JPH062566A - Power transmitting device - Google Patents

Abstract

PURPOSE:To provide compactness with a reduction mechanism included, in a constitution of a power transmitting device of using a reciprocating engine formed of a plurality of cylinders. CONSTITUTION:In a power transmitting device 100, a half in one side symmetrical relating to a drive shaft 30 is constituted of a connecting member 21 rotatably supported to a piston 15, guide members 25, 26 for straight advance guiding this connecting member 21, cam followers 23, 24 rotatably supported to the connecting member 21 and the drive shaft 30 having a predetermined cam groove 31a in a cylindrical side surface of a cylindrical cam part 31. A plurality of cylinders of an engine are arranged in an axial direction of a cylinder or in a cylindrical side surface direction in parallel to this axis, and a direction of arranging the drive shaft is in the same direction to a direction of motion of the piston. Thus in the power transmitting device, a plurality of the cylinders are very compactly arranged relating to a concentrical circle direction of the drive shaft, and smooth high torque can be obtained by arranging the cylinder at an equal angle.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device for converting a linear reciprocating motion of a piston in a reciprocating engine into a rotary motion in a plane perpendicular to the direction.

[0002]

2. Description of the Related Art Conventionally, positive displacement internal combustion engines are classified into reciprocating engines and rotary engines when they are classified according to a piston motion system. Among them, the reciprocating engine is a method in which reciprocating motion of a piston is converted into rotational motion of a crankshaft via a connecting rod to obtain power, and is most widely used.

[0003]

In the above reciprocating engine, the direction of reciprocal movement of the piston and the direction of arrangement of the crankshaft that makes rotational movement are perpendicular to each other. For this reason, although the cylinder and the piston portion are relatively compact, the motion conversion mechanism portion after the connecting rod largely protrudes in the vertical direction from the reciprocating direction of the piston. Since the direction of utilizing the rotation of the crank shaft is limited, it is difficult to obtain a device having a compact structure including the crank shaft. or,
In addition, in a reciprocating engine consisting of multiple cylinders, the size of the reciprocating engine was inevitably increased when a reduction gear was included.

The present invention has been made to solve the above problems, and an object of the present invention is to reciprocate a piston in the direction in which a power take-off shaft of a reciprocating engine having a plurality of cylinders is arranged. The object of the present invention is to provide a compact power transmission device including a speed reducing mechanism and a direction parallel to the direction.

[0005]

The structure of the invention for solving the above-mentioned problems is a piston that reciprocates in the cylinders of each cylinder in a reciprocating engine having a plurality of cylinders and performs each action of intake, compression, explosion and exhaust. A connecting member pivotally supported on the connecting member, a guide member for guiding the connecting member in a straight line, a force transmitting member axially supported by the connecting member, and the force transmitting member formed on a cylindrical side surface and having a predetermined cam curve. A plurality of cylinders, each of which has a corresponding cam and which is rotationally moved by a rectilinear reciprocating motion of the force transmission member in a plane perpendicular to the direction, wherein the plurality of cylinders are in an axial direction of the cylinder in which the cams are formed. Alternatively, it is arranged in a side surface of the cylinder parallel to the axis of the cylinder.

[0006]

According to the above means, the rectilinear reciprocating motion of the connecting member pivotally supported by each piston reciprocating in the cylinders of the plurality of cylinders is transmitted to the drive shaft via the force transmitting member and the cam. Then, the drive shaft is rotated in a plane perpendicular to the rectilinear reciprocating direction of the connecting member. That is, the arrangement direction and the rotation direction of the drive shaft of the power transmission device of the present invention are perpendicular to the crankshaft of the conventional reciprocating engine when the linear reciprocating motion direction of the piston is the same. Further, a plurality of cylinders are arranged in the axial direction of the cylinder in which the cam is formed or in the side surface of the cylinder parallel to the axis of the cylinder, and are integrated with the cylinder through a force transmission member from a connecting member pivotally supported by the piston of each cylinder. Torque is transmitted to the dynamic drive shaft. At this time, it is possible to eliminate the action and reaction of the drive shaft in the axial direction by simultaneously exploding the same number of cylinders in opposite directions. Further, by disposing a plurality of cylinders at an equal angle with respect to the rotation direction of the drive shaft and causing continuous explosion, it is possible to generate smooth and high torque on the drive shaft.

