WO2011016084A1

WO2011016084A1 - Two-cylinder engine

Info

Publication number: WO2011016084A1
Application number: PCT/JP2009/003727
Authority: WO
Inventors: 清水茂治郎; 竹村利彦
Original assignee: Shimizu Shigejiro; Takemura Toshihiko
Priority date: 2009-08-04
Filing date: 2009-08-04
Publication date: 2011-02-10
Also published as: JPWO2011016084A1; JP5328918B2; DE112009005123T5

Abstract

A piston crank mechanism (20) of a horizontally opposed two-cylinder engine (1) is provided with first to fourth rotating circular discs (21-24) coaxially arranged along a rotation center axis (L2) at predetermined intervals. The rotating circular discs (21-24) are supported by a circular inner peripheral surface (2a) of a crankcase (2) through deep groove ball bearings (31-34). Piston rods (9A, 9B) of a first cylinder (5) are connected to a first pin (41) connected between the first and second rotating circular discs (21, 22), and piston rods (10A, 10B) of a second cylinder (6) are connected to second and third pins (42, 43) connected respectively between the first and third rotating circular disc (21, 23) and between the second and fourth rotating circular discs (22, 24). Because large torsional stress and bending stress do not occur in the rotating circular discs (21-24), the weight of the horizontally opposed two-cylinder engine is less than the weight of an engine using a highly rigid, heavy crankshaft.

Description

2-cylinder engine

The present invention relates to a two-cylinder engine in which a piston crank mechanism that converts a reciprocating motion of a piston into a rotational motion and outputs the same is output. In particular, the present invention relates to a two-cylinder engine equipped with a lightweight piston crank mechanism suitable for use in a horizontally opposed engine.

Motor paragliders that fly using the propeller thrust are equipped with an engine in the harness (seat) as a propeller drive source. As an engine mounted on a motor paraglider, a small, light and low vibration engine is required so as not to be a burden on the operator during takeoff and landing.

As a low vibration engine, a boxer (horizontally opposed type) engine described in Patent Document 1 is known. In a boxer engine, vibrations are reduced by reciprocating a pair of horizontally opposed cylinders with a phase difference of 180 degrees so that the pistons cancel each other's vibrations. If the boxer engine is installed in the motor paraglider, the burden on the operator due to vibration can be reduced.

Engines such as boxer engines are equipped with a crankshaft for converting the linear motion of the piston of each cylinder into rotational motion. As described in Patent Document 1, the crankshaft of the engine is bent in the radial direction from the rotation center line and connected to the piston rod of each cylinder, and the crankarm portion is mutually connected. For this purpose, the connecting shaft portions extending along the rotation center line are alternately formed, and the connecting shaft portions located at both ends are supported in a rotatable state by the crankcase via journal bearings. Has been.

JP-T-2002-525481

In the crankshaft of the engine, a large force is periodically applied from each cylinder in each part in the axial direction. Therefore, the crankshaft is made of a rigid and heavy material having high rigidity, and is generally a component that occupies a large weight among engine components.

It is desirable that the engine mounted on the device used on the human body, such as a motor paraglider, is small and light and has low vibration as described above. A boxer engine may be used to reduce the vibration, but it is desired to reduce the weight of the crankshaft that occupies a large weight in order to reduce the weight.

In view of the above, an object of the present invention is to propose a two-cylinder engine that is improved in weight by reducing the piston crank mechanism.

In order to solve the above problems, the two-cylinder engine of the present invention is
A first rotating disk and a second rotating disk arranged coaxially with a predetermined interval in the direction of a preset rotation center line;
The first rotating disk and the second rotating disk are supported so as to be rotatable around the rotation center line via the bearing mechanism mounted on the circular outer peripheral surfaces of the first rotating disk and the second rotating disk. A crankcase,
A first pin which is fixed between the first rotating disk and the second rotating disk so as to extend over a portion off the rotation center line;
In the first outer circular side surface of the first rotating disk opposite to the second rotating disk, a portion deviated from the rotation center line, and separated from the first pin by a predetermined angle around the rotation center line. A first outer pin fixed to the site;
In the second outer circular side surface of the second rotating disk opposite to the first rotating disk, a portion deviated from the rotation center line, and separated from the first pin by a predetermined angle around the rotation center line. A second outer pin fixed to the part,
A first piston rod of a first cylinder that is attached to an inner end of the first pin so as to be rotatable around a connecting axis parallel to the rotation center line and extends in a direction perpendicular to the rotation center line. When,
A first outer piston of a second cylinder that is attached to an inner end of the first outer pin so as to be rotatable about a connecting axis parallel to the rotation center line and extends in a direction perpendicular to the rotation center line. The rod,
An inner end is attached to the second outer pin so as to be rotatable about a connecting axis parallel to the rotation center line, and is spaced from the first outer piston rod by a predetermined distance to the rotation center line. And a second outer piston rod of the second cylinder extending in a direction perpendicular to the second cylinder.

