FLUID MACHINE

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a fluid machine, and more particularly, to a (volumetric/rotary) fluid machine in which no vibration occurs as in a general reciprocating fluid machine, a force of a high-pressure fluid does not generate a force of a piston to abrade a cylinder wall surface as in the reciprocating fluid machine, and processing is relatively easy even during mass production, so that a manufacturing cost is greatly reduced due to a structure that is precise while facilitating manufacture, and a volume change is caused only by a mutual rotational motion of a (rotary) cylinder and a rotary piston.

2. Description of the Related Art

As conventional fluid machines commercialized and widely used, there were mainly those based on reciprocating motions of pistons, or those based on gears, screws, and other various rotary types.

In the past technological advancements, among the most advanced mass-produced form of rotary fluid machines, the Wankel type (Wankel rotary type) was not durable in terms of sealing, abrasion, and the like so that the mass production of the Wankel type failed in general markets such as vehicles and ships despite arduous efforts of the past 70 years. In addition, the screw type was successful only in air compression, whereas a great manufacturing cost was required so as to be several times more expensive than the most general reciprocating fluid machines, and there were limitations in that the screw type may not be applied or used as a technology for a motorizing device or a torque converter due to operation principles. While many other rotary fluid machines have been proposed, there has been no example that has satisfied efficiency, durability, and low manufacturing costs that surpass the existing reciprocating and screw types, and has succeeded in mass production in the general market.

SUMMARY OF THE INVENTION

Conventional fluid machines that are generally mass-produced, such as those using reciprocating pistons or those using gears or screws, are as follows: the reciprocating type has vibration and noise since a force generated by a high-pressure fluid structurally acts as a force applied by a piston to a cylinder side wall, so that much friction and abrasion occurred due to the vibration and noise; the gear type has difficulties in high precision for maintaining airtightness of a gear curved surface, so that it was difficult to form high pressure in terms of sealing when not manufactured with high precision; and the screw type has difficulties in manufacturing with high precision for maintaining airtightness of a helical curved surface, so that there were problems such as a high manufacturing cost.

In addition, mechanically, there were patents for the rotary type in principle, but no one has applied patents related to a commercially-successful rotary engine that operates well in terms of engineering, is maintainable, and is completely durable. There were also no other lesser-known rotary/volumetric fluid machines. In reality, there were many problems such as impossibility of manufacture in terms of engineering, or impossibility of actual operations.

To solve the problems described above, an object of the present invention is to provide a (rotary/volumetric) fluid machine including

• • components having operation parts that perform only complete circular motions,
  • which include a cylinder, a main shaft having a rotation center that coincides with an operation center of the cylinder, a rotary piston-rotation shaft provided on one side of an inside of the main shaft, and configured to maintain (rotate/revolve) an eccentric interval (d) from the main shaft, a rotary piston having a center that is eccentric to the rotary piston-rotation shaft by a distance (r) that is equal to the eccentric interval (d) (d=r), and a rotation ratio restraining device configured to restrain a ratio of a main shaft-rotational angular velocity (x) and a rotary piston rotation shaft-rotational angular velocity (y) to 1:2,
  • so as to cause an operation process of a volume change due to interaction between the (rotary) cylinder and the rotary piston that only performs a complete circular motion.

The operation process may be mathematically proved,

• • the components may be configured as mechanical components that may actually operate in terms of engineering,
  • a high-pressure force may not be applied to a friction portion between the (rotary) cylinder and the rotary piston despite a high-pressure compressed fluid, and
  • multiple stages of cylinders and pistons may be assembled into one integral configuration or formed integrally with each other similarly to a cylindrical rotation shaft in terms of structure, so that each of the stages may be retrained by a rotation ratio when rotating with respect to each other despite the multiple stages.

In addition, the multiple stages may be freely formed at any angle (e.g., 0 degrees, 60 degrees, 120 degrees, etc.) with an arrangement that satisfies a condition of a rotary cylinder-angular velocity (x) and a rotary piston-angular velocity (y=2x).

In addition, according to the fluid machine, the (rotary) cylinder and the rotary piston, which are structurally configured in multiple stages, are arranged so that the center of gravity is always at a rotation center as in a cylindrical rotation shaft so as to prevent vibration such as a precessional motion or reciprocating vibration as in reciprocating pistons and connecting rods from occurring, so that a mechanical mechanism may be in the form of a complete circle and a straight line, and thus there may be very less difficulties in high-precision mechanical manufacture as in the screw type (as in the helical type). In addition, the (rotary/volumetric) fluid machine may be manufactured only with the processing of circles and straight lines, so that the fluid machine may be mass-produced at a significantly low cost even when manufactured with high precision, and vibration may be eliminated or significantly reduced.

According to the present invention, the (rotary/volumetric) fluid machine configured to induce and form a volume change by interaction of the (rotary) cylinder and the rotary piston, which rotate only with complete circular motions, respectively, may have many advantages in which an operation of the complete circular motion alone may not cause a precessional motion or a reciprocating inertial change so as to have almost no vibration, there are no abrasion and friction losses caused by a high-pressure conversion fluid that applies pressure to a cylinder wall as in the reciprocating type, only the pure pressure of the high-pressure conversion fluid can be directly applied to the rotary piston so as to reduce abrasion and increase fluid energy conversion efficiency, a structure of a complete circle or a straight line can be provided in terms of mechanical mechanisms so as to facilitate high-precision manufacture at a low cost without requiring a separate special processing machine, and mass production can be facilitated in terms of engineering/commerce.

In addition, according to the fluid machine, the rotation ratio restraining device includes a gear.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an exploded perspective view showing a fluid machine including a cylinder formed/fixed to a housing according to a basic embodiment of the present invention.

FIG. 2 is a view showing an operation principle and an operation process of the fluid machine (including the fixed cylinder) according to the present invention.

FIG. 3 is a basic view for mathematically proving an operation principle process of the fluid machine (including the fixed cylinder) according to the present invention, in which

• • a rotary piston-rotation center C1 and a main shaft-rotation center C2 are spaced apart from each other by an eccentric interval d,
  • an eccentric distance r, which is an interval between a rotary piston-center C3 and the rotary piston-rotation center C1 and formed at the same interval, forms an isosceles with a (fixed) cylinder-center line S1 as a base during all operation processes, and when a rotary piston-rotation center (C1) angular velocity y and a main shaft-rotation center (C2) angular velocity x satisfy y:x=2:1, the view is a relation view for mathematically proving that the rotary piston-center C3 that rotates is always located to coincide with the (fixed) cylinder-center line S1.

FIG. 4 is a sectional view showing assembly of the fluid machine according to the present invention.

FIG. 5 is a perspective sectional view showing an assembled state of the fluid machine according to the present invention.

FIG. 6 is an exploded perspective view showing a fluid machine according to the present invention, which is an embodiment obtained by modifying the fluid machine in FIG. 1 to have more engineering and practical configurations, and includes a cylinder formed/fixed to a housing, a main shaft, a separate eccentric shaft, a separate rotation/revolution shaft, and a rotary piston.

FIG. 7 is a perspective view showing an assembled state of an exterior of the fluid machine according to the present invention in FIG. 6.

FIGS. 8(A) and 8(B) are perspective sectional views showing assembly of the fluid machine according to the present invention in FIG. 7.

FIG. 9 is a sectional view showing an assembled state of the fluid machine according to the present invention in FIG. 7.

FIG. 10 is a sectional view showing an example of a gear part of the fluid machine according to the present invention in FIG. 6, in which a rotation ratio restraining device configured to restrain the main shaft-rotation center (C2) angular velocity x and the rotary piston-rotation center (C1) angular velocity y to x:y=1:2 is configured as quaternary-stage gears.

