JPH1082328A - Transmission method of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an internal combustion engine's transmission method that uses no crankshaft. SOLUTION: A rocking end of a rocker member 3 doing a rocking motion with a rocking shaft 4 as the center is engaged with a connecting rod 2 transmitting the reciprocating motion of a piston 1, converting this piston reciprocating motion into the rocking motion, and thereby the rocking motion of the rocker member is converted into a rotational motion by a one-way clutch 3a being connected to this rocking shaft and transmitting the rocking motion only in case of down motion at the explosion stroke of the piston and then transmitting rotative driving force to an engine output shaft 9, while the piston is reciprocated by three cam means 5, 6 and 7 interlocking with the rotational motion. In this case, if desirable, each of these cam means is equipped with an upping cam 5 being driven by the rotative driving force, and this upping cam sets up a lowermost point of the piston while it makes the lowered piston go upward, or differently, the cam means is further equipped with a downing cam 6 being driven by the rotative driving force, and this downing cam makes the upper piston go down.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission mechanism for an internal combustion engine, that is, a mechanism for converting a reciprocating motion generated by a piston into a rotary motion and transmitting the rotational motion to an engine output shaft.

[0002]

2. Description of the Related Art In a conventional internal combustion engine, a mechanism for converting a reciprocating motion generated by a piston into a rotary motion and transmitting it to an engine output shaft generally includes a connecting rod pivotally supported by the piston. And a crankshaft on which the connecting rod is rotatably supported.

[0003]

However, the conventional transmission mechanism using the connecting rod and the crankshaft of the internal combustion engine has the following problems. 1. Near the top dead center and the bottom dead center of the crank, the force of the piston hardly contributes to the rotational force of the crankshaft. In particular, at the beginning of the explosion stroke, that is, near the top dead center of the crankshaft, the explosive force does not become a rotational force, but strongly presses the crankshaft in the axial direction.

[0004] 2. When the connecting rod is perpendicular to the crank, the torque efficiency is maximized, while the inclination angle between the piston and the connecting rod is also maximized, so the power factor transmitted from the piston to the connecting rod is reduced accordingly. . Further, since the connecting rod is considerably inclined with respect to the piston to generate a large lateral pressure on the piston, power is lost and uneven wear of the cylinder is caused to deteriorate engine performance.

[0005] 3. The crankshaft has a large shaft diameter due to its rigidity and the bearing is split so that ball bearings cannot be used. Therefore, wear loss of the bearing is not small. Further, since the rotational motion of the crankshaft is complicated, it is difficult to take measures to suppress the generated vibration. Furthermore, there is a great difficulty in manufacturing a crankshaft, especially for large marine engines.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems caused by using a crankshaft. The present invention uses a crankshaft as a mechanism for converting a reciprocating motion of a piston into a rotary motion. An object of the present invention is to provide a power transmission mechanism for an internal combustion engine that does not have the same.

[0007]

In order to solve the above-mentioned problems, a transmission mechanism for an internal combustion engine according to the present invention comprises a connecting rod for transmitting a reciprocating motion of a piston, and a connecting rod for transmitting a reciprocating motion of a piston. The swinging end of the swinging member is converted by a one-way clutch which is engaged with the swinging end of the member to convert the reciprocating movement of the piston into a swinging motion and is connected to the swinging shaft and transmits the swinging movement only when the piston is lowered. The motion is converted into a rotational motion to transmit a rotational driving force to an engine output shaft, and the piston is reciprocated by cam means linked to the rotational motion. For example, while the connecting rod is provided with a rack, the swinging member may be formed of a pinion that meshes with the rack, and the connecting rod may swing the pinion. Further, the engine output shaft may be rotated once by one reciprocation of the piston.

