Fluid machinery

Abstract

This invention provides a fluid machine (positive displacement, rotary type) that is extremely easy to manufacture with high precision, can be produced using only circular and straight line machining, can be mass-produced at a significantly lower cost even with high precision, and exhibits little to no vibration. [Solution] The fluid machine consists of a main shaft having a rotation center that coincides with the operating center of the cylinder, an eccentric shaft fixed to the main shaft and rotating at an eccentric interval, a rotation and revolution axis that rotates while rotating and revolving on the eccentric shaft, a rotary piston 10 whose center is eccentric by the same distance as the eccentric interval and which is coupled with and rotates as an integrated unit with the rotation and revolution axis, and a rotation ratio constraint means that constrains the ratio of the rotation angular velocity x of the main shaft and the rotation angular velocity y of the rotary piston to 1:2. As a result, a volume change is induced and formed by the interaction of the cylinder and the rotary piston 10, which each rotate only in perfect circular motion.

Description

Technical Field

[0001] The present invention relates to fluid machinery. More specifically, it relates to a fluid machinery without vibration like a universal reciprocating fluid machinery, where the force of high-pressure fluid does not generate a force that causes the piston to wear the wall surface of the cylinder like a reciprocating fluid machinery. With a structure that is relatively easy to process, precise, and simple to manufacture even during mass production, the manufacturing cost is significantly reduced. It relates to a (rotary) fluid machinery that causes a volume change only by the mutual rotational movement of a (rotary) cylinder and a rotary piston (positive displacement, rotary type).

Background Art

[0002] Conventional and widely used fluid machinery mainly includes those based on the reciprocation of pistons, or those based on gears, screws, or other various rotary types.

[0003] Due to past technological advancements, from the most advanced and mass-produced state of rotary fluid machinery, the Wankel rotary type lacks durability due to sealing and wear, and despite 70 years of arduous efforts, it failed in mass production in universal market applications such as automobiles and ships. Also, the screw type was limited to air compression and was successful, but the manufacturing cost was very high, several times higher than the most common reciprocating fluid machinery, and there were limitations in terms of whether it could be applied as a technology to prime movers or torque converters or not. In addition, technologies for various other rotary fluid machineries have been proposed, but there have been no examples that satisfy the efficiency, durability, and low cost that exceed those of conventional reciprocating and screw types and have been successful in mass production in the universal market.

Summary of the Invention

Problems to be Solved by the Invention

[0004] Conventional piston-driven, gear-driven, and screw-driven systems are universally mass-produced. However, reciprocating systems suffer from vibration and noise, and structurally, the force generated by the high-pressure fluid also acts as a force applied by the piston to the side wall of the cylinder, resulting in a lot of friction and wear. Gear-driven systems have difficulties in achieving the high precision required to maintain airtightness of the gear curved surface, and if high precision is not achieved, high pressure may not be properly formed in a sealed environment. Screw-driven systems have the difficulty of being manufactured with high precision to maintain airtightness of the helical curved surface, resulting in high manufacturing costs.

[0005] Furthermore, while there were patents for rotary systems in terms of mechanism and principle, there were no commercially successful rotary engines that were well-engineered, easy to maintain, and fully durable. There were also no other lesser-known rotary or positive displacement fluid machines, and they were either impossible to engineer or actually work, among other problems. [Means for solving the problem]

[0006] The present invention aims to solve the aforementioned problems. Components in which the operating part performs only perfect circular motion, and The system consists of a cylinder, a main shaft having a rotation center that coincides with its operating center, a rotary piston-rotation axis placed on one side inside the cylinder (rotating and revolving) while maintaining an eccentricity d, a rotary piston whose center is eccentric by the same distance r (d=r) as the eccentricity d, and a rotation ratio constraint means that constrains the ratio of the rotational angular velocity x of the main shaft and the rotational angular velocity y of the rotary piston rotation axis to 1:2. The (rotary) cylinder and the rotary piston, which only performs perfect circular motion, are configured to generate a volume change through their interaction. This can be proven mathematically, This is then engineered and constructed into mechanical parts that are actually functional. Despite the high-pressure compressed fluid, the high-pressure force is not applied to the frictional parts between the (rotary) cylinder and rotary piston. Structurally, the multi-stage cylinders and pistons are assembled as a single unit, or designed to be a single unit, like a cylindrical rotating shaft, so that despite the multiple stages, each stage is constrained by a rotational ratio when rotating relative to the others. Furthermore, by arranging the rotary cylinder to satisfy angular velocity x and the rotary piston to angular velocity (y=2x), it is possible to freely construct multiple stages at all angles (e.g., 0 degrees, 60 degrees, 120 degrees, etc.). Furthermore, the objective is to provide a fluid machine in which the structure of the multi-stage (rotary) cylinder and rotary piston is such that all centers of gravity are always at the center of rotation, like a cylindrical rotating axis, thereby preventing vibrations such as precession and reciprocating vibrations like those of reciprocating pistons and connecting rods. The mechanical mechanism is in the form of perfect circles and straight lines, making it very easy to manufacture with high precision mechanical ease, unlike screw-type (or helical) fluid machines. Moreover, it can be manufactured using only circular and straight line processing, and even with high precision manufacturing, it can be mass-produced at a significantly lower cost, and the objective is to provide a (rotary, positive displacement) fluid machine with no vibration or significantly reduced vibration. [Effects of the Invention]

[0007] According to the present invention, a rotary positive displacement fluid machine is provided that induces and forms a volume change through the interaction of a rotary cylinder and a rotary piston, each rotating solely in perfect circular motion. Because it operates solely in perfect circular motion and does not generate precession or reciprocating inertial changes, it has virtually no vibration. Unlike reciprocating systems, there is no wear and friction loss caused by the high-pressure conversion fluid applying pressure to the cylinder wall. Only the pure pressure of the high-pressure conversion fluid is directly applied to the rotary piston, resulting in less wear and high fluid energy conversion efficiency. Furthermore, because the mechanical mechanism is a perfectly circular or linear structure, it can be easily manufactured with high precision at low cost, does not require separate special processing machinery, and is easy to mass-produce both from an engineering and commercial standpoint, among other advantages. [Brief explanation of the drawing]

