KR100512076B1 - Rotating Piston type Revolving Machine - Google Patents

Abstract

In the fluid processing (compression, transfer, fluid power, internal combustion engine) machine field, in order to change the cylinder volume by circular motion alone, several rotating shafts are placed in a rotor integral with the power shaft, and the rotating shafts are planetary gears and rotating gears. The piston and the rotor have a rotating auto gear, and the housing has several idle pinion gears, and the idle pinion gear and the planetary gear are composed of shifting gears.The rotation of the rotating piston is linked with the rotation of the rotor. In parallel, the phases of the rotating pistons are the same, and the ball and rotating movement trajectory space of the rotating pistons are defined as the cylinder space, and the cylinder member is formed as the surface surface element. As all parts acquire the volume change by circular motion, there is no vibration because the weight and the center of rotation match, and the volume of fluid treatment per unit volume is large, especially Combustion engine sought goal of increasing output, reducing vibration and noise, small size, wide rotation region, volume rotating piston type rotary fluid machinery to achieve varying the problems of acceleration delay of only a circular motion.

Description

 Rotating Piston type Revolving Machine

The present invention provides a compression device (air compressor) for compressing air, a conveying device (pump) for transporting a fluid, a fluid power device that rotates with the pressure energy of the fluid, and sucks, compresses, expands and exhausts the gas to power the expansion energy. To the field of internal combustion engines.

The goals of the internal combustion engine are to have a high output per unit weight, such as quiet operation, high acceleration / deceleration response, wide rotation range, low fuel consumption, low noise and vibration, and low pollutant emission. . However, the reciprocating internal combustion engine uses a large number of cylinders to increase the output by vibrating the reciprocation of the piston mechanism and low output relative to the weight, so the fuel consumption is increased due to the wider space and the weight increase. It is easy to cause trouble by valve mechanism, noise of valve mechanism is generated a lot and filling efficiency in cylinder is low due to limitation of intake area, and some additional devices are attached, and weight balance weight and flywheel are connected to crankshaft for quietness of operation. However, the rotational inertia is smoothed, but the power characteristic of the output shaft is still uneven, and due to the added weight, the weight increase and acceleration delay are caused by the added weight. In the case of the Bankel engine, the center of gravity of the piston rotor is not located on the power axis. Because it shakes along the trajectory of the engine, it causes vibration and cylinder wear. The long combustion chamber structure increases the generation of hydrocarbons, causing pollution and increasing fuel consumption, and requiring expensive ignition before excessive heat load before ignition. Lack of operational efficiency in the area, high fuel consumption at partial load, engine braking It can not function, can not avoid the acceleration delay.

Source: Automobile Institution I (Automatic Institution):

The vane rotary fluid treatment device is difficult to cool the blade (blade) inserted radially in the rotor, and the reciprocating control means of the blade (blade) to the shape of the inner surface of the housing, the friction portion is airtight due to excessive wear and scratching Loses their ability to function properly,

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Air compressors can be classified into speed type and volume change type compressors, and speed type compressors cannot secure a gas having a desired degree of compression at low speeds, and volume change type compressors are as pointed out in the internal combustion engine. The conveying device (pump) is similar to the description of the compressor. The type of fluid power unit that converts the kinetic energy or pressure energy of the fluid into power has a structure in which the inlet part of the fluid transfer device is the outlet and the outlet part is the inlet. Similar to the problem. In addition, the contents of the invention described in Korean Unexamined Patent Publication No. 2000-0059664 (2000.10.05) do not support the rotation of the vane without the support of the casing. Since it is a dependent motion, it does not solve the problem of serious friction generated between the inner wall of the casing and the vane, which is a problem of the vane rotary fluid processing apparatus.

In the process of processing the working fluid and converting it into the desired shape, the cylinder space should be changed in volume while all the parts connected to the shaft are rotated, and the rotational characteristics should be close in a wide range of rotation. In order to prevent excessive wear between the cylinder and the piston, the relative movement of the cylinder and the piston should be made independently. In addition, the internal combustion engine is provided with a cooling means for preventing the temperature increase of the core parts involved. Means should be invented, the means for engine brake function should be invented, the efficiency of intake and exhaust should be increased to reduce mechanical losses, high output to volume, low sensitivity to fuel, short combustion It should be invented in the form of a spatial structure.

In order to achieve the above object, the configuration of the present invention is as follows.

Detailed description will be made as to the means for treating the fluid by rotating the rotating piston between the cylinder and the rotating piston in a circular motion, and in addition, the fuel supply means, the ignition activity means, the continuous combustion activity means, the cooling means, and the lubrication means. do.

The present invention can be roughly divided into a power shaft 100, a rotor 200, a housing. Connected to the power shaft 100 is composed of the rotor 200, the sub-rotator 250, the rotor 280, the rotating shaft 300, the switch gear 380, and the cylinder in the housing The revolving pinion gears A, B (290, 294), the fluid inlet pipe 672, the fluid discharge pipe 674 is configured, the rotating shaft 300 is composed of a rotating piston 310, the planetary gear 350.

There is a power shaft 100 and a rotor 200 integrated therein and constitutes several bearing parts for supporting the rotating shaft 300 arranged at several equal angles on the same circumference at the center of the rotor 200, There is a sub-rotor 250 that is integrally fastened with the rotor 200 supporting one side of the rotating shaft 300, and the planetary gear with the rotating shaft 300 as the axis between the rotor 200 and the sub-rotor 250 There is a 350, the other side of the rotating shaft 300, the rotating piston 310 is integrated, the negative rotor 250 supports one side of the rotating shaft 300, and also the number of revolutions of the rotating piston 310 Rotor wheel 280 is fixed to sub-rotator 250 to perform the role of controlling, a number of revolving pinion gear A (290) having a specific rotation ratio on the rotor circle 280 pitch circle, idle The pinion toothed shaft bar 292 is configured in the right housing 500. The idler pinion gear A (290) is configured to be connected to the rotary car 280 at a constant rotation ratio, and the idler pinion gear A (290) is joined to the integral idler pinion gear B (294) having the same shaft bar 292 again. It is. The planetary gear 350 press-fitted on the outer surfaces of the several rotating shafts 300 and the declination gear 380 meshed with a fixed rotation ratio are meshed with the revolving pinion gear B 294 at a constant rotation ratio. A rotating piston 300 is integrated with one axis of the rotating shaft 300, and a cross section perpendicular to the rotating shaft 300 line has a rhombus structure or a shape in which four vertices are processed in a circle, and the rotating shaft 300 has a rotating center. The rotation of the rotating piston 310 is controlled by the gear ratio so as to rotate a predetermined angle in the opposite direction in proportion to the rotational work of the rotor 200, and the outer locus surface formed by the rotating piston 310 rotates and rotates the cylinder The inner surface of the outer member 600 is configured, and the inner track surface is configured of the outer surface of the inner cylinder member 650. Then, the space formed between the outer surface of the inner cylinder member 650 and the inner surface of the outer cylinder member 600 becomes a passage through which the rotating piston 310 rotates in parallel with the revolution and rotates and becomes a cylinder space for processing the fluid. 670 is configured to be in close contact with the inner and outer members (650,600) in the cylinder and the cylinder right side is replaced by one surface of the rotor (200). In addition, the procedure for forming the gear ratio and cylinder surface of each gear is X rotation of the rotating piston in one rotation of the rotor, and the internal combustion engine sets the number of rotations as an integer multiple of the revolution period, and the compression device, fluid transfer device, and fluid power The device sets the number of rotations to 0.5 multiples of the idle period. The rotation ratio between the planetary gear 350 and the idler gear 380 is determined first, and then, the rotational ratio L between the idle pinion gear B 294 and the idler gear 380 and the idler pinion gear A 290 and the rotary gear 280 Rotation ratio M with) satisfies the following equation.

