NZ720917A - Linear gear shift power transfer mechanism - Google Patents
Linear gear shift power transfer mechanismInfo
- Publication number
- NZ720917A NZ720917A NZ720917A NZ72091716A NZ720917A NZ 720917 A NZ720917 A NZ 720917A NZ 720917 A NZ720917 A NZ 720917A NZ 72091716 A NZ72091716 A NZ 72091716A NZ 720917 A NZ720917 A NZ 720917A
- Authority
- NZ
- New Zealand
- Prior art keywords
- teardrop
- rotator
- shaped recesses
- balls
- power output
- Prior art date
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- Friction Gearing (AREA)
- Transmission Devices (AREA)
Abstract
A linear gear shift power transfer mechanism includes a gear shift unit; a power input clamp ring element having an inward-tilted power input ring surface, first teardrop-shaped recesses and first radial positioning hole; a power output clamp ring element having an inward-tilted power output ring surface, second teardrop-shaped recesses and second radial positioning hole; a first ball ring element whose first positioning ring element has a first positioning portion and bulging ring element each provided with limiting slots; a power input rotator having a third teardrop-shaped recesses and first axial positioning hole; a power output rotator having fourth teardrop-shaped recesses and second axial positioning hole; helical resilient elements having radial and axial positioning posts and received in bulging ring elements, with the radial positioning posts disposed in first and second radial positioning holes through the limiting slots, the axial positioning posts disposed in first and second axial positioning holes.
Description
LINEAR GEAR SHIFT POWER TRANSFER MECHANISM
FIELD OF THE INVENTION
The present invention relates to linear gear shift power transfer
mechanisms and more particularly to a linear gear shift power transfer
mechanism which is structurally simple and compact, incurs little transmission
loss, and never jerks while shifting gear.
BACKGROUND OF THE INVENTION
To adjust speed and reduce gasoline consumption, every means of
transportation nowadays is equipped with a gear shift mechanism. A conventional
gear shift mechanism transfers power with a gear train or with a gear train and an
oil duct. However, the gear train or the combination of the gear train and the oil
duct is structurally intricate and bulky, incurs much transmission loss, and tends to
jerk while shifting gear. Therefore, a stepless gear shift mechanism characterized
by two grooved wheels operating in conjunction with a V-shaped belt is developed.
However, the stepless gear shift mechanism has a disadvantage, namely large
volume of the grooved wheels and the V-shaped belt. Accordingly, the present
invention aims to disclose a linear gear shift power transfer mechanism which is
structurally simple and compact, incurs little transmission loss, and never jerks
while shifting gear.
SUMMARY OF THE INVENTION
In view of the aforesaid drawbacks of the prior art, the inventor of the
present invention recognized room for improvement in the prior art and thus
conducted extensive researches to therefore develop a linear gear shift power
transfer mechanism which is structurally simple and compact, incurs little
transmission loss, and never jerks while shifting gear.
The present invention provides a linear gear shift power transfer
mechanism which comprises: a gear shift unit having a support rotator, a plurality
of transmission balls and a plurality of driving posts, with the transmission balls
spaced apart from each other and movably disposed at the support rotator, the
transmission balls each having a cylindrical receiving portion along a radial
direction thereof, the driving posts having inward ends movably disposed in the
cylindrical receiving portions, respectively, along a radial direction of the support
rotator, and the driving posts driving the support rotator to rotate; a power input
clamp ring element having a lateral side provided with an inward-tilted power input
ring surface and another lateral side provided with first teardrop-shaped recesses
arranged annularly, wherein a first radial positioning hole is disposed at an inner
edge of the power input clamp ring element; a power output clamp ring element
having a lateral side provided with an inward-tilted power output ring surface and
another lateral side provided with annularly arranged second teardrop-shaped
recesses, wherein a second radial positioning hole is disposed at an inner edge of
the power output clamp ring element, with the transmission balls movably
clamped between the inward-tilted power input ring surface, the inward-tilted
power output ring surface and the support rotator, wherein heads of the first
teardrop-shaped recesses and heads of the second teardrop-shaped recesses
face same tangential direction; two first ball ring elements each having a plurality
of first balls and a first positioning ring element, with the first positioning ring
elements each having a plurality of first positioning portions whereby the first balls
are positioned, respectively, wherein a bulging ring element is disposed on an
inner edge of each said first positioning ring element and has a limiting slot; a
power input rotator having a lateral side provided with a first axial positioning hole
and annularly arranged third teardrop-shaped recesses, wherein heads of the
third teardrop-shaped recesses and heads of the first teardrop-shaped recesses
face opposite tangential directions, wherein the first balls of the first ball ring
elements are movably clamped between the first teardrop-shaped recesses and
the third teardrop-shaped recesses; a power output rotator having a lateral side
provided with a second axial positioning hole and annularly arranged fourth
teardrop-shaped recesses, wherein heads of the fourth teardrop-shaped recesses
and heads of the second teardrop-shaped recesses face opposite tangential
directions, wherein the first balls of the first ball ring elements are movably
clamped between the second teardrop-shaped recesses and the fourth
teardrop-shaped recesses; and two helical resilient elements each having two
ends provided with a radial positioning post and an axial positioning post,
respectively, the two helical resilient elements being received in the bulging ring
elements, respectively, with the radial positioning posts disposed in the first radial
positioning hole and the second radial positioning hole through the limiting slots,
respectively, and with the axial positioning posts disposed in the first axial
positioning hole and the second axial positioning hole, respectively.
Regarding the linear gear shift power transfer mechanism, the
inward-tilted power input ring surface and the inward-tilted power output ring
surface are disposed on two opposing sides of the transmission balls, respectively,
and the transmission balls are movably disposed on an outer circumferential
surface of the support rotator.
