JP5315490B1 - Rotary heat engine and rotary heat engine driven generator - Google Patents

Abstract

Provided are a rotary heat engine and a rotary heat engine-driven power generator having a simple structure, a small number of parts, and high reliability without using a complicated crank mechanism.
High temperature combustion gas is generated in a combustor 13 and first and second sleeves 158 and 160 are disposed between first and second piston rotor bodies 150 and 152, respectively. By the sleeve portion fastening clutches 170 and 172, the first and second sleeve portions are respectively brought into a locked state and an unlocked state between the first and second rotational directions in each step of suction, compression, expansion, and exhaust. By switching, the first and second boss portion fastening clutches cause the first and second boss portions 154 and 156 to be locked and unlocked with respect to the clutch engaging portion between the second rotation direction and the first rotation direction. By switching to the locked state, the structure of the rotary heat engine and the rotary heat engine driving power generator is simplified and the size and performance are improved.
[Selection] Figure 3

Description

  The present invention relates to a heat engine and a heat engine-driven power generator, and more particularly, to a rotary heat engine that can be operated with fossil fuels such as LNG, LPG, and shale oil derived from shale gas, and a power generator using the same.

  In recent years, global warming and climate change have become serious environmental problems due to a dramatic increase in demand for electric power and an increase in greenhouse gas emissions from vehicles such as automobiles, ships and airplanes. It has become. As an effective countermeasure, a high-efficiency rotary heat engine is expected to appear, and a high-efficiency rotary piston engine has been proposed in place of the conventional reciprocating engine.

  Patent Documents 1 to 3 disclose a crank / planet that is disposed between a first rotor and a first rotor, in which a first and second rotor having a pair of radially opposed pistons are rotatably housed in an engine housing. A rotary piston engine has been proposed in which the relative movement of the rotor piston is controlled by a gear mechanism.

  In Patent Document 4, a plurality of pairs of motor vanes opposed in the radial direction are supported by concentric inner and outer sleeves, and relative movement of the disk-type rotor connected to each of axial end portions of the motor vane is performed. A concentric rotor engine designed to be controlled has been proposed.

  Patent Documents 5 to 8 further describe a rotary piston engine in which a rotationally moving relationship of pistons is controlled by various piston timing control mechanisms in a structure in which a radially contrasting piston is rotatably housed in an engine housing. Has been proposed.

  In Patent Document 9, in an engine housing, a plurality of pairs of rotor pistons opposed in the radial direction are supported on an output shaft, an output gear is provided on the output shaft, and a plurality of planetary gears are engaged with the output gear. There has been proposed a rotary engine in which an eccentric protrusion is provided on each planetary gear and the relative movement of the rotor piston is controlled by sliding the eccentric protrusion in an arm groove of an arm member.

  Patent Document 10 proposes an integrated structure of an engine / generator in which a generator is connected concentrically to a rotary engine.

U.S. Pat. No. 3,829,257 US Pat. No. 5,147,191 US Pat. No. 5,527,165 Published Patent Publication No. H05-5401 US Pat. No. 6,305,345 US Pat. No. 6,526,307 US Pat. No. 6,886,527 US Pat. No. 7,560,869 Published Patent Publication No. 2000-303843 Published Patent Publication No. 2005-214105

  By the way, in the rotary engine disclosed in Patent Documents 1 to 3, the crank / planetary gear is arranged on the outer side in the axial direction of the main components of the rotary piston part for the purpose of controlling the lock / unlock state of the rotary piston part. The mechanism is adopted. These crank / planetary gear mechanisms are composed of a crank, a plurality of connecting rods, a large number of planetary gears, a planetary gear support disc, and the like. Therefore, not only the structure of the crank / planetary gear mechanism is complicated, but the number of parts is increased, and the axial dimension of the crank / planetary gear mechanism is extremely large. Therefore, the overall structure and total weight of the engine are inevitably large, and the production cost is high. In addition, since many gears and crank mechanisms used in the piston drive control mechanism have large backlash, even if high-temperature combustion gas acts on the rotary piston part, the pressure energy directly affects the mechanical energy. Was not converted, and after a certain amount of backlash, torque was generated on the output shaft. As a result, mechanical loss has increased and engine efficiency has deteriorated. In addition, in the crank / planetary gear mechanism, the vibration and noise of the engine increase as the crank moves at a higher speed. Due to such a special structure, it has been difficult to reduce engine vibration and noise. Furthermore, since these rotary engines are composed of a large number of sliding parts and moving parts, the maintenance and maintenance costs also increase, which has caused an increase in running costs.

