wheel respectively, and
are a cutoff between the
functional and non-functional regions, values of ci) , 2 , OP 3 , cP 4 which
can to be solved for by using arbitrary
values for 01,,
and ki are constants, which are all equal.
8 The infinitely variable transmission of claim 2, further comprising one or
more additional driving Geneva pin
wheel and driven Geneva slot wheel pairs, wherein the pairs of driving Geneva
pin wheel and driven
Geneva slot wheel are stacked in layers and a sum ot all functional regions of
all the pairs of driving
Geneva pin wheel and driven Geneva slot wheel in each angular velocity module
is greater than or equal
to 360- and is placed such that the Geneva pin wheel and slot wheel pairs are
in the functional region in
sequence with an overlap between the functional regions of consecutive driven
Geneva slot wheels.
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7) The infinitely variable transmission of claim 2, wherein the
angular velocity modules are oriented such
that their Geneva pin wheel and the Geneva slot wheel are in the functional
region in sequence with an
overlap when the input disk completes approximately one rotation, ensuring
that at least one angular
velocity module is in the functional region at any given time.
8) The infinitely variable transmission of claim 18, wherein an amount of
overlap between each pair of
consecutively engaged rectifier modules are substantially identical.
9) The infinitely variable transmission of claim 2, further comprising a dead
weight and a wheel that transfers
motion from the rack to a dummy rack with teeth identical to the rack and
located 180 degrees relative to
the rack, and the dummy rack moves in a substantially opposite direction of
the rack.
10) The infinitely variable transmission of claim 2, further comprising a
dummy crank pin having a mass
substantially identical to a mass of the crank pin that slides in an opposite
direction of the crank pin.
11) The infinitely variable transmission of claim 2, further comprising:
a differential assembly comprising an input miter bevel gear and a pair of
substantially co-axial output
miter bevel gears operably connected with the input miter bevel gear such that
the output miter bevel
gears rotate in opposite directions, each output miter bevel gear having a
through-bore substantially at a
central axis thereof and substantially co-axial with each other;
a through-shaft positioned through the through-bores of the output miter bevel
gears; and a pair of collars
operably coupled with the through-shaft and rotatably fixed therewith, each
collar configured to move
axially along the through-shaft independently of the other collar and
configured to engage with one of the
output miter bevel gears;
wherein the power link shaft is operably coupled with the input miter bevel
gear to cause rotation of the
input miter gear.
12) The infinitely variable transmission of claim 11, wherein:
when a first one of the collars is engaged with a first one of the output
miter bevel gears and a second
one of the collars is not engaged with a second one of the output miter bevel
gears, the through-shaft
rotates about its longitudinal axis in a first direction corresponding to a
rotational direction of the first one
of the output miter bevel gears; and
when the second one of the collars is engaged with the second one of the
output miter bevel gears and
the first one of the collars is not engaged with the first one of the output
miter bevel gears, the through-
shaft rotates about its longitudinal axis in a second direction corresponding
to a rotational direction of the
second one of the output miter bevel gears.
13) The infinitely variable transmission of claim 11, wherein when neither of
the collars is engaged with the
output miter bevel gears, the through-shaft is free to rotate in any direction
about its longitudinal axis.
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14) The infinitely variable transmission of claim 11, wherein when each of the
collars is engaged with a
respective one of the output miter bevel gears, the through-shaft is
restricted from rotating about its
longitudinal axis.
15) The infinitely variable transmission of claim 14, wherein the input shaft
is connected to a ring gear, a
carrier or a sun gear, the output from the output gear thru an output shaft is
connected to another one of
the ring gear, the carrier or the sun gear and the final output is connected
to another one of the ring
gear, the carrier or the sun gear.
16) The infinitely variable transmission of claim 14, wherein a final output
from a planetary gear system
temporarily stores energy in a fly-wheel-system and later delivers power back
to the input shaft or to a
wheel-system.
17) A infinitely variable transmission comprising:
A) at least one scotch yoke module comprising:
h)a crank pin perpendicularly mounted on
i) a crank pin collar having a non-circular orifice and sliding on
j) a co-axial crank pin collar shaft having a matching non-circular cross-
section, and the crank
pin collar shaft is mounted perpendicularly on
k) a notched auxiliary input shaft, such that a longitudinal axis of the crank
pin is coplanar and
parallel and at an offset distance to the longitudinal axes of the auxiliary
input shaft,
wherein the offset distance can be altered by displacing the crank pin by
0 a crank pin displacement mechanism comprising:
iii. a sliding collar disposed co-axially with the auxiliary input shaft,
wherein one of the
sliding collar and the auxiliary input shaft has a non-circular cross-section
and another
of the sliding collar and the auxiliary input shaft has a matching non-
circular orifice,
such that the sliding collar and the auxiliary input shalt rotate
synchronously with each
other while having the ability to slide axially relative to each other,
iv. a link assembly comprising
d) a link pivoting on the sliding collar and the crank pin collar through
the notch
e) a sliding collar pivot pin on one end of the link and pivoting the crank
pin collar
with
0 a crank pin collar pivot pin on another end
m) at least one thrust bearing that is co-axially placed in contact with the
sliding collar, such
that an external force applied en the thrust bearing causes an axial
displacement of the
thrust bearing and the sliding collar with respect to the auxiliary input
shaft, which alters
the offset distance by moving the crank pin collar together with the crank pin
along the
crank pin collar shaft,
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n) a slotted rack holder comprising one or more racks, which is restricted to
only move
along a direction of a longitudinal axis of the one or more racks, and a crank
pin slot for
receiving the crank pin, with a longitudinal axis of the crank pin slot
orthogonal to the one
or more racks,
B) at least one angular velocity module comprising:
d) an input shaft,
e) at least one driving Geneva pin wheel mounted on the input shaft and
driving
f) at least one driven Geneva slot wheel mounted co-axially on the
auxiliary input shaft, at a
fixed orientation to the axis of the crank pin shaft and
C) at least one rectifier module comprising:
a) a pinion engaged with the one or more racks, and mounted on
b) a pinion shaft through
c) a computer-controlled clutch, a one-way bearing, or a ratchet mechanism;
arranged such that a uniform rotation of the driving Geneva pin wheel via the
input shaft, causes a non-
uniform angular velocity of the auxiliary input shaft via the driven Geneva
slot wheel, causing the crank pin to
revolve the auxiliary input shaft reciprocating the one or more racks
substantially along a longitudinal direction
of the one or more racks at a substantially constant velocity and slowing down
briefly during direction reversal
and accelerating to the constant velocity, where a rnagnitude of the
rec.iprocation is proportional to the offset
distance of the crank pin and the auxiliary input shaft, and this
reciprocation of the rack causes an altemating
rotation of the pinion and the rotation of the pinion is converted to a
unidirectional rotation of an output gear,
or output sprocket mounted on the pinion shaft via the computer controlled
clutch, the one way bearing or the
ratchet mechanism.
