WO2005111464A1

WO2005111464A1 - Cylinder type rotary power transmission device

Info

Publication number: WO2005111464A1
Application number: PCT/JP2005/009490
Authority: WO
Inventors: Young Saeng Kim; Kengo Hiruta; Tadahito Yamanouchi
Original assignee: Hiruta Corporation
Priority date: 2004-05-19
Filing date: 2005-05-18
Publication date: 2005-11-24

Abstract

[PROBLEMS] To provide a cylinder type rotary power transmission device capable of efficiently converting a force from a linear motion to a rotating motion or from a rotating motion to a linear motion and transmitting the force at the highest efficiency without diminishing an inertia force generated in the conversion. [MEANS FOR SOLVING PROBLEMS] This cylinder type rotary power transmission device comprises three two-way rotary gears basically formed of a rack and pinion utilizing inertia force and always meshing with an intermediate part between two pairs of two cylinders incorporating pistons and a rack gear and a one-way transmission clutch bearing. The mechanism receives an explosive force (expansion force) at an angle of 90° (right angle) with the highest efficiency in place of a boiled rice ball type rotor of a conventional rotary engine, the crank mechanism of a reciprocating engine sets a transmission force to a neutral or produces braking phenomenon to diminish the inertia force in those strokes other than an explosion stroke, and the piston cylinder eliminating the deteriorated airtightness of the rotary engine and its turbine is completely sealed airtight. Thus, the power transmission device can convert the explosive force (expansion force) to the power under the best conditions.

Description

Description Cylinder type rotary power transmission

The present invention relates to a cylinder-type rotary power transmission device that efficiently converts a force from a linear motion to a rotational motion and vice versa and converts the rotational motion into a linear motion, and develops the most efficient transmission method without reducing the generated inertial force. It is. Background art

The most popular conventional driving methods are the reciprocating engine and the rotary engine that use a common crank.First, the conventional rotary engine has a triangular rotor that receives the internal explosive power. This shape cannot be used at the most efficient 90 degrees when the rotor is subjected to explosive power, and requires a fairly high level of technology to achieve perfect sealing at the time of manufacture. In addition, it is difficult to always maintain the sealing performance in the best condition. Furthermore, conventional reciprocating engines with cranks consist of four processes: explosion (expansion), exhaust, intake, and compression, and convert the explosive power into rotational motion. Is the case where the piston rod extends from about 45 degrees to 90 degrees, and this is the time when the speed of the piston is the highest and the power is most efficiently transmitted to the rotating body.In other processes, The inertia of the rotating body connected as neutral or brake every time is also reduced. This braking force is applied every four cycles before the rotating body has sufficient inertia, so the efficiency is greatly reduced. Disclosure of the invention

Problems to be solved by the invention

As described above, the conventional reciprocating engine is a crank mechanism, so even if the object that transmits power has inertial force, it works as a neutral or brake except for the expansion (explosion) process, and the loss is enormous. Is also big. In addition, turbines and rotary engines that do not kill the inertial force have an expansion force of 90 degrees, and are not affected by the blades or the rotor in the shape of a rice ball, and have poor airtightness. These problems have been ameliorated, and despite the cylinder type that does not kill the inertia force and has no crank and good airtightness, the power transmission rate eliminates the defects of the turbine and rotary engine, and the power is efficiently straightened. It is an object of the present invention to provide a cylinder type rotary one power transmission device developed by a most efficient transmission method without converting generated motion into rotary motion, and from rotary motion into linear motion, without reducing generated inertia force.

Means for solving the problem

The present invention for achieving the above object is as follows. The cylinder-type rotary power transmission device according to the present invention is basically based on the principle of rack and pinion, and adds a new power transmission mechanism to efficiently convert linear motion into rotary motion and rotary motion into linear motion. It is composed of a mechanism. The first invention consists of a cylinder with a built-in piston and a rack gear attached to a biston opening that connects to a biston. A pair of the two cylinders, and a pair of the two cylinders in the same manner as above, and a pair of two cylinders for alternately sucking high-pressure fluid into the cylinder and reciprocating the piston; And a power transmission mechanism that rotates in synchronism with each other.

