Hydraulic machine (embodiments)

Abstract

FIELD: hydraulic machines.SUBSTANCE: hydraulic machine includes: a cylinder, a main shaft, the centre of rotation of which coincides with the working centre of the cylinder, an eccentric shaft secured to the main shaft and configured to rotate and maintain an eccentric interval (d) relative to the main shaft. The hydraulic machine also comprises a rotating / rotary shaft, configured to rotate / turn on an eccentric shaft; a rotary piston, connected together with the rotating / rotary shaft to rotate and having a centre that is eccentric relative to the rotating / rotary shaft by a distance (r) equal to the eccentric interval (d) (d = r); and a rotation coefficient limiting device configured to limit the ratio between the angular velocity (x) of rotation of the main shaft and the angular velocity (y) of rotation of the rotary piston by a ratio of 1:2.EFFECT: improved maintainability and durability.12 cl, 30 dwg

Description

[0001] Field of technology to which the present invention pertains

[0002] The present invention relates to a hydraulic machine, in particular to a hydraulic machine (volume / rotary), in which, unlike a conventional reciprocating hydraulic machine, vibration does not occur, and the force created by high-pressure fluid does not generate a piston force, under the influence of which the surface of the cylinder wall is abraded, as in a reciprocating hydraulic machine, while machining is facilitated even in the serial production of such hydraulic machines, so that the cost of its manufacture is significantly reduced due to the precise design that facilitates the production process, and the change in volume is caused only by the mutual rotational movement of the cylinder (rotating) and the rotary piston.

[0003] Background Art of the Present Invention

[0004] As serial production and widespread use of conventional hydraulic machines were established, machines based primarily on the reciprocating motion of pistons appeared, as well as machines based on gear and worm gears and rotary machines of various other types.

[0005] Within the context of past technological advancements, among the most advanced types of mass-produced rotary hydraulic machines, Wankel machines (rotary Wankel machines) have proven unreliable in terms of tightness, wear resistance, and other similar parameters. Therefore, the mass production of Wankel machines for such broad markets as the vehicle and marine markets has failed, despite unremitting efforts over the past 70 years. In addition, worm-type machines have proven successful only in the field of air compression, while their production required high costs, several times higher than the cost of most conventional reciprocating hydraulic machines. Furthermore, there were limitations in that worm-type machines could not be applied or used as a suitable technology for electric drive devices or torque converters.Although many other rotary hydraulic machines have been proposed, there has never been a single example that has surpassed existing reciprocating and worm type machines in efficiency, durability and low production cost, and that has been successfully launched into mass production on a wide market.

[0006] Brief Disclosure of the Present Invention

[0007] Ordinary hydraulic machines, which are mostly mass-produced, such as machines using reciprocating pistons, or machines using gears or worm gears, have the following characteristics: reciprocating machines generate vibration and noise, because the force generated by the high-pressure fluid, due to the design features, acts as the force applied by the piston to the side wall of the cylinder, which causes noise, and the vibration causes strong friction and wear; in machines with gears, it is difficult to ensure a constant tightness of the fit between the curved surfaces of the gears, which must be manufactured with high precision, which makes it difficult to achieve high pressure according to the sealing criterion unless they are manufactured with high precision;and in worm-type machines, difficulties arise in their production with high precision to ensure a constant tightness of the screw curved surface, which causes problems such as high production costs.;

[0008] Furthermore, various rotary machines had been patented in the field of mechanics, but no one had ever patented a commercially successful rotary engine that would operate reliably, be repairable, and durable. Other, lesser-known rotary / positive-displacement hydraulic machines also didn't exist. In fact, numerous problems arose, such as the technical impossibility of manufacturing such machines or the impossibility of actually operating them.

[0009] In order to solve the above problems, the object of the present invention is to provide a hydraulic machine (rotary / positive displacement), including:

[0010] Components whose working parts perform only complete circular movements, including:

[0011] cylinder; a main shaft, the center of rotation of which coincides with the working center of the cylinder; a rotating shaft of a rotary piston, located on one side of the inner part of the main shaft and configured to maintain (with the possibility of rotation / reversal) an eccentric interval (d) relative to the main shaft; a rotary piston, the center of which is eccentric relative to the rotating shaft of the rotary piston by a distance (r) equal to the eccentric interval (d) (d = r); and a rotation ratio limiting device configured to limit the ratio between the angular velocity (x) of rotation of the main shaft and the angular velocity (y) of rotation of the rotating shaft of the rotary piston to a ratio of 1:2.

[0012] All this is provided to initiate the working process of changing the volume due to the interaction between the cylinder (rotating) and the rotary piston, which perform exclusively full circular movements.

[0013] The work process can be mathematically justified;

[0014] The components can be configured as mechanical components that can actually function from a technical point of view;

[0015] The friction portion between the cylinder (rotating) and the rotary piston may not be subjected to high pressure force despite the high pressure of the compressed fluid; and

[0016] multiple stages of cylinders and pistons can be combined into a single configuration or formed as a single unit, similar - from a design point of view - to a cylindrical rotating shaft, so that each of the stages can be limited by the rotation coefficient when rotating relative to each other, despite the multi-stage structure.

[0017] In addition, a plurality of stages can be freely formed at any angle (such as 0 degrees, 60 degrees, 120 degrees, etc.) with an arrangement that satisfies the condition of the angular velocity (x) of the rotating cylinder and the angular velocity (y = 2x) of the rotary piston.

[0018] Furthermore, according to the design of the hydraulic machine, the cylinder (rotating) and rotary piston, structurally combined into multiple stages, are arranged so that their center of gravity is always at the center of rotation, as in a cylindrical rotating shaft. This prevents vibrations such as precessional motion or reciprocating vibrations, as in reciprocating pistons and connecting rods. Thus, the mechanical mechanism can be shaped as a closed circle and a straight line, minimizing the difficulties in high-precision mechanical production, as is the case with worm-type machines (including auger machines).In addition, the production of a hydraulic machine (rotary / volumetric) may involve the mechanical processing of only circles and straight lines, which allows for their mass production to be set up at a significantly lower cost, even when manufactured with high precision, while vibrations can be significantly reduced or eliminated altogether.

[0019] According to the present invention, a hydraulic machine (rotary / positive displacement) configured to initiate and generate a volume change through the interaction of a cylinder (rotating) and a rotary piston, which respectively perform full circular motions during rotation, can have many advantages, namely: its operation with full circular motions does not cause precession motion or reciprocating inertial change, resulting in almost no vibration; there is no abrasion and friction loss caused by the high-pressure conversion fluid that exerts pressure on the cylinder wall as in reciprocating type machines; only the pure pressure of the high-pressure conversion fluid can act directly on the rotary piston, which reduces abrasion and improves the energy conversion efficiency of the fluid;In terms of mechanical mechanisms, a closed circle or straight line design can be achieved, which facilitates high-precision production at low cost without requiring a separate dedicated processing machine; and the mass production of such machines can be facilitated from a technical / commercial point of view.

[0020] In addition, according to the design of the hydraulic machine, the rotation coefficient limiting device includes a gear transmission.

[0021] Brief description of drawings

[0022] Fig. 1 is an exploded perspective view illustrating a hydraulic machine with a cylinder formed / fixed on a housing according to a basic embodiment of the present invention.

[0023] Fig. 2 is a view illustrating the operating principle and process of operation of a hydraulic machine (including a fixed cylinder) according to the present invention.

[0024] Fig. 3 shows a basic view that mathematically justifies the operating principle of a hydraulic machine (including a fixed cylinder) according to the present invention, in which:

[0025] the rotation center C1 of the rotary piston and the rotation center C2 of the main shaft are separated from each other by a distance equal to the eccentric interval d;

[0026] the center distance r, which is the interval between the center C3 of the rotary piston and the center C1 of rotation of the rotary piston and formed with the same interval, forms an isosceles figure with the center line S1 of the cylinder (fixed) as the base during the entire working process, and when the angular velocity (y) of the center (C1) of rotation of the rotary piston and the angular velocity (x) of the center (C2) of rotation of the main shaft satisfy the ratio y:x = 2:1, this view displays the relationship that mathematically justifies that the center C3 of the rotary piston always coincides with the center line S1 of the cylinder (fixed).

[0027] Fig. 4 is a sectional view illustrating a hydraulic machine assembly according to the present invention.

[0028] Fig. 5 is a perspective view in section illustrating a hydraulic machine according to the present invention in an assembled state.

[0029] Fig. 6 is an exploded perspective view illustrating a hydraulic machine according to the present invention, which is one embodiment of the present invention obtained by modifying the hydraulic machine shown in Fig. 1 to give it a more technically acceptable and practical configuration, and which includes a cylinder formed / fixed on a housing, a main shaft, a separate eccentric shaft, a separate rotating / rotary shaft and a rotary piston.

[0030] Fig. 7 is a perspective view illustrating the external appearance of the hydraulic machine according to the present invention shown in Fig. 6 in an assembled state.

[0031] Fig. 8(A) and 8(B) are sectional perspective views illustrating the hydraulic machine according to the present invention shown in Fig. 7 in an assembled state.