18. An infinitely variable transrnission comprising:
A) at least one scotch yoke module comprising:
a. a crank pin revolving around
b, a notched auxiliary input shaft, at an offset
distance between longitudinal axes of the
crank pin and the auxiliary input shaft that remain parallel to each other,
and the offset
distance that can be altered from zero when the crank pin is co-axiai to the
auxiliary input
shaft to a non-zero real n u m be r by displacing the crank pin along a radial
siot of
c. an input disk rigidly mounted on the auxiliary input
shaft, by
B) a crank pin displacement mechanism cornprising:
a. a sliding collar disposed co-axially with the
auxiliary input shaft with a feature
preventing relative angular displacement while allowing relative translation,
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b. a link assembly comprising
i. a link pivoting the crank pin through the notch
ii. a crank pin pivot pin on one end and pivoting the sliding collar about
iii. a sliding collar pivot pin on another end of the link,
c. at least one thrust bearing that is co-axially placed
in contact with the sliding collar,
such that an external force applied on the thrust bearing causing an axial
displacement of
the thrust bearing along with the sliding collar wfth respect to the auxiliary
input shaft, afters
the offset distance by moving the crank pin along the radial slot of the input
disk,
d. a slotted rack holder comprising one or more racks,
which is restricted to only move
along a direction of the longitudinal axis of the one or more racks, and a
crank pin slot for
receiving the crank pin, with a longitudinal axis of the crank pin slot
orthogonal to the one or
more racks,
C) at least one angular velocity module comprising:
a. an input shaft,
b. one or more driving circular or non-circular gear mounted on the input
shaft and
driving
c. at least one driven circular or non-circular gear that is mounted free
(o spin on a
fixed shaft, where the driven non-circular gear further functions as a carrier
of a planetary
gear system, with
d. at least one free to spin planet gear meshing with a stationary sun gear
mounted
on the fixed shaft and is axially attached to
e. a primary cam that is operably engages with
f. a secondary cam that is mounted on the auxiliary input shaft and
0) at least one rectifier module comprising:
a. a pinion engaged with the rack, and mounted on
b. a pinion shaft through
c. a computer-controlled clutch, a one-way clutch or a ratchet mechanism
arranged such that a uniform rotation of the driving non-circular gear via the
input shaft, causes a non-uniform
angular velocity of the auxiliary input shaft via the driven non-circular gear
and the planetary gear system,
causing the crank pin to reciprocate the rack substantially along a
longitudinal direction of the rack at a
substantially constant velocity and slowing down briefly during direction
reversal and accelerating to the
constant velocity, where a magnitude of the reciprocation is proportional to
the offset distance of the crank pin
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and the auxiliary input shaft, and this reciprocation of the rack causes an
alternating rotation of the pinion and
this alternating rotation of the pinion is converted to a unidirectional
rotation of the pinion shaft via the
computer-controlled clutch, the one-way clutch or the ratchet mechanism.