[0008] [Figure 1]An exploded perspective view of a basic embodiment of a fluid machine comprising a cylinder formed and fixed in a housing according to the present invention. [Figure 2] A diagram illustrating the operating principle and process of a fluid machine (consisting of a fixed cylinder) according to the present invention. [Figure 3] This is a basic diagram for mathematically proving the operating principle of a fluid machine (consisting of a fixed cylinder) according to the present invention, in which the rotary piston-rotation center C1 and the main shaft-rotation center C2 are separated by an eccentricity d, and the distance between the rotary piston-center C3 and the rotary piston-rotation center C1, the eccentric distance r, which is formed at the same distance, is an isosceles side with the (fixed) cylinder-center line S1 as the base throughout the entire operating process, and when the angular velocity y of the rotary piston-rotation center C1 and the angular velocity x of the main shaft-rotation center C2 are y:x=2:1, the rotating rotary piston-center C3 is always located on the (fixed) cylinder-center line S1, as shown in the diagram for mathematical proof. [Figure 4] Assembly cross-sectional view of the fluid machine according to the present invention. [Figure 5] An assembled perspective cross-sectional view of the fluid machine according to the present invention. [Figure 6] An exploded perspective view of a fluid machine according to the present invention, which is an embodiment of the fluid machine shown in Figure 1 that is further modified for engineering and practical purposes, comprising a cylinder and main shaft formed and fixed in a housing, a separate eccentric shaft and rotation / revolution shaft, and a rotary piston. [Figure 7] An assembled external perspective view of the fluid machine shown in Figure 6 according to the present invention. [Figure 8] Figure 7 shows an assembled perspective cross-sectional view of the fluid machine according to the present invention. [Figure 9] A cross-sectional view of the assembled fluid machine shown in Figure 7 according to the present invention. [Figure 10] Figure 6 is a cross-sectional view of the gear section of a fluid machine according to the present invention, in which a rotation ratio constraint means is configured with a fourth-stage gear so that the main shaft - rotation center C2, angular velocity x and the rotary piston - rotation center C1, angular velocity y are constrained to x:y=1:2. [Figure 11]Operating principle and operating process diagram of an engineering and practical fluid machine (consisting of a fixed cylinder) according to the present invention. [Figure 12] A fluid machine according to the present invention, configured in multiple stages (consisting of fixed cylinders) to cancel out vibrations. [Figure 13] An exploded perspective view of an embodiment of the fluid machine according to the present invention, which, unlike Figures 1 and 6, consists of a rotating rotary cylinder (not a fixed cylinder). [Figure 14] An assembled external perspective view of the fluid machine according to the present invention. [Figure 15] Figure 13 is a cross-sectional view of the gear section of a fluid machine according to the present invention, in which a rotation ratio constraint means is configured with a 7th order 4-stage gear so that the rotation ratio constraint means for the rotary cylinder (rotation center C2, angular velocity x) and the rotary piston (rotation center C1, angular velocity y) are constrained to x:y=1:2. [Figure 16] The operating principle and operating process of a fluid machine according to the present invention, which, unlike the one in Figure 2, consists of a rotating rotary cylinder (not a fixed cylinder). [Figure 17] A basic diagram for mathematically proving the operating principle and process of a fluid machine consisting of a rotary cylinder according to the present invention, wherein the rotary piston-rotation center C1 and the rotary cylinder-rotation center C2 are separated by an eccentric distance d, and the distance between the rotary piston-center C3 and the rotary piston-rotation center C1, which are formed at the same distance, is an isosceles line with the rotary cylinder-operation center line S1 as the base throughout the entire operating process, and the relationship diagram for mathematically proving that when the angular velocity y of the rotary piston-rotation center C1 and the angular velocity x of the main shaft-rotation center C2 are x:y=1:2, the rotating rotary piston-center C3 is always located on the rotary cylinder-operation center line S1. [Figure 18] An exploded perspective view of a fluid machine according to the present invention, in which a rotating rotary cylinder and rotary piston pair are configured in multiple stages [ex) x=0 degrees, 60 degrees, 120 degrees, y=2x=0 degrees, 120 degrees, 240 degrees]. [Figure 19]In Fig. 18, an example of rotary cylinders arranged at different angles from each other (for example, x = 0, 60, 120 degrees), and accordingly, an example of rotary pistons arranged at different angles with y = 2x (y = 0, 120, 240 degrees). [Figure 20] Cross-sectional view of a rotating rotary cylinder and a rotary piston pair according to the present invention. [Figure 21] When the rotating rotary cylinder and the rotary piston according to the present invention are configured in one stage, a state where power transmission is impossible (dead zone) occurs (A) to (B). When configured in multiple stages and mechanically connected to each other [the cylinders are integrally coupled to each other, and the rotary pistons are coupled to each other (C)], they operate like a plurality of inner gear teeth (rotary cylinder) and a plurality of gear teeth (rotary piston), and with a 1:2 rotation ratio restraint means, it is explained that the multi-stage configured rotary cylinder - rotary piston pair can operate with a gear (c) (D). [Figure 22] A fluid machine according to the present invention, having a structure in which a cavity 10h is formed such that the center of gravity of the rotary piston is located on the center of the rotation axis. [Figure 23] A fluid machine according to the present invention, capable of coupling one fluid machine P to a power machine (prime mover (motor, engine, etc.)), and also capable of coupling another fluid machine P to a manual machine (automobile tire, aircraft rotor, etc.). The fluid machines P connected to the power and manual machines are connected by a working fluid - closed circuit (pipe, high pressure hose, etc.) to generate a rotational displacement and a torque displacement between the two power machines and the manual machine, or a valve SV is added to the working fluid - closed circuit so that the displacement amounts can be controlled separately. [Figure 24]A fluid machine according to the present invention is configured such that one fluid machine P can be coupled to a prime mover (a motor, an engine, etc.), and a plurality of other fluid machines P, or a multi-stage configuration, are placed in one housing, and a multi-stage (P) fluid machine Pn is formed by coupling one output rotating shaft in multiple stages. 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.). A plurality of valves SV for controlling the flow of the working fluid are added to the working fluid closed circuit for multi-stage connection, so that the rotation amount R1 and torque amount of the prime mover (a motor, an engine, etc.) can be controlled by the output rotating shaft of the multi-stage (P) fluid machine Pn with a rotation amount R2 and torque amount displacement. [Figure 25] In FIG. 23, the mathematical input-output model of the fluid machine according to the present invention is represented by the cross-sectional view (A), the external perspective view (B) of the fluid machine, and the graph (C) with 2d*COS(F) and 2d*COS(F - 90)[=2d*sin(F)]. (A) is the fluid machine of the present invention in FIGS. 23 and 24, which is a 2d*COS(F) fluid machine with a pair of rotary cylinders - rotary pistons. (B) is the fluid machine of the present invention in FIGS. 23 and 24. A pair of rotary cylinders - rotary pistons and another pair with a 90-degree phase difference compared to it are added and placed in one housing, and it is a fluid machine P connected to one shaft. (C) is the graph showing the suction and discharge characteristics [2d*COS(F)+2d*COS(F - 90)] of the fluid machine P of the present invention in FIGS. 23 and 24. [Figure 26] (A) and (B) are shown in the mathematical proof diagrams of a pair of fluid machines according to the present invention in FIGS. 3 and 17. (C) is the fluid machine of the present invention in FIGS. 23 and 24, and it is a diagram for mathematically proving that the distance displacement characteristic is proportional to COS(F) with respect to the distance displacement dPS [or the distance displacement between the cylinder and the rotary piston] between each rotary cylinder and the rotary piston. (D) is a diagram showing the total volume sucked and discharged by one pair in a half cylinder during one stroke with the distance displacement dPS = 2d*COS(F) derived in (C). [Figure 27] A diagram of applying the fluid machine according to the present invention in FIG. 23 to an automobile. [Figure 28]Figure 23 shows an example of applying the fluid machine according to the present invention to a drone, enabling flight by controlling four rotors with a single prime mover instead of using four prime movers for each rotor. [Figure 29] Figure 23 shows an application example of the fluid machine according to the present invention applied to an aircraft rotor, enabling flight without a propeller shaft connecting the main engine to the tail fin, or a transmission gear. [Figure 30] The fluid machinery according to the present invention, shown in Figure 23, is applied to ships. Conventionally, to connect the external propeller to the internal engine of a ship, holes are drilled in the hull to connect the main shaft, which necessitates many devices and poses risks to waterproof against water entering from the outside. According to the present invention, power is transmitted without drilling shaft holes in the ship's hull, resulting in a completely waterproof application. [Modes for carrying out the invention]

[0009] The present invention, in order to achieve the aforementioned objectives, A fixed cylinder formed in the main housing, A main shaft having a rotation center that coincides with the operating center of the cylinder, A rotary piston-rotating shaft is provided on one side inside the main shaft and rotates and revolves while maintaining an eccentric distance d on the main shaft. The rotary piston - a rotary piston whose (mechanically geometric) center is eccentric by a distance r (d=r) equal to the eccentricity interval d on the axis of rotation, and The system is characterized by being configured with a rotation ratio constraint means that constrains the ratio of the main shaft rotation angular velocity x to the rotary piston-rotation shaft rotation angular velocity y to 1:2.

[0010] The rotation ratio constraint means is characterized by being composed of a gear.

[0011] The rotary piston is characterized by having a cavity on the heavier side to eliminate vibrations that may occur due to eccentric rotation, so that the center of gravity coincides with the center of rotation.