In the cylinder type rotary power transmission device according to the first aspect of the invention, a switching valve is provided in a supply path for supplying high-pressure fluid to two pairs of two cylinders, and an operation path of the high-pressure fluid is established by operation of the switching valve. It is good to configure to switch.

Further, the power transmission mechanism of the cylinder type rotary power transmission device, which is the first aspect of the present invention, is configured such that three intermediate bidirectional rotary gears always matching with the four rack gears and one rack gear are used. It is preferable that the rack gear is composed of a one-way transmission clutch bearing that converts the reciprocating linear motion of the rack gear into only one direction of rotation, and a power shaft that transmits the rotational force to the load, so that the power transmission can be continuously supplied.

Furthermore, the cylinder type rotary power transmission device, which is the second invention configuration, includes a center part of a piston that reciprocates linearly in a cylinder, and a certain range inside a hole (upper and lower surfaces) penetrated in an opal shape. A pinion gear with a tooth profile formed within a certain angle range is connected to the drive shaft to protrude and form the tooth profile of the rack gear, and the rack gear inside the biston is connected with the forward and backward linear motion of the biston. The surface is smoothly switched by a rotary cam mechanism so that the pinion gear can rotate continuously in one direction. The invention's effect

The present invention can easily convert a force from a linear motion to a rotary motion and vice versa, and can supply a stable power to a load by the most efficient power transmission method without reducing generated inertia force. Demonstrate the excellent effect that can be.

Brief Description of Drawings

FIG. 1 is an explanatory diagram for describing Embodiment 1 of the present invention.

FIG. 2 is a cross-sectional view of FIG. 1 for explaining Embodiment 1 of the present invention.

FIG. 3 is an explanatory diagram for explaining Embodiment 2 of the present invention.

Explanation of symbols

1 First cylinder

2 Second cylinder

3 Third cylinder

4 4th cylinder

5 Power shaft

6 Fly Hoi

7 Fluid switching valve

8 Valve switching mechanism

9 Pressure source

1 1 First biston

1 1, 1st Piston Lo K

1 2 2nd piston

1 2 '2nd screw

1 3 3rd piston

1 3, 3rd bis Thong rod,

1 4 4th piston

1 4 '4th Pis Thong Lo K

2 1 1st rack gear

2 2 2nd rack gear

2 3 3rd rack gear 4th rack gear

1st clutch bearing (--direction transmission) 2nd clutch bearing (1 'direction transmission) 3rd clutch bearing (--direction transmission) 4th clutch bearing (--direction transmission) 1st bidirectional rotary gear

, Axis

2nd bidirectional rotating gear

'' Axis

3rd bidirectional rotating gear

'' Axis

1st intake valve

'' 1st exhaust valve

2nd intake valve

'' 2nd exhaust valve

Third intake valve

'' 3rd exhaust valve

4th intake valve

'' 4th exhaust valve

1st cylinder-chamber

2nd cylinder, -chamber

Third cylinder-chamber.

4th cylinder -Room

cylinder

Biston

Oval shape

Rack gear one

Pinion gear 7 6 1-pinion gear

7 7 Rotating cam

7 8 Moving shaft

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, the present invention will be described in detail with reference to embodiments.

FIGS. 1 and 2 do not show Embodiment 1 of the present invention, wherein 1 is a first cylinder, and a first piston 11 is built in the first cylinder. Is connected to the first bistro rod 1 1 ′. Reference numeral 21 denotes a first rack gear fixed to the first piston rod 11 ', and teeth on the side surface of the first rack gear correspond to a first bidirectional rotary gear 41 of a power transmission mechanism described later. I have.

In FIG. 1, reference numeral 2 denotes a second cylinder. A second piston 12 is built in the second cylinder, and a second piston rod 12 ′ is connected to the second piston 12. Reference numeral 22 denotes a second rack gear fixed to the second piston port 12 ', and teeth on the side surface of the second rack gear 1 are first and second bidirectional rotary gears of a power transmission mechanism described later. 4 1 and 4 2 respectively.