Regarding the linear gear shift power transfer mechanism, the driving
posts rotate from the radial direction of the support rotator to but not reach the
axial direction of the support rotator.
Regarding the linear gear shift power transfer mechanism, the power
input rotator and the power output rotator rotate in opposite directions.
Regarding the linear gear shift power transfer mechanism, the bulging
ring elements are received in the power input clamp ring element and the power
output clamp ring element, respectively.
Regarding the linear gear shift power transfer mechanism, the power
input rotator has a first connection shaft for pivotally connecting with a lateral side
of the support rotator, and the power output rotator has a second connection shaft
for pivotally connecting with another lateral side of the support rotator.
The linear gear shift power transfer mechanism, further comprises two
annular covers, two bearings and two second ball ring elements, with a power
input shaft disposed on another lateral side of the power input rotator, and a
power output shaft disposed on another lateral side of the power output rotator,
wherein the second ball ring elements each have a plurality of second balls and a
second positioning ring element, and the second positioning ring elements each
have a plurality of second positioning portions whereby the second balls are
positioned, respectively, wherein the bearings fit around the power input shaft and
the power output shaft, respectively, and the annular covers fit around the
bearings, respectively, wherein the second balls of the second ball ring elements
are movably clamped between the annular covers and the power input rotator and
between the annular covers and the power output rotator, respectively.
The present invention provides another linear gear shift power transfer
mechanism which comprises: a gear shift unit having a support rotator, a plurality
of transmission balls and a plurality of driving posts, with the transmission balls
spaced apart from each other and movably disposed at the support rotator, and a
cylindrical receiving portion disposed in a radial direction of each said
transmission ball, wherein the driving posts having inward ends movably disposed
in the cylindrical receiving portions, respectively, along a radial direction of the
support rotator, and the driving posts driving the support rotator to rotate; a power
input clamp ring element having a lateral side provided with an inward-tilted power
input ring surface and another lateral side provided with annularly arranged first
teardrop-shaped recesses and first connecting portions; a power output clamp
ring element having a lateral side provided with an inward-tilted power output ring
surface and another lateral side provided with annularly arranged second
teardrop-shaped recesses and second connecting portions, with the transmission
balls movably clamped between the inward-tilted power input ring surface, the
inward-tilted power output ring surface and the support rotator, wherein heads of
the first teardrop-shaped recesses and heads of the second teardrop-shaped
recesses face opposite tangential directions; a first ball ring element having a
plurality of first balls and a first positioning ring element, with the first positioning
ring element having a plurality of first positioning portions whereby the first balls
are positioned, respectively; a second ball ring element having a plurality of
second balls and a second positioning ring element, with the second positioning
ring element having a plurality of second positioning portions whereby the second
balls are positioned, respectively; a power input rotator having a lateral side
provided with annularly arranged third teardrop-shaped recesses and third
connecting portions, wherein heads of the third teardrop-shaped recesses and
heads of the first teardrop-shaped recesses face opposite tangential directions,
and the first balls of the first ball ring element are movably clamped between the
first teardrop-shaped recesses and the third teardrop-shaped recesses; a power
output rotator having a lateral side provided with annularly arranged fourth
teardrop-shaped recesses and fourth connecting portions, wherein heads of the
fourth teardrop-shaped recesses and heads of the second teardrop-shaped
recesses face opposite tangential directions, and the second balls of the second
ball ring element are movably clamped between the second teardrop-shaped
recesses and the fourth teardrop-shaped recesses; and a plurality of elastic
elements connected between the first connecting portions and the third
connecting portions and between the second connecting portions and the fourth
connecting portions, respectively.
Regarding the other linear gear shift power transfer mechanism, the
inward-tilted power input ring surface and the inward-tilted power output ring
surface are positioned on the same side of the transmission balls, wherein a
lateral ring surface of the support rotator is positioned beside the transmission
balls in a manner to be opposite to the inward-tilted power input ring surface and
the inward-tilted power output ring surface.
Regarding the other linear gear shift power transfer mechanism, further
comprises a fourth ball ring element having a plurality of fourth balls and a fourth
positioning ring element, with the fourth positioning ring element having a plurality
of fourth positioning portions whereby the fourth balls are positioned, respectively,
wherein the fourth balls of the fourth positioning ring element are movably
clamped between the power input rotator and the power output rotator.
Regarding the other linear gear shift power transfer mechanism, further
comprises two annular covers, two bearings and two third ball ring elements, with
a power input shaft disposed on another lateral side of the power input rotator,
and a power output shaft disposed on another lateral side of the power output
rotator, wherein the third ball ring elements each have a plurality of third balls and
a third positioning ring element, and the third positioning ring elements each have
a plurality of third positioning portions whereby the third balls are positioned,
respectively, wherein the bearings fit around the power input shaft and the power
output shaft, respectively, and the annular covers fit around the bearings,
respectively, wherein the third balls of the third ball ring elements are movably
clamped between the annular covers and the support rotator and between the
annular covers and the power output rotator, respectively.
Regarding the other linear gear shift power transfer mechanism, the
driving posts rotate from the radial direction of the support rotator to but not reach
the axial direction of the support rotator.
Regarding the other linear gear shift power transfer mechanism, the
power input rotator and the power output rotator rotate in the same direction.
Regarding the other linear gear shift power transfer mechanism, the first
connecting portions and the second connecting portions are each a bulging
structure, wherein the third connecting portions and the fourth connecting portions
are each a U-shaped receiving structure, with the bulging structures disposed at
openings of the U-shaped receiving structures, respectively, and the elastic
elements disposed in the U-shaped receiving structures, respectively.
Therefore, the linear gear shift power transfer mechanism of the present
invention is structurally simple and compact, incurs little transmission loss, and
never jerks while shifting gear.