[0008] Preferably, the cam means includes a raising cam driven by a rotational driving force, and the raising cam sets the lowest point of the piston and raises the lowered piston, or is driven by the rotational driving force. A down cam is further provided, and the down cam lowers the raised piston.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The transmission mechanism for an internal combustion engine described above
The reciprocating motion of the piston is converted into a oscillating motion by engaging the oscillating end of a oscillating member that oscillates about the oscillating shaft with a connecting rod that transmits the reciprocating motion of the piston, and is connected to the oscillating shaft. The one-way clutch that transmits the oscillating motion only when the piston is lowered converts the oscillating motion of the oscillating member into rotational motion by transmitting the rotational driving force to the engine output shaft, and cam means that is linked to this rotational motion. The reciprocating motion of the piston can be converted into a rotational motion without using a crankshaft and transmitted to the engine output shaft as a rotational driving force without using a crankshaft. That is, since the reciprocating motion is converted into the rotary motion by using the swinging member and the one-way clutch, the so-called top dead center and bottom dead center do not exist, and the power transmission at the turning point of the reciprocating motion of the piston is performed. Is performed extremely smoothly, and the swing angle of the connecting rod with respect to the reciprocating piston, that is, the inclination angle is extremely small. Note that the cam means reciprocates the piston during a stroke in which an external force such as an explosion does not act on the piston.

Here, for example, the connecting rod may be provided with a rack, while the swinging member may be formed of a pinion that meshes with the rack, and the connecting rod may be used to swing the pinion. In this case, since the connecting rod reciprocates linearly without swinging with respect to the piston as compared with the case where, for example, a swing arm is used as the swinging member, the inclination angle of the connecting rod with respect to the piston is substantially equal. It becomes zero, and the swing range can be increased without any particular limitation. Further, the engine output shaft may be rotated once by one reciprocation of the piston. In this case, the same relationship between the stroke number of the piston and the engine speed as in the case of the conventional internal combustion engine using the crankshaft is maintained.

Preferably, the cam means includes a raising cam driven by the rotational driving force, and the raising cam sets the lowest point of the piston and raises the lowered piston. Thus, for the two-cycle engine or the four-cycle engine, the piston is raised, and the piston stroke can be easily changed by replacing the lifting cam. No,
Further provided is a lowering cam driven by the rotational driving force,
This lowering cam lowers the raised piston. As a result, the piston is lowered for the four-stroke engine in which the external force for lowering the piston does not act during intake.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to FIGS. 1 and 2 show a power transmission mechanism of an internal combustion engine according to the present invention implemented in an in-line two-cylinder four-cycle engine. 1 and 2, reference numeral 1 denotes a piston, and a connecting rod 2 is pivotally supported on the piston 1 so as to be swingable. The swing arm 3 swinging about the swing shaft 4 is rotatably supported (engaged) on the connecting rod 2 using a pin. A one-way clutch 3a is built in the boss of the swing arm 3. FIG. 3B shows details of the one-way clutch 3a. The one-way clutch 3a locks the roller by cutting into the wedge-shaped portion only when the piston 1 is lowered.
Is converted into rotational motion and transmitted to the swing shaft 4.
As shown in FIGS. 1 and 2, a counterweight 3 b is provided at the end of the swing arm 3 opposite to the engaging portion with the connecting rod 2. The swing shaft 4 meshes with the engine output shaft 9 via the gears 10 and 11. The engine output shaft 9 makes one revolution with one reciprocation of the piston 1. As described above, the anti-vibration measure of this transmission mechanism only requires the counterweight 3b to be attached to the swing arm 3, and is extremely simple as compared with the conventional crankshaft.

A raising cam 5 and a lowering cam 6 are respectively arranged on the side of the piston. The camshaft 12 has gears 13 and 1
Meshing with the engine output shaft 9 via 4, 15, 16
The lowering cam 6 is connected to the engine output shaft 9 by the cam shaft 12.
Is rotated clockwise in the figure at the same rotation speed as. Raising cam 5
Is driven by a camshaft 12 via a gear, and rotates counterclockwise in the figure at the same speed as the engine output shaft 9. In this manner, the raising cam 5 and the lowering cam 6 make one rotation each in the opposite direction with each reciprocation of the piston 1. The cam lever 7 is rotatably supported around the fulcrum 8. One end of the cam lever 7 is pivotally supported by the connecting rod 2, while a roller is rotatably supported by the other end, and the roller moves on the outer periphery of the raising cam 5 and the lowering cam 6, which will be described later. Rolling. The cam lever 7 is loosely fitted to the fulcrum 8 so as not to restrict the movement of the connecting rod 2.

