Note: Descriptions are shown in the official language in which they were submitted.
CA 02846687 2015-09-21
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RING DISK RECIPROCATING POWER CONVERSION DEVICE
BACKGROUND OF THE INVENTION
1. Field of the Invention
Present invention provides a ring disk reciprocating power conversion device,
especially a
planetary gear set and an off-center control panel set used to convert power,
and more especially
a rotary disk of the off-center control panel set used to guide the planet
gear, and a variable
volume chamber and spacer used to control the self rotation of the planet
gear. Present invention
also relates to an oil resilient torque convertor, a rotation damping
decelerator, a compressor, and
a switch chamber type internal combustion engine, which are all built by the
ring disk
reciprocating power conversion device.
2. Description of the Related Art
The traditional power conversion technique is mainly used in the torque
conversion on the
transportation vehicle. The technique includes a soft oil pressure flowing
type torque converting
device, which has two corresponding propeller blades, and one of the propeller
blades drives the
oil to generate oil eddy to propel another propeller blade in order to reach
the purpose of power
conversion. However, the propelling force of the propelling blades cannot be
fully reflected on
the power output of another propelling blade, which results the problem of
power lost in the
power conversion.
Besides, the traditional rotation deceleration technique mainly uses a brake
lining to clamp
or make a friction against the axle or the wheel frame to decelerate. However,
after long time
clamping and friction, the brake is very easy to break down due to overheat.
Moreover, the traditional compressor includes piston type and scroll type. The
compressing
and drawing efficiency of scroll type compressor is better than the other one,
but the power of
compressing and drawing is not strong enough, which is also hard to improve.
Thus, the scroll
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type compressor cannot be used when the strong power is needed. The piston
type compressor
has relatively good power, but only one compressing can be made in one
compression cycle,
resulting bad efficiency.
In addition, traditional combustion engine has a fixed type cylinder, and by
way of the
explosion power of the fuel, the piston in the cylinder can be driven to push
the crank to output
the power. However, half of the explosion power pushes against the surface of
the piston, and the
other half of the explosion power pushes against the cylinder head, which
cause 10% power lost.
After the power lost, the explosion power will push the piston surface again,
which causes time
differences for the twice pushing. Thus, the explosion power cannot be fully
transformed to the
piston propelling power.
Presently, combining the foresaid techniques of rotation deceleration,
compressor, and
combustion engine has not been disclosed in the traditional power conversion
technique, which
means lots of improvement can be made in the future.
SUMMARY OF THE INVENTION
Present invention aims to overcome the problems of the prior arts as follows:
1. Using two propelling blades via oil to output power, which causes high
power lost.
2. Using brake lining to clamp or make a friction against the rotation
elements, and the
overheat due to over-friction, which makes the brake to break down.
3. The compressing and drawing power and efficiency of the traditional piston
type and
scroll type compressor cannot be improved.
4. The explosion power of the fuel is partially lost in the cylinder, and the
explosion time
point differences cause the power of the explosion unable to be fully
transformed to the piston
propelling power.
In order to solve the problems mentioned above, present invention provides a
ring disk
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,
reciprocating power conversion device, comprising:
a planetary gear set provided with a sun gear and a plurality of planet gears
engaged in the
periphery of the sun gear;
at least one off-center control panel set, comprising:
a rotary disk pivoted on a center axle of the sun gear and arranged opposite
to the
planetary gear set, being able to receive the guiding from self rotation of
the planet gear,
forcing the rotary disk to do a reciprocating movement in limited amplitude;
an annular chamber, formed at interval in the periphery of the rotary disk,
the annular
chamber accommodating a press forming medium, wherein the medium is oil;
more than one separation parts, separating the annular chamber to form more
than one
variable volume chambers; and
equal amount of spacer as the variable volume chambers, movably arranged in
the
periphery of the rotary disk, being able to enter the variable volume chambers
to compress
or draw the medium to regulate and stop self rotation of the planet gear, and
being able to
exit the variable volume chambers to release the planet gear for self
rotation.
When the outer power inputs to the sun gear, the self rotation of the planet
gear can be
driven via the sun gear, and the outer power can be engine powered. The self
rotation of the
planet gear guides the rotary disk to do a reciprocating movement, making the
planet gear to do
the revolution and without fully reflecting the power of sun gear. When the
spacer enters the
variable volume chamber to regulate and stop the self rotation of the planet
gear, the sun gear can
drive the planet gear to enhance the revolution force. By increasing the
revolution force of the
planet gear, the output of the sun gear can be increased as well. As such, by
way of oil flowing
cut-off technique, such as dampening or locking the rotation of the planet
gear, the power output
can be controlled, and the power conversion efficiency can be improved.