BRIEF DESCRIPTION OF THE DRAWINGS
Objectives, features, and advantages of the present invention are
hereunder illustrated with specific embodiments in conjunction with the
accompanying drawings, in which:
is an exploded view of a preferred embodiment of the present
invention;
is an exploded view of a preferred embodiment of the present
invention from another angle of view;
is an exploded view of a preferred embodiment of the present
invention from yet another angle of view;
is a cross-sectional view of a gear shift unit, a power input clamp
ring element and a power output clamp ring element according to a preferred
embodiment of the present invention;
is a partial assembled schematic view of a preferred embodiment
of the present invention;
is a partial assembled schematic view of a preferred embodiment
of the present invention from another angle of view;
is an assembled schematic view of a preferred embodiment of the
present invention;
is an assembled schematic view of a preferred embodiment of the
present invention from another angle of view;
is an exploded view of another preferred embodiment of the
present invention;
is an exploded view of another preferred embodiment of the
present invention from another angle of view;
is a partial assembled schematic view of another preferred
embodiment of the present invention;
is a partial assembled schematic view of another preferred
embodiment of the present invention from another angle of view;
is a cross-sectional view of a gear shift unit, a power input clamp
ring element and a power output clamp ring element according to another
preferred embodiment of the present invention;
is another partial assembled schematic view of another
preferred embodiment of the present invention;
is another partial assembled schematic view of another
preferred embodiment of the present invention from another angle of view;
is an assembled schematic view of another preferred
embodiment of the present invention;
is an assembled schematic view of another preferred
embodiment of the present invention from another angle of view; and
is a cross-sectional view of elastic elements and first through
fourth connecting portions according to another preferred embodiment of the
present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring to through to illustrate how transmission balls 13,
driving posts 12, a power input clamp ring element 2 and a power output clamp
ring element 3 are connected, shows only how a transmission ball 13 and a
driving post 12 are connected to the power input clamp ring element 2 and the
power output clamp ring element 3, because the other transmission balls and
driving posts not shown are connected in the same way as illustrated with
As shown in the diagrams, the present invention provides a linear gear shift power
transfer mechanism which comprises a gear shift unit 1, a power input clamp ring
element 2, a power output clamp ring element 3, two first ball ring elements 4, a
power input rotator 5, a power output rotator 6 and two helical resilient elements 7.
The gear shift unit 1 has a driving ring element 11, a plurality of driving posts 12, a
plurality of transmission balls 13 and a support rotator 14. The transmission balls
13 are spaced apart from each other by the same angle of circumference and
movably disposed on the outer circumferential surface of the support rotator 14. A
cylindrical receiving portion 131 is disposed on each transmission ball 13 along
the radial direction thereof. The cylindrical receiving portion 131 is a cylindrical
receiving recess. The driving posts 12 have inward ends movably disposed in the
cylindrical receiving portion 131, respectively, along the radial direction of the
support rotator 14. The outward ends of the driving posts 12 are pivotally
connected to the driving ring element 11 and spaced apart from each other by the
same angle of circumference. The driving ring element 11 undergoes translation
in the axial direction of the support rotator 14 to drive the driving posts 12 and the
transmission balls 13 to rotate clockwise or counterclockwise from the radial
direction of the support rotator 14 to but not reach the axial direction of the support
rotator 14. An inward-tilted power input ring surface 21 is disposed in the vicinity
of the outer edge of a lateral side of the power input clamp ring element 2.
Annularly arranged first teardrop-shaped recesses 22 are disposed in the vicinity
of the outer edge of the other lateral side of the power input clamp ring element 2.
A first radial positioning hole 23 is disposed at the inner edge of the power input
clamp ring element 2. An inward-tilted power output ring surface 31 is disposed in
the vicinity of the outer edge of a lateral side of the power output clamp ring
element 3. Annularly arranged second teardrop-shaped recesses 32 are disposed
in the vicinity of the outer edge of the other lateral side of the power output clamp
ring element 3. A second radial positioning hole 33 is disposed at the inner edge
of the power output clamp ring element 3. The inward-tilted power input ring
surface 21 and the inward-tilted power output ring surface 31 are disposed on two
opposing sides of the transmission balls 13, respectively. The transmission balls
13 are movably disposed on the outer circumferential surface of the support
rotator 14. The transmission balls 13 are movably clamped between the
inward-tilted power input ring surface 21, the inward-tilted power output ring
surface 31 and the outer circumferential surface of the support rotator 14. The
heads of the first teardrop-shaped recesses 22 and the heads of the second
teardrop-shaped recesses 32 face the same tangential direction. The first ball ring
elements 4 each have a plurality of first balls 41 and a first positioning ring
element 42. The first positioning ring elements 42 each have a plurality of first
positioning portions 421 whereby the first balls 41 are positioned, respectively.