FIG. 11 is a view showing the operation principle and the operation process of the fluid machine having the engineering and practical configurations (including the fixed cylinder) according to the present invention.

FIG. 12 is a view showing a fluid machine (including a fixed cylinder) configured in multiple stages to offset vibration according to the present invention.

FIG. 13 is an exploded perspective view showing a fluid machine according to an embodiment of the present invention, which includes a rotary cylinder that rotates (not a fixed cylinder), unlike in FIGS. 1 and 6.

FIG. 14 is a perspective view showing an assembled state of an exterior of the fluid machine according to the present invention.

FIG. 15 is a sectional view showing an example of a gear part of the fluid machine according to the present invention in FIG. 13, in which a rotation ratio restraining device configured to restrain a rotary cylinder-rotation center (C2) angular velocity x and a rotary piston-rotation center (C1) angular velocity y to x:y=1:2 is configured as seven quaternary-stage gears.

FIG. 16 is a view showing the fluid machine according to the present invention, in which an operation principle and an operation process of the fluid machine including a rotary cylinder that rotates (not a fixed cylinder), unlike in FIG. 2, are shown.

FIG. 17 is a basic view for mathematically proving an operation principle process of the fluid machine including the rotary cylinder according to the present invention, in which a rotary piston-rotation center C1 and a rotary cylinder-rotation center C2 are spaced apart from each other by an eccentric interval d, an eccentric distance r, which is an interval between a rotary piston-center C3 and the rotary piston-rotation center C1 and formed at the same interval, forms an isosceles with a rotary cylinder-operation center line S1 as a base during all operation processes, and when a rotary piston-rotation center (C1) angular velocity y and a main shaft-rotation center (C2) angular velocity x satisfy x:y=1:2, the view is a relation view for mathematically proving that the rotary piston-center C3 that rotates is always located to coincide with the rotary cylinder-operation center line S1.

FIG. 18 is an exploded perspective view showing a fluid machine according to the present invention, in which a pair, which includes a rotary cylinder and a rotary piston that rotate, is configured in multiple stages (e.g., x=0 degrees, 60 degrees, or 120 degrees, and y=2x=0 degrees, 120 degrees, or 240 degrees).

FIG. 19 is a view showing examples of a rotary cylinder (e.g., x=0, 60, or 120 degrees) arranged at different angles and a rotary piston (y=0, 120, or 240 degrees) arranged at different angles to correspond to the rotary cylinder so as to satisfy y=2x in FIG. 18.

FIG. 20 is a sectional view showing the pair, which includes the rotary cylinder and the rotary piston that rotate, according to the present invention.

FIG. 21 is a view for describing that when the rotary cylinder and the rotary piston, which rotate, according to the present invention are configured in one stage, a state in which power transmission is impossible (dead zone) occurs ((A) and (B)), and when the rotary cylinders and the rotary pistons are configured in multiple stages and mechanically connected to each other (cylinders are coupled integrally with each other, and rotary pistons are coupled to each other (C)), the rotary cylinders and the rotary pistons may operate as multiple inner gear teeth (the rotary cylinders) and multiple gear teeth (the rotary pistons) at 1:2 by the rotation ratio restraining device so that the rotary cylinder-rotary piston pair configured in the multiple stages may operate as gears (C) (D).

FIG. 22 is a view showing a fluid machine according to the present invention, which has a structure in which a cavity 10h is formed so that the center of gravity of the rotary piston of the fluid machine P may be located on a rotation shaft center.

FIG. 23 is a view showing a fluid machine according to the present invention, in which one fluid machine P may be coupled to an active machine (a motorizing device (a motor, an engine, etc.)), another fluid machine P may be coupled to a passive machine (a vehicle wheel, an aircraft rotor, etc.), and the fluid machines P connected to the active machine and the passive machine are connected by a working fluid-closed circuit (a pipe, a high-pressure hose, etc.), so that a rotation amount displacement and a torque amount displacement are generated between the active machine and the passive machine, or a valve SV is added to the working fluid-closed circuit so as to separately control the displacements.

FIG. 24 is a view showing a fluid machine according to the present invention, in which one fluid machine P may be coupled to an active machine (a motorizing device (a motor, an engine, etc.)), a multi-stage (P) fluid machine Pn formed by inserting multiple other fluid machines P configured in multiple stages into one housing and coupling one output rotation shaft to the multiple stages is provided, the fluid machine P and the multi-stage (P) fluid machine Pn are connected by a working fluid-closed circuit (a pipe, a high-pressure hose, etc.), and a plurality of valves SV configured to control a working fluid flow are added to the working fluid closed circuit in multi-stage connection, so that displacements of a rotation amount R2 and a torque amount with respect to a rotation amount R1 and a torque amount of the active machine (a motorizing device (a motor, an engine, etc.)) may be controlled at the output rotation shaft of the multi-stage (P) fluid machine Pn.

FIG. 25(A)-(C) is a set of views showing a mathematical input/output model of the fluid machine according to the present invention in FIG. 23, which is expressed by 2d*COS (F) and 2d*COS(F−90) (=2d*sin (F)) in a sectional view FIG. 25(A), a perspective view FIG. 25(B) showing an exterior, and a graph FIG. 25(C).

FIG. 25(A) is a view showing the fluid machine according to the present invention in FIGS. 23 and 24, in which 2d*COS (F) in the rotary cylinder-rotary piston pair of the fluid machine is shown.

FIG. 25(B) is a view showing the fluid machine according to the present invention in FIGS. 23 and 24, in which the fluid machine P is configured such that the rotary cylinder-rotary piston pair and another pair having a phase difference of 90 degrees therefrom and added thereto are inserted into one housing, and the pairs are connected by one shaft.

FIG. 25(C) is a graph showing the fluid machine according to the present invention in FIGS. 23 and 24, in which suction/discharge characteristics of the fluid machine P, which is (2d*COS(F)+2d*COS(F−90)), are shown.

FIGS. 26(A) and 26(B) are taken from the mathematical proof view showing one pair of the fluid machine according to the present invention in FIG. 3 and FIG. 17.

FIG. 26(C) is a view for mathematically proving that, for a distance displacement dPS between the rotary cylinder and the rotary piston (or a distance displacement between the cylinder and the rotary piston), a distance displacement (dPS) characteristic is proportional to COS (F) in the fluid machine according to the present invention in FIG. 23 and FIG. 24.

FIG. 26(D) is a view showing a total volume of suction/discharge in one-half cylinder of one pair during one stroke, which is calculated by the distance displacement dPS=2d*COS (F) derived from 26(C).

FIG. 27 is a view showing a state in which the fluid machine according to the present invention in FIG. 23 is applied to a vehicle.

FIG. 28 is a view showing an application example in which the fluid machine according to the present invention in FIG. 23 is applied to a drone so that the drone may fly by controlling four rotors with one motor without using four motorizing devices for the rotors, respectively.

FIG. 29 is a view showing an application example in which the fluid machine according to the present invention in FIG. 23 is applied to an aircraft rotor so that an aircraft may fly without a propeller shaft, a transmission gear, or the like that connects a main engine to a tail wing.

FIG. 30 is a view showing a state in which the fluid machine according to the present invention in FIG. 23 is applied to a ship. Conventionally, in order to connect a screw outside the ship to an engine inside the ship, a hole was drilled in a hull to connect the main shaft, so that there were many devices and risks to achieve waterproof against water introduced from an outside. The present invention provides an application example in which completely waterproof that allows power to be transmitted without drilling a shaft hole in a ship hull is achieved.

