KR20180087081A - New Power Transmission of Boxer Engine - Google Patents

Abstract

The present invention relates to a new power transmission apparatus of a Boxer engine, which comprises both side pistons (100) facing each other, a rack type connecting rod (300) including two rack gears (320A, 320B) installed on the bottom and the top of a body (310) to be tilted and faced with each other and a fixing means (330) to fix both ends of the body (310) to both the pistons (100) facing each other, an output shaft (200), and two one-way gears (400A, 400B) fixed to the output shaft so as to convert linear reciprocating motion of both the pistons facing each other into rotary motion of the output shaft through the rack type connecting rod and the one-way gear. According to the present invention, when the new power transmission apparatus is applied to the Boxer engine, most of gas pressure applied to a piston is converted into linear reciprocating motion of the piston and most of the linear reciprocating motion of the piston is converted into rotary motion of the output shaft. Moreover, a design to maximize the gas pressure (explosive force) applied to the piston when the piston reaches the top dead center is implemented. Accordingly, the new power transmission apparatus is installed in the Boxer engine, thereby being able to remarkably increase fuel efficiency of the Boxer engine.

Description

{New Power Transmission of Boxer Engine}

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[TECHNICAL FIELD OF THE INVENTION AND RELATED ART OF THE SAME]

The present invention relates to a power transmission device (new power transmission device) for converting a linear reciprocating motion of both pistons opposed to each other in a boxer engine into a rotary motion of an output shaft (crankshaft). In the present specification, the power transmission device refers to a device that converts the linear reciprocating motion of the two side pistons against each other into the rotational motion of the output shaft. Conventionally, the crankshaft of a piston engine and a boxer engine has been described as an output shaft in the power transmission device of the present invention.

1 is a conceptual view of a boxer engine having two side pistons opposed to each other. These boxer engines are sometimes referred to as horizontal engines in that the two engines are facing each other. The two side pistons 10 opposed to each other in the boxer engine linearly reciprocate and the linear reciprocating motion of the piston is converted into the rotational motion of the output shaft 40 through the connecting rod 20 and the crank 30. Therefore, in the conventional boxer engine, the power transmission apparatus is composed of the two side pistons, the connecting rod, the crank, and the output shaft (crankshaft) which oppose each other. These boxing engines have common problems with piston engines.

2 is a conceptual view showing four strokes of a piston engine. In general, the piston engine is distinguished by a two-stroke engine and a four-stroke engine. In the two-stroke engine, one cycle including suction, compression, explosion and exhaust is completed during one revolution of the crank. In the four-stroke engine, one cycle is completed while the crank rotates twice. In this piston engine, the linear reciprocating motion of the piston is converted into rotational motion of the output shaft through the connecting rod and the crank. Thus, in a piston engine, the power train consists of a piston, a connecting rod, a crank, and an output shaft.

In the case of the box-shaped engine and the piston engine, the power transmission apparatus has a serious problem in the process of converting the linear reciprocating motion of the piston into the rotational motion of the crankshaft.

First, the power loss during the power transmission process is very large. Generally, the piston engine begins to explode at approximately 5 ° before reaching the top dead center. Then, at approximately 15 ° past the top dead center, the piston cylinder is at its maximum pressure. Here, the explosive force acting on the piston until the piston reaches the top dead point is opposite to the rotational direction of the crank. Therefore, the explosive force acting on the piston until the piston reaches the top dead center reduces the rotational force of the crank.

Second, the piston and power transmission device are prone to breakage or deformation during power transmission. Conventional piston engines and boxer engines have an explosive force generated in the piston cylinder acting substantially perpendicular to the piston, the connecting rod, and the crank and crankshaft. Particularly, when the piston reaches the top dead center in the explosion stroke, the connecting rod, the crank and the crankshaft become straight. At this time, since the explosive force generated in the piston cylinder acts perpendicularly to the connecting rod, the crank and the crankshaft, the connecting rod, the crankshaft and the crankshaft are subjected to a very large impact. Therefore, the piston and the connecting rod, and the crank and the crankshaft are liable to be damaged or deformed.