Next, referring to FIG. 5 and FIG.
The shape of No. 6 will be described. FIG. 5 shows the dimensions of each part of the raising cam 5 at a position advanced by 8 ° from the ignition point position in FIG. At this time, the fulcrum 8 is located at the center of the cam lever 7. Assuming that the radius of the cam of the vertex A = R1 and the radius of the lowest point B which is a position advanced by 180 ° from the point A = R2, (R
1-R2) = piston stroke. That is, R2
Sets the lowest point of the piston. Here, the radius R3 at the point C, which is a position advanced by 8 ° from the point A, rapidly decreases, and at this time, the engagement between the raising cam 5 and the cam lever 7 is released. That is, even if the piston 1 suddenly drops due to the explosion, the movement of the piston 1 is not restricted by the raising cam 5, and all the explosive power is transmitted to the swing arm 3.

FIG. 6 shows the dimensions of each part of the lowering cam 6 at a position where the piston 1 is lowered by a half stroke from the top position in FIG. 2 during the intake stroke. If the radius of the vertex D is R4 and the radius of the lowest point E, which is a position advanced by 180 ° from the point D, is R5, then (R4-R5) = piston stroke. If the radius of the intermediate point F, which is a position advanced by 90 ° from the point E, is R = R6, R6 = (R4 + R5)
At the time of / 2, the speed at which the lowering cam 6 lowers the piston 1 is the same as the speed at which the piston 1 moves the swing arm 3 assuming that the one-way clutch 3a is locked. However, if the speed of the lowering cam 6 is higher than this, the one-way clutch 3a is locked, and the lowering cam 6 rotates the engine, which makes it difficult. Therefore, both speeds need to be equal. Alternatively, it is safer for the lowering cam 6 to be slightly slower. Similarly, the radius R7 of the down cam 6 at the position G where the piston 1 is further lowered by a quarter stroke and the cam 6 is advanced by 30 ° from the point F is R7
= (R6 + R4) / 2. Thus, the cam curve is determined.

Next, the operation of the transmission mechanism for an internal combustion engine according to the present invention will be described. The operation of the transmission mechanism of the internal combustion engine of the present invention is different from that of the conventional crankshaft only in the explosion stroke only, and the other exhaust, intake and compression strokes are basically the same as those of the conventional crankshaft. The same is true. The operation in each step will be described below.

1. Explosion process FIG. 2 shows the state of each part at the time of ignition. Since the engine is rotating and the explosive power generation is slightly delayed from the ignition, the engagement between the raising cam 5 and the cam lever 7 is disengaged at the initial stage of the explosive power activation. Therefore, the explosive force is not transmitted to the raising cam 5 but transmitted only to the swing arm 3 and further transmitted to the engine output shaft 9 via a gear group. Then, at the end point of the explosion, each part is rotated by 180 ° from the state shown in FIG. 2 to the state shown in FIG. 4, and at this time, the one-way clutch 3a of the swing arm 3 starts to idle. Thus, in this transmission mechanism,
Since the explosive force is transmitted only to the swing arm 3 and not to the lifting cam 5, the mechanical loss of power is small and the mechanism is simplified.

2. Exhaust stroke When the exhaust starts, the raising cam 5 raises the piston 1 from the position shown in FIG. At this time, the one-way clutch 3a of the swing arm 3 idles, so that the raising cam 5 raises the piston 1 without receiving any braking. In this way, the state shown in FIG. 4 is rotated by 180 ° and returned to the state shown in FIG. 2 again, and the exhaust is completed.

3. Intake stroke From the state shown in FIG. 2, when the down cam 6 pushes up the cam lever 7 to lower the piston 1, the intake starts. After rotating 180 ° from the state shown in FIG. 2, the state returns to the state shown in FIG. 4. Compression Stroke Similar to the exhaust stroke described above, from the state shown in FIG. 4, compression is started when the raising cam 5 pushes down the cam lever 7 to raise the piston 1. Then, it rotates 180 ° from the state shown in FIG. 4 and returns to the state shown in FIG. 2 again.
End compression.