In FIG. 1, reference numeral 3 denotes a third cylinder, and a third piston 13 is built in the third cylinder. A third piston rod 13 is connected to the third piston 13. Reference numeral 23 denotes a third rack gear fixed to the third piston rod 13 ', and teeth on the side surface of the third rack gear 1 have second and third bidirectional rotating gears 4 2 of a power transmission mechanism described later. , 4 and 3 respectively.

In FIG. 1, reference numeral 4 denotes a fourth cylinder, and a fourth piston 14 is built in the fourth cylinder, and a fourth piston port 14 ′ is connected to the fourth piston 14. Have been. Reference numeral 24 denotes a fourth rack gear fixed to the fourth biston rod 14, and the teeth on the side surface of the fourth rack gear correspond to a third bidirectional rotary gear 43 of a power transmission mechanism described later. You.

The first cylinder, the second cylinder, the third cylinder, and the fourth cylinder containing the piston constitute a two-cylinder two-pair type.

In FIG. 1, reference numeral 51 denotes a first intake valve provided in a first cylinder 1, 51 ′ denotes a first exhaust valve, 52 denotes a second intake valve provided in a second cylinder 2, and 52 denotes a second exhaust valve. 5 3 is the third system The third intake valve provided in the cylinder 13, 53 is a third exhaust valve, 54 is a fourth intake valve provided in the fourth cylinder 4, and 5 4 ′ is a fourth exhaust valve, which switches a fluid described later. A fluid switching valve 7 is connected to each of the pipes by a pipe, a valve switching rod is provided at an end of each of the above-mentioned bis ports, and a valve switching mechanism 8 is provided at a head portion of each of the cylinders. The switching valve is actuated in conjunction with the reciprocating movement of the piston rod to switch between the intake valve and the exhaust valve.

Although each cylinder is provided with an intake valve and an exhaust valve separately, a mechanism for switching between intake and exhaust with one valve may be used.

In FIG. 1, reference numeral 7 denotes a fluid switching valve, which has eight ports, and is connected to an intake valve and an exhaust valve provided in each cylinder by pipes. The first port of the fluid switching valve 7 is connected to the first intake valve 51, the second port is connected to the first exhaust valve 51 ′, the third port is connected to the second intake valve 52, and the fourth port To the second exhaust valve 52 ', the fifth port to the third intake valve 53, the sixth port to the third exhaust valve 53', and the seventh port to the fourth intake valve 54. The eighth port is connected to the fourth exhaust valve 54 ′ by a pipe, and the high-pressure fluid (for example, steam, compressed air, etc.) stored in the pressure source 9 is supplied to the main suction port of the fluid switching valve 7. After being supplied, the distribution path can be switched to each of the ports by interlocking with the valve switching mechanism 8 described above.

In FIG. 1, reference numeral 41 denotes a first bidirectional rotary gear of the power transmission mechanism, which is rotatably supported on a shaft 4 1 ′. The first bidirectional rotary gear 41 includes the first rack gear 21 and the second rack gear 21. 22 respectively, and rotates clockwise and counterclockwise following the movement of the first and second rack gears. Reference numeral 42 denotes a second bi-directional rotary gear, which is rotatably supported on a shaft 4 2 ′. The second bi-directional rotary gear 42 is attached to the teeth on the side surfaces of the second rack gear 122 and the third rack gear 123. The two rack gears follow each other and rotate clockwise and counterclockwise following the movement of the second and third rack gears. Reference numeral 43 denotes a third bidirectional rotary gear, which is rotatably supported on a shaft 4 3 ′. The third bidirectional rotary gear 43 is provided on the teeth on the side surfaces of the third rack gear 123 and the fourth rack gear 124. They rotate in clockwise and counterclockwise directions following the movements of the third and fourth rack gears. The first, second and third two-way rotations. The gears 41, 42 and 43 are arranged in the middle of the first, second, third and fourth rack gears 21, 22, 23 and 24, respectively. A power transmission that transmits the linear motion force of the piston generated in each cylinder efficiently and evenly to a clutch bearing described later by interlocking the reciprocating linear motion with each of the rack gears. It plays an important role in the mechanism.