[Equation]

M / L + X / A = 1

Dimensions satisfying these conditions are determined to be pitch sources for each tooth type. Then, when the rotor 200 rotates once, the rotating piston 310 rotates X, and the number of volume reduction strokes is generated during 2X rotation.

In order to clarify and concise, it is as following Table 1 and Table 2 according to the arrangement and the number of rotation conditions.

The inflow and outflow of the fluid to be processed in the cylinder space is made by connecting the housing fluid tube to each of the fluid through the fluid inlet on the cylinder surface, the axis of rotation (300) on the power shaft (100) line should be either vertically or horizontally. The rotor wheel 280 is configured by selecting either the inner tooth or the outer tooth, and the rotary gear 280 is configured at a portion integrated with the rotor 200.

Rotating piston 310 rotates the outer portion is configured in a circular shape, the rotating piston 310 rotates to form a straight oil tight piece 312 that is supported by a leaf spring in the outer groove of the rotating piston 310 for oil tightness of the working fluid, It consists of several half grooves arranged so that the fluid easily flows from the high place to the low place due to the pressure difference, and half the grooves for inserting the straight oil tight 312 pieces at the left and right 60 degree points based on the maximum rotation radius. The bone groove is cut and the head of the letter “b” is exposed on the surface, and the groove is formed so that the bottom part is located at the core part, but in the “b” type to form a straight oil tight piece 312 in one unit of the rotating piston 310. Four grooves are formed, but one side of the rotating piston 310 is configured so that the tail of the "b" facing each other and the other side of the tail is far from each other. In addition, in order to support the engagement action between the left and right locking jaws of the straight oil tight piece 312 and the edges of both ends of the leaf spring when rotating the intake and exhaust pipes (672, 674), Configure.

The straight oil tight piece 312 is composed of fine half grooves on both sides of the straight oil tight piece 312 so as to prevent adhesion due to high temperature on both sides and to facilitate the entry of fluid to the bottom of the straight oil tight piece 312, and the lower ends of both leaf springs. It constitutes so that the cross section shape is "b" type by configuring the engaging jaw at both ends coupled to the end and the engaging jaw at one side of the linear oil tight piece 312 in order to prevent the straight oil piece 312 from being separated by the centrifugal force. .

In the case of high temperature fluid treatment, the cooling of the device is performed by the lubricating oil centered on the rotating piston 310 which is the core part of the cooling. And lubricating oil supplied from the lubricating oil cooling tank flows along the supply pipe and reaches the position of the right housing 500, whereby the lubricating oil which cools the rotor 200 and the cooling and lubrication of the gears is combined through the holes in the supply pipe. It is supplied to the lubricating oil circumferential groove of the right housing. Lubricate and cool the journal bearings in the vicinity. The lubricating oil of the circumferential groove is accelerated rotationally by the circulating piece 504 in the inner diameter portion, and the lubricating oil introduced through the right housing 500 is formed on the sub-rotor 250 and the sub-rotor lid 252 by the centrifugal force of the engine. It enters through the space and is introduced into the hole of the rotating shaft 300 through the hole in one end surface of the rotating shaft 300 of the rotating piston 310 in the negative rotor 250, the lubricant of the rotating shaft 300 is the rotating shaft 300 inner diameter Into the smaller lube oil inlet pipe 306 joined to the lube oil inlet pipe 306 is connected to the rotating piston 310 to supply lubricating oil into the rotating piston 310, the supplied lubricant is a rotating piston 310 The temperature of the rotating piston 310 is prevented from being brought into contact with the inner surface, and the heated lubricant flows through the space between the inner diameter hole of the rotating shaft 300 and the inlet pipe 306 and supports the planetary gear 350. When you reach the rotating shaft 300 Lubricant flows into the space formed in the rotor 200, which is in close contact with the tooth side portion through the hole in the toothed boss portion through the outlet in the shaft 300, and at this time, some lubricant oil in the dynamic tightness portion It flows to the surface of the electron 200 and flows by the centrifugal force to the edge of the rotor 200 to achieve cooling of the edge of the rotor 200, and lubricating and lubricating each gear. Lubricant pumped into the rotor 200 Transfers the centrifugal force to the rotor 200 and moves to the center of rotation of the rotor 200 by centripetal force. The lubricating oil moving to the center of the rotor 200 moves to the circumferential groove of the left housing 530 through several holes penetrating the rotor 200, and the left housing 530 receives the portion of the rolling bearing. Cooling and lubrication is carried out and the lubricating oil pumped to the left housing 530 is discharged to the outside of the engine and some of them flow through the lubricating oil filter to the temperature control valve. The temperature control valve operates to adjust the valve to determine the direction of the cooling tank and the fuel supply tank, and the lubricating oil passing through the lubricating oil cooling tank is supplied to the lubricating oil supply tank to continuously flow the lubricating oil. The flow of the lubricating oil uses a centrifugal force to act by using a rotation radius difference between the lubrication inlet and the outlet of the rotor 200 and the sub-rotor 250. The lubricating oil cooling the rotor 200 edge cools or lubricates the gear and continuously flows through the housing surface by the centrifugal force of the rotor 200 and the gear and merges through the holes of the lubricating oil supply pipe.

Protrusion sealing piece 652 is the position of the cylinder inner member 650 in the position of the portion where the shape of the rotation piston is not coincident with the outer movement trajectory 310 is supported by a leaf spring is supported by the rotating piston 310 Make a sliding contact with the body. The gap generated when the rotating piston 310 passes through the leaf spring in the lower portion of the projection oil tight piece 652 operates to be in close contact with the rotating piston 310 body to prevent the movement of the fluid between the cylinder unit compartment. This is because the protrusion of the projection sealing piece 652 is pressed by overlapping with the slide path of the rotating piston 310, the projection sealing piece 652 operates.

In the cylinder, the portion of the outer side of the outer member (650, 600) and the side of the rotor 200 in dynamic contact prevents the leakage of the lubricating oil and the high-pressure fluid by the two rims 690 installed on the cylinder member side. The oil tight frame 690 continuously supports the flow gap that may occur while the rotor 200 rotates by the tension of the lower leaf spring of the oil tight frame 690 to maintain the oil tightness to prevent the high pressure fluid from leaking. . The clearance between the rotating shaft 300 support hole in the rotor 200 and the rotating shaft 300 acts to seal the clearance between the oil-tight springs 354.