[0032] Fig. 9 is a sectional view illustrating the hydraulic machine according to the present invention shown in Fig. 7 in an assembled state.

[0033] Fig. 10 is a sectional view illustrating one example of the implementation of a part of the transmission mechanism of the hydraulic machine according to the present invention, shown in Fig. 6, in which the rotation coefficient limiting device, configured to limit the angular velocity (x) of the center (C2) of rotation of the main shaft and the angular velocity (y) of the center (C1) of rotation of the rotary piston by a ratio of x:y = 1:2, is configured in the form of a four-stage gear transmission.

[0034] Fig. 11 shows a view illustrating the operating principle and process of operation of a hydraulic machine according to the present invention in technically acceptable and practical configurations (including with a fixed cylinder).

[0035] Fig. 12 is a view illustrating a hydraulic machine according to the present invention (including a fixed cylinder) consisting of several stages for compensating for vibration.

[0036] Fig. 13 is an exploded perspective view illustrating a hydraulic machine according to one embodiment of the present invention, which, unlike the hydraulic machines shown in Figs. 1 and 6, includes a rotating cylinder (rather than a stationary cylinder).

[0037] Fig. 14 is a perspective view illustrating the external appearance of a hydraulic machine according to the present invention in an assembled state.

[0038] Fig. 15 is a sectional view illustrating one example of the implementation of the transmission mechanism of the hydraulic machine according to the present invention, shown in Fig. 13, in which the rotation coefficient limiting device, configured to limit the angular velocity (x) of the center (C2) of rotation of the rotating cylinder and the angular velocity (y) of the center (C1) of rotation of the rotary piston by a ratio of x:y = 1:2, is configured in the form of seven gears of a four-stage gear transmission.

[0039] Fig. 16 is a view illustrating a hydraulic machine according to the present invention, which shows the operating principle and process of operation of the hydraulic machine, which includes, in contrast to the hydraulic machine shown in Fig. 2, a rotating cylinder (rather than a stationary cylinder).

[0040] Fig. 17 is a basic view that mathematically justifies the operating principle of the hydraulic machine (including a rotating cylinder) according to the present invention, in which the rotation center C1 of the rotary piston and the rotation center C2 of the rotating cylinder are spaced from each other by a distance equal to the eccentric interval d; and the center-to-center distance r, which is the interval between the center C3 of the rotary piston and the rotation center C1 of the rotary piston and is formed with the same interval, forms an isosceles figure with the center line S1 of the rotating cylinder as the base during the entire working process; and

[0041] When the angular velocity (y) of the rotation center (C1) of the rotary piston and the angular velocity (x) of the rotation center (C2) of the main shaft satisfy the ratio x:y=1:2, this view displays the relationship that mathematically justifies that the center C3 of the rotary piston always coincides with the center line S1 of the rotating cylinder during its operation.

[0042] Fig. 18 is an exploded perspective view illustrating a hydraulic machine according to the present invention, in which a pair consisting of a rotating cylinder and a rotary piston has a multi-stage configuration (for example, x = 0 degrees, 60 degrees or 120 degrees, and y = 2x = 0 degrees, 120 degrees or 240 degrees).

[0043] Fig. 19 is a view illustrating examples of the implementation of a rotating cylinder (for example, x = 0, 60 or 120 degrees) located at different angles, and a rotary piston (y = 0, 120 or 240 degrees) located at different angles relative to the rotating cylinder, satisfying the condition y = 2x, as shown in Fig. 18.

[0044] Fig. 20 is a sectional view illustrating a pair consisting of a rotating cylinder and a rotary piston according to the present invention.

[0045] Fig. 21 is a view showing the following: when the rotating cylinder and the rotary piston according to the present invention are designed to form a single-stage configuration, a state in which power transmission is impossible (dead zone) occurs (views (A) and (B)), and when the rotating cylinders and the rotary pistons are designed to form a multi-stage configuration and are mechanically connected to each other (the cylinders form a single unit and the rotary pistons are connected to each other (C)), the rotating cylinders and the rotary pistons can perform the function of a plurality of internal gear teeth (rotary cylinders) and a plurality of gear teeth (rotary pistons) at a ratio of 1:2, which is achieved by a rotation ratio limiting device, so that the rotating cylinder-rotary piston pair forming the multi-stage configuration can perform the function of gears (views (C) and (D)).

[0046] Fig. 22 is a view illustrating a hydraulic machine according to the present invention, having a structure in which a cavity 10h is formed so that the center of gravity of the rotary piston of the hydraulic machine P can be located at the center of the rotation axis.

[0047] Fig. 23 is a view illustrating a hydraulic machine according to the present invention, where one hydraulic machine P can be connected to an active machine (a driving device (electric motor, engine, etc.)), and another hydraulic machine P can be connected to a passive machine (a wheel of a vehicle, a rotor of an aircraft, etc.), wherein the hydraulic machines P connected to the active machine and the passive machine are connected by means of a closed circuit of a working fluid (a tube, a high-pressure hose, etc.), so that an offset of the rotational magnitude and an offset of the torque magnitude are formed between the active and passive machines, or an SV valve is added to the closed circuit of the working fluid for separate control of the offsets.

[0048] Fig. 24 is a view illustrating a hydraulic machine according to the present invention, where one hydraulic machine P can be connected to an active machine (a driving device (electric motor, engine, etc.)), and a multi-stage (P) hydraulic machine Pn is provided, formed by installing several other hydraulic machines P, forming a multi-stage configuration, in one housing and connecting one output rotating shaft with a plurality of stages, wherein the hydraulic machine P and the multi-stage (P) hydraulic machine Pn are connected by means of a closed circuit of working fluid (a tube, a high-pressure hose, etc.), and in a multi-stage connection, a plurality of valves SV are added to the closed circuit of the working fluid, designed with the possibility of regulating the flow of the working fluid, so that on the output rotating shaft of the multi-stage (P) hydraulic machine Pn, the displacements of the rotation value R2 and the torque value relative to the rotation value R1 and the torque value of the active machine (drive device (electric motor, engine, etc.)) can be adjusted.

[0049] Fig. 25 is a view illustrating the mathematical model of the input-output of the hydraulic machine according to the present invention shown in Fig. 23, which is expressed by the formulas 2d*COS(F) and 2d*COS(F - 90) (= 2d*sin(F)) in the sectional view (A), in the perspective view (B) of the external appearance of this hydraulic machine and in the graph (C).

[0050] Fig. 25(A) is a view illustrating the hydraulic machine according to the present invention shown in Fig. 23 and 24, which shows the formula 2d*COS(F) for the “rotary cylinder-rotary piston” pair of the hydraulic machine.

[0051] Fig. 25(B) is a view illustrating the hydraulic machine according to the present invention shown in Fig. 23 and 24, in which the hydraulic machine P is configured such that the rotary cylinder-rotary piston pair and another pair added to it with a phase shift of 90 degrees are inserted into one housing, and these pairs are connected by one shaft.

[0052] Fig. 25(C) shows graphs illustrating the hydraulic machine according to the present invention shown in Fig. 23 and 24, which show the suction / discharge characteristics of the hydraulic machine P, expressed by the formula (2d*COS(F) + 2d*COS(F - 90)).

[0053] Fig. 26(A) and 26(B) are taken from the view with mathematical justification illustrating one pair of the hydraulic machine according to the present invention in Fig. 3 and 17.

[0054] Fig. 26(C) shows a view mathematically justifying that for the distance displacement dPS between the rotating cylinder and the rotary piston (or the distance displacement between the cylinder and the rotary piston), the distance displacement characteristic (dPS) is proportional to COS(F) in the hydraulic machine according to the present invention shown in Fig. 23 and 24.

[0055] Fig. 26(D) is a view illustrating the total suction / discharge volume in the half-cylinder of one pair in one stroke, which is calculated based on the distance displacement dPS = 2d*COS(F) obtained from Fig. 26(C).

[0056] Fig. 27 is a view illustrating the application of the hydraulic machine according to the present invention shown in Fig. 23 in a vehicle.

[0057] Fig. 28 is a view illustrating an example of using the hydraulic machine according to the present invention shown in Fig. 23 in an unmanned aerial vehicle (UAV), so that the UAV can fly by controlling four rotors with one electric motor, without using four drive devices to control the rotors, respectively.

[0058] Fig. 29 is a view illustrating an example of the application of the hydraulic machine according to the present invention, shown in Fig. 23, in the rotor of an aircraft, so that the aircraft can fly without a propeller shaft, transmission or other elements of the same kind that connect the main engine to the tail wing.

[0059] Figure 30 is a view illustrating the application of the hydraulic machine according to the present invention, shown in Figure 23, in a watercraft. Traditionally, to connect a propeller located outside the vessel to an engine located inside the vessel, a hole was drilled in the hull for connection to the main shaft, which required numerous devices to prevent water penetration from the outside and carried associated risks. The present invention is an example of an application that ensures absolute watertightness, allowing power transmission without drilling a hole for the shaft in the vessel's hull.

