JP5218929B1 - Rotary combustion engine, hybrid rotary combustion engine, and machine equipped with these - Google Patents

Abstract

A rotary combustion engine, a hybrid rotary combustion engine, and a highly reliable rotary combustion engine having a simple structure, a small number of parts, high performance and low cost production without using a complicated crank mechanism The present invention provides a mechanical device including these.
SOLUTION: A supercritical fluid generator / combustor 500 generates a high-temperature combustion gas and a supercritical fluid, and a rotary expander 100 expands the high-temperature combustion gas and the supercritical fluid to generate power on an output shaft. The low-temperature and low-pressure steam discharged from the rotary expander is cooled and liquefied by the cooler 12 to generate a low-temperature and low-pressure working fluid, and the low-temperature and low-pressure working fluid is pressurized by a rotary pump and the supercritical fluid generator / combustor 500 By generating high-temperature and high-pressure supercritical fluid by pumping it to the critical fluid generator 550, the structure of the rotary combustion engine, hybrid rotary combustion engine, and mechanical device equipped with these is simplified and the size and performance are improved. .
[Selection] Figure 1A

Description

  The present invention relates to a heat engine and a heat engine drive mechanical device, and more particularly, to a rotary combustion engine, a hybrid rotary combustion engine, and a mechanical device including these.

  In recent years, as a countermeasure against global warming, a hybrid engine has been proposed in which combustion heat energy and steam generated by collecting exhaust heat energy of a heat engine are expanded to improve engine efficiency.

  In Patent Document 1 of the invention of the same inventor, a rotary combustion engine and a rotary expander are connected in tandem, and the rotary expander is operated with steam generated by recovering exhaust heat energy of the rotary combustion engine. A hybrid rotary engine and a hybrid vehicle equipped with the same have been proposed.

  In Patent Document 2, a composite piston that operates with combustion heat energy and water vapor is built in a reciprocating internal combustion engine, and the composite piston that operates by recovering exhaust heat energy of the internal combustion engine is operated with water vapor and output. A torque-assisted hybrid engine has been proposed.

Japanese Patent Laid-Open No. 2002-227609 US Pat. No. 7,997,080

  By the way, in the hybrid rotary engine disclosed in Patent Document 1, a plurality of housings and a plurality of working chambers for a rotary combustion engine and a rotary expander, and a plurality of rotary pistons and timing rotors disposed in the respective working chambers are provided. Since there was a sliding part, it was difficult to efficiently perform a confidential seal, so the leakage of working gas was large, and it was difficult to put a small high-performance hybrid rotary engine into practical use.

  The hybrid engine disclosed in Patent Document 2 has a configuration in which water vapor obtained by recovering exhaust heat energy by an exhaust heat recovery heat exchanger disposed on the exhaust side of the internal combustion engine is expanded by a composite piston. For example, when this engine is employed in automobiles such as passenger cars and trucks and buses, when driving in urban areas, low-speed driving is frequently performed and the engine output is low. For this reason, in urban driving, the exhaust temperature is rarely maintained at a high temperature continuously, and the generation of water vapor is insufficient. Therefore, it was difficult to put into practical use a small high-performance hybrid engine with a simple structure.

  The present invention has been made in view of such conventional problems, and is a rotary combustion engine, a hybrid rotary combustion engine, and a mechanical device including these, having a simple structure, a small number of parts, and capable of low-cost production. The purpose is to provide.

In order to achieve the above object, according to the first aspect of the present invention, the rotary heat engine compresses the compressed air by compressing the intake air and the rotary pump that pressurizes the working medium to generate the high-pressure working medium. A rotary compressor to be generated; and the rotary pump and the rotary compressor are drivingly connected to generate a high-temperature high-pressure combustion gas by combusting a mixture of the compressed air and fuel, and thermal energy of the high-temperature high-pressure combustion gas A supercritical fluid generator / combustor that generates a supercritical fluid from the high-pressure working medium, and a rotary expander that generates power by expanding the high-temperature and high-pressure combustion gas and the supercritical fluid. A rotary combustion engine, wherein the rotary expander has first and second end face wall portions having first and second sleeve portion fastening clutches, respectively. An engine housing, an annular working chamber formed in the engine housing, an output shaft having a clutch engaging portion disposed at an axially intermediate portion of the annular working chamber, and a rotatable housing in the annular working chamber And the first and second boss portions and the first and second boss portions extending axially outward from the first and second boss portions and between the first and second rotational directions by the first and second sleeve portion fastening clutches. The first and second rotary pistons having first and second sleeve portions that can be switched between a locked state and an unlocked state with respect to the first and end face wall portions, the clutch engaging portion, and the first and second The first and second boss portions are respectively switched between a locked state and an unlocked state with respect to the clutch engaging portion between the second rotational direction and the first rotational direction between the second boss portion and the second boss portion. First Beauty and second boss engagement clutch, in that it comprises the gist.

According to the invention described in claim 2, in addition to the structure of claim 1, the combustor in which the supercritical fluid generator / combustor is disposed concentrically with the rotary pump and the rotary compressor. A casing, a combustion chamber formed in the combustor casing, and a portion of the thermal energy of the high-temperature high-pressure combustion gas that is disposed along the combustion chamber and receives the heat energy to heat the high-pressure working medium A gist is provided with a supercritical fluid generator that generates the supercritical fluid .

  According to the invention described in claim 3, in addition to the configuration of claim 2, the rotary compressor includes a rotor working chamber having an inlet for introducing the intake air and an outlet communicating with the combustor; A charge rotor that is rotatably accommodated in the rotor working chamber and is drivingly connected to the output shaft, and sucks the intake air while rotating on the inner peripheral surface of the rotor working chamber, and the suction after suction. At least one lobe discharging air into the combustor while pressurizing air, a curved sliding recess formed in a circumferential rear edge of the lobe in a radially inner region of the lobe, and adjacent to the inlet A movable valve movable with respect to the charge rotor, and formed between the movable valve and the curved sliding recess, and discharges the intake air to the combustor under pressure. And summarized in that and a charge chamber.