  In the coaxial rotor engine disclosed in Patent Document 4, a plurality of motor vanes are respectively supported by disk-type rotors, and each of the disk-type rotors is provided with an inner sleeve and an outer sleeve, and a high pressure is provided inside the inner sleeve. A structure in which a fluid passage is formed is employed. In this structure, since the sleeve member, which is a component for generating torque, cannot be directly connected to the output shaft, each sleeve is connected to form an annular chamber on the outer side in the axial direction of the rotor plates on both sides. Each of the disk-type end plates is connected to each other, and the center portion of these disk-type end plates is connected to the end portion of the output shaft to transmit torque. Therefore, in the coaxial rotor engine, the effective operation area for extracting the output torque is extremely small with respect to the entire structure, and as a result, the structure of the coaxial rotor engine is increased. Moreover, these structures are extremely complicated, and not only the number of parts of the engine is inevitably increased, but also the axial and radial dimensions of the engine are remarkably increased. Therefore, it has been difficult to manufacture a rotary piston engine having a compact and lightweight structure at low cost.

  In the rotary engine disclosed in Patent Document 5, a crank timing mechanism including three cranks, three connecting rods, and a coupling unit connected to the connecting rods is employed. This kind of crank timing mechanism not only has a complicated structure, but also increases the number of parts including bearings and other parts arranged in the movable part, increases the overall structure and total weight of the engine, and increases the production cost. It was. Furthermore, since the vibration of the connecting rod increases during high-speed rotation of the rotary engine, it is difficult to achieve a quiet operation.

  The rotary engine disclosed in Patent Document 6 employs a structure in which a crank / planetary gear mechanism for controlling the drive timing of the piston is arranged in a wide range of space outside the axial direction of the piston assembly. In this rotary engine, the crank / planetary gear mechanism includes a plurality of sun gears, a plurality of planetary gears, a plurality of carriers, a plurality of cranks, a plurality of connecting rods, and the like. Therefore, not only the structure of the crank / planetary gear mechanism itself is complicated, but also the number of parts is increased, and the axial dimension of the crank / planetary gear mechanism is significantly larger than the structure of the rotary piston body. Therefore, the overall structure and total weight of the engine are increased, and the production cost is high. Furthermore, there is a large backlash between the large number of gears employed in the crank / planetary gear mechanism, the plurality of cranks, and the plurality of connecting rods. Therefore, in the explosion process, a time lag occurs when the piston moves, and mechanical loss is inevitably increased, resulting in poor engine efficiency. In addition, when the engine rotates at high speed, the vibrations of the crank and connecting rod increase, and the engine generates significant vibrations and noise.

  The rotary engine disclosed in Patent Document 7 employs a structure in which a planetary gear timing mechanism for driving timing control of a piston is provided in a space in a wide range outside the axial direction of the piston assembly. In this type of rotary heat engine, a drive gear having a large diameter is provided on the output shaft, a second rotating shaft is provided in parallel with the output shaft to support the driven gear, and the output is achieved by engaging the drive gear and the driven gear. The structure which drives a planetary gear timing mechanism using a part of torque is adopted. A large-diameter ring gear is arranged around the second rotation shaft, and is composed of a sun gear, a plurality of planet gears, a carrier and a crank, and a plurality of elliptical gears. The structure of the planetary gear timing mechanism itself is complicated. It was. For this reason, the number of parts has also increased significantly, and the axial and lateral dimensions of the rotary heat engine have become remarkably large. Therefore, the overall structure and total weight of the engine are increased, and the production cost is high.