In the case of an internal combustion engine, the fuel is supplied from the fuel container to the final injection device through the solenoid valve, and is composed of a fuel supply pipe 582 and a fuel injection valve 580, and the fuel injection valve 580 is an intake passage or compression. The cylinder outer member 600 of the stroke stage is configured in the cross section, and the inner tube body of the fuel injection valve 580 is configured of a plunger 584 and a coil spring 586. The pipe body of the injection valve forms a fuel injection hole in the cylinder space direction and forms a narrow and long jet port so that the jet port area is adjusted in proportion to the movement of the plunger 584, and the fuel jet pressure in the fuel supply pipe due to the change in the supply amount per unit time The amount of fuel injected into the cylinder space per unit time is controlled by the change of the injection hole area by the movement of the plunger 584 in the fuel injection valve 580 according to the change of the pressure. When the solenoid valve is shut off, the pressure in the injection valve is equal to or less than the opening pressure. With the tension of the coil spring 586, the plunger 584 immediately moves and closes the injection port to stop the fuel injection operation. When the fuel pressure is increased to reach a certain opening pressure, the injection valve plunger 584 moves in response to opening the injection hole area corresponding to the condition.

The front end of the plunger 584 is configured to be inclined to meet between the injection valve tube portion and the plunger 584 to reduce the initial resistance when moving from the nozzle closing time to the operation time. In the case of an internal combustion engine, the ignition activity is activated only when the ignition before 590 is required to start and during operation. The ignition operation at the start is connected to the power source and the starter motor rotates the power shaft 100 and generates a high-pressure secondary induction current according to the spatial angle of the rotating piston 310 by the electric interrupter connected to the power shaft 100. Electric flame works. Ignition activity for re-ignition during operation is to shut off the fuel when the engine is operating in engine brake state and the combustion activity in the cylinder disappears, thus performing the engine brake function, and when the engine leaves the engine brake condition again, fuel is supplied again. Reignition activity begins while driving. The pressure is detected by the pressure sensor 592 mounted on the outer cylinder member 600 in the expansion stroke, and if it is not larger than the minimum combustion pressure value, the power is connected to the ignition flame. If the combustion minimum pressure value is equal to or greater than the combustion minimum pressure value, the combustion state is cut off before the ignition 590 before the ignition 590 enters the dormant state.

In the case of the internal combustion engine, the continuous combustion activity is divided into each cylinder space by the rotating piston 310, and the space between the divided spaces is prevented by gas-tightness by a straight oil-tight piece 312 formed at the outer portion of the rotating piston 310. It acts to maintain. The linear hermetic piece 312 supported by the leaf spring 314 slides in continuous cylinder contact with the inner and outer members 650 and 600, and the linear hermetic piece 312 is made by the compressed air at a high compression stage in the compression process. ) It is filled at the lower end to be in close contact with the cylinder wall side to increase the airtight holding means, which is later in the combustion tailing or inflation stage, and the pressure difference between the final and uncompressed final compression space is the driving force of the "b" of the straight oil tight piece 312. Combustion gas is filled in the latching jaw of the overcoming to overcome the tension of the leaf spring 314 supporting the linear oil tight piece 312, and the linear oil tight piece 312 is pushed into the rotating piston 310 so that the hot combustion gas is still present. It acts to ignite by ejecting and moving to the mixer space of the unburned trailing space. In addition, the movement of the combustion gas into the preceding space during the expansion process after combustion is filled with a trailing high pressure combustion gas at the lower end of the linear oil tight piece 312 so that the linear oil tight piece 312 is moved to the wall of the inner and outer members 650 and 600. The close contact prevents the leakage of combustion gas.

Locations of the fluid inlet pipe 672 and the fluid discharge pipe 674 of the working fluid is different depending on the application as shown in Figures 8, 9, 10, 11, and will be described in detail here for the operation of the fluid of the internal combustion engine. The fluid drawn into the fluid inlet pipe 672 is a fluid suction up to the maximum point of the volume of the unit space divided by the inner and outer members (650, 600) and the rotating piston 310, the sucked fluid is the rotor 200 As it rotates, the cylinder is compressed in the unit space formed by the inner and outer members 650 and 600 and the rotating piston 310. At this time, the only type of air suction is the fuel injector in the outer cylinder member 600 and during the compression process. The fuel is injected to form a mixer, and the linear oil-tight piece 312 acts between the cylinder and the rotating piston 310 to maintain the maximum oil tightness. As the rotor 200 rotates further in this process, the volume is reduced. The degree of compression of the air or mixer is increased so that the atmosphere is formed in a condition that the compression space is capable of ignition combustion near the minimum apex and is ignited at this point. The inside of the cylinder generates power by rotating the rotor 200 in a direction in which the volume formed between the cylinder and the rotating piston 310 is increased by the expansion pressure energy of the combustion gas. At this time, a part of the combustion gas is pushed into the trailing linear sealing piece (312) in contact with the cylinder inside the rotating piston 310 and moved to the trailing space, the hot gas is ejected to the mixed and compressed mixer in the trailing compression space to ignite Let's do it. In the preceding space, the linear oil tight piece 312 is brought into close contact with the cylinder wall due to the pressure difference, and thus the oil tight function is not increased. The expansion stroke is terminated at the maximum volume, from which the exhaust stroke enters the exhaust stroke, and the exhaust stroke is performed until just before the volume is minimized, and the flow proceeds to the intake stroke stage and repeats continuously.

An embodiment in which a rotating fluid treatment device having a rotating piston changes its volume while moving in a circular motion will be described in detail below, and in addition to the necessary functions of an internal combustion engine.

Example 1

Example of a case having a rotating shaft parallel to the power shaft, the number of cylinders is one, the gearing direction of the rotor wheel is an external gear, and the number of rotations is one

The present invention can be largely divided into the power shaft 100, the right housing 500, the middle housing 570, the left housing 530, the power shaft 100, the rotor 200, journal bearing (534), the conical roller bearing 532 inner ring, rotor anti-nut nut 108, lubricating oil sealing member 102 is configured, the rotor 200 is a rotating shaft 300, idler gear 380, rotation The electronic lid 202, the secondary rotor 250, the rotating shaft sliding body A (302), the ring oil tight spring 354 is configured, the secondary rotor 250, the rotor wheel 280, the secondary rotor lid 252, It consists of a rotating shaft slide body B304. The rotating shaft 300 is composed of a planetary gear 350, a lubricating oil inlet pipe 306, a rotating piston 310, the rotating piston 310 is a rotating piston cap 316, lubricating oil induction piece 308, straight oil sealing piece 312, a leaf spring 314 for supporting the straight oil tight piece is configured. The right housing 500 includes an idle pinion gear A, B (290, 294), an idle pinion gear shaft 292, a shaft sliding body 296, an idle pinion gear bearing, a lubricant supply pipe 502, a journal bearing 534 To configure, the middle housing 570 is the coolant supply pipe 520, the cylinder outer member 600 is configured, the cylinder outer member 600 is configured with a oil tight frame 690, the left housing 530 is the cylinder left The outer ring of the member 670, the cylinder inner member 650, the fluid inlet pipe 672, the fluid discharge pipe 674, the coolant discharge pipe 522, the lubricating oil discharge pipe 536, and the conical roller bearing 532.