Third, it can not be designed to maximize the gas pressure acting on the piston cylinder when the piston reaches the top dead center. In theory, the force acting on the piston becomes maximum when the gas pressure reaches a maximum when the piston reaches the top dead center. However, in the conventional piston engine and the boxer engine, the gas pressure acting on the piston cylinder is not the maximum when the piston reaches the top dead center. In conventional piston engines and boxer engines, the explosion stroke typically begins just before the piston reaches the top dead center. And the gas pressure acting on the piston cylinder at about 15 degrees past the top dead center of the piston is at its maximum. The reason for this design is to reduce the explosive force acting in the direction opposite to the rotation direction of the output shaft. In theory, when the gas pressure acting on the piston becomes maximum when the piston reaches the top dead center, the rotational force of the piston becomes zero. If about 50% of the gas pressure acting on the piston acts in the direction of rotation of the crankshaft, about 50% of the gas pressure acts opposite the direction of rotation of the crankshaft. Therefore, in the conventional piston engine and the boxer engine, the gas pressure when the piston reaches the top dead center can not be designed to be the maximum.

Fourth, in conventional boxer engines and piston engines all pistons must work together. If the engine has five pistons, the five pistons always work together. It is not possible to control the number of pistons operating according to the situation in the process of power transmission. Therefore, the fuel loss is large.

As described above, the conventional boxer engine and the piston engine have a large energy loss during the power transmission process, and the piston and the power transmission device are liable to be damaged or deformed. Also, it can not be designed so that the gas pressure acting on the piston cylinder becomes maximum when the piston reaches the top dead center. And it can not be adjusted to operate only a specific piston in many pistons. In this respect, the conventional boxer engine and the piston engine are low in fuel consumption, prone to failure, and have poor performance.

[Technical Problem]

The present invention seeks to create a new power transmission device that solves problems arising in conventional box engine and piston engines. Specifically, by applying a new power transmission device to the boxer engine, most of the explosive force acting on the piston is converted into rotary motion of the output shaft, so that damage and breakage of the piston and the power transmission device do not occur. By applying a new power transmission system to the boxer engine, we want to maximize the gas pressure of the cylinder when the piston reaches the top dead center.

To this end, two unidirectional gears are provided on the output shaft for connecting the two pistons opposing each other of the boxer engine with connecting rods and converting the linear reciprocating motion of the connecting rod into rotary motion. The connecting rods used here constitute two rack gears with the body facing each other in a staggered manner. This is referred to as " rack-type connecting rod 300 " in the specification of the present invention. Here, a one-way gear is a gear that transmits power in one direction by installing a one-way clutch therein. Generally, one-way clutch bearings are installed at the center of the one-way gear.

Specifically, the rack-type connecting rod performs a linear reciprocating motion to the left and right when the two pistons opposed to each other in the boxer engine explode. The linear reciprocating motion of the rack-type connecting rod is converted into rotational movement of the output shaft through two rack gears provided on the rack-shaped connecting rod and two unidirectional gears provided on the output shaft.

[Structure and operation of the invention]

The construction of the present invention will be described in detail with reference to the accompanying drawings. Fig. 3 is a perspective view of a new power transmission device of a boxer engine, and Fig. 4 is an exploded perspective view of a new power transmission device of a boxer engine. 3 to 6 are photographs of a model of a new power transmission apparatus of the present invention.

The present invention relates to a bicycle comprising two side racks 320A and 320B provided on both sides of a body 310 opposite to each other at a lower end and an upper end thereof, A rack-type connecting rod 300 constituted by a fixing means 330 for fixing the two pistons 100 to the opposite pistons 100 against each other, and two unidirectional gears 400A and 400B fixed to the output shaft 200 and the output shaft .