[0007]

EXAMPLES The present invention will be described below based on specific examples. FIG. 1 is a central sectional view showing the configuration of a power transmission device according to the present invention. 2 is a sectional view taken along the line AA of FIG. The power transmission device 100 is configured symmetrically with respect to the central cylindrical housing 20. Therefore, the configuration of one half of the power transmission device 100 will be described below. In the engine 10, a cylinder 11 and a cylinder head 13 are sealed with a gasket or the like, and a piston 15 is arranged inside thereof. The engine 10 is fixed to the housing 20 via a plate 19. The engine 10 of the embodiment shown in FIG. 1 is a two-cycle engine, and the ignition plug and its electrical system components that are normally screwed into the cylinder head 13 are omitted. Further, the piston 15 reciprocates from the top dead center position where compression / explosion is performed shown in FIG. 1 to the bottom dead center position shown by a chain double-dashed line. Then, at the bottom dead center position, intake and exhaust are executed simultaneously. A connecting member 21 is pivotally supported on the piston 15 via a piston pin 17,
The side of the connecting member 21 opposite to the piston 15 is bifurcated, and cam followers 23 and 24, which are force transmitting members, are axially supported by the tip portions 21a and 21b, respectively.
Then, by the guide member 25 fixed to the housing 20, the tip portions 21a and 21b of the connecting member 21 are linearly guided in the same direction as the moving direction of the piston 15. The cam followers 23, 24 are drive shafts 30 rotatably supported by bearing members 28, 29 arranged in the housing 20.
It is slidably fitted in a continuous cam groove (cam) 31a, which will be described later, formed in the cylindrical cam portion 31 integral with the. Further, a gear 33 is fixedly mounted on the drive shaft 30, and a gear 35 for taking out an output is meshed with the gear 33.

Similarly to the above, the remaining half of the power transmission device 100 is also constructed. In addition, about the component similar to the above, the dash (') is attached to the same code | symbol and the description is omitted. In the power transmission device 100 configured as described above, there are two cylindrical cam portions 31, 31 ′ that are integral with each other at both ends of the drive shaft 30, and each cylindrical cam portion 31, 31 ′.
Cam grooves 31a and 31a 'are formed in the respective grooves. That is, the power transmission device 100 of this embodiment has two cam grooves 31a and 31a 'corresponding to the number of cylinders.

The two cam grooves 31a and 31a 'have cam followers 23, 24 or 23', depending on the rotation angle thereof.
The cam diagram showing the displacement of 24 'on Cartesian coordinates is shown in Fig. 3.
It consists of basic curves as shown in (a). Therefore, the cam grooves 31a, 31 'of the cylindrical cam portions 31, 31' of the drive shaft 30 are
The developed view of a'is as shown in FIG. 3 (b). That is,
The cam grooves 31a, 31a 'are formed by the cam followers 23, 24.
Alternatively, 23 'and 24' make a single chordal motion, and the displacement curve becomes a sine curve. The cam having such a shape has many advantages such as excellent pressure angle performance and easy creation. Various other cam basic curves can be adopted.

FIG. 4 is an explanatory view showing the force F _R in the rotational direction of the cylindrical cam portion when the force F is applied to the cam groove. Here, at the center position of the stroke of the piston 15, the cam groove 31
The inclination of a is 45 ° because the displacement curve is a sine curve. FIG. 4B shows the force F _R in the rotation direction of the cylindrical cam portion 31 when the force F is applied to the cam groove having the inclination angle of 45 °. When the inclination angle is θ, the force F _{R in} the rotation direction of the cylindrical cam portion is expressed by the following equation.