There is a power shaft 100 and a rotor 200 integrated therein and constitute 12 bearing parts supporting 12 rotating shafts 300 disposed at equal angles from the center of the rotor 200 at equal center distances. Twelve rotating shaft slide bodies A 302 are inserted into the twelve bearing bore diameters supporting the rotating shaft 300, and a round oil tight spring 354 is formed at one end of the sliding tube to suppress leakage of lubricant and fluid in the cylinder. do. Radial grooves are formed at the end of the circumference to form a radial groove to form a passage for lubricating oil, and the shaft portion of the rotating shaft 300 is dynamically connected with a groove for discharging the lubricating oil of the planetary gear 350 to receive the lubricating oil into the rotor 200 space. In this case, some of the volume is adjusted to leak. 12 holes are formed to deliver the received lubricant to the left housing 530, and the sub-rotor 250 is fixedly fastened to the rotor 200, and the movement path of the lubricating oil is transferred to the sub-rotor 250 and the sub-rotor. Rotor which divides the space between the lid 252 and the sub-rotator lid 252 to form a space, and divides the angle between the support shaft 300 and the support hole at the same center distance as the support shaft 300. Holes are formed in the sub-rotor 250 and the sub-rotor lid 252 at the fastening hole positions with the 200.

The blade pieces of the rotating piston 310 have a rotating radius so as not to interfere during rotation between adjacent blade pieces, and are composed of left and right symmetry. The planetary gear 350 between the rotor 200 and the sub-rotor 250 has a hollow park leaf spring A 352 on both sides thereof, and the blade angle of the rotating piston 310 is set based on the hexagonal foot of the rotating shaft 300. The planetary gear 350 may be formed by positioning the angle of the angle of the six-foot square, and a rotation piston 310 may be configured at another end of the rotation shaft 300, and the sub-rotor 250 may support one side of the rotation shaft 300. In addition, the rotary wheel 280 for controlling the rotation speed of the rotating piston 310 is configured on the edge. The rotor wheel 280 is attached to the edge of the sub-rotator 250 by positioning the tooth reference and the fastening hole, and the three orbital pinion gears A 290 are circumscribed with the rotor wheel 280 and the rotation ratio 8.4: 1. And rotate to mesh with each other. The idler pinion gear A 290 is configured to be side-joined with the idler pinion gear B 294, and the idler tooth 380 constitutes a tooth in the inner diameter and the outer diameter, respectively, and extends the inner diameter gear pitch portion to the middle of the rotor 200. The rotation is supported by the circumferential end of the part so that the rotational center does not deviate during the rotation, and is used as a flow path of the lubricating oil. The idle displacement gear 380 uses the planetary gear 350 as an internal gear 1: 8. The rotational pinion gear B (294) was configured to have a rotation ratio of 1: 9.6 as an external tooth difference. The rotating shaft 300 was integrally formed with the rotating piston 310 and the rotating of the rotating piston 310 rotates as the rotor 200 rotates while the rotor 200 rotates through several steps by gears. The trajectory space formed by the piston 310 while rotating and rotating is made into the cylinder space, and the outer track surface is formed by the inner surface of the outer cylinder member 600 on the surface of the cylinder space, and the inner track surface is the inner cylinder member. (650) It consists of the outer surface. Then, the space formed between the outer surface of the cylinder inner member 650 and the inner surface of the cylinder outer member 600 becomes a passage through which the rotating piston 310 rotates and rotates and is divided by twelve rotating pistons 310 to form 12 cylinder compartments. This creates a twelve-cylinder compartment that becomes a space for treating the fluid by repeatedly increasing and decreasing its volume. In addition, the projection sealing piece 652 is formed in two places where a gap occurs between the outer surface of the cylinder inner member 650 and the surface of the movement trajectory of the rotating piston 310. At this time, a portion of the surface of the cylinder is configured to replace one side of the rotor having the bearing portion of the rotating piston 310 and the cylinder left member 670 is inserted into the edge end formed on one side of the outer member, the inner member (600,650) It is configured to support by the left housing 530. The cylinder left member 670, which is in direct contact with the left side of the rotating piston 310, constitutes a fluid inlet pipe 672, a fluid discharge pipe 674, a coolant discharge pipe 522, a lubricating oil discharge pipe 536, and a rotating piston 310 The side and the rotor 200 are configured to be in dynamic contact. In one end surface of the outer and inner members 650 and 600 in the cylinder, the oil frame 690 supported by the leaf spring that maintains oil tightness during the movement of the rotor 200 is provided. Each jaw is configured in a ring-shaped shape in the cross section.

The right housing 500 is composed of a journal bearing 534 supporting the power shaft 100 and a lubricating oil sealing member 102 on the outer side of the bearing, and a circular inner shape which dynamically contacts the sub rotor 250 on the center inner surface. The groove is formed, and the flow piece 504 is formed at the outlet to increase the rotational acceleration property of the supply lubricant. A hole in which both ends of the idler pinion gear shaft 292 are fitted in the inner side of the right housing 500 is machined to the right side in contact with the intermediate housing 570 to support both ends of the shaft pin 292, and the idler pinion car slide body And insert grooves in three places so that the teeth of the pinion gear A, B (290, 294) do not interfere with rotation

The inner side of the intermediate housing 570 constitutes a circumferential groove for the coolant passage, is configured to be in a state of interference with the outer cylinder side member 600, and a conical roller bearing 532 supporting the power shaft 100 is configured at the center thereof. The lubricant oil sealing member 102 is configured to prevent the leakage of lubricant oil on the outside thereof. The portion protruding inside the left housing 530 is configured to be in an interference fit state with the inner surface of the cylinder inner member 650. In addition, the outer surface of the inner protruding portion constitutes a circumferential groove to form the cooling water passage. A groove is formed circumferentially on the side of the inner protrusion, and a lubricant discharge pipe 536 is fastened by constituting an external discharge hole in the circumference of the groove. In addition, a hole for coupling the fluid inlet pipe 672 and the fluid discharge pipe 674 is disposed at a position coincident with the inlet and the discharge hole of the fluid inlet cap 676, and the hole for fastening the coolant discharge pipe 522 on the upper side. Configure. The positions of the fluid inlet pipes and the discharge pipes 672 and 674 are different as follows depending on the purpose. In the air compressor, the fluid inlet pipe is configured in the volume increase stroke section, the fluid discharge pipe is configured in the position where the volume reduction is greatest, and the fluid conveying device is the same as the air compressor, and the fluid discharge pipe is configured in the volume reduction stroke section. In the case of a fluid power unit, the liquid inlet is the same as the fluid conveying unit in the case where the liquid volume is not expanded in the combustion chamber, and the position of the fluid inlet pipe in the device in which the volume of the gas is expanded in the combustion chamber is reduced. Is located at the largest position, and the position of the fluid discharge line is configured in the section of the volume reduction stroke.