19. An infinitely variable transmission comprising:
A) at least one scotch yoke module comprising:
a. a crank pin revolving around
b. a notched auxiliary input shaft, at an offset distance between
longitudinal axes of the
crank pin and the auxiliary input shaft that remain parallel to each other,
and the offset
distance that can be altered from zero when the crank pin is co-axial to the
auxiliary input
shaft to a non-zero real number by displacing the crank pin along a radial
slot of
c. an input disk rigidly mounted on the auxiliary input shaft, by
B) a crank pin displacement mechanism comprising:
a. a sliding collar disposed co-axially with the
auxiliary input shaft with a feature
preventing relative angular displacement while allowing relative translation ,
b. a link assembly comprising
i. a link pivoting the crank pin through the notch
ii. a crank pin pivot pin on one end and pivoting the sliding collar about
iii. a sliding collar pivot pin on another end of the link,
c. at least one thrust bearing that is co-axially placed
in contact with the sliding collar,
such that an external force applied on the thrust bearing causing an axial
displacement of
the thrust bearing along with the sliding collar with respect to the auxiliary
input shaft, alters
the offset distance by moving the crank pin along the radial slot of the input
disk,
d. a slotted rack holder comprising one or more racks,
which is restricted to only move
along a direction of the longitudinal axis of the one or more racks, and a
crank pin slot for
receiving the crank pin, with a longitudinal axis of the crank pin slot
orthogonal to the one or
more racks,
C) at least one angular velocity rnodule cornprising:
a, an input shaft,
b. one or more driving circular or non-circular gear mounted on the input
shaft and
driving
c. at least one driven circular or non-circular gear that is mounted free
to spin on a
fixed shaft, where the driven non-circular gear further functions as a carrier
of a planetary
gear system, with
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d. at least one free to spin planet gear meshing with a stationary ring
gear that is
mounted on a frame and is axially attached to
e. a primary cam that is operably engages with
f. a secondary cam that is mounted on the auxiliary input shaft and
D) at least one rectifier module comprising:
a. a pinion engaged with the rack, and mounted on
b. a pinion shaft through
c. a computer-controlled clutch, a one-way clutch or a ratchet mechanism
arranged such that a uniform rotation of the driving non-circular gear via the
input shaft, causes a non-uniform
angular velocity of the auxiliary input shaft via the driven non-circular gear
and the planetary gear system,
causing the crank pin to reciprocate the rack substantially along a
longitudinal direction of the rack at a
substantially constant velocity and slowing clown briefly during direction
reversal and accelerating to the
constant velocity, where a magnitude of the reciprocation is proportional to
the offset distance of the crank pin
and the auxiliary input shaft, and this reciprocation of the rack causes an
alternating rotation of the pinion and
this alternating rotation of the pinion is converted to a unidirectional
rotation of the pinion shaft via the
computer-controlled clutch, the one-way clutch or the ratchet mechanisrn.
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Description

WO 2021/163583
PCT/US2021/017984
1
TITLE OF INVENTION:
INFINITELY VARIABLE TRANSMISSION WITH UNIFORM INPUT-TO-OUTPUT RATIO
THAT IS NON-DEPENDENT ON FRICTION
CROSS REFERENCE TO RELATED APPLICATIONS
BACKGROUND OF THE INVENTION:
FIELD OF THE INVENTION
This invention pertains to transmissions having variable ratios between input
and output
velocities. Specifically, it relates to all-gear transmissions whose velocity
ratios may be changed continuously
over a wide range of values ranging from zero to non-zero values, without
depending on friction.
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DESCRIPTION OF THE RELATED ART
The patents US 5603240 and US 20100199805 use some of the features used in
this design.
The patent US 5603240 does not have a co-axial input to output and therefore
cannot be used for
applications requiring this configuration. The output travels as the ratio is
changed. Therefore,
this design cannot be used when stationary output is required. US 20100199805
offers a sinusoidal output
and uses several modules just to minimize the "ripple" when a steady and
uniform input is provided.
Therefore, the design cannot be used when a steady and uniform output is
desired.
The patent US 9970520 offers a steady input to output ratio and co-axial input
and output shaft in a
comparably smaller envelope than that of its prior art. This is achieved with
a use of a set of non-circular
gears using as few as three modules. The drawback is that it is hard to mass
produce the desired non-circular
gears and will add significant manufacturing cost. It is also difficult to
accurately design the tooth profile to
achieve a uniform input to output ratio.
The present invention uses a custom designed Geneva wheel mechanism to achieve
uniform rack velocity
during functional region and circular/ non-circular gear for non-functional
region. The portion of the region
used by the Geneva wheel mechanism is also non-functional region which overlap
with the non-functional
region achieved by the circular/non-circular gears for smooth transition. It
is also possible to use Geneva
wheel mechanism for functional and non-functional region. However, it will be
economical to use a partial
circular gear for the non-functional region. The path of the Geneva slot
engaging with the Geneva pin
determines the shape of the functional or non-functional region. Using a
commonly used Geneva wheel
mechanism with straight slot will not achieve uniform rack movement in the
functional region and these slots
has to have a specific shape to achieve uniform rack movement in the
functional region. In general, a Geneva
wheel mechanism has straight slot and is commonly used in applications needing
indexing.
BRIEF SUMMARY OF THE INVENTION:
The main objective of this invention is to provide a UNIFORM and STEADY
output,
when the input is uniform and steady, with the ability to transmit high torque
without depending
on friction or friction factor. Many of the continuously variable
transmissions that are in the
market today are friction dependent and therefor lack the ability to transmit
high torque. Those
continuously variable transmissions, which are non-friction dependent do not
have a uniform and
steady output when the input is uniform and steady. The design that offers all
is too complex and hard to
mass produce. And This design aids reduction in the overall size and can be
economically mass produced.
This design can be easily integrated into any system. This design is very
versatile and can be used ranging
from light duty to heavy duty applications. This design allows replacement of
existing regular transmission,
requiring very little modification. This design offers stationary and co-axial
input and output.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS:
All the gears partial or full in the following figures can be replaced with a
sprocket and chain system.
Fig 1- IVT general assembly perspective view - Exploded.
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Fig 2- Angular velocity module using Geneva pin and wheel mechanism along with
partial circular /non-
circular gears
Fig 3a - Crank pin displacement mechanism using link mechanism with sliding
collar placed coaxially inside
the input shaft and crank pin shaft
Fig 3b - Crank pin displacement mechanism using link mechanism with sliding
collar placed coaxially inside
the input shaft and input disk
Fig 4A-4B - Scotch yoke module and rectifier module. Rectifier module showing
rack and pinion, with pinions
placed on a common output shaft on a one-way bearing along with dummy rack,
and common output shaft.
Showing force acting on the rack is co-planer with longitudinal axis of the
pinion.