In a two-stroke engine and a four-stroke engine in which compressed air is blown in the intake stroke to depress the piston, it is not necessary to depress the piston by the depressing cam. Therefore, as shown in FIG. Can be arranged directly below the connecting rod 2. In this case, the size of the engine can be significantly reduced. Further, also in the case of a normal four-stroke engine, as shown in FIG. 8, the lowering cam 6 can be arranged so that the piston can be lowered by a cam lever extending in the opposite direction of the swing arm. As a result, the size of a normal four-stroke engine can be reduced.

Further, as shown in FIG. 3, a connecting rod is provided with a rack 17 without using the swing arm 3 as a swing member.
The swing member may be constituted by a pinion 18 meshing with the rack 17, and the pinion 18 may be swung by the connecting rod 2. In this case, the inclination angle between the piston 1 and the connecting rod 2 becomes almost zero, the force of the piston 1 is transmitted to the swing shaft 4 more efficiently and smoothly, and mechanical loss of power and deviation of the cylinder are caused. Polishing is prevented. Also, pinion 1
8, the swing range as the swing member can be increased without any particular limitation as compared with the case of the swing arm 3 described above, there is no need to attach a counterweight, and the size of the engine can be reduced. Can be planned.

[0022]

As described in detail above, the transmission mechanism of the internal combustion engine according to the present invention uses a swinging member and a one-way clutch instead of a conventional crankshaft to convert reciprocating motion into rotary motion. Therefore, the following excellent effects can be obtained. 1. In the case of a crank, so-called top dead center and bottom dead center do not exist, and power transmission at the turning point of the reciprocating motion of the piston is performed extremely smoothly, so that efficient rotational force can be obtained over the entire stroke of the explosion stroke. And the mechanical loss of power is reduced. Further, the average torque and output can be improved with less torque unevenness, and the number of cylinders can be reduced by reducing the torque unevenness.

2. Since the inclination angle of the connecting rod with respect to the piston is extremely small, the side pressure generated on the piston is small, so that the mechanical loss of power can be reduced, and uneven wear of the cylinder can be prevented. 3. Since the crankshaft is not used, the mass of each part of the reciprocating part which causes vibration can be reduced, and the rotational movement is also simplified, so that measures for preventing vibration are facilitated.
Further, a ball bearing can be used instead of the split mold as the bearing of the rotary shaft, and wear loss and power loss of the bearing can be reduced. further,
The present invention is based on a combination of parts that are relatively easy to manufacture, and can eliminate the production of parts that are difficult to manufacture, such as a large crankshaft, and preferably replace the raising cam. By doing so, it becomes possible to easily change the stroke of the piston, so that significant cost reduction can be achieved.

[Brief description of the drawings]

FIG. 1 is a plan view showing an embodiment of a transmission mechanism for an internal combustion engine according to the present invention.

FIG. 2 is a front view showing a transmission mechanism of the internal combustion engine of FIG.

FIG. 3 is a view showing another embodiment of the swing member.
(A) is a front view, (B) is a sectional front view showing details of the one-way clutch 3a of FIG.

4 is a front view showing a state of the power transmission mechanism of the internal combustion engine of FIG. 2 at the time of completion of an explosion stroke or an intake stroke.

FIG. 5 is a front view showing each position dimension of the raising cam 5 of FIG. 2;

FIG. 6 is a front view showing each position dimension of the lowering cam 6 of FIG. 2;

FIG. 7 is a plan view showing another embodiment of the transmission mechanism of the internal combustion engine of the present invention.

FIG. 8 is a plan view showing still another embodiment of the transmission mechanism for an internal combustion engine of the present invention.

[Description of Signs] 1 piston, 2 connecting rod, 3 swing arm, 3a one-way clutch, 3b counterweight, 4 swing shaft, 5 up cam, 6 down cam, 7 cam lever, 8
Fulcrum, 9 engine output shaft, 10, 11 gear, 12
Camshaft, 13, 14, 15, 16 gears, 17 racks, 18 pinions,

[Procedure amendment]

[Submission date] December 9, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Full text

[Correction method] Change

[Correction contents]

[Document Name] Statement

Patent application title: Power transmission method for an internal combustion engine

[Claims]

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission method for an internal combustion engine.
Law, i.e., to convert the reciprocating motion generated by the piston into a rotational movement to a method for transmitting the engine output shaft.