The cylinder outer member 600 has two oil-tight frames 690 circumferentially in contact with the rotor 200 to form a lubricating oil sealing function and a fluid sealing function. The oil-tight frame 690 is supported by a leaf spring at the bottom, and is configured as a rim end portion so as to be in close contact with the cylinder left member 670 on the left side, and is configured to be in continuous contact with the intermediate housing 570.

The cylinder inner member 650 constitutes two sets of oil tight frames 690 on the end face in dynamic contact with the rotor 200 to function as a lubricant oil tightness and an oil tightness of the fluid in the cylinder. The oil-tight frame 690 is supported by a leaf spring at the bottom, and is configured as a rim end portion to be in close contact with the cylinder left member 670 on the left side, and protrudes inside the cylinder left member 670 on the inner surface of the cylinder inner member 650. Consists of continuous contact with the indented area. When the movement of the rotating piston 310 passes through the minimum volume point, since the movement traces of the body parts forming the rotating piston 310 overlap each other, the protrusions protruded on the position surface where the outer surface of the inner cylinder member 650 cannot be fixed. The oil-tight piece 652 is installed so as to be supported by the leaf spring to prevent the movement of the fluid by sliding the rotating piston 310.

The cylinder left member 670 constitutes the fluid inlet pipe 672 and the discharge pipe 674, and the outer diameter portion and the inner diameter portion are inserted close to the edge portions formed in the outer cylinder member 600 and the inner cylinder member 650, respectively. Configure. For smooth inflow and outflow of fluids, the fluid inlet and the fluid outlets have a cross-sectional area in the shape of a banana in the cylinder left member 670 at the maximum cross-sectional area of the cylinder space, and the fluid is inlet and outlet pipes 672,674. The fluid inlet cap 676 having a circular hole corresponding to the fluid inlet pipes and the discharge pipes 672 and 674 of the left housing 530 is joined to the cylinder left member 670.

The rotating piston 310 is integrated with the rotating shaft 300 at the center of rotation thereof, and the rotating piston size of the rotating body 310 is configured to have a size that does not interfere with the adjacent rotating piston 310, and the rotating piston 310 and rotating shaft 300 is formed integrally, and the outer diameters of the twelve rotating shafts 300 include a portion inserted into the rotating shaft sliding body A 302 and a portion into which the planetary gear 350 is inserted into the rotor 200 and the sub-rotor 250. The inner diameter of the rotating shaft supported by the rotating shaft sliding body A (302) to ensure that the rotating shaft 300 is assembled through the rotor 200, The outer diameter portion of the rotation shaft 300 of the portion where the planetary gear 350 is inserted, the rotation axis sliding body A (302) so that the blade angle of the rotary piston 310 and the tooth position of the planetary gear (350) are assembled in exactly the same direction. ) Hexagonal column inscribed in inner diameter should be formed. Composed of the matching point position, and constitutes a flow path that is connected to the inner diameter of the rotation axis 300 to a second side opposite to the hexagonal main myeonjung 6 for use as a lubricating oil passage. The outer diameter portion of the rotating shaft 300 supported by the rotating shaft sliding body B 304 in the sub-rotator 250 is configured by using a circle inscribed on each side of the hexagonal cylinder as the outer diameter. The inside of the rotating piston 310 constitutes a passage of cooling lubricant, the passage constitutes a lubricating oil guide piece 308, and the lubricating oil guide piece 308 is a lubricant inlet pipe 306 in the inner diameter of the rotating shaft 300. The guide piece 308 is recessed and fixed, and the rotating piston lid 316 protrusion supports the lubricating oil guide piece 308, and the edge of the rotating piston lid 316 is inserted into the side edge end of the rotating piston 310. Bonding seal is constructed. The lube oil inlet pipe 306 is inserted into the rotating shaft 300, and the difference between the outer diameter of the inlet pipe and the inner diameter of the rotating shaft 300 is configured so that the space is used as the lubricant outlet, and the inside of the inlet pipe is configured as the lubricant inlet. Outside of the 300, the planetary gear 350 is configured to be positioned between the tooth shape and the rotating piston 310 to prevent interference fit.

In the internal combustion engine, fuel injection valve 580, ignition lamp 590, pressure sensor 592 are added, and the cylinder space can be divided into intake stroke, compression stroke, expansion stroke, and exhaust stroke space. The two narrowest spaces of the cylinder spaces in which (650,600) are formed inside and outside each other can be classified into a combustion chamber and an exhaust residual chamber. The position of the fuel injection valve 580 can be configured differently depending on the type of engine and the characteristics of the fuel used, whether it is in the intake passage pipe, during the intake stroke, or during the compression stroke. However, the present embodiment is intended to form a mixer, to increase the air filling rate, to reduce the compression load by installing a continuous fuel injection at the position 20 ° (degree) starting point of the compression stroke. Therefore, the configuration of the fuel injection valve 580 is configured in the intermediate housing 570 such that the fuel supply pipe 582 is fastened and connected from the outer surface of the intermediate housing 570 to the inner surface at the start position of the compression stroke 20 degrees. The installation of the fuel injection edge 580 coincides with the position of the intermediate housing 570 fuel supply pipe 582, and the circular hole is formed in the thickness of the outer cylinder member 600 at the left end of the cylinder in accordance with the length of the fuel injection edge 580. It constitutes and forms a narrow long rectangular hole in the shortest part of the wall which isolate | separates cylinder space. Before the ignition 590 is formed in the recessed recess in the upper portion of the intermediate housing 570 forming the combustion chamber described above, and forms a screw hole to be fastened. The cylinder outer member 600 of the combustion chamber has a hole into which the electrode portion before the ignition 590 is inserted, and forms a hole connected to the pressure sensing unit 592 sensing unit at an initial stage of the expansion stroke. To install.

Example 2

Embodiment of a case in which the rotating shaft is perpendicular to the power shaft A100 and the gearing direction of the rotor is inner tooth and the number of rotations is 1