According to the invention described in claim 4 , in addition to the structure described in any one of claims 1 to 3 , the rotary expander is a first for generating primary power by expanding the high-temperature high-pressure combustion gas. A rotary machine section; and a second rotary machine section that expands the supercritical fluid to generate secondary power, and further cools the low-temperature and low-pressure expansion gas discharged from the second rotary machine section, thereby rotating the rotary pump. It is a summary to provide a cooler to be supplied to.

According to the fifth aspect of the present invention, the gist is that the mechanical device includes the rotary combustion engine according to any one of the first to third aspects.

In the configuration according to claim 1, the rotary combustion engine includes a supercritical fluid generator and a combustor, and generates a high-temperature high-pressure combustion gas by combusting a mixture of compressed air and fuel, and a high-temperature high-pressure combustion gas. A supercritical fluid is generated from a high-pressure working medium using a part of the thermal energy of the medium. When natural gas is used as the fuel, the high-temperature and high-pressure combustion gas reaches 1200 ° C. to 1500 ° C. in the combustion chamber, and the supercritical fluid generator uses a part of the thermal energy of this high-temperature gas. When the working medium is water, supercritical water of around 350 bar is generated at 600 ° C. to 800 ° C., and the supercritical water expands explosively with a rotary expander. The explosion pressure generated at this time reaches about 1000 kg per 10 cm 2 in the rotational direction of the rotary piston. For this reason, a high-performance hybrid rotary combustion engine can be put into practical use. The usage distribution of the thermal energy of high-temperature and high-pressure combustion gas in the production of supercritical water can be set appropriately. In addition to water, the working medium may be carbon dioxide, a mixed fluid of water and carbon dioxide, a mixed fluid of water and acetone (mixing ratio: 50%: 50%), or other working fluid. In the rotary expander, part of the housing and part of the output shaft are part of the clutch means, so a rotary combustion engine with a simple structure that greatly reduces the number of parts without using separate and independent components. Can be produced at low cost.

In the configuration of claim 2, the supercritical fluid generator / combustor includes the supercritical fluid generator disposed along the combustion chamber formed in the combustor casing. The supercritical fluid can be generated from the high-pressure working medium by efficiently receiving a part of the thermal energy.

  According to a third aspect of the present invention, in the charge rotor having at least one lobe, the rotary compressor forms a curved sliding recess in the radially inner region of the lobe and sucks from the charge chamber while cooperating with the movable valve. Since air is discharged into the combustor under pressure, a rotary compressor with a small number of parts and a high pressure ratio can be employed with a simple structure.

According to the invention described in claim 4 , the rotary expander expands the high-temperature high-pressure combustion gas to generate primary power, and expands the supercritical fluid to generate secondary power. The second rotary machine unit is provided, and the primary power and the secondary power can be simultaneously generated on the output shaft by one rotary expander. As a result, a small and high-performance hybrid rotary combustion engine with a simple structure can be put into practical use. The rotary expander further includes a cooler that cools the low-temperature and low-pressure expanded gas discharged from the second rotating machine unit and supplies the gas to the rotary pump, so that the working medium can be repeatedly used. It is also possible to significantly reduce the running cost.

According to the fifth aspect of the present invention, the mechanical device includes the rotary combustion engine according to any one of the first to fourth aspects, whereby a small high-performance mechanical device can be put into practical use. For example, when this mechanical device is applied to a power generation device, it is possible to generate power with extremely high energy efficiency. In addition, when this machine is applied to vehicles such as passenger cars, trucks and buses, locomotives and ships, it is possible to provide a machine with a simple structure, low production costs, and high fuel efficiency. Become.

1 shows a block diagram of a mechanical device using a hybrid rotary combustion engine according to an embodiment of the present invention. 1B is a schematic diagram of the hybrid rotary combustion engine shown in FIG. 1A. FIG. 1C-1C sectional drawing of the supercritical fluid production | generation part and combustor shown to FIG. 1B is shown. 1D-1D sectional drawing of the rotary compressor shown to FIG. 1B is shown. 1C shows a cross-sectional view of the rotary expander shown in FIG. 1B. 1E shows a partial cross-sectional perspective view of the rotary expander shown in FIG. 1E. 3A shows a IIIA-IIIA cross-sectional view of the rotary expander of FIG. 1E. FIG. 3B shows a IIIB-IIIB cross-sectional view of the rotary expander of FIG. 1E. FIG. 1E shows a cross-sectional view of the rotary expander of FIG. FIG. 4B shows a cross-sectional view of the rotary expander of FIG. 1E along IVB-IVB. An example of the retainer of the clutch for 1st sleeve part fastening shown to FIG. 3A is shown. An example of the spring member of the clutch for 1st sleeve part fastening shown to FIG. 3A is shown. 1E shows a partially enlarged cross-sectional view of the rotary expander shown in FIG. 1E.

  Hereinafter, a mechanical apparatus employing a hybrid rotary combustion engine according to a first embodiment of the present invention will be described in detail with reference to the drawings. In the following description, the mechanical device 10 is described as being applied to a load driven by the hybrid rotary combustion engine 50. However, the mechanical device 10 of the present invention may be, for example, a truck, a bus, a motorcycle, an automatic three-wheel vehicle. Vehicles such as cars, steam locomotives, diesel locomotives, ships, aircraft, space shuttles, special vehicles such as tanks, and various other machines such as agricultural machinery, construction machinery, and stationary / movable generators Including equipment.

  The mechanical device 10 includes a rotary expander 100 that is drivingly connected to a load L such as a propulsion device and a generator via a power transmission device (not shown) such as a speed reducer, a transmission, and a clutch. The hybrid rotary combustion engine 50 further compresses the intake air of the intake system Ai including an air filter (not shown) to generate compressed air CA, and pressurizes the working medium to generate the high-pressure working medium WF. A rotary pump 350A to be generated and a supercritical fluid generator / combustor 500 are provided. The working medium is selected from water, carbon dioxide, a mixed fluid of water and carbon dioxide, a mixed fluid of water and acetone, or other working media. As will be described later, the rotary expander 100 expands the high-temperature and high-pressure combustion gas to generate the primary power on the output shaft 132 and expands the supercritical fluid to generate the secondary power on the output shaft 132. 2 rotation machine part.

