Note: Descriptions are shown in the official language in which they were submitted.
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Attorney Docket No. 26779-26
LINEAR GEAR SHIFT MECHANISM
FIELD OF THE INVENTION
[0001] The present invention relates to linear gear shift mechanisms and more
particularly to a linear gear shift mechanism which is structurally simple and
compact, has a wide linear gear-changing range, incurs little transmission
loss,
and never jerks while shifting gear.
BACKGROUND OF THE INVENTION
[0002] To adjust speed and reduce gasoline consumption, every means of
transportation nowadays is equipped with a gear shift mechanism. A
conventional
gear shift mechanism essentially comprises a gear train or essentially
comprises
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, has a narrow
gear-changing range, 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 disadvantages, namely large
volume of the grooved wheels and the V-shaped belt, and a narrow
gear-changing range. Accordingly, the present invention aims to disclose a
linear
gear shift mechanism which is structurally simple and compact, has a wide
linear
gear-changing range, incurs little transmission loss, and never jerks while
shifting
gear.
Attorney Docket No. 26779-26
SUMMARY OF THE INVENTION
[0003] 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
mechanism which is structurally simple and compact, has a wide linear
gear-changing range, incurs little transmission loss, and never jerks while
shifting
gear.
[0004] The present invention provides a linear gear shift mechanism,
comprising: a support rotator; a plurality of transmission balls spaced apart
from
each other and movably disposed on an outer circumferential surface of the
support rotator, with a cylindrical recess disposed on each said transmission
ball
along a radial direction thereof; a plurality of driving posts with inward
ends
movably disposed in the cylindrical recesses along the radial direction of the
support rotator; a gear shift unit movably connected to outward ends of the
driving
posts and adapted to drive the driving posts to rotate from the radial
direction of
the support rotator towards but not reach the axial direction of the support
rotator;
an axial power input rotator having an inward-tilted power input annular
surface;
an axial power output rotator having an inward-tilted power output annular
surface,
wherein the axial power input rotator and the axial power output rotator are
disposed on two opposite sides of the transmission balls to movably clamp the
transmission balls between the inward-tilted power input annular surface, the
inward-tilted power output annular surface and the outer circumferential
surface of
the support rotator.
[0005] Regarding the linear gear shift mechanism, a first oil-guiding groove
is
disposed on a circumferential surface of each said driving post.
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[0006] Regarding the linear gear shift mechanism, the gear shift unit has a
driving ring pivotally connected to the outward ends of the driving posts and
capable of undergoing translation in an axial direction of the support
rotator.
[0007] Regarding the linear gear shift mechanism, the gear shift unit has two
halved driving rings which mesh with each other, with a plurality of cavities
disposed on each said halved driving ring to join and thereby form a plurality
of
pivotal through holes for pivotally connecting with the outward ends of the
driving
posts, wherein the halved driving rings undergo translation in an axial
direction of
the support rotator.
[0008] Regarding the linear gear shift mechanism, the axial power input
rotator
has a first connection shaft pivotally connected to one side of the support
rotator,
and the axial power output rotator has a second connection shaft pivotally
connected to the other side of the support rotator.
[0009] Regarding the linear gear shift mechanism, two bearings are disposed
on two sides of the support rotator, respectively, and connected to the first
connection shaft and the second connection shaft, respectively.