The present invention can be largely divided into the appearance of the power shaft (A100), the left housing (A530), the right housing (A500), the power shaft (A100), the rotor (A200), the inner ring of the cone roller (A532), hollow plate A spring B (A106), a rotor anti-screw nut (A108), a lubricating oil sealing member (A102), an annular rubber sealing material (A104) is configured, and the rotor (A200) has a rotating shaft (A300), a sub-rotator (A250), Half cone sliding body (A320), rotating shaft 12-foot bearing (A322), rotating shaft support plate spring (A324), ring oil sealing spring (A354), the rotating shaft (A300) planetary gear (A350), lubricating oil inlet pipe ( A306) and a rotating piston A310, and the rotating piston A310 includes a rotating piston cap A316, a straight oil tight piece A312, and a leaf spring A314 that supports the straight oil tight piece. The sub-rotator (A250) is composed of a rotor (A280), a sub-rotor cover (A252), an inner cone support (A538), a conversion gear (A380), a half-conical sliding body (A320), the rotating shaft 12-axle shaft part It consists of a rotating shaft slide body (A304). The left housing (A530) is the idler pinion gear housing, the circulating piece (A504), the outer ring of the cone roller bearing (A532), the cylinder left member (A670), the lubricating oil supply pipe (A502), the oil tight frame (A690), the cooling water supply pipe (A520) , Fluid inlet pipe (A672), fluid discharge pipe (A674), lubricating oil sealing member (A102) and the idler pinion gear housing A, B (A290, 294), inner member (A274), left member ( A272), the right side member A270, the fixing mechanism and the idler pinion gear shaft A292, and the shaft sliding body A296, and the oil tight frame A690 is configured with a leaf spring for supporting the oil tight piece. The right housing (A500) is a conical roller bearing (A532) outer ring, cylinder right member (A620), lubricating oil discharge pipe (A536), oil tight frame (A690), coolant discharge pipe (A522), lubricating oil sealing member (A102). There is a rotor (A200) integrated with the power shaft (A100) and the rotor (A200) each of the 12 bearing parts supporting the rotating shaft (A300) arranged at 12 equiangular in the vertical direction with the power shaft (A100) at the center Make up the half inner cone groove. Similarly, the twelve half inner conical grooves are configured in the sub-rotator A250. In addition, the half inner conical groove each constitutes a half cone sliding body (A320), and supports only the half of the rotor cone (A200) and only the other half of the remaining cone running surface of the rotating shaft (A300) for supporting only half of the conical slide surface of the rotating shaft (A300). The sub-rotator (A250) is fixed to the fixing mechanism A (A256), for example, 12 bolts in the space for dividing the angle between the bearing portion with a bolt, and configured to indent and cover the sub-rotator cover for fixing the depression A (A256) A252 is composed of a disc that is coupled to the inner circumferential end of the secondary rotor (A250) side, the outer diameter is configured to be inserted into the circumferential end of the side of the secondary rotor (A250), so as to form a plane with the side of the secondary rotor (A250) do. At this time, the outer end surface generated by coupling between the rotor (A200) and the sub-rotator (A250) is composed of the inner surface of the cylinder space surface, so the coupling step must be maintained so as not to occur, and the inserted 12 half-cone slide bodies (A320) One side of the) constitutes a ring oil tight spring (A354) to suppress the leakage of fluid. The blades of the rotating piston (A310) consist of left and right symmetry without interfering between adjacent blades during rotation, and the straight oil tight piece (A312) is the same as mentioned above. Side is composed,

Between the rotor (A200) and the sub-rotator (A250) there is a planetary bevel gear (A350) having a rotation axis (A300) as an axis, one side of the rotation axis (A300) is integrally formed with a rotating piston (A310). The support of the central rotating shaft (A300) is composed of a rotating shaft 12-corner shaft bearing portion (A 322) that is fixed to the rotor by a fixing mechanism B (A326), the rotating shaft 12-foot cylinder bearing portion (A322) has a 12-sided outer structure It is configured so that the inner diameter is circular and fitted to the circumferential end of the rotor (A200). Then, it is configured to penetrate through the support hole in which the rotating shaft is inserted in the center of each of the octagonal surfaces, and the rotating shaft sliding body B (A304) is inserted into the hole. Conical slide surfaces of the twelve rotating shafts 300 to withstand the centrifugal force and torsional action of the rotating shaft, and also to the negative rotor (A250) to control the rotational speed of the rotating piston (A310) ) Is formed in the inner diameter part. The joint between the autonomous rotor (A280) and the sub-rotator (A250) is configured in accordance with the position criteria, and the three revolution pinion gear A (A290) in engagement with the rotor bogie (A280) at a rotation ratio of 4: 1 to engage and rotate. Configure. The idler pinion gear A (A290) constitutes a side junction with the idler pinion gear B (A294), and the idler tooth (A380) constitutes an internal tooth and a side bevel tooth, and the idler tooth (A380) is a planetary bevel tooth (A350). ) Is configured to have a rotation ratio of 1: 5 to the side, and the idler pinion gear B (A294) was configured to have a rotation ratio of 1: 5 as the internal gear difference. The idler pinion gear housing includes the idler pinion gears A and B (A290 and A294) inside, and includes a fixing mechanism and an idler pinion gear shaft bar (A292), an inner member (A274), a left member (A272), and a right member (A270). It consists of a shaft slide body (A296), and a lubricant hole is provided in the center of the revolution pinion gear shaft (A292) to supply lubricant to the shaft (A292), the shaft slide body (A296), and the boss inner diameter. The left member A272 serves as a support function of the process pinion gear shaft A292 by serving as a lubricating oil supply circumferential groove in the left housing A530 and a lid of the circulating piece A504. The inner diameter of the inner member A274 becomes a lubricating oil supply passage, and the portion incorporating the idler pinion gear recesses the groove so as not to interfere when the gear is rotated. The rotation of the rotating piston (A310) is a trajectory space formed by rotating the rotor (A200) while rotating the rotor (A200) rotating the rotor (A200) as the rotating piston (A310) rotates and rotates. A cylinder space was used, and the left track surface was constituted by the inner surface of the cylinder left member A670 on the surface of the cylinder space, and the right track surface was constituted by the inner surface of the cylinder right member A620. Then, the space formed between the inner surface of the cylinder left member A670 and the inner surface of the cylinder right member A620 becomes a passage through which the rotating piston A310 rotates and rotates and is divided by twelve rotating pistons A310 and is divided into 12 cylinder compartments. This creates a twelve-cylinder compartment that becomes a space for treating the fluid by repeatedly increasing and decreasing its volume. Either one of the cylinders on the side of the rotating piston (A310) in which the rotational direction coincides with the rotational direction. Here, two places where a gap occurs between the inner surface of the right cylinder member (A620) and the surface of the movement trajectory of the rotating piston (A310) It is configured to be oil-tight with the oil-tight piece A652. At this time, the inner diameter element of the cylinder space is configured to replace the outer cross-section by the combination of the rotor (A200) and the sub-rotator (A250) having the bearing portion of the rotating piston (A310). A fluid frame (A690) supported by a leaf spring that maintains oil tightness during the movement of the rotor (A200) inside each of the left and right housings (A530, A500) that surround and support the cylinder left and right members (A670, A620). ) Each of the two tanks in a circular ring shape on the inner side. Outer coupling of the cylinder left and right members (A670, A620) is fitted to the left and right uneven portions formed to be closely supported by the left and right housings (A530, A500), the left housing (A530) is the power shaft (A100) To support the conical roller bearing (A532), to form a lubricating oil sealing member (A102) on the outside of the bearing, to the center inner surface to form a circulating piece (A504) at the outlet of the circumferential groove in order to increase the lubricating oil supply speed In addition, three screw holes for installing the idler pinion gear housing are formed at the position of the circulating piece A504, and the integration of the left member A272, the inner member A274 and the right member A270 is combined with a fixing mechanism. . The inner side of the left housing A530 has a coolant passage in a radial structure so that the coolant flows evenly through the left and right housings A530 and A500, and the coolant passage in the center of the left housing A530 forms a circumferential passage. It is configured to be supplied circumferentially. Installed on the left housing (A530), the oil tight frame (A690) in dynamic contact with the surface of the sub-rotor (A252) is supported by a leaf spring at the bottom, and constituted by inserting a circumferential groove in the left housing (A530). The fluid inlet pipe, the discharge pipe (A672, 674) is configured in the left housing but the first embodiment, the lower side is composed of a hole for fastening the cooling water supply pipe (A520) for the inlet of the cooling water.