The rack-type connecting rod 300 includes a rack gear A (320A) provided at the lower end of the body 310 in the longitudinal direction, a rack gear B (320B) provided at the upper end of the body in the longitudinal direction, Quot;) < / RTI > to the opposite side pistons 100 against each other ".

Two unidirectional gears 400A and 400B functioning to transmit power to the output shaft 200 in one direction are provided. Generally, a one-way clutch gear is composed of an inner gear portion and an outer gear portion, and a one-way clutch is provided therebetween. Here, power is transmitted when the one-way clutch connects the inner gear portion and the outer gear portion.

The arrangement of the main part of the present invention is as follows. Both ends of the rack-type connecting rod 300 are fixed to the both side pistons 100 against each other by the fixing means 330. The rack gear A (320A) formed at the lower end of the rack-type connecting rod and the rack gear B (320B) formed at the upper end are staggered with each other. The output shaft 200 is located at the center between the lower rack gear A 320A and the upper rack gear B 320B and two unidirectional gears 400A and 400B are fixed to the output shaft. Here, the rack gear A (320A) at the lower end of the rack-type connecting rod is engaged with the one-way gear A (400A) located at the front side. Concretely, the rack gear A (320A) at the lower end of the rack-shaped connecting rod and the lower portion of the one-way gear A (400A) at the output shaft are engaged with each other. And the rack gear B (320B) at the top of the rack-type connecting rod is engaged with the one-way gear B (400B) located at the rear side. Concretely, the rack gear B (320B) at the upper end of the rack-shaped connecting rod and the upper portion of the one-way gear B (400B) at the output shaft are engaged with each other.

In the present invention, the process of converting the linear reciprocating motion of the two side pistons against each other into the rotary motion of the output shaft is as follows. Here, the two unidirectional gears 400A and 400B all transmit the power when the outer gear portion rotates forward. The linear reciprocating motion of the two side pistons against each other is finally transmitted to the forward rotation of the output shaft. In this case, the clutch connection (power transmission) of the one-way gear is shown in the following table.

First, let's look at the power transmission process when both pistons 100 against each other advance to the right (F). The two side pistons are advanced to the right side, and at the same time, the rack-type connecting rod 300 is advanced to the right side. And the outer gear portion of the one-way gear A (400A) engaged with the rack gear A (320A) at the lower end of the rack-type connecting rod makes a reverse rotation. At this time, since the clutch of the one-way gear is disengaged, no power is transmitted. And the outer gear portion of the unidirectional gear B (400B) engaged with the rack gear B (320B) at the upper end of the rack-like connecting rod makes forward rotation. At this time, since the clutch of the one-way gear is connected, power is transmitted. Therefore, the one-way gear B (400B) and the output shaft (200) rotate forward.

When the two side pistons 100 opposed to each other are moved back to the left side (B), the rack-type connecting rod 300 is moved backward to the left. Then, the outer gear portion of the one-way gear A (400A) engaged with the rack gear A (320A) at the lower end of the rack-type connecting rod performs forward rotation. At this time, since the clutch of the one-way gear is connected, power is transmitted. Therefore, the one-way gear A and the output shaft rotate normally. And the outer gear portion of the unidirectional gear B (400B) engaging with the rack gear B (320B) at the upper end of the rack-shaped connecting rod makes a reverse rotation. At this time, since the clutch of the one-way gear is disengaged, no power is transmitted.

When the rotational speed of the output shaft 200 is faster than the linear reciprocating speed of the rack-type connecting rod, the output shaft idles. Such a case generally occurs when the output shaft 200 rotates normally in rotational inertia after the engine stops operating. And the inner gear portion of the front one-way gear A (400A) performs forward rotation together with the forward rotation of the output shaft. At this time, since the clutch of the one-way gear is disengaged, the rotational force of the output shaft is not transmitted to the rack gear A (300A). And the inner gear portion of the rear unidirectional gear B (400B) performs forward rotation together with the normal rotation of the output shaft. At this time, since the clutch of the one-way gear is disengaged, the rotational force of the output shaft is not transmitted to the rack gear B (300B).