  The high-pressure working medium WF is supplied to the working medium supply nozzle 552 of the supercritical fluid generator / combustor 500 via the check valve CV1. The compressed air CA is supplied to the intake air supply port 56. A fuel injection nozzle 60 is connected to the intake air supply port 56, and fossil fuel or waste vegetable oil such as natural gas, shale gas, shale oil, kerosene, heavy oil, etc. from the fuel tank FT through the fuel pump FP and the fuel control valve FV. The fuel F selected from the biomass fuel which consists of etc. is supplied. The supercritical fluid generator / combustor 500 burns a premixed mixture of the compressed air CA and the fuel F to generate a high-temperature and high-pressure combustion gas HTG, and supplies it from the discharge port 44 to the first inlet 124 of the rotary expander 100. At the same time, a part of the thermal energy of the high-temperature high-pressure combustion gas HTG is used to heat the high-pressure working medium to generate a supercritical fluid SCF and supply it to the second inlet 126 of the rotary expander 100 via the open / close control valve COV. To do. At this time, exhaust gas is exhausted from the first rotating machine part of the rotary expander 100 via the first outlet 128, and low-temperature and low-pressure expanded gas is discharged from the second outlet 130 from the second rotating machine part.

  The low-temperature and low-pressure expanded gas is cooled and liquefied by the cooler (condenser) 12, and when the working medium is water, it is recovered as working water LWF. The working water LWF is pressurized by the rotary pump 35A to become the high-pressure working medium WF. It will be recycled in subsequent cycles.

  The supercritical fluid generator / combustor 500 includes a pressure sensor 4 that detects an internal pressure of the supercritical generator and outputs a pressure signal PS, and a temperature sensor 16 that detects an operating temperature and outputs a temperature signal. The rotation speed sensor 18 is mounted in the vicinity of the output shaft 132, and these detection signals S1, S2S3 are output to the controller 20. The input device 22 sets various control programs for controlling the opening degree of the fuel control valve FV and the opening / closing timing of the opening / closing control valve CO with respective operation patterns, calendar signals, and input signals such as operation parameters. In response to the detection signals S1, S2S3, the controller 20 opens and closes the open / close control valve COV at a predetermined cycle, for example, several Hz to several hundred Hz, and the pressure of the supercritical fluid becomes a predetermined pressure, for example, a maximum pressure value of 300 to 450 bar. To control.

  As shown in FIG. 1C, the supercritical fluid generator / combustor 500 includes a premixed gas generator 40 that generates a premixed gas of the compressed air CA for combustion and the fuel F. The premixed gas generator 40 is supplied with the fuel F from the fuel tank FT via the fuel control valve FV and the fuel pump FP. As the fuel, a fossil fuel such as heavy oil, light oil or kerosene or a carbonaceous fuel such as biomass liquid fuel such as waste cooking oil is used. In recent years, shale gas and shale oil, which have a high degree of attention, are preferably used. The fuel F is premixed with the compressed air CA, and the premixed gas is ignited by the ignition unit 42 to generate a high-temperature and high-pressure combustion gas HTG. The high-temperature high-pressure combustion gas HTG is supplied to the first inlet 124 of the rotary expander 100 and is expanded by the first rotating machine unit, and primary power is generated on the output shaft 132. The exhaust gas is exhausted from the first outlet 128 to the outside.

  In FIG. 2, the supercritical fluid generator / combustor 500 supplies a high-temperature and high-pressure combustion gas HTG discharged from the discharge port 44 to the first inlet 124 of the rotary expander 100 (not shown). Is provided with a cylindrical combustor casing 36 connected to the rotary expander 100 via a spacer 30 formed therein. The combustor casing 36 is formed from a high-temperature heat-resistant material such as a Ni-based ultra-high-temperature heat-resistant alloy or ceramic, but the inner peripheral portion may be formed of a liner formed from the high-temperature heat-resistant material. A spiral wall portion 37 is formed on the radially inner side of the combustor casing 36, and the spiral wall portion 37 extends in a spiral shape from the outer peripheral side toward the center portion, and has an inner diameter larger than the outer shape of the output shaft 132 of the rotary combustion engine 100. An inner sleeve 37S having an inner peripheral wall 37a is provided. A spiral combustion chamber 38 is formed in the space between the combustor casing 36 and the spiral wall portion 37 so as to extend to the inner sleeve 37 </ b> S in a spiral shape in a plane region perpendicular to the central axis of the output shaft 132. The spiral combustion chamber 38 promotes complete combustion of the premixed gas by extending the contact time and residence time between the fuel and air, and effectively superheats the heat energy of the high-temperature high-pressure combustion gas HTG. There is an effect to transmit to.

On the upstream side of the spiral combustion chamber 38, an ignition part 42 made of a spark plug or a ceramic heater is disposed in the vicinity of the premixed gas generation part 40. The premixed gas generation unit 40 includes an air supply unit 50 including a cylindrical outer tube supported in a tangential direction of the combustor casing 36, and a fuel supply nozzle 60. A cylindrical inner tube 52 extending concentrically therewith is disposed inside the cylindrical outer tube 50. The air supply unit 50 includes a swirl flow collision unit 54 that generates a premixed gas by mixing with the fuel F while generating a high-speed swirl flow of the compressed air CA. The air supply unit 50 includes an annular compressed air jet chamber 55 that functions as a compressed air flow passage, a compressed air introduction port 56 for guiding the compressed air CA into the annular compressed air jet chamber 55, and an annular compressed air jet chamber 55. And a conical high-speed flow generating portion 58 formed at the tip portion. A plurality of swirl flow generating blades 62 for generating a swirl flow of compressed air are formed in the high-speed flow generating unit 58 of the annular compressed air jet chamber 55, and a swirl flow generating unit 59 is formed by the swirl flow generating blades 62.