According to the present invention, the first piston rod of the first cylinder is configured to move between the pair of first outer piston rod and second outer piston rod of the second cylinder. Two cylinders can be arranged on the same plane perpendicular to the rotation center line.

When the two-cylinder engine of the present invention is of a horizontally opposed type, the first cylinder and the second cylinder are arranged opposite to each other on a horizontal line orthogonal to the rotation center line, and the first pin and the second pin May be arranged at an angular interval of 180 degrees around the rotation center line.

In the horizontally opposed two-cylinder engine having this configuration,
The rotating disk includes a third rotating disk that is coaxially arranged at a predetermined interval with respect to the first rotating disk on the first outer circular side surface of the first rotating disk, and the second rotating disk. 2 on the side of the outer circular side surface, and a fourth rotating disk arranged coaxially with a constant interval with respect to the second rotating disk,
The first to fourth rotating disks are supported by the crankcase via the bearing mechanism so as to be rotatable around the rotation center line,
The first outer pin is spanned between the first rotating disk and the third rotating disk,
The second outer pin is preferably bridged between the second rotating disk and the fourth rotating disk.

In this case, it is desirable to employ a rolling bearing such as a deep groove ball bearing as the bearing mechanism, and to install a rolling bearing between the circular outer peripheral surface of the first to fourth rotating disks and the crankcase.

Further, in order to prevent a rotational phase shift from occurring between the third and fourth rotating disks on both sides, a synchronous rotating mechanism that synchronously rotates the third rotating disk and the fourth rotating disk is provided. It is desirable.

Here, the synchronous rotation mechanism is
A first drive-side gear attached to the third rotating disk so as to rotate integrally in a coaxial state;
A second drive-side gear attached to the fourth rotating disk so as to rotate integrally in a coaxial state;
An output rotation axis arranged parallel to the rotation center line;
A first driven gear that is coaxially mounted so as to rotate integrally with the output rotating shaft and meshes with the first driving gear;
It is possible to use one provided with a second driven gear that is coaxially attached to the output rotating shaft and meshed with the second driving gear.

In this case, the output rotation shaft is preferably a cam shaft for supplying fuel to the first cylinder and the second cylinder with a phase difference of 180 degrees. If the output rotation shaft is also used as a cam shaft for intake / exhaust control of the first cylinder and the second cylinder, the number of parts can be reduced.

In the two-cylinder engine of the present invention, the first pin is fitted in a playable state with respect to pin holes formed in the first rotating disc and the second rotating disc,
The first outer pin is fitted in a playable state with respect to a pin hole formed in the third rotating disk,
The second outer pin may be fitted in a playable state with respect to a pin hole formed in the fourth rotating disk.

In other words, in the piston crank mechanism of the two-cylinder engine of the present invention, the first to fourth rotating disks for converting the linear reciprocating motion of the piston rod into the rotational motion can be freely rotated by the crankcase via the bearing mechanism. It is supported. Therefore, the first to fourth rotating disks need only be connected so as to be able to rotate synchronously, and there is no need to have a structure that is firmly connected and fixed as in the conventional crankshaft.

Next, to reduce the number of parts,
The first piston rod includes a first inner piston rod and a second inner piston rod having the same shape extending in parallel.
The first and second outer piston rods and the first and second inner piston rods are common parts,
The first to fourth rotating disks are preferably common parts.

The piston crank mechanism of the two-cylinder engine of the present invention includes a plurality of rotating disks supported in a rotatable state by a crankcase via a bearing mechanism. Therefore, unlike the conventional mechanism in which a single crankshaft receives a force acting from the piston rod of each cylinder at an intermediate position in the axial direction, the in-plane direction from the piston rod of each cylinder to the rotating disk is different. A force acts in the direction, and this force is transmitted to the crankcase via a bearing mechanism mounted on the circular outer peripheral surface of the rotating disk. Therefore, compared to the crankshaft, the stress concentration can be alleviated, and the generation of forces such as torsional force and bending force that can deform the parts is suppressed or alleviated. Therefore, it is not necessary to form a rotating disk or the like from a highly rigid and heavy material, and the weight of the engine can be reduced.