The first positioning portions 421 are spaced apart from each other by the same
angle of circumference. The first positioning portions 421 are recesses or through
holes. A bulging ring element 422 is disposed on the lateral side of the inner edge
of each first positioning ring element 42. The bulging ring elements 422 each have
a limiting slot 423. The power input rotator 5 has a lateral side provided with a first
axial positioning hole 52 and annularly arranged third teardrop-shaped recesses
51. The third teardrop-shaped recesses 51 are disposed in the vicinity of the outer
edge of the power input rotator 5. The heads of the third teardrop-shaped
recesses 51 and the heads of the first teardrop-shaped recesses 22 face opposite
tangential directions. The first balls 41 of the first ball ring elements 4 are movably
clamped between the first teardrop-shaped recesses 22 and the third
teardrop-shaped recesses 51. The diameter of the first balls 41 is slightly less
than the diameter of the heads of the first teardrop-shaped recesses 22 and the
diameter of the heads of the third teardrop-shaped recesses 51. The power output
rotator 6 has a lateral side provided with a second axial positioning hole 62 and
annularly arranged fourth teardrop-shaped recesses 61. The fourth
teardrop-shaped recesses 61 are disposed in the vicinity of the outer edge of the
power output rotator 6. The heads of the fourth teardrop-shaped recesses 61 and
the heads of the second teardrop-shaped recesses 32 face opposite tangential
directions. The first balls 41 of the first ball ring elements 4 are movably clamped
between the second teardrop-shaped recesses 32 and the fourth
teardrop-shaped recesses 61. The diameter of the first balls 41 is slightly less
than the diameter of the heads of the second teardrop-shaped recesses 32 and
the diameter of the heads of the fourth teardrop-shaped recesses 61. A radial
positioning post 71 and an axial positioning post 72 are disposed at the two ends
of each helical resilient element 7, respectively. The helical resilient elements 7
are received in the bulging ring elements 422, respectively. The radial positioning
posts 71 are disposed in the first radial positioning hole 23 and the second radial
positioning hole 33 through the limiting slots 423, respectively. The axial
positioning posts 72 are disposed in the first axial positioning hole 52 and the
second axial positioning hole 62, respectively.
Referring to and when the power input rotator 5 has not
transferred power, the helical resilient elements 7 cause the first balls 41 of the
first ball ring elements 4 to stay with the heads of the first teardrop-shaped
recesses 22 and the heads of the third teardrop-shaped recesses 51 (as shown in
. When the power input rotator 5 transfers power (by rotating
counterclockwise), the first balls 41 of the first ball ring elements 4 move from the
heads of the first teardrop-shaped recesses 22 and the heads of the third
teardrop-shaped recesses 51 to the tails of the first teardrop-shaped recesses 22
and the tails of the third teardrop-shaped recesses 51 (as shown in , such
that the power input clamp ring element 2 moves in the axial direction of the
support rotator 14 and toward the transmission balls 13 to therefore pull the two
ends of each helical resilient element 7 away from each other. Similarly, when the
power output rotator 6 has not transferred power, the helical resilient elements 7
cause the first balls 41 of the first ball ring elements 4 to stay with the heads of the
second teardrop-shaped recesses 32 (as shown in and the heads of the
fourth teardrop-shaped recesses 61. When the power output rotator 6 are driven
by the power input rotator 5, the power input clamp ring element 2, the
transmission balls 13 and the power output clamp ring element 3 (as shown in
to move and transfer power (by rotating clockwise), the first balls 41 of the
first ball ring elements 4 move from the heads of the second teardrop-shaped
recesses 32 and the heads of the fourth teardrop-shaped recesses 61 toward the
tails of the second teardrop-shaped recesses 32 (as shown in and the tails
of the fourth teardrop-shaped recesses 61, such that the power output clamp ring
element 3 moves in the axial direction of the support rotator 14 and toward the
transmission balls 13 to therefore pull the two ends of each helical resilient
element 7 away from each other. Afterward, the transmission balls 13 are
movably clamped between the inward-tilted power input ring surface 21, the
inward-tilted power output ring surface 31 and the outer circumferential surface of
the support rotator 14. Then, the power of the power input rotator 5 is transferred
to the power output rotator 6 through the power input clamp ring element 2, the
transmission balls 14 and the power output clamp ring element 3. The power input
rotator 5 drives the power input clamp ring element 2 to rotate counterclockwise.
The power input clamp ring element 2 drives the transmission balls 13 to rotate
clockwise. The transmission balls 13 drive the power output clamp ring element 3
and the power output rotator 6 to rotate clockwise.
As described before, since the transmission balls 13 come into smooth
contact with the inward-tilted power input ring surface 21, and the inward-tilted
power output ring surface 31 comes into smooth contact with the circumferential
surface of the support rotator 14, the linear gear shift power transfer mechanism
of the present invention is structurally simple and compact, incurs little
transmission loss, and never jerks while shifting gear.
Referring to and and the above description, regarding the
linear gear shift power transfer mechanism, the power input rotator 5 and the
power output rotator 6 rotate in opposite directions.
Referring to and regarding the linear gear
shift power transfer mechanism, the bulging ring elements 422 are received in the
power input clamp ring element 2 and the power output clamp ring element 3,
respectively. Therefore, the linear gear shift power transfer mechanism of the
present invention is capable of reducing width and reducing volume.
Referring to and regarding the linear gear shift power
transfer mechanism, the power input rotator 5 has a first connection shaft 54 for
pivotally connecting with a bearing 141 disposed on a lateral side of the support
rotator 14. The power output rotator 6 has a second connection shaft 64 for
pivotally connecting with another bearing 141 disposed on the other lateral side of
the support rotator 14. Therefore, the support rotator 14 is supported by the power
input rotator 5 and the power output rotator 6, whereas the power input rotator 5
and the power output rotator 6 connect with each other and rotate in reverse
direction.
Referring to and the linear gear shift power
transfer mechanism further comprises two annular covers 81, two bearings 82
and two second ball ring elements 83. A power input shaft 53 is disposed on the
other lateral side of the power input rotator 5. A power output shaft 63 is disposed
on the other lateral side of the power output rotator 6. The second ball ring
elements 83 each have a plurality of second balls 831 and a second positioning
ring element 832. The second positioning ring elements 832 each have a plurality
of second positioning portions 833 whereby the second balls 831 are positioned,
respectively. The second positioning portions 833 are recesses or through holes.
The bearings 82 fit around the power input shaft 53 and the power output shaft 63,
respectively. The annular covers 81 fit around the bearings 82, respectively. The
second balls 831 of the second ball ring elements 83 are movably clamped
between the recesses of the annular covers 81 and recess of the power input
rotator 5 and between the recesses of the annular covers 81 and recess of the
power output rotator 6.