In FIG. 1, reference numeral 31 denotes a first clutch bearing of a power transmission mechanism, which is a clutch bearing which is rotatably supported by a power shaft 5 and transmits rotational force only in one direction. The first clutch bearing 31 includes the first clutch bearing 31. 3 2 is a second clutch bearing, which is rotatably supported by the power shaft 5 and is combined with the teeth of the second rack gear 1 2 3. 3 3 is a third clutch bearing. , Which is supported by the power shaft 5 and is in mesh with the teeth of the third rack gear 23. Reference numeral 34 denotes a fourth clutch bearing, which is supported by the power shaft 5 and is connected to the fourth rack gear 24. The clutch bearings convert the reciprocating linear motion of each of the rack gears into one-way rotation, and convert the linear motion force of bistons generated in each of the aforementioned cylinders into rotational power. Transmitted to the power shaft 5 and shown If unusual example supplied to a load such as an electrical generator and the like.

In FIG. 1, reference numeral 6 denotes a flywheel, which is provided on the power shaft 5, and supplies inertial force to the above-mentioned rotational power to supply stable rotational power to a load such as a generator (not shown). Basically, since the inertia force is easily applied to the device itself and does not kill the generated inertia force, stable rotational power can be supplied even without a flywheel.

Next, the operation will be described.

As shown in FIG. 1, the operation by the fluid switching valve 7 and the valve switching mechanism 8 causes the first intake valve 51 of the first cylinder 1 and the third intake valve 53 of the third cylinder 3 to open, and the pressure source 9 High pressure fluid

When water (eg, steam, air, oil, etc.) is supplied to the first cylinder chamber 61 and the third cylinder chamber 63 through pipes, the first piston 11 and the third cylinder 11 The button 13 is pushed downward (arrow direction) in FIG. 1 and moves downward. Accordingly, when the first piston 11 and the third piston 13 are pushed downward, the first rack gear 21 connected to the first piston 11 is connected to the third piston 13. The third rack gear 23 moves linearly downward, and the first bidirectional rotary gear 41 of the power transmission mechanism that matches the rack gears 21 23 The rotary gear 42 and the third bidirectional rotary wheel 43 rotate counterclockwise and clockwise, respectively, and transmit the transmission force of the rack gears 21 and 23 equally to the next power transmission mechanism. The directional rotation is transmitted to the first clutch bearing 31 and the third clutch bearing 33, and the rotational power is transmitted from the power shaft 5 to a load (not shown). Along with the above-described movement, the second rack gear 122 becomes a bi-directional rotating gear 41 which is combined with the first rack gear 21 and a bi-directional rotating gear 41 which is combined with the third rack gear 123. contrary rotary gear 4 first rack gear one 2 1 depending on the rotation of the two and the third rack gear one ² 3 motion, and the fourth rack gear one 2 4, the third rack gear one 2 3 and嚙合Tsu and are bidirectional Due to the rotation of the rotary gear 43, opposite to the movement of the third rack gear 123, it moves linearly upward (in the direction of the arrow) in FIG. (At this time, the one-way transmission of the second clutch bearing 32 and the fourth clutch bearing 34 is opposite to the rotation of the first clutch bearing 31 and the third clutch bearing 33, so that the first clutch bearing 31 and the third clutch bearing 33 rotate idly and transmit power. Accordingly, the ^second piston 12 connected to the second rack gear 122 and the fourth piston 14 connected to the fourth rack gear 124 move upward, respectively. At the same time, the fluid switching mechanism 8 reacts to the movement of the valve switching port provided in the second piston rod 12 and the valve switching rod provided in the fourth piston rod 14 ′, and The second exhaust valve 5 2 ′ of the second cylinder 2 and the fourth exhaust valve 5 4 ′ of the fourth cylinder 4 are opened to fill the second cylinder chamber 6 2 and the fourth cylinder chamber 64. Fluid (eg, steam, air, oil, etc.) passes through the pipe and passes through the fluid switching valve 7. It is discharged to the outside from the discharge port. Then, the first intake valve 51 of the first cylinder 1 and the third intake valve 53 of the third cylinder 3 are closed by the operation of the valve switching mechanism 8, and the second exhaust of the second cylinder 1 The valve 52 'and the fourth exhaust valve 54' of the fourth cylinder are also closed, and the high-pressure fluid path of the fluid switching valve 7 is switched in conjunction with it. In other words, the path is switched to the reverse path, and the high-pressure fluid is conducted.