4A - Perspective view
4B ¨ Perspective view exploded
Fig 5 ¨ Input shaft and input disk assembly perspective view
Fig 6A - 6D Input disk, crank pin shaft and link pivot pin assembly
6A ¨ Top view
6B- Front view
6C- Side view 1
6D- Perspective view
Fig 7A ¨ 7C Different configurations for slotted rack holder
Fig 8A ¨ 80 - Geneva pin wheel
8A- Front view
8B- Side view 1
8C- Perspective view
Fig 9 Input disk
Fig 10A ¨ 10B ¨ Geneva slot wheel double sided with slot and wall
10A ¨ Perspective view showing details of the bottom
10B - Perspective view showing details of the top
10C ¨ Perspective view showing different configuration
Fig 11 - 12 Additional optional configurations for Geneva slot wheel
Fig 13 ¨ Scotch yoke input frame
Fig 14 ¨ Scotch yoke frame
Fig 15 ¨ Scotch yoke rectifier frame
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Fig 16¨ Ratio modifier frame
Fig 17 - Ratio plate
Fig 18 ¨ Partial driving/driven gear for non-functional region
Fig 19 ¨ Link
Fig 20 ¨ crank pin
Fig 21A ¨ 21D Link Mechanism on crank pin shaft with non-circular input shaft
and collar with matching
orifice, using offset crank pin mounted on crank pin collar with non-circular
orifice sliding on crank pin shaft
with matching cross-section
21A- Top view
21B- Front view
21C- Side view
21D-Perspective view
Fig 22A ¨ 22D Link Mechanism on crank pin shaft with non-circular input shaft
and collar with matching
orifice, using input disk
22A- Top view
22B- Front view
22C- Side view
22D-Perspective view
Fig 23 ¨ Rack velocity profile
Fig 24 -
Fig 25 ¨ 30 ¨ Options for connecting input, output and wheel using planetary
gear
Fig 31 ¨ Possible path of crank pin on Geneva wheel mechanism and showing
partial gears for non-functional
region
Fig 32 ¨ 34 ¨ Alternate configurations for ratio changing mechanism assembly
using different shapes for input
shaft, crank pin and collar
Fig 35 ¨ 36 ¨ Input shaft with notch for crank pin shaft, link and pivot pin
for collar and link
Fig 35 ¨ Front view
Fig 36 ¨ Side view
Fig 37 ¨ Dummy crank pin assembly
Fig 38 ¨ Mechanism to compensate for vibration due to rotational imbalance
Fig 39 ¨ Slotted hollow input shaft
39A-Top view
39B-Front view
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390-Side view
39D-Perspective view
Fig 40 ¨ Collar with thrust bearings
40A-Top view
40B-Front view
400-Side view
40D-Perspective view
Fig 41 ¨ 2 racks shown 180 degrees apart
40A-Top view
40B-Front view
400-Side view
40D-Perspective view
Fig 42 ¨ 2 dummy racks shown 180 degrees apart
40A-Top view
40B-Front view
400-Side view
40D-Perspective view
Fig 43A ¨ 43B ¨ Alternative angular velocity module using stationary sun gear
43A - Perspective view
43B ¨ Section through driven gear
Fig 44A ¨ 44B ¨ Alternative angular velocity module using stationary ring gear
44A - Perspective view
44B ¨ Section through driven gear
Fig 45 - 48 ¨ achieving Reverse/Park/Neutral using bevel gears:
Fig 49 ¨ Rack velocity profile and overlap of functional regions of
consecutive modules in X-Y plane
Fig 50- Rack velocity profile and overlap of functional regions of consecutive
modules using polar
coordinates
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DETAILED DESCRIPTION OF THE INVENTION:
SUMMARY OF THE INVENTION
To briefly describe this invention is an Infinitely Variable Transmission
(IVT). Unlike
existing CVT designs, this particular design does NOT depend on friction to
transmit power.
Most of the CVTs that exist today depend on friction to transmit power and
therefore cannot be
used where there is a need to transmit high power at low speed. Due to this
advantage, it is
possible to use this invention where high torque transmission is required. Co-
axial input and
output can be achieved with this layout.
LIST OF COMPONENTS:
All the gears in the following component list can be replaced with a sprocket
and chain system. The non-
circular gear system can be replaced with a sprocket and chain system where at
least one of the sprockets is
non-circular.
1) Scotch yoke Input frame
2) Ratio modifier frame
3) Scotch yoke rectifier frame
4) Output frame
5) Ratio plate
6) Geneva slot wheel mechanism
a) Pin wheel
b) Slot wheel
7A-7B) Non-functional region partial driving and driven gear
a) driving partial gear
b) driven partial gear
8) Input shaft
9) Crank-Pin
10) Input disk
11) Slotted Rack holder
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12) Rack
13) Dummy Rack
14) Pinion
15) Pinion shaft
16) Collar
17) Link
18) Dummy link
19) Input shaft bearing
20) Input-Disk bearing
21) Thrust-Bearing
22) One-way bearing/ Computer-Controlled-Clutch / Ratchet-mechanism
23) Crank pin shaft
24) Dummy Crank-Pin
25) Non-functional region driving gear
26) Non-functional region driven gear
27) Crank pin to link pivot pin
28) Collar to link pivot pin
29) Power shaft
30) Planetary-Gear
31) Miter/Bevel-Gear-Differential-input shaft
32) Miter/Bevel-Gear-Differential-output shaft
33) Miter/Bevel-Gear
34) Rack velocity profile
35) Clutch-Park/Neutral/Reverse clutch/dog clutch
36) Stationary sun gear
37) Shaft-Cam
38) Cam gear
39) Driving circular or non-circular gear
40) Driven circular or non-circular gear
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41) Cam-Input-Shaft
42) Planet gear
43) Stationary sun gear
44) Stationary ring gear
45) Carrier shaft
The working of this CVT can be described by the following simple sequential of
operations.
a) A Crank pin 9 (Fig. 3B), revolves around the longitudinal axis of an Input
disk 10
(Fig. 9) or a Input shaft 4 (Fig. 39) at an offset distance as shown in Fig.