  In the rotary engine disclosed in Patent Document 8, each piston is supported by first and second half ring-shaped case members provided with a plurality of spoke members extending in the radial direction, and the first and second half ring shapes are provided. A timing mechanism is employed in which planetary gear sets are arranged on the outer sides in the axial direction of the case members, eccentric pins are fixed to the planetary gears of the planetary gear sets, and the eccentric pins are moved in the spoke members. . In this timing mechanism, the axial dimension of the engine is increased, and the overall dimensions and weight of the rotary engine are remarkably increased, resulting in an increase in production cost. Further, the engine efficiency has been reduced due to the backlash of the planetary gear set structure and the friction between the spoke and the eccentric pin. Moreover, the operation mechanism of the intake and exhaust valves for intake and exhaust of the engine is complicated, and it is difficult to improve the engine performance.

  In the rotary engine disclosed in Patent Document 9, for the purpose of controlling the operation timing of a pair of rotary pistons, an arm is connected to the side surface of the rotary piston, and a central gear is attached to an output shaft. A crank / planetary gear mechanism is arranged in which a plurality of planetary gears are engaged with each other so that the crankpins of the planetary gears are slidably fitted into the arm grooves of the arms. Since this crank / planetary gear mechanism is composed of a plurality of crankpins, a plurality of planetary gears and a central gear, not only the structure of the crank / planetary gear mechanism is complicated, but also the increase in the number of parts increases the overall engine. The structure and total weight were large and the production cost was high. Furthermore, since this mechanism inevitably has a large backlash, the mechanical loss of the engine increases and the engine efficiency deteriorates. In addition, in the crank / planetary gear mechanism, the vibration and noise of the engine increase particularly as the engine speed increases. In addition, this type of rotary engine requires a large number of sliding parts and movable parts to control the operation timing of the rotary piston, so that maintenance / maintenance factors cannot be reduced, leading to an increase in running costs. It was.

  In the rotary engine disclosed in Patent Document 10, a plurality of pivot blades are arranged on a rotor, and the actuator is moved eccentrically by a rotor bearing that rotates eccentrically with respect to an output shaft, thereby causing the plurality of pivot blades to have a diameter. The structure is such that each step of intake, compression, combustion, and exhaust is completed by swinging in the direction. In this structure, a plurality of double-acting bearings each having a crank pin are supported by the actuator so as to be capable of rotating in the circumferential direction, corresponding to the plurality of pivot blades, and the rotation of the actuator via the crank pins is supported. Motion is transmitted to the plurality of pivot wings. For this reason, the engine structure is complicated and the number of parts increases, which causes an increase in engine cost. In this structure, the vibration of the engine is large, and the sliding friction is large between the actuator and the actuator and between the actuator and the double-acting bearing, and it is difficult to supply the lubricating oil to these sliding surfaces. For this reason, it has not been possible to improve the reliability and longevity of the engine. Moreover, when this type of rotary engine is used as a power source for an automobile or the like, in order to recover the regenerative energy generated when the vehicle is decelerated, both the motor and the generator must be combined with the rotary engine. In addition, the overall structure of the rotary engine has increased, and the manufacturing cost has increased.

  The present invention has been made in view of such conventional problems, and has a simple structure with a small number of parts, high reliability and durability, low vibration and low noise, and low production cost. It is an object of the present invention to provide a rotary heat engine and a rotary heat engine drive power generator with high pressure ratio and high efficiency.