[0012] Furthermore, the present invention, in order to achieve the above-mentioned objectives, A fixed cylinder formed in the main housing, A main shaft having a rotation center that coincides with the operating center of the cylinder, An eccentric shaft fixed to the main shaft and rotating while being held at an eccentric distance d, The aforementioned eccentric axis rotates while rotating and revolving, A rotary piston whose center is eccentric by a distance r (d=r) equal to the eccentricity interval d, which is coupled to and rotates together with the aforementioned rotation and orbital axes, and The system is characterized by being configured with a rotation ratio constraint means that constrains the ratio of the main shaft rotation angular velocity x to the rotary piston rotation angular velocity y to 1:2.

[0013] The rotation ratio constraint means is characterized by being composed of a gear.

[0014] The rotation ratio constraint means is coupled to the main shaft and rotates in conjunction with the primary gear, A secondary planetary gear that rotates in connection with the primary gear, A tertiary gear is connected to the secondary planetary gear on the inside and rotates so that the main shaft and the rotation center line coincide, and The system is characterized by being connected to the aforementioned third gear internally and rotating, and being configured with a fourth gear installed on one side of the rotation and revolution axes, which rotates so as to coincide with the rotary piston and its rotational centerline.

[0015] The rotary piston is, To eliminate vibrations that can be generated by eccentric rotation, This design is characterized by providing a cavity on the heavier side so that the center of gravity coincides with the center of rotation.

[0016] Furthermore, the present invention, in order to achieve the above-mentioned objectives, Rotary cylinder, A rotary piston whose center (mechanically structural center) is eccentric to the rotation center that maintains the rotation center and eccentricity distance d of the rotary cylinder, and whose center (mechanically structural center) is eccentric by the same distance r (d=r) as the eccentricity distance d, and The system is characterized by comprising a rotation ratio constraint means that constrains the ratio of the rotational angular velocity x of the rotary cylinder to the rotational angular velocity y of the rotary piston to 1:2.

[0017] The rotation ratio constraint means is characterized by being composed of a gear.

[0018] The aforementioned rotary cylinder and rotary piston pairs are arranged in multiple rows and in multiple stages. Each stage is characterized by being configured in a multi-stage manner, where the centerlines of each rotary cylinder (perpendicular to the rotational centerline) and the center of the rotary piston (mechanically circular) are positioned and arranged at twice the rotary piston-center-displacement angle (y) (y=2x) relative to the rotary cylinder-centerline-displacement angle (x), with respect to a pair of reference point 0 angles. [e.g., (x=0, y=0), (x=60, y=120), (x=120, y=240)]

[0019] The rotation ratio constraint means is Multiple pairs of rotary cylinders and rotary pistons are arranged in multiple stages. [For each rotary cylinder, the rotational piston has a rotational angle y that is twice that of the rotational cylinder (y=2x), and multiple pairs of these are arranged at different angles to each other in multiple stages.] Each rotary cylinder and rotary piston operates as if it were a gear with two teeth (rotary cylinder) and a gear with one tooth (rotary piston), in multiple pairs. The system is characterized by a multi-stage alternative configuration such that the rotation ratio is constrained to 1:2.

[0020] The rotary piston is, To eliminate vibrations that can be generated by eccentric rotation, This design is characterized by providing a cavity on the heavier side so that the center of gravity coincides with the center of rotation.

[0021] Furthermore, the present invention, in order to achieve the above-mentioned objectives, Rotary cylinder, A rotary piston whose center (mechanically structural center) is eccentric to the center of rotation that maintains an eccentricity distance d with respect to the center of rotation of the rotary cylinder, and whose center is eccentric by the same distance r (d=r) as the eccentricity distance d, The rotary cylinder and rotary piston, two pairs, are connected in two stages. One pair of stages is configured such that the fluid output is proportional to cos(θ) with respect to the rotary cylinder angle x=θ=0 and the piston angle y=θ=0. Another pair of stages is coupled such that the cylinder angle x=θ=-,+90 and the piston angle y=2x=180 to displace the working fluid phase by -,+90 degrees, and the fluid output is coupled so that it is proportional to COS(θ-90) (or COS(θ+90)). A rotation ratio constraint means that constrains the ratio of the rotational angular velocity x of the rotary cylinder to the rotational angular velocity y of the rotary piston to 1:2. The fluid machine P, which combines the two pairs of stages mentioned above to make the intake and discharge DC, The fluid machine P is coupled to an active machine [prime mover (motor, engine, etc.)], and the other fluid machine P is coupled to a manual machine (automobile tire, aircraft rotor, etc.), The two fluid machines P, which are connected to the active machine and the manual machine respectively, are connected by a working fluid-closed circuit (pipe, high-pressure hose, etc.), It is characterized by being configured to generate rotational and torque displacements between two active machines and a manually operated machine.

[0022] The working fluid-closed circuit is characterized by the addition of a valve SV to control the flow of the working fluid, thereby enabling control of the amount of rotation and torque displacement applied to each manual machine.

[0023] The rotation ratio constraint means is characterized by being composed of a gear.

[0024] The rotation ratio constraint means is characterized by replacing multiple pairs of rotary cylinders and rotary pistons, each having different angles, in multiple stages.

[0025] Furthermore, the present invention, in order to achieve the above-mentioned objectives, Rotary cylinder, A rotary piston whose center is eccentric to the rotation center that maintains an eccentricity distance d with respect to the rotation center of the rotary cylinder, and whose center is eccentric by the same distance r (d=r) as the eccentricity distance d, The rotary cylinder and rotary piston, two pairs, are connected in two stages. One pair of stages is configured such that the fluid output is proportional to cos(θ) with respect to cylinder angle x=θ=0 and piston angle y=θ=0. Another pair of stages is coupled so that the cylinder angle x=θ=-,+90 and the piston angle y=2x=180 to displace the working fluid phase by -,+90 degrees, and the fluid output is coupled so that it is proportional to COS(θ-90) [or COS(θ+90)]. A rotation ratio constraint means that constrains the ratio of the rotational angular velocity x of the rotary cylinder to the rotational angular velocity y of the rotary piston to 1:2. The fluid machine P, which combines the two pairs of stages mentioned above into one, has its suction and discharge converted to DC. In addition to this, The fluid machine P is coupled in multiple stages (P*n) to form a multi-stage fluid machine Pn with a single output rotating shaft in a single housing, and the fluid machine P is coupled to an active machine (prime mover (motor, engine, etc.)), The fluid machine P and the multi-stage (P*n) fluid machine are connected by a working fluid-closed circuit (pipe, high-pressure hose, etc.). The aforementioned working fluid-closed circuit is further enhanced by adding a multi-stage (P*n) fluid machine and multiple valves (SV*n) that control the flow of working fluid in each stage. The active machine's output shaft rotation amount is configured to be controlled by displacing the rotational displacement and torque applied to the output rotation shaft of the multi-stage fluid machine Pn.

[0026] The rotation ratio constraint means is characterized by being composed of a gear.

[0027] The rotation ratio constraint means is This invention is characterized by the use of multiple rotary cylinder and rotary piston pairs, each positioned at different angles, arranged in multiple stages.

[0028] The fluid machine according to the present invention will be described in detail below with reference to the attached drawings.

[0029] Figure 1 is an exploded perspective view of the fluid machine according to the present invention.

[0030] A cylinder formed (fixed) in the housing is made to rotate via a main shaft 12 at its operating center, and an eccentric shaft 11a (rotation, revolution - planetary axis) is provided inside the main shaft at a position eccentric by a distance d. A rotary piston 10 rotates on the aforementioned eccentric shaft, which is eccentrically positioned at a distance r (=d) from the center of rotation, with respect to its structurally circular center. The eccentric shaft 11a and the main shaft 12 are constrained to each other in a 2:1 ratio by rotation ratio constraint means, which consist of an eccentric shaft gear 113g and a gear 311g formed to coincide with the rotation center of the main shaft.

[0031] In other words, the rotational velocity y of the rotary piston (rotation center C1) and the rotational velocity x of the main shaft (rotation center C2) are constrained to a rotational ratio of y:x = 2:1.