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In fact, the center axle of the sun gear is provided with a first axial rod,
and an end surface
of the planet gear movably hitches a frame piece, and the center axle of the
frame piece is
provided with a second axial rod. The first axial rod is used as a power input
terminal, and the
first axial rod can drive the planet gear to self rotate via the sun gear, and
the second axial rod is
used as a power output terminal to transfer the power of revolution of the
planet gear.
In present invention, the outer power can be input to the planet gear to
directly drive the
planet gear. The outer power can be the power of the wheel axle. The rotary
disk is guided by the
self rotation of the planet gear to do the reciprocating movement, and the
planet gear does the
revolution along the sun gear. When the spacer enters the variable volume
chamber to regulate
and stop the self rotation of the planet gear, the revolution along the sun
gear of the planet gear
can be lowered or stopped, further reducing or stopping the power of the outer
wheel axle. By
utilizing the damping effect of the oil cut-off, the deceleration of the outer
wheel axle can be
achieved, and the brake failing duo to overheat will no longer exist.
In fact, the first axial rod can be used as the fixed end to brake the planet
gear, and the
second axial rod can be used as the movable end to drive the planet gear, or
vice versa. The
movable end can drive the planet gear to self rotate or do the revolution
along the sun gear.
In another embodiment of the present invention, equal amount of troughs as the
spacers are
formed in the periphery of the rotary disk. The troughs are able to
accommodate the spacer, and
the spacer can enter the variable volume chamber via the trough, or enter the
trough to exit the
variable volume chamber. The center axle of the rotary disk is provided with a
casing tube. The
casing tube connects the spacer, and the casing tube can drive the spacer to
enter or exit the
variable volume chamber.
Besides, present invention provides another ring disk reciprocating power
conversion device,
comprising:
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a planetary gear set provided with a sun gear and a plurality of planet gears
engaged in the
periphery of the sun gear;
at least one off-center control panel set, comprising:
a rotary disk pivoted on a center axle of the sun gear and arranged opposite
to the
planetary gear set, being able to receive the guiding from self rotation of
the planet gear,
forcing the rotary disk to do a reciprocating movement in limited amplitude;
an annular chamber, formed in interval in the periphery of the rotary disk,
and the
annular chamber accommodating a press forming medium, wherein the medium is
air or
coolant;
1 0 more than one separation parts, separating the annular chamber to
form more than one
variable volume chambers; and
equal amount of spacers as the variable volume chambers, fixed to the
periphery of the
rotary disk, the spacers separating the variable volume chamber and being able
to compress
or draw the medium.
The spacer and separation part are used to separate the variable volume
chamber to form
four compressing and drawing chambers. The outer power inputs to the sun gear,
and the planet
gear is driven by the sun gear. The outer power can be motor powered. The
rotary disk is guided
by the self rotation of the planet gear, making the spacer with the rotary to
do the reciprocating
movement in limited amplitude, and thus compressing or drawing the air or the
coolant in the
chamber. By the volume changing in every chamber of the variable volume
chamber, the
compressing and drawing operation can be continuously alternating to compress
or draw the air
or coolant. Thus, the compressing and drawing power can be improved, and so do
the efficiency.
Practically, the center axle of the sun gear is provided with a fist axial rod
which is used as
the power input terminal. Or, the medium of present invention can be fuel oil,
and the fuel oil can
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be ignited in one of the variable volume chambers to generate the explosion
power. The
explosion power drives the spacer to further drive the rotary disk to do the
reciprocating
movement in limited amplitude, which results in the self rotation of the
planet gear. The self
rotation of the planet gear drives the sun gear to output the power.
Meanwhile, the spacer
compresses the fuel oil in another chamber of the variable volume chamber. By
those described
above, the chamber can be used as drawing chamber, compressing chamber,
explosion chamber,
and emission chamber, and the planet gear can be driven and continuously
drives the sun gear to
output the power, improving the power output efficiency from converting the
explosion power of
the fuel oil. The center axle of the planet gear is pivoted in a fixed
position around the periphery
of the sun gear, or the center axle of the planet gear uses the rotary disk as
a fixed end to pivot the
planet gear around the periphery of the sun gear. Or, the center axle of the
planet gear uses the
gear rim as a fixed end to pivot the planet gear around the sun gear.