[0010] The present invention further provides another linear gear shift
mechanism, comprising: a support rotator; a plurality of transmission balls
spaced
apart from each other and movably disposed on a lateral annular surface of the
support rotator, wherein a cylindrical channel or a cylindrical recess is
disposed
on each said transmission ball along a radial direction thereof; a plurality
of driving
posts with inward ends movably penetrating the cylindrical channels along the
radial direction of the support rotator, respectively, or movably disposed in
the
cylindrical recesses along the radial direction of the support rotator,
respectively;
a gear shift unit movably connected to inward ends and outward ends of the
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driving posts when the inward ends of the driving posts movably penetrate the
cylindrical channels, respectively, and movably connected to the outward ends
of
the driving posts when the inward ends of the driving posts are movably
disposed
in the cylindrical recesses, respectively, wherein the gear shift unit drives
the
driving posts to rotate from the radial direction of the support rotator
towards but
not reach the axial direction of the support rotator; an axial power input
rotator
having an inward-tilted power input annular surface; and an axial power output
rotator having an inward-tilted power output annular surface, wherein the
axial
power input rotator and the axial power output rotator are disposed on a same
side of the transmission balls, whereas the support rotator is positioned
beside
the transmission balls in a manner to be opposite to the axial power input
rotator
and the axial power output rotator, so as to movably clamp the transmission
balls
between the inward-tilted power input annular surface, the inward-tilted power
output annular surface and the lateral annular surface of the support rotator.
[0011] Regarding the aforesaid linear gear shift mechanism, when the inward
ends of the driving posts movably penetrate the cylindrical channels,
respectively,
the gear shift unit has a driving ring and a limitator. A plurality of oblique
guide
slots is disposed on an inward annular surface of the driving ring. The
limitator
has a plurality of axial limiting through holes arranged in a manner to
surround an
axis of the support rotator. An axial guide opening is disposed on a radial
outward
side of each axial limiting through hole. An axial curved guide slot is
disposed on a
radial inward side of each axial limiting through hole. The driving ring is
movably
disposed outside the limitator. The transmission balls are movably confined to
the
axial limiting through holes, respectively. Two opposite sides of the
transmission
balls are exposed from two opposite sides of the axial limiting through holes
so as
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to movably come into contact with the inward-tilted power input annular
surface,
the inward-tilted power output annular surface and the lateral annular surface
of
the support rotator. The inward ends of the driving posts are movably disposed
in
the axial curved guide slots, respectively. The outward ends of the driving
posts
are movably disposed in the oblique guide slots through the axial guide
openings,
respectively, with the driving ring rotating about the !imitator by an axis of
the
support rotator.
[0012] Regarding the aforesaid linear gear shift mechanism, when the inward
ends of the driving posts are movably disposed in the cylindrical recesses,
respectively, the gear shift unit has a driving ring pivotally connected to
the
outward ends of the driving posts, thereby allowing the driving ring to
undergo
translation in an axial direction of the support rotator.
[0013] Regarding the aforesaid linear gear shift mechanism, when the inward
ends of the driving posts are movably disposed in the cylindrical recesses,
respectively, the gear shift unit has two halved driving rings which mesh with
each
other, with a plurality of cavities disposed on each said halved driving ring
and
adapted to join and thereby form a plurality of pivotal through holes for
pivotally
connecting with the outward ends of the driving posts. The halved driving
rings
undergo translation in an axial direction of the support rotator.
[0014] Regarding the aforesaid linear gear shift mechanism, the axial power
input rotator has an axial power input shaft which passes the transmission
balls
and penetrates the support rotator to get exposed from the support rotator.
[0015] The aforesaid linear gear shift mechanism further comprises a ball ring
which has a plurality of balls and a positioning ring. The balls are spaced
apart
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from each other, movably positioned at the positioning ring, and movably
clamped
between the axial power input rotator and the axial power output rotator.
[0016] Therefore, the linear gear shift mechanism of the present invention is
structurally simple and compact, has a wide linear gear-changing range, incurs
little transmission loss, and never jerks while shifting gear.