It is a schematic perspective view of the principal part of the 2-cylinder engine to which this invention is applied. FIG. 2 is a schematic longitudinal sectional view of a two-cylinder engine showing a portion cut along line AA in FIG. 1. FIG. 2 is a schematic cross-sectional view of a two-cylinder engine showing a portion cut along line BB in FIG. 1. It is explanatory drawing which shows the piston crank mechanism of the 2-cylinder engine of FIG. It is a fragmentary sectional view which shows the bearing mechanism which supports the 1st, 2nd rotation disc, and the bearing mechanism of the connection part of a 1st piston rod and a pin. It is a fragmentary sectional view which shows the bearing mechanism which is supporting the 3rd rotation disk, and the bearing mechanism of the connection part of a 2nd piston rod and a pin. It is explanatory drawing which shows an example of the multicylinder engine to which this invention is applied. It is explanatory drawing which shows an example of the multicylinder engine to which this invention is applied. It is explanatory drawing which shows an example of the piston crank mechanism to which this invention is applied. It is explanatory drawing which shows an example of the piston crank mechanism to which this invention is applied.

Hereinafter, an embodiment of a two-cylinder engine to which the present invention is applied will be described with reference to the drawings.

(overall structure)
FIG. 1 is a schematic perspective view of a horizontally opposed two-cylinder engine to which the present invention is applied. The two-cylinder engine 1 includes a rectangular cylindrical crankcase 2 that is flat in the front-rear direction, and a pair of

cylinder blocks

3 and 4 that extend horizontally from the left and right side surfaces of the crankcase 2 horizontally.

FIG. 2 is a vertical cross-sectional view of the two-cylinder engine 1, which is a cross section taken along line AA in FIG. FIG. 3 is a cross-sectional view of the two-cylinder engine 1, which is a cross-sectional view taken along line BB in FIG. Referring to these figures, the first cylinder 5 and the second cylinder 6 are formed in the left and

right cylinder blocks

3 and 4. These first and

second cylinders

5 and 6 are arranged opposite to each other on a horizontal line L1 extending in the left-right direction of the engine, and in each of them, a linear reciprocating motion is performed in the reverse direction while maintaining a phase difference of 180 degrees. A first piston 7 and a second piston 8 are arranged.

The first piston rod 9 of the first piston 7 and the second piston rod 10 of the second piston 8 extend toward the piston crank mechanism 20 incorporated in the crankcase 2, respectively. It is connected. The piston crank mechanism 20 converts the linear reciprocating motion of the first piston 7 and the second piston 8 into a rotational motion about a rotational center line L2 extending horizontally in the longitudinal direction of the engine.

The engine output converted into the rotational motion by the piston crank mechanism 20 is taken out from the output rotating shaft 70 of the synchronous rotating mechanism 60 attached to the lower portion of the crankcase 2 and transmitted to the driven side (not shown). Is done.

(Piston crank mechanism)
FIG. 4 is an explanatory view showing a part of the piston crank mechanism 20 taken out. 2, 3, and 4, the piston crank mechanism 20 is coaxially arranged at a predetermined interval in the direction of the rotation center line L 2 that extends horizontally in the front-rear direction (front-rear direction) 4. The first to fourth rotating disks 21 to 24 are provided. The first rotating disc 21 and the second rotating disc 22 are arranged adjacent to each other at regular intervals, and the third rotating disc 23 is arranged adjacent to the front side of the front first rotating disc 21 at regular intervals. The rotating disk 24 is disposed adjacent to the rear side of the second rotating disk 22 on the rear side at a constant interval.

Each of the first to fourth rotating disks 21 to 24 is supported by the crankcase 2 so as to be rotatable around the rotation center line L2 via a bearing mechanism. In this example, a first deep groove ball bearing 31 is mounted between the circular outer peripheral surface 21a of the first rotating disk 21 and the inner peripheral surface of the crankcase 2 to support the first rotating disk 21 in a rotatable state. Similarly, the other second to fourth rotating disks 22 to 24 are also respectively rotatable by second to fourth deep groove ball bearings 32 to 34 mounted between the inner peripheral surface of the crankcase 2. It is supported.

Here, the first piston rod 9 of this example includes a first inner piston rod 9A and a second inner piston rod 9B which are common parts. These first and second

inner piston rods

9A and 9B are arranged in parallel in the front-rear direction, and their rear ends (inner ends on the clan case side) are respectively connected to the inner first through the first pins 41. The first rotating disk 21 and the second rotating disk 22 are connected. The first pin 41 is a pin having a circular cross section and having a predetermined length. The first and second pins 41 are parallel to the rotation center line L2 at a position away from the rotation center line L2 by a predetermined distance radially outward. It spans between the

rotating disks

21 and 22. The rear ends of the first and second

inner piston rods

9A, 9B are coupled to the first pin 41 in a rotatable state via deep

groove ball bearings

51, 52.