Referring to through , to illustrate how transmission balls
13, driving posts 12, power input clamp ring element 2 and power output clamp
ring element 3 are connected, shows only how two transmission balls 13
and two driving posts 12 are connected to the power input clamp ring element 2
and power output clamp ring element 3, because the other transmission balls and
driving posts not shown are connected in the same way as illustrated with .
As shown in the diagrams, the present invention provides another linear gear shift
power transfer mechanism which comprises a gear shift unit 1, a power input
clamp ring element 2, a power output clamp ring element 3, a first ball ring
element 4, a second ball ring element 43, a power input rotator 5, a power output
rotator 6 and a plurality of elastic elements 56, 66. The gear shift unit 1 has a
driving ring element 11, a plurality of driving posts 12, a plurality of transmission
balls 13 and a support rotator 14. The transmission balls 13 are spaced apart from
each other by the same angle of circumference and movably disposed on a lateral
ring surface 142 of the support rotator 14. The lateral ring surface 142 is
concaved and curved to thereby operate in conjunction with the transmission balls
13. The transmission balls 13 each have a cylindrical receiving portion 131 along
the radial direction thereof. The cylindrical receiving portion 131 is a cylindrical
receiving recess or a cylindrical receiving channel. The driving posts 12 have
inward ends movably disposed in the cylindrical receiving portion 131,
respectively, along the radial direction of the support rotator 14. The outward ends
of the driving posts 12 are pivotally connected to a plurality of pivotal through
holes 111 of the driving ring element 11 and spaced apart from each other by the
same angle of circumference. The driving ring element 11 undergoes translation
in the axial direction of the support rotator 14 to drive the driving posts 12 and the
transmission balls 13 to rotate clockwise or counterclockwise from the radial
direction of the support rotator 14 to but not reach the axial direction of the support
rotator 14. The power input clamp ring element 2 has a lateral side provided with
an inward-tilted power input ring surface 21 and the other lateral side provided
with annularly arranged first teardrop-shaped recesses 22 and first connecting
portions 24. The power output clamp ring element 3 has a lateral side provided
with an inward-tilted power output ring surface 31 and the other lateral side
provided with annularly arranged second teardrop-shaped recesses 32 and
second connecting portions 34. The inward-tilted power input ring surface 21 of
the power input clamp ring element 2 is positioned inward to the inward-tilted
power output ring surface 31 of the power output clamp ring element 3. Both the
inward-tilted power input ring surface 21 of the power input clamp ring element 2
and the inward-tilted power output ring surface 31 of the power output clamp ring
element 3 are positioned on the same side of the transmission balls 13. The
lateral ring surface 142 of the support rotator 14 is positioned beside the
transmission balls 13 in a manner to be opposite to the inward-tilted power input
ring surface 21 and the inward-tilted power output ring surface 31. The
transmission balls 13 are movably clamped between the inward-tilted power input
ring surface 21, the inward-tilted power output ring surface 31, and the lateral ring
surface 142 of the support rotator 14. The heads of the first teardrop-shaped
recesses 22 and the heads of the second teardrop-shaped recesses 32 face
opposite tangential directions. The first ball ring element 4 has a plurality of first
balls 41 and a first positioning ring element 42. The first positioning ring element
42 has a plurality of first positioning portions 421 whereby the first balls 41 are
positioned, respectively. The first positioning portions 421 are spaced apart from
each other by the same angle of circumference. The first positioning portions 421
are recesses or through holes. The second ball ring element 43 has a plurality of
second balls 431 and a second positioning ring element 432. The second
positioning ring element 432 has a plurality of second positioning portions 433
whereby the second balls 431 are positioned, respectively. The second
positioning portions 433 are spaced apart from each other by the same angle of
circumference. The second positioning portions 433 are recessed or through
holes. The first ball ring element 4 is disposed inside the second ball ring element
43. The power input rotator 5 has a lateral side provided with annularly arranged
third teardrop-shaped recesses 51 and third connecting portions 55. The third
teardrop-shaped recesses 51 and the third connecting portions 55 are disposed in
the vicinity of the outer edge of the power input rotator 5. The heads of the third
teardrop-shaped recesses 51 and the heads of the first teardrop-shaped recesses
22 face opposite tangential directions. The first balls 41 of the first ball ring
element 4 are movably clamped between the first teardrop-shaped recesses 22
and the third teardrop-shaped recesses 51. The diameter of the first balls 41 is
slightly less than the diameter of the heads of the first teardrop-shaped recesses
22 and the diameter of the heads of the third teardrop-shaped recesses 51. The
power output rotator 6 has a lateral side provided with annularly arranged fourth
teardrop-shaped recesses 61 and fourth connecting portions 65. The fourth
teardrop-shaped recesses 61 and the fourth connecting portions 65 are disposed
in the vicinity of the outer edge of the power output rotator 6. The heads of the
fourth teardrop-shaped recesses 61 and the heads of the second
teardrop-shaped recesses 32 face opposite tangential directions. The second
balls 431 of the second ball ring element 43 are movably clamped between the
second teardrop-shaped recesses 32 and the fourth teardrop-shaped recesses 61.
The diameter of the second balls 431 is slightly less than the diameter of the
heads of the second teardrop-shaped recesses 32 and the diameter of the heads
of the fourth teardrop-shaped recesses 61. The power output rotator 6 is
cap-shaped. The power input rotator 5 is disposed inside the power output rotator
6. The elastic elements 56, 66 are connected between the first connecting
portions 24 and the third connecting portions 55 and between the second
connecting portions 34 and the fourth connecting portions 65, respectively.