[0002]

2. Description of the Related Art In a conventional internal combustion engine, a method of converting a reciprocating motion generated by a piston into a rotary motion and transmitting the rotational motion to an engine output shaft generally includes a connecting rod which is swingably supported by the piston. And a crankshaft on which the connecting rod is rotatably supported.

[0003]

However, the conventional transmission method using a connecting rod and a crankshaft of an internal combustion engine has the following problems. 1. Near the top dead center and the bottom dead center of the crank, the force of the piston hardly contributes to the rotational force of the crankshaft. In particular, at the beginning of the explosion stroke, that is, near the top dead center of the crankshaft, the explosive force does not become a rotational force, but strongly presses the crankshaft in the axial direction.

[0004] 2. When the connecting rod is perpendicular to the crank, the torque efficiency is maximized, while the inclination angle between the piston and the connecting rod is also maximized, so the power factor transmitted from the piston to the connecting rod is reduced accordingly. . Further, since the connecting rod is considerably inclined with respect to the piston to generate a large lateral pressure on the piston, power is lost and uneven wear of the cylinder is caused to deteriorate engine performance.

[0005] 3. The crankshaft has a large shaft diameter due to its rigidity and the bearing is split so that ball bearings cannot be used. Therefore, wear loss of the bearing is not small. Further, since the rotational motion of the crankshaft is complicated, it is difficult to take measures to suppress the generated vibration. Furthermore, there is a great difficulty in manufacturing a crankshaft, especially for large marine engines.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems caused by the use of a crankshaft, and uses a crankshaft as a method of converting a reciprocating motion of a piston into a rotary motion. An object of the present invention is to provide a power transmission method for an internal combustion engine that does not have the same.

[0007]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a transmission method for an internal combustion engine according to the present invention comprises a connecting rod for transmitting a reciprocating motion of a piston to a swinging rod which swings about a swinging shaft. The swinging end of the swinging member is converted by a one-way clutch which is engaged with the swinging end of the member to convert the reciprocating movement of the piston into a swinging motion and is connected to the swinging shaft and transmits the swinging movement only when the piston is lowered. The motion is converted into a rotational motion to transmit a rotational driving force to an engine output shaft, and the piston is reciprocated by cam means linked to the rotational motion. For example, while the connecting rod is provided with a rack, the swinging member may be formed of a pinion that meshes with the rack, and the connecting rod may swing the pinion. Further, the engine output shaft may be rotated once by one reciprocation of the piston.

[0008] Preferably, the cam means includes a raising cam driven by a rotational driving force, and the raising cam sets the lowest point of the piston and raises the lowered piston, or is driven by the rotational driving force. A down cam is further provided, and the down cam lowers the raised piston.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The above-described transmission method for an internal combustion engine includes:
The reciprocating motion of the piston is converted into a oscillating motion by engaging the oscillating end of a oscillating member that oscillates about the oscillating shaft with a connecting rod that transmits the reciprocating motion of the piston, and is connected to the oscillating shaft. The one-way clutch that transmits the oscillating motion only when the piston is lowered converts the oscillating motion of the oscillating member into rotational motion by transmitting the rotational driving force to the engine output shaft, and cam means that is linked to this rotational motion. The reciprocating motion of the piston can be converted into a rotational motion without using a crankshaft and transmitted to the engine output shaft as a rotational driving force without using a crankshaft. That is, since the reciprocating motion is converted into the rotary motion by using the swinging member and the one-way clutch, the so-called top dead center and bottom dead center do not exist, and the power transmission at the turning point of the reciprocating motion of the piston is performed. Is performed extremely smoothly, and the swing angle of the connecting rod with respect to the reciprocating piston, that is, the inclination angle is extremely small. Note that the cam means reciprocates the piston during a stroke in which an external force such as an explosion does not act on the piston.