BRIEF DESCRIPTION OF THE DRAWINGS
[0017] Objectives, features, and advantages of the present invention are
hereunder illustrated with specific embodiments in conjunction with the
accompanying drawings, in which:
FIG. 1 is an exploded view of a preferred embodiment of the present
invention;
FIG. 2 is an exploded view of a preferred embodiment of the present
invention from another angle of view;
FIG. 3 is a perspective view of a preferred embodiment of the present
invention;
FIG. 4 is a perspective view of a preferred embodiment of the present
invention from another angle of view;
FIG. 5 includes cross-sectional views of a preferred embodiment of the
present invention;
FIG. 6 is an exploded view of another driving ring according to a
preferred embodiment of the present invention;
FIG. 7 is a perspective view of another driving ring according to a
preferred embodiment of the present invention;
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FIG. 8 is an exploded view of another preferred embodiment of the
present invention;
FIG. 9 is an exploded view of another preferred embodiment of the
present invention from another angle of view;
FIG. 10 is a perspective view of another preferred embodiment of the
present invention;
FIG. 11 is a perspective view of another preferred embodiment of the
present invention from another angle of view; and
FIG. 12 includes cross-sectional views of another preferred embodiment
of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0018] Referring to FIG. 1 through FIG. 5, to illustrate how transmission
balls 2
and a driving post 3 operate, FIG. 5 shows only how a transmission ball 2 and
a
driving post 3 operate, because the other transmission balls and the driving
post
also operate in the way shown in FIG. 5. As shown in the diagrams, the present
invention provides a linear gear shift mechanism which comprises a support
rotator 1, a plurality of transmission balls 2, a plurality of driving posts
3, a gear
shift unit 4, an axial power input rotator 5 and an axial power output rotator
6. The
transmission balls 2 are spaced apart from each other and movably disposed on
the outer circumferential surface of the support rotator 1. A cylindrical
recess 21 is
disposed on each transmission ball 2 along the radial direction thereof. The
inward ends of the driving posts 3 are movably disposed in the cylindrical
recesses 21 along the radial direction of the support rotator 1, respectively.
The
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outward ends of the driving posts 3 are exposed from the cylindrical recesses
21,
respectively. The gear shift unit 4 is movably connected to the outward ends
of
the driving posts 3 and adapted to drive the driving posts 3 to rotate from
the
radial direction of the support rotator 1 towards but not reach the axial
direction of
the support rotator 1. The axial power input rotator 5 has an inward-tilted
power
input annular surface 51. The axial power input rotator 5 is pivotally
connected to
one side of the support rotator 1. The axial power output rotator 6 has an
inward-tilted power output annular surface 61. The axial power output rotator
6 is
pivotally connected to another side of the support rotator 1. Referring to
FIG. 5,
the axial power input rotator 5 and the axial power output rotator 6 are
disposed
on two opposite sides of the transmission balls 2 to thereby movably clamp the
transmission balls 2 between the inward-tilted power input annular surface 51,
the
inward-tilted power output annular surface 61 and the outer circumferential
surface of the support rotator 1 and also clamp the other transmission balls
(not
shown) in the aforesaid manner. The axial power input rotator 5 and the axial
power output rotator 6 rotate in opposite directions.
[0019] Referring to FIG. 3, when the axial power input rotator 5 rotates
clockwise, the transmission balls 2 are driven by the inward-tilted power
input
annular surface 51 (shown in FIG. 2) of the axial power input rotator 5 to
rotate
counterclockwise, whereas the inward-tilted power output annular surface 61
(shown in FIG. 1) of the axial power output rotator 6 and the axial power
output
rotator 6 are driven by the transmission balls 2 to rotate counterclockwise;
when
the axial power input rotator 5 rotates counterclockwise, the transmission
balls 2
are driven by the inward-tilted power input annular surface 51 (shown in FIG.
2) of
the axial power input rotator 5 to rotate clockwise, whereas the inward-tilted
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power output annular surface 61 (shown in FIG. 1) of the axial power output
rotator 6 and the axial power output rotator 6 are driven by the transmission
balls
2 to rotate clockwise.