[0032] In this way, all parts only perform perfect circular motion, but it is possible to achieve the same volume change as a reciprocating piston-cylinder. Unlike cranks and connecting rods, there is no need to convert circular motion to linear motion, eliminating the friction loss and wear that occurs when the piston slides against the cylinder wall while applying force during the conversion process, thus reducing vibration. Furthermore, in the manufacturing process, all component parts are in circular and linear forms, eliminating the need for specialized machinery to process complex structures like screw-type designs. This allows for high-precision manufacturing, making it applicable to various industries, easy to mass-produce, and offering advantages such as simpler components and structure.

[0033] Figure 2 is a diagram illustrating the operating principle and operating process of the fluid machine according to the present invention shown in Figure 1. One cycle is completed through the process of (a)~(h)~(a).

[0034] (a)-(b) If the main shaft 12 rotates counterclockwise during the process, the rotary piston 10 rotates clockwise by twice the eccentric axis rotation angle due to the eccentric axis gear 113g of the rotary piston 10 which meshes with the gear 311g formed in the housing, and the center C3 of the rotary piston (geometrically circular) moves to the right along the cylinder operating center line S1. This operation causes an expansion of volume between the cylinder and the rotary piston, and fluid begins to be drawn into the resulting vacuum space.

[0035] The inhalation is completed in (e) after going through steps (c)-(d). The main axis rotates 180 degrees counterclockwise. The rotary piston and rotary piston shaft 11a rotated 360 degrees (180*2) clockwise [by means of the rotation ratio constraint means of the eccentric shaft gear 113g and gear 311g, with a rotation ratio of 2:1] while revolving 180 degrees (counterclockwise - around the main shaft rotation center).

[0036] In the process of (e)-(f), the rotary piston 10, passing through a fixed point on the right side of the cylinder, continues to rotate its main shaft counterclockwise, and also continues to revolve and rotate on its axis, and begins to move to the left, leading to the discharge process.

[0037] The discharge process is completed in (a) after going through the (g)-(h) process, The main axis rotated 360 degrees counterclockwise.

[0038] The rotary piston and rotary piston shaft 11a complete one cycle by rotating 720 degrees (360*2) clockwise while revolving 360 degrees (counterclockwise - around the main shaft's rotation center) [by the rotation ratio constraint means of the eccentric shaft gear 113g and gear 311g, with a rotation ratio of 2:1].

[0039] Figure 3 is a diagram that mathematically proves the operation process shown in Figure 2. As shown in Figure 2, the main shaft and the rotary piston (which rotates on its axis and revolves around the main shaft) rotate with angular velocities x and y, respectively.

[0040] Each rotation is constrained by the rotation ratio constraint means, the rotation ratio of gear 311g and eccentric shaft gear 113g, which is 1:2 = x:y. We explained how to mathematically prove that the eccentric center C3 of the rotary piston is always located on the cylinder-center line S1.

[0041] In other words, in Figure 3, the sum of the interior angles of triangle (c1c2c3) is 180,

[0042] x+c+a=180 (formula 1)

[0043] Here, since a = (180 - y),

[0044] x+c+(180-y)=180(Formula 2)

[0045] If we move the remaining part after removing y to the right side,

[0046] y=x+c (formula 3)

[0047] Here, the eccentric distance d (between the main shaft and the rotation center C2 and the rotary piston and the rotation center C1) was designed to be the same as the distance r (between the rotary piston and the rotation center C1, and between the rotary piston and the center C3), so d = r. therefore, Since triangle (c1c2c3) is an isosceles triangle with d=r, Angle x=c, Therefore, in (Equation 3),

[0048] y = x + c = x + x = 2x (Equation 4)

[0049] [In other words, with angle x=c (d=r, since it is isosceles), and y=2x, In other words, when the ratio is constrained to y:x=2:1, point C3 always coincides with the cylinder-center line S1.

[0050] In other words, as proven in (Equation 4), The main shaft 12 rotates at point c2 (which coincides with the center of cylinder 20f) with angular velocity x. From point c2 (center of rotation of the main axis), at a distance d, If the eccentric shaft (rotary piston - rotation center c1) rotates at an angular velocity y (=2x), twice the speed of the main shaft, and at a constrained ratio, It can be mathematically proven that the eccentric center c3 of the rotary piston 10 always coincides with the cylinder-center line S1.

[0051] Figure 4 is an assembled plan cross-sectional view of the fluid machine according to the present invention shown in Figure 1.

[0052] Figure 5 is an assembled perspective cross-sectional view of the fluid machine according to the present invention shown in Figure 1, which allows for a clearer understanding of the operation and coupling relationship between the cylinder 20f, rotary piston 10, rotary piston shaft 11a, cylinder housing side wall center gear 311g, and rotary piston shaft gear 113g, as described in Figures 2 and 3.

[0053] Figure 6 is an exploded perspective view of the fluid machine according to the present invention. The fluid machine, which has the basic principle structure shown in Figure 1, has been further applied and put into practical use, and has been improved from an engineering standpoint to be able to withstand large forces, operate smoothly with less wear, and when attempting to configure multiple stages, (in the fluid machine of Figure 1, structurally, the rotary piston must rotate and revolve on one side of the main shaft, so the main shaft cannot pass through the inside of the rotary piston and move to the cylinder of the next stage (a structure that makes it difficult to form multiple stages), and since the main shaft and rotary piston shaft are all supported on only one side, there are many parts that are not sufficiently engineered in terms of force transmission and uneven wear compared to a structure that is supported by bearings on both sides) and a multi-stage configuration has been made possible.

[0054] In other words, Figure 6 shows a more engineeringly applied and improved version of the fluid machine according to the present invention shown in Figure 1, in which an eccentric shaft 113c is connected to the outside of the main shaft 112 (like a crank structure), a rotation and revolution shaft 113p rotates externally on the eccentric shaft 113c, and a rotary piston 10 is integrated with the rotation and revolution shaft 113p and rotates, with the main shaft 112 passing through both ends of the rotary piston 10 and through both side walls of the cylinder housing, supported by bearings and able to rotate (a multi-stage structure that is easy to manufacture).

[0055] There is an eccentricity difference of distance d between the rotation center of the main shaft 112 and the rotation center of the eccentric shaft 113c laid outside of it. There is an eccentricity difference of distance r between the rotation center of the rotary piston 10 and the structural circular center C3 of the rotary piston 10, and the distance between d and r must be the same, d = r.

[0056] (That is, in the structure shown in Figure 1, the main shaft, as well as the other rotation and revolution axes, the rotary piston shaft and rotary piston, rotate inside the main shaft, and the main shaft and rotary piston shaft are shielded from each other and may exist only on one side, and the structure is such that expansion to the side walls of both housings is impossible (a structure in which multi-stage expansion is difficult)).

[0057] The housing 30, which forms the cylinder 20f inside, has a side wall 301w that connects and supports the tertiary gear 43g, a side wall 31w that connects and supports the planetary secondary gear 42g shaft 42s and the main shaft bearing, and a bearing cover side wall 32w that are connected in sequence, and the intermediate outer wall has intake and exhaust ports 30a and 30b.

[0058] Fourth gears 44g are formed at both ends of the rotation and revolution axis 113p, and the rotary piston 10 is connected by a key 70 so that it can rotate as a single unit.

[0059] The rotation of the main shaft and the rotation of the rotary piston are constrained to each other in a 1:2 ratio. In this process, the main shaft 112 is connected in such a way that a primary gear 41g is coupled to one side, a secondary gear 42g is connected around it like a planetary gear, and an inner tertiary gear 43g is connected to the upper part of the main shaft 112 with bearing support on the side wall of the housing, allowing it to rotate. Furthermore, a quaternary gear 44g for the rotation and revolution axes is connected to the other side of the tertiary gear 43g, so that the rotary piston 10, which is integrally coupled to the main shaft 112 and the rotation and revolution axis 113p, rotates with respect to the main shaft under mutual constraint at a rotation ratio of 1:2 (x:y = main shaft rotation: rotary piston rotation).

[0060] In this way, in addition to the advantages of the fluid machine according to the present invention shown in Figure 1, it is also more durable, easier to maintain, more practical from an engineering standpoint, can be used for fluid conversion requiring large forces, and can be made in multiple stages to be applied to larger-scale fluid machines.