Similarly, the second piston rod 10 is also composed of a first outer piston rod 10A and a second outer piston rod 10B which are common parts, and the common parts with the first and second

inner piston rods

9A and 9B are also used. Has been. A rear end portion of the first outer piston rod 10 A on the front side is connected to the first and third

rotary disks

21 and 23 on the front side via a first outer pin 42. The first outer pin 42 is bridged between the first and third

rotating disks

21 and 23 in a state parallel to the rotation center line L2 at a position rotated 180 degrees with respect to the first pin 41. A rear end portion of the first outer piston rod 10 A is connected to the first outer pin 42 through a deep groove ball bearing 53 so as to be rotatable.

The rear end portion of the first outer piston rod 10B on the right side is connected to the second and fourth

rotary disks

22 and 24 on the rear side via the second outer pin 43. Parts common to the first outer pin 42 are used for the second outer pin 43, and at the same position as the first outer pin 42, the second and fourth

rotating disks

22 and 24 are parallel to the rotation center line L2. It is bridged between. A rear end portion of the second outer piston rod 10 B is connected to the second outer pin 43 through a deep groove ball bearing 54 so as to be rotatable.

Here, the first pin 41 is fitted into the pin holes formed in the first rotating disk 21 and the second rotating disk 22 in a state where there is play, and the first outer pin 42 rotates in the first and third rotations. The

discs

21 and 23 are each fitted with play in the pin holes formed therein. Similarly, the second outer pin 43 is fitted into the pin holes formed in the second and fourth

rotating disks

22 and 24 with play. That is, these pins 41 to 43 are not firmly fixed to the first to fourth rotating disks 21 to 24, and are inserted into the pin holes formed in these rotating disks in a floating state.

Two first and second

inner piston rods

9A and 9B constituting the first piston rod 9, and two first and second outer piston rods 10A constituting the

second piston rod

10, 10B and the first to fourth rotating disks 21 to 24 have the same thickness dimension in the direction of the rotation center line L2. Further, they are arranged within the radial dimensions of the first cylinder 5 and the second cylinder 6 in the direction of the rotation center line L2.

Next, FIG. 5A is a partial cross-sectional view showing a mounting portion of the first and second deep

groove ball bearings

31 and 32 and the deep

groove ball bearings

51 and 52, and FIG. 5B is a view of the third deep groove ball bearing 33 and the deep groove ball bearing 53. It is a fragmentary sectional view which shows a mounting part.

First, the bearing mechanism of the first to fourth rotating disks 21 to 24 will be described with reference to these drawings. The first and second deep

groove ball bearings

31 and 32 include annular

outer rings

31a and 32a attached to the circular inner peripheral surface 2a of the crankcase 2 on both sides of the first and second

inner piston rods

9A and 9B. The intervals between these outer rings (intervals in the direction of the rotation center line L2) are held by a plurality of annular collars 35 having different widths mounted on the circular inner peripheral surface 2a. Inner ring raceway surfaces 31b and 32b formed integrally with the circular outer

peripheral surfaces

21a and 22a of the first and second

rotary disks

21 and 22 are arranged concentrically inside the

outer rings

31a and 32a. Between these

outer rings

31a, 32a and inner ring raceway surfaces 31b, 32b,

balls

31d, 32d are arranged in a rollable manner along the circumferential direction at regular intervals by

ball retainers

31c, 32c.

As shown in FIG. 5B, the third deep groove ball bearing 33 has the same structure, and the fourth deep groove ball bearing 34 (not shown) has the same structure as the third deep groove ball bearing 33.

Next, the deep

groove ball bearings

51, 52 arranged between the first pin 41 and the first piston rod 9 (9 A, 9 B) have inner ring raceway surfaces 51 a, 52 a on the circular outer peripheral surface of the first pin 41. The outer ring raceway surfaces 51b and 52b are integrally formed on the circular inner peripheral surface of the pin hole of the first piston rod 9 (9A and 9B). That is, the first pin 41 is an inner ring integrated type pin, and the first piston rod 9 is an outer ring integrated type rod.

As shown in FIG. 5B, the deep groove ball bearing 53 disposed between the second pin 42 and the first outer piston rod 10A of the second pstron rod 10 has a similar structure, and a third pin (not shown) The deep groove ball bearing 54 disposed between the second piston rod 10 B and the second outer piston rod 10 B of the second piston rod 10 has the same structure as the deep groove ball bearing 53.

(Synchronous rotation mechanism)
Next, the rotations of the first to fourth rotating disks 21 to 24 are taken out from the output rotating shaft 70 to the driven side via the synchronous rotating mechanism 60 as described above.

The synchronous rotation mechanism 60 will be described with reference to FIGS. A first gear shaft 61a is coaxially attached to the front side surface of the third rotating disk 23 located on the most front side, and the first gear shaft 61a projects forward from the front end of the crankcase 2, A first driving gear 61 is fixed to the protruding shaft end portion in a coaxial state.