Referring to and , when the power input rotator 5 has not
transferred power, the elastic elements 56 cause the first balls 41 of the first ball
ring element 4 to stay with the heads of the first teardrop-shaped recesses 22 (as
shown in ) and the heads of the third teardrop-shaped recesses 51. When
the power input rotator 5 transfers power (by rotating clockwise), the first balls 41
of the first ball ring element 4 move from the heads of the first teardrop-shaped
recesses 22 and the heads of the third teardrop-shaped recesses 51 toward the
tails of the first teardrop-shaped recesses 22 (as shown in ) and the tails of
the third teardrop-shaped recesses 51, such that the power input clamp ring
element 2 moves in the axial direction of the support rotator 14 and toward the
transmission balls 13 to therefore pull the two ends of each elastic element 56
away from each other. Similarly, when the power output rotator 6 has not
transferred power, the elastic elements 66 cause the second balls 431 of the
second ball ring element 43 to stay with the heads of the second teardrop-shaped
recesses 32 (as shown in ) and the heads of the fourth teardrop-shaped
recesses 61. When the power output rotator 6 is driven by the power input rotator
, the power input clamp ring element 2, the transmission balls 13 and the power
output clamp ring element 3 to move and transfer power (by rotating clockwise),
the second balls 431 of the second ball ring element 43 move from the heads of
the second teardrop-shaped recesses 32 and the heads of the fourth
teardrop-shaped recesses 61 toward the tails of the second teardrop-shaped
recesses 32 (as shown in ) and the tails of the fourth teardrop-shaped
recesses 61, such that the power output clamp ring element 3 moves in the axial
direction of the support rotator 14 and toward the transmission balls 13 to
therefore pull the two ends of each elastic element 66 away from each other.
Afterward, the transmission balls 13 are movably clamped between the
inward-tilted power input ring surface 21, the inward-tilted power output ring
surface 31 and the lateral ring surface 142 of the support rotator 14. Then, power
of the power input rotator 5 is transferred to the power output rotator 6 through the
power input clamp ring element 2, the transmission balls 14 and the power output
clamp ring element 3. The power input rotator 5 drives the power input clamp ring
element 2 and the transmission balls 13 to rotate clockwise. The transmission
balls 13 drive the power output clamp ring element 3 and the power output rotator
6 to rotate clockwise.
As described before, since the transmission balls 13 come into smooth
contact with the inward-tilted power input ring surface 21, and the inward-tilted
power output ring surface 31 comes into smooth contact with the lateral ring
surface 142 of the support rotator 14, the linear gear shift power transfer
mechanism of the present invention is structurally simple and compact, incurs
little transmission loss, and never jerks while shifting gear.
Referring to and and the above description, regarding the
other linear gear shift power transfer mechanism, the power input rotator 5 and
the power output rotator 6 rotate in the same direction.
Referring to through and , regarding the other
linear gear shift power transfer mechanism, the power input rotator 5 comes into
smooth contact with the power output rotator 6, and the other linear gear shift
power transfer mechanism further comprises a fourth ball ring element 44 having
a plurality of fourth balls 441 and a fourth positioning ring element 442. The fourth
positioning ring element 442 has a plurality of fourth positioning portions 443
whereby the fourth balls 441 are positioned, respectively. The fourth positioning
portions 443 are recesses or through holes. The fourth balls 441 of the fourth
positioning ring element 442 are movably clamped between the recess of the
power input rotator 5 and the recess of the power output rotator 6 to therefore
reduce the loss incurred by the friction between the power input rotator 5 and the
power output rotator 6.
Referring to , and , the other linear gear
shift power transfer mechanism further comprises two annular covers 81, two
bearings 82 and two third ball ring elements 84. A power input shaft 53 is
disposed on the other lateral side of the power input rotator 5. A power output
shaft 63 is disposed on the other lateral side of the power output rotator 6. The
third ball ring elements 84 each have a plurality of third balls 841 and a third
positioning ring element 842. The third positioning ring elements 842 each have a
plurality of third positioning portions 843 whereby the third balls 841 are
positioned, respectively. The third positioning portions 843 are recesses or
through holes. The bearings 82 fit around the power input shaft 53 and the power
output shaft 63, respectively. The annular covers 81 fit around the bearings 82,
respectively. The third balls 841 of the third ball ring elements 84 are movably
clamped between the recesses of the annular covers 81 and the recess of the
support rotator 14 and between the recesses of the annular covers 81 and the
recess of the power output rotator 6, respectively. The power input shaft 53
passes through the first ball ring element 4, the power input clamp ring element 2,
the transmission balls 14, the support rotator 14, the third ball ring elements 84,
the annular covers 81 and the bearings 82 to connect with a power input bevel
gear 85.
Referring to through , , and ,
regarding the other linear gear shift power transfer mechanism, the first
connecting portions 24 and the second connecting portions 34 are each a bulging
structure. The third connecting portions 55 and the fourth connecting portions 65
are each a U-shaped receiving structure. The elastic elements 56, 66 are each a
helical spring. The openings of the U-shaped receiving structures of the power
input rotator 5 and the openings of the U-shaped receiving structures of the power
output rotator 6 face opposite tangential directions. The bulging structures are
located at or in the vicinity of the openings of the U-shaped receiving structures,
respectively. The elastic elements 56, 66 are disposed inside the U-shaped
receiving structures, respectively. The two ends of the helical springs are fixedly
connected to the bulging structures and U-shaped ends of the U-shaped receiving
structures, respectively, such that the helical springs are firmly positioned.
The present invention is disclosed above by preferred embodiments.
However, persons skilled in the art should understand that the preferred
embodiments are illustrative of the present invention only, but should not be
interpreted as restrictive of the scope of the present invention. Hence, all
equivalent modifications and replacements made to the aforesaid embodiments
should fall within the scope of the present invention. Accordingly, the legal
protection for the present invention should be defined by the appended claims.