In order to achieve the above object, according to the first aspect of the present invention, a rotary heat engine includes an engine housing having end face wall portions spaced apart in the axial direction, combustion air, and fuel. A combustion part for generating a high-temperature combustion gas, an expansion chamber formed between the end face wall part in the engine housing and expanding the high-temperature combustion gas to generate the power, and discharging the expansion gas An annular working chamber having an exhaust chamber, an output shaft having a clutch engagement portion extending in an axial direction of the annular working chamber and disposed at an intermediate portion of the annular working chamber, and rotating to the output shaft First and second piston rotor bodies that are movably supported and rotatably accommodated in the annular working chamber and output torque in an operation cycle, the first and second piston rotor bodies are radially aligned with the clutch engaging portion. And A second boss portion; first and second rotor pistons extending radially outward of the first and second boss portions and rotatably accommodated in the annular working chamber; and the first and second bosses The first and second piston rotor bodies having first and second sleeve portions respectively extending in the axial direction from the portion, and disposed between the end face wall portion and the first and second sleeve portions, respectively. In each of the steps, the first and second sleeve portions are fastened so that the first and second sleeve portions are switched between a locked state and an unlocked state with respect to the end wall portion between the first and second rotational directions. And the clutch engaging portion and the first and second boss portions, respectively, and in the operation cycle, the first and second boss portions are arranged in the second rotational direction and the second rotation direction, respectively. 1st First and second boss portion fastening clutches that switch between a locked state and an unlocked state with respect to the clutch engagement portion between the first and second sleeve portion fastening clutches. A sleeve portion fastening wedge-shaped cam space portion and a sleeve portion fastening cam element for locking and unlocking the first and second sleeve portions with respect to the end face wall portion, respectively, A boss portion fastening cam space portion and a boss portion fastening cam element for drivingly connecting the first and second boss portions to the clutch engaging portion of the output shaft in the same rotational direction ,
A high-temperature and high-pressure water generator that generates high-temperature and high-pressure water by cooling the combustor; a high-temperature superheated steam generator that generates high-temperature superheated steam from the high-temperature and high-pressure water while cooling the combustor; A high-temperature high-pressure water injection nozzle for injecting the high-temperature high-pressure water into the combustion chamber and bringing the high-temperature steam into contact with the high-temperature combustion gas; and a high-temperature superheated steam supply line for supplying the high-temperature superheated steam to the combustor. with the gist of the Rukoto.

  According to the second aspect of the present invention, in addition to the structure of the first aspect, the first and second sleeve portion fastening clutches are integrated with the end face wall portion, respectively. Part fastening outer race part, first and second sleeve part fastening inner race parts integral with the first and second sleeve parts, respectively, the first and second sleeve part fastening outer race parts, and A wedge-shaped cam space portion for fastening the first and second sleeve portions formed between the first and second sleeve portion fastening inner race portions and constituting the sleeve portion fastening cam space portion; First and second boss portions, each of which is disposed in a wedge-shaped cam space portion for fastening a second sleeve portion, and includes first and second cam elements for fastening the sleeve portion that constitute the sleeve portion fastening cam element. First and second boss part fastening, each of the linking clutches being integral with the first and second boss parts, respectively, and first and second boss part fastening outer race parts, and the clutch engaging part, respectively. The boss portion fastening cam space is provided between the inner race portion, the outer lace portion for fastening the first and second boss portions, and the inner race portion for fastening the first and second boss portions. The first and second boss portion fastening wedge-shaped cam space portions constituting the portion and the first and second boss portion fastening wedge-shaped cam space portions are respectively arranged to constitute the boss portion fastening cam element. The gist is to include the first and second boss portion fastening cam elements.

  According to the invention described in claim 3, in addition to the structure of claim 2, the first and second sleeve portion fastening clutches and the first and second boss portion fastening clutches are respectively The sleeve portion fastening cam element and the boss portion fastening cam element are housed in the first and second sleeve portion fastening wedge cam space portions and the first and second boss portion fastening wedge cam space portions. The gist of the present invention is to provide an anti-backlash mechanism comprising a retainer for supporting each and a spring means for urging the retainer to an anti-backlash position.