Here, for example, the connecting rod may be provided with a rack, while the swinging member may be formed of a pinion that meshes with the rack, and the connecting rod may be used to swing the pinion. In this case, since the connecting rod reciprocates linearly without swinging with respect to the piston as compared with the case where, for example, a swing arm is used as the swinging member, the inclination angle of the connecting rod with respect to the piston is substantially equal. It becomes zero, and the swing range can be increased without any particular limitation. Further, the engine output shaft may be rotated once by one reciprocation of the piston. In this case, the same relationship between the stroke number of the piston and the engine speed as in the case of the conventional internal combustion engine using the crankshaft is maintained.

Preferably, the cam means includes a raising cam driven by the rotational driving force, and the raising cam sets the lowest point of the piston and raises the lowered piston. Thus, for the two-cycle engine or the four-cycle engine, the piston is raised, and the piston stroke can be easily changed by replacing the lifting cam. No,
Further provided is a lowering cam driven by the rotational driving force,
This lowering cam lowers the raised piston. As a result, the piston is lowered for the four-stroke engine in which the external force for lowering the piston does not act during intake.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to FIGS. 1 and 2 relate to the present invention .
1 shows a transmission mechanism of an in- line two-cylinder four-stroke engine for implementing the method described above. 1 and 2, reference numeral 1 denotes a piston, and a connecting rod 2 is pivotally supported on the piston 1 so as to be swingable.
The swing arm 3 swinging about the swing shaft 4 is rotatably supported (engaged) on the connecting rod 2 using a pin. A one-way clutch 3a is built in the boss of the swing arm 3. FIG. 3B shows details of the one-way clutch 3a. In the one-way clutch 3a, only when the piston 1 is lowered, the roller bites into the wedge-shaped portion and locks, and the linear motion of the piston 1 is converted into rotational motion and transmitted to the swing shaft 4. As shown in FIGS. 1 and 2, a counterweight 3 b is provided at the end of the swing arm 3 opposite to the engaging portion with the connecting rod 2. The swing shaft 4 meshes with the engine output shaft 9 via the gears 10 and 11. The engine output shaft 9 is connected to the piston 1
Make one revolution in reciprocation. As described above, the anti-vibration measure of this transmission mechanism only requires the counterweight 3b to be attached to the swing arm 3, and is extremely simple as compared with the conventional crankshaft.

A raising cam 5 and a lowering cam 6 are respectively arranged on the side of the piston. The camshaft 12 has gears 13 and 1
Meshing with the engine output shaft 9 via 4, 15, 16
The lowering cam 6 is connected to the engine output shaft 9 by the cam shaft 12.
Is rotated clockwise in the figure at the same rotation speed as. Raising cam 5
Is driven by a camshaft 12 via a gear, and rotates counterclockwise in the figure at the same speed as the engine output shaft 9. In this manner, the raising cam 5 and the lowering cam 6 make one rotation each in the opposite direction with each reciprocation of the piston 1. The cam lever 7 is rotatably supported around the fulcrum 8. One end of the cam lever 7 is pivotally supported by the connecting rod 2, while a roller is rotatably supported by the other end, and the roller moves on the outer periphery of the raising cam 5 and the lowering cam 6, which will be described later. Rolling. The cam lever 7 is loosely fitted to the fulcrum 8 so as not to restrict the movement of the connecting rod 2.

Next, referring to FIG. 5 and FIG.
The shape of No. 6 will be described. FIG. 5 shows the dimensions of each part of the raising cam 5 at a position advanced by 8 ° from the ignition point position in FIG. At this time, the fulcrum 8 is located at the center of the cam lever 7. Assuming that the radius of the cam of the vertex A = R1 and the radius of the lowest point B which is a position advanced by 180 ° from the point A = R2, (R
1-R2) = piston stroke. That is, R2
Sets the lowest point of the piston. Here, the radius R3 at the point C, which is a position advanced by 8 ° from the point A, rapidly decreases, and at this time, the engagement between the raising cam 5 and the cam lever 7 is released. That is, even if the piston 1 suddenly drops due to the explosion, the movement of the piston 1 is not restricted by the raising cam 5, and all the explosive power is transmitted to the swing arm 3.