When the high-pressure fluid path is switched, the second intake valve 52 of the second cylinder 2 and the fourth intake valve 54 of the fourth cylinder 14 shown in FIG. 1 are opened, and the high-pressure fluid (eg, steam, air) of the pressure source 9 is opened. , Oil, etc.) are supplied through pipes to the second cylinder chamber 62 and the fourth cylinder chamber 64, respectively, so that the second piston 12 and the fourth piston 14 are supplied by the high-pressure fluid. Is pushed downward (in the direction opposite to the arrow) in FIG. 1 and moves downward. Accordingly, when the second and fourth pistons 12 and 14 are pushed downward, they are connected to the second rack gear 122 and fourth piston 14 connected to the second piston 12. The fourth rack gear 124 moves linearly downward, and the first bidirectional rotary gear 41 and the second bidirectional rotary gear of the power transmission mechanism that matches the rack gears 222, 24. 42, the third bidirectional rotating gear 43 rotates counterclockwise and clockwise, respectively, to evenly transmit the transmission force of the rack gears 222 and 224 to the next gear. The power is transmitted to the second clutch bearing 32 and the ^fourth clutch pairing 34 of the one-way rotation transmission, which is a force transmission mechanism, and the rotational power is transmitted from the power shaft 5 to a load (not shown).

Along with the above-mentioned movement, the first rack gear 21 is moved by the rotation of the bi-directional rotating gear 41 of the power transmission mechanism which is combined with the second rack gear 22 and the movement of the second rack gear 22 The opposite is true, and the third rack gear 123 is the rotation of the bi-directional rotating gear 42 matching the ^second rack gear 122 and the bidirectional rotating gear 43 matching the fourth rack gear 124. In contrast to the movements of the second rack gear 122 and the fourth rack gear 124, they move linearly upward (in the direction opposite to the arrow) in FIG. (At this time, the first clutch bearing 31 and the third clutch bearing 33, which are one-way transmission, rotate in the opposite direction to the second clutch bearing 32 and the fourth clutch bearing 34, so that the first clutch bearing 31 and the third clutch bearing 34 rotate idle and transmit power. Therefore, the first piston 11 connected to the first rack gear 21 and the third piston 13 connected to the third rack gear 23 move upward, respectively. And at the same time, reacts to the movement of the valve switching rod provided in the first piston rod 11 'and the valve switching rod provided in the third piston port 13 by the fluid switching mechanism. 8, the first exhaust valve 51 of the first cylinder 1 and the third exhaust valve 53 'of the third cylinder 3 are opened, and the first cylinder chamber 61 and the third cylinder chamber 63 are filled. Fluid (eg, steam, air, oil, etc.) passes through a pipe and the fluid switching valve 7 It is discharged to the outside than as the discharge port. Thereafter, the first exhaust valve 51 'and the third exhaust valve 53' are closed by the operation of the valve switching mechanism 8, and a series of operations is completed, and the operation returns to the above, and the operation is repeated.

In the first embodiment, the high-pressure fluid of the pressure source 9 switches the fluid switching valve 7 by operating the valve switching rod and the valve switching mechanism 8 that interlock with the movement of the piston to operate the biston in an interlocking manner. The kinetic force was transmitted to the load by using a rack gear, bidirectional rotating gears, and a one-way clutch bearing to convert to rotational power.

With such a configuration, not only can the linear motion force be converted to rotational power, but also the rotational power can be transmitted to the load instead of linear power by a power transmission mechanism.