[0060] Detailed Disclosure of the Present Invention

[0061] According to the present invention, in order to achieve the above objectives, a hydraulic machine is proposed, including:

[0062] fixed cylinder formed in the main body;

[0063] a main shaft having a rotation center that coincides with the working center of the cylinder;

[0064] a rotating shaft of a rotary piston, configured to rotate and rotate, wherein the rotating shaft of the rotary piston is installed on one side of the inner portion of the main shaft and is configured to maintain an eccentric interval (d) relative to the main shaft;

[0065] a rotary piston, the center of which is eccentric with respect to the rotating shaft of the rotary piston by a distance (r) that is equal to the eccentric interval (d) (d = r); and

[0066] a rotation ratio limiting device configured to limit the ratio between the angular velocity (x) of rotation of the main shaft and the angular velocity (y) of rotation of the rotating shaft of the rotary piston to a ratio of 1:2.

[0067] The rotation coefficient limiting device includes a gear transmission.

[0068] A cavity is provided on one side of the rotary piston, which is initially heavy, so that the center of gravity coincides with the center of rotation, eliminating vibration that may occur due to eccentric rotation.

[0069] Furthermore, according to the present invention, in order to achieve the objectives stated above, a hydraulic machine is proposed, including:

[0070] cylinder (fixed) formed in the main body;

[0071] a main shaft having a rotation center that coincides with the working center of the cylinder;

[0072] an eccentric shaft fixed to the main shaft and configured to rotate and maintain an eccentric interval (d) relative to the main shaft;

[0073] rotary / turning shaft, configured to rotate and rotate on an eccentric shaft;

[0074] a rotary piston rotatably coupled to a rotating / turning shaft and having a center that is eccentric with respect to the rotating / turning shaft by a distance (r) equal to an eccentric interval (d) (d = r); and

[0075] a rotation ratio limiting device configured to limit the ratio between the angular velocity (x) of rotation of the main shaft and the angular velocity (y) of rotation of the rotary piston to a ratio of 1:2.

[0076] The rotation coefficient limiting device includes a gear transmission.

[0077] The rotation coefficient limiting device may include:

[0078] a drive gear connected to the main shaft and configured to rotate in accordance with the rotation of the main shaft;

[0079] secondary planetary gear connected to the driving gear so as to rotate;

[0080] a third stage gear connected internally to the secondary planetary gear and configured to rotate so that its rotation axis coincides with the rotation axis of the main shaft; and

[0081] a fourth-stage gear, internally connected to a third-stage gear with the ability to rotate, mounted on one side of the rotating / turning shaft and configured to rotate in such a way that its rotation axis coincides with the rotation axis of the rotary piston.

[0082] A cavity is provided on one side of the rotary piston, which is initially heavy, so that the center of gravity coincides with the center of rotation, eliminating vibration that may occur due to eccentric rotation.

[0083] Furthermore, according to the present invention, in order to achieve the objectives stated above, a hydraulic machine is proposed, including:

[0084] Rotating cylinder;

[0085] a rotary piston having such an eccentricity that its center of rotation maintains an eccentric interval (d) relative to the center of rotation of a rotating cylinder, and having a center (center of a mechanical structure) that is eccentric relative to the rotary piston by a distance (r) equal to the eccentric interval (d) (d = r); and

[0086] a rotation ratio limiting device configured to limit the ratio between the angular velocity (x) of rotation of the rotating cylinder and the angular velocity (y) of rotation of the rotary piston to a ratio of 1:2.

[0087] The rotation coefficient limiting device may include a gear transmission.

[0088] A plurality of pairs, each including a rotating cylinder and a rotary piston, may be arranged in a plurality of stages; and

[0089] each stage may be part of a multi-stage configuration in which the axis of the rotating cylinder (perpendicular to the axis of rotation) and the center of the rotary piston (the center of the circular mechanical structure) may be positioned such that the offset angle (y) of the center of the rotary piston is twice the offset angle (x) of the axis of the rotating cylinder (y = 2x), wherein a pair of reference points with a zero angle are taken as a basis (e.g., (x = 0, y = 0), (x = 60, y = 120), or (x = 120, y = 240)).

[0090] The rotation coefficient limiting device may be configured to be replaceable in a multi-stage configuration in which:

[0091] a plurality of pairs, each of which includes a rotating cylinder and a rotary piston, may be arranged in a plurality of stages; and

[0092] pairs, each of which is designed in such a way that the angle (y) of the rotary piston is twice the angle (x) of the rotating cylinder (y = 2x), can be arranged in a multi-stage configuration at different angles;

[0093] whereby pairs, each including a rotating cylinder and a rotary piston, can function as if a two-tooth internal gear (rotary cylinder) interacts with a single-tooth gear (rotary piston);

[0094] which limits the rotation ratio to 1:2.

[0095] A cavity is provided on one side of the rotary piston, which is initially heavy, so that the center of gravity coincides with the center of rotation, eliminating the vibration that may occur due to eccentric rotation.

[0096] Furthermore, according to the present invention, in order to achieve the objectives stated above, a hydraulic machine is proposed, including:

[0097] Rotating cylinder;

[0098] a rotary piston having such an eccentricity that its center of rotation maintains an eccentric interval (d) relative to the center of rotation of a rotating cylinder, and having a center (center of a mechanical structure) that is eccentric relative to the rotary piston by a distance (r) equal to the eccentric interval (d) (d = r);

[0099] a rotation coefficient limiting device in which:

[0100] Two pairs, each including a rotating cylinder and a rotary piston, are connected in two stages;

[0101] One pair stage is configured so that the liquid output is proportional , based on angle of the rotating cylinder and the angle piston:

[0102] The other paired stage is configured in such a way that the phase shift of the working fluid by ±90 degrees is provided by such an arrangement and connection that provides an angle rotating cylinder and the angle y = 2x = 180 of the piston, so that the liquid output is proportional (or ; And

[0103] the ratio limiting device is configured to limit the ratio between the angular velocity (x) of rotation of the rotating cylinder and the angular velocity (y) of rotation of the rotary piston to a ratio of 1:2; and

[0104] hydraulic machine (P) formed by connecting two pairs representing two stages, so that suction / discharge is carried out in the form of a constant flow, while:

[0105] one hydraulic machine (P) is connected to an active machine (drive device (electric motor, engine, etc.));

[0106] another hydraulic machine (P) is connected to a passive machine (vehicle wheel, aircraft rotor, etc.); and

[0107] two hydraulic machines (P), connected, respectively, to an active machine and a passive machine, are connected by means of a closed circuit of working fluid (tube, high-pressure hose, etc.);

[0108] so that rotation magnitude / torque magnitude offsets are formed between the active and passive machines.

[0109] A valve (SV) capable of regulating the flow of working fluid can be added to the closed circuit of the working fluid, thereby making it possible to correct the rotational / torque value offsets for each passive machine.

[0110] The rotation coefficient limiting device may include a gear transmission.

[0111] The rotation coefficient limiting device can be configured to be replaceable, wherein a plurality of pairs, each of which includes a rotating cylinder and a rotary piston located at different angles, are arranged in the form of a plurality of stages.

[0112] Furthermore, according to the present invention, in order to achieve the objectives stated above, a hydraulic machine is proposed, including:

[0113] Rotating cylinder;

[0114] a rotary piston having such an eccentricity that its center of rotation maintains an eccentric interval (d) relative to the center of rotation of a rotating cylinder, and having a center that is eccentric relative to the rotary piston by a distance (r) equal to the eccentric interval (d) (d = r);

[0115] a rotation coefficient limiting device, in which:

[0116] Two pairs, each including a rotating cylinder and a rotary piston, are connected in two stages;

[0117] One paired stage is configured so that the liquid output is proportional , based on the angle rotating cylinder and angle piston:

[0118] The other paired stage is configured in such a way that for a phase shift of ±90 degrees, such an arrangement and connection is provided that provides an angle rotating cylinder and the angle y = 2x = 180 of the piston, so that the liquid output is proportional ; And

[0119] the ratio limiting device is configured to limit the ratio between the angular velocity (x) of rotation of the rotating cylinder and the angular velocity (y) of rotation of the rotary piston to a ratio of 1:2;

[0120] a hydraulic machine (P) formed by connecting together two pairs representing two stages so that the suction / discharge is carried out in the form of a constant flow; and

[0121] a multi-stage hydraulic machine (Pn) formed by connecting hydraulic machines (P) in a multi-stage configuration (P*n), so that one output rotating shaft is formed in one housing; wherein:

[0122] The hydraulic machine (P) is connected to the active machine (drive device (electric motor, engine, etc.));

[0123] the hydraulic machine (P) and the multi-stage hydraulic machine (P*n) are connected by means of a closed circuit of the working fluid (tube, high-pressure hose, etc.); and

[0124] a plurality of (SV*n) valves are added to the closed circuit of the working fluid, designed with the ability to regulate the flow of the working fluid of each stage, forming a hydraulic machine of a multi-stage configuration (P*n);

[0125] so that it is possible to shift and adjust the rotation value applied to the output rotating shaft of the multi-stage hydraulic machine (Pn) relative to the rotation value of the output shaft of the active machine and the torque value.

[0126] The rotation coefficient limiting device may include a gear transmission.