In one embodiment of the present invention, the off-center control panel set
is provided with
a shell, an interior wall of the shell is provided with a corresponding first
engagement part and a
second engagement part, the planetary gear set is pivoted on the first
engagement part, the rotary
disk is pivoted on the second engagement part, and the annular chamber is
formed between the
outer periphery of the rotary disk and the interior wall of the shell, and one
side of the rotary disk
is corresponding to the planetary gear set.
In another embodiment, present invention further comprises:
a plurality of first guiding grooves, using the sun gear as a center and
formed in the first
engagement part in a radical shape, respectively;
two end surfaces of the planet gear being provided with an eccentric axis
respectively, the
eccentric axis being arranged on both sides of the center axle of the planet
gear respectively; and
a plurality of second guiding grooves, using the center axle of the rotary
disk as a center and
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formed in the plate surface in a radical shape, the planet gear via the
eccentric axis being guided
by the first guiding groove and the second guiding groove respectively to
rotate, the rotary disk
being guided by the eccentric axis to do the reciprocating movement via the
second guiding
groove.
The eccentric axis is pivoted with a sliding member, and the sliding member is
slidably
arranged in the guiding groove. The separation part is formed in the interior
of the shell.
In still another embodiment, the ring disk reciprocating power conversion
device has four
planet gears , which are arranged on the periphery of the sun gear,
respectively, the ring disk
reciprocating power conversion device having two off-center control panel
sets, each of the
off-center control panel sets leading two planet gears to self rotate
respectively, the ring disk
reciprocating power conversion device having two separation parts, the two
separation parts
separating the annular chamber to form two variable volume chambers. The outer
periphery of
the planet gear engages a self-rotatable gear rim, the two end surfaces of the
gear rim are
provided with a ring, respectively, the planet gear is situated between the
rings, the two end
surfaces of the planet gear movably hitching a frame piece, respectively, and
the frame piece
situated in the ring.
In order to facilitate the movement for the separation part in the medium, the
sectional view
of the separation part is H shape.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention is illustrated by way of example, and not by way of limitation,
in the figures
of the accompanying drawings in which like reference numerals refer to similar
elements and in
which:
FIG. 1 is an exploded view of the first embodiment of present invention;
FIG. 2 is a front view of the present invention;
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FIG. 3 is a side view of FIG. 2;
FIG. 4 is an A-A sectional view of FIG. 3;
FIG. 5 is a B-B sectional view of FIG. 2;
FIG. 6 is a C-C sectional view of FIG. 2;
FIG. 7 is a partially enlarged view of the planetary gear set in FIG. 1;
FIG. 8 is an exploded view of one of the off-center control panel set in FIG.
1;
FIG. 9 is an exploded view of another off-center control panel set in FIG. 1;
FIG. 10 is a D-D sectional view of FIG. 3;
FIG. 11 is a schematic view in operating the apparatus of FIG. 4;
FIG. 12 is a schematic view in operating the apparatus of FIG. 4;
FIG. 13 is a schematic view in operating the apparatus of FIG. 4;
FIG. 14 is one of a schematic view in operating the apparatus of FIG. 10;
FIG. 15 is one of a schematic view in operating the apparatus of FIG. 10;
FIG. 16 is a schematic view in operating the apparatus of FIG. 5;
FIG. 17 is another schematic view in operating the apparatus of FIG. 10;
FIG. 18 is an exploded view of the second embodiment of the present invention;
FIG. 19 is an exploded view of the third embodiment of the present invention;
and
FIG. 20 is an exploded view of the fourth embodiment of the present invention.
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 discloses the exploded view of the first embodiment of present
invention. FIGS. 1, 2, and 7 disclose the ring disk reciprocating power
conversion
device of present invention, which includes a planetary gear set 1 and at
least one
off-center control panel set 3. The planetary gear set 1 is provided with a
sun gear
10 and a plurality of planet gears 21,21a engaged in the periphery of the sun
gear
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10. In the present embodiment, the quantity of the planet gears 21,21a can be
four,
which are provided in the periphery of the sun gear 10 with equal interval,
and
thus making a 180 degrees angle between the planet gears 21,21a which arranged
in both sides of the sun gear 10. The angle between planet gears 21a is also
180
degrees. Planet gears 21 are defined as a first group, and planet gears 21a
are
defined as second group. The periphery of the first group planet gear 21 and
the
second group planet gear 21a engage to a self-rotatable gear rim 23, making
the
planet gears 21, 21a movably arranged in the periphery of the sun gear 10. Two
end surfaces 231,232 of gear rim 23 are provided with rings 41, 42,
respectively.