Such a configuration is basically a power transmission system in which a single rack gear, a two-way rotating gear, and a one-way transmission clutch bearing are matched with each other. In this method, the discontinuity of the gear that occurs when switching between the forward and backward paths of the biston occurs every time, even if only slightly, and unnecessary vibration occurs. I was most concerned about damaging it, but the discontinuous time could be eliminated by connecting the rack gear with a bidirectional rotating gear.

In such a configuration, for example, when a large force is required for the operation of the load, the switching of the fluid switching valve 7 is interlocked with the movement of the piston, so that intermittent and stable rotational force cannot be supplied to the load. is there. Therefore, for example, when a large load is required, a valve switching rod and a limit switch are combined so that the fluid switching valve 7 switches instantaneously when the valve switching port operates the limit switch. With this configuration, the power transmission mechanism rotates smoothly, and a stable torque can be supplied to the load.

Next, as a second embodiment, the basic power transmission method described above is the same, and as a more compact structure, the biston shape is formed in the center of the biston 71 as shown in FIG. The gear teeth 73 and 74 protrude inside the hole (upper and lower surfaces in the figure), and the center of the cylinder 70 is inserted into the center of the cylinder 70 so as to intersect the hole 72 vertically. 8 is arranged, and a toothed shape 76 protrudes from a fixed angle range that is fixed to the driving shaft 78 and rotates together with the rack gears 73, 74 at the center of the piston 71 so as to match. And a rotating cam 77. The piston 71 alternately sucks and discharges a pressurized fluid (for example, steam, air, oil, etc.) from the outside to both ends of the cylinder 70, and reciprocates around the driving shaft 78 under the pressure. Start linear motion. The reciprocating linear lotus is converted into a continuous rotary motion by a pinion gear 75 corresponding to the rack gears 73, 74, and the rotary power is transmitted to a driving shaft 78, for example, a generator (not shown). To supply the load. Conversely, the rotational motion of the drive shaft 78 is connected by a pinion gear 75, and the rotational motion is converted to reciprocal linear motion by the rack gears 73, 74, and the rotational power is supplied to the load as a linear motion force. A form that can be used.

The range of tooth profile formation of the rack gears 73 and 74 provided at the center of the piston 71 (upper and lower surfaces in the figure), and the range of tooth profile formation 76 of the pinion gear 75 corresponding to the range (constant) The angle range) is the range in which the pinion gear 75 can move from the drive shaft 78 left and right (reciprocating) by half a turn (half the circumference of the pinion gear).

The rotating cam 77 is fixed to the drive shaft 78 together with the pinion gear 75, and the tooth shape of the pinion gear Ί 6 is located at the end of the movement range of the rack gears 73, 74 of the piston 71. When the part is approaching, it absorbs the impact of the tooth form 76 of the pinion gear and smooth movement This is a mechanism that switches the surfaces of the rack gears 73 and 74 by switching the surfaces (upper and lower surfaces in the figure), and the pinion gears 75 continuously rotate in the negative direction. Note that the pinion gear 75 is idled on both sides of the central part 7 of the flat shape 7 2 according to the rotational force 77, and the protruding tooth form of the pinion gear 75 However, there is no tooth profile on the surface to make it easier to switch the mating surface of the piston 71 with the rack gears 73, 74 (upper and lower surfaces in the figure).

Such a configuration is characterized in that the number of main components such as the number of cylinders, pistons, and rack gears can be reduced by half compared to the first embodiment, and the device itself can be configured compactly.

Industrial applicability

According to the above-described embodiment of the present invention, considering a conventional reciprocating engine with a crank and a rotary engine in terms of inertia force, if the power transmission system of the present invention is used, except for the mechanical loss, it will be difficult If the rotating body has a characteristic of inertia, except for mechanical and physical losses, once inertia is added, it is only necessary to compensate for the loss lost by the loss, so the fuel efficiency is remarkably improved. There is. In the sense that this inertial force is not killed, it applies to both cases where linear motion is converted into rotary motion and rotary motion is converted into linear motion. Furthermore, the cylinder type power transmission system of the present invention is the most efficient and always transmits power because the part that receives the expansion (explosion) of a conventional reciprocating engine or rotary engine is the cylinder. It is excellent in that the directional rotating gear, one-way transmission clutch bearing, and pinion gear are combined and always receive at 90 degrees (at right angles).