[Formula 1] F _R = 2F · sin θ cos θ = 2F · (1/2) sin 2θ = F · sin 2θ (0 ° ≦ θ ≦ 90 °) From the above equation, if the tilt angle is 45 °, F _R = F . As is clear from FIGS. 4 (a) and 4 (c), the tilt angle is
The force F _R above or below 45 ° is shown in Fig. 4 (b).
That is, the tilt angle becomes smaller than that when the tilt angle is 45 °.

Next, the operation will be described with respect to one side half as in the above-mentioned configuration. Fuel mixed with air is delivered from a carburetor (not shown), and the engine 1
0 repeats the intake, compression, explosion and exhaust processes.
The piston 15 is reciprocated with a predetermined stroke by the intake, compression, explosion, and exhaust processes of the engine 10. The connecting member 21 axially supported by the piston 15 via the piston pin 17 is a guide member 2 fixed to the housing 20.
5, the tip portions 21a and 21b of the connecting member 21 are linearly guided in the movement direction of the piston 15. Then, the leading end portions 21a and 21b of the connecting member 21 are guided to the guide members 26 and 2.
The cam followers 23 and 24, which are guided straight to the shaft 7, and are axially supported by the tip portions 21a and 21b, are the drive shaft 30 described above.
It reciprocates linearly along a cam groove 31a formed in the cylindrical cam portion 31. As shown in FIG. 3 (b), the cam groove 31 a is formed so as to have the same stroke as the piston 15 and 360 ° for two cycles. Therefore, when the piston 15 reciprocates two times, the drive shaft 30 makes one revolution. The rotation of the drive shaft 30 causes the gear 3
The gear 35 meshed with the gear 3 is rotated, and power is transmitted to the outside by utilizing the shaft of the gear 35 or a gear connection (not shown).

The operation of the remaining one half of the power transmission device 100 of this embodiment can be explained in the same manner as above. In the apparatus of this embodiment, the engine 10,
10 'is configured to explode at the same timing, so that double torque is applied to the drive shaft 30. In the conventional reciprocating engine, the reciprocating motion of the piston is converted into the rotary motion of the crankshaft via the connecting rod. As described above, in the power transmission device 100 of this embodiment, the reciprocating motion of the pistons 15 and 15 'of the engines 10 and 10' is converted into the rotational motion of the drive shaft 30 via the connecting members 21 and 21 '. . The major difference between them is that the conventional crankshaft is supported and rotated in a plane perpendicular to the movement direction of the piston, but the drive shaft 30 is supported in a plane parallel to the movement direction of the piston (a straight direction in FIG. 1). It is to be rotated. Thus, except for the fuel supply system and the ignition system, the power transmission device 100
Can be made extremely compact in the direction concentric with the cylinders 11, 11 'of the engines 10, 10'. Further, at this time, by simultaneously exploding the cylinders in mutually opposite directions, it is possible to eliminate the action / reaction of the drive shaft 30 in the axial direction and eliminate unnecessary vibration. The reduction ratio between the engine 10, 10 'and the drive shaft 30 is determined by the drive shaft 3
The cam groove 31 corresponding to the number of reciprocations of the pistons 15 and 15 'within one rotation (360 °) of the cylindrical cam portions 31 and 31' of 0.
a, 31a 'is formed. That is, when the number of reciprocations of the pistons 15 and 15 'is n times, the gear ratio is equal to n.

Here, the case where the cam groove 31a of the cylindrical cam portion 31 on one side of the drive shaft 30 is set to one cycle will be considered. The radius of the cylindrical cam portion 31 is r, its rotation angle is θ, the moving distance in the circumferential direction is x, its vertical displacement is y, and the total stroke of the piston 15 is S _t . Then, at the center position of the stroke of the piston 15, the cam groove 31
the inclination a is assumed to be 45 °, the following relationship exists between the full stroke S _t of the radius r and the piston 15 of the cylindrical cam portion 31 of the drive shaft 30.