The planet gears 21, 21a are situated between the rings 41, 42, and the rings
41,
42 can clamp the position where the planet gears 21, 21a engage to the gear
rim
23. First axial parts 211, 211a and second axial parts 212, 212a are provided
on
the two end surfaces of the planet gears 21, 21a, respectively, as shown in
FIG. 8
and FIG. 9. The first axial parts 211, 211a and the second axial parts 212,
212a of
the planet gears 21, 21a movably hitch a first frame piece 43 and a second
frame
piece 44, respectively.
The first frame part 43 is formed as a round plate shape, and first frame
slots 431 which has
equal amount as the planet gears 21, 21a are formed in the edge of the first
frame part 43. The
first axial parts 211, 211a are pivoted in the first frame slots 431, and the
first frame part 43 is
pivoted in the ring 41. The second frame part 44 is also formed as a round
plate shape, and
second frame slots 441 which is equal amount as the planet gear 21, 21a is
fomied in the edge of
the frame part 44. The first axial parts 212, 212a are pivoted in the second
frame slot 441, and the
second frame piece 44 is pivoted in the ring 42. A first axial rod 101 is
provided on a center axle
of the sun gear 10. The center axle of the sun gear 10 means the axle of the
rotation center of the
sun gear 10. A second axial rod 432 is provided on the center axle of the
first frame piece 43, and
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the center axle means the axle of the rotation center of the first frame piece
43. The sun gear 10
and the first frame piece 43 are arranged in the same axis line. A through
hole 433 is formed in
the second axial rod 432, and one end of the first axial rod 101 is pivoted in
the through hole 433.
The top surface of the first axial parts 211, 211a of the planet gears 21,21a
are provided with first
eccentric axes 213, 213a. The top surface of the second axial parts 212, 212a
of the planet gears
21,21a are provided with second eccentric axes 214, 214a. The first eccentric
axes 213, 213a and
the second eccentric axes 214, 214a are arranged in both sides of the center
axle of the planet
gears 21, 21a, respectively. The center axles of the planet gears 21, 21a mean
the axles of the
rotation center of the planet gears 21, 21a. A 180 degrees included angle is
formed between the
first eccentric axes 213, 213a and the second eccentric axes 214, 214a. The
first eccentric axes
213, 213a are pivoted with rectangle shaped first sliding members 241, 241a,
and the second
eccentric axes 214, 214a are pivoted with rectangle shaped second sliding
members 242, 242a.
The off-center control panel set 3 includes a shell 30, a rotary disk 35, an
annular chamber
36, more than one separation parts 37, more than one variable volume chambers
38, and equal
amount of spacers 39 as the variable volume chambers 38. The shell 30 is
formed as a cylindrical
shape, and further provided with a containing room 300. The interior wall of
the containing room
300 is provided with a corresponding first engagement part 301 and a second
engagement part
302. The planetary gear set 1 is arranged in the containing room 300, and
further pivoted in the
first engagement part 301 via the first axial rod 101 and second axial rod
432. The second axial
rod 432 extends to outside the shell 30 via the first engagement part 301. The
shell 30 can be
composed of a ring housing 31, a ring cover 32, and a round shape lower cover
plate 34. A cover
opening 313 is formed on one end of the ring housing 31. A first opening 323
and a second
opening 324 are formed on both ends of the ring cover 32. The cover opening
313 of the ring
housing 31 and the first opening 323 of the ring cover 32 embed each other via
a plurality of
teeth 311, 321 and groove parts 312, 322, making the interior of the ring
housing 31 and the
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interior of the ring cover 32 connected to form the containing room 300. The
lower cover plate 34
is pivoted in the second opening 324 of the ring cover 32 to close the
containing room 300. The
first engagement part 301 is provided in the interior wall of the ring housing
31, and the planetary
gear set 1 is accommodated in the ring housing 31. The second engagement part
302 is arranged
in the second opening 324.