Other advantages of the present invention are that it is easy to manufacture using conventional technology, and because it is a cylinder type, other mechanisms such as valves used in conventional reciprocating engines can be used as is. It is possible to generate electricity using steam, etc. as the engine of a fuel engine, and it can be applied to two or four cycles, and it can also use a direct fuel injection system. In other words, it can be used for various fuels other than gasoline, such as light oil, kerosene, and alcohol (methanol using plant biomass). When these characteristics are combined, it is possible to efficiently convert biston motion into rotational motion and to rotate a generator with inertia efficiently, so it can be said that this is an optimal mechanism for a hybrid car or pump as an example.

Claims

The scope of the claims

1. A cylinder part is composed of a cylinder containing bistons and a rack gear attached to the biston opening to connect with the piston. Similarly, another pair of cylinders is composed. One pair, and two cylinders, one pair in the same manner as above, and two pairs of two cylinders, which alternately suck high-pressure fluid into the cylinder and reciprocate the biston, and the rack gear, respectively. A cylinder-type rotary power transmission device consisting of a power transmission mechanism that rotates in parallel.

2. A switching valve (two sets of 8-way valves or 4-way valves) is provided in the supply path for supplying high-pressure fluid to the two pairs of 2 cylinders, and the high-pressure fluid conduction path is switched by the operation of this switching valve. 2. The cylinder type rotary power transmission device according to claim 1, wherein the cylinder type rotary power transmission device is configured.

3. The power transmission mechanism converts the reciprocating linear motion of the three rack gears and the three reciprocating linear motions of the rack gears that are always engaged with the four rack gears into rotation in only one direction. It comprises a one-way transmission clutch bearing and a power shaft that transmits rotation, and can convert linear motion into rotary motion and convert rotary motion into linear motion, and continuously supply the power transmission force to the load. 4. A cylinder type rotary power transmission device according to item 1.

4. At the center of the biston that reciprocates linearly in the cylinder, a tooth profile of the rack gear is formed to project within a certain range inside (upper and lower surfaces) of the hole penetrated in an opal shape, and a certain angle range to match it A pinion gear with a tooth profile formed inside is connected to the drive shaft. A cylinder-type rotary power transmission device that is constructed so that it can rotate continuously in one direction, converts linear motion to rotary motion, and converts rotary motion to linear motion, and supplies the power to the load.

5. A mechanism in which the power transmission mechanism does not have a crank mechanism, and the device itself tends to have inertial force The cylinder-one type rotary-one power transmission device according to claim 1, 2, 3, or 4, which can supply a stable power transmission to a load.

6. Since the power generation mechanism is a cylinder and piston mechanism, the power transmission is always 90 degrees (vertical) and the most efficient connection to the power transmission mechanism compared to the rotor part of the conventional rotary engine. The cylinder type rotary power transmission device according to claim 1, 2, 3, or 4, characterized in that:

7. Claims 1, 2, and 3 characterized in that the number of parts is smaller than that of a reciprocating engine and a rotary engine that use a crank mechanism, which is a conventional driving device, and the structure is compact, and vibration is small. 4. The cylinder type rotary power transmission device according to 4.

8.Since the structure of the power transmission device is simple, and the parts and mechanisms used in the conventional reciprocating engine can be applied as they are, they can be applied to two or four cycles, and the direct fuel injection method can be adopted. 5. The cylinder type rotary power transmission device according to claim 1, 2, 3, or 4, which is applicable to various fuels such as gasoline, light oil, kerosene, and alcohol.

9. A cylinder type rotary power transmission device capable of supplying a larger motive power by connecting the power transmission devices according to claim 1, 2, 3, and 4.

10. The cylinder-type rotary power transmission device according to claim 1, 2, 3, or 4, wherein the cylinder type has a basic structure different from the turbine mechanism, and enables sufficiently stable power transmission even with low-pressure fluid and low fuel consumption. .