3A, and this offset distance can be
altered. The offset distance ranges from zero to a non-zero value. The concept
described in this operation
exists in several other patent application US 20100199805, US 9970520 etc.
b) This offset Crank pin 9 is caged in
1) the Input disk 10 or alternatively slides on a Crank pin shaft 23, and
2) a slot of a Slotted rack holder 11 (Fig. 7A-7C).
The input shaft is slotted to allow the crankpin and link to pass thru it
allowing the longitudinal axis of the input
shaft or the input disk to be co-axial with the longitudinal axis of the crank
pin. The Slotted rack holder 11 is
restricted such that it can move only in the direction that is normal to its
slot. A Rack 12is fastened to the
Slotted rack holder 11, such that the Rack 12 is parallel to the Slotted rack
holder's 44 direction of movement.
In the alternative construction, the Crank pin shaft 23 is orthogonal to the
Input shaft 4. The revolution of the
Crank pin 9 about the longitudinal axis 1021 of Input disk 10 is translated to
pure linear back and forth
movement or reciprocating movement of the Rack 12. This mechanism is commonly
known as "Scotch-Yoke-
Mechanism" in the industry. The distance of this linear back and forth
movement (stroke) is directly
proportional to the radial distance of the Crank pin 9 from the longitudinal
axis 1021 of the Input disk 10. Since
the work done is constant, which is a product of force applied multiplied by
the distance traveled (F*stroke),
for a smaller stroke, the force applied is greater and for a longer stroke,
the force applied is smaller.
c) The Rack 12 is linked to a Pinion 14 (Fig. 4A) converting this linear
movement of the Rack 12
to rocking oscillation of the Pinion 14.
d) This rocking oscillation is converted to a unidirectional rotation, using a
One-way bearing/ Computer-
Controlled-Clutch / Ratchet-mechanism 22.
One main purpose of this invention is to achieve a CONSTANT AND UNIFORM output
angular velocity when the input angular velocity is constant and uniform.
However, using the
steps described above, this is NOT achieved, as the output is sinusoidal.
By modifying the rate of change of angular displacement of the Input disk 10,
a uniform steady output can be
achieved. Patent U59970520 uses a pair of non-circular gears to achieve this.
This invention achieves it by
using modified Geneva mechanism customized for this.
By using a set of Geneva pin wheel 6a (Fig. 8A-8C) and Geneva slot wheel 6b
(Fig. 10A ¨ 10C) the
instantaneous rate of change of angular displacement at the Input disk 10can
be altered.
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The components are grouped into modules/mechanisms for easier understanding:
Detailed description of Assembly, Sub-assembly of components/ Modules and
their functions:
a) Angular-Velocity-Modifier-Module (Fig. 2) The main purpose of this module
is to change
the uniform power input to a reciprocal of sinusoidal output. This is to
reverse the
effect of the sinusoidal output in a scotch yoke mechanism. This module
comprises of:
1) Driving Geneva pin wheel,
2) Driven Geneva slot wheel and
3) Power shaft
The Driving Geneva pin wheel 6a is mounted on the Input shaft 4. The shape of
the Geneva slot wheel 6b
is designed to achieve the end result which is the reciprocal of sinusoidal
output. Multiple pins and multiple
slots are used and with an overlap of more than one pin achieving a portion of
the same results
simultaneously. More than one set of driving Geneva pin wheel and driven
Geneva slot wheel can be used in
a single module. The slot or the walls of the slot are terminated where a
pin's path forms loop. Also, multiple
modules can share a common Geneva pin wheel or a common Geneva slot wheel. In
the slot wheel the paths
of the slots are cut from a slot wheel or the walls of the path can be raised
from a slot wheel or a combination
of both. This is to clear the interference of the pin where the pin and slot
or slot walls do not produce desired
result. Pins of the Geneva pin wheel can be made with different heights so
that they do not interfere with the
wall of slots of other Geneva pins. A portion of the rotation of the Geneva
pin wheel and Geneva slot wheel be
achieved using one or more partial circular gears and/or one or more partial
non-circular gear in parallel. The
partial gears generate the non-functional region of the rack velocity while
the Geneva wheel system
generates functional portion of the rack velocity. The Geneva wheel slots also
have an overlap of the region
generated by the partial gear. This is to achieve a 1:X ratio of rotation
between Geneve pin wheel and
Geneva slot wheel. Here X is an integer or a reciprocal of an integer.
Optionally, a one-way bearing can be
placed between the circular or non-circular gear linking the Geneva slot wheel
to the partial driven gear.
Depending on the scenario either the Geneva pin wheel or the Geneva slot wheel
can be made driving or
driven.
b) Scotch-Yoke-Module (Fig. 4A, 4B): The main purpose of this module is to
convert circular
motion to a reciprocating motion. The output is sinusoidal for a steady,
uniform input. This
output is converted to a steady, uniform output using Angular-Velocity-
Modifier-Module.
This Scotch-Yoke-Module comprises of:
1) Input disk 10,
2) Slotted Rack holder 11, and
3) Crank pin 9
The Input disk 10has a radial slot.