The rotary disk 35 is arranged in the containing room 300 and provided with a
first plate
surface 351 and a second plate surface 352, as shown in FIG. 8. The second
plate surface 352 is
fixed on the lower cover plate 34. The rotary disk 35 is pivoted in the second
engagement part
302 via the lower cover plate 34, and further pivoted on the center axle of
the sun gear 10. Thus,
the rotary disk 35 is arranged opposite to the planetary gear set 1, and the
first plate surface 351
of the rotary disk 35 corresponds to the planetary gear set 1. An upper cover
plate 33 is fixed on
the first plate surface 351. Besides, the first axial rod 101 extends outside
the shell 30 via the
second engagement part 302, and the upper cover plate 33, rotary disk 35, and
the lower cover
plate 34 are coaxial pivoted on the first axial rod 101. The rotary disk 35
can be guided by the
self rotation of the planet gear 21, as shown in FIG. 12 and 13, and the
rotary disk 35 can do
reciprocating movement with limited amplitude, as shown in FIGS. 14 and 15. In
fact, the present
invention further includes a plurality of first guiding grooves 314 and second
guiding grooves
331. Using the sun gear 10 as the center, the first guiding groove 314 is
formed in the first
engagement part 301 in a radical shape. The first eccentric axis 213 of the
first planet gear 21 is
slidably arranged in the first guiding groove 314 via the first sliding member
214. Using the
center axle of the rotary disk 35 as the center, the second guiding groove 331
is formed in the
upper cover plate 33 of the first plate surface 351 in a radical shape. The
second eccentric axis
214 of the first planet gear 21 is slidably arranged in the second guiding
groove 331 via the
second sliding member 242. Thus, the first planet gear 21 can be guided by the
first guiding
groove 314 and the second guiding groove 331 to self rotate via the first
eccentric axis 213 and
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the second eccentric axis 214, and the rotary disk 35 can be guided by the
second eccentric axis
214 to do the reciprocating movement via the second guiding groove 331.
The annular chamber 36 is formed at intervals in the periphery of the rotary
disk 35. In fact,
the annular chamber 36 is separated to between the outer peripheral wall of
the rotary disk 35 and
the interior wall of the containing room 300 of the shell 30 by the upper
cover plate 33 and the
lower cover plate 34, as shown in FIG. 10. The interior of the annular chamber
36 can
accommodate a pressure forming medium, which can be oil in the present
embodiment. The
separation part 37 is formed in the interior wall of the ring cover 32 of the
shell 30, as shown in
FIG. 8. Thus, the separation part 37 is arranged in the containing room 300.
The separation part
37 separates the annular chamber 36 to form the variable volume chamber 38. In
the present
embodiment, the number of the separation part 37 can be two, and the separated
annular chamber
36 forms two variable volume chambers 38.
The spacer 39 is movably arranged in the periphery of the rotary disk 35.
Actually, equal
amount of containing troughs 353 as the spacers 39 are formed in the periphery
of the rotary disk
35. The containing trough 353 connects the variable volume chamber 38 and
accommodates the
spacer 39. Thus, the spacer 39 can enter the variable volume chamber 38 via
the containing
trough 353, as shown in FIG. 17, and do the reciprocating movement in limited
amplitude with
the rotary disk 35 to push or draw the medium to regulate and stop the self
rotation of the first
planet gear 21. The spacer 39 can also return to the containing trough 353 to
depart from the
variable volume chamber 38, as shown in FIG. 16, and further releases the
first planet gear 21 to
self rotate. Besides, the center axle of the rotary disk 35 is provided with a
casing tube 5. The
center axle of the rotary disk 35 means the rotation center of the rotary disk
35. The casing tube 5
and the spacer 39 can connect to each other by a rope. The casing tube 5 can
move in accordance
with the rotation direction of the rotary disk 35, and further drives the
spacer 39 to enter or exit
the variable volume chamber 38. In the present embodiment, the number of the
spacer can be two.
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The cross section of the spacer 39 can be "H" shape, which benefits the
movement of the spacer
39 in the medium. The variable volume chamber 38 is the operating section of
the high positive
pressure oil and the high negative pressure oil. Thus, the oil leaking between
the variable volume
chamber 38 and operating elements is hard to avoid. In order to replenish the
oil into the variable
volume chamber 38, equal amount of via holes 342 as the containing troughs 353
are formed on
the lower cover plate 34, and the via hole 342 connects the containing trough
353 to outside.
