BACKGROUND OF THE INVENTION
1. Field of the Invention:
[0001] The present invention relates an engine and, more particularly, to a high-output
engine, which has the crank arm of the crank made eccentric so as to impart an upward
pressure to the piston when the link coupled between the piston and the crank moved
to a predetermined angle, achieving an enhanced output of the engine.
2. Description of the Related Art:
[0002] FIGS. 1 and 3 show the structure and operation of an engine according to the prior
art. As illustrated, the engine comprises a cylinder
11', a piston
12' reciprocating in the cylinder
11', a crank
15', and a link
14', which has one end pivoted to the piston
12' by a pivot pin
13' and the other end provided with a connector
141' pivoted to the crank
14'. As illustrated, the link is a straight rod member coupled between the piston and
the crank. During reciprocating motion of the piston, the link drives the crank to
make a rotary motion. The maximum torque of the link is equal to the radius of the
arm of rotation of the crank arm
151' (when the crank arm at 45°). The thrust force reaches the maximum when the engine
ignited to explode. However, the torque is reduced to the minimum statue at this time.
When the piston lowered, the thrust force is gradually reduced, and the torque is
relatively increased. Due to the aforesaid problem, the performance of the aforesaid
engine cannot be effectively improved.
[0003] Further, the engine is ignited to explode when the piston moved to the upper limited
position, i.e., the dead line position where the center of the piston and the center
of the link and the center of the crank are vertically aligned in a line). At this
time, the volume of the chamber of the cylinder is minimized, providing the best compression
ratio. Therefore, this time is the best time for explosion. When passed over the dead
line, the piston starts to move downwards, and the best compression ratio and the
best explosion time cannot be maintained. The maximum output of the engine is when
the crank moved from 0° toward 90° (the moving distance "
e" of the piston). After this angle, the output of the engine is gradually reduced.
The output power of the engine has a great concern with the variation of the volume
of the cylinder chamber
111'. When the volume of the cylinder chamber
111' relatively increased, the explosion pressure is relatively reduced, resulting in
a reduction of output power of the engine. On the contrary, when the volume of the
cylinder chamber is relatively reduced during this stage and same explosion pressure
is maintained, the fuel mixture can be completely burned to relatively increase the
output power of the engine.
[0004] Further, in order to obtain the optimum compression ratio, the engine igniting time
must be before the dead line. The engine provides no power output or a negative power
before the dead line after the explosion. This drawback results in low engine performance,
a waste of fuel energy, and a big amount of exhaust gas. Further, because the piston
is reciprocated at a high speed when the combustion chamber of the engine is ignited
to explode, fuel gas is not completely burned before a next cycle. This problem reduces
the efficiency of the engine and, causes the engine to produce much waste gas.
[0005] Therefore, it is desirable to have a high-output engine that eliminates the aforesaid
drawbacks.
SUMMARY OF THE INVENTION
[0006] The present invention has been accomplished under the circumstances in view. It is
the main object of the present invention to provide a high-output engine, which enhances
the output, saves fuel gas, and reduces the production of waste gas. According to
the invention, the engine comprises a cylinder, a piston adapted to reciprocate in
the cylinder, the piston being provided with a pivot pin, a crank having a crank arm
and a crank shaft, and a link, the link having a first end pivoted to the pivot pin
of the piston and a second end pivoted to the crank arm of the crank, the crank arm
being an eccentric arm coupled to the second end of the link such that the center
of the second end of the link is at an eccentric status relative to the piston and
spaced from one side of the center line passing through the center of the piston and
the axis of rotation of the crank when the piston moved to the upper limit position.
When the piston moved to the upper limit position, the link is at an eccentric position
relative to the piston, and the connection area between the link and the crank is
moved to a position away from the axis passing through the center of the piston and
the axis of rotation of the crank. Therefore, the eccentric crank arm of the crank
forces the piston upwards to reduce the volume of the cylinder chamber when the crank
moved to a particular angle, enabling the fuel mixture to be completely burned to
increase the output power of the engine. Further, the link has a curved portion turning
in one direction and terminating in the second end so that the direction of applied
force of the link passes over the axis of rotation of the crank at one side of the
axis passing through the center of the piston and the axis of rotation of the crank
opposite to the longitudinal central axis of the crank.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007]
FIG. 1 is a sectional view of an engine according to the prior art.
FIG. 2 is similar to FIG. 1 but showing the crank moved to 90°.
FIG. 3 is a sectional view of showing the basic architecture of the present invention.
FIG. 4 is a sectional view of the present invention, showing the crank moved to 0°.
FIG. 5 is a sectional view of the present invention, showing the crank moved to 90°.
FIG. 6 is a sectional view of the present invention, showing the crank moved to 180°.
FIG. 7 is a sectional view of the present invention, showing the crank moved to 270°.