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The Slotted rack holder 11 has a slot namely "Crank-Pin-Slot" 1013. It also
has an extension on either side of
the slot at the middle of the slot. This extension is normal to the Crank-Pin-
Slot 1013. The Slotted rack holder
44, is placed on the other side of the Input disk 10 sandwiching the Input
disk 10between the Slotted rack
holder 11 and a Ratio-Changing- Mechanism, which is described in subsequent
paragraphs. The Crank pin 9
passes through the slots of Ratio-Changing-Mechanism, Input disk 10, and
Slotted rack holder 11
C) Rectifier-Module: The main purpose of this module is a mechanical
equivalent to a diode in an electrical
circuit. It allows power transfer to one specific direction.
1) Rack 12,
2) Pinion 14,
3) Shaft-Pinion 48 and
4) One-way bearing/ Computer-Controlled-Clutch / Ratchet-mechanism 22
The Rack 121s attached to the Slotted rack holder 11 normal to the Crank-Pin-
Slot 1013 and
paired with the Pinion 14. The Pinion 14 is mounted on a Shaft-Pinion 48. The
Computer-
Controlled-Clutch /One-Way-Bearing / Ratchet-Mechanism 50 is mounted on the
Shaft-
Pinion 48. The Output-Gear! Output-Sprocket 51 is mounted on the OD of the One-
Way-
Bearing 50.
Multiple pinions from multiple modules can be mounted on a common shaft-pinion
48. The one-way bearing
can be placed between the pinion and the pinion shaft. In this scenario the
shaft-pinion 48 will function as the
CVT output. The shaft-pinion can be made hollow so that the CVT input shaft
can pass thru the shaft-pinion
48 making the input and output of the CVT co-axial.
d) Gear-Changing-Mechanisms
Link Mechanism:
The Input shaft 66 has a non-circular hole in the middle. This is paired with
a Sliding-Collar with a
matching exterior contour, which is co-axially placed allowing relative axial
movement while restricting
rotational angular displacement with respect to each other. Two thrust-
Bearings 40 are co-axially placed in
contact with one on either end of the Sliding-Collar 67 as shown in Fig. 22D
and the Sliding-Collar-Auxiliary-
Shaft 67 has a pivot 1028 on the other end. One end of a Link 68 is attached
to the pivot 1028 and the other
end of the Link 68 is either attached to the Crank pin 9, as shown in (Fig.
3A) or to the Crank pin shaft 23, as
shown in (Fig. 3A) as appropriate. An axial displacement of the Sliding-Collar-
Auxiliary-Shaft 67 will cause a
radial displacement of the Crank pin 9 thru the Link 68. This axial
translation is achieved with a Lever-Ratio-
Changing-Spiral-Flute-Mechanism 41 that pushes the Thrust-Bearing 40 attached
to the Sliding-Collar-
Auxiliary-Shaft 67. Optionally this can be sprung back with a Compression-
Spring 39 placed between Input
disk 10and the Sliding-Collar-Auxiliary-Input-Shaft 67. Also, when this link
mechanism is used the Driven-
Geneva-slot wheel 6b can also function as the Input disk 10when a radial slot
is added to the Driven-Geneva-
slot wheel 6b, thereby eliminating the need for a separate Input disk 10.
For each scotch yoke module two Racks 64 can be placed on the Slotted rack
holder 11with a phase
shift of 180 engaged with their respective pinions placed co-axially on a
common pinion shaft via a
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one-way bearing/computer-controlled clutch/a ratchet mechanism to allow the
pinion shaft to rotate in
a specific direction. Many of these scotch yoke modules can be stacked and all
the pinions of all the
modules can be placed on one common pinion shaft, making the pinion shaft the
output of the Rff.
Further this common pinion shaft can be made hollow allowing the power shaft
which drives the
driving Geneva pin wheel, to pass thru. With this arrangement a co-axial input
to output can be
achieved. This configuration allows to modify the output with a planetary gear
system to achieve
reverse gear converting the CVT to an IVT. This configuration also allows the
force on the rack holder
to pass thru the plane of the common pinion shaft axis. In other words, the
longitudinal axis of the
common pinion and the force of the crankpin acting on the rack holder will be
co-planer. This will
minimize the moment of the force from the crank pin acting on the rack holder
due to the resistance
by the pinion and maximize the tangential force on the pinion.
Two Rectifier-Modules 1001 are placed next to the Slotted rack holder 11 as
shown in
Fig. 83 such that the Rack 12is placed normal to the Slotted rack holder's 44
Crank-Pin-Slot
1013.
MECHANISM TO COMPENSATE VIBRATION (ROTATIONAL IMBALANCE):
1. Dummy-Crank-Pin 43: The Crank pin 9 is placed off-center when the Input
disk 10
revolves. This imbalance will result in vibration. To compensate this, a Dummy-
Crank-Pin 43
is placed at same distance 180 apart. This movement is identical to the
movement of the Crank pin 9. The
dummy crank pin is attached to a dummy link that links to the dummy crank pin
43 that is pivoted to the collar
placed to move in the opposite direction of the crank-pin. The input shaft is
slotted to allow the link and crank
pin and dummy link and dummy crank pin to pass thru
2. Dummy-Rack 55 for counter oscillation: As the Input disk 10 rotates the
Slotted Rack holder 11 has
an oscillatory motion which will result in vibration. It is cancelled by
having an
appropriate mass oscillating in the opposite direction. This is achieved by
pinion as shown in Fig.4A&4B in
contact with the Rack 12, which will spin back and forth. Bringing an
appropriate mass in contact with the
pinion at 180 apart will compensate for this vibration. A separate wheel can
also be used in spite of the
pinion or a lever pivoting on the pinion shaft can be used to link the rack
and the dummy rack such that they
move in opposite direction. A slider connecting the lever and sliding in a
slot normal to the rack teeth will
guide the lever allowing the rack and dummy rack to only slide in the
direction of the longitudinal axis of the
rack.