The right housing (A500) has a conical roller bearing (A532) for supporting the power shaft (A100) at the center, the lubricant oil sealing member (A102) for preventing the leakage of lubricant oil is formed on the outside. The lubricating oil discharge pipe A536 penetrates through the right housing A500 at one end of the lubricating oil circumferential groove formed therein and is fastened to the right housing A500. The cooling water discharge pipe (A522) is configured to penetrate the upper side of the right housing (A500) and the cooling water passage is formed in a radial structure inside the right housing (A500) so that the coolant is evenly discharged from the left and right housings and the center of the right housing (A500). Cooling water passage in the configuration is configured as a cylindrical passage so that the cooling water is supplied in a circumferential shape. Installed on the right housing (A500), the oil tight frame (A690) that is in dynamic contact with the rotor side is supported by a leaf spring at the bottom, and constitutes by inserting a circumferential groove in the right housing (A500).

The cylinder left member A670 constitutes the fluid inlet pipe 672 and the discharge pipe A674, and the fluid inlet cross section is approximately banana shaped to the cylinder left member A670 at the maximum cross sectional area level of the cylinder space for smooth entry and exit of the fluid. Configure each.

The cylinder right side member A620 is protruded in two places because the trajectory surface of the rotating piston A310 is not fixed to the cylinder space surface having the same rotational direction as the rotating direction of the rotating piston A310. A sealing piece A652 is constituted. When the movement of the rotating piston A310 passes through the minimum volume point, the movement traces of the body parts forming the rotating piston A310 overlap each other, and thus the projection oil tight piece on the position where the outer surface of the cylinder right member A620 cannot be fixed. It is installed to support the (A652) by the leaf spring to prevent the movement of the fluid by sliding the sliding of the rotating piston (A310). The outer side is composed of a protruding frame to be in close contact with the cylinder seat member (A670),

The rotor (A200) is composed of a power shaft (A100) and gear tooth (spline) in the center of the rotation, the outer surface serves as a cylinder inner member, the support of the central rotation axis (A300) to the rotor (A200) It consists of a rotating shaft 12-foot column bearing part (A322) that is fixed by a fixing mechanism, the rotating shaft 12-foot cylinder bearing part (A322) has an outer end of the octagonal structure, the inner diameter is circular and inserted into the circumferential end of the rotor (A200) Configure to Then, through the support hole in which the rotation axis (A300) is inserted in the center of each of the octagonal surface, the rotation axis sliding body B (A304) is inserted into the hole. Rotating shaft support plate spring (A324) is configured to prevent sagging of the rotating shaft (A300) is configured in the 12-foot inner diameter. In the inner wall of the rotor (A300), the planetary bevel gear (A350) is composed of twelve grooves at equal angles so that rotation interference does not occur, and the grooves for the lubricating oil passage connecting the grooves with the grooves, and the lubricating oil to the right housing (A500) Twelve holes are allowed to pass through.

In order to control the number of revolutions of the rotating piston (A310) in the sub-rotator (A250) to generate a rotary car (A280) in the inner diameter or position reference between the rotor (A280) and the sub-rotor (A250) It joins together and it is comprised so that a lubricating oil may be conveyed by the centrifugal force of the sub-rotator A250 to the hole of the rotating shaft A300. The inner rotor support (A538) is formed on the inclined portion of the left side of the sub-rotator (A250), and is supported by a leaf spring below the inner cone support (A538), so that the sub- rotor A250 is elastically supported to be spaced to the left. , The surface of the inner cone support (A538) is composed of a groove through which lubricating oil flows, the rest is the same as in Example 1.

The technical effect of the rotating piston piston fluid treatment machine of the present invention is to minimize the problems of friction loss and inner wall damage by the independent movement of the piston is not constrained to the cylinder, and to obtain a change in volume to process the fluid. All components connected to the power shaft in the process of doing the rotational motion can be eliminated by the reciprocating crank mechanism in the meantime, and it is possible to eliminate the problems caused by the reciprocating crank mechanism. Compression device, fluid transfer device, fluid power device, rotating piston of internal combustion engine The cooling system is proposed to cool to a level that maintains the mechanical strength, and the following is added to the internal combustion engine.

By realizing continuous combustion and using only the first ignition before ignition, the life of the ignition is longer than the existing system, and it is possible to remove the imbalance of combustion expansion pressure, and stable combustion is possible even at the mixing ratio near the lowest ignition limit. You can improve it,

It is possible to secure a homogeneous mixer even at partial load by minimizing the variation of atomization particle size, injection distance and injection angle of the injected fuel due to the change of injection area according to the change of fuel injection amount. Since there are several unit cylinder spaces in the expansion stroke in the cylinder, the output characteristics of the power are stabilized, so there is no danger of engine stop at low speed.In high speed operation, the power characteristics are stable at high speed because the combustion speed increases in proportion to the fluidity of the mixer.

By eliminating unnecessary counterweights and flywheels, it is possible to improve the responsiveness of the operation and the fuel cost by reducing the axial inertia force, and also because the air tightness in the unit space formed by the cylinder and the rotating piston is almost the same as that of the reciprocating engine. The function of the brake can be effective only by blocking the fuel,

In terms of annular configuration of the cylinder space, high output per unit volume is obtained, fuel injection valves and ignition can be made with only one, valve driving mechanisms can be removed, and the area of the inlet and exhaust pipes is reduced to the level of the cylinder cross section. It is possible to increase the efficiency to provide a technical effect that is possible.

Therefore, it may be possible to replace the conventional fluid treatment apparatus.

1 is a cross-sectional view of a rotating piston processing fluid rotating machine with 12 horizontal rotating shafts and 1 rotating motion, with the outer autonomous vehicle externally driven.

2 is a cross-sectional view of a rotating piston processing fluid rotating machine with 12 vertical rotational axes and 1 rotational movement, with the inner rotor inside;

3 is a gear connection cross-sectional view of FIG.

4 is a cutaway view of idle pinion gears A and B

5 is a cross-sectional main part configuration diagram of FIG.

6 is a toothed cross-sectional configuration of FIG. 2 and FIG.

7 is a process diagram of the volume change due to the rotation and rotation by angle of FIG.

8 is an operational cross-sectional view of a fluid compression device of the type 1

9 is an operational cross-sectional view of the fluid transfer and power unit of FIG.

10 is a cross-sectional view of an operation of a gas expansion fluid power unit of the type 1 in the FIG.