[0061] Figure 7 is an assembled external perspective view of the fluid machine shown in Figure 6 according to the present invention.

[0062] Figures 8(A) and 8(B) are assembled perspective cross-sectional views of the fluid machine shown in Figure 7 according to the present invention, and Figure 9 is an assembled cross-sectional view of the fluid machine according to the present invention, which allows for a better understanding of the interconnection relationships between the parts described in more detail in Figure 6.

[0063] Figure 10 illustrates, in an easy-to-understand cross-sectional view, the connection process from the primary gear 41g, secondary gear 42g, tertiary gear 43g to the quaternary gear 44g in the fluid machine according to the present invention shown in Figure 6, where the rotation ratio constraint means is composed of gears. This is an example in which the rotation ratio constraint means, which constrains 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 composed of gears in the fourth stage.

[0064] Figure 11 shows the operation process of the fluid machine shown in Figure 6 according to the present invention.

[0065] One cycle is completed through the process of (a)~(b)~(c)~(d)~(a).

[0066] As the main shaft 112 rotates clockwise during the process of (a) to (b), the rotary piston 10 is connected to the rotation and revolution axis gear 44g, which is linked by the 1st to 4th gears 41g, 42g, 43g, and 44g. This gear causes the rotary piston to rotate counterclockwise by twice the eccentric axis rotation angle, while the center C3 of the rotary piston (geometrically circular) moves to the right along the cylinder operating center line S1. This operation causes an expansion of volume between the cylinder and the rotary piston, and fluid begins to be drawn into the resulting vacuum space.

[0067] (b) After going through the process, (c) the inhalation is completed. The main axis rotated 180 degrees clockwise.

[0068] The rotary piston 10 rotated 360 degrees (180*2) counterclockwise while revolving 180 degrees (clockwise - around the main axis rotation center) [by means of the rotation ratio constraint of the gears connected by primary to quaternary gears 41g, 42g, 43g, and 44g, with a rotation ratio of 2:1].

[0069] (c) In the process, the rotary piston 10, having passed a fixed point on the right side of the cylinder, begins to move to the left side, while the main shaft 112 continues to rotate clockwise, and also continues to revolve and rotate on its axis, leading to the discharge process.

[0070] (c) The discharge process is completed in (a) after going through process (c), The main axis rotated 360 degrees clockwise.

[0071] The rotary piston 10 completes one cycle by rotating 720 degrees (360*2) in a counterclockwise direction while revolving 360 degrees (clockwise - around the main axis rotation center) [by means of rotation ratio constraints for the primary to fourth gears 41g, 42g, 43g, and 44g, with a rotation ratio of 2:1].

[0072] Figure 12 shows an example of a fluid machine according to the present invention, in which the fluid machine according to the present invention shown in Figure 6 is configured in multiple stages.

[0073] A multi-stage fluid machine was completed by combining a total of four cylinders and pairs of rotary pistons. Here, the direction of connection of the rotary pistons is such that two rotary pistons face each other in their respective directions of motion, and the phase is aligned so that the direction of motion of the other two rotary pistons is 180 degrees opposite to that of the other two rotary pistons, thus forming a multi-stage fluid machine.

[0074] Figure 13 is an exploded perspective view of the fluid machine according to the present invention.

[0075] In other words, unlike the (fixed) cylinders in Figures 1 and 6, the same operation is achieved using a "rotating rotary cylinder" instead of a "rotating main shaft".

[0076] In other words, the rotary cylinder 20 is positioned to rotate so as to coincide with the operating center, and the main shaft 122 is installed inside the rotary cylinder at a position eccentric by a distance d. A rotary piston 10, whose structural circular center is eccentrically offset by a distance r (=d) from the center of rotation, rotates on the main shaft 122. The relationship of mutual rotation ratio constraint between the rotary cylinder 20 and the rotary piston 10 is as follows: Gear 401g is connected to the main shaft 122 which is coupled to the rotary piston, gear 402g is connected to it, gear 403ga is connected to it, gear 403gb is coupled to one side of the same shaft, gear 404ga is connected to it, gear 404gb is coupled to one side of the same shaft and has moved to the opposite side of the gearbox, and gear 405g is installed on one side of the rotary cylinder which is connected to it, so that they are constrained to each other with a rotation ratio of 1:2 (=x:y=rotary cylinder rotation angle x:rotary piston rotation angle y).

[0077] In this way, all parts only perform perfect circular motion, but it is possible to achieve volume changes similar to those of a reciprocating piston-cylinder. Unlike cranks and connecting rods, there is no need to convert circular motion to linear motion, eliminating frictional losses and wear that occur when the piston slides against the cylinder wall while applying force during that conversion process, thus eliminating vibration. Furthermore, in the manufacturing process, all elements are composed of circles and straight lines, eliminating the need for complex machining and specialized machinery like that required for helical screw designs. This allows for easier high-precision manufacturing and simplifies the components and structure, among other advantages.

[0078] Figure 14 is an assembled external perspective view of the fluid machine shown in Figure 13 according to the present invention.

[0079] Figure 15 shows the rotation ratio constraint means of the fluid machine of Figure 13 according to the present invention, which is composed of seven 4-stage gears 401g, 402g, 403ga, 403gb, 404ga, and 404gb, in two interconnected partial cross-sectional views.

[0080] Figure 16 illustrates the operating principle and process of the fluid machine shown in Figure 13 according to the present invention, completing one cycle through processes (a) to (h) to (a).

[0081] As the rotary piston 10 coupled to the main shaft 122 rotates clockwise during the process of (a) to (b), the rotary cylinder 20 rotates clockwise at half the rotation angle of the rotary piston [for every rotary cylinder rotation angle x, the rotary piston rotation angle y is twice as much (y=2x)] by the rotation ratio constraint means, with seven 4-stage gears 401g, 402g, 403ga, 403gb, 404ga, and 404gb, while the structural circular center C3 of the rotary piston moves along the cylinder operating center line S1, creating a gap between the rotary cylinder and the rotary piston.

[0082] This operation causes an expansion of volume between the rotary cylinder and the rotary piston, and fluid begins to be drawn into that vacuum space.

[0083] (c) to (d) are followed, and inhalation is completed in (e). The rotary cylinder 20 rotates 180 degrees (x) clockwise, The rotary piston 10 rotated 360 degrees (180*2) clockwise (y) according to the rotation ratio constraint means and the rotation ratio (1:2=x:y).

[0084] During the process from (e) to (f), the distance between the rotary cylinder and rotary piston passes through a fixed point at its maximum, and as the rotary piston 10 continues to rotate clockwise, the distance between the rotary cylinder and rotary piston narrows, the fluid pressure begins to increase, and this leads to the discharge process.

[0085] The discharge process is completed in (a) after going through processes (g) to (h). The rotary cylinder rotation angle x rotates 360 degrees clockwise. The rotary piston rotation angle y completes one cycle by rotating 720 degrees (360*2) clockwise, according to the mutually constrained rotation ratio constraint means rotation ratio (1:2=x:y).

[0086] Figure 17 is a diagram that mathematically proves the operation process shown in Figure 16. The rotary cylinder 20 and the rotary piston 10 connected to the main shaft 122 rotate with angular velocities x and y, respectively. Each rotation is constrained to a ratio of 1:2=x:y by the rotation ratio constraint means, We explained how to mathematically prove that the (mechanical) center C3 of the rotary piston is always located on the rotary cylinder-center line S1.

[0087] In other words, in Figure 17, the sum of the interior angles of triangle (c1c2c3) is 180,

[0088] x+c+a=180 (formula 1)

[0089] Here, since a = (180 - y),

[0090] x+c+(180-y)=180(Formula 2)

[0091] If we move the remaining part after removing y to the right side,

[0092] y=x+c (formula 3)

[0093] Here, the eccentricity distance d between the rotary cylinder and its rotation center C2 and between the rotary piston and its rotation center C1 was designed to be the same as the distance r between the rotary piston and its rotation center C1, and between the rotary piston's rotation center and its mechanical center C3, so d = r. therefore, Since triangle (c1c2c3) is an isosceles triangle with d=r, Angle x=c, Therefore, in (Equation 3),

[0094] y = x + c = x + x = 2x (Equation 4)

[0095] [In other words, with angle x=c (d=r, since it is isosceles), and y=2x, In other words, when the ratio is constrained to (1:2=x:y), point C3 always coincides with the rotary cylinder-center line S1.