[Mathematical formula-see original document] y = (S _t / 2) ・ sin θ x = r ・ θ ∴ y = (S _t / 2) ・ sin (x / r) dy / dx = (S _t / 2) ・ (1 / r ) · Cos (x / r) In the above equation, the center position of the stroke of the piston 15, that is,
If x = 0,

Dy / dx = (S _t / 2r) When x = 0, the inclination of the cam groove 31a is 45 °, that is, dy / dx = 1.

[Equation 4] ∴ r = S _t / 2 Therefore, under the condition that the inclination of the cam groove 31a is 45 ° at the center position of the stroke of the piston 15, the radius r of the cylindrical cam portion 31 of the drive shaft 30 is equal to the total stroke of the piston 15. It is (1/2) times S _t .

Next, consideration will be given to a case where the cam groove 31a of the cylindrical cam portion 31 on one side of the drive shaft 30 has a length of n cycles. When the rotation angle of the drive shaft 30 is a real angle Θ, the operation angle θ of the cam groove 31a corresponding to the real angle Θ is represented as follows.

[Mathematical formula-see original document] In the same manner as described above, the radius of the cylindrical cam portion 31 is r, the moving distance in the circumferential direction is x, the amount of vertical displacement thereof is y, and the total stroke of the piston 15 is S. _{Let t} . When the inclination of the cam groove 31a is 45 ° at the center position of the stroke movement of the piston 15, the cylindrical cam portion 31 of the drive shaft 30 is assumed.
There is the following relationship between the radius r of the stroke and the total stroke S _t of the piston 15.

[6] _{y = (S t / 2)} · sinθ x = r · Θ = (r / n) · θ ∴ y = (S t / 2) · sin (nx / r) dy / dx = (S t / 2) · (n / r) · cos (nx / r) Similarly, at the center position of the stroke of the piston 15 described above, that is, at x = 0, the inclination of the cam groove 31a is 45 °, that is, dy / dx = 1.

[Formula 7] ∴ r = nS _t / 2 Therefore, under the condition that the inclination of the cam groove 31a is 45 ° at the center position of the stroke of the piston 15, the radius r of the cylindrical cam portion 31 of the drive shaft 30 is the entire stroke of the piston 15. It is (n / 2) times S _t .

The power transmission device of the present invention is a primary reduction gear having a reduction ratio of 1 / n times by forming a cam groove having n (n is a positive integer) cycles in the cylindrical cam portion of the drive shaft. It can be equivalent to the built-in one. However, in the above-described embodiment, the two cam followers 23, 24 or the cam followers 23 ', 24' are engaged with the cam grooves 31a, 31a 'at the same stroke position.
31a 'is for 2n cycles, and a reduction ratio of 1 / 2n times is achieved. Further, in the power transmission device of the present invention, the cam engaged with the force transmission member may be a cam having a convex wall formed on the cylindrical side surface, other than the cam groove as in the above-described embodiment. Further, as the cam formed on the cylindrical side surface of the power transmission device of the present invention, in addition to the above-mentioned cylindrical outer peripheral cam, a cylindrical inner peripheral cam can be applied. In this case, the structure is such that the force transmitting member of the connecting member pivotally supported by the piston is engaged with the cylindrical inner peripheral cam inside the cylinder.