DETAILED DESCRIPTION OF THE INVENTION

To achieve the objects described above, according to the present invention, there is provided a fluid machine including:

• • a fixed cylinder formed in a main body housing;
  • a main shaft having a rotation center that coincides with an operation center of the cylinder;
  • a rotary piston-rotation shaft configured to rotate and revolve, the rotary piston-rotation shaft installed on one side of an inside of the main shaft, and configured to maintain an eccentric interval (d) from the main shaft;
  • a rotary piston having a center that is eccentric to the rotary piston-rotation shaft by a distance (r) that is equal to the eccentric interval (d) (d=r); and
  • a rotation ratio restraining device configured to restrain a rotation ratio of a main shaft rotational angular velocity (x) of and a rotary piston-rotation shaft rotational angular velocity (y) to 1:2.

The rotation ratio restraining device may include a gear.

The rotary piston is provided with a cavity on one side thereof having a large weight such that a center of gravity coincides with a rotation center, in order to eliminate vibration that is able to occur due to eccentric rotation.

In addition, to achieve the objects described above, according to the present invention, there is provided a fluid machine including:

• • a (fixed) cylinder (formed in a main body housing);
  • a main shaft having a rotation center that coincides with an operation center of the cylinder;
  • an eccentric shaft fixed to the main shaft, and configured to maintain and rotate at an eccentric interval (d) from the main shaft;
  • a rotation-revolution shaft configured to rotate and revolve on the eccentric shaft;
  • a rotary piston coupled integrally with the rotation-revolution shaft to rotate, and having a center that is eccentric to the rotation-revolution shaft by a distance (r) that is equal to the eccentric interval (d) (d=r); and
  • a rotation ratio restraining device configured to restrain a rotation ratio of a main shaft rotational angular velocity (x) and a rotary piston rotational angular velocity (y) to 1:2.

The rotation ratio restraining device may include a gear.

The rotation ratio restraining device may include:

• • a primary gear coupled to the main shaft, and configured to rotate in accordance with the main shaft;
    • a secondary planetary gear connected to the primary gear to rotate;
    • a tertiary gear inwardly connected to the secondary planetary gear, and configured to rotate so as to have a rotation center line that coincides with a rotation center line of the main shaft; and
    • a quaternary gear inwardly connected to the tertiary gear to rotate, installed on one side of the rotation-revolution shaft, and configured to rotate so as to coincide with a rotation center line of the rotary piston.

The rotary piston may be provided with a cavity on one side thereof having a large weight such that a center of gravity coincides with a rotation center, in order to eliminate vibration that is able to occur due to eccentric rotation.

In addition, to achieve the objects described above, according to the present invention, there is provided a fluid machine including:

• • a rotary cylinder;
  • a rotary piston eccentric so as to have a rotation center that maintains an eccentric interval (d) from a rotation center of the rotary cylinder, and having a center (a mechanical structural center) that is eccentric to the rotary piston by a distance (r) that is equal to the eccentric interval (d) (d=r); and
  • a rotation ratio restraining device configured to restrain a ratio of a rotary cylinder-rotational angular velocity (x) and a rotary piston-rotational angular velocity (y) to 1:2.

The rotation ratio restraining device may include a gear.

A plurality of pairs, each of which includes the rotary cylinder and the rotary piston, may be arranged in multiple stages, and

• • each of the stages may form the multiple stages such that a rotary cylinder center line (perpendicular to a rotation center line) and a rotary piston (mechanical circular) center may be located/arranged to allow a rotary piston-center-displacement angle (y) to be two times compared to a rotary cylinder-center line-displacement angle (x) (y=2x) based on one pair of reference points of 0 angle. (e.g., (x=0, y=0), (x=60, y=120), or (x=120, y=240))

The rotation ratio restraining device may be configured so as to be replaceable in multiple stages, in which

• • a plurality of pairs, each of which includes the rotary cylinder and the rotary piston, may be arranged in multiple stages,
  • (the pairs, each of which is configured such that a rotary piston-arrangement angle (y) is two times compared to a rotary cylinder-arrangement angle (x) (y=2x), may be arranged in the multiple stages at different angles),
  • so that the pairs, each of which includes the rotary cylinder and the rotary piston, may operate as if an inner gear having two gear teeth (the rotary cylinder) and a gear having one gear tooth (the rotary piston) operate with each other,
  • thereby restraining a rotation ratio to 1:2.

The rotary piston may be provided with a cavity on one side thereof having a large weight such that a center of gravity coincides with a rotation center, in order to eliminate vibration that is able to occur due to eccentric rotation.

In addition, to achieve the objects described above, according to the present invention, there is provided a fluid machine including:

• • a rotary cylinder;
  • a rotary piston eccentric so as to have a rotation center that maintains an eccentric interval (d) from a rotation center of the rotary cylinder, and having a center (a mechanical structural center) that is eccentric to the rotary piston by a distance (r) that is equal to the eccentric interval (d) (d=r);
  • a rotation ratio restraining device in which
    • two pairs, each of which includes the rotary cylinder and the rotary piston, are coupled into two stages,
    • one pair stage is configured such that a fluid output is proportional to COS(θ) based on a rotary cylinder angle of x=θ=0 and a piston angle of y=θ=0, another pair stage is configured such that, in order to displace a working fluid phase by +90 degrees, arrangement and coupling are performed to satisfy a cylinder angle of x=θ=±90 and a piston angle of y=2x=180, so that a fluid output is proportional to COS(θ−90) (or COS(θ±90)), and the rotation ratio restraining device is configured to restrain a ratio of a rotary cylinder-rotational angular velocity (x) and a rotary piston-rotational angular velocity (y) to 1:2; and
  • a fluid machine (P) formed by coupling the two pairs, which are the two stages, so that suction/discharge is configured as a direct current,
  • wherein one fluid machine (P) is coupled to an active machine (a motorizing device (a motor, an engine, etc.)),
  • another fluid machine (P) is coupled to a passive machine (a vehicle wheel, an aircraft rotor, etc.), and
  • the two fluid machines (P) connected to the active machine and the passive machine, respectively, are connected by a working fluid-closed circuit (a pipe, a high-pressure hose, etc.),
  • so that rotation amount/torque amount displacements are generated between the active machine and the passive machine.

A valve (SV) configured to control a working fluid flow may be added to the working fluid-closed circuit so that the rotation amount/torque amount displacements applied to each passive machine is able to be controlled.

The rotation ratio restraining device may include a gear.

The rotation ratio restraining device may be configured so as to be replaceable, in which a plurality of pairs, each of which includes the rotary cylinder and the rotary piston arranged at different angles, are arranged in multiple stages.