REVERSE GEAR MECHANISM:
When the output from the Pinion shaft 15 is coupled with Miter/Bevel-Gear-
Differential-input shaft 31. The
Miter/Bevel-Gear-Differential-output shaft 32 will rotate in opposite
directions via Miter/Bevel-Gear 33. The
Miter/Bevel-Gear-Differential-input shaft 31 of this differential-mechanism is
placed co-axial with The
Miter/Bevel-Gear-Differential-output shaft 32 with clearance so that it is
free to spin independently with
respect to the Miter/Bevel-Gear-Differential-input shaft 31. Two Clutch-
Park/Neutral/Reverse clutch/dog clutch
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35 with a clutch are placed on the Miter/Bevel-Gear 33 allowing them to move
axially. These can be made to
link with
either of the Miter/Bevel-Gear 33, which rotate in opposite direction. When
one of the
collars is made to link via the Clutch-Park/Neutral/Reverse clutch/dog clutch
35, by means of clutch, with a
particular output Clutch-Park/Neutral/Reverse clutch/dog clutch 35 and the
Miter/Bevel-Gear-Differential-
output shaft 31 will rotate in a particular direction. It will reverse its
direction if the link is swapped to the other
Miter/Bevel-Gear 33.
NEUTRAL GEAR MECHANISM:
When the collars are not in link via the Clutch-Park/Neutral/Reverse
clutch/dog clutch 35 with any of the
Miter/Bevel-Gear 33, the collar and the Miter/Bevel-Gear-Differential-output
shaft 32 are not restricted and,
therefore, they are free to spin in any direction and function as a "neutral"
gear.
PARK MECHANISM:
When the collars are in link via the Clutch-Park/Neutral/Reverse clutch/dog
clutch 35 with both the
Miter/Bevel-Gear 33, the collar is restricted from spinning and the
Miter/Bevel-Gear-Differential-output shaft
32 is totally restricted and, therefore, they are restricted to spin in any
direction and function as a "parking" gear.
CONVERTING CVT TO AN IVT (INFINITELY-VARIABLE-TRANSMISSION):
Having a co-axial input and output allows the CVT to function as an IVT. This
can be
achieved by adding a Planetary-Gear-System with a Sun-Gear, Ring-Gear and
Planets supported
by Carriers, and linking with Input shaft 4, the Co-Axial-Output-Element-With-
Internal-
Gear/Planetary-Gear 65.
The following are the options to achieve this:
a) The Input shaft 4 is directly linked to the Sun-Gear of the planetary-Gear-
System with
following 2 sub-options
a. The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is
directly
linked to the Carrier of the Planetary-Gear-System and Ring-Gear of the
Planetary-Gear-System functions as the final output or wheel system 1022
b. The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is linked
to
the Ring-Gear of the Planetary-Gear-System and the Carrier functions as the
final
output or wheel system 1022.
b) The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is
directly linked to
the Sun-Gear of the Planetary-Gear-System with following 2 sub-options.
a. The Input shaft 4 is directly linked to the Carrier of the Planetary-Gear-
System
and the Ring-Gear of the Planetary-Gear-System functions as the final output
or wheel system
1022.
b. The Input shaft 4 is directly linked to the Ring-Gear of the Planetary-Gear-
System and the Carrier functions as the final output or wheel system.
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c) The Input shaft 4 is directly linked to the Ring-Gear of the planetary-Gear-
System with
following 2 sub-options
a. The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is
directly
linked to the Carrier of the Planetary-Gear-System and Sun-Gear of the
Planetary-
Gear-System functions as the final output or wheel system 1022.
b. The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is linked
to
the Sun-Gear of the Planetary-Gear-System and the Carrier functions as the
final
output or wheel system 1022.
d) The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is
directly linked to
the Ring-Gear of the Planetary-Gear-System with following 2 sub-options.
a. The Input shaft 4 is directly linked to the Carrier of the Planetary-Gear-
System
and the Carrier of the Planetary-Gear-System and the Sun-Gear of the Planetary-
Gear-System functions as the final output or wheel system 1022.
b. The Input shaft 4 is directly linked to the Sun-Gear of the Planetary-Gear-
System
and the Carrier functions as the final output or wheel system 1022.
e) The Input shaft 4 is directly linked to the Carrier of the planetary-Gear-
System with
following 2 sub-options
a. The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is
directly
linked to the Ring-Gear of the Planetary-Gear-System and Sun-Gear of the
Planetary-Gear-System functions as the final output or wheel system 1022.
b. The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is linked
to
the Sun-Gear of the Planetary-Gear-System and the Sun-Gear functions as the
final output or wheel system 1022.
f) The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear 65 is
directly linked to
the Carrier of the Planetary-Gear-System with following 2 sub-options.
a. The Input shaft 4 is directly linked to the Ring-Gear of the Planetary-Gear-
System and the Ring-Gear of the Planetary-Gear-System and the Sun-Gear of the
Planetary-Gear-System functions as the final output or wheel system 1022.
b. The Input shaft 4 is directly linked to the Sun-Gear of the Planetary-Gear-
System
and the Ring-Gear functions as the final output or wheel system 1022.
In other words, The Co-Axial-Output-Element-With-Internal-Gear/Planetary-Gear
65 is
connected to one of the three elements, either a Ring-Gear, a Carrier, or a
Sun-Gear of a
Planetary-Gear-System. The Input shaft 4 is connected to one of the remaining
two elements of
the Planetary-Gear-System. The third remaining element of the Planetary-System
functions as
the final output or wheel system 1022. This converts the CVT to an IVT.