FIG. 8 illustrates the status of the present invention and the status of the prior
art design when the crank moved to 0°.
FIG.9 illustrates the status of the present invention and the status of the prior
art design when the crank moved to 45°.
FIG. 10 illustrates the status of the present invention and the status of the prior
art design when the crank moved to 90°.
FIG. 11 illustrates the status of the present invention and the status of the prior
art design when the crank moved to 180°
FIG. 12 illustrates the status of the present invention and the status of the prior
art design when the crank moved to 270°
FIG. 13 is a schematic drawing showing one embodiment of the crank arm of the crank
according to the present invention.
FIG. 13a is a top plain view of FIG. 13.
FIG. 14 is a sectional view showing an alternate form of the crank arm of the crank
according to the present invention.
FIG. 15 is a sectional view showing another alternate form of the crank arm of the
crank according to the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0008] Referring to FIG. 3, a high-output engine
1 in accordance with the present invention is shown comprising a cylinder
11, a piston
12 adapted to reciprocate in the cylinder
11, a crank
15, and a link
14 coupled between the piston
12 and the crank
15. The link
14 has a first end pivoted to the piston
12 by a pivot pin
13, and a second end fixedly mounted with a crank arm connector
141, which is coupled to the crank arm
151 of the crank
15. The crank arm
151 of the crank
15 has an arm shaft
1511 and an eccentric portion
1512 at the arm shaft
1511. The eccentric portion
1512 is coupled to the crank arm connector
141 at the link
14 in such a manner that when the piston
12 moved to the upper limit position, the center of the second end remote from the pivot
pin
13 is disposed in an eccentric status relative to the piston
12 and spaced from one side of the center line "
a" passing through the center of the piston
12 and the axis of rotation of the crank
15. When the crank
15 moved to 0°, the line of action of force "
b" of the link
14 extends over the center "
c" of the crank
15 to act against the arm of force "
d" of the crank 15, preventing the dead line problem of the conventional design and,
relatively prolonging the length of the arm of force
"d" of the crank
15. Because the arm of force
"d" of the crank
15 is prolonged, the output power of the engine
1 is relatively enhanced. Because the link
14 and the crank arm
151 are biased from one side of the center line "
a" passing through the center of the piston
12 and the axis of rotation of the crank
15, the eccentric portion
1512 forces the piston
12 upwards during rotary motion of the crank arm
151 (i.e., the eccentric portion
1512 buffers downward stroke of the piston
12), therefore the down stroke of the piston
12 is relatively shortened to relatively reduce the compressive chamber
111 in the cylinder
11 without reducing the cylinder pressure after explosion, enabling fuel mixture to
be completely burned to enhance the output of the engine. The eccentric portion
1512 of the crank arm
151 is preferably integrated with the arm shaft
1511 to achieve the best effect in pushing the piston
12 upwards. Alternatively, the eccentric portion
1512 may be coupled to the arm shaft
1511 of the crank arm
151 by a slip joint, however this arrangement provides an amount of compensation less
than the design of having the eccentric portion
1512 integrated with the arm shaft
1511. Further, the link
14 has a curved portion
142 turning in one direction and terminating in the crank arm connector
141 such that the line of action of force of the link
14 is biased toward one side of the crank shaft
152 opposite to the connecting area between the crank arm
151 and the crank arm connector
141. This design eliminates the output loss resulted from the dead line problem seen
in the prior art design.
[0009] FIGS. 4∼7 show the operation of the present invention. When the crank arm
151 turned to 0°, the eccentric portion
1512 is at the left side (see FIG. 4). When the eccentric portion
512 turned toward the top side, as shown in FIG. 5, the compensation of the eccentric
portion
1512 prolongs the distance between the piston
12 and the crank
14, thereby causing the down stroke time of the piston
12 to be delayed. When the crank arm
151 moved to 0°, the arm of force
"d" of the crank
15 passed over the enter
"c" of the crank
15 to act against the arm of force
"d" of the crank
15, preventing the dead line problem of the conventional design and, relatively prolonging
the length of the arm of force "
d" of the crank
15, and therefore the crank torque is relatively increased to enhance the output power
of the engine
1.FIGS. 6 and 7 show the action continued, completing one cycle.