On the other hand, the second gear shaft 62a is coaxially attached to the rear side surface of the fourth rotating disk 24 located at the rearmost side, and this gear shaft 62a is rearward from the rear end of the crankcase 2. The second drive side gear 62 is fixed to the projecting shaft end portion coaxially. A rotor shaft 63 is connected and fixed coaxially to the rear side of the second drive side gear 62, and a shaft end of the rotor shaft 63 is connected to a generator for supplying electric power to a spark plug or the like. The outer rotor 64 is fixed coaxially.

An output rotation shaft 70 having a rotation center line L3 extending in the front-rear direction in parallel with the rotation center line L2 as a center axis is disposed below the first to fourth rotation disks 21 to 24. A first driven gear 65 is fixed coaxially to the front portion of the output rotating shaft 70, and a second driven gear 66 is fixed coaxially to the rear portion. The first and second driven gears 65 and 66 mesh with the first and second drive gears 61 and 62, respectively.

A shaft end portion 70a on the front side of the output rotating shaft 70 passes through a front cover case 68 attached to the front end portion of the crankcase 2 and protrudes forward, and is supported by the front cover case 68 in a rotatable state. ing. The shaft end portion 70b on the rear side of the output rotation shaft 70 is also supported in a rotatable state by the inner side surface portion of the rear cover case 69 attached to the rear end portion of the crankcase 2. The front cover case 68 covers the first driving gear 61 and the second driven gear 65, and the rear cover case 69 covers the second driving gear 62 and the second driven gear 66. .

(Function and effect)
In the piston crank mechanism 20 of the two-cylinder engine 1, the force from the

piston rods

9 and 10 of the

cylinders

5 and 6 acts on the rotary disks 21 to 24 in the in-plane direction. Therefore, unlike the conventional case where the force from the piston rod acts in the direction perpendicular to the axis at the midway position of the crankshaft on which the shaft end portions on both sides are supported, each rotating disk 21 to 24 has a large size. There is no stress concentration and no large bending stress or torsional stress is generated. Therefore, it is not necessary to form the rotary disks 21 to 24 from a material having high rigidity and weight like a conventional crankshaft.

Further, the first to third pins 41 to 43 for connecting the

piston rods

9 and 10 to the rotary disks 21 to 24 do not need to be used for firmly connecting and fixing the rotary disks 21 to 24 to each other. Therefore, they do not need to be formed of a material having high rigidity and weight as in the prior art, and the connection structure between the pins 41 to 43 and the rotating disks 21 to 24 is a light connection that is simply inserted and fixed. The structure may be sufficient.

Furthermore, since the synchronous rotation mechanism 60 is disposed, it is possible to prevent the rotational phases of the rotating disks 21 to 24 that are not firmly connected and fixed to each other from being shifted. Therefore, the rotational force can be efficiently output via the rotary disks 21 to 24.

A pair of first and second outer sides in which the

cylinders

5 and 6 are coaxially disposed opposite to each other on the horizontal line L 1 and the first piston rod 9 connected to the first piston 7 is connected to the second piston 8. Since it is arranged to move between the

piston rods

10A and 10B, a piston crank mechanism is provided from each

cylinder

5 and 6 via the first piston rod 9 and the pair of first and second

outer piston rods

10A and 10B. The action point of the couple acting on 20 is approaching. As a result, since the influence of the couple on the piston crank mechanism 20 is suppressed, the vibration of the two-cylinder engine 1 can be reduced.

Further, the first and second

inner piston rods

9A and 9B and the first and second

outer piston rods

10A and 10B are common parts, and the first to fourth rotating disks 21 to 24 are common parts, and the second, The third pins 42 and 43 are common parts, and these parts, including the first pin 41, are arranged so as to be symmetric with respect to the plane including the horizontal line L1 orthogonal to the rotation center line L2. . As a result, the piston crank mechanism 20 balances the weight before and after the horizontal line L1, so that the vibration of the two-cylinder engine 1 is further suppressed.

The second and

third pins

42 and 43 are common parts, and the first and second

inner piston rods

9A and 9B and the first and second

outer piston rods

10A and 10B are common parts. Since the four-rotation disks 21 to 24 are also common parts, engine components can be greatly reduced.

Further, the first and second

inner piston rods

9A and 9B, the first and second

outer piston rods

10A and 10B, and the first to fourth rotating disks 21 to 24 are formed thin in the direction of the rotation center line L2. Therefore, the lubricating oil can easily go around the deep groove ball bearings 31 to 34 and the deep groove ball bearings 51 to 54, and wear at each bearing portion can be reduced.