5 to 6 show another embodiment of the new power transmission device of the boxer engine of the present invention. Fig. 5 is a perspective view, and Fig. 6 is an exploded perspective view. The new power transmission device of the boxer engine as shown in Figs. 5 to 6 is for preventing a deflected impact from being generated in a part of the piston during the power transmission process. Three rack gears 320A, 320B and 320C are provided on the body 310 of the rack-type connecting rod 300 and three one-way gears 400A, 400B and 400C are provided on the output shaft 200. [ The rack gear A 320A and the one-way gear A 400A, the rack gear B 320B and the one-way gear B 400B and the rack gear C 320C and the one-way gear C 400C are engaged with each other.

The rack-type connecting rod 300 advances to the right when both the pistons 100 opposed to each other advance to the right (F). And the outer gear portion of the unidirectional gear B (400B) engaged with the rack gear B (320B) at the upper end of the rack-like connecting rod makes forward rotation. At this time, since the clutch of the one-way gear is connected, the power is transmitted to the output shaft 200.

When the two side pistons 100 opposed to each other move back to the left (B), the rack-type connecting rod is moved back to the left. Then, the one-way gear A 400A engaged with the rack gear A 320A and the rack gear C 320C at the lower end of the rack-type connecting rod and the outer gear portion of the one-way gear C 400C rotate forward. At this time, since the clutch of the one-way gear is connected, the power is transmitted to the output shaft 200.

In the new power transmission apparatus of the boxer engine described in Figs. 3 to 6, there is one set of pistons opposed to each other. Such cases are applicable to two-administration institutions and not to four-agency institutions. This is because the explosion stroke is always required when the piston reaches the top dead point in order for the piston to reciprocate linearly in the left and right direction in the boxer engine having one set of pistons. In order to apply the new power transmission apparatus of the present invention to a two-stroke boxer engine, there must be two or more sets of pistons opposed to each other.

Fig. 7 is an embodiment of a rack-type connecting rod capable of adjusting the length. FIG. 7 shows a simple method of adjusting the length of the rack-type connecting rod by adjusting the length of the fixing means 330 of the rack-type connecting rod. The cylindrical pipe 331 is fixed to the body 310 of the rack connecting rod 300 and a cylinder 332 movable in the left and right directions inside the cylindrical pipe is fixed to the piston 100. Then, the cylindrical pipe and the cylinder are fixed by the fixing pin 333.

The length of the fixing means is shortened when the cylinder 332 is inserted into the cylindrical pipe 331 with a greater depth to fix the cylinder 332 with the fixing pin 333. [ The shorter length of the fixing means means that the length of the rack-type connecting rod is shortened. On the other hand, the length of the fixing means becomes longer when the cylindrical pipe and the cylinder are opened and fixed with the fixing pin. The increased length of the fastening means means that the length of the rack-like connecting rod is longer.

When the length of the rack-type connecting rod is increased, the distance between the top dead center and the bottom dead center of the piston is shortened. Therefore, the linear reciprocating distance of the piston is shortened, and the time between strokes becomes shorter in the two-stroke boxer engine and the four-stroke boxer engine. Thus, the number of explosion strokes increases for one minute. As a result, the rotational speed of the output shaft is maintained to be similar, and the magnitude of the rotational force becomes very large. However, the number of explosion strokes per minute increases, so fuel efficiency drops. Therefore, it is desirable to selectively adjust the length of the rack-type connecting rod in a long period of time in the case where a large force is required on the output shaft.