[0010] FIGS. 8∼11 show a comparison between the invention and the prior art design in which
A'∼E' show the actions of the prior art design;
A∼E show the actions of the present invention. With reference to FIG. 8, when the crank
15 moved to 0°, the engine
1 is ignited to start the explosion stroke, at this time the output force reaches the
maximum status, and the torque of the prior art design is on the dead line and zeroed;
the arm of force "
d" of the crank
15 according to the present invention is great, providing a relatively greater output
torque. FIG. 9 shows the crank
15 moved to 45°. At this time, the piston of the prior art design moving downwards at
a high speed and the push force is gradually reducing, the arm of force
"d" of the crank
15 of the present invention is at the maximum status, and the downward displacement
of the piston
12 of the present invention is about one half of the prior art design. Therefore, the
invention provides much greater thrust force than the prior art design, enabling fuel
mixture to be completely burned. When moved to the position shown in FIGS. 10 and
11, the thrust force of the prior art design is going to be ended, however the invention
still works effectively. When moved to 180° as shown in FIG. 12, the arm of force
"d" of the crank
15 of the present invention is reduced to zero. As indicated in the drawings, the arm
of force "
d" of the crank
15 of the present invention is much greater than the prior art design, and therefore
the invention provides a relatively greater output torque. During one full cycle,
the piston
12 of the present invention is lowered at a relatively slow speed during working, for
enabling fuel mixture to be burned completely and the output thrust to be concentrated
when the arm of force "
d" of the crank
15 reached the maximum status.
[0011] FIGS. 13 and 13 show one embodiment of the crank arm. As illustrated, the crank arm
151 of the crank
15 is an eccentric arm having an eccentric portion
1512 in the arm shaft
1511. When the crank arm
151 turned to 0°, the link
14 is in an eccentric status.
[0012] FIG. 14 shows an alternate form of the crank arm. As illustrated, the crank arm
151 of the crank
15 is comprised of a straight arm shaft
1511 and an eccentric portion
1512, which is an eccentric axle bush formed of two symmetrical halves
1512' and arranged around the straight arm shaft
1511.
[0013] FIG. 15 shows another alternate form of the crank arm. As illustrated, the crank
arm
151 of the crank
15 is comprised of a straight arm shaft
1511 and an eccentric portion
1512, which is an eccentric axle bearing having an inner diameter
1514 coupled to the straight arm shaft
1511 and an outer diameter
1516 eccentrically spaced around the inner diameter
1514.
[0014] Although particular embodiments of the invention have been described in detail for
purposes of illustration, various modifications and enhancements may be made without
departing from the spirit and scope of the invention. Accordingly, the invention is
not to be limited except as by the appended claims.
1. A high-output engine comprising a cylinder, a piston adapted to reciprocate in said
cylinder, said piston being provided with a pivot pin, a crank having a crank arm
and a crank shaft, and a link, said link having a first end pivoted to the pivot pin
of said piston and a second end pivoted to the crank arm of said crank, wherein the
crank arm of said crank is an eccentric arm coupled to the second end of said link
such that the center of the second end of said link is at an eccentric status relative
to said piston and spaced from one side of the center line passing through the center
of said piston and the axis of rotation of said crank when said piston moved to the
upper limit position.
2. The high-output engine as claimed in claim 1, wherein said link has a curved portion
turning in one direction and terminating in said second end such that the line of
action of force of said link is biased toward one side of the crank shaft of said
crank opposite to the connecting area between said crank arm and the second end of
said link.
3. The high-output engine as claimed in claim 1, wherein the crank arm of said crank
comprises an arm shaft, said arm shaft having an eccentric portion disposed on the
middle and coupled to the second end of said link.
4. The high-output engine as claimed in claim 1, wherein said crank arm of said crank
comprises a straight arm shaft and an eccentric axle bush mounted on said arm shaft
and fastened pivotally with the second end of said link.
5. The high-output engine as claimed in claim 4, wherein said eccentric axle bush is
fixedly fastened to said arm shaft and fastened pivotally with the second end of said
link.
6. The high-output engine as claimed in claim 4, wherein said eccentric axle bush is
axially movably sleeved onto said arm shaft and fastened pivotally with the second
end of said link.
7. The high-output engine as claimed in claim 1, wherein said crank arm of said crank
comprises a straight arm shaft and an eccentric axle bush mounted on said arm shaft
and fastened pivotally with the second end of said link, said eccentric axle bush
being formed of two symmetrical halves.
8. The high-output engine as claimed in claim 5, wherein the two symmetrical halves of
said eccentric axle bush are abutted against each other and fixedly fastened to the
periphery of said arm shaft.
9. The high-output engine as claimed in claim 4, wherein the two symmetrical halves of
said eccentric axle bush are abutted against each other and axially slidably sleeved
onto said arm shaft.
10. The high-output engine as claimed in claim 1, wherein said crank arm of said crank
comprises a straight arm shaft and an eccentric axle bearing mounted on said arm shaft
and fastened pivotally with the second end of said link.
11. The high-output engine as claimed in claim 10, wherein said eccentric axle bearing
having an inner diameter fastened pivotally with said arm shaft, and an outer diameter
eccentrically disposed around said inner diameter and fastened pivotally with the
second end of said link.
12. The high-output engine as claimed in claim 10, wherein said eccentric axle bearing
having an inner diameter fixedly fastened to the periphery said arm shaft, and an
outer diameter eccentrically disposed around said inner diameter and fastened pivotally
with the second end of said link.