[0127] The rotation coefficient limiting device can be configured to be replaceable, wherein a plurality of pairs, each of which includes a rotating cylinder and a rotary piston located at different angles, are arranged in the form of a plurality of stages.

[0128] Hereinafter, the hydraulic machine according to the present invention will be described in detail in connection with the accompanying drawings.

[0129] Fig. 1 is an exploded perspective view illustrating a hydraulic machine according to the present invention.

[0130] The main shaft 12 can be installed so as to rotate relative to the working center of the cylinder (fixed) formed in the housing, and an eccentric shaft 11a (planetary rotating / rotary shaft) with an eccentricity equal to a distance d can be installed inside the main shaft;

[0131] a rotary piston 10 can rotate on an eccentric shaft, and the center of its circular mechanical structure is characterized by an eccentricity relative to the center of rotation equal to a distance r(= d); and

[0132] The eccentric shaft 11a and the main shaft 12 can be connected to each other in such a way that their angular speeds of rotation are in a ratio of 2:1, which is achieved by using a rotation ratio limiting device consisting of a gear engagement 113g of the eccentric shaft and a gear engagement 311g formed so as to ensure that they coincide with the center of rotation of the main shaft.

[0133] In other words, the angular velocity (y) of the center (C1) of rotation of the rotary piston and the angular velocity (x) of the center (C2) of rotation of the main shaft can be limited by the ratio y:x = 2:1.

[0134] Thus, although all the parts perform exclusively full circular motion, a volume change similar to a reciprocating piston-cylinder can be achieved, eliminating the need to convert circular motion into linear motion, as is the case with a crank and connecting rod. Friction and abrasion losses caused by the sliding of the piston when applying force to the cylinder wall during the conversion process can be eliminated; and the likelihood of vibration can be reduced. Furthermore, in terms of the manufacturing process, since all the components of the parts are shaped like circles and straight lines, they can be manufactured with high precision without the need for a special machine for processing complex structures, as is the case with worm-type hydraulic machines. This facilitates their industrial application and mass production, and further simplifies the components and structures.

[0135] Fig. 2 is a view illustrating the operating principle and process of the hydraulic machine according to the present invention, shown in Fig. 1, wherein:

[0136] One cycle can be completed by performing steps (a)-(h)-(a).

[0137] In steps (a)-(b), when the main shaft 12 rotates counterclockwise, the rotary piston can rotate clockwise due to the gear meshing 113g of the eccentric shaft of the rotary piston 10, which meshes with the gear meshing 311g formed in the housing, with an angle of rotation twice that of the eccentric shaft, and the center C3 of the rotary piston (the geometric center of its circular structure) can move to the right along the working axis S1 of the cylinder. This operation can cause the volume between the cylinder and the rotary piston to expand, and liquid can begin to be sucked into the vacuum space formed due to this expansion.

[0138] After passing through steps (c)-(d), the suction can be completed during step (e) when:

[0139] The main shaft has rotated 180 degrees counterclockwise, and

[0140] Rotary piston and shaft The rotary piston rotates and makes a clockwise rotation of 360 degrees (180*2) (with a rotation ratio (2:1) provided by the rotation ratio limiting device consisting of the eccentric shaft gear mesh of 113g and the gear mesh of 311g), while rotating 180 degrees (counterclockwise - around the rotation center of the main shaft).

[0141] At stages (e) to (f), the rotary piston 10 that has passed the right upper point of the cylinder can continue to rotate and circulate, while the main shaft continues to rotate counterclockwise, so that the rotary piston 10 can start to move to the left to enter the pumping stage.

[0142] After passing through stages (g)-(h), the injection process can be completed during stage (a) when:

[0143] The main shaft has rotated 180 degrees counterclockwise, and

[0144] The rotary piston and the rotary piston shaft 11a rotate and complete a clockwise rotation of 720 degrees (360*2) (with a rotation ratio (2:1) provided by the rotation ratio limiting device consisting of the eccentric shaft gear mesh 113g and the eccentric shaft gear mesh 311g), rotating 360 degrees (counterclockwise - around the rotation center of the main shaft), which completes one cycle.

[0145] Fig. 3 is a view that mathematically justifies the operating process illustrated in Fig. 2, where it is mathematically proven that since the main shaft and the rotary piston (which rotates and revolves around the main shaft) rotate, respectively, with angular velocities (x) and (y), as shown in Fig. 2, and

[0146] The rotation of the main shaft and the rotary piston is limited by a rotation ratio of 1:2 = x:y, provided by a rotation ratio limiting device consisting of a 113g gear engagement of the eccentric shaft and a 311g gear engagement,

[0147] The eccentricity center C3 of the rotary piston is always located on the cylinder centerline S1.

[0148] In other words, as shown in Fig. 3, since the sum of the interior angles of triangle c1c2c3 is 180 degrees, then

[0149]

[0150] In this case, since a = (180 - y), then

[0151]

[0152] If the variables, except y, are moved to the right side, then the following is obtained:

[0153]

[0154] In this case, since the distance d (the eccentricity between the rotation center C2 of the main shaft and the rotation center C1 of the rotary piston) is designed to be equal to the value r (the distance between the rotation center C1 of the rotary piston and the rotation center C3 of the rotary piston), d = r.

[0155] Therefore,

[0156] since triangle c1c2c3 is isosceles, where d = r,

[0157] angle x = c.

[0158] Accordingly, based on formula 3 we obtain the following:

[0159]

[0160] (in other words, when the state in which the angle x = c (“d = r”, since the triangle is isosceles), and there is a constraint y = 2x,

[0161] i.e. the rotation coefficient is limited by the ratio y:x = 2:1, point C3 will always be located in such a way that it will coincide with the centerline S1 of the cylinder).

[0162] In other words, what does formula 4 prove,

[0163] when the main shaft 12 rotates with angular velocity (x) at point C2 (coinciding with the center of cylinder 20f), and

[0164] while standing at a certain distance from point C2 (the center of rotation of the main shaft),

[0165] The eccentric shaft (the rotation center C1 of the rotary piston) rotates at an angular velocity y (= 2x), which is twice the rotation speed of the main shaft at a limited ratio,

[0166] and this proves mathematically,

[0167] that the center C3 of eccentricity of the rotary piston 10 will always be located in such a way that

[0168] that it coincides with the center line S1 of the cylinder.

[0169] Fig. 4 is a sectional view illustrating the hydraulic machine according to the present invention shown in Fig. 1 in an assembled state.

[0170] Fig. 5 is a perspective sectional view illustrating the hydraulic machine according to the present invention shown in Fig. 1 in an assembled state. From the descriptions of Figs. 2 and 3, the operation and relationship of the cylinder 20f, the rotary piston 10, the rotary piston shaft 11a, the central gear 311g in the side wall of the cylinder body, and the gear 113g of the rotary piston shaft can be more clearly understood.

[0171] Fig. 6 is an exploded perspective view illustrating a hydraulic machine according to the present invention, and this hydraulic machine, the basic principle structure of which is shown in Fig. 1, is applied and realized in practice for transmitting and receiving a large force from the viewpoint of technical solutions, as well as for smooth operation with less wear. In addition, in a multi-stage configuration (since the hydraulic machine shown in Fig. 1 has a structure in which the main shaft cannot enter the rotary piston to pass into the cylinder of the next stage, since the rotary piston is forced to rotate and revolve only on one side of the main shaft (a structure unfavorable for forming a plurality of stages), and both shafts of the main shaft and the rotary piston shaft are supported only on one side, this structure has many disadvantages related to force transmission, uneven wear, etc., from the point of view of technical solutions, compared to a design that is supported on both sides by bearings), the design of the hydraulic machine can be improved to provide a multi-stage configuration.

[0172] In other words, as shown in Fig. 6, certain technical improvements can be made to the hydraulic machine according to the present invention shown in Fig. 1 and to its application, namely:

[0173] The eccentric shaft 113c can be connected to the outside of the main shaft 112 (as a crank structure), the rotating / turning shaft can rotate outside the eccentric shaft 113c, and the rotary piston 10 can be integrally formed with the rotating / turning shaft 113p so as to be rotatably formed, so that the main shaft 112 can pass through both ends of the rotary piston 10 and through both side walls of the cylinder body, supported by a bearing so as to be rotatably formed (a structure that is easy to configure in multiple stages at the production stage).

[0174] Between the rotation center of the main shaft 112 and the rotation center of the eccentric shaft 113c installed outside the shaft 112, there may exist an eccentricity difference equal to a distance d.

[0175] Between the rotation center of the rotary piston 10 and the center C3 of the circular structure of the rotary piston 10, there may be an eccentricity difference equal to the distance r, and the distances d and r must be equal to each other, satisfying the condition d = r.

[0176] (In other words, in the structure shown in Fig. 1, the rotating / turning shaft, the rotary piston shaft, and the rotary piston can rotate inside the main shaft, so that the main shaft and the rotary piston shaft can be locked relative to each other. Therefore, the main shaft and the rotary piston shaft can be provided only on one side, and their expansion toward the side walls of the housings on both sides may not be possible (a structure that is difficult to expand to a multi-stage configuration)).