When the length of the rack-type connecting rod is shortened, the distance between the top dead center and the bottom dead center of the piston becomes long. The position of the top dead center is raised slightly due to the pressure in the cylinder occurring in the compression stroke and the explosion stroke, while the position of bottom dead center is greatly lowered. That is, the position change of the bottom dead center is larger than the position change of the top dead center. Therefore, the linear reciprocating distance of the piston becomes longer, and the inter-stroke time becomes longer in the two-stroke boxer engine and the four-stroke boxer engine. This reduces the number of explosions for one minute and increases the reciprocating distance of the rack-type connecting rod. As a result, the rotational speed of the output shaft is maintained at a similar level, but the magnitude of the rotational force is reduced. However, fuel consumption increases as the number of explosions per minute decreases.

When the distance between the top dead center and the bottom dead center of the piston changes as described above, the pressure in the cylinder in the compression stroke is different. Therefore, it is necessary to regulate the amount of fuel supplied to the cylinder through the fuel device. With this method, an optimal compression ratio can be realized when the distance between the top dead center and the bottom dead center of the piston changes.

Fig. 8 shows two sets of two side pistons opposed to each other, and two rack-type connecting rods connecting the pistons opposed to each other. Therefore, the two rack-type connecting rods are independent of each other. Such a new power transmission apparatus is applicable to a two-stroke engine and is difficult to apply to a four-stroke engine. This is because each piston needs an explosion stroke when it reaches the top dead point in order for the piston to reciprocate linearly.

The explosion time of the piston A, the piston B, the piston C, and the piston D is designed to be different in the power transmission process of the boxer engine equipped with the new power transmission device as shown in Fig. When the piston A is at the top dead center, the piston C is between the top dead center and the bottom dead center, and when the piston C is at the top dead center, the piston A is between the top dead center and bottom dead center. In this way, the power can be reliably transmitted to the output shaft.

Fig. 9 shows a case of a boxer engine in which the piston set 1 (S1) and the piston set 2 (S2) are connected to each other by a single rack-like connecting rod. This new power transmission system can be applied to both two-stroke box engines and four-stroke boxer engines. Since piston set 1 and piston set 2 are connected by a single rack-shaped connecting rod, all pistons are reciprocating in the same direction.

First, the sequence of the explosion stroke in the two-stroke boxer engine is as follows. An explosion stroke occurs simultaneously when the piston AC on the left reaches the top dead center. When the piston BD on the right side reaches the top dead center, an explosion stroke occurs simultaneously. In this way, two strokes are completed in a boxer engine with two sets of pistons opposing each other.

And the sequence of explosion administration in the four - stroke boxer engine is as follows. First, an explosion stroke occurs in the piston A when the piston AC on the left side reaches the top dead center. And an explosion stroke occurs in the piston B when the piston BD on the right side reaches the top dead center. And an explosion stroke occurs in the piston C when the piston AC on the left reaches the top dead point again. And an explosion stroke occurs in the piston D when the piston BD on the right side reaches the top dead point again. In this way, four strokes are completed in a boxer engine with two sets of pistons.

Fig. 10 shows a case in which four pistons are opposed to each other, and all the pistons are connected by a single rack-like connecting rod. This case applies to both two-stroke boxer engines and four-stroke boxer engines. Since all the pistons are connected by a single rack-shaped connecting rod, all the pistons are reciprocating in the same direction.

First, the sequence of the explosion stroke in the two-stroke boxer engine is as follows. An explosion stroke occurs simultaneously when the piston ACEG on the left reaches the top dead center. Also, when the piston BDFH on the right side reaches the top dead point, an explosion stroke occurs simultaneously. In this way, two strokes are completed in a boxer engine with two sets of pistons opposing each other.

And the sequence of explosion administration in the four - stroke boxer engine is as follows. First, an explosion stroke occurs in the piston AG when the piston ACEG on the left side reaches the top dead center. When the piston BDFH on the right side reaches the top dead point, an explosion stroke occurs in the piston DF. When the piston ACEG on the left side reaches the top dead point again, an explosion stroke occurs on the piston CE. When the piston BDFH on the right side reaches the top dead point again, an explosion stroke occurs in the piston BH. In this manner, four strokes are completed in a boxer engine with four sets of pistons.