Thus, the oil can be supplied to the containing trough 353 via the via hole
342, and the oil can
also be guided into the variable volume chamber 38 by the spacer 39 which has
H shape cross
section.
Besides, present embodiment adopts two off-center control panel set 3, 3a, as
shown in FIG.
9. The off-center control panel 3 is defined as the first set, and the off-
center control panel 3a is
defined as the second set. According to the operating method mentioned above,
the second
off-center control panel 3a is arranged on the outer periphery of the first
off-center control panel
3 to guide the second planet gear 21a to self rotate. The difference is that
the upper cover plate 33,
the rotary disk 35, and the lower cover plate 34 of the first off-center
control panel 3 form equal
amount of ports 332, 354, and 341 as the second planet gear 21a, and the
second axial part 212a
of the second planet gear 21a extends to the outside of the lower cover plate
34 of the first
off-center control panel 3 in order to be guided by the rotary disk 35a of the
second off-center
control panel 3a. Except the differences mentioned above, the assembly of the
ring housing 31a,
the upper cover plate 33a, ring cover 32a, lower cover plate 34a, spacer 39a
and casing tube 5a
are the same as the first off-center control panel 3.
The method describe above can be used in the torque conversion of the
transportation
vehicle. The first axial rod 101 can be used as the exterior engine power
input terminal, and the
second axial rod 432 can be used as the engine power output terminal. When the
spacer 39 not
yet enters the variable volume chamber 38 to cut off the oil, as shown in FIG.
10, and the exterior
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engine power input via the first axial rod 101 and sun gear 10, as shown in
FIGS. 11 and 12, the
revolution and self rotation of the first planet gear 21 and the second planet
gear 21a can be
driven by the sun gear 10. At the same time, the first planet gear 21 self
rotates and guides the
rotary disk 35 of the first off-center control panel set 3 to do the
reciprocating movement.
Meanwhile, the first guiding groove 314 arranged in the shell 30 restricts the
first sliding member
241 of the first eccentric axis 213 to move in the first guiding groove 314,
as shown in FIG. 13.
The second guiding groove 331 which swings with the rotary disk 35 can
restrict the second
sliding member 242 of the second eccentric axis 214 to move in the second
guiding groove 331,
and further makes the first planet gear 21 to self rotate. At this time, the
revolution and the self
rotation of the planet gear 21 are in a balance condition, and the power
output from the sun gear
10 cannot be fully released. The first eccentric axis 213 moves with the
rotation of the planet gear
21, and via the first guiding groove 314 to guide the shell 30 to do the
reciprocating movement in
limited amplitude, as shown in FIGS. 14 and 15. The second eccentric axis
moves with the
rotation of the planet gear 21, and via the second guiding groove 331 to guide
the rotary disk 35
to do the reciprocating movement in limited amplitude, which makes a pendulum
like
reciprocating movement between the shell 30 and the rotary disk 35.
When the spacer 39 partially enters the variable volume chamber 38 to cut off
the oil, as
shown in FIG. 16, the spacer 39 can do the reciprocating movement with the
rotary disk 35 to
push or draw the medium, making the medium to form oil pressure, which dampens
the relative
reciprocating movement between the shell 30 and the rotary disk 35, forcing
the planet gear 21
not being able to freely self rotate. Thus, the rotation force of the planet
gear 21 will increase
with the revolution of the sun gear 10, and the torque used to output the
power from the planet
gear 21 via the second axial rod 432 will be increased. As such, the self
rotation of the first planet
gear 21 and the revolution with the sun gear 10 can be regulated, and the
torque output can also
be controlled by regulating the dampening force.