[0177] The housing 30, in which the cylinder 20f is provided, can be configured such that the side wall 301w, connected to the third stage gear 43g for supporting it, the side wall 31w, connected to the shaft 42s of the secondary planetary gear 42g and the main shaft bearing for supporting them, and the side wall 32w of the bearing cover can be connected in series, and suction / discharge holes 30a and 30b can be formed on the middle outer wall.

[0178] A gear engagement 44g can be formed at both ends of the rotating / turning shaft 113p, and the rotating / turning shaft 113p itself can be connected to the rotary piston 10 via a key 70 so that they can rotate as a single unit.

[0179] The rotation of the main shaft and the rotation of the rotary piston can be mutually limited in the ratio of 1:2;

[0180] wherein the driving gear 41g can be connected to one side of the main shaft 112, and the secondary gear 42g can embrace the main shaft 112 as a planetary gear; the internal gear 43g of the third stage can be connected to the upper part of the secondary gear 42g, supported by a bearing on the side wall of the housing so as to rotatably, and the gear 44g of the fourth stage of the rotating / rotary shaft can be connected to the opposite side of the gear 43g of the third stage, so that the main shaft 112 and the rotary piston 10 connected to the rotating / rotary shaft 113p, forming a single whole with it, can mutually restrict each other's rotation relative to the main shaft with a ratio of 1:2 (x:y = (rotation of the main shaft): (rotation of the rotary piston)).

[0181] Thus, complementing the advantages of the hydraulic machine according to the present invention shown in Fig. 1,

[0182] The hydraulic machine can be used, which has the advantages of higher durability, easier maintenance, more practical design, can be used for high-force liquid transformation, and has a multi-stage configuration, which ensures its scalability.

[0183] Fig. 7 is a perspective view illustrating the external appearance of the hydraulic machine according to the present invention shown in Fig. 6 in an assembled state.

[0184] Fig. 8(A) and 8(B) are sectional perspective views illustrating the hydraulic machine according to the present invention shown in Fig. 7 in an assembled state.

[0185] Fig. 9 is a sectional view illustrating a hydraulic machine according to the present invention in an assembled state, in which the relationship of the components is shown in more detail for better understanding.

[0186] Fig. 10 is a view illustrating a rotation ratio limiting device of the hydraulic machine according to the present invention shown in Fig. 6, which shows the process of connecting the driving gear 41g with the secondary gear 42g, the third-stage gear 43g and the fourth-stage gear 44g, which are formed in the form of gear wheels and are shown in corresponding cross-sections for ease of understanding. In this example, the rotation ratio limiting device, configured to limit the angular velocity (x) of the center (C2) of rotation of the main shaft and the angular velocity (y) of the center (C1) of rotation of the rotary piston by a ratio of x:y = 1:2, is formed in the form of a four-stage gear transmission.

[0187] Fig. 11 is a view illustrating the operation process of the hydraulic machine according to the present invention shown in Fig. 6.

[0188] One cycle can be completed by performing steps (a)-(b)-(c)-(d)-(a).

[0189] In steps (a) to (b), when the main shaft 12 rotates clockwise, since the gears 41g, 42g, 43g and 44g are connected to each other in a series pattern, the rotary piston 10 can rotate counterclockwise due to the fact that the gear 44g of the rotating / turning shaft is connected to the rotary piston with a rotation angle twice that of the eccentric shaft, and the center C3 of the rotary piston (the geometric center of its circular structure) can move to the right along the working axis S1 of the cylinder. This operation can cause the volume between the cylinder and the rotary piston to expand, and liquid can begin to be sucked into the vacuum space formed due to this expansion.

[0190] After passing step (b), the suction can be completed by performing process (c) when:

[0191] The main shaft has rotated 180 degrees clockwise, and

[0192] The rotary piston 10 has rotated and completed a 360 degree (180*2) counterclockwise rotation (with a rotation ratio (2:1) provided by a rotation ratio limiting device consisting of gears 41g, 42g, 43g and 44g connected in series with each other), while rotating 180 degrees (clockwise - around the rotation center of the main shaft).

[0193] At step (c), the rotary piston 10, which has passed the upper right point of the cylinder, can continue to rotate and circulate, while the main shaft 112 continues to rotate clockwise, so that the rotary piston 10 can start to move to the left to enter the pumping process.

[0194] After completing stage (c), the injection process can be completed during stage (a) when:

[0195] The main shaft has rotated 360 degrees clockwise, and

[0196] The rotary piston 10 has rotated and completed a revolution of 720 degrees (360*2) counterclockwise (with a rotation ratio (2:1) provided by a rotation ratio limiting device consisting of a gear of gears 41g, 42g, 43g and 44g connected in series with each other), while rotating 360 degrees (clockwise - around the rotation center of the main shaft), which completes one cycle.

[0197] Fig. 12 shows a view illustrating one example of the implementation of a hydraulic machine according to the present invention, where the hydraulic machine according to the present invention, shown in Fig. 6, consists of a plurality of stages.

[0198] A total of four pairs, each comprising a cylinder and a rotary piston, can be connected to form a single multi-stage hydraulic machine. This example shows how the connecting directions of the rotary pistons are configured so that their phases are aligned, allowing the rotary pistons to move in opposite directions. The directions of motion of two rotary pistons are 180 degrees opposite to those of the other two rotary pistons, thereby forming a single multi-stage hydraulic machine.

[0199] Fig. 13 is an exploded perspective view illustrating a hydraulic machine according to the present invention.

[0200] In other words, the same operation as the operation performed by the "rotating main shaft" can be performed by the "rotating cylinder", unlike the cylinder (stationary) shown in Fig. 1 and Fig. 6.

[0201] In other words, the rotating cylinder 20 may be installed in such a way as to ensure its alignment with the work center so as to be able to rotate, and the main shaft 122 may be installed inside the rotating cylinder with an eccentricity equal to a distance d,

[0202] on the main shaft 122, a rotary piston 10 can rotate, the center of the circular structure of which is located with an eccentricity relative to the center of rotation equal to the distance r (= d), and

[0203] the mutually limiting relationship in rotation coefficient between the rotating cylinder 20 and the rotary piston 10 can be configured such that:

[0204] gear 401g connected to the main shaft 122 which is connected to the rotary piston, gear 402g connected to gear 401g, gear 403ga connected to gear 402g, gear 403gb connected to one side of the same shaft as gear 403ga, gear 404ga connected to gear 403gb, gear 404gb connected to one side of the same shaft as gear 404ga and located on the opposite side of the reducer, and gear 405g connected to gear 404gb and mounted on one side of the rotating cylinder can be connected in series with each other, providing mutual limitation on the rotation ratio in the ratio of 1:2 (= x:y = (angle (x) of rotation of the rotating cylinder): (angle (y) of rotation of the rotary piston)).

[0205] Thus, although all parts perform exclusively full circular motion, a volume change similar to a reciprocating piston-cylinder can be achieved, eliminating the need to convert circular motion into linear motion, as is the case with a crank and connecting rod. Friction and abrasion losses caused by the piston sliding when applying force to the cylinder wall during the conversion process can be eliminated; and the likelihood of vibration can be reduced. Furthermore, in terms of the manufacturing process, since all components are shaped like circles and straight lines, high-precision manufacturing can be ensured without the need for a specialized machine for processing complex structures, as is the case with worm-type hydraulic machines. The components and structures can be further simplified.

[0206] Fig. 14 is a perspective view illustrating the external appearance of the hydraulic machine according to the present invention shown in Fig. 13 in an assembled state.

[0207] Fig. 15 is a sectional view illustrating a rotation coefficient limiting device including seven gears 401g, 402g, 403ga, 403gb, 404ga and 404gb of a four-stage gear transmission of a hydraulic machine according to the present invention shown in Fig. 13, wherein said device is shown in two interconnected partial sections.

[0208] Fig. 16 is a view illustrating the operating principle and process of the hydraulic machine according to the present invention shown in Fig. 13, in which one cycle can be completed by performing steps (a)-(h)-(a).

[0209] In steps (a)-(b), when the rotary piston 10 connected to the main shaft 122 rotates clockwise, due to the seven gears 401g, 402g, 403ga, 403gb, 404ga and 404gb of the four-stage gear transmission configured as a rotation ratio limiting device, the rotating cylinder 20:

[0210] can rotate clockwise at an angle that is 1 / 2 of the rotation angle of the rotary piston (where the rotation angle (y) of the rotary piston is twice the rotation angle (x) of the rotating cylinder (y=2x)), and the center C3 of the rotary piston (its round structure) can move along the working axis S1 of the cylinder, thereby increasing the clearance between the rotating cylinder and the rotary piston.

[0211] This operation may cause the volume between the rotating cylinder and the rotary piston to expand, and liquid may be drawn into the vacuum created by this expansion.

[0212] After going through stages (c)-(d), the injection process can be completed during stage (e) when:

[0213] the rotating cylinder 20 rotated 180 degrees clockwise (x), and

[0214] The rotary piston 10 has rotated 360 degrees (180*2) clockwise (y) (with a rotation ratio (1:2 = x:y) provided by the rotation ratio limiting device).