Next, the structure of the second embodiment of the power transmission device according to the present invention will be described with reference to FIGS. Figure 5
6 is a central sectional view showing the configuration of the power transmission device 200, FIG.
FIG. 6 is a schematic diagram showing the cylinder arrangement of FIG. 5. The same components as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be omitted. Power transmission device 20 of the present embodiment
0 indicates that the engine has 2 cycles 6 as shown in FIG.
It is composed of cylinders, and two cylinders are shown in FIG. still,
Regarding the engine, mainly only the pistons inserted into the cylinders of the respective cylinders are shown. Of the above six cylinders, the following description will be made with reference to the two cylinders shown in FIG. Pistons 151 and 154 are arranged concentrically with the cylindrical side surface of the cylindrical cam portion 31 of the drive shaft 30. The pistons 151 and 154 have connecting members 211 and 214.
Is pivotally supported, and the connecting members 211, 214 are linearly guided in the movement direction of the pistons 151, 154 by guide members 251, 254 fixed to the housing 20. Then, the cam followers 231 and 234 pivotally supported by the respective tip end portions of the connecting members 211 and 214 make a rectilinear reciprocating motion along the cam grooves 31 a formed in the cylindrical cam portion 31 of the drive shaft 30 described above. The cam groove 31a is similar to that shown in FIG. 3 (b), and when the pistons 151 and 154 reciprocate twice, the cylindrical cam portion 31 makes one revolution movement. Then, the rotation of the cylindrical cam portion 31 becomes the rotation of the drive shaft 30 at both ends thereof in the direction of the arrow, and the power is transmitted to the outside.

The power transmission device 200 configured as described above.
In this case, since the explosion of each cylinder of the engine in one rotation of the drive shaft is twice at every uniform angle (180 ° C.) for a total of 12 times, it is possible to obtain a smooth and high torque. or,
In the power transmission device 200 of this embodiment, the cylinders of the engine are arranged in the concentric direction of the drive shaft 30, so that the power transmission device is compact. Further, the drive shaft 30 is provided at both ends with respect to the cylindrical cam portion 31, and output can be taken out from any of them.

Next, the configuration of the third embodiment of the power transmission device according to the present invention will be described with reference to FIG. FIG. 7 is a central cross-sectional view showing the configuration of the power transmission device 300. The same components as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be omitted. In the power transmission device 300 of this embodiment, the engine is composed of 6 cylinders each having two cycles, as shown in FIG. 6, and two cylinders are shown in FIG. Regarding the engine, mainly only the pistons inserted into the cylinders of the respective cylinders are shown. Pistons 151 and 154 are arranged concentrically with the cylindrical side surface of the cylindrical cam portion 31 of the drive shaft 30. The difference from the embodiment of FIG. 5 is that the cylinders are alternately arranged on the opposite side of the cylindrical cam portion 31. As described above, the power transmission device of the present invention can be arranged with a plurality of cylinders, and it can be said that the degree of freedom in design is extremely large.

Next, the structure of the fourth embodiment of the power transmission device according to the present invention will be described with reference to FIGS. 8 and 9. Figure 8
9 is a central sectional view showing the configuration of the power transmission device 400, FIG.
FIG. 9 is a schematic diagram showing the cylinder arrangement of FIG. 8. The same components as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be omitted. Power transmission device 40 of the present embodiment
0 indicates that the engine has 2 cycles 1 as shown in FIG.
Six cylinders are arranged around the cylindrical cam portion 31 so as to face each other by two cylinders in a direction perpendicular to the paper surface. Regarding the engine, mainly only the pistons inserted into the cylinders of the respective cylinders are shown. Pistons 151, 151 ', 152, 152', 153, 15
3 ', 154, 154', 155, 155 'and 15
6, 156 'are connecting members 211, 211', 2
12, 212 ', 213, 213', 214, 21
It is pivotally supported by 4 ', 215, 215' and 216, 216 '. That is, each piston is configured to be movable by one connecting member.