As described above, the horizontally opposed two-cylinder engine 1 is lightweight and has low vibration, and is therefore suitable as an engine mounted on a device used by being mounted on a human body such as a motor paraglider. Of course, it can also be used as an engine for other purposes, for example, an engine for automobiles or other industrial machines.

In the above embodiment, the pair of

inner piston rods

9A and 9B is used as the first piston rod 9, but a single piston rod can also be used. Further, the bearing mechanism for rotatably supporting the rotating disks 21 to 24 is not limited to the deep groove ball bearing, and other rolling bearing mechanisms may be employed. Further, the output rotating shaft 70 can be used as a hollow shaft to reduce the weight of the engine.

Next, in the case of a four-cycle engine, the output rotation shaft 70 can function as a camshaft shaft for driving and controlling the intake and exhaust valves with a phase difference of 180 degrees with respect to the first cylinder and the second cylinder. it can. In this case, the first and second drive side gears 61 and 62, the second drive side gears 61 and 62, and the second drive side gears 61 and 62 can be transmitted to the output rotary shaft 70 by decelerating the rotation of the first to fourth rotary disks 21 to 24 to ½. What is necessary is just to set the reduction ratio of the gear type transmission mechanism consisting of the driven gears 65 and 66 to ½.

That is, in the 4-cycle engine, the first piston rod and the second piston rod reciprocate twice during the intake process, the compression process, the combustion expansion process, and the exhaust process. The side gear 62 rotates twice. On the other hand, since the intake valve and the exhaust valve need only be driven once, if the rotational speed of the output rotary shaft 70 is set to 1/2 the rotational speed of the rotary disks 21 to 24, the output rotary shaft 70 And camshaft. Of course, the two-cylinder engine 1 may be a two-cycle engine. In the case of a two-cycle engine, a scavenging port and an exhaust port are configured for each

cylinder

5 and 6.

(Configuration example of multi-cylinder engine)
By connecting the two-cylinder engine of the present invention, a multi-cylinder engine having an even number of four or more cylinders can be constructed.

For example, as shown in FIG. 6A, a plurality of, for example, two, two-cylinder engines 1 are connected to each other so that the rotation center line L2 of the piston crank mechanism 20 is common and the output rotation shaft 70 is connected to each other. Thus, a 4-cylinder engine can be constructed. Instead, as shown in FIG. 6B, a four-cylinder engine can be constructed by connecting a plurality of, for example, two, two-cylinder engines 1 so that their output rotation shafts 70 are common.

Of course, it is also possible to construct a composite multi-cylinder engine by mutually connecting the output rotation shafts 70 of the connected four-cylinder engine shown in FIG. 6A and the four-cylinder engine shown in FIG. 6B. Further, the number of two-cylinder engines 1 to be connected is not limited to the two shown in FIGS. 6A and 6B, and a high-power engine can be realized by increasing the number of stations.

(Other embodiments)
FIG. 7A is an explanatory view showing another example of a piston crank mechanism provided with two rotating disks to which the present invention is applied. The illustrated piston crank mechanism 20A includes two

rotating disks

21A and 21B arranged coaxially with a preset rotation center line L2, and these

rotation disks

21A and 21B are constant in the direction of the rotation center line L2. Are arranged in parallel with a gap of. These

rotary disks

21A and 21B are supported in a freely rotatable state by the circular inner peripheral surface of the crankcase 2A via bearing

mechanisms

31A and 31B mounted on the circular outer peripheral surfaces.

A first pin 41A is bridged between the

rotating disks

21A and 21B. The first pin 41A is located at a portion deviating from the rotation center line L2. A first outer pin 42A is attached to the first outer circular side surface 21a of the rotating disk 21A opposite to the rotating disk 21B, and the second outer circular side surface 21b of the rotating disk 21B opposite to the rotating disk 21A is attached. The second outer pin 43A is attached. The first and second

outer pins

42A and 43A are attached to a portion that is deviated from the rotation center line L2 and is 180 degrees away from the first pin 41A around the rotation center line L2.

The rear end portion of the first piston rod 9C of the first cylinder 5A on the crankcase 2A side is attached to the first pin 41A so as to be rotatable around a connecting axis parallel to the rotation center line L2. One piston rod 9C extends in a direction perpendicular to the rotation center line L2. The second piston rod of the second cylinder 6A includes a first outer piston rod 10C and a second outer piston rod 10D. The first outer piston rod 10C is connected to the first outer pin 42A, and the second outer piston rod. 10D is connected to the second outer pin 43A.