According to the fourth aspect of the present invention, in addition to the configuration according to any one of the first to third aspects, the main lubricating oil supply path formed along the central axis of the output shaft, and the main lubricating A plurality of lubricating oil guide passages extending in a radial direction from an oil supply passage and guiding lubricating oil to the first and second sleeve portion fastening clutches and the first and second boss portion fastening clutches; A lubricating oil pump for supplying the lubricating oil to a main lubricating oil supply passage, wherein the sleeve portion fastening wedge cam space portion and the boss portion fastening wedge cam space portion communicate with the lubricating oil guide passage, respectively. It is a summary.

According to the invention described in claim 5, in addition to the configuration according to any one of claims 1 to 4, the combustion part is a combustion part casing and a combustion chamber formed in the combustion part casing. A premixed gas generating unit that generates a premixed gas of the fuel and the combustion air in the combustion chamber, an ignition unit that ignites the premixed gas to generate the high temperature combustion gas, and the high temperature combustion And a combustion gas discharge port for supplying gas to the expansion chamber.

According to the invention described in claim 6 , in addition to the structure described in any one of claims 1 to 5 , the annular working chamber is formed adjacent to the exhaust chamber and sucks ambient air. An intake chamber, and a compression chamber that generates compressed air from the intake air and supplies the compressed air as the combustion air to the combustor, the intake chamber and the compression chamber, the expansion chamber, and the exhaust chamber, The gist is to operate as a compressor / expander having a compressor function for compressing the intake air and an expander function for expanding the high-temperature combustion gas in cooperation with the first and second piston rotor bodies.

According to the seventh aspect of the present invention, in addition to the configuration of the sixth aspect , the rotary heat engine further sprays water on the intake air to generate a mixed fluid of the intake air and the pressurized water. Intake air cooling / exhaust gas that is introduced into the intake chamber and the compression chamber and collects exhaust heat energy of high-temperature components including the engine housing, the end wall portion, and the first and second piston rotor bodies in the intake and compression processes. The gist is to further include a thermal energy recovery spray device.

According to the invention described in claim 8 , the rotary heat engine drive power generator includes a combustion section that generates high-temperature combustion gas by burning combustion air and fuel, and compresses intake air to compress the compressed air. A compressor / expander having a function as a compressor that generates as combustion air and a function as an expander that expands the high-temperature combustion gas to obtain power, and a generator driven by the power, the compressor / expander Is formed between the end face wall portions in the engine housing and expands the high-temperature combustion gas to generate the power. A chamber, an exhaust chamber that discharges expansion gas, an intake chamber that is formed adjacent to the exhaust chamber and sucks in ambient air, and An annular working chamber formed adjacent to the air chamber and having a compression chamber for generating compressed air from intake air, and extending in the axial direction of the annular working chamber and disposed in an intermediate portion of the annular working chamber An output shaft provided with a clutch engaging portion, and rotatably supported by the output shaft and in the intake chamber, the compression chamber, the expansion chamber, and the exhaust chamber, respectively, a suction process and a compression 1st and 2nd piston rotor main body which performs a process, an expansion process, and a discharge process, Comprising: The 1st and 2nd boss part which is aligned with the clutch engaging part in the diameter direction, The 1st and 2nd First and second rotor pistons extending radially outward of the boss portion and rotatably accommodated in the annular working chamber, and first and second extending axially from the first and second boss portions, respectively. First and second pistons having sleeve portions And the end face wall portion and the first and second sleeve portions, respectively, and in each step, the first and second sleeve portions are respectively arranged in the first and second rotational directions. Between the first and second sleeve portion fastening clutches for switching between the locked state and the unlocked state with respect to the end wall portion, and between the clutch engaging portion and the first and second boss portions Each of the first and second boss portions is locked and unlocked with respect to the clutch engaging portion between the second rotation direction and the first rotation direction in the operating cycle. The first and second boss portion fastening clutches, and the combustion portion cools the combustor and generates high-temperature and high-pressure water, while cooling the combustor. The high temperature / high pressure water A high-temperature superheated steam generating section for generating high-temperature superheated steam, a high-temperature high-pressure water injection nozzle for injecting the high-temperature high-pressure water into the combustion chamber and bringing it into contact with the high-temperature combustion gas to generate high-pressure steam, and the high-temperature superheated steam the the gist Rukoto a high temperature superheated steam supply line supplied to the combustor.