Of the 12 cylinders described above, the four cylinders shown in FIG. 8 will be described below. Pistons 151 and 151 ′ and pistons 154 and 154 ′ are arranged on the cylindrical side surface of the cylindrical cam portion 31 of the drive shaft 30. The connecting members 211 and 214 are arranged symmetrically with respect to the cylindrical cam portion 31 of the drive shaft 30 so as to correspond to the cam grooves 31 a of the cylindrical cam portion 31. Further, the cylindrical cam portion 31
Corresponding to the cam grooves 31a 'of the respective connecting members 21
1'and 214 'are arranged symmetrically with respect to the cylindrical cam portion 31 of the drive shaft 30. In addition, the cam groove 3 of the cylindrical cam portion 31
The cam curves of 1a and 31a 'are formed in the same manner as in FIG. 3 (b), and the cam groove 31a and the cam groove 31a are arranged on the cylindrical cam portion 31 so that the cylinders facing each other are at the top dead center position or the bottom dead center position at the same time. 31a 'is formed symmetrically. Then, the cam grooves 31a, 31a 'of the cylindrical cam portion 31 are constantly forced to move in the vicinity of the top dead center and the bottom dead center by the explosion of the engine to cause the connecting members 211, 214, 211', 214 'to move linearly in a reciprocating direction. Cam followers 231, 234,
It will be received via 231 'and 234'. The drive shaft 30 integrated with the cylindrical cam portion 31 is rotated in the arrow direction.

The power transmission device 400 configured as described above
In this case, the number of explosions of each cylinder of the engine in one rotation of the drive shaft 30 is 24 times, which is two times for each uniform angle (180 °), so that extremely smooth and high torque can be obtained. Further, in the power transmission device 200 of the present embodiment, each cylinder of the engine is arranged in the concentric direction of the drive shaft 30, so that the power transmission device is compact as a whole. Further, since the opposed cylinders always explode at the same time, it is possible to eliminate the action / reaction in the direction of the drive shaft and eliminate unnecessary vibration. Further, the drive shaft 30 is provided at both ends with respect to the cylindrical cam portion 31, and output can be taken out from any of them.

Next, the configuration of the fifth embodiment of the power transmission device according to the present invention will be described with reference to FIGS. 10 and 11.
10 is a central cross-sectional view showing the configuration of the power transmission device 500, and FIG. 11 is a schematic view showing the cylinder arrangement of FIG.
Further, components having the same configurations as those in the above-described embodiment are designated by the same reference numerals and the description thereof will be omitted. As shown in FIG. 11, the power transmission device 500 of the present embodiment has an engine composed of 12 cylinders each having two cycles, and two cylinders are opposed to each other in the vertical direction with respect to the paper surface, and six cylinders are provided around the cylindrical cam portion 31. It is arranged. Regarding the engine, only the pistons inserted into the cylinders of the respective cylinders are mainly shown, as in the above-described embodiment. Piston 151,15
1 ', 152, 152', 153, 153 ', 154,
154 ', 155, 155' and 156, 156 'are respectively one connecting member 211, 212, 213, 21.
It is pivotally supported at 4, 215 and 216. That is, each pair of pistons is configured to be integrally movable by one connecting member.

Of the above-mentioned 12 cylinders, 4 shown in FIG.
It will be described below with reference to a cylinder. A pair of pistons 151, 1 are attached to the cylindrical side surface of the cylindrical cam portion 31 of the drive shaft 30.
51 'and pistons 154, 154' are arranged. The connecting members 211 and 214 are arranged symmetrically with respect to the cylindrical cam portion 31 of the drive shaft 30 so as to correspond to the cam grooves 31 a of the cylindrical cam portion 31. The cam curve of the cam groove 31a of the cylindrical cam portion 31 is formed in the same manner as in FIG. 3 (b). Furthermore, when the pistons 151 and 154 are at the top dead center, the pistons 151 ′ and 154 ′ are at the bottom dead center, and when the pistons 151 and 154 are at the bottom dead center, the pistons 151 ′ and 154 ′ are at the top dead center. To be configured. Then, the cam groove 31a of the cylindrical cam portion 31 is constantly in the vicinity of the top dead center and the bottom dead center thereof due to the explosion of the engine and thus the connecting member 2
The cam followers 23 and 24 receive the force of the reciprocating motion of the straight movements of the arrows 11 and 212 in the arrow directions. And
The drive shaft 30 integrated with the cylindrical cam portion 31 is rotated in the arrow direction.