FIG. 6 shows the dimensions of each part of the lowering cam 6 at a position where the piston 1 is lowered by a half stroke from the top position in FIG. 2 during the intake stroke. If the radius of the vertex D is R4 and the radius of the lowest point E, which is a position advanced by 180 ° from the point D, is R5, then (R4-R5) = piston stroke. If the radius of the intermediate point F, which is a position advanced by 90 ° from the point E, is R = R6, R6 = (R4 + R5)
At the time of / 2, the speed at which the lowering cam 6 lowers the piston 1 is the same as the speed at which the piston 1 moves the swing arm 3 assuming that the one-way clutch 3a is locked. However, if the speed of the lowering cam 6 is higher than this, the one-way clutch 3a is locked, and the lowering cam 6 rotates the engine, which makes it difficult. Therefore, both speeds need to be equal. Alternatively, it is safer for the lowering cam 6 to be slightly slower. Similarly, the radius R7 of the down cam 6 at the position G where the piston 1 is further lowered by a quarter stroke and the cam 6 is advanced by 30 ° from the point F is R7
= (R6 + R4) / 2. Thus, the cam curve is determined.

Next, the transmission method of the internal combustion engine according to the present invention will be described. Transmission method for an internal combustion engine of the present invention, compared with the method according to the conventional crankshaft, only particular only the explosion stroke is different, the other exhaust gas, intake, each stroke of compression similar to basically conventional is there. The operation in each step will be described below.

1. Explosion process FIG. 2 shows the state of each part at the time of ignition. Since the engine is rotating and the explosive power generation is slightly delayed from the ignition, the engagement between the raising cam 5 and the cam lever 7 is disengaged at the initial stage of the explosive power activation. Therefore, the explosive force is not transmitted to the raising cam 5 but transmitted only to the swing arm 3 and further transmitted to the engine output shaft 9 via a gear group. Then, at the end point of the explosion, each part is rotated by 180 ° from the state shown in FIG. 2 to the state shown in FIG. 4, and at this time, the one-way clutch 3a of the swing arm 3 starts to idle. Thus, in this transmission method ,
Since the explosive force is transmitted only to the swing arm 3 and not to the lifting cam 5, the mechanical loss of power is small and the mechanism is simplified.

2. Exhaust stroke When the exhaust starts, the raising cam 5 raises the piston 1 from the position shown in FIG. At this time, the one-way clutch 3a of the swing arm 3 idles, so that the raising cam 5 raises the piston 1 without receiving any braking. In this way, the state shown in FIG. 4 is rotated by 180 ° and returned to the state shown in FIG. 2 again, and the exhaust is completed.

3. Intake stroke From the state shown in FIG. 2, when the down cam 6 pushes up the cam lever 7 to lower the piston 1, the intake starts. After rotating 180 ° from the state shown in FIG. 2, the state returns to the state shown in FIG. 4. Compression Stroke Similar to the exhaust stroke described above, from the state shown in FIG. 4, compression is started when the raising cam 5 pushes down the cam lever 7 to raise the piston 1. Then, it rotates 180 ° from the state shown in FIG. 4 and returns to the state shown in FIG. 2 again.
End compression.

In a two-stroke engine and a four-stroke engine in which compressed air is blown in the intake stroke to depress the piston, it is not necessary to depress the piston by the depressing cam. Therefore, as shown in FIG. Can be arranged directly below the connecting rod 2. In this case, the size of the engine can be significantly reduced. Further, also in the case of a normal four-stroke engine, as shown in FIG. 8, the lowering cam 6 can be arranged so that the piston can be lowered by a cam lever extending in the opposite direction of the swing arm. As a result, the size of a normal four-stroke engine can be reduced.

Further, as shown in FIG. 3, a connecting rod is provided with a rack 17 without using the swing arm 3 as a swing member.
The swing member may be constituted by a pinion 18 meshing with the rack 17, and the pinion 18 may be swung by the connecting rod 2. In this case, the inclination angle between the piston 1 and the connecting rod 2 becomes almost zero, the force of the piston 1 is transmitted to the swing shaft 4 more efficiently and smoothly, and mechanical loss of power and deviation of the cylinder are caused. Polishing is prevented. Also, pinion 1
8, the swing range as the swing member can be increased without any particular limitation as compared with the case of the swing arm 3 described above, there is no need to attach a counterweight, and the size of the engine can be reduced. Can be planned.