COMPENSATING FOR DEVIATION IN RACK MOVEMENT WITH CAMS:
It is beneficial to have smooth and gradual transitions in the rack movement
profile to
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improve the life of the transmission. As shown in Fig. 23, the ideal rack
velocity profile is as
follows:
1. gradual increase in acceleration from rest 1025
2. a region of acceleration 1026
3. gradual reduction in acceleration to a constant velocity 1027
4. a region of constant velocity 1028
5. gradual increase in deceleration to a constant deceleration 1029
6. a region of deceleration 1030
7. gradual reduction in deceleration to zero velocity 1031
8. steps 1 through 7 above repeated in the opposite direction
It may not always be possible to generate perfect Geneva wheel mechanism to
meet the above desired Rack
12movement. If the slot curves 1006 of the Geneva slot wheel and the Geneva
pin wheel 6a & 6b do not to
achieve this desired Rack 12 movement, a planetary system can be used to
compensate for any deviations
from the desired Rack 12 movement profile. To achieve this, a Stationary Sun
Gear 36 with respective to the
ratio modifier frame 2 is placed co-axial with a driven circular or non-
circular gear 40 which is driven by a
driving circular or non-circular gear 39 as appropriate. This can be used in
addition to the Geneva wheel
system. This is shown in Fig.43A& 43B. This driving circular or non-circular
gear is mounted on the power
shaft 29. One or more Shaft-Cam 37 is placed on the driven circular or non-
circular gear 40 which acts like a
carrier of the planetary gear system. A Cam-Gear 38 is rigidly attached on the
Shaft-Cam 37. Each of this
Cam-Gear 38 is made to engage another Cam-Input-Shaft 41each. which is rigidly
attached on the Input shaft
8. The cams can be designed to give a desired rack velocity profile. The above
configuration will also work
when the stationary sun is replaced with a stationary ring gear. This is shown
in Fig. 44A&44B.
Mathematical Model
The following formula is used in pitch curve generation of the driving non-
circular gear and driven non-circular
gear, when expressed using Cartesian coordinates (X,,Y,) and (X2, Y2)
respectively, as a function of angle 19
are
CTR *cici>(9) &PO)
CTR * -
dB =
=-,--== cla *cos(9)
* sm(0);
1+ dcP09)
1+ dcP09)
di9 di9
CTR CTR
X2 =====-, ____________________________ * cos(1,(9)) , Y2
do (9) sin(l, (9));
1+ d(0)
1 + __________________________________________________________
d9 1+
where .4(6) is a solution to a piece-wise differential equation which gives
rotation ratio of the driving and
driven Geneva wheel system as well as the driving and driven non-circular
gears.
&I>
N * * sin(N * cP) =
function of any linear or nonlinear curve connecting points * 2 * N * , 0)
to (Click)
n
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i * 2 *
if ________________________________________ N * n < < 01i,
ki if 04i <0 <02,
function of any linear or nonlinear curve connecting points (02i3O)to (03i,
¨1(0
if 02i <
¨ki if 03. <0 <04.,
function of any linear or nonlinear curve connecting points (04i, 0) to
((i + 1)* 2 * 7T(i+1)*2*ir
=
N * n ____________________________________ , k1) if 04i < 0 < ____
N * n
Or
cicID
N * ¨cl0 * cos(N * cP) =
i * 2 * k1 if __ N * n < < 011,
function of any linear or nonlinear curve connecting points (04i,lci)to (02,-
10
if 0. <0 <02.,
¨k, if 0. <0 <0:,
function of any linear or nonlinear curve connecting points (03, ¨k1) to
(04i,k1)
if 03. <0 <04.,
(i + 1) * 2 * 7T
ki if 04i < 0 < ______________
N * n
where boundary conditions are
cl,(0) = 0;
((i + 1) * 2 * n-) = (i + 1) * 2 * n-
cl) ___________________________________________
N *72
CP (0ii) = ______________________________________ N +'P1;
* 2 * 7T
(02i) __________________________________________ N +3 ;
, i * 2 * 7T
N ___________________________________________________ +P3,
* 2 * n-
009,i) ¨ N __ + ;
Where,
CTR is a center-to-center distance of the driving non-circular gear and the
driven non-circular gear,
e is an angular displacement of the driving non-circular gear;
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WO 2021/163583
PCT/US2021/017984
16
(1) is an angular displacement of the driven non-circular gear;
i refers to an i-th revolution the input disk from 0 to N*n-1 with a 1st
rotation being i=0;
N is a number of times the input disk rotates when the driven non-circular
gear rotates once;
n is a number of times the driven non-circular gear rotates when the driving
non-circular gear rotates once;
regions where the piece-wise function for the rack velocity is constant are
functional regions and regions
where the piece-wise function for the rack velocity is not constant are non-
functional regions which can be
linear or non-linear functions of e;
191,,192,,193,,194, are specific angular positions of the driving non-circular
gear, the values of which are solved
for using a solution to the piece-wise differential equation;
01, CP2, CP3, CP4 are specific angular positions of the driven non-circular
gear corresponding to angular
positions 8, 82i, 83, 84i of the driving non-circular gear respectively, and
are a cutoff between the
functional and non-functional regions, values of ckl, cP2, 01,3, C1,4 which
can to be solved for by using arbitrary
values for 01192193,, 04, ;
and k, are constants, which are all equal.
CA 03165829 2022- 7- 22

Representative Drawing