Fig. 11 shows a case in which there are four sets of pistons opposed to each other and two rack-type connecting rods connecting the pistons opposed to each other. This new power transmission system can be applied to both two-stroke box engines and four-stroke boxer engines.

First, the piston set 1 (S1) and the piston set 2 (S2) perform a linear reciprocating motion in the two-stroke boxer engine, and the piston set 3 (S3) and the piston set 4 (S4) reciprocate linearly together. In addition, the explosion time of the piston AC, piston BD, piston EG, and piston FH is designed differently in the power transmission process. When the piston AC is at the top dead center, the piston AC is between the top dead center and the bottom dead center when the piston EG is between the top dead center and the bottom dead center and the piston EG is at the top dead center. Therefore, when the explosion stroke occurs at the top dead center of the piston AC, the piston BD is at the bottom dead center, and the piston EG and the piston FH are between the top dead center and the bottom dead center. In this way, two strokes are completed.

In the four-stroke boxer engine, the piston set 1 (S1) and the piston set 2 (S2) together make a linear reciprocating motion, and the piston set 3 (S3) and the piston set 4 (S4) reciprocate linearly together. And, during the power transmission process, the piston EG is between the top dead center and the bottom dead center when the piston AC is at the top dead center. Here, when the piston AC is at the top dead center, an explosion stroke occurs in the piston A, and an exhaust stroke occurs in the piston C. When the piston AC is again at the top dead center, an exhaust stroke takes place in the piston A, and an explosion stroke occurs in the piston C. In this way, four strokes are completed.

The new power transmission of the boxer engine of the present invention is applicable to both two-stroke boxer engines and four-stroke boxer engines. Depending on the type of boxer engine (two-stroke boxer engine, four-stroke boxer engine) or the number of piston sets, various configurations of the new transmission are possible. The number of piston sets which are basically opposed to each other can be increased to two or more in the manner shown in Figs. It is necessary to design the configuration of the new power transmission device and the explosion stroke time of each piston in accordance with the requirements of the boxer engine.

The rack-type connecting rod in the new power transmission apparatus of the boxer engine of the present invention is partially deformable. You can change the position of the rack gear on the bottom and the rack gear on the top. In the new power transmission apparatus of the boxer engine of the present invention, a flywheel, a reverse gear, or a multi-stage transmission may be mounted on the output shaft 200. Depending on the requirements of the boxer engine, a different power transmission device may be installed on the output shaft of the new power train.

The new power transmission device of the boxer engine of the present invention converts most of the linear reciprocating force acting on both pistons against each other into rotational motion of the output shaft. Theoretically, all the forces except the frictional force between the piston and the cylinder and the frictional force generated by the gear type power transmission process are converted into the rotational motion of the output shaft. Specifically, the new power transmission device of the boxer engine of the present invention has the following advantages over the conventional piston engine and the boxer engine.

First, most of the explosive force acting on the piston in the new power transmission apparatus of the boxer engine of the present invention is converted into rotational motion of the output shaft.

In the new power transmission apparatus of the boxer engine of the present invention, the explosive force acting on the piston functions in the same way as the rotation direction of the output shaft (crankshaft). Therefore, the explosive force acting on the piston until the piston reaches the top dead center serves to enhance the rotational motion of the output shaft.

Second, the new power transmission device of the boxer engine of the present invention has little mechanical damage generated in the structure of the power transmission device. Because the force of the linear reciprocating motion of the piston acts on the side of the unidirectional gear through the rack-type connecting rod. Therefore, the problems occurring in the power transmission device of the conventional boxer engine can be drastically reduced.

Third, the new power transmission device of the boxer engine of the present invention can be designed so that the explosion pressure of the piston reaches a maximum when the piston reaches the top dead center. With this design, the explosion pressure acting on the piston can be maximized. With this design, the maximum explosive force generated in the piston can be converted into a linear reciprocating motion of the piston.