In addition, to achieve the objects described above, according to the present invention, there is provided a fluid machine including:

• • a rotary cylinder;
  • a rotary piston eccentric so as to have a rotation center that maintains an eccentric interval (d) from a rotation center of the rotary cylinder, and having a center that is eccentric to the rotary piston by a distance (r) that is equal to the eccentric interval (d) (d=r);
  • a rotation ratio restraining device in which
    • two pairs, each of which includes the rotary cylinder and the rotary piston, are coupled into two stages,
    • one pair stage is configured such that a fluid output is proportional to COS(θ) based on a cylinder angle of x=θ=0 and a piston angle of y=θ=0,
    • another pair stage is configured such that, in order to displace a working fluid phase by +90 degrees, arrangement and coupling are performed to satisfy a cylinder angle of x=0=+90 and a piston angle of y=2x=180, so that a fluid output is proportional to COS(θ−90) (or COS(θ+90)), and
    • the rotation ratio restraining device is configured to restrain a ratio of a rotary cylinder-rotational angular velocity (x) and a rotary piston-rotational angular velocity (y) to 1:2;
  • a fluid machine (P) formed by coupling the two pairs, which are the two stages, into one so that suction/discharge is configured as a direct current; and
  • a multi-stage fluid machine (Pn) formed by coupling fluid machines (P) in multiple stages (P*n) so that one output rotation shaft is formed in one housing,
  • wherein the fluid machine (P) is coupled to an active machine (a motorizing device (a motor, an engine, etc.)),
  • the fluid machine (P) and the multi-stage (P*n)-fluid machine are connected by a working fluid-closed circuit (a pipe, a high-pressure hose, etc.), and
  • a plurality of valves (SV*n) configured to control a working fluid flow of each stage, which is the multi-stage (Pn)-fluid machine, are added to the working fluid-closed circuit,
  • so that a rotation amount applied to an output rotation shaft of the multi-stage-fluid machine (Pn) from a rotation amount of an output shaft of the active machine and a torque amount are able to be displaced and controlled.

The rotation ratio restraining device may include a gear.

The rotation ratio restraining device may be configured so as to be replaceable, in which a plurality of pairs, each of which includes the rotary cylinder and the rotary piston arranged at different angles, are arranged in multiple stages.

Hereinafter, a fluid machine according to the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 is an exploded perspective view showing a fluid machine according to the present invention.

A main shaft 12 may be provided to rotate at an operation center of a (fixed) cylinder formed in a housing, and an eccentric shaft 11a (rotation/revolution-planetary shaft) may be provided inside the main shaft at a position that is eccentric by a distance d,

• • a rotary piston 10, which has a structural circular center that is eccentric from a rotation center by a distance r (=d), may rotate on the eccentric shaft, and
  • the eccentric shaft 11a and the main shaft 12 may be restrained to each other at 2:1 by a rotation ratio restraining device of an eccentric shaft gear 113g and a gear 311g formed to coincide with the rotation center of the main shaft.

In other words, a rotary piston-rotation center (C1) angular velocity y and a main shaft-rotation center (C2) angular velocity x may be restrained to a rotation ratio of y:x=2:1.

In this way, while all parts perform only a complete circular motion, a volume change as in a reciprocating piston-cylinder may be achieved, it may not be necessary to convert a circular motion into a linear motion as in a crank and a connecting rod, friction losses and abrasion caused by a piston sliding while applying a force to a cylinder wall during the conversion process may be eliminated, and vibration generation may be reduced. In addition, regarding a manufacturing process, since all components of the parts are in the form of circles and straight lines, manufacture may be achieved with high precision without the need of a dedicated machine for processing a complex structure as in the screw type, so that application to industries and mass production may be facilitated, and components and structures may be simplified further.

FIG. 2 is a view for describing an operation principle and an operation process of the fluid machine according to the present invention in FIG. 1, in which

one cycle may be completed through processes (a)-(h)-(a).

In processes (a)-(b), when the main shaft 12 rotates counterclockwise, the rotary piston may rotate clockwise due to the eccentric shaft gear 113g of the rotary piston 10, which is engaged with the gear 311g formed in the housing, by two times of an eccentric shaft rotation angle, and a (geometric circular) center C3 of the rotary piston may move to the right along a cylinder operation center line S1. This operation may cause expansion of a volume between the cylinder and the rotary piston, and fluid suction may begin into a vacuum space formed by the expansion.

Through processes (c)-(d), the suction may be completed at a process (e), in which

• • the main shaft has rotated 180 degrees counterclockwise, and
  • the rotary piston and the rotary piston shaft 11a have rotated and revolved 360 degrees (180*2) clockwise (at a rotation ratio (2:1) by the rotation ratio restraining device of the eccentric shaft gear 113g and the gear 311g) while revolving 180 degrees (counterclockwise-around a main shaft rotation center).

In processes (e)-(f), the rotary piston 10 that has passed a right peak of the cylinder may continue to rotate and revolve while the main shaft continues to rotate counterclockwise, so that the rotary piston 10 may begin to move to the left so as to enter a discharge process.

Through processes (g)-(h), the discharge process may be completed at the process (a), in which

• • the main shaft has rotated 360 degrees counterclockwise, and
  • the rotary piston and the rotary piston shaft 11a have rotated and revolved 720 degrees (360*2) clockwise (at the rotation ratio (2:1) by the rotation ratio restraining device of the eccentric shaft gear 113g and the gear 311g) while revolving 360 degrees (counterclockwise-around the main shaft rotation center), thereby completing one cycle.

FIG. 3 is a view for mathematically proving the operation process of FIG. 2, which describes mathematical proof that, since the main shaft and the rotary piston (which rotates and revolves about the main shaft) rotate at angular velocities x and y as shown in FIG. 2, respectively, and

• • the rotation of the main shaft and the rotary piston is restrained at the rotation ratio of 1:2=x:y by the rotation ratio restraining device of the gear 311g and the eccentric shaft gear 113g,
  • an eccentric center C3 of the rotary piston may be always located on a cylinder-center line S1.

In other words, in FIG. 3, since sum of internal angles of a triangle c1c2c3 is 180,

x + c + a = 1 ⁢ 8 ⁢ 0 ( Formula ⁢ 1 )

In this case, since a=(180−y),

x + c + ( 180 - y ) = 1 ⁢ 8 ⁢ 0 ( Formula ⁢ 2 )

When variables except y is moved to the right side,

y = x + c ( Formula ⁢ 3 )

In this case, since (an eccentric distance between a main shaft-rotation center C2 and a rotary piston-rotation center C1) d is designed to be equal to (a distance between the rotary piston-rotation center C1 and a rotary piston-center C3) r, d=r.

Therefore,

• • since the triangle clc2c3 is an isosceles triangle with d=r, an angle x=c.

Accordingly, in (Formula 3),

y = x + c = x + x = 2 ⁢ x ( Formula ⁢ 4 )

(In other words, when a state in which the angle x=c (“d=r”, since it is isosceles) and y=2x is restrained,

• • that is, the ratio is restrained to y:x=2:1, a point C3 may be always located to coincide with the cylinder-center line S1.)

In other words, as proven in (Formula 4),

• • when the main shaft 12 rotates at the angular velocity x at a point c2 (coinciding with a center of a cylinder 20f), and
  • while being spaced apart from the point c2 (main shaft rotation center) by the distance,
  • the eccentric shaft (the rotary piston-rotation center c1) rotates at the angular velocity y (=2x), which is two times the speed of the main shaft at the restrained ratio,
  • it is mathematically proven that the eccentric center c3 of the rotary piston 10 is always located to coincide with the cylinder-center line S1.

FIG. 4 is a sectional view showing an assembled state of a plane of the fluid machine according to the present invention in FIG. 1.

FIG. 5 is a perspective sectional view showing an assembled state of the fluid machine according to the present invention in FIG. 1. From the descriptions of FIG. 2 and FIG. 3, operation and coupling relation of the cylinder 20f, the rotary piston 10, the rotary piston shaft 11a, a cylinder housing side wall center gear 311g, and a rotary piston shaft gear 113g may be more clearly understood.