[0215] At stages (e)-(f), when the rotary piston 10 continues to rotate clockwise, the gap between the rotating cylinder and the rotary piston can pass the maximum peak value and then narrow, so that the fluid pressure can begin to increase to enter the pumping stage.

[0216] After passing through stages (g)-(h), the injection process can be completed during stage (a) when:

[0217] the angle (x) of rotation of the rotating cylinder has rotated 360 degrees clockwise, and

[0218] The rotation angle (y) of the rotary piston has rotated 720 degrees (360*2) clockwise with the rotation ratio (1:2 = x:y) provided by the mutually limiting rotation ratio limiting device, which completes one cycle.

[0219] Fig. 17 shows a view that mathematically justifies the operating process illustrated in Fig. 16, which mathematically proves that,

[0220] since the rotating cylinder 20 and the rotary piston 10 connected to the main shaft 112 rotate, respectively, with angular velocities (x) and (y), and

[0221] the rotation of the rotating cylinder 20 and the rotary piston 10 is mutually limited by the ratio 1:2 = x:y, provided by the rotation ratio limiting device,

[0222] The center C3 of the rotary piston (its mechanical structure) always coincides with the center line S1 of the rotating cylinder during its operation.

[0223] In other words, as shown in Fig. 17, since the sum of the interior angles of triangle c1c2c3 is 180 degrees, then

[0224]

[0225] In this case, since a = (180 - y), then

[0226]

[0227] If the variables, except y, are moved to the right side, then the following is obtained:

[0228]

[0229] In this case, since the distance d (the eccentricity between the rotation center C2 of the rotating cylinder and the rotation center C1 of the rotary piston) is designed to be equal to the value r (the distance between the rotation center C1 of the rotary piston and the rotation center C3 of the rotary piston, coinciding with the center of its mechanical structure), d = r.

[0230] Therefore,

[0231] since triangle c1c2c3 is isosceles, where d = r,

[0232] angle x = c.

[0233] Accordingly, based on formula 3 we obtain the following:

[0234]

[0235] (in other words, when the state in which the angle x = c (“d = r”, since the triangle is isosceles), and there is a constraint y = 2x,

[0236] i.e. the rotation coefficient is limited by the ratio 1:2 = x:y, point C3 will always be located in such a way that it will coincide with the axial line S1 of the rotating cylinder).

[0237] In other words, what does formula 4 prove,

[0238] when the rotating cylinder 20 rotates with angular velocity (x) at point C2 (coinciding with the center of the rotating cylinder), and

[0239] while standing at a distance d from point C2 (the center of rotation of the rotating cylinder),

[0240] the center C1 of rotation of the rotary piston is limited to rotation with an angular velocity (y) (= 2x), which is twice the angular velocity (x) of rotation of the rotating cylinder,

[0241] and this proves mathematically,

[0242] that the geometric center C3 of the circular structure of the rotary piston 10 is always located in such a way that

[0243] that it coincides with the center line S1 of the rotating cylinder.

[0244] Fig. 18 and 19 are views illustrating examples in which the hydraulic machines according to the present invention shown in Fig. 13 and 17 have a multi-stage configuration.

[0245] To achieve the multi-stage configuration of a pair that includes a rotating cylinder and a rotary piston, when the next stage is set to "arbitrary value x1", the value of y1 shall be set to "twice the arbitrary value x1" based on the equalities x=0 and y=0 for the reference pair (stage).

[0246] In other words, for example, in order to satisfy the operating principle illustrated in Fig. 17, the reference first stage must satisfy the equalities x = 0 and y = 0, the next second stage must satisfy the equalities x = 60 and y = 2x = 120, and the third stage must satisfy the equalities x = 120 and y = 2x = 240.

[0247] Fig. 18 and 19 are views illustrating examples in which the hydraulic machines according to the present invention have a three-stage configuration.

[0248] Fig. 20 is a sectional view illustrating the structure of one pair consisting of a rotating cylinder and a rotating piston in the hydraulic machine according to the present invention shown in Fig. 18.

[0249] Fig. 21 is a view illustrating the following: when the rotating cylinder and the rotary piston performing rotation according to the present invention are designed so as to form a single-stage configuration, a state occurs in which a dead zone is formed in which power transmission is impossible (views (A) and (B)), and when the rotating cylinders and rotary pistons are designed so as to form a multi-stage configuration and are mechanically connected to each other, these rotating cylinders and rotary pistons can perform the function of a plurality of internal gear teeth (rotary cylinders) and a plurality of gear teeth (rotary pistons) in a ratio of 1:2, which is ensured by the rotation ratio limiting device, thereby performing the function of gears (views (C) and (D)).

[0250] In other words, although there is no separate device to limit the rotation coefficient,

[0251] In the case where rotation is performed with only one pair, which includes a rotating cylinder and a rotary piston, as shown in Fig. 21(A), when only the rotary piston itself rotates, even without the rotation ratio limiting device, the force of the rotary piston can be applied to the wall of the rotating cylinder at a position corresponding to the state (A), so that the rotating cylinder will inevitably move and rotate to match the movement of the rotary piston, and thus mutual transmission of torque is possible.

[0252] However,

[0253] When the rotary piston rotates 180 degrees in the state (A) to "coincide with the rotation center of the rotating cylinder" as shown in Fig. 21(B) (mutual torque transmission is impossible (dead zone)), the rotating cylinder theoretically needs to rotate 90 degrees to reach the Ob position. However, in reality, since the rotating cylinder does not have a component to lock the left and right rotation as in the state (A) (the rotary piston locks the wall), the rotating cylinder can rotate 360 ​​degrees, and the rotating cylinder may be in a deviation position such as Oa or Oc due to the clearance caused by the manufacturing precision between the rotating cylinder and the rotary piston and due to various external forces and torques received by the rotating cylinder and the rotary piston, and when the rotary piston is forced to continue rotating further, the hydraulic machine may stop or the shaft may break.

[0254] However, in a multi-stage configuration as shown in Fig. 21(C),

[0255] i.e., when a plurality of pairs, each of which includes a rotating cylinder and a rotary piston and is configured in such a way that the angle (y) of the location of the rotary piston is twice the angle (x) of the location of the rotary cylinder (y = 2x), are arranged in several stages at different angles, the rotating cylinders are connected to each other to form a single whole, and the rotary pistons are mechanically connected into a single whole with the shaft of the rotary piston,

[0256] since the rotating cylinders connected in all three stages and the rotary pistons connected in all three stages,

[0257] are configured in such a way that even when one of the three pairs of stages is in a state in which "the rotary piston coincides with the rotation center of the rotating cylinder", as in state (B), the remaining two pairs can continuously carry out mutual torque transmission since the wall of the rotating cylinder is in a position in which this wall holds the rotary piston.

[0258] In other words, as shown in Fig. 21(D), while one rotating cylinder functions as two teeth of the internal gear, and

[0259] One rotary piston functions as one gear tooth,

[0260] When the rotating cylinder and the rotary piston are arranged in multiple stages, the rotating cylinders and rotary pistons can achieve the functions of multiple internal gear teeth and multiple gear teeth at a ratio of 1:2 through the rotation ratio limiting device, replacing the gears.

[0261] (However, if separate gears are not installed to act as a rotation ratio limiting device to ensure a 1:2 ratio, large abrasion losses caused by friction may occur in the process of transmitting rotational forces and torques between the rotating cylinder and the rotary piston.)

[0262] Fig. 22 is a view illustrating a rotary piston of a hydraulic machine according to the present invention. The rotary piston is configured to rotate eccentrically, which may cause significant vibration at high rotation speeds. Therefore, according to the present invention, the hydraulic machine can have a structure in which a cavity 10h is provided so that the center of gravity of the rotary piston is located at the center of rotation, so that the center of rotation and the center of gravity of the rotary piston can coincide with each other even during high-speed rotation, which can prevent the occurrence of vibration.

[0263] Fig. 23 is a view illustrating a hydraulic machine according to the present invention, where the hydraulic machine shown in Fig. 6 and 13 can be connected in two stages in such a way that: one stage can be set as a reference stage with a cylinder angle satisfying the equality , and the piston angle satisfying the equality to ensure proportionality liquid outlet; another stage can be connected in such a way that the angle of the cylinder satisfies the equality , and the piston angle satisfies the equality y = 2x = 180 to ensure proportionality liquid outlet for phase shift of the working fluid by ± 90 degrees; two pairs (stages) can be combined into a single unit and connected to each other in one housing so that the suction / discharge value is proportional , thereby ensuring a constant flow of fluid as opposed to a flow during rotation; a hydraulic machine P, configured to suck / pump a working fluid, can be connected to an active machine (a drive device (electric motor, engine, etc.)); another hydraulic machine P can be connected to a passive machine (a wheel of a vehicle, a rotor of an aircraft, etc.); and both hydraulic machines P can be connected by means of a closed circuit of the working fluid (a tube, a high-pressure hose, etc.), or a valve SV configured to regulate the flow of the working fluid can be added to the closed circuit of the working fluid, as a result of which it is possible to regulate the offset of the rotational value and the offset of the torque value of the passive machine using the rotational value and the torque of the active machine.