  The rear end portion of the cylindrical inner tube 52 is connected to the fuel supply nozzle 60. The tip of the cylindrical inner tube 52 includes a fuel injection nozzle 52a, and the fuel injection nozzle 52a is adjacent to each of the plurality of swirl flow generation blades 62 and has a first fuel injection port 64 that opens to the conical high-speed flow generation unit 58. The second fuel injection port 65 that opens to the swirl flow collision portion 54 and the swirl flow generation member 66 that is disposed at an intermediate portion of the cylindrical inner tube 52 and generates the swirl flow Vs with respect to the fuel. When fuel is injected from the first fuel injection port 64 and the second fuel injection port 65 with respect to the swirling flow of the compressed air CA generated by the swirling flow generating blade 62, the compressed air is caused by collision with the swirling flow of the compressed air CA. CA and fuel are uniformly mixed to produce a premixed gas AFM. In the premixed gas, fuel and air are uniformly mixed, and a local high temperature portion is not generated inside the flame, so that the amount of NOx generated can be greatly suppressed.

  In the spiral combustion chamber 38, a turbulent flow generation baffle member 67 disposed at a predetermined distance from the swirling flow collision unit 54 is disposed, and the space between the turbulent flow generation baffle member 67 and the premixed gas generation unit 40 is disposed. A high temperature combustion section 540 is formed. The turbulent flow generation baffle member 67 has a central portion in which a combustion gas ejection opening 67a is formed. A part of the high-temperature and high-pressure combustion gas HTG collides with the wall surface of the turbulent flow generation baffle member 67, reverses to the swirl flow collision part 54 side, becomes a reversal flow RF, and comes into contact with the premixed gas ejected from the swirl flow collision part 54 Combustion is promoted by mixing.

Pressure sensor The high-pressure working medium WF supplied from the rotary pump 350A is supplied to the high-pressure working medium supply nozzle 552 via the check valve CV1. The supercritical fluid generator 550 extends in an arc shape in the circumferential direction along the spiral combustion chamber 38 in the combustor casing 36, and includes a saturated steam generator 550A, a superheated steam generator 550B, and a supercritical generator 550C. The supercritical fluid SCF is generated from the high-pressure working medium WF using a part of the thermal energy of the high-temperature and high-pressure combustion gas HTG while cooling the combustor casing 36, and then rotated through the control valve COV. It supplies to the 2nd inlet 126 of the expander 100 (refer FIG. 1A).

  In FIG. 1C, the supercritical fluid generator 550 is disposed along the combustion zone 38a of the spiral combustion chamber 38 on the radially inner side of the cylindrical combustor casing 36, and is welded to the cylindrical combustor casing 36 or other fixing means. The arc-shaped heat transfer member 570 fixedly supported by the The arc-shaped heat transfer member 570 is manufactured from a high-temperature heat-resistant material such as a Ni-based ultra-high temperature heat-resistant alloy or ceramic, and is located between the combustor casing 36 and the arc-shaped heat transfer member 570 at a position adjacent to the turbulent flow generation baffle member 67. A high-pressure working medium introduction portion 572 that is formed between the high-pressure working medium supply nozzle 552 and a high-pressure working medium introduction portion 572 that is ejected from the high-pressure working medium supply nozzle 552, and a plurality of openings 574a. A radial partition wall 574, a supercritical fluid generation chamber 576, and a plurality of heat transfer spheres 578 made of a commercially available stainless steel ball, tungsten ball, ceramic ball, or the like having a diameter of 6 mm to 25 mm filled in the supercritical fluid generation chamber 576; The supercritical fluid is generated at a position adjacent to the plurality of turbulent flow generation paths 578 a and the supercritical fluid outlet port 564. And a radial partition wall 598 formed in the edge end portion after 550.

  As shown in FIGS. 1B and 1D, the rotary compressor 350 includes a rotor housing 352 supported by the combustor casing 36 of the supercritical fluid generator / combustor 500 and a side plate 354. The rotor housing 352 is press-fitted into the drive shaft 132 and a pair of inlets 356 connected to the air supply system Ai, a pair of outlets 358 communicating with 126 intake ports, a rotor working chamber 360 in which the inlets 356 and outlets 358 open. A charge rotor 362 that is drivingly connected by other connecting means and is rotatably accommodated in the rotor working chamber 360 is provided. The charge rotor 362 can supply a small amount of lubricating oil to the outer peripheral end portion of the lobe 364 from the lubricating oil passage 362a extending radially outward from the main lubricating oil supply passage 132L, the lubricating oil supply port 362b, and the lubricating oil supply port 362b. A porous plug 362c. The main lubricating oil supply passage 132L is a lubricating oil pump described in Japanese Patent Application No. 2011-290720 “Rotary Fluid Machine” (Japanese Patent No. XXXXX) by the same inventor as the inventor of this patent application. Lubricating oil is supplied by such means.

  A lobe 364 that sucks intake air from the inlet 356 while rotating on the inner peripheral surface of the rotor working chamber 360 and compresses the intake air after suction and discharges it from the outlet 358 to the intake port 126, and a radially inner region of the lobe 364 A curved sliding recess 366 formed at the circumferential rear edge, a movable valve 368 movable relative to the charge rotor 362 adjacent to the inlet 356, and between the movable valve 368 and the curved sliding recess 366. And a charge chamber 370 formed. The movable valve 368 includes a valve element 376 that is housed in a valve expansion chamber 372 formed in the rotor housing 352 and rotates via a pivot shaft 374. A distal end portion of the valve element 376 includes a curved seal portion 376a and a communication opening 376b that slide while contacting the lobe 364 and the curved sliding recess 366. A pressure spring 380 presses the valve element 376 toward the charge rotor 362 in the spring housing portion 378 formed in the rotor housing 352. A starter motor or a motor motor is drivingly connected to the drive shaft 132 via power transmission means (not shown) such as a pulley and a timing belt. Accordingly, when the drive shaft 132 is driven to rotate clockwise in FIG. 1D when the engine is started, for example, air in the intake system is sucked into the charge chamber 370 from the inlet 356 in the rotary compressor 350 and the intake air in the charge chamber 370 is sucked. Is discharged from the outlet 358 to the intake port 126 under pressure. Thus, the rotary compressor 350 functions as a part of the engine starting means when the engine is started, and functions as a rotary compressor after the engine is started.