In the piston crank mechanism 20A configured as described above, the weight of the piston crank mechanism can be reduced as compared with the case of using a conventional crankshaft. Further, since the piston crank mechanism 20A can be configured in a well-balanced manner so as to be symmetric with respect to the plane including the horizontal line L1 orthogonal to the rotation center line L2, low vibration can be achieved.

FIG. 7B is an explanatory diagram showing a piston crank mechanism of a horizontally opposed two-cylinder engine to which the present invention is applied as a reference example. The illustrated piston crank mechanism 20B includes a rotating disk 21C disposed coaxially with a preset rotation center line L2 and a rotating mechanism 21C mounted on a circular outer peripheral surface 21a of the rotating disk 21C. And a crankcase 2A that supports 21C in a rotatable state. In addition, in one circular side surface 21d of the rotating disk 21C, the first pin 41B attached to a portion deviating from the rotation center line L2, and in the other circular side surface 21e of the rotating disk 21C, a portion deviating from the rotation center line L2. The first pin 41B includes a second pin 42B attached to a portion 180 degrees away from the rotation center line L2.

A rear end portion of the first piston rod 9D of the first cylinder 5B on the crankcase 2B side is attached to the first pin 41B so as to be rotatable around a connecting axis parallel to the rotation center line L2. One piston rod 9D extends in a direction perpendicular to the rotation center line L2. Similarly, the rear end portion of the second piston rod 10E of the second cylinder 6B is attached to the second pin 42B so as to be rotatable around a connecting axis parallel to the rotation center line L2, and this second piston The rod 10E also extends in a direction perpendicular to the rotation center line L2.

Here, in FIG. 7B, the first cylinder 5B and the second cylinder 6B are arranged at positions that are perpendicular to the rotation center line L2 and shifted from the plane including the horizontal line L1 in the opposite directions to the rotation center line L2. ing. That is, the first cylinder 5B is slightly shifted from the horizontal line L1 to the second piston rod 10E side, and the second cylinder 6B is slightly shifted from the horizontal line L1 to the first piston rod 9D side. Further, the outer end portion of the first piston rod 9D is bent in a crank shape so as to be positioned on the central axis L2 of the first cylinder 5B, and the outer end portion of the second piston rod 10E is the central axis of the second cylinder 6B. It is bent in a crank shape so as to be positioned at L3.

Also in the piston crank mechanism 20B configured as described above, the weight of the piston crank mechanism can be reduced as compared with the case where the conventional crankshaft is used. In addition, since the piston crank mechanism 20B is thinly configured in the direction of the rotation center line L2, for example, if the cylinder 5B and the cylinder 6B are disposed opposite to each other on a plane including the rotation center line L2, the first piston from each

cylinder

5, 6 The action point of the couple acting on the piston crank mechanism 20 approaches through the rod 9D and the second piston rod 10E. As a result, since the influence of the couple on the piston crank mechanism 20 can be suppressed, vibration can be reduced.

In the piston crank

mechanisms

20A and 20B, the

rotary disks

21A, 21B, and 21C may be rotatably supported by a gear mechanism in order to extract the rotation of the

rotary disks

21A, 21B, and 21C to the outside. In this case, the gear mechanism includes external teeth formed on the circular outer peripheral surface of each rotating disk, and a plurality of driven gears that are arranged along the outer periphery of each rotating disk and mesh with the external teeth of each rotating disk. Shall be provided. Further, the external teeth of the rotating disk and the driven gear are formed so as not to disengage not only in the radial load but also in the axial load. The rotation of each rotating disk is taken out via a plurality of driven gears.

1 2-

cylinder engine

2, 2A, 2B Crankcase 3 First cylinder block 4

Second cylinder block

5, 5A,

5B First cylinder

6, 6A, 6B Second cylinder 7 First piston 8

Second piston

9, 9C, 9D First piston rod 9A First inner piston rod 9B Second

inner piston rod

10, 10E

Second piston rod

10A, 10C First

outer piston rod

10B, 10D Second

outer piston rod

20, 20A, 20B Piston crank mechanisms 21-24 Rotating disks 31 to 34 Deep groove ball bearing 35

Collar

41, 41A,

41B First pin

42, 42A First outer pin 42B, 43B Second pin 43A Second outer pin 51-54 Deep groove ball bearing 60

Synchronous rotation mechanism

61, 62

Drive Side gear

65, 66 Driven side gear 70 Output rotating shaft L1 Horizontal line L2 Rotating Core L3 rotation center line