[0096] In other words, as proven in (Equation 4), The rotary cylinder 20 rotates at point C2 (the center of rotation of the rotary cylinder) with angular velocity x. At point C2 (the rotation center of the rotary cylinder), at a distance d, When the rotary piston-rotation center C1 rotates with angular velocity y (=2x) and is constrained to rotate at twice the rotational angular velocity x of the rotary cylinder, It can be mathematically proven that the geometric circular center C3 of the rotary piston 10 always coincides with the rotary cylinder centerline S1.

[0097] Figures 18 and 19 show examples of multi-stage configurations of the fluid machine according to the present invention shown in Figures 13 and 17.

[0098] To configure a rotary cylinder and rotary piston pair in multiple stages, the reference pair (stage) is set with x=0, y=0 as the base, and for the next stage, when an "arbitrary x1 value" is set, the y1 value must be set to "twice the arbitrary x1 value".

[0099] In other words, for example, if the reference first stage is x=0, y=0, the next second stage is x=60, y=2x=120, and the third stage is x=120, y=2x=240, then it will operate in accordance with the operating principle shown in Figure 17.

[0100] Figures 18 and 19 show an example of the fluid machine according to the present invention, configured in three stages.

[0101] Figure 20 clearly illustrates the structural cross-sectional view of the rotating rotary cylinder and rotary piston pair according to the present invention, as shown in Figure 18.

[0102] Figure 21 shows that, according to the present invention, when there is a single stage between the rotating rotary cylinder and rotary piston, a dead zone occurs where power transmission is impossible (A)-(B), and when there are multiple stages and they are mechanically connected to each other, they operate like multiple inner gear teeth (rotary cylinder) and multiple gear teeth (rotary piston), and can be operated by gears (C)(D) with a rotation ratio constraint means of 1:2.

[0103] In other words, without a separate rotation ratio constraint means, As shown in Figure 21(A), when the system rotates using only a pair of rotary cylinders and a rotary piston, in state (A), even without a rotation ratio constraint means, if only the rotary piston rotates, the force is applied to the rotary cylinder wall, forcing the rotary cylinder to move and rotate accordingly, thus enabling the transmission of rotational power between them.

[0104] however, As shown in Figure 21(B), when the rotary piston rotates 180 degrees in state (A) and "aligns with the rotation center of the rotary cylinder," (where rotational power transmission between them is impossible) (dead zone), the rotary cylinder should theoretically also rotate 90 degrees to position Ob. However, in reality, because the rotary cylinder lacks the elements that control left and right rotation as in state (A) (the rotary piston obstructing the wall), it rotates 360 degrees. Due to the manufacturing precision and clearance between the rotary cylinder and rotary piston, and the different external forces and torques acting on the rotary cylinder and rotary piston, the rotary cylinder ends up in positions Oa and Oc, which are far apart. If the rotary piston is forced to continue rotating in this position, the fluid machine will stop or the shaft will break.

[0105] However, as shown in Figure 21(C), when it is configured in multiple stages, In other words, if rotary cylinders and rotary pistons are arranged in multiple stages in pairs at different angles, with the rotary piston-to-rotary piston angle y being twice the rotary cylinder-to-rotary cylinder angle x (y=2x), and each rotary cylinder is integrally connected to the others, and the rotary pistons are mechanically integrated by a rotary piston-to-rotary piston axis, In a rotary cylinder and rotary piston with three connected stages, even when one of the three pairs of stages is in state (B), where "the rotary piston coincides with the rotation center of the rotary cylinder," the other two pairs remain in the position where the rotary cylinder wall fixes the rotary piston, allowing for continuous transmission of rotational power between them.

[0106] In other words, as shown in Figure 21(D), one rotary cylinder operates as if it had two inner gear teeth and one rotary piston as if it had one gear tooth, but when arranged in multiple stages, it operates as if it had multiple inner teeth and multiple teeth, and the gears can be changed and operated using a 1:2 rotation ratio constraint means.

[0107] (However, if a gear is not installed as a means of restricting the rotational ratio to 1:2, further wear losses due to friction may occur during the process of transmitting rotational force and torque between the rotary cylinder and the rotary piston.)

[0108] Figure 22 shows a rotary piston for a fluid machine according to the present invention. Because the rotary piston rotates eccentrically, large vibrations can occur when it rotates at high speeds. Therefore, in the present invention, a cavity 10h is formed so that the center of gravity of the rotary piston is located on the center of rotation. This ensures that even when rotating at high speeds, the center of rotation of the rotary piston and the center of gravity coincide, thus preventing vibrations from occurring.

[0109] Figure 23 shows a fluid machine according to the present invention, which combines the fluid machines in Figures 6 and 13 into two stages. One stage is configured so that the fluid output is proportional to COS(θ) based on a cylinder angle x=θ=0 and a piston angle y=θ=0. The other stage is configured so that the working fluid phase is displaced at - and +90 degrees, with a cylinder angle x=θ=- and +90 degrees and a piston angle y=2x=180 degrees, and the fluid output is proportional to COS(θ-90). These two pairs (stages) are integrated and combined into a single housing, and the intake and discharge amounts to COS(θ) + COS(θ-90) = COS(θ) + SIN(θ). This fluid machine connects a fluid machine P that draws in and discharges a working fluid that is a constant DC current relative to the rotational displacement, proportional to [=COS(θ)+COS(θ+90)], to an active machine (prime mover, motor, engine, etc.), and another fluid machine P is connected to a manual machine (automobile tire, aircraft rotor, etc.). The two fluid machines P are connected by a working fluid-closed circuit (pipe, high-pressure hose, etc.), or a valve SV that controls the flow of the working fluid is added to the working fluid-closed circuit, so that the rotational amount and torque of the active machine can be controlled by the manual machine.

[0110] In other words, it is a fluid machine that can transmit the rotational force output from the engine to the tires, resulting in a displacement of rotational force and torque, without the need for a propeller shaft, differential gears, or transmission.

[0111] This eliminates the need for mechanical parts such as propeller shafts and differential gears that connect the power between the car engine and tires (or the aircraft engine and rotor), reducing the weight of the car or aircraft due to the many mechanical parts, and saving on costs and maintenance expenses.

[0112] Figure 24 shows a fluid machine according to the present invention, which combines the fluid machines in Figures 6 and 13 into two stages, but in one stage, the fluid output is made proportional to cos(θ) with respect to the cylinder angle x=θ=0 and piston angle y=θ=0. Furthermore, to displace the working fluid phase by - and +90 degrees, the cylinder angle x=θ=- and +90 degrees, and the piston angle y=2x=180 degrees are coupled, so that the fluid output is proportional to COS(θ-90). Two pairs (stages) are integrated and coupled in one housing, and the intake and discharge are proportional to COS(θ)+COS(θ-90)=COS(θ)+SIN(θ), [=COS(θ)+COS(θ+90)], and the fluid machine P that draws in and discharges the working fluid, which consists of a constant DC current relative to the rotational displacement, is coupled to an active machine (prime mover, motor, engine, etc.). Furthermore, other multi-stage fluid machines Pn (the figure shows an example with 6 stages), [a fluid machine Pn formed by combining n of the above fluid machines P into one integrated fluid machine], The fluid machine P and the fluid machine Pn are connected by a working fluid-closed circuit (pipe, high-pressure hose, etc.) and control valves (SV1~SV6~SVn), The rotational amount and torque amount R1 of the fluid machine P coupled to the active machine can be displaced by the rotational displacement amount and torque displacement amount R2 of the fluid machine Pn, which is integrated in multiple stages.