According to the ninth aspect of the present invention, in addition to the configuration of the eighth aspect , intake air cooling and exhaust heat energy for generating a mixed fluid of the intake air and the pressurized water by adding pressurized water to the intake air. The gist is to further include a recovery spray device.

In the rotary heat engine according to claim 1, first and second sleeve portion fastening clutches are respectively disposed between the end wall portion of the engine housing and the first and second sleeve portions, and the first And the second sleeve portion between the first and second boss portions between the clutch engaging portion and the first and second boss portions, respectively, between the first and second rotational directions. The first and second boss portion fastening clutches are respectively disposed, and the first and second boss portions are respectively disposed between the second rotational direction and the first rotational direction. On the other hand, a structure that switches between a locked state and an unlocked state is adopted. The locked and unlocked states are automatically switched in response to the high-temperature combustion gas acting on the expansion chamber, eliminating the need for complex crank / planetary gear mechanisms and timing mechanisms that were previously required. It is possible to provide a rotary heat engine with a high pressure ratio and high efficiency with a simple structure and a compact configuration. Moreover, since the rotary heat engine does not use any crank motion, vibration and noise of the heat engine are greatly improved, and smooth operation is possible. Furthermore, since the number of parts of the rotary heat engine is greatly reduced, the assembling property of the parts can be improved, and high reliability and cost reduction can be achieved. Since the combustion part is cooled by the high-pressure water passing through the high-temperature high-pressure water generation part and further cooled by the high-temperature superheated steam generation part, the temperature of the combustion gas in the combustion part casing is, for example, 1500-1700 ° C. The engine output can be improved by raising the temperature to a high temperature range. In addition, since the high-temperature high-pressure water obtained by cooling the combustion section is injected into the combustion chamber and brought into contact with the high-temperature combustion gas, a large amount of water vapor is instantaneously generated to generate the high-temperature combustion gas and the high-pressure water vapor. It is possible to generate a working fluid composed of a mixed fluid. Moreover, because it is providing the high-temperature superheated steam into the combustion unit, it is possible to remarkably improve the engine efficiency and further increase the pressure of the hot combustion gases. In addition, the amount of NOx generated can be suppressed by injecting the high-temperature high-pressure water and the high-temperature superheated steam into the combustion chamber.

  According to a second aspect of the present invention, the first and second sleeve portion fastening clutches are constituted by end surface wall portions of the engine housing and sleeve portions of the first and second piston rotor bodies, and the first and second clutch portions. 2 Since the boss part fastening clutch is composed of the boss parts of the first and second piston rotor bodies and the clutch engaging part provided on the output shaft, the number of parts of the rotary heat engine is small and the structure is simple. Production at low cost is possible.

  In the configuration according to claim 3, since both the first and second sleeve portion fastening clutches and the first and second boss portion fastening clutches are provided with an anti-backlash mechanism, high-temperature combustion gas is generated in the piston. At the time of action, the operation delay due to backlash can be suppressed. Accordingly, the fastening action of the first and second sleeve portion fastening clutches and the first and second boss portion fastening clutches are smoothly executed, and torque transmission to the output shaft is quickly executed. As described above, the conversion efficiency of the high-temperature combustion gas into power is increased by minimizing the backlash (play) of the cam roller, and the operation efficiency of the rotary heat engine is improved.

  According to a fourth aspect of the present invention, the first and second sleeve portion fastening clutches and the first and second bosses via a main lubricating oil supply passage and a plurality of radial lubricating oil supply passages formed on the output shaft. Lubricating oil is always supplied to both the part fastening clutches. For this reason, the smooth operation of these clutches is ensured, and wear of the contact surfaces between the constituent members is reduced. As a result, the reliability and noise reduction of the rotary heat engine are improved, and further, the life of the rotary heat engine can be extended. In addition, the reduction in the wear of the contact surfaces between the constituent members significantly reduces the number of times of maintenance and maintenance of the rotary heat engine, and the long-term operation and running cost of the rotary heat engine can be greatly reduced.