FIG. 6 is an exploded perspective view showing a fluid machine according to the present invention, in which the fluid machine, which has a basic principle structure in FIG. 1, is applied and made practical so as to give and receive a great force in terms of engineering, and operate smoothly with less abrasion. In addition, when configuring multiple stages, (since the fluid machine in FIG. 1 has a structure in which the main shaft may not penetrate into the rotary piston to move to a cylinder of a next stage because the rotary piston has to rotate and revolve on one side of the main shaft (a structure that is disadvantageous for forming multiple stages), and both the main shaft and the rotary piston shaft are supported on only one side, the structure has many shortcomings regarding transmission of a force, uneven abrasion, and the like in terms of engineering as compared with a structure that supports on both sides by bearings) the structure may be improved to enable a multi-stage configuration.

In other words, in FIG. 6, application and improvement of the fluid machine according to the present invention in FIG. 1 may be performed in terms of engineering,

• • such that an eccentric shaft 113c may be coupled to an outside of the main shaft 112 (as a crank structure), a rotation/revolution shaft 113p may rotate at an outside of the eccentric shaft 113c, and the rotary piston 10 may be formed integrally with the rotation/revolution shaft 113p to rotate, so that the main shaft 112 may penetrate both ends of the rotary piston 10 and penetrate both side walls of the cylinder housing so as to be supported with a bearing to rotate. (a structure that is easy to be configured in multiple stages for manufacture)

There may be an eccentric difference of a distance d between a rotation center of the main shaft 112 and a rotation center of the eccentric shaft 113c installed outside the shaft 112, there may be an eccentric difference of a distance r between a rotation center of the rotary piston 10 and a structural circular center C3 of the rotary piston 10, and the distances d and r have to be equal to each other to satisfy d=r.

(In other words, in the structure of FIG. 1, the rotation/revolution shaft, the rotary piston shaft, and the rotary piston may rotate inside the main shaft, so that the main shaft and the rotary piston shaft may be blocked from each other. Therefore, the main shaft and the rotary piston shaft may exist only on one side, and expansion to side walls of both side housings may be impossible (a structure that is difficult to be subjected to multi-stage expansion).)

A housing 30 in which the cylinder 20f is provided may be configured such that a side wall 301w coupled to a tertiary gear 43g to support the same, a side wall 31w coupled to a shaft 42s of a secondary planetary gear 42g and a main shaft bearing to support the same, and a bearing cover side wall 32w may be sequentially coupled, and suction/discharge ports 30a and 30b may be formed on a middle outer wall.

A quaternary gear 44g may be formed on both ends of the rotation/revolution shaft 113p, and the rotation/revolution shaft 113p may be coupled to the rotary piston 10 by a key 70 so as to rotate integrally with each other.

The rotation of the main shaft and the rotation of the rotary piston may be restrained to each other at a ratio of 1:2, and in the process thereof, a primary gear 41g may be coupled to one side of the main shaft 112, and a secondary gear 42g may be connected around the main shaft 112 as a planetary gear, an inner tertiary gear 43g may be connected to an upper portion of the secondary gear 42g so as to be supported by a bearing on the housing side wall to rotate, and the quaternary gear 44g of the rotation/revolution shaft may be connected to an opposite side of the tertiary gear 43g, so that the main shaft 112 and the rotary piston 10 coupled integrally with the rotation/revolution shaft 113p may be restrained to each other to rotate at the rotation ratio of 1:2 with respect to the main shaft (x:y=(main shaft rotation):(rotary piston rotation)).

In this way, in addition to advantages of the fluid machine according to the present invention in FIG. 1, additionally, a fluid machine that has superior durability, is easier to maintenance, more practical in terms of engineering, may be used for fluid conversion that requires a large force, and is configured in multiple stages to have larger scales may be applied.

FIG. 7 is a perspective view showing an assembled state of an exterior of the fluid machine according to the present invention in FIG. 6.

FIGS. 8(A) and 8(B) are perspective sectional views showing assembly of the fluid machine according to the present invention in FIG. 7.

FIG. 9 is a sectional view showing an assembled state of the fluid machine according to the present invention, in which mutual coupling relation between portions described in FIG. 6 may be better understood in more detail.

FIG. 10 is a view showing a rotation ratio restraining device of the fluid machine according to the present invention in FIG. 6, in which a connection process from the primary gear 41g to the secondary gear 42g, the tertiary gear 43g, and the quaternary gear 44g, which are configured as gears, is shown with respective sectional views so as to be easily understood. This is an example in which the rotation ratio restraining device configured to restrain the main shaft-rotation center (C2) angular velocity x and the rotary piston-rotation center (C1) angular velocity y to x:y=1:2 is configured as quaternary-stage gears.

FIG. 11 is a view showing the operation process of the fluid machine according to the present invention in FIG. 6.

One cycle may be completed through processes (a)-(b)-(c)-(d)-(a).

In the processes (a)-(b), when the main shaft 112 rotates clockwise, since the primary to quaternary gears 41g, 42g, 43g, and 44g are sequentially connected to each other, the rotary piston 10 rotate due may counterclockwise to a rotation/revolution shaft gear 44g coupled to the rotary piston by two times of an eccentric shaft rotation angle, and a (geometric circular) center C3 of the rotary piston may move to the right along a cylinder operation center line S1. This operation may cause expansion of a volume between the cylinder and the rotary piston, and fluid suction may begin into a vacuum space formed by the expansion.

Through the process (b), the suction may be completed at the process (c), in which

• • the main shaft has rotated 180 degrees clockwise, and
  • the rotary piston 10 has rotated and revolved 360 degrees (180*2) counterclockwise (at a rotation ratio (2:1) by the rotation ratio restraining device of the gears, which are the primary to quaternary gears 41g, 42g, 43g, and 44g that are sequentially connected to each other) while revolving 180 degrees (clockwise—around a main shaft rotation center).

In the process (c), the rotary piston 10 that has passed a right peak of the cylinder may continue to rotate and revolve while the main shaft 112 continues to rotate clockwise, so that the rotary piston 10 may begin to move to the left so as to enter a discharge process.

Through the process (c), the discharge process may be completed at the process (a), in which

• • the main shaft has rotated 360 degrees clockwise, and
  • the rotary piston 10 has rotated and revolved 720 degrees (360*2) counterclockwise (at the rotation ratio (2:1) by the rotation ratio restraining device of the primary to quaternary gears 41g, 42g, 43g, and 44g) while revolving 360 degrees (clockwise-around the main shaft rotation center), thereby completing one cycle.

FIG. 12 is a view showing an example of a fluid machine according to the present invention, in which the fluid machine according to the present invention in FIG. 6 is configured in multiple stages.

A total of four pairs, each of which includes the cylinder and the rotary piston, may be coupled to each other, thereby completing one multi-stage fluid machine. In this case, this is an example in which coupling directions of the rotary pistons are configured such that phases are aligned to allow movement directions of the rotary pistons to be opposite to each other, so that movement directions of two rotary pistons are 180 degrees opposite to movement directions of other two rotary pistons, thereby configuring one multi-stage fluid machine.

FIG. 13 is an exploded perspective view showing a fluid machine according to the present invention.

In other words, the same operation may be performed with a ‘rotary cylinder that rotates’ instead of the ‘main shaft that rotates’, unlike the (fixed) cylinder in FIG. 1 and FIG. 6.

In other words, a rotary cylinder 20 may be provided to coincide with an operation center so as to rotate, a main shaft 122 may be provided inside the rotary cylinder at a position that is eccentric by a distance d,

• • a rotary piston 10, which has a structural circular center that is eccentric from a rotation center by a distance r (=d), may rotate on the main shaft 122, and
  • mutual rotation ratio restraining relation between the rotary cylinder 20 and the rotary piston 10 may be configured such that
  • a gear 401g coupled to the main shaft 122 that is coupled to the rotary piston, a gear 402g connected to the gear 401g, a gear 403ga connected to the gear 402g, a gear 403gb coupled to one side of the same shaft as the gear 403ga, a gear 404ga connected to the gear 403gb, a gear 404gb coupled to one side of the same shaft as the gear 404ga and located on an opposite side of a gearbox, and a gear 405g connected to the gear 404gb and installed on one side of the rotary cylinder may be sequentially connected to each other so as to be restrained to each other at a rotation ratio of 1:2 (=x:y=(rotary cylinder rotation angle x):(rotary piston rotation angle y)).