[0113] In other words, if all the pairs of stages (P) inside the fluid machine P and the multi-stage integrated fluid machine Pn are the same size and capacity, then when only valve SV1 is ON (OPEN) and all the others are OFF (CLOSE), R2 is 1 / 1*R1 (=R2=1 / 1*R1) compared to the rotational displacement R1. When valves SV1 and SV2 are ON (OPEN) and all others are OFF (CLOSE), the rotational displacement R2 is 1 / 2 * R1 (= R2 = 1 / 2 * R1) compared to R1. ..., ..., when all valves SV1 to SV6 are ON (OPEN), the rotational displacement R2 is 1 / 6 * R1 (= R2 = 1 / 6 * R1) compared to the rotational displacement R1. ..., ..., when all valves SV1 to SVn are ON (OPEN), the rotational displacement R2 is 1 / n*R1 (=R2=1 / 6*R1) compared to the rotational displacement R1, This is a fluid machine that allows the rotational amount R1 of an active machine to be changed by a rotational displacement R2 (in the example shown in the figure, n=6 steps), thereby changing both the rotational amount and the torque.

[0114] Figures 25 and 26 are shown to mathematically prove that a fluid machine P produces a constant DC output (+)(-)PV for the rotation axis displacement angle shown in Figures 23 and 24.

[0115] In other words, the stroke distance between the rotary cylinder and rotary piston as shown in Figure 25(A) is 2d*COS(θ) (=dPS).

[0116] The reason is that Figures 26(A) and 26(B) are parts of Figures 3 and 17, respectively, and when these figures are combined into Figure 26(C), (Process 1) If you draw a line segment (c2c3) in the middle of an isosceles triangle (c1c2c3) and a perpendicular line dividing it in half at a right angle, you will get a right-angled triangle (c1c2c4).

[0117] (Process 2) Here, the length of the lower boundary of the right triangle (c1c2c4) is d*COS(x)(1) The total distance dPS is twice the line segment (c2c4) in equation (1) above, dPS = 2 * d * cos(x)(2).

[0118] The internal volume of half a cylinder in one stage in Figure 25(A) is as shown in Figure 26(D),

[0119] The total volume for one process is [2*d*COS(x)]*Pw*Pd(3).

[0120] And if you add another stage (rotary cylinder, rotary piston pair) that is displaced by -90 degrees, Total volume of the two stages = [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)

[0121] In other words, Figure 25(A) shows a fluid machine (proportional to the suction / discharge cos(θ)), and two of these fluid machines are coupled with a phase displacement to form a fluid machine (proportional to the suction / discharge cos(θ) + cos(θ-90)). Figure 25(B) is a fluid machine P that has the same sine wave and pulsation-free, DC-like working fluid suction / discharge characteristics as (C).

[0122] Figure 27 shows the fluid machine according to the present invention, as shown in Figure 23, applied to an automobile.

[0123] Figure 28 shows the application of the fluid machine according to the present invention shown in Figure 23 to a drone, enabling flight by controlling four rotors with a single prime mover (motor, engine, etc.) instead of using four prime movers (motors, engines, etc.) for each rotor.

[0124] Figure 29 shows the fluid machine according to the present invention, as shown in Figure 23, applied to an aircraft rotor, enabling flight without a propeller shaft connecting the main engine to the tail fin, or a transmission gear.

[0125] Figure 30 shows the application of the fluid machinery according to the present invention shown in Figure 23 to a ship. Previously, holes were drilled in the hull to connect the external propeller to the engine and then to the main shaft. This required many mechanical parts and costs to waterproof and repair the water that flowed into the outside. However, by applying the fluid machinery according to the present invention, power can be transmitted via the propeller without drilling holes in the hull to the main shaft, which has the advantage of saving many waterproof mechanical parts and maintenance costs.

[0126] (Newton's law of universal gravitation was not proven by Newton, but by many scientists before him, as in the "Leaning Tower of Pisa" experiment, where all objects (mass m1) move at a rate of 9.8 m / sec relative to the Earth's surface.) 2 Experiments had shown that it would fall. However, Newton stated that it is proportional to the Earth's mass (m²) and the amount of material being dropped (m¹), and the square of the distance between the Earth's center of mass and the center of the material being dropped (r²) 2 The formula (G.m1.m2 / r) is inversely proportional to ). 2He created the equation (which also mathematically proved that it applies not only to objects on Earth but equally to all celestial bodies). This proved Galileo's statement that "the Earth revolves around the Sun." [Explanation of Symbols]

[0127] 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 formation) 112: Main shaft (connected to an eccentric shaft externally) 122: Main shaft (rotary piston rotation shaft) 112h: Hole into which the main shaft is inserted into the rotary piston. 112g, 113g: Rotary piston shaft gear (gear ratio 1) 113c: Eccentric axis (similar to a crank axle) 113p: Rotation and orbital axes 20: Rotary Cylinder 21: Rotary cylinder side wall 21s: Rotary cylinder shaft 20i: Rotary cylinder inlet and outlet openings 20f: Cylinder (formed and fixed to the main housing) 213b, 113b, 302b, 312b, 311b: Bearings 213s: Rotary cylinder side wall inner surface shaft 211g, 311g: Cylinder gear (gear ratio 2) 30: Main housing 30c: Main housing combustion chamber (high pressure) 30h: Rotary cylinder support hole on the side wall of the main housing 30W, 301W: Main housing side wall 30h: Main housing side wall, tertiary gear rotation shaft bearing support hole 30a: Inlet 30b: Outlet 30GB: Main housing gearbox 301h, 302h: Fluid guideway side wall groove 31c: Main housing side wall extension 31, 31a, 31b: Side walls of the main housing 31w: Main shaft and planetary gear bearing shaft support body housing side wall 32w: Main shaft bearing cover body housing side wall 31h: Planetary gear bearing shaft support hole 311c: Main housing - Rotary piston shaft inner surface bearing mounting section 312c: External bearing mounting section between main housing and rotary cylinder 401g, 402g, 403ga, 403gb, 404ga, 404gb, 405g: Gear 41g: Primary gear 42g: Secondary gear 43g: 3rd gear 44g: 4th gear 42s: Planetary gear shaft 60: O-ring 61: Oil seal 70: Key 71: Keyway 90, 90a, 90b, 90c: Bolt S1: Cylinder-centerline C1: Rotation center of the rotary piston shaft C2: Rotary cylinder - center of rotation, main shaft center of rotation (coincides with cylinder center) C3: Eccentricity center of rotary piston Cv: Check valve d: Distance between the main axis rotation center and the eccentric axis rotation center dPS: Distance traveled by the rotary piston within the cylinder. r: Distance between the eccentric axis rotation center and the rotary piston center. Oa, Oc: Mismatch (When there are no gears that mutually connect in a 2:1 ratio, when the rotary piston is at the center of rotation of the cylinder, the rotary cylinder will have an incorrect rotational difference that causes it to come to all positions due to manufacturing precision gaps and the difference between the two rotational forces) Rotary cylinder position Ob: Ideal rotary cylinder position M, E: Active machinery [prime movers (motors, engines, etc.)] Mc: Rotary piston center of gravity P: A fluid machine P having DC suction and discharge characteristics, formed by combining two pairs of fluid machines [two pairs of rotary cylinders and rotary pistons arranged with a 90-degree phase difference (2d*COS(θ) + 2d*COS(θ-90))]. Pn: A fluid machine Pn formed by connecting multiple fluid machines P in multiple stages. P1, P2: Intake and discharge of one fluid machine PV: Intake and discharge of two fluid machines PW: Width of the stroke space of a single fluid machine Pd: Thickness of the stroke space of one fluid machine R1: Displacement of the output rotation shaft of the fluid machine P, which is coupled with an active machine. R2: Displacement of the output rotating shaft of the multi-stage fluid machine Pn SV, SV1, SV2, SV3, SV4, SV5, SV6: Fluid flow control valves Wh: Active machinery (car tires, drone propellers, etc.)