11 is an operational cross section of an internal combustion engine of the type 1

12 is a diagram showing the inner shaft of the power shaft and the conical roller control ring of FIG.

13 is a cross-sectional view of the rotor of FIG.

14 is a shape diagram of the inner cylinder member and the outer member of FIG.

FIG. 15 is a configuration diagram of the cylinder left member of FIG.

FIG. 16 is a cutaway view of the bundle of rotating pistons of FIG.

17 is a detailed cross-sectional view of the rotating piston

18 is a detailed cross-sectional view of the combustion chamber portion of FIG.

19 is a detailed cross-sectional view of the fuel injection device bundle of FIG.

20 is a detailed (front, side, plane) view of the straight oil tight piece

21 is a lubrication supply relationship of the right housing of FIG.

※ Explanation of Codes and Terms of Major Parts of Drawings

100, A100-Power Shaft, 102, A102-Lubricant Oil Seal,

104, A104-Round rubber confinement, 106, A106-Hollow park leaf spring,

108, A108-Rotor anti-nut, 200, A200-Rotor,

202-rotor lid, 250, A250-secondary rotor,

252, A252-Sub rotor lid, A256-Fixture A, A270-Right member,

A272-left member, A274-inner member, 280, A280-rotor

290, A290-idle pinion gear A, 292, A292-idle pinion gear shaft,

294, A294-Static pinion gear B, 296, A296-Shaft sliding body,

300, A300-Rotating shaft, 302-Rotating shaft sliding body A,

304, A304-Rotating shaft body B, 306, A306-Lubricant inlet pipe,

308-- Lube guide piece, 310, A310-Rotating piston,

312, A312-Straight sealing piece, 314, A314-Straight sealing piece spring,

316, A316-Rotating piston lid, A320 --- Half cone cylinder

A322-rotating shaft 12 foot bearing, A324 --- rotating shaft supporting leaf spring,

A326 --- Fixture B, 350, A350 --- Planetary Gear,

352-Hollow Spring Leaf A, 354, A354 ---

380, A380 --- changeover gear, 500, A500 --- right housing

502, A502 --- Lubricant supply lines, 504, A504-Flow section

520, A520-Cooling water supply line, 522, A522-Cooling water discharge line

530, A530-Left housing, 532, A532-Conical roller bearing,

534-Journal bearings, 536, A536-Lubricant drain lines

A538-Inner cone support, 570-Intermediate housing, 580, A580-Fuel injection valve,

582, A582-fuel supply pipe, 584, A584-plunger, 586, A586-coil spring,

590, A590-Before ignition, 592, A592-Pressure sensor, 600-Cylinder outer member,

A620-cylinder right member, 650-cylinder inner member,

652, A652 --- Proof seal, 670, A670-Cylinder left member

672, A672-fluid inlet pipe, 674, A674-fluid outlet pipe,

676, A676-Fluid inlet projection, 690, A690 ---

Oil tightness: prevent leakage of fluid

Oil-tight frame: ring-shaped to prevent leakage of fluid

Protrusion oil seal: It is installed at the edge of cylinder inner member and is oil-tight.

Inner cone: Conical space

Claims (20)

In the means for treating fluid, the housing is composed of a power bearing part, a cylinder member, an idle pinion difference A, B, a bearing part, a fluid inlet and an outlet, The power shaft consists of rotor, sub-rotator, rotor gear, idle gear, and rotating shaft, and the rotating piston and planetary gear are composed on each side of several rotating shafts composed of equidistant angles of power axis on the rotor. And B is composed of side joints, the transition gear is composed of two teeth of the same body, If the number of rotations of the rotating piston is X in one rotation of the rotor, the number of teeth of the idler gear that meshes with the planetary gear becomes A times, and the number of teeth of the idler gear that engages the idler pinion teeth B is L times, and the idler pinion gear The number of teeth of the rotor that meshes with A is multiplied by M times, and it consists of a linkage relationship of M / L + X / A = 1, The inner surface of the cylinder member is composed of the surface element of the trajectory space formed only by the revolution and rotation of the rotating piston, replaces part of the surface of the cylinder space with the surface of the rotor, and constitutes the inlet and outlet of the fluid at the surface of the cylinder member. Rotating piston type rotary fluid processing machine, characterized in that The rotating piston processing machine according to claim 1, wherein the rotating piston rotating shaft is configured parallel to the power shaft. delete The rotating piston rotating fluid processing machine according to claim 1, wherein the rotating piston rotating shaft is configured perpendicular to the power shaft. The rotating piston processing type rotating fluid treatment machine according to claim 1, characterized in that the autonomous vehicle consists of an internal tooth. The rotating piston processing machine according to claim 1, wherein the autonomous vehicle is composed of an external tooth. The rotating piston processing machine of claim 1, wherein the outer surface of the rotating piston has several half-hone grooves for fluid movement. The rotating piston processing machine according to claim 1, wherein the cross-sectional shape of the straight oil tight member on the outer surface of the rotating piston becomes 'b' to have a rotational separation prevention jaw. The method according to claim 8, wherein the outer surface of the rotating piston has four straight oil pieces and the 'b' direction of the four straight oil pieces is configured so that the tails of 'b' face each other on one side of the rotating piston, Rotating fluid processing machine characterized in that the tail portion is formed to be mutually opposite, has a left and right locking jaw at the lower end of the straight oil tight piece, the side surface of the straight oil tight piece is composed of a half bone groove for preventing adhesion and fluid penetration gap The rotating piston processing machine according to claim 1, having 12 rotating pistons and at least three rotating pinion teeth A and B. delete The rotating piston processing machine according to claim 1, wherein a projection oil-tight piece is formed in one cylinder space so as to form a gap between the track surfaces of the rotating pistons. The rotating piston processing machine according to claim 1, wherein the housing part includes a cylinder space function. The rotating piston processing machine according to claim 1, wherein the rotating piston is a fixed flow piece for accelerating the lubricating oil from the lubricating oil supply circular half groove formed in the housing to the outlet of the rotor. The rotating piston processing machine according to claim 1, wherein the position of the outlet of the lubricating oil configured in the rotor is configured to have a radius larger than that of the inlet so that the feeding of the lubricating oil is performed by the centrifugal force difference of the rotor. delete The rotating piston processing machine according to claim 1, wherein the cooling fluid passage is formed inside the rotating piston rotating shaft and divided into inflow and outflow passages. The inlet gas is a fuel and air mixer when the fuel injection valve is in the intake passage, and the inlet gas is air when the fuel injection valve is located in the cylinder space, and is configured at the compression peak of the ignition transition mixer, and there is no combustion. Rotating piston type rotating fluid treatment machine, characterized by a pressure sensor attached and operating as an internal combustion engine 19. The fuel injection device of claim 18, wherein the fuel injection device is configured at a compression stroke start position and is installed in a cross-sectional direction of the cylinder space. Rotating piston type rotating fluid treatment machine, characterized in that the spring is configured The rotating piston processing machine according to claim 1, wherein the rotation speed of the rotor and the rotation speed of the rotating shaft are the same.