[0022]

As described above in detail, the transmission method for an internal combustion engine according to the present invention uses a swinging member and a one-way clutch instead of a conventional crankshaft to convert reciprocating motion into rotary motion. Therefore, the following excellent effects can be obtained. 1. In the case of a crank, so-called top dead center and bottom dead center do not exist, and power transmission at the turning point of the reciprocating motion of the piston is performed extremely smoothly, so that efficient rotational force can be obtained over the entire stroke of the explosion stroke. And the mechanical loss of power is reduced. Further, the average torque and output can be improved with less torque unevenness, and the number of cylinders can be reduced by reducing the torque unevenness.

2. Since the inclination angle of the connecting rod with respect to the piston is extremely small, the side pressure generated on the piston is small, so that the mechanical loss of power can be reduced, and uneven wear of the cylinder can be prevented. 3. Since the crankshaft is not used, the mass of each part of the reciprocating part which causes vibration can be reduced, and the rotational movement is also simplified, so that measures for preventing vibration are facilitated.
Further, a ball bearing can be used instead of the split mold as the bearing of the rotary shaft, and wear loss and power loss of the bearing can be reduced. further,
The present invention is based on a combination of parts that are relatively easy to manufacture, and can eliminate the production of parts that are difficult to manufacture, such as a large crankshaft, and preferably replace the raising cam. By doing so, it becomes possible to easily change the stroke of the piston, so that significant cost reduction can be achieved.

[Brief description of the drawings]

FIG. 1 shows an internal combustion engine that implements a power transmission method according to an embodiment of the present invention.
FIG. 2 is a plan view showing a transmission mechanism of the engine .

FIG. 2 is a front view showing a transmission mechanism of the internal combustion engine of FIG.

FIG. 3 is a diagram showing another swing member . (A) is a front view, (B) is a sectional front view showing details of the one-way clutch 3a of FIG.

4 is a front view showing a state of the power transmission mechanism of the internal combustion engine of FIG. 2 at the time of completion of an explosion stroke or an intake stroke.

FIG. 5 is a front view showing each position dimension of the raising cam 5 of FIG. 2;

FIG. 6 is a front view showing each position dimension of the lowering cam 6 of FIG. 2;

7 is a plan view showing another embodiment of the present invention.

Is a plan view showing another embodiment in Figure 8 is found.

[Description of Signs] 1 piston, 2 connecting rod, 3 swing arm, 3a one-way clutch, 3b counterweight, 4 swing shaft, 5 up cam, 6 down cam, 7 cam lever, 8
Fulcrum, 9 engine output shaft, 10, 11 gear, 12
Camshaft, 13, 14, 15, 16 gears, 17 racks, 18 pinions,

Claims (5)

[Claims] 1. A swinging end of a swinging member (3, 18) which swings around a swinging shaft (4) is engaged with a connecting rod (2) for transmitting a reciprocating movement of a piston (1). The one-way clutch (3a), which is connected to the swing shaft and transmits the swing motion only when the piston descends, converts the swing motion of the swing member into swing motion. A transmission mechanism for an internal combustion engine, wherein the piston is reciprocated by cam means (5, 7) interlocked with the rotational movement while transmitting the rotational driving force to an engine output shaft (9) by converting the rotational drive into a rotational movement. . 2. The connecting rod (2) is provided with a rack (17), while the swinging member comprises a pinion (18) meshing with the rack, and the connecting rod swings the pinion. The transmission mechanism for an internal combustion engine according to claim 1, wherein: 3. The transmission mechanism of an internal combustion engine according to claim 1, wherein the engine output shaft (9) makes one revolution with one reciprocation of the piston (1). 4. The cam means includes a raising cam (5) driven by the rotational driving force, the raising cam setting a lowermost point of the piston (1) and raising the lowered piston. 3. The method according to claim 1, wherein:
Or a transmission mechanism for an internal combustion engine according to 3. 5. The cam means further comprising a down cam (6) driven by the rotational driving force, wherein the down cam lowers the raised piston (1). Transmission mechanism for an internal combustion engine according to claim 1.