Claims

A first rotating disk (21A) and a second rotating disk (21B) arranged coaxially at a predetermined interval in the direction of a preset rotation center line (L2);
The first rotating disk (21A) and the second rotating disk via the bearing mechanisms (31A, 31B) mounted on the circular outer peripheral surfaces of the first rotating disk (21A) and the second rotating disk (21B). A crankcase (2A) supporting (21B) in a rotatable state around the rotation center line (L2);
A first pin (41A) fixed between the first rotating disk (21A) and the second rotating disk (21B) across and fixed to a portion off the rotation center line (L2);
In the first outer circular side surface of the first rotating disk (21A) opposite to the second rotating disk (21B), the first pin (41A) is a portion deviated from the rotation center line (L2). ) Is a first outer pin (42A) fixed to a part separated by a predetermined angle around the rotation center line (L2),
In the second outer circular side surface of the second rotating disk (21B) opposite to the first rotating disk (21A), the second rotating disk (21B) is a portion deviated from the rotation center line (L2), and the first pin (41A ) Includes a second outer pin (43A) fixed at a predetermined angle and away from the rotation center line (L2),
An inner end portion is attached to the first pin (41A) so as to be rotatable around a connecting axis parallel to the rotation center line (L2), and extends in a direction perpendicular to the rotation center line (L2). A first piston rod (9C) of the first cylinder (5),
An inner end is attached to the first outer pin (42A) so as to be rotatable around a connecting axis parallel to the rotation center line (L2), and extends in a direction perpendicular to the rotation center line (L2). A first outer piston rod (10C) of the second cylinder (6),
An inner end is attached to the second outer pin (43A) so as to be rotatable around a connecting axis parallel to the rotation center line (L2), and is fixed to the first outer piston rod (10C). A two-cylinder engine having a second outer piston rod (10D) of a second cylinder (6) extending in a direction perpendicular to the rotation center line (L2) with a gap therebetween.
The two-cylinder engine according to claim 1,
The first cylinder (5) and the second cylinder (6) are arranged to face each other on a horizontal line (L1) orthogonal to the rotation center line (L2),
The two-cylinder engine, wherein the first pin (41B) and the second pin (42B, 43B) are arranged at an angular interval of 180 degrees around the rotation center line (L2).
The two-cylinder engine according to claim 2,
The rotating disk includes a third rotating disk (23) arranged coaxially with a constant interval with respect to the first rotating disk (21) on the side of the first outer circular side surface of the first rotating disk (21). And a fourth rotating disk (24) arranged coaxially with a constant distance to the second rotating disk (22) on the second outer circular side surface side of the second rotating disk (22). ,
The first to fourth rotating disks (21 to 24) are supported by the crankcase (2) through the bearing mechanism so as to be rotatable around the rotation center line (L2),
The first outer pin (42) is bridged between the first rotating disk (21) and the third rotating disk (23),
The two-cylinder engine, wherein the second outer pin (43) is bridged between the second rotating disk (22) and the fourth rotating disk (24).
The two-cylinder engine according to claim 3,
The two-cylinder engine is characterized in that the bearing mechanism is a rolling bearing and is mounted between a circular outer peripheral surface of the first to fourth rotating disks (21 to 24) and the crankcase (2).
The two-cylinder engine according to claim 3,
A two-cylinder engine comprising a synchronous rotation mechanism (60) for synchronously rotating the third rotating disk (23) and the fourth rotating disk (24).
The two-cylinder engine according to claim 5,
The synchronous rotation mechanism (60)
A first drive-side gear (61) attached to the third rotating disk (23) so as to rotate integrally therewith;
A second driving gear (62) attached to the fourth rotating disk (24) so as to rotate integrally therewith, coaxially;
An output rotation axis (70) arranged parallel to the rotation center line (L2);
A first driven gear (65) attached coaxially so as to rotate integrally with the output rotating shaft (70) and meshing with the first driving gear (61);
A second driven gear (66) that is coaxially attached to the output rotary shaft (70) and is meshed with the second drive gear (62) is provided. 2-cylinder engine.
The two-cylinder engine according to claim 6,
The two-cylinder engine, wherein the output rotation shaft is a cam shaft for supplying fuel with a phase difference of 180 degrees to the first cylinder (5) and the second cylinder (6).
The two-cylinder engine according to claim 3,
The first pin (41) is fitted in a playable state with respect to pin holes formed in the first rotating disk (21) and the second rotating disk (22),
The first outer pin (42) is fitted in a playable state with respect to a pin hole formed in the third rotating disk (23),
The two-cylinder engine is characterized in that the second outer pin (43) is fitted in a playable state with respect to a pin hole formed in the fourth rotating disk (24).
The two-cylinder engine according to claim 3,
The first piston rod (9) includes a first inner piston rod (9A) and a second inner piston rod (9B) having the same shape extending in parallel.
The first and second outer piston rods (10A, 10B) and the first and second inner piston rods (9A, 9B) are common parts,
The two-cylinder engine, wherein the first to fourth rotating disks (21 to 24) are shared parts.