  Since the rotary pump 350A shown in FIG. 1A has the same structure as the rotary compressor 350, detailed description thereof is omitted.

  Next, the rotary expander 100 will be described with reference to FIGS. 1E to 7. 1E and 2, the rotary expander 100 includes a center housing 108 having end wall portions 102 and 104 that are spaced apart in the axial direction and an annular working chamber 106 that is formed between the end wall portions. A housing 110 is provided. The end wall portions 102 and 104 and the center housing 108 are fixedly supported at predetermined positions by bolts or other fixing means (not shown). Although the housing 110 is shown as having a thin case, cooling means such as cooling fins or coolant passages may be formed on the outer periphery or inside of the housing 110 as necessary.

  A cylinder liner (not shown) is disposed on the inner peripheral portion of the center housing 108, and annular grooves (not shown) are formed on the end wall portions 102 and 104 so as to face the inner side in the axial direction. A side liner (not shown) may be fitted into these annular grooves to form the annular working chamber 106 between the cylinder liner and the side liner. In this case, a cooling water passage formed by a plurality of annular grooves is formed on the outer periphery of the cylinder liner, and oblique grooves are formed in each of the cooling water passages, so that the cooling water passage from one end to the other end sequentially. The cooling water may be circulated in such a way as to communicate with the Similarly, in each of the side liners, a plurality of annular grooves having different diameters are formed so as to face the end face wall portions 102 and 104, cooling water passages formed by these annular grooves are formed, and these cooling water passages are formed. Each of the inclined grooves may be formed to communicate with the cooling water passage at one end to the cooling water passage at the other end in order to circulate the cooling water.

  As is clear from FIGS. 1E and 2, and FIGS. 4A and 4B, the center housing 108 includes first and second inlets 124 and 126 that open into the annular working chamber 106, and first and second outlets 128 and 130. A first expansion chamber 116 that communicates with the first inlet 124, an exhaust chamber 120 that communicates with the first outlet 128, and a discharge chamber 122 that communicates with the second outlet 130. High-temperature and high-pressure combustion gas HTG is introduced into the expansion chamber 116, and supercritical fluid SCF is introduced into the second expansion chamber 118 via the second inlet 124.

  As apparent from FIGS. 1E, 2 and 4A and 4B, the output shaft 132 extends in the axial direction of the annular working chamber 106 and is supported by the end wall portions 102 and 104. (Only shown) is rotatably supported. The roller bearing 136 is held at a predetermined position by a bearing pressing member 135 holding an oil seal 137 fixed to the end wall by bolts or other fixing means (not shown).

  As shown in FIG. 1E, the output shaft 132 is disposed at the center of the annular working chamber 106, and has a relatively large diameter clutch engaging portion 132a, 132b and a diameter smaller than that of the clutch engaging portion 132a, 132b. Piston rotation support parts 132c and 132d are provided. The rotary piston part 200 is rotatably supported by the piston rotation support parts 132c and 132d of the output shaft 132 via needle bearings 142 and 144. The rotary piston part 200 allows the first and second annular working chambers 106 to be formed. It is divided into two expansion chambers 116 and 118, an exhaust chamber 120, and an exhaust chamber 122. The needle bearings 142 and 144 roll around the piston rotation support portions 132c and 132d via the retainers 142R and 144R, respectively.

  As is clear from FIGS. 1E and 2, the rotary piston unit 200 includes first and second rotary pistons having first and second rotor pistons 150 p and 152 p each having a pair of pistons arranged symmetrically in the radial direction. Piston bodies 150 and 152 are provided. The first and second rotary piston main bodies 150 and 152 include first and second boss portions 154 and 156 that support the first and second rotor pistons 150p and 152p, respectively, and first and second boss portions 154 and 156, respectively. The first and second sleeve portions 158 and 160 each extend outward in the axial direction.

  First and second sleeve portion fastening clutches 170 and 172 are disposed between the end surface wall portions 102 and 104 of the housing 110 and the first and second rotary piston main bodies 150 and 152, respectively. As shown in FIGS. 1E and 3A, the first sleeve portion fastening clutch 170 includes a sleeve portion fastening outer race portion 170 a integral with the end face wall portion 102, and a first sleeve portion 158 of the first rotary piston main body 150. And an inner race portion 170b for fastening the sleeve portion. The sleeve portion fastening outer race portion 170a has a hexagonal cam surface 170c. Between the sleeve portion fastening outer race portion 170a and the sleeve portion fastening inner race portion 170b, a plurality of sleeve portion fastening wedge-shaped cam spaces 174 are formed at intervals in the circumferential direction. The space portion 174 houses sleeve portion fastening cam rollers 176 as a plurality of cam elements.

  An annular retainer 178 is accommodated between the sleeve portion fastening outer race portion 170a and the sleeve portion fastening inner race portion 170b. As shown in FIGS. 1, 3A, and 5, the annular retainer 178 includes a retainer body 178b having a plurality of openings 178a formed at intervals in the circumferential direction to accommodate the sleeve portion fastening cam roller 176. . The diameter of the inner peripheral portion 178c of the retainer main body 178b is set slightly larger than the outer periphery of the sleeve portion 158 to form a later-described lubricating oil introduction space. The first and second sleeve portion fastening clutches 170 and 172 include anti-backlash mechanisms 180 and 182, respectively.