[0020] Referring to the middle diagram through the leftmost diagram of FIG. 5,
when the gear shift unit 4 drives the driving posts 3 to rotate
counterclockwise, the
driving posts' 3 inner ends that rotate counterclockwise on the outer
circumferential surface of the support rotator 1 while the transmission balls
2 are
prevented from planetary rotation around the support rotator 1 by the driving
ring
41 acting as a planetary carrier for the transmission balls 2; meanwhile, the
inward-tilted power input annular surface 51 of the axial power input rotator
5
comes into contact with the large circumference of the transmission balls 2,
whereas the inward-tilted power output annular surface 61 of the axial power
output rotator 6 comes into contact with the small circumference of the
transmission balls 2, thereby allowing the axial power input rotator 5 to be
of a
higher speed than the axial power output rotator 6; hence, the linear gear
shift
mechanism of the present invention effectuates deceleration whenever the
driving
posts 3 rotate counterclockwise. Referring to the middle diagram through the
rightmost diagram of FIG. 5, when the gear shift unit 4 drives the driving
posts 3 to
rotate clockwise, the driving posts' 3 inner ends that rotate clockwise on the
outer
circumferential surface of the support rotator 1 while the transmission balls
2 are
prevented from planetary rotation around the support rotator 1 by the driving
ring
41 acting as a planetary carrier for the transmission balls 2; meanwhile, the
inward-tilted power input annular surface 51 of the axial power input rotator
5
comes into contact with the small circumference of the transmission balls 2,
whereas the inward-tilted power output annular surface 61 of the axial power
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output rotator 6 comes into contact with the large circumference of the
transmission balls 2, thereby allowing the axial power input rotator 5 to be
of a
lower speed than the axial power output rotator 6; hence, the linear gear
shift
mechanism of the present invention effectuates acceleration whenever the
driving
posts 3 rotate clockwise. The operation of a driving post 3 and a transmission
ball
2 is described above. The other driving posts and transmission balls also
operate
in the aforesaid manner.
[0021] Referring to FIG. 5, the larger the distance between the axial power
input
rotator 5 and the axial power output rotator 6, the larger the angle by which
the
driving posts 3 can rotate. Hence, the linear gear shift mechanism of the
present
invention is not only structurally simple and compact but also has a wide
linear
gear-changing range. Furthermore, to enable the linear gear shift mechanism of
the present invention to change gear efficiently, the transmission balls 2
come into
contact with the inward-tilted power input annular surface 51 smoothly,
whereas
the inward-tilted power output annular surface 61 comes into contact with the
outer circumferential surface of the support rotator 1 smoothly. Therefore,
the
linear gear shift mechanism of the present invention incurs little
transmission loss
and never jerks while shifting gear.
[0022] Referring to FIG. 1 and FIG. 2, regarding the linear gear shift
mechanism,
a first oil-guiding groove 31 is disposed on the outer circumferential surface
of
each driving post 3. Therefore, a lubricant can be disposed between the
driving
posts 3 and the transmission balls 2 to reduce transmission loss.
[0023] Referring to FIG. 1 through FIG. 5, regarding the linear gear shift
mechanism, the gear shift unit 4 has a driving screw 42, a driving ring 41 and
at
least one guiding rod 43. The driving ring 41 is annular. After the driving
screw 42
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has been driven by a driving motor 421 to rotate, the outward ends of the
driving
posts 3 get pivotally connected to the driving ring 41 as soon as a pin 32
passes
through the two sides of a plurality of pivotal slots 411 on the lateral side
of the
driving ring 41. The guiding rod 43 is a post. The driving screw 42 penetrates
and
meshes with a threaded hole 412 of the driving ring 41. The guiding rod 43
movably penetrates a guide hole 413 of the driving ring 41. Referring to FIG.
1,
FIG. 3 and FIG. 5, the driving screw 42 drives the driving ring 41 to undergo
translation in the axial direction of the guiding rod 43 and the support
rotator 1,
such that the driving ring 41 drives the driving posts 3 and the transmission
balls 2
to rotate, thereby allowing the linear gear shift mechanism of the present
invention
to change gear. Furthermore, the guiding rod 43 is provided in the plural and
arranged symmetrically, such that the driving ring 41 moves in a balanced
manner
while being driven by the driving screw 42 to undergo translation.
[0024] Referring to FIG. 6 and FIG. 7, regarding the linear gear shift
mechanism,
the gear shift unit 4 has two halved driving rings 414 which mesh with each
other.