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When the spacer 39 fully enters the variable volume chamber 38 to cut off the
oil, as shown
in FIG. 17, the variable volume chamber 38 is separated into 4 oil pressure
chambers 381, 382,
383, 384, forcing the planet gear 21 to be fully locked and not being able to
self rotate. The planet
gear 21 does the revolution with the sun gear 10 and fully responses the power
of the sun gear 10,
and further outputs the power of the sun gear 10 via the planet gear 21 and
the second axial rod
432. At this time, the revolution power of the planet gear 21 is the same as
the power of the sun
gear 10, and the power can be output via the torque generated by the
revolution of the planet gear
21. When the exterior engine power drives the second planet gear 21a via the
sun gear 10, the
second planet gear 21a is also guided by the rotary disk 35a of the second off-
center control panel
set 3a, and the operation principle is the same as previous disclosure. When
the first eccentric
axis 213 and the second eccentric axis 214 of the first planet gear 21 rotate
without dampening
force generating, the first eccentric axis 213a and the second eccentric axis
214a of the second
planet gear 21a have the maximum dampening force. Therefore, the driving force
of dampening
generated by the first planet gear 21 and the second planet gear 21a is a
composite function of
sine function and cosine function, and which means the driving force always
exist.
Present invention can control the output of the driving force by cutting off
the oil or locking
the planet gears 21, 21a with damping. Present invention is a rigid hydraulic
oil resistance torque
converter, which is able to totally cut off the oil flowing, and the driving
force can completely be
reflected on the output power, lowering the power lost to nearly zero after
the power conversion.
Present invention can be applied to light or heavy mechanical equipment to
enhance the power
conversion efficiency and save lots of energy.
Please refer to FIG. 18, the difference between the cross-section view of the
second
embodiment and the first embodiment of the present invention is that in the
second embodiment,
the first axial rod 101 can be arranged in a fixed base to be a fixed end,
which restricts the
rotation of the sun gear 10. The second axial rod 432 can be a movable end
which drives the
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planet gears 21, 21a, as shown in FIGS. 5 and 6. The movable end can connect
an exterior
rotation mechanism and drive the planet gears 21, 21a to do the revolution and
self rotation along
the sun gear 10, and other elements or configuration are the same as the first
embodiment. The
operation principle as described above can be applied to the rotation
deceleration of the
transportation vehicle. An axle 6 is used as the rotation mechanism in the
present embodiment.
When the power of the axle 6 inputs via the second axial rod 432 and the
planet gears 21, 21a, the
planet gears 21, 21a can be directly driven, and the rotary disks 35, 35a will
do the reciprocating
movement by the guiding of the self rotation of the planet gears 21, 21a, and
the planet gears 21,
21a will do the revolution along the sun gear 10.
When the spacers 39, 39a partially enter the variable volume chamber 38 (see
FIG. 16), the
damping force of the oil will slow down the self rotation of the planet gears
21, 21a, and so do
the revolution of the planet gears 21, 21a along the sun gear 10, thus
generating dampening force
to slow down the axle 6. When the spacers 39, 39a fully enter the variable
volume chamber 38
(see FIG. 17), the oil flowing in the chambers 381, 382, 383, 384 is
completely cut off, which
locks the planet gears 21, 21a with the sun gear 10 and further stops the axle
6. Thus, by
regulating the dampening force, the power input from the axle 6 can be
dampened and the power
of the axle 6 can be diminished. Other operation principles are the same as
the first embodiment
of the present invention. In the present embodiment, the dampening force of
the oil can be used
for deceleration. When the dampening force completely applied, the power will
translate to the
pressing force for compressing the oil, therefore only the friction heat of
the flowing oil and the
oil compressing heat will be generated. The heat will disperse in the whole
annular chamber 36 to
avoid the friction heat that concentrated on the friction surface of the
traditional brake lining, and
in addition to avoid the accidentally locked-up of rotation.
Please refer to FIG. 19, the difference between the cross-section view of the
third
embodiment and the first embodiment of the present invention is that the
spacer 39b is integral as
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a whole or fixed to the periphery of the rotary disk 35b, and the spacer 39
separates the variable
volume chamber 38 to compress or draw the medium. The first axial rod 101 of
the sun gear 10 is
used as power input terminal, and other elements and configurations are the
same as the first
embodiment. The operation principle as described above can be applied to a
compressor. The
separation part 37 and the spacer 39b separate the variable volume chamber 38
into four
compressing and drawing chambers 381, 382, 383, 384, and the medium in the
present
embodiment can be air or coolant. The chambers 381, 382, 383, 384 are
connected to the inlet or
outlet pipes, respectively. When the power of a motor drives the planet gears
21, 21a to self rotate
via the first axial rod 101 and the sun gear 10, the rotary disk 35b is guided
by the self rotation of
the planet gears 21, 21a, making the spacer 39b to do the reciprocating
movement with the rotary
disk 35b in limited amplitude, and further reciprocatingly compress and
drawing the air or
coolant in the chambers 381, 382, 383, 384 in sequence. Air and coolant are
discharged via
output pipes after being compressed.