  As shown in FIG. 3A, the anti-backlash mechanism 180 includes an anti-backlash suppression seal storage portion 180 a formed at a position facing the radial direction in the central portion of the end face wall portion 102, and a radial direction from the outer periphery of the retainer 178. An operating protrusion 178d that extends outwardly and is accommodated in the anti-backlash suppression seal accommodating portion 180a is provided. The S-shaped spring member 184 (see FIG. 6) urges the operating protrusion 178d to the anti-backlash position in the anti-backlash suppression seal storage portion 182a, thereby minimizing the backlash (play) of the cam roller 176 for fastening the sleeve portion. Turn into. Therefore, when the sleeve portion 158 of the piston 150p is counterclockwise in FIG. 3A, the sleeve portion 158 is quickly locked to the end surface wall portion 102 via the inner race portion 170a, and the sleeve portion fastening cam roller 176 The machine conversion efficiency is improved due to less play.

  On the other hand, as shown in FIG. 3B, the second sleeve portion fastening clutch 172 is integrated with the sleeve portion fastening outer race portion 172 a integral with the end face wall portion 104 and the sleeve portion 160 of the second rotary piston main body 152. And a sleeve portion fastening interlace portion 172b. The sleeve portion fastening outer race portion 172a has a hexagonal cam surface 172c. A plurality of sleeve-like fastening wedge-shaped cam spaces 174A are formed between the sleeve-part fastening outer race 172a and the interlaced part 172b in the circumferential direction. A sleeve portion fastening cam roller 176A as a plurality of cam elements is housed.

  Further, an annular retainer 178A is housed between the sleeve portion fastening outer race portion 172a and the sleeve portion fastening interlace portion 172b. The annular retainer 178A includes a retainer body 178b having a plurality of openings 178a formed at intervals in the circumferential direction to accommodate the sleeve portion fastening cam roller 176A, and the diameter of the inner periphery 178c of the retainer body 178b is the sleeve It is set slightly larger than the outer periphery of the portion 158. The second sleeve portion fastening clutch 172 includes an anti-backlash mechanism 182.

  As shown in FIG. 3B, the anti-backlash mechanism 182 includes an anti-backlash suppression seal storage portion 182a formed at a position facing the radial direction in the end face wall portion 104, and a radially outer side from the outer periphery of the retainer 178A. An operation protrusion 178d that extends so as to protrude and is housed in the anti-backlash suppression seal housing 182a is provided. The S-shaped spring member 184 (see FIG. 6) urges the operating protrusion 178d to the anti-backlash position in the anti-backlash suppressing seal storage portion 182a, thereby minimizing the backlash (play) of the cam roller 176A for fastening the sleeve portion. Turn into. Therefore, when the sleeve portion 160 of the piston 152p is counterclockwise in FIG. 3B, the sleeve portion 160 is quickly locked to the end face wall portion 104. Since the retainer 178A has the same structure as the retainer 178, the illustration is omitted.

  In FIG. 1E, FIG. 2 and FIGS. 4A and 4B, the first and second boss portions are respectively provided between the clutch engaging portions 132a and 132b of the output shaft 132 and the first and second rotary piston main bodies 150 and 152. Fastening clutches 186 and 188 are arranged. The first and second boss portion fastening clutches 186 and 188 include boss portion fastening outer race portions 186a and 188a that are integral with the first and second boss portions 154 and 156, respectively, and a clutch engaging portion 132a of the output shaft 132. , 132b and boss portion fastening inner race portions 186b, 188b, respectively.

  As shown in FIG. 4A, the outer race portion 186a for fastening the boss portion has a hexagonal cam surface 186c. A wedge-shaped cam space portion 186d for fastening the boss portion is formed between the outer race portion 186a for fastening the boss portion and the clutch engaging portion 132b of the output shaft 132 at a circumferential interval, and a wedge-shaped cam space portion for fastening the boss portion. A boss portion fastening cam roller 186e as a plurality of cam elements is housed in 186d. An annular retainer 186f is housed between the boss portion 154 and the clutch engaging portion 132a of the output shaft 132, and a plurality of openings 186g are formed at positions separated in the circumferential direction of the annular retainer 186f. These openings 186g The boss portion fastening cam rollers 186e are respectively stored in the plurality of boss portion fastening wedge-shaped cam spaces 186d.

  In FIG. 1E and FIG. 4B, the second boss portion fastening clutch 188 includes a boss portion fastening outer race portion 188a integral with the boss portion 156 of the second rotary piston main body 152, and a clutch engaging portion 132b of the output shaft 132. And an integrated boss portion fastening inner race portion 188b. A plurality of wedge-shaped cam space portions 188d for fastening the boss portion are formed between the boss portion 156 and the clutch engaging portion 132b of the output shaft 132 at intervals in the circumferential direction, and the wedge-shaped cam space portion 188d for fastening the boss portion is formed. Accommodates a boss portion fastening cam roller 188e as a plurality of cam elements. An annular retainer 188f is housed between the boss portion 156 and the clutch engaging portion 132b of the output shaft 132, and a plurality of openings 188g are formed at positions separated in the circumferential direction of the annular retainer 188f, and these openings 188g. The boss portion fastening cam rollers 188e are respectively stored in the plurality of boss portion fastening wedge cam space portions 188d.

  As shown in FIGS. 4A and 4B, the boss portion fastening one-way clutches 186 and 188 include anti-backlash mechanisms 190 and 192, respectively. In FIG. 4A, the anti-backlash mechanism 190 is provided on the outer periphery of the anti-backlash suppressing seal storage portion 190a formed so as to face the radial direction in the annular inner wall portion 154a of the boss portion 154 and the annular retainer 186f. And an actuating member 186h accommodated in the anti-backlash suppression seal accommodating portion 190a. The annular retainer 186f has a similar structure to the retainer 178 of FIG. The S-shaped spring member 194 biases the actuating member 186h to the anti-backlash position in the anti-backlash suppression seal storage portion 190a. The S-shaped spring member 194 has a similar structure to that of FIG. In FIG. 4B, the anti-backlash mechanism 192 is provided on the outer periphery of the anti-backlash suppression seal storage portion 192a formed so as to face the radial direction in the annular inner wall portion 156a of the boss portion 156, and the retainer 188f. And an actuating member 188h accommodated in the backlash suppressing seal accommodating portion 192a. The retainer 188f has a similar structure to the retainer 178 of FIG. The S-shaped spring member 194 biases the actuating member 188h to the anti-backlash position in the anti-backlash suppression seal storage 192a. The S-shaped spring member 194 has a similar structure to that of FIG.