In this way, while all parts perform only a complete circular motion, a volume change as in a reciprocating piston-cylinder may be achieved, it may not be necessary to convert a circular motion into a linear motion as in a crank and a connecting rod, friction losses and abrasion caused by a piston sliding while applying a force to a cylinder wall during the conversion process may be eliminated, and vibration generation may be eliminated. In addition, regarding a manufacturing process, since all components are configured in circles and straight lines, manufacture may be facilitated with high precision without the need of complex processing and a dedicated machine therefor as in the helical screw type, and components and structures may be simplified further.

FIG. 14 is a perspective view showing an assembled state of an exterior of the fluid machine according to the present invention in FIG. 13.

FIG. 15 is a sectional view showing a rotation ratio restraining device including seven quaternary-stage gears 401g, 402g, 403ga, 403gb, 404ga, and 404gb of the fluid machine according to the present invention in FIG. 13, which is shown in two partial sectional views interworking with each other.

FIG. 16 is a view for describing an operation principle and an operation process of the fluid machine according to the present invention in FIG. 13, in which one cycle may be completed through processes (a)-(h)-(a).

In processes (a)-(b), when the rotary piston 10 coupled to the main shaft 122 rotates clockwise, due to seven quaternary-stage gears 401g, 402g, 403ga, 403gb, 404ga, and 404gb configured as the rotation ratio restraining device, the rotary cylinder 20 may rotate clockwise by ½ times of a rotary piston rotation angle (where a rotary piston rotation angle y with respect to a rotary cylinder rotation angle x is two times (y=2x)), and a structural circular center C3 of the rotary piston may move along a cylinder operation center line S1, thereby widening a gap between the rotary cylinder and the rotary piston.

This operation may cause expansion of a volume between the rotary cylinder and the rotary piston, and fluid suction may begin into a vacuum space formed by the expansion.

Through processes (c)-(d), the suction may be completed at a process (e), in which

• • the rotary cylinder 20 has rotated 180 degrees clockwise (x), and
  • the rotary piston 10 has rotated 360 degrees (180*2) clockwise (y) (at a rotation ratio (1:2=x:y) by the rotation ratio restraining device).

In processes (e)-(f), as the rotary piston 10 continues to rotate clockwise, the gap between the rotary cylinder and the rotary piston may pass a maximum peak so as to narrow, so that fluid pressure may begin to increase so as to enter a discharge process.

Through processes (g)-(h), the discharge process may be completed at the process (a), in which

• • the rotary cylinder rotation angle x has rotated 360 degrees clockwise, and
  • the rotary piston rotation angle y has rotated 720 degrees (360*2) clockwise at the rotation ratio (1:2=x:y) by the mutually restrained rotation ratio restraining device, thereby completing one cycle.

FIG. 17 is a view for mathematically proving the operation process of FIG. 16, which describes mathematical proof that,

• • since the rotary cylinder 20 and the rotary piston 10 coupled to the main shaft 122 rotate at angular velocities x and y, respectively, and
  • the rotation of the rotary cylinder 20 and the rotary piston 10 is mutually restrained at 1:2=x:y by the rotation ratio restraining device,
  • a (mechanical structural) center C3 of the rotary piston may be always located on a rotary cylinder center line S1.

In other words, in FIG. 17, since sum of internal angles of a triangle c1c2c3 is 180,

x + c + a = 1 ⁢ 8 ⁢ 0 ( Formula ⁢ 1 )

In this case, since a=(180−y),

x + c + ( 1 ⁢ 8 ⁢ 0 - y ) = 1 ⁢ 8 ⁢ 0 ( Formula ⁢ 2 )

When variables except y is moved to the right side,

y = x + c ( Formula ⁢ 3 )

In this case, since (an eccentric distance between a rotary cylinder-rotation center C2 and a rotary piston-rotation center C1) d is designed to be equal to (a distance between the rotary piston-rotation center C1 and a rotary piston rotation center-mechanical center C3) r, d=r.

Therefore,

• • since the triangle c1c2c3 is an isosceles triangle with der, an angle x=c.

Accordingly, in (Formula 3),

y = x + c = x + x = 2 ⁢ x ( Formula ⁢ 4 )

(In other words, when a state in which the angle x=c (“d=r”, since it is isosceles) and y=2x is restrained,

• • that is, the ratio is restrained to (1:2=x:y), a point C3 may be always located to coincide with the rotary cylinder-center line S1.)

In other words, as proven in (Formula 4),

• • when the rotary cylinder 20 rotates at an angular velocity x at a point C2 (a rotation center of the rotary cylinder), and
  • while being spaced apart from the point C2 (the rotation center of the rotary cylinder) by the distance d,
  • the rotary piston-rotation center C1 is restrained to rotate at the angular velocity y (=2x), which is a rate that is two times a rotary cylinder rotational angular velocity x,
  • it is mathematically proven that
  • a geometric circular center C3 of the rotary piston 10 is always
  • located to coincide with the rotary cylinder-center line S1.

FIG. 18 and FIG. 19 are views showing examples in which the fluid machines according to the present invention in FIG. 13 and FIG. 17 are configured in multiple stages.

In order to configure the pair, which includes the rotary cylinder and the rotary piston, in multiple stages, when a next stage is set to an ‘arbitrary value x₁’, a value y₁ has to be set to ‘two times the arbitrary value x₁’ based on a reference pair (stage) of x=0 and y=0.

In other words, for example, in order to satisfy the operation principle of FIG. 17 upon operation, a reference first stage has to be x=0 and y=0, a next second stage has to be x=60 and y=2x=120, and a third stage has to be x=120 and y=2x=240.

FIG. 18 and FIG. 19 are views showing examples in which the fluid machines according to the present invention are configured in three stages.

FIG. 20 is a sectional view clearing showing a structure of one pair, which includes the rotary cylinder and the rotary piston that rotate, according to the present invention in FIG. 18.

FIG. 21 is a view showing that when the rotary cylinder and the rotary piston, which rotate, according to the present invention are configured in one stage, a dead zone in which power transmission is impossible occurs ((A) and (B)), and when the rotary cylinders and the rotary pistons are configured in multiple stages and mechanically connected to each other, the rotary cylinders and the rotary pistons may operate as multiple inner gear teeth (the rotary cylinders) and multiple gear teeth (the rotary pistons) at 1:2 by the rotation ratio restraining device so as to operate as gears (C) (D).

In other words, while there is no separate rotation ratio restraining device, in a case where the rotation is performed with only one pair, which includes the rotary cylinder and the rotary piston, as shown in FIG. 21(A), when only the rotary piston rotates even without the rotation ratio restraining device, a force of the rotary piston may be applied to a rotary cylinder wall at a positon of a state (A), so that the rotary cylinder may inevitably move and rotate to correspond to the rotary piston, and thus mutual transmission of rotational power may be possible.