Fourth, the boxer engine equipped with the new power transmission device of the present invention can cause a specific piston to operate in the power transmission process. This is because the linear reciprocating motion of the piston against each other is transmitted to the output shaft through the rack gear 320 and the one-way gear 400. Therefore, the boxer engine equipped with the new power transmission device of the present invention can save fuel by controlling the number of pistons in the process of power transmission.

Fifth, the new power transmission device of the boxer engine of the present invention can adjust the magnitude of the rotational force of the output shaft by adjusting the length of the rack-type connecting rod. Conventionally, the boxer engine and the piston engine are structurally difficult to control the distance between the top dead center and the bottom dead center of the piston. The rack-type connecting rod of the new power transmission apparatus of the present invention can be adjusted in length by various methods. Simply by adjusting the length of the fastening means 330, the length of the rack-like connecting rod can be adjusted. More simply, a plurality of rack-shaped connecting rods of different lengths, which can be mounted on one boxer engine, can be made. You will be able to select and use a rack-type connecting rod of the appropriate length for the use of the boxer engine.

In the future, various methods of automatically adjusting the length of the rack-type connecting rod using an actuator and an electronic control unit (ECU) may be developed. With the current technology of actuators and electronic controls, the length of the rack-type connecting rod can be adjusted in various ways.

For the above reasons, the box-shaped engine equipped with the new power transmission device of the present invention has remarkably high fuel consumption and hardly causes mechanical breakage or deformation. With a rack-type connecting rod that automatically changes its specific length, the boxer engine will have a high performance and a completely different performance from the conventional boxer engine and piston engine of the engine.

In particular, the new power transmission device of the boxer engine of the present invention can be applied to marine engines, power generation engines, airplane engines, and motorcycle engines that transmit power in one direction.

1 is a conceptual diagram of a power transmitting device of a conventional boxer engine
Figure 2 shows a four-stroke conceptual diagram of a conventional piston engine
3 is a perspective view of a new power transmission device of a boxer engine according to the present invention.
4 is an exploded perspective view of the new power transmission device of the boxer engine of the present invention
5 to 6 show another embodiment of the new power transmission device of the boxer engine
Fig. 7 shows an embodiment of a rack-type connecting rod whose length can be adjusted
Figs. 8 to 9 show an embodiment in the case of two sets of horizontal opposing pistons
Figs. 10 to 11 show the embodiment in the case of four sets of horizontally opposed pistons
Description of the Related Art
100. Piston 200. Output shaft 300. Rack-type connecting rod
310. Body 320. Rack gear 320A. Rack Gear A
320B. Rack Gear B 320C. Rack gear C 330. Fixing means
331. Pipe 332. Cylinder 333. Fixing pin
400. One-way gear 400A. One-way gear A 400B. One-way gear B
400C. One-way gear C F. Forward B. Backward
S1. Horizontal Piston Set 1 S2. Horizontal Piston Set 2
S3. Horizontal Piston Set 3 S4. Horizontal Piston Set 4

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Claims (3)

Two rack gears 320A and 320B provided on the body 310 opposite to each other at a lower end and an upper end of the body 310, A rack-type connecting rod 300 composed of fixing means 330 for fixing both ends to opposite pistons 100 facing each other, two unidirectional gears 400A and 400B fixed to the output shaft 200 and the output shaft, &Quot; A new power transmission device of a boxer engine that converts the linear reciprocating motion of the two side pistons against each other into the rotary motion of the output shaft through the rack- In the first aspect of the present invention, three rack gears 320A, 320B and 320C are provided on the body 310 of the rack-type connecting rod 300 and three unidirectional gears 400A, 400B and 400C are provided on the output shaft 200 New power transmission system of Boxer engine The method of claim 1, wherein the length of the fastening means (330) of the rack-type connecting rod (300) is adjusted to adjust the length of the rack-

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