Besides, the numbers of compressing and drawing in a rotation cycle can be set
by the gear
ratio of the sun gear 10 and the planet gears 21, 21a, and the numbers of the
variable volume
chambers 38. For example, the gear ratio is 1:1, and the variable chamber 38
is separated into
four chambers 381, 382, 383, 384. One circle rotation of the sun gear 10 also
makes the planet
gears 21, 21a to rotate one circle as well. As such, four compressions and
drawings can be made,
and the other operation principles are the same as the first embodiment. By
the volume changing
of the chambers 381, 382, 383, 384 of the variable volume chamber 38, the
compressed and drew
operation are continuously and alternately changing, to achieve the goal of
push-out and draw-in
the air or the coolant, and further improves the compress-draw power, as well
as the
compress-draw efficiency.
Please refer to FIG. 20, the difference between the cross-section view of the
fourth
embodiment and the third embodiment of the present invention is that the
center axle of the
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planet gears 21, 21a can be pivoted on the first engagement part 301, as shown
in FIGS. 5 and 6,
and thus situated on the periphery of the sun gear 10. Or, the center axle of
the planet gears 21,
21a can used the rotary disk 35b as a fixed end, and the planet gears 21, 21a
are pivoted on the
periphery of the sun gear 10. Or, the center axle of the planet gears 21, 21a
can also use the gear
ring 23 as a fixed end, and the planet gears 21, 21a are pivoted on the
periphery of the sun gear
10. The first axial rod 101 of the sun gear 10 is used as the power output
terminal, and other
elements or configurations are the same as the third embodiment of the present
invention. Present
embodiment can be applied to the switch chamber type internal combustion
engine. The
chambers 381, 382, 383, 384 can be used as the combustor of the cylinder. The
medium can be
fuel oil. The chambers 381, 382, 383, 384 are connected to the inlet or outlet
pipes for the fuel oil,
respectively. The spacer 39b in the present embodiment can be used as piston.
Therefore, there
will be two volume decreased chambers and two volume increased chambers among
the
chambers 381, 382, 383, 384 at the same time. The fuel can be ignited in the
chamber 381 of the
variable volume chamber 38 to generate the explosive force, as shown in FIG.
9. The explosive
force drives the spacer 39b to extend the chamber 381, making the spacer 39b
to drive the rotary
disk 35b to do the reciprocating movement in limited amplitude, which further
guides the planet
gears 21, 21a to self rotate. By the self rotation of the planet gears 21,
21a, the sun gear 10 and
the first axial rod 101 can be driven to output the power. Meanwhile, the
spacer 39b compresses
the chamber 382 to force the chamber 382 to discharge the exhaust gas
generated by burning fuel
oil. The spacer 39b extends another chamber 383, forcing the chamber 383 to
draw in the fuel oil.
The spacer 39b compresses another chamber 384 to force the chamber 384 to
compress the fuel
oil. By way of this, drawing, compressing, explosion, and emission of the
internal combustion
can continuously and orderly happen, which can continuously drive the planet
gears 21, 21a to
force rotation of the sun gear 10. Other elements and configurations are the
same as the third
embodiment.
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Thus, the chambers 381, 382, 383, 384 can be used as an air-drawing chamber, a
compressing chamber, an explosion chamber, and an emission chamber,
respectively. By
continuously driving the planet gears 21, 21a, the sun gear 10 and the first
axial rod 101 can be
driven to output the power. The enhancement of the explosion power of the fuel
oil can be
transformed to improve the power output efficiency. Besides, the spacer 39b is
a movable
element for doing the reciprocating movement in limited amplitude. The
explosion power can
simultaneously drive every spacer 39b, and so do the same planet gears 21, 21a
to generate the
self rotation of the planet gears 21, 21a. Thus, the explosion power can
completely transformed to
the self rotation propelling power of the planet gears 21, 21a, and the power
lost is zero, which
can improve the fuel burning efficiency and save energy.
While the invention has been described in connection with a number of
embodiments and
implementations, the invention is not so limited but covers various obvious
modifications and
equivalent arrangements, which fall within the purview of the appended claims.
Although
features of the invention are expressed in certain combinations among the
claims, it is
contemplated that these features can be arranged in any combination and order.
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