However,

• • when the rotary piston rotates 180 degrees in the state (A) so as to “coincide with the rotation center of the rotary cylinder” as shown in FIG. 21(B), (the mutual transmission of rotational power is impossible (dead zone) and) the rotary cylinder has to theoretically rotate 90 degrees so as to reach a position Ob. However, in reality, since the rotary cylinder does not have a component that holds left and right rotation as in the state (A) (the rotary piston blocks a wall), the rotary cylinder may rotate 360 degrees, the rotary cylinder may be located in a deviating position such as Oa or Oc due to a manufacturing-precision-gap between the rotary cylinder and the rotary piston and due to different external forces and torques received by the rotary cylinder and the rotary piston, and when the rotary piston is forced to continue to rotate further, the fluid machine may be stopped, or the shaft may be broken.

However, when configured in multiple stages as shown in FIG. 21(C),

• • that is, when a plurality of pairs, each of which includes the rotary cylinder and the rotary piston and is configured such that a rotary piston-arrangement angle y is two time compared to a rotary cylinder-arrangement angle x (y=2x), are arranged in multiple stages at different angles, the rotary cylinders are connected integrally with each other, and the rotary pistons are mechanically connected integrally with a rotary piston-shaft,
  • since the rotary cylinders connected in all three stages and the rotary pistons connected in all three stages
  • are configured such that even when one of the three stage pairs is under a condition where “the rotary piston coincides with a rotary cylinder rotation center” as in a state (B), the remaining two pairs may continuously perform the mutual transmission of rotational power because the rotary cylinder wall is located at a position where the rotary cylinder wall holds the rotary piston.

In other words, as shown in FIG. 21(D), while one rotary cylinder operates as two inner gear teeth, and

• • one rotary piston operates as one gear tooth,
  • when the rotary cylinder and the rotary piston are arranged in multiple stages, the rotary cylinders and the rotary pistons may operate as multiple inner gear teeth and multiple gear teeth at 1:2 by the rotation ratio restraining device so as to operate to replace gears.

(However, when the gears are not separately mounted as the rotation ratio restraining device having the ratio of 1:2, abrasion losses caused by friction may occur more during a process of transmitting rotational forces and torques between the rotary cylinder and the rotary piston.)

FIG. 22 is a view showing a rotary piston of a fluid machine according to the present invention, in which the rotary piston is structured to rotate eccentrically, so that large vibration may be generated upon high-speed rotation. Therefore, according to the present invention, the fluid machine may have a structure in which a cavity 10h is formed so that the center of gravity of the rotary piston is located on a rotation center, so that the rotation center and the center of gravity of the rotary piston may coincide with each other even upon the high-speed rotation, and thus vibration may not be generated.

FIG. 23 is a view showing a fluid machine according to the present invention, in which the fluid machine in FIG. 6 and FIG. 13 may be coupled in two stages such that: one stage may be set as a reference with a cylinder angle of x=θ=0 and a piston angle of y=θ=0 so as to allow a fluid output to be proportional to COS(θ); another stage may be coupled with a cylinder angle of x=θ=±90 and a piston angle y=2x=180 so as to allow a fluid output to be proportional to COS(θ−90) in order to displace a working fluid phase by ±90 degrees; the two pairs (stages) may be integrated and coupled in one housing so that a suction/discharge amount may be proportional to Cos(θ)+COS(θ−90)=COS(θ)+SIN(θ) (=COS(θ)+COS(θ+90)) so as to be configured as a direct current that is constant as compared with a rotation displacement; a fluid machine P configured to suck/discharge a working fluid may be coupled to an active machine (a motorizing device (a motor, an engine, etc.)); another fluid machine P may be coupled to a passive machine (a vehicle wheel, an aircraft rotor, etc.); and the two fluid machines P may be connected by a working fluid-closed circuit (a pipe, a high-pressure hose, etc.), or a valve SV configured to control a flow of the working fluid may be added to the working fluid-closed circuit, so that a rotation amount displacement and a torque amount displacement of the passive machine may be controlled by using a rotation amount and a torque of the active machine.

In other words, this is a fluid machine capable of transmitting an output rotational force that is output from an engine to a wheel without a propeller shaft, a differential gear, a transmission, or the like with a displaced rotation amount and a displaced torque.

In this way, mechanical portions that connect power between a vehicle engine and a wheel (or an aircraft engine and a rotor), such as a propeller shaft or a differential gear, may not be necessary, so that weights of a vehicle and an aircraft due to many mechanical components may be reduced, and costs and maintenance costs may be saved.

FIG. 24 is a view showing a fluid machine according to the present invention, in which the fluid machine in FIG. 6 and FIG. 13 may be coupled in two stages such that: one stage may be set as a reference with a cylinder angle of x=θ=0 and a piston angle of y=θ=0 so as to allow a fluid output to be proportional to COS(θ);

• • another stage may be coupled with a cylinder angle of x=θ=±90 and a piston angle y=2x=180 so as to allow a fluid output to be proportional to COS(θ−90) in order to displace a working fluid phase by ±90 degrees; the two pairs (stages) may be integrated and coupled in one housing so that a suction/discharge amount may be proportional to COS(θ)±COS(θ−90)=COS(θ)+SIN(θ) (=COS(θ)+COS(θ+90)) so as to be configured as a direct current that is constant as compared with a rotation displacement; a fluid machine P configured to suck/discharge a working fluid
  • may be coupled to an active machine (a motorizing device (a motor, an engine, etc.));
  • another multi-stage fluid machine Pn (the view shows an example of six stages) (the fluid machine Pn formed by coupling n fluid machines P to integrate into one) may be provided; and
  • the fluid machine P and the fluid machine Pn may be connected by a working fluid-closed circuit (a pipe, a high-pressure hose, etc.) and control valves SV1 to SV6 to SVn,
  • so that a rotation amount/torque amount R1 of the fluid machine P coupled to the active machine
  • may be displaced into a rotation displacement/torque displacement R2 of the fluid machine Pn integrated in multiple stages.

In other words, this is a fluid machine in which if the fluid machine P and one pair stage P inside the fluid machine Pn integrated in multiple stages have the same size and capacity, when only the valve SV1 is turned on (open) while the remaining valves are turned off (close), R2 with respect to a rotation displacement R1 may be 1/1*R1 (=R2=1/1*R1),

• • when the valves SV1 and SV2 are turned on (open) while the remaining valves are turned off (close), R2 with respect to the rotation displacement R1 may be ½*R1 (=R2=½*R1),
  • . . . , . . . , when all the valves SV1 to SV6 are turned on (open), R2 with respect to the rotation displacement R1 may be ⅙*R1 (=R2=⅙*R1),
  • . . . , . . . , when all the valves SV1 to SVn are turned on (open), R2 is 1/n*R1 (=R2=⅙*R1) compared to the rotation displacement R1 may be 1/n*R1 (=R2=1/n*R1),
  • so that a rotation amount and a torque amount may be displaced from the rotation amount R1 of the active machine to the rotation displacement R2 (in n=6 stages in the example of the view).

FIGS. 25 and 26 are shown to mathematically prove the fluid machine P that produces a constant output (±)P V as a direct current in comparison with a rotation shaft displacement angle in FIGS. 23 and 24.

In other words, a stroke distance of the rotary cylinder and the rotary piston as in FIG. 25(A) may be 2d*COS(θ) (=dPS).