The halved driving rings 414 are annular. A plurality of cavities 4141 and a
plurality of semi-cylindrical notches 4142 are disposed on the lateral side of
each
halved driving ring 414. Each cavity 4141 is bilaterally in communication with
a
semi-cylindrical notch 4142. The cavities 4141 pair up to form a plurality of
pivotal
through holes 4143. The semi-cylindrical notches 4142 pair up to form a
plurality
of pivotal cylindrical passages (not shown). A pin 32 passes through the
outward
ends of the driving posts 3. The outward ends of the driving posts 3 are
movably
received in the pivotal through holes 4143, respectively. The two ends of each
pin
32 are movably received in the pivotal cylindrical passages, respectively,
such
that the outward ends of the driving posts 3 are pivotally connected to the
halved
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driving rings 414. Similarly, the halved driving rings 414 operate in
conjunction
with the driving screw 42, the driving motor 421 and the guiding rod 43, such
that
the driving screw 42 drives the halved driving rings 414 to undergo
translation in
the axial direction of the guiding rod 43 and the support rotator 1.
[0025] Referring to FIG. 1 and FIG. 2, regarding the linear gear shift
mechanism,
a second oil-guiding groove 431 is disposed on the circumferential surface of
each guiding rod 43. Therefore, a lubricant can be disposed between the
guiding
rod 43 and the driving ring 41 to reduce transmission loss.
[0026] Referring to FIG. 1 and FIG. 2, regarding the linear gear shift
mechanism,
the axial power input rotator 5 has a first connection shaft 52 pivotally
connected
to one side of the support rotator 1, whereas the axial power output rotator 6
has a
second connection shaft 62 pivotally connected to the other side of the
support
rotator 1. Therefore, the support rotator 1 is supported by the axial power
input
rotator 5 and the axial power output rotator 6, such that the axial power
input
rotator 5 and the axial power output rotator 6 connect with each other and
rotate
backward.
[0027] Referring to FIG. 1 and FIG. 2, regarding the linear gear shift
mechanism,
two bearings 11 are disposed on two sides of the support rotator 1,
respectively,
and connected to the first connection shaft 52 and the second connection shaft
62,
respectively. Therefore, the support rotator 1 is supported by the axial power
input
rotator 5 and the axial power output rotator 6, such that the axial power
input
rotator 5 and the axial power output rotator 6 connect with each other and
rotate
backward.
[0028] Referring to FIG. 8 through FIG. 12, to illustrate how transmission
balls 2
and driving posts 3 operate, FIG. 12 shows only how a transmission ball 2 and
a
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driving posts 3 operate, because the other transmission balls and driving
posts
also operate in the way shown in FIG. 12. As shown in the diagrams, the
present
invention provides another linear gear shift mechanism which comprises a
support rotator 1, a plurality of transmission balls 2, a plurality of driving
posts 3, a
gear shift unit 4, an axial power input rotator 5 and an axial power output
rotator 6.
The transmission balls 2 are spaced apart from each other and movably disposed
on a lateral annular surface 12 of the support rotator 1. The lateral annular
surface
12 is concaved and curved to thereby operate in conjunction with the
transmission
balls 2. A cylindrical channel 22 or a cylindrical recess 21 (shown in FIG. 5
and
FIG. 6) is disposed on each transmission ball 2 along the radial direction
thereof.