  As shown in FIG. 1E, FIG. 2 and FIG. 7, the first and second rotary piston main bodies 150, 152 are sealed with a C-shaped cross section formed in the axial direction of the first and second rotor pistons 150p, 152p. Part 210, a split seal member 220 housed in the seal housing part 210 and movable relative to the inner peripheral wall 106 a and the side wall 106 b of the annular working chamber 106 and the first and second boss parts 154 and 156, and a seal A plurality of spring members 230 that are disposed between the storage portion 210 and the divided seal member 220 and press the divided seal member 220 against the inner peripheral wall 106a, the side wall 106b, and the outer periphery of the first and second boss portions. With.

  As is clear from FIG. 7, the split seal member 220 includes first and second corner seals 240 and 242 having L-shaped cross sections, and first and second side seals 250 and 252. The first and second corner seals 240 and 242 have spring housing seal housing portions 240a, 240b, 242a, and 242b that engage with the tip of the spring member 230 made of a leaf spring. A spring member 230 is accommodated in the spring accommodating seal accommodating portions 240a and 242a, and the first and second corner seals 240 and 242 are always provided via the inclined surface 244 by the pressing force acting on the radially outer side of the spring member 230. While being held in contact, they engage with the inner peripheral wall 106a and the side wall 106b of the annular working chamber 106 so as to be in close contact with each other. Similarly, the first and second side seals 250 and 252 have spring storage seal storage portions 250a and 252a radially aligned with the spring storage seal storage portions 240b and 242b of the first and second corner seals 240 and 242, respectively. . The first and second side seals 250 and 252 are inclined by a pressing force acting on the radially outer side of the spring member 230 housed in the spring housing seal housing portions 240b and 250a and the spring housing seal housing portions 242b and 252a, respectively. 256, the contact state is always maintained. At this time, the first side seal 250 slides on the side wall 106 b of the annular working chamber 106. The radial wall portion of the second side seal 252 slides while engaging with the side wall 106b of the annular working chamber 106 and the second boss portion 156 in close contact with each other. The axial seal wall portion 252b of the second side seal 252 slides so as to be in close contact with the outer periphery of the boss portion 156. For this reason, the leakage of the working medium between the first and second rotary piston main bodies 150 and 152 and the housing 110 is minimized, and the efficiency of the engine is improved correspondingly, and a high power output is obtained.

  In FIG. 1E and FIG. 7, a main lubricating oil supply path 132L is formed along the central axis of the output shaft 132, and a plurality of radial lubricating oil supply paths 132L1, 132L2, and 132L3 extend in the radial direction from the main lubricating oil supply path 132L. The lubricant is supplied to the main lubricant supply passage 132L from the lubricant storage tank 260 via the lubricant pump 162 and the lubricant supply line 264. Lubricating oil is supplied to the first and second boss engaging clutches 186 and 188, the first and second needle bearings 142 and 144, and the first and second sleeve engaging clutches 170 and 172 from the radial lubricating oil supply passage. The As apparent from FIGS. 1C and 7, the central radial lubricating oil supply passage 132 </ b> L <b> 1 further communicates with the seal lubricating passages 300, 302, 304, and 306 formed inside the rotary piston main body 150. The seal lubrication passages 302, 304, and 306 extend to the slit-shaped groove portion 210 and supply lubricating oil to the divided seal member 220 through the slit-shaped groove portion 210. Porous plugs 308 and 310 are attached to both end portions of the seal lubrication passages 302 and 306, respectively, and a porous plug 312 is attached to the tip end portion of the seal lubrication passage 304, and the slit-shaped groove portion 210 passes through these porous plugs. Therefore, the lubricating oil is gradually supplied to the split seal member 220, and the seal member 220, the inner wall and the side wall of the housing, and the outer periphery of the boss portion 156 are smoothly lubricated. Lubricating oil after lubrication is recovered in the annular lubricating oil recovery chamber 322 formed in the inner diameter region of the end wall by the high-temperature and high-pressure combustion gas and the supercritical fluid introduced into the annular working chamber 106 during the operation of the combustion engine. The recovered high-temperature lubricating oil is returned to a lubricating oil sump (not shown) via a lubricating oil return line (not shown).

  Next, based on FIG. 1A, the effect | action of the mechanical apparatus 10 by a present Example is demonstrated. In FIG. 1A, when a key switch (not shown) is closed when the hybrid rotary combustion engine 50 is started, a starter motor (not shown) is activated and the output shaft 132 is cranked so that the rotary compressor 350 and the rotary pump 350A are turned on. to start. At this time, the rotary compressor 350 draws intake air from the intake system Ai and pressurizes it to generate compressed air CA. The compressed air CA is supplied to the supercritical fluid generator / combustor 500. In synchronization with this, a command signal is output from the controller 20, the fuel control valve FV is opened, and the fuel F is supplied to the supercritical fluid generator / combustor 500. In the supercritical fluid generator / combustor 500, the premixed mixture of the compressed air CA and the fuel F is ignited and burned by the ignition means 42 to generate a high-temperature high-pressure combustion gas HTG of 1500 ° C. to 1700 ° C., and spiral combustion The chamber 38 advances from the upstream side to the downstream side, is discharged from the discharge port 44, and is introduced into the first inlet 124 of the rotary expander 100 via the internal gas flow path of the spacer 30. On the other hand, in the process in which the high-temperature high-pressure combustion gas HTG at 1500 ° C. to 1700 ° C. passes through the spiral trajectory through the spiral combustion chamber 38, a part of the thermal energy of the high-temperature high-pressure combustion gas HTG is a plurality of The heat transfer sphere 578 is transferred to the heat transfer sphere 578 and becomes a high temperature state. At this time, the high pressure working medium is injected from the high pressure working medium supply nozzle 552 to the high pressure working medium introduction unit 572 from the rotary pump 350A. As a result, when the high-pressure working medium is, for example, water, the water contacts the heat transfer sphere 578 and becomes saturated steam in the saturated steam western part 550A, and the saturated steam becomes superheated steam in the superheated steam generation part 550B. Supercritical water SCF is generated in the supercritical generator 550C. When the temperature and pressure of the supercritical water SCF reach predetermined values, a command signal is output from the controller 20 in response to the detection signals S1 and S2, the open / close control valve COV is opened, and the supercritical water SCF is subjected to rotary expansion. Supplied to the second inlet 126 of the machine 100. Thus, in the first rotary machine part A (see FIGS. 4A and 4B) of the rotary expander 100, the high-temperature and high-pressure combustion gas HTG expands to generate primary power on the output shaft 132, and in the second rotary machine part B, The critical water SCF expands and secondary power is generated on the output shaft 132. The exhaust of the first rotary machine part A is discharged from the first outlet 128 to standby, and the low-temperature and low-pressure expansion steam LTF of the second rotary machine part B is cooled and liquefied by the cooler 12 to become the working water LWF. Is sucked and pressurized by the rotary pump 350A and circulated in the subsequent cycles.