[0264] In other words, a hydraulic machine is presented that is capable of transmitting an output rotational force, which is transmitted from an engine to a wheel without a cardan shaft, differential gear, transmission or other components of a similar kind with an offset rotation value and offset torque.

[0265] Therefore, mechanical parts that transmit power from the vehicle engine to the wheel (or from the aircraft engine to the rotor), such as the propeller shaft or differential gear, may be unnecessary, and therefore the weight of the vehicle and aircraft caused by the presence of many mechanical components can be reduced, and the cost and maintenance costs can be reduced.

[0266] Fig. 24 is a view illustrating a hydraulic machine according to the present invention, where the hydraulic machine shown in Fig. 6 and 13 can be connected in two stages such that:

[0267] One stage can be set as a reference stage with the cylinder angle satisfying the equality , and the piston angle satisfying the equality to ensure proportionality liquid outlet;

[0268] Another step can be connected in such a way that the angle of the cylinder satisfies the equality , and the piston angle satisfies the equality y = 2x = 180 to ensure proportionality liquid outlet for phase shift of the working fluid by ± 90 degrees;

[0269] Two pairs (stages) can be combined into a single unit and connected to each other in one housing so that the suction / discharge amount is proportional , thereby ensuring a constant flow of liquid, as opposed to the flow during rotation;

[0270] hydraulic machine P, designed with the ability to suck / pump working fluid, can be connected to an active machine (drive device (electric motor, engine, etc.));

[0271] Another multi-stage hydraulic machine Pn (this view shows an example with six stages) can be provided (a hydraulic machine Pn formed by combining n hydraulic machines P into a single whole); and

[0272] The hydraulic machine P and the hydraulic machine Pn can be connected by a closed circuit of the working fluid (a tube, a high-pressure hose, etc.) or the valves SV1 to SV6 and up to SVn, so that the displacement R1 of the rotation / torque value of the hydraulic machine P connected to the active machine can be converted into the displacement R2 of the rotation / torque value of the hydraulic machine Pn integrated in multiple stages.

[0273] In other words, a hydraulic machine is presented in which the following is provided: if the hydraulic machine P and the stage P, consisting of one pair, inside the multi-stage hydraulic machine Pn have the same size and performance, then when only the valve SV1 is activated (opened), and the other valves are disabled (closed), the value of R2 in relation to the rotational displacement R1 can be 1 / 1*R1 (= R2 = 1 / 1*R1),

[0274] When the valves SV1 and SV2 are activated (opened) and the other valves are disabled (closed), the value of R2 in relation to the rotation offset R1 can be 1 / 2*R1 (= R2 = 1 / 2*R1),

[0275] …, …, when all valves SV1-SV6 are activated (opened), the value of R2 in relation to the rotation offset R1 can be 1 / 6*R1 (= R2 = 1 / 6*R1), and

[0276] …, …, when all SVI-SVn valves are activated (opened), the value of R2 in relation to the rotation offset R1 can be 1 / n*R1(= R2 = 1 / n*R1),

[0277] so that the rotation amount and torque amount can be converted from the rotation amount R1 of the active machine to the rotation offset R2 (in the example shown in this view, n=6 steps).

[0278] Fig. 25 and 26 present mathematical proofs that the hydraulic machine P, in comparison with the angle of displacement of the rotating shaft, which is illustrated in Fig. 23 and 24, provides a constant output power (±) PV, i.e. a constant fluid flow.

[0279] In other words, the stroke length of the rotating cylinder and the rotary piston, as shown in Fig. 25(A), may be

[0280] The basis is as follows:

[0281] Fig. 26(A) and 26(B) are parts of Fig. 3 and 17, respectively, and if these images are integrated into Fig. 26(C) and viewed vertically, then:

[0282] (Stage 1)

[0283] If from the midpoint of an isosceles triangle c1c2c3 a vertical line is drawn that divides the segment c2c3 in half at a right angle, then a right triangle c1c2c4 can be obtained; and

[0284] (Stage 2)

[0285] in this case, the length of the base of the right triangle c1c2c4 can be:

[0286] And

[0287] Since the total length of the dPS move is twice the c2c4 segment in the above formula (1), then:

[0288]

[0289] As shown in Fig. 26(D), the internal volume of the single stage semi-cylinder in Fig. 25(A) may be:

[0290] one full working volume

[0291]

[0292] Furthermore, when another stage (a pair including a rotating cylinder and a rotary piston) is added, offset by -90 degrees, we get:

[0293] Two full working volumes

[0294]

[0295]

[0296] In other words, the hydraulic machine shown in Fig. 25(B) (the suction / discharge of which is proportional , formed by connecting two hydraulic machines shown in Fig. 25(A) (the suction / discharge of which is proportional , with a phase shift, can be a hydraulic machine P, having a suction / discharge characteristic of the working fluid similar to a constant flow of fluid, without sinusoidal oscillations or pulsations, as in Fig. 25(C).

[0297] Fig. 27 is a view illustrating a state in which the hydraulic machine according to the present invention shown in Fig. 23 is applied to a vehicle.

[0298] Fig. 28 is a view illustrating a state in which the hydraulic machine according to the present invention shown in Fig. 23 is applied to an unmanned aerial vehicle (UAV) so that the UAV can fly by controlling four rotors with one electric motor without using four drive devices (electric motors, motors, etc.) to control the rotors.

[0299] Fig. 29 is a view illustrating a state in which the hydraulic machine according to the present invention shown in Fig. 23 is applied to the rotor of an aircraft so that the aircraft can fly without a propeller shaft, transmission, or other similar elements that connect the main engine to the tail wing.

[0300] Figure 30 is a view illustrating a state in which the hydraulic machine according to the present invention shown in Figure 23 is applied to a watercraft. Previously, to connect a propeller located outside the vessel to an engine located inside the vessel, a hole was drilled in the hull for connection to the main shaft, which required numerous mechanical devices and high costs for preventing water penetration from the outside and for maintenance. However, by applying the hydraulic machine according to the present invention, power can be transmitted by the propeller without drilling a hole for the main shaft in the hull of the vessel, thereby reducing the number of watertight mechanical components and lowering the maintenance costs.

[0301] As for Newton's law of universal gravitation, thanks to experiments such as the "Leaning Tower of Pisa" experiment, even before Newton, many scientists knew that all bodies (of mass m1) fall to the surface of the Earth with an acceleration of 9.8 m / s 2 However, Newton derived the formula (G.m1.m2 / r 2 ), according to which the force of attraction is proportional to the mass of the Earth (m2) and the mass of the falling body (m1) and inversely proportional to the square of the distance between the center of mass of the Earth and the center of mass of the falling body (r 2 ), and mathematically proved that this is true for all celestial bodies, as well as for bodies on the Earth's surface. Accordingly, Galileo's assertion that the Earth revolves around the Sun was also proven.

[0302] Reference positions

[0303] 10: Rotary piston;

[0304] 10h: Cavity for adjusting the center of gravity of the rotary piston;

[0305] 11: Rotary piston shaft;

[0306] 11a: Eccentric shaft of planetary rotary piston;

[0307] 11j: Rotary piston shaft spline;

[0308] 12: Main shaft (the eccentric shaft of the eccentric planetary rotary piston formed inside it);

[0309] 112: Main shaft (the eccentric shaft is connected to its outer side);

[0310] 122: Main shaft (rotary piston rotation shaft);

[0311] 112h: The hole through which the main shaft enters the rotary piston;

[0312] 112g, 113g: Rotary piston shaft gear engagement (gear ratio 1:);

[0313] 113с: Eccentric shaft (similar to crankshaft);

[0314] 113p: Rotating / pivoting shaft;

[0315] 20: Rotating cylinder;

[0316] 21: Side wall of rotating cylinder;

[0317] 21s: Rotating cylinder shaft;

[0318] 20i: Inner / outer hole (inlet / outlet) of rotating cylinder;

[0319] 20f: Cylinder (formed / fixed on the main body);

[0320] 213b, 113b, 302b, 312b, 311b: Bearing;

[0321] 213s: Inner shaft of the side wall of the rotating cylinder;

[0322] 211g, 311g: Cylinder gear (gear ratio 2:);

[0323] 30: Main building;

[0324] 30s: Combustion chamber in the main body (high pressure);

[0325] 30h: Support hole for rotating cylinder in the side wall of the main body;

[0326] 30w, 301w: Side wall of the main body;

[0327] 30h: Support hole for bearing of rotating shaft of third stage gear on the side wall of main body;

[0328] 30a: Suction port (inlet);

[0329] 30b: Discharge port (outlet);

[0330] 30gb: Gearbox in the main body;

[0331] 301h, 302h: Groove in the side wall on the liquid supply path;

[0332] 31c: Main body side wall protrusion;

[0333] 31, 31a, 31b: Side wall of the main body;

[0334] 31w: Side wall of the main body in the form of a support for the main shaft and the planetary gear bearing shaft;

[0335] 32w: Side wall of the main body in the form of a main shaft bearing cover;

[0336] 31h: Support hole for planetary gear bearing shaft;

[0337] 311c: Part for fixing the inner bearing between the main body and the rotary piston shaft;

[0338] 312c: Part for fixing the outer bearing between the main body and the rotating cylinder;