Claims

1. A fixed cylinder formed in the main housing, A main shaft having a rotation center that coincides with the operating center of the cylinder, A rotary piston-rotating shaft is installed on one side inside the main shaft and rotates and revolves on the main shaft, maintaining an eccentricity d. The rotary piston - a rotary piston whose center is eccentrically offset from the rotation axis by a distance (r) (d=r) equal to the eccentricity interval (d), and A fluid machine characterized by comprising a rotation ratio constraint means that constrains the rotation ratio of the main shaft rotation angular velocity (x) and the rotary piston-rotation shaft rotation angular velocity (y) to 1:

2.

2. The fluid machine according to claim 1, characterized in that the rotation ratio constraint means is composed of a gear.

3. The fluid machine according to claim 1, characterized in that the rotary piston is configured to have a cavity on the heavier side so that the center of gravity coincides with the center of rotation, in order to eliminate vibrations that may be generated by eccentric rotation.

4. A fixed cylinder formed in the main housing, A main shaft having a rotation center that coincides with the operating center of the cylinder, An eccentric shaft fixed to the main shaft and rotating while being held at an eccentric interval (d), The aforementioned eccentric axis rotates while rotating and revolving, A rotary piston whose center is eccentric by a distance (r) equal to the eccentricity interval (d) (d=r), which is coupled with and rotates together with the aforementioned rotation and orbital axes, and A fluid machine characterized by being configured with a rotation ratio constraint means that constrains the rotation ratio between the rotation angular velocity (x) of the main shaft and the rotation angular velocity (y) of the rotary piston to 1:

2.

5. The fluid machine according to claim 4, characterized in that the rotation ratio constraint means is composed of a gear.

6. The rotation ratio constraint means is A primary gear that is connected to the main shaft and rotates in unison with it. A secondary planetary gear that rotates in connection with the primary gear, A tertiary gear is connected to the secondary planetary gear on the inside and rotates so that the main shaft and the rotation center line coincide, and The fluid machine according to claim 4, characterized in that it is composed of a fourth gear which is connected to the third gear on the inside and rotates, and is installed on one side of the rotation and revolution axis and rotates so as to coincide with the rotation centerline of the rotary piston.

7. The rotary piston is, To eliminate vibrations that can be generated by eccentric rotation, The fluid machine according to claim 4, characterized in that a cavity is provided on the heavier side so that the center of gravity coincides with the center of rotation.

8. Rotary cylinder, A rotary piston is eccentric to the rotation center that maintains the rotation center and eccentricity distance (d) of the rotary cylinder, and whose center is eccentric by the same distance (r) (d=r) as the eccentricity distance (d), and A fluid machine characterized by comprising rotation ratio constraint means that constrains the ratio of the rotational angular velocity (x) of the rotary cylinder to the rotational angular velocity (y) of the rotary piston to 1:

2.

9. The fluid machine according to claim 8, characterized in that the rotation ratio constraint means is composed of a gear.

10. The aforementioned rotary cylinder and rotary piston pairs are arranged in multiple rows and in multiple stages. The fluid machine according to claim 8, characterized in that each stage is configured in multiple stages, with the centerlines of each rotary cylinder and the center of the rotary piston positioned and arranged with respect to a pair of reference points (0), such that the rotary piston-center-displacement angle (y) is twice (y = 2x) relative to the rotary cylinder-centerline-displacement angle (x).

11. The rotation ratio constraint means is The aforementioned rotary cylinder and rotary piston pairs are arranged in multiple rows and in multiple stages. With respect to the rotary cylinder's centerline and displacement angle (x), the rotary piston's centerline and displacement angle (y) are doubled (y = 2x), and multiple pairs of these are arranged in multiple stages at different angles to each other. Each rotary cylinder and rotary piston operates as if multiple pairs of gears with two inner teeth and one tooth each were working together. The rotation ratio is constrained to 1:2, and alternative configurations are provided in multiple stages. The aforementioned inner gear is a rotary cylinder, The fluid machine according to claim 8, characterized in that the gear having one tooth is a rotary piston.

12. The rotary piston is, To eliminate vibrations that can be generated by eccentric rotation, The fluid machine according to claim 8, characterized in that a cavity is provided on the heavier side so that the center of gravity coincides with the center of rotation.

13. Rotary cylinder, A rotary piston whose center is eccentric to the rotation center that maintains the rotation center and eccentricity distance (d) of the rotary cylinder, and whose center is eccentric by the same distance (r) (d=r) as the eccentricity distance (d), The rotary cylinder and rotary piston, two pairs, are connected in two stages, but the fluid output of one pair is made proportional to COS(θ) with respect to the rotary cylinder angle x = θ = 0 and the piston angle y = θ = 0. Another pair of stages is coupled such that the cylinder angle x = θ = -, +90 and the piston angle y = 2x = 180 degrees to displace the working fluid phase by -, +90 degrees, and the fluid output is coupled so that it is proportional to COS(θ - 90) (or COS(θ + 90) yields the same result). A rotation ratio constraint means that constrains the ratio of the rotational angular velocity (x) of the rotary cylinder to the rotational angular velocity (y) of the rotary piston to 1:

2. A fluid machine (P) is formed by combining the two pairs of stages into one, thereby converting the suction and discharge to direct current. The fluid machine (P) is connected to the active machine, The aforementioned or other fluid machine (P) is connected to a manual machine, The two fluid machines (P) connected to the aforementioned active machine and manual machine are connected by a working fluid-closed circuit, A fluid machine characterized by being configured to generate rotational and torque displacements between two active machines and a manually operated machine.

14. The fluid machine according to claim 13, wherein a valve (SV) for controlling the flow of the working fluid is added to the working fluid-closed circuit, and the amount of rotation and torque displacement applied to each manual machine can be controlled.

15. The fluid machine according to claim 13, characterized in that the rotation ratio constraint means is composed of a gear.

16. The rotation ratio constraint means is The fluid machine according to claim 13, characterized in that multiple pairs of rotary cylinders and rotary pistons, each having different angles to each other, are used as a substitute configuration in multiple stages.

17. Rotary cylinder, A rotary piston whose center is eccentric to the rotation center that maintains the rotation center and eccentricity distance (d) of the rotary cylinder, and whose center is eccentric by the same distance (r) (d=r) as the eccentricity distance (d), The rotary cylinder and rotary piston, two pairs, are connected in two stages. One pair of stages is configured such that the fluid output is proportional to COS(θ) with respect to cylinder angle x = θ = 0 and piston angle y = θ = 0. Another pair of stages is coupled such that the cylinder angle x = θ = -, +90 and the piston angle y = 2x = 180 degrees to displace the working fluid phase by -, +90 degrees, and the fluid output is coupled so that it is proportional to COS(θ - 90) [or COS(θ + 90) yields the same result]. A rotation ratio constraint means that constrains the ratio of the rotational angular velocity (x) of the rotary cylinder to the rotational angular velocity (y) of the rotary piston to 1:

2. A fluid machine (P) is formed by combining the two pairs of stages into one, thereby converting the suction and discharge to direct current. In addition to this, The fluid machine (P) is coupled in multiple stages (P*n) to form a multi-stage fluid machine (Pn) with a single output rotating shaft in a single housing. The fluid machine (P) is connected to the active machine, The fluid machine (P) and the multi-stage fluid machine (Pn) are connected by a working fluid-closed circuit. The aforementioned working fluid-closed circuit is further enhanced by adding a multi-stage fluid machine (Pn) and multiple valves (SVn) that control the flow of working fluid in each stage (P). A fluid machine characterized by being configured to control the amount of rotation (R1) of a fluid machine (P) coupled to the output shaft of an active machine by displacing the amount of rotation (R2) and torque applied to the multi-stage (Pn) fluid machine output rotating shaft.

18. The fluid machine according to claim 17, characterized in that the rotation ratio constraint means is composed of a gear.

19. The fluid machine according to claim 17, characterized in that the rotation ratio constraint means is configured to replace multiple pairs of rotary cylinders and rotary pistons, each having different angles to each other, in multiple stages.

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