The reason is that:

FIGS. 26(A) and 26(B) are portions of FIG. 3 and FIG. 17, respectively, and when the views are integrated into FIG. 26(C) and observed upright,

(Process 1)

• • when a vertical line that divides a line segment c2c3 in the middle into half at a right angle is drawn in the middle of the isosceles triangle c1c2c3, a right-angled triangle c1c2c4 may be created; and

(Process 2)

• • in this case, a length of a bottom of the right-angled triangle c1c2c4 may be

d * COS ⁢ ( x ) , ( 1 )

• • since a total stroke distance dPS is two times the line segment c2c4 in the above formula (1),

dPS = 2 * d * COS ⁢ ( x ) . ( 2 )

As shown in FIG. 26(D), an inner volume of one-half cylinder of one stage in FIG. 25(A) may be

one ⁢ stroke ⁢ total ⁢ capacity = [ 2 * d * COS ⁢ ( x ) ] * Pw * Pd . ( 3 )

In addition, when another stage (a pair including a rotary cylinder and a rotary piston) that is displaced by −90 degrees is added,

two ⁢ stage ⁢ stroke ⁢ total ⁢ ⁢ capacity = [ 2 * d * COS ⁢ ( x ) ] * Pw * Pd + [ 2 * d * COS ⁡ ( x - 90 ) ] * Pw * Pd ( 4 ) = [ 2 * d * { COS ⁡ ( x ) + COS ⁡ ( x - 90 ) } ] * Pw * Pd ( 5 ) = [ 2 * d * { COS ⁡ ( x ) + SIN ⁡ ( x ) } ] * Pw * Pd ( 6 ) = 2 * d * Pw * Pd . ( 7 )

In other words, the fluid machine of FIG. 25(B) (suction/discharge is proportional to COS(θ)+COS(θ−90) formed by coupling two fluid machines of FIG. 25(A) (suction/discharge is proportional to COS(θ)) with a phase displacement may be a fluid machine P having a direct-current-like working fluid suction/discharge characteristic without sine waves or pulsations as in FIG. 25(C).

FIG. 27 is a view showing a state in which the fluid machine according to the present invention in FIG. 23 is applied to a vehicle.

FIG. 28 is a view showing a state in which the fluid machine according to the present invention in FIG. 23 is applied to a drone so that the drone may fly by controlling four rotors with one motor without using four motorizing devices (motors, engines, etc.) for the rotors, respectively.

FIG. 29 is a view showing a state in which in which the fluid machine according to the present invention in FIG. 23 is applied to an aircraft rotor so that an aircraft may fly without a propeller shaft, a transmission gear, or the like that connects a main engine to a tail wing.

FIG. 30 is a view showing a state in which the fluid machine according to the present invention in FIG. 23 is applied to a ship. Until now, in order to connect a screw outside the ship to an engine, a hole was drilled in a hull to connect the main shaft, so that there were many mechanical components and costs to achieve waterproof against water introduced from an outside and perform maintenance. However, when the fluid machine according to the present invention is applied, power transmission may be performed by a screw without drilling a main shaft hole in a ship hull, and many waterproof mechanical components and maintenance costs may be reduced.

(Regarding the law of universal gravitation of Newton, many scientists knew through experiments, such as the ‘Leaning Tower of Pisa’ experiment, that all objects (mass m1) fall to the surface of the Earth at 9.8 m/sec² even before Newton. However, Newton created a formula (G·m1·m2/r²) that is proportional to the mass of the Earth (m2) and the mass of a falling object (m1), and inversely proportional to the square of a distance between the center of mass of the Earth and the center of mass of the falling object (r²), and mathematically proved that this applies all celestial bodies as well as objects on the ground of the Earth. Accordingly, the statement “the Earth revolves around the Sun” of Galileo was also proven.)

DESCRIPTION OF REFERENCE NUMERALS

• • 10: Rotary piston 10h: Rotary piston center-of-gravity adjustment cavity
  • 11: Rotary piston shaft
  • 11a: Planetary rotary piston eccentric shaft 11j: Rotary piston shaft spline
  • 12: Main shaft (eccentric-planetary rotary piston eccentric shaft formed in inside thereof)
  • 112: Main shaft (eccentric shaft coupled to outside thereof)
  • 122: Main shaft (rotary piston rotation shaft)
  • 112h: Hole in which main shaft is to be inserted into rotary piston
  • 112g, 113g: Rotary piston shaft gear (gear ratio 1:)
  • 113c: Eccentric shaft (similar to crankshaft)
  • 113p: Rotation/revolution shaft
  • 20: Rotary cylinder 21: Rotary cylinder side wall
  • 21s: Rotary cylinder shaft
  • 20i: Rotary cylinder inner/outer opening (inlet/outlet)
  • 20f: Cylinder (formed/fixed to main body housing)
  • 213b, 113b, 302b, 312b, 311b: Bearing
  • 213s: Rotary cylinder side wall inner shaft
  • 211g, 311g: Cylinder gear (gear ratio 2:)
  • 30: Main body housing 30c: Main body housing combustion chamber (high pressure)
  • 30h: Main body housing side wall rotary cylinder support hole
  • 30w, 301w: Main body housing side wall
  • 30h: Main body housing side wall tertiary gear rotation shaft bearing support hole
  • 30a: Suction port (inlet) 30b: Discharge port (outlet)
  • 30gb: Main body housing gearbox
  • 301h, 302h: Fluid induction path side wall groove
  • 31c: Main body housing side wall extension part
  • 31, 31a, 31b: Main body housing side wall
  • 31w: Main shaft and planetary gear bearing shaft support main body housing side wall
  • 32w: Main shaft bearing cover main body housing side wall
  • 31h: Planetary gear bearing shaft support hole
  • 311c: Inner bearing attachment part between main body housing and rotary piston shaft
  • 312c: Outer bearing attachment part between main body housing and rotary cylinder
  • 401g, 402g, 403ga, 403gb, 404ga, 404gb, 405g: Gear
  • 41g: Primary gear 42g: Secondary gear 43g: Tertiary gear 44g: Quaternary gear
  • 42s: Planetary gear shaft
  • 60: O-ring 61: Oil seal
  • 70: Key 71: Key groove
  • 90, 90a, 90b, 90c: Bolt
  • S1: Cylinder-center line c1: Rotation center of rotary piston shaft
  • C2: Rotary cylinder-rotation center, Main shaft rotation center (coinciding with cylinder center)
  • C3: Eccentric center of rotary piston Cv: Check valve
  • d: Distance between main shaft rotation center and eccentric shaft rotation center
  • dPS: Distance by which rotary piston moves within cylinder
  • r: Distance between eccentric shaft rotation center and rotary piston center
  • Oa, Oc: Rotary cylinder position where mismatch (if there are no gears engaged each other in 2:1, when rotary piston comes to cylinder rotation center position, wrong rotation difference that rotary cylinder may come to any position due to manufacturing precision gap or difference in two rotational forces) occurs
  • Ob: Ideal rotary cylinder position
  • M, E: Active machine (motorizing device (motor, engine, etc.)) Mc: Rotary piston center-of-gravity
  • P: Fluid machine (P) in which two pairs of fluid machines (two pairs of rotary cylinder-rotary piston arranged with a 90-degree phase difference (2d*COS(θ)+2d*COS(θ−90))) are coupled to have direct-current suction/discharge characteristic
  • Pn: Fluid machine (Pn) formed by coupling fluid machines in multiple stages
  • P1, P2: Suction/discharge amount of one fluid machine PV: Suction/discharge amount of two fluid machines
  • PW: Width of one stroke space of one fluid machine
  • Pd: Thickness of one stroke space of one fluid machine
  • R1: Displacement of output rotation shaft of fluid machine
  • (P) coupled to active machine
  • R2: Displacement of output rotation shaft of multi-stage fluid machine (Pn)
  • SV, SV1, SV2, SV3, SV4, SV5, SV6: Fluid flow control valve
  • Wh: Active machine (vehicle wheel, drone propeller, etc.)