Claims (14)
1. A linear gear shift power transfer mechanism, comprising: a gear shift unit having a support rotator, a plurality of transmission balls and a plurality of driving posts, with the transmission balls spaced apart from each other and movably disposed at the support rotator, the transmission balls each having a cylindrical receiving portion along a radial direction thereof, the driving posts having inward ends movably disposed in the cylindrical receiving portions, respectively, along a radial direction of the support rotator, and the driving posts driving the support rotator to rotate; a power input clamp ring element having a lateral side provided with an inward-tilted power input ring surface and another lateral side provided with first teardrop-shaped recesses arranged annularly, wherein a first radial positioning hole is disposed at an inner edge of the power input clamp ring element; a power output clamp ring element having a lateral side provided with an inward-tilted power output ring surface and another lateral side provided with annularly arranged second teardrop-shaped recesses, wherein a second radial positioning hole is disposed at an inner edge of the power output clamp ring element, with the transmission balls movably clamped between the inward-tilted power input ring surface, the inward-tilted power output ring surface and the support rotator, wherein heads of the first teardrop-shaped recesses and heads of the second teardrop-shaped recesses face same tangential direction; two first ball ring elements each having a plurality of first balls and a first positioning ring element, with the first positioning ring elements each having a plurality of first positioning portions whereby the first balls are positioned, respectively, wherein a bulging ring element is disposed on an inner edge of each said first positioning ring element and has a limiting slot; a power input rotator having a lateral side provided with a first axial positioning hole and annularly arranged third teardrop-shaped recesses, wherein heads of the third teardrop-shaped recesses and heads of the first teardrop-shaped recesses face opposite tangential directions, wherein the first balls of the first ball ring elements are movably clamped between the first teardrop-shaped recesses and the third teardrop-shaped recesses; a power output rotator having a lateral side provided with a second axial positioning hole and annularly arranged fourth teardrop-shaped recesses, wherein heads of the fourth teardrop-shaped recesses and heads of the second teardrop-shaped recesses face opposite tangential directions, wherein the first balls of the first ball ring elements are movably clamped between the second teardrop-shaped recesses and the fourth teardrop-shaped recesses; and two helical resilient elements each having two ends provided with a radial positioning post and an axial positioning post, respectively, the two helical resilient elements being received in the bulging ring elements, respectively, with the radial positioning posts disposed in the first radial positioning hole and the second radial positioning hole through the limiting slots, respectively, and with the axial positioning posts disposed in the first axial positioning hole and the second axial positioning hole, respectively.
2. The linear gear shift power transfer mechanism of claim 1, wherein the inward-tilted power input ring surface and the inward-tilted power output ring surface are disposed on two opposing sides of the transmission balls, respectively, and the transmission balls are movably disposed on an outer circumferential surface of the support rotator.
3. The linear gear shift power transfer mechanism of claim 1, wherein the driving posts rotate from the radial direction of the support rotator to but not reach the axial direction of the support rotator.
4. The linear gear shift power transfer mechanism of claim 1, wherein the power input rotator and the power output rotator rotate in opposite directions.
5. The linear gear shift power transfer mechanism of claim 1, wherein the bulging ring elements are received in the power input clamp ring element and the power output clamp ring element, respectively.
6. The linear gear shift power transfer mechanism of claim 1, wherein the power input rotator has a first connection shaft for pivotally connecting with a lateral side of the support rotator, and the power output rotator has a second connection shaft for pivotally connecting with another lateral side of the support rotator.
7. The linear gear shift power transfer mechanism of claim 1, wherein further comprising two annular covers, two bearings and two second ball ring elements, with a power input shaft disposed on another lateral side of the power input rotator, and a power output shaft disposed on another lateral side of the power output rotator, wherein the second ball ring elements each have a plurality of second balls and a second positioning ring element, and the second positioning ring elements each have a plurality of second positioning portions whereby the second balls are positioned, respectively, wherein the bearings fit around the power input shaft and the power output shaft, respectively, and the annular covers fit around the bearings, respectively, wherein the second balls of the second ball ring elements are movably clamped between the annular covers and the power input rotator and between the annular covers and the power output rotator, respectively.
8. A linear gear shift power transfer mechanism, comprising: a gear shift unit having a support rotator, a plurality of transmission balls and a plurality of driving posts, with the transmission balls spaced apart from each other and movably disposed at the support rotator, and a cylindrical receiving portion disposed in a radial direction of each said transmission ball, wherein the driving posts having inward ends movably disposed in the cylindrical receiving portions, respectively, along a radial direction of the support rotator, and the driving posts driving the support rotator to rotate; a power input clamp ring element having a lateral side provided with an inward-tilted power input ring surface and another lateral side provided with annularly arranged first teardrop-shaped recesses and first connecting portions; a power output clamp ring element having a lateral side provided with an inward-tilted power output ring surface and another lateral side provided with annularly arranged second teardrop-shaped recesses and second connecting portions, with the transmission balls movably clamped between the inward-tilted power input ring surface, the inward-tilted power output ring surface and the support rotator, wherein heads of the first teardrop-shaped recesses and heads of the second teardrop-shaped recesses face opposite tangential directions; a first ball ring element having a plurality of first balls and a first positioning ring element, with the first positioning ring element having a plurality of first positioning portions whereby the first balls are positioned, respectively; a second ball ring element having a plurality of second balls and a second positioning ring element, with the second positioning ring element having a plurality of second positioning portions whereby the second balls are positioned, respectively; a power input rotator having a lateral side provided with annularly arranged third teardrop-shaped recesses and third connecting portions, wherein heads of the third teardrop-shaped recesses and heads of the first teardrop-shaped recesses face opposite tangential directions, and the first balls of the first ball ring element are movably clamped between the first teardrop-shaped recesses and the third teardrop-shaped recesses; a power output rotator having a lateral side provided with annularly arranged fourth teardrop-shaped recesses and fourth connecting portions, wherein heads of the fourth teardrop-shaped recesses and heads of the second teardrop-shaped recesses face opposite tangential directions, and the second balls of the second ball ring element are movably clamped between the second teardrop-shaped recesses and the fourth teardrop-shaped recesses; and a plurality of elastic elements connected between the first connecting portions and the third connecting portions and between the second connecting portions and the fourth connecting portions, respectively.