  The operation of the rotary combustion engine 100 is the same as that of the inventor of the present invention. Japanese Patent Application No. 2011-XXXXXX "rotary fluid machine and rotary engine using the same" filed on August 20, 2012 by the same inventor. ”(Japanese Patent No. XXXXX), the detailed description is omitted.

  As mentioned above, although each Example of this invention was described based on drawing, these show only one embodiment to the last, and this invention is the aspect which added the various change and improvement based on the knowledge of those skilled in the art. Can be implemented.

  For example, in the vehicle in the first embodiment shown in FIG. 1A, the first and second rotary expanders are shown in a tandem connection via a common output shaft. They may be arranged in parallel and connected to the output device via respective clutches. Similarly, in the vehicle according to the second embodiment shown in FIG. 8, a structure in which the rotary combustion engine and the rotary expander are connected in tandem via a common output shaft is shown. A rotary expander is arranged in parallel and connected to an output device via a clutch, and each drive state is switched by an electronic control unit (ECU) according to the driving parameters of the vehicle, or during acceleration, etc. You may control to drive simultaneously at the time of a heavy load.

  10. . . Mechanical device; 12. . . Cooler; 20. . . Controller; 22. . . Input device; . . Rotary expander; 106. . . 110. annular working chamber; . . Housing; 132. . . Output shaft; 132a, 132b. . . Clutch engagement portion; 142, 144. . . Needle bearings; 150, 152. . . First and second rotary piston bodies; 170,172. . . Clutches for fastening the first and second sleeve portions; 186,188. . . Clutches for fastening the first and second boss parts; 190,192. . . Anti-backlash mechanism; 264. . . Lubricating oil supply line; 324. . . Lubricating oil return line; 350. . . Rotary compressor; 350A. . . Rotary pump; 500. . . Supercritical fluid generator and combustor

Claims (5)

A rotary pump that pressurizes the working medium to generate a high-pressure working medium;
A rotary compressor that compresses intake air to generate compressed air;
The high-pressure high-pressure combustion gas is generated by burning an air-fuel mixture of the compressed air and fuel, and is driven by a part of thermal energy of the high-temperature high-pressure combustion gas. A supercritical fluid generator / combustor for generating a supercritical fluid from a working medium;
A rotary combustion engine comprising a rotary expander that expands the high-temperature and high-pressure combustion gas and the supercritical fluid to generate power ,
The rotary expander includes an engine housing having first and second end wall portions each having a first and second sleeve portion fastening clutch;
An annular working chamber formed in the engine housing;
An output shaft having a clutch engaging portion disposed in an axially intermediate portion of the annular working chamber;
The first and second boss portions are rotatably accommodated in the annular working chamber, and extend axially outward from the first and second boss portions. The first and second sleeve portion fastening clutches First and second rotary pistons having first and second sleeve portions that are switched between a locked state and an unlocked state with respect to the first and end face wall portions between the first and second rotational directions;
The first and second boss portions are respectively disposed between the clutch engagement portion and the first and second boss portions with respect to the clutch engagement portion between the second rotation direction and the first rotation direction. A first and second boss portion fastening clutch that switches between a locked state and an unlocked state,
A rotary combustion engine comprising: The supercritical fluid generator / combustor includes a combustor casing disposed concentrically with the rotary pump and the rotary compressor, a combustion chamber formed in the combustor casing, and the combustion chamber. And a supercritical fluid generator configured to receive the thermal energy of the high-temperature and high-pressure combustion gas and generate the supercritical fluid by heating the high-pressure working medium. The rotary combustion engine according to claim 1.   The rotary compressor includes a rotor working chamber having an inlet for introducing the intake air and an outlet communicating with the combustor, and a charge rotor that is rotatably housed in the rotor working chamber and is drivingly connected to the output shaft. And at least one lobe that sucks the intake air while rotating on the inner peripheral surface of the rotor working chamber and discharges the intake air after suction to the combustor while pressurizing, and the radial direction of the lobe A curved sliding recess formed in a circumferential rear edge of the lobe in the inner region, a movable valve movable relative to the charge rotor adjacent to the inlet, the movable valve and the curved sliding recess; And a charge chamber that is formed between the discharge chamber and discharges the intake air to the combustor under pressure. Rotary combustion engine. The rotary expander includes a first rotating machine unit that expands the high-temperature and high-pressure combustion gas to generate primary power, and a second rotating machine unit that expands the supercritical fluid to generate secondary power, The rotary combustion engine according to any one of claims 1 to 3, further comprising a cooler that cools the low-temperature and low-pressure expansion gas discharged from the second rotary machine unit and supplies the cooled low-pressure expansion gas to the rotary pump. A mechanical device including the rotary combustion engine according to any one of claims 1 to 4 .

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