The inward ends of the driving posts 3 movably penetrate the cylindrical
channels
22, respectively, along the radial direction of the support rotator 1, and,
alternatively, the inward ends of the driving posts 3 are movably disposed in
the
cylindrical recesses 21, respectively, along the radial direction of the
support
rotator 1, as shown in FIG. 5 and FIG. 6. The outward ends of the driving
posts 3
are exposed from the cylindrical channels 22 or the cylindrical recesses 21,
respectively, as shown in FIG. 5 and FIG. 6. When the inward ends of the
driving
posts 3 movably penetrate the cylindrical channels 22, respectively, the gear
shift
unit 4 is movably connected to the inward ends and outward ends of the driving
posts 3. When the inward ends of the driving posts 3 are movably disposed in
the
cylindrical recesses 21, respectively, as shown in FIG. 5 and FIG. 6, the gear
shift
unit 4 is movably connected to the outward ends of the driving posts 3,
thereby
allowing the gear shift unit 4 to drive the driving posts 3 to rotate from the
axial
direction of the support rotator 1 towards but not reach the axial direction
of the
support rotator 1. The axial power input rotator 5 has an inward-tilted power
input
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annular surface 51. The axial power output rotator 6 has an inward-tilted
power
output annular surface 61. Referring to FIG. 12, the inward-tilted power input
annular surface 51 of the axial power input rotator 5 is positioned inward to
the
inward-tilted power output annular surface 61 of the axial power output
rotator 6,
and both the axial power input rotator 5 and the axial power output rotator 6
are
positioned on the same side of the transmission balls 2. The support rotator 1
is
positioned beside the transmission balls 2 in a manner to be opposite to the
axial
power input rotator 5 and the axial power output rotator 6. Hence, the
transmission balls 2 are movably clamped between the inward-tilted power input
annular surface 51, the inward-tilted power output annular surface 61 and the
lateral annular surface 12 of the support rotator 1, so are the other
transmission
balls not shown. The axial power input rotator 5 and the axial power output
rotator
6 rotate in the same directions.
[0029] Referring to FIG. 8, when the axial power input rotator 5 rotates
clockwise, the transmission balls 2 are driven by the inward-tilted power
input
annular surface 51 of the axial power input rotator 5 to rotate clockwise,
whereas
the inward-tilted power output annular surface 61 of the axial power output
rotator
6 and the axial power output rotator 6 are driven by the transmission balls 2
to
rotate clockwise; when the axial power input rotator 5 rotates
counterclockwise,
the transmission balls 2 are driven by the inward-tilted power input annular
surface 51 of the axial power input rotator 5 to rotate counterclockwise,
whereas
the inward-tilted power output annular surface 61 of the axial power output
rotator
6 and the axial power output rotator 6 are driven by the transmission balls 2
to
rotate counterclockwise.
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[0030] Referring to the middle diagram through the leftmost diagram of FIG.
12,
when the gear shift unit 4 drives the driving posts 3 to rotate
counterclockwise, the
driving posts' 3 inner ends that rotate counterclockwise on the lateral
annular
surface 12 of the support rotator 1 while the transmission balls 2 are
prevented
from planetary rotation around the support rotator 1 by the driving ring 45
acting
as a planetary carrier for the transmission balls 2; meanwhile, the inward-
tilted
power input annular surface 51 of the axial power input rotator 5 comes into
contact with the large circumference of the transmission balls 2, whereas the
inward-tilted power output annular surface 61 of the axial power output
rotator 6
comes into contact with the small circumference of the transmission balls 2,
thereby allowing the axial power input rotator 5 to be of a higher speed than
the
axial power output rotator 6; hence, another linear gear shift mechanism of
the
present invention effectuates deceleration whenever the driving posts 3
rotates
counterclockwise. Referring to the middle diagram through the rightmost
diagram
of FIG. 12, when the gear shift unit 4 drives the driving posts 3 to rotate
clockwise,
the driving posts' 3 also inner ends that rotate clockwise on the lateral
annular
surface 12 of the support rotator 1 while the transmission balls 2 are
prevented
from planetary rotation around the support rotator 1 by the driving ring 45
acting
as a planetary carrier for the transmission balls 2; meanwhile, the inward-
tilted
power input annular surface 51 of the axial power input rotator 5 comes into
contact with the small circumference of the transmission balls 2, whereas the
inward-tilted power output annular surface 61 of the axial power output
rotator 6
comes into contact with the large circumference of the transmission balls 2,
thereby allowing the axial power input rotator 5 to be of a lower speed than
the
axial power output rotator 6; hence, another linear gear shift mechanism of
the
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present invention effectuates acceleration whenever the driving posts 3
rotates
clockwise. The operation of a driving post 3 and a transmission ball 2 is
described
above. The other driving posts and transmission balls also operate in the
aforesaid manner.