9. The linear gear shift power transfer mechanism of claim 8, wherein the inward-tilted power input ring surface and the inward-tilted power output ring surface are positioned on same side of the transmission balls, wherein a lateral ring surface of the support rotator is positioned beside the transmission balls in a manner to be opposite to the inward-tilted power input ring surface and the inward-tilted power output ring surface.
10. The linear gear shift power transfer mechanism of claim 9, further comprising a fourth ball ring element having a plurality of fourth balls and a fourth positioning ring element, with the fourth positioning ring element having a plurality of fourth positioning portions whereby the fourth balls are positioned, respectively, wherein the fourth balls of the fourth positioning ring element are movably clamped between the power input rotator and the power output rotator.
11. The linear gear shift power transfer mechanism of claim 9, further comprising two annular covers, two bearings and two third ball ring elements, with a power input shaft disposed on another lateral side of the power input rotator, and a power output shaft disposed on another lateral side of the power output rotator, wherein the third ball ring elements each have a plurality of third balls and a third positioning ring element, and the third positioning ring elements each have a plurality of third positioning portions whereby the third balls are positioned, respectively, wherein the bearings fit around the power input shaft and the power output shaft, respectively, and the annular covers fit around the bearings, respectively, wherein the third balls of the third ball ring elements are movably clamped between the annular covers and the support rotator and between the annular covers and the power output rotator, respectively.
12. The linear gear shift power transfer mechanism of claim 8, wherein the driving posts rotate from the radial direction of the support rotator to but not reach the axial direction of the support rotator.
13. The linear gear shift power transfer mechanism of claim 8, wherein the power input rotator and the power output rotator rotate in same direction.
14. The linear gear shift power transfer mechanism of claim 8, wherein the first connecting portions and the second connecting portions are each a bulging structure, wherein the third connecting portions and the fourth connecting portions are each a U-shaped receiving structure, with the bulging structures disposed at openings of the U-shaped receiving structures, respectively, and the elastic elements disposed in the U-shaped receiving structures, respectively.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TW104132813A TWI571576B (en) | 2015-09-21 | 2015-10-06 | Linear gear transmission mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| NZ720917A true NZ720917A (en) | 2016-11-25 |
Family
ID=57395722
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| NZ720917A NZ720917A (en) | 2015-10-06 | 2016-06-07 | Linear gear shift power transfer mechanism |
Country Status (7)
| Country | Link |
|---|---|
| AU (1) | AU2016203787B2 (en) |
| BR (1) | BR102016020632A2 (en) |
| CA (1) | CA2936459C (en) |
| MX (1) | MX2016011353A (en) |
| NZ (1) | NZ720917A (en) |
| TW (1) | TWI571576B (en) |
| ZA (1) | ZA201605096B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI652419B (en) * | 2017-10-31 | 2019-03-01 | 摩特動力工業股份有限公司 | Continuously variable stepless transmission |
| TWI648491B (en) * | 2017-11-21 | 2019-01-21 | 摩特動力工業股份有限公司 | Coaxial electric power stepless transmission |
| TWI653409B (en) | 2018-02-08 | 2019-03-11 | 摩特動力工業股份有限公司 | Bidirectional power transmission mechanism of stepless transmission |
| TWI663347B (en) | 2018-02-23 | 2019-06-21 | 摩特動力工業股份有限公司 | Bidirectional ramp type power transmission mechanism of stepless transmission |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3407687A (en) * | 1967-03-27 | 1968-10-29 | Hayashi Tadashi | Variable ratio power transmission device |
| CA2976893C (en) * | 2005-12-09 | 2019-03-12 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| WO2011101991A1 (en) * | 2010-02-22 | 2011-08-25 | トヨタ自動車株式会社 | Power transmission device |
| WO2012169056A1 (en) * | 2011-06-10 | 2012-12-13 | トヨタ自動車株式会社 | Continuously variable transmission |
| US9347532B2 (en) * | 2012-01-19 | 2016-05-24 | Dana Limited | Tilting ball variator continuously variable transmission torque vectoring device |
| TWM484652U (en) * | 2014-03-07 | 2014-08-21 | Motive Power Industry Co Ltd | Rolling vehicle continuously variable transmission device |
-
2015
- 2015-10-06 TW TW104132813A patent/TWI571576B/en active
-
2016
- 2016-06-07 AU AU2016203787A patent/AU2016203787B2/en not_active Ceased
- 2016-06-07 NZ NZ720917A patent/NZ720917A/en not_active IP Right Cessation
- 2016-07-19 CA CA2936459A patent/CA2936459C/en not_active Expired - Fee Related
- 2016-07-21 ZA ZA2016/05096A patent/ZA201605096B/en unknown
- 2016-09-02 MX MX2016011353A patent/MX2016011353A/en unknown
- 2016-09-06 BR BR102016020632A patent/BR102016020632A2/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| ZA201605096B (en) | 2017-07-26 |
| MX2016011353A (en) | 2017-04-05 |
| BR102016020632A2 (en) | 2017-04-25 |
| CA2936459A1 (en) | 2017-04-06 |
| AU2016203787A1 (en) | 2017-04-20 |
| CA2936459C (en) | 2017-08-15 |
| TWI571576B (en) | 2017-02-21 |
| AU2016203787B2 (en) | 2018-05-17 |
| TW201712254A (en) | 2017-04-01 |
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| PSEA | Patent sealed | ||
| LAPS | Patent lapsed |