The power transmission device 200 configured as described above
In this case, the number of explosions of each cylinder of the engine in one rotation of the drive shaft 30 is 24 times, which is two times for each uniform angle (180 °), so that extremely smooth and high torque can be obtained. Further, in the power transmission device 200 of the present embodiment, each cylinder of the engine is arranged in the concentric direction of the drive shaft 30, so that the power transmission device is compact as a whole. Further, the drive shaft 30 is provided at both ends with respect to the cylindrical cam portion 31, and output can be taken out from any of them. In all of the above-described embodiments, the description has been made assuming the 2-cycle engine which does not require the intake and exhaust valves and has a simple structure, but there is no problem even if the 4-cycle engine is used. In this case, both output ends of the drive shaft can be used for the above-mentioned valve control, and compared with the valve control in the conventional engine, since the output shaft exists near the intake and exhaust valves, there is a timing error. Very few precise controls are possible.

[0025]

The present invention is configured as described above, and a plurality of cylinders of the engine can be arranged in the axial direction of the cylinder in which the cam is formed or in the cylindrical side surface direction parallel to the axis.
The disposing direction of the drive shaft is the same as the moving direction of the piston. Therefore, the power transmission device of the present invention can have an extremely compact configuration in the concentric direction of the drive shaft even if the engine has a plurality of cylinders. Further, in the power transmission device of the present invention, since the rotational speed of the drive shaft for one reciprocating motion of the piston is determined by the cam curve shape of the cam per revolution on the cylindrical side surface of the drive shaft, it is equivalent to the one in which the primary reduction device is incorporated. However, the configuration can be made extremely simple. Further, the power transmission device of the present invention has a large degree of freedom in the arrangement of the cylinders, the engine can be exploded every time the drive shaft is rotated at an equal angle, and smooth and high torque rotation is possible. Furthermore, since it is easy to use both ends of the drive shaft as output ends, there is an effect that various configurations and applications are possible.

[Brief description of drawings]

FIG. 1 is a sectional view showing a configuration of a power transmission device according to a specific embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

FIG. 3 is an explanatory view showing a cam shape of a cylindrical cam portion of the drive shaft according to the embodiment.

FIG. 4 is an explanatory view showing generation of force with respect to cam inclination of the cylindrical cam portion of the drive shaft according to the embodiment.

FIG. 5 is a sectional view showing the configuration of a second embodiment of the power transmission device according to the present invention.

FIG. 6 is a schematic diagram showing a cylinder arrangement in the engine of FIG.

FIG. 7 is a sectional view showing a configuration of a third embodiment of the power transmission device according to the present invention.

FIG. 8 is a sectional view showing a configuration of a fourth embodiment of the power transmission device according to the present invention.

9 is a schematic diagram showing a cylinder arrangement in the engine of FIG.

FIG. 10 is a sectional view showing a configuration of a fifth embodiment of the power transmission device according to the present invention.

11 is a schematic diagram showing a cylinder arrangement in the engine of FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 ... Engine 11 ... Cylinder 15 ... Piston 20 ... Housing 21 ... Connecting member 23, 24 ... Cam follower (force transmission member) 25, 26 ... Guide member 30 ... Drive shaft 31 ... Cylindrical cam part 31a ... Cam groove (cam) 100 ... Power transmission device

Claims (1)

[Claims] 1. A reciprocating engine comprising a plurality of cylinders, which reciprocates in and out of the cylinders of each cylinder to suck, compress, and explode.
A connecting member that is axially supported by a piston that performs each function of exhaust, a guide member that linearly guides the connecting member, a force transmitting member that is axially supported by the connecting member, and a predetermined cam curve formed on a cylindrical side surface. And a drive shaft that is rotated by a rectilinear reciprocating motion of the force transmitting member in a plane perpendicular to the direction, the cam is formed in the plurality of cylinders. The power transmission device is arranged in an axial direction of the formed cylinder or in a cylindrical side surface direction parallel to the axis of the cylinder.