[0339] 401g, 402g, 403ga, 403gb, 404ga, 404gb, 405g: Gear;

[0340] 41g: Drive gear;

[0341] 42g: Secondary gear;

[0342] 43 g: Third stage gear;

[0343] 44g: Fourth stage gear;

[0344] 42s: Planetary gear shaft;

[0345] 60: Sealing ring;

[0346] 61: Oil seal;

[0347] 70: Key;

[0348] 71: Keyway;

[0349] 90, 90a, 90b, 90c: Bolt;

[0350] S1: Cylinder center line;

[0351] C1: Rotation center of rotary piston shaft;

[0352] C2: Rotation center of rotating cylinder, rotation center of main shaft (coinciding with the center of the cylinder);

[0353] C3: Eccentricity center of rotary piston;

[0354] Cv: Check valve;

[0355] d: Distance between the rotation center of the main shaft and the rotation center of the eccentric shaft;

[0356] dPS: The distance that the rotary piston moves inside the cylinder;

[0357] r: Distance between the rotation center of the eccentric shaft and the center of the rotary piston;

[0358] Oa, Os: The position of the rotating cylinder where the misalignment occurs (when the rotary piston reaches the position of the cylinder rotation center without gear meshing at a ratio of 2:1, an incorrect rotation difference may occur, causing the rotating cylinder to take any position due to clearances caused by manufacturing inaccuracy or the difference between two rotational forces);

[0359] Ob: Ideal position of rotating cylinder;

[0360] M, E: Active machine (drive device (electric motor, engine, etc.));

[0361] Mc: Center of gravity of rotary piston;

[0362] P: A hydraulic machine (P) in which two pairs of hydraulic machines (two pairs of “rotating cylinder-rotary piston” located with a phase shift of 90 degrees connected in such a way that a suction / discharge characteristic of a constant flow of working fluid is ensured;

[0363] Pn: Hydraulic machine (Pn), formed by connecting hydraulic machines in several stages;

[0364] P1, P2: Suction / discharge value of one hydraulic machine;

[0365] PV: Suction / discharge value of two hydraulic machines;

[0366] PW: Width of the working volume of one cylinder of one hydraulic machine;

[0367] Pd: Thickness of the working volume of one cylinder of one hydraulic machine;

[0368] R1: Displacement of the output rotating shaft of the hydraulic machine (P) connected to the active machine;

[0369] R2: Offset of the output rotating shaft of the multi-stage hydraulic machine (Pn);

[0370] SV, SV1, SV2, SV3, SV4, SV5, SV6: Liquid flow control valve;

[0371] Wh: Active machine (vehicle wheel, UAV propeller, etc.).

Claims

1. A hydraulic machine comprising: a fixed cylinder formed in the main body and having a straight axial line (S1) of the mechanical volumetric space and a center (C2); a main shaft capable of rotation around a center of rotation (C2) which coincides with the working center of the cylinder; an eccentric shaft secured to the main shaft and configured to rotate together with the main shaft, wherein the eccentric shaft has a center of rotation (C1) with the ability to mechanically rotate and maintain an eccentric interval (d) relative to the main shaft; a rotary piston configured to rotate on an eccentric shaft and having a center (C3) that is eccentric relative to the rotating shaft of the rotary piston by a distance (r) that is equal to the eccentric interval (d) (d = r); and a rotation ratio limiting device configured to limit the ratio between the angular velocity (x) of rotation of the main shaft and the angular velocity (y) of rotation of the rotating shaft of the rotary piston to a ratio of 1:2, which is the only condition under which the center (C3) of the rotary piston always operates in the same plane with the straight axial line (S1) of the mechanical volumetric space of the stationary cylinder, in this case, the internal angle (x + c + a) of the triangle connecting the three centers (C1), (C2) and (C3) is equal to 180 degrees due to the relationship between the internal angles.

2. The hydraulic machine according to claim 1, wherein the rotation coefficient limiting device includes a gear transmission.

3. A hydraulic machine according to claim 1, in which a cavity is provided on one side of the rotary piston, which initially has a large weight, so that the center of gravity coincides with the center of rotation, eliminating vibration that may arise due to eccentric rotation.

4. A hydraulic machine comprising: a fixed cylinder formed in the main body and having a straight axial line (S1) of the mechanical volumetric space and a center (C2); a main shaft capable of rotation around a center of rotation (C2) which coincides with the working center of the cylinder; an eccentric shaft secured to the main shaft and configured to rotate together with the main shaft, wherein the eccentric shaft has a center of rotation (C1) with the ability to mechanically rotate and maintain an eccentric interval (d) relative to the main shaft; a rotating / turning shaft supported by a bearing on an eccentric shaft and configured to rotate and turn on the eccentric shaft; a rotary piston rotatably coupled to a rotating / pivoting shaft and having a center (C3) that is eccentric relative to the rotating / pivoting shaft by a distance (r) equal to an eccentric interval (d) (d = r); and a rotation coefficient limiting device configured to limit the ratio between the angular velocity (x) of rotation of the main shaft and the angular velocity (y) of rotation of the rotary piston to a ratio of 1:2, which is the only condition under which the center (C3) of the rotary piston always operates in the same plane with the straight axial line (S1) of the mechanical volumetric space of the stationary cylinder, in this case, the internal angle (x + c + a) of the triangle connecting the three centers (C1), (C2) and (C3) is equal to 180 degrees due to the relationship between the internal angles.

5. The hydraulic machine according to claim 4, wherein the rotation coefficient limiting device includes a gear transmission.

6. The hydraulic machine according to paragraph 4, in which the rotation coefficient limiting device includes: a drive gear connected to the main shaft and configured to rotate in accordance with the rotation of the main shaft; a secondary planetary gear connected to the drive gear so as to rotate; a third stage gear connected internally to the secondary planetary gear and configured to rotate in such a way that its axis of rotation coincides with the axis of rotation of the main shaft; and a fourth-stage gear connected internally to a third-stage gear with the ability to rotate, mounted on one side of the rotating / turning shaft and configured to rotate in such a way that its rotation axis coincides with the rotation axis of the rotary piston.

7. A hydraulic machine according to claim 4, in which a cavity is provided on one side of the rotary piston, which initially has a large weight, so that the center of gravity coincides with the center of rotation, eliminating vibration that may arise due to eccentric rotation.

8. A hydraulic machine comprising: a rotating cylinder capable of rotation and having a straight axial line (S1) and a center of rotation (C1); a main shaft configured to rotate around a center of rotation (C1) and maintain an eccentric interval (d) relative to the center of rotation (C1) of the rotating cylinder; a rotary piston configured to rotate on the main shaft and having a center (C3) that is eccentric relative to the rotary piston by a distance (r) equal to the eccentric interval (d) (d = r); and a rotation coefficient limiting device configured to limit the ratio between the angular velocity (x) of rotation of the rotating cylinder and the angular velocity (y) of rotation of the rotary piston to a ratio of 1:2, which is the only condition under which the center (C3) of the rotary piston always operates in the same plane with the straight axial line (S1) of the mechanical volumetric space of the stationary cylinder, in this case, the internal angle (x + c + a) of the triangle connecting the three centers (C1), (C2) and (C3) is equal to 180 degrees due to the relationship between the internal angles.

9. The hydraulic machine according to claim 8, wherein the rotation coefficient limiting device includes a gear transmission.

10. The hydraulic machine according to clause 8, in which the rotation coefficient limiting device is designed so that: a plurality of pairs of rotating cylinders and rotary pistons are arranged at different angles; and a plurality of rotating cylinders are connected to each other; and each rotating cylinder and rotating piston are configured in a multi-stage configuration in which a plurality of pairs of internal gears having two teeth corresponding to the rotating cylinder and gears having one tooth corresponding to the rotating piston are configured to operate together, wherein the gear ratio is limited to 1:

2.

11. A hydraulic machine according to claim 8, in which a cavity is provided on one side of the rotary piston, which initially has a large weight, so that the center of gravity coincides with the center of rotation, eliminating vibration that may arise due to eccentric rotation.

12. A system of hydraulic machines configured so that a hydraulic machine generating a sinusoidal output flow and a hydraulic machine generating a cosine output flow are combined into one pair for transmitting power, rotational speed and torque between the active and passive machines in the form of a constant output flow, wherein the system of hydraulic machines includes: rotating cylinder; a rotary piston having an eccentricity such that its center of rotation maintains an eccentric interval (d) relative to the center of rotation of the rotating cylinder, and having a center that is eccentric relative to the rotary piston by a distance (r) equal to the eccentric interval (d) (d = r); and two pairs, each comprising a rotating cylinder and a rotary piston, are connected in two stages; one paired stage is configured as a support stage having a stroke determined by the line segment C2C3 = 2d COS(x); and the other pair stage is configured in such a way that the rotating cylinder is positioned with a phase shift of 90 degrees, and the rotary piston is positioned with a phase shift of 180 degrees, while the stroke of the second pair stage is determined by the segment C2C3 = 2d COS(x+90); while the total fluid output from the two pairs is proportional to the constant flow characteristic determined by the stroke of the segment C2C3 = 2d (COS(x) + SIN(x)).

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