[0031] Referring to FIG. 12, the larger the distance between the support
rotator
1, the axial power input rotator 5, and the axial power output rotator 6, the
larger
the angle by which the driving posts 3 can rotate. Hence, another linear gear
shift
mechanism of the present invention is not only structurally simple and compact
but also has a wide linear gear-changing range. Furthermore, to enable another
linear gear shift mechanism of the present invention to change gear
efficiently, the
transmission balls 2 come into contact with the inward-tilted power input
annular
surface 51 smoothly, whereas the inward-tilted power output annular surface 61
comes into contact with the lateral annular surface 12 of the support rotator
1
smoothly. Therefore, another linear gear shift mechanism of the present
invention
incurs little transmission loss and never jerks while shifting gear.
[0032] Referring to FIG. 8, FIG. 9 and FIG. 12, regarding the aforesaid linear
gear shift mechanism, in the situation where the inward ends of the driving
posts 3
movably penetrate the cylindrical channels 22, respectively, the gear shift
unit 4
has a driving ring 45 and a !imitator 46. As shown in FIG. 8 and FIG. 9, the
limitator 46 is divided into halves, whereas the axial limiting through holes
461, the
axial guide opening 462 and the axial curved guide slot 463 of the limitator
46 are
each divided into halves. The inward annular surface of the driving ring 45 is
arranged in a manner to curve to be become circular and has oblique guide
slots
451 which are spaced apart from each other. The limitator 46 is cylindrical
and
has a plurality of axial limiting through holes 461 arranged in a manner to
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surround the axis of the support rotator 1. The axial limiting through holes
461 are
each internally curved. An axial guide opening 462 is disposed on the radial
outward side of each axial limiting through hole 461. An axial curved guide
slot
463 is disposed on the radial inward side of each axial limiting through hole
461.
Referring to FIG. 12, the axial curved guide slot 463 sinks toward the axis
thereof
so as to become curved. The driving ring 45 is movably disposed outside the
limitator 46. The transmission balls 2 are movably confined to the axial
limiting
through holes 461, respectively. The two opposite sides of the transmission
balls
2 are exposed from the two opposite sides of the axial limiting through holes
461
so as to roll and come into contact with the inward-tilted power input annular
surface 51, the inward-tilted power output annular surface 61 and the lateral
annular surface 12 of the support rotator 1. The inward ends of the driving
posts 3
are movably disposed in the axial curved guide slots 463, respectively. The
outward ends of the driving posts 3 are movably disposed in the oblique guide
slots 451 through the axial guide openings 462, respectively. The driving ring
45
rotates about the !imitator 46 by the axis of the support rotator 1. Referring
to FIG.
8 and FIG. 12, since the two ends of each driving post 3 are guided by the
axial
guide opening 462 and the axial curved guide slot 463, respectively, the two
ends
of the driving post 3 can only move in the axial direction of the support
rotator 1;
afterward, when the driving ring 45 starts to rotate about the limitator 46,
the
outward ends of the driving posts 3 are guided to move rightward (as shown in
the
middle diagram through the leftmost diagram of FIG. 12) or leftward (as shown
in
the middle diagram through the rightmost diagram of FIG. 12) by the oblique
guide slots 451 of the driving ring 45, so as to cause the driving posts 3 and
the
transmission balls 2 to simultaneously rotate counterclockwise (as shown in
the
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Attorney Docket No. 26779-26
middle diagram through the leftmost diagram of FIG. 12) or simultaneously
rotate
clockwise (as shown in the middle diagram through the rightmost diagram of
FIG.
12.)
[0033] Referring to FIG. 8, FIG. 10 and FIG. 12 as well as FIG. 1, FIG. 3 and
FIG. 5, regarding the aforesaid linear gear shift mechanism, in the situation
where
the inward ends of the driving posts 3 are movably disposed in the cylindrical
recesses 21, respectively, the gear shift unit 4 has a driving screw 42, a
driving
ring 41 and at least one guiding rod 43, just like the previous linear gear
shift
mechanism. The driving ring 41 is annular. After the driving screw 42 has been
driven by a driving motor 421 to rotate, the outward ends of the driving posts
3 get
pivotally connected to the driving ring 41 as soon as a pin 32 passes through
the
two sides of a plurality of pivotal slots 411 on the lateral side of the
driving ring 41.
The guiding rod 43 is a post. The driving screw 42 penetrates and meshes with
a
threaded hole 412 of the driving ring 41. The guiding rod 43 movably
penetrates a
guide hole 413 of the driving ring 41. The driving screw 42 drives the driving
ring
41 to undergo translation along the guiding rod 43 as shown in FIG. 1, FIG. 3
and
FIG. 5 and in the axial direction of the support rotator 1, such that the
driving ring
41 drives the driving posts 3 and the transmission balls 2 to rotates as shown
in
FIG. 8, FIG. 10 and FIG. 12, thereby allowing another linear gear shift
mechanism
of the present invention to change gear. Furthermore, the guiding rod 43 is
provided in the plural and arranged symmetrically, such that the driving ring
41
moves in a balanced manner while being driven by the driving screw 42 to
undergo translation.
[0034] Referring to FIG. 8, FIG. 10 and FIG. 12 as well as FIG. 6 and FIG. 7,
regarding the aforesaid linear gear shift mechanism, in the situation where
the
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inward ends of the driving posts 3 are movably disposed in the cylindrical
recesses 21, respectively, the gear shift unit 4 has two halved driving rings
414
which mesh with each other, just like the previous linear gear shift
mechanism.
The halved driving rings 414 are annular. A plurality of cavities 4141 and a
plurality of semi-cylindrical notches 4142 are disposed on the lateral side of
each
halved driving ring 414. Each cavity 4141 is bilaterally in communication with
a
semi-cylindrical notch 4142. The cavities 4141 pair up to form a plurality of
pivotal
through holes 4143. The semi-cylindrical notches 4142 pair up to form a
plurality
of pivotal cylindrical passages (not shown). A pin 32 passes through the
outward
ends of the driving posts 3. The outward ends of the driving posts 3 are
movably
received in the pivotal through holes 4143, respectively. The two ends of each
pin
32 are movably received in the pivotal cylindrical passages, respectively,
such
that the outward ends of the driving posts 3 are pivotally connected to the
halved
driving rings 414. Similarly, the halved driving rings 414 operate in
conjunction
with the driving screw 42, the driving motor 421 and the guiding rod 43, such
that
the driving screw 42 drives the halved driving rings 414 to undergo
translation in
the axial direction of the guiding rod 43 and the support rotator 1 as shown
in FIG.
8, FIG. 10 and FIG. 12.
[0035] Referring to FIG. 8 through FIG. 10, regarding the aforesaid linear
gear
shift mechanism, the axial power input rotator 5 has an axial power input
shaft 53.
The axial power input shaft 53 passes through the center of the limitator 46
of the
gear shift unit 4, the center between the transmission balls 2, and the center
of the
support rotator 1, such that the axial power input shaft 53 can be exposed
from
the support rotator 1. The axial power output rotator 6 has an axial power
output
shaft 63. Therefore, another linear gear shift mechanism of the present
invention
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Attorney Docket No. 26779-26
is characterized in that power is input through the axial power input shaft 53
and
then output from the axial power output shaft 63.
[0036] Referring to FIG. 8 and FIG. 9, the aforesaid linear gear shift
mechanism
further comprises a ball ring 7. The ball ring 7 has a plurality of balls 71
and a
positioning ring 72. The balls 71 are spaced apart from each other and movably
positioned in a plurality of positioning recesses of the positioning ring 72.
The
balls 71 are movably clamped between the axial power input rotator 5 and the
axial power output rotator 6 to reduce the friction-induced loss incurred
between
the axial power input rotator 5 and the axial power output rotator 6.
[0037] 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.
CA 2936457 2017-11-28