  In the configuration according to claim 5, since the combustor includes a spiral combustion chamber formed in a plane perpendicular to the axis of the output shaft in the engine housing, the axial dimension of the combustor is reduced. As a result, the axial dimension of the rotary heat engine is greatly shortened, and a small size and high performance can be realized. Further, since the spiral combustion chamber forms a relatively long combustion path, the combustion time of the premixed gas of fuel and combustion air becomes long. Therefore, even when a fuel made of carbonaceous fuel is employed, complete combustion of the fuel is promoted, unburned components such as CO and HC are reduced, and exhaust gas is purified. In addition, since the combustor premixes the fuel and the combustion air uniformly and combusts them with the premixed gas generating section, no local high temperature section is generated in the combustion gas. Therefore, combined with the effect of the addition of high-temperature superheated steam, which will be described later, it becomes possible to greatly suppress the NOx emission.

In the structure of Claim 6 , the said 1st and 2nd piston rotor main body is made to function as a compressor and an expander by cooperating with both the said compression chamber and the said expansion chamber. Furthermore, by adding pressurized water to the intake air by the intake air cooling / exhaust heat energy recovery spray device to form a mixed fluid of the intake air and the pressurized water, moisture in the intake air evaporates in the compression process to cool the intake air Therefore, the power required for the compression process is reduced, and the output power is increased accordingly. Further, in the expansion stroke, the thermal energy of the high-temperature combustion gas is transmitted to the first and second piston rotor bodies and becomes high temperature. In the configuration of the present invention, in the compression step, the mixed fluid is brought into contact with the surfaces of the first and second piston rotor bodies, and the exhaust heat energy of the first and second piston rotor bodies is efficiently recovered. As the water contained in the fluid evaporates, the surfaces of the first and second piston rotor bodies and the inner peripheral surface of the engine housing are further effectively cooled, and the exhaust heat energy oh of these components is efficiently recovered. Can do. This makes it possible to further improve the engine efficiency. In addition, by adopting this cooling method and the waste heat energy recovery method, the temperature of the combustion gas can be increased to a high temperature region of 1500 ° C. or higher, so that the engine efficiency can be improved. Furthermore, the durability of the engine can be improved, and the practical use of a small, high-performance and highly durable rotary heat engine is facilitated.

In the configuration according to claim 7, the exhaust heat energy of the high-heat components including the engine housing, the end wall portion, and the first and second piston rotor bodies that have become high temperature in the expansion stroke of the high-temperature combustion gas is used as intake air and pressurized water. It is made to collect | recover in a suction | inhalation / compression process using the mixed fluid. Since the pressurized water contained in the mixed fluid evaporates in the suction / compression process, not only the mixed fluid itself is cooled, but also the exhaust heat energy of the high heat component can be recovered and cooled. Therefore, it is possible to reduce the power required for the compression process and increase the net power that can be extracted from the output shaft. Furthermore, the engine efficiency is further improved because the mixed fluid also recovers the exhaust heat energy of the hot components. In addition, high-temperature components that have become hot due to high-temperature combustion gas during the expansion stroke are cooled in each intake and compression process, so the temperature of the combustion gas can be raised to 1700 ° C, further increasing engine efficiency, This makes it possible to put a long-life rotary heat engine into practical use.

In the rotary heat engine drive power generator according to claim 8, the generator is driven by a compressor / expander having an extremely simple structure, so that the vibration and noise are high and the efficiency is high, and the number of parts is greatly reduced. As a result, the assembling property of the parts is improved, and high reliability and cost reduction can be realized. Since the combustion part is cooled by the high-pressure water passing through the high-temperature high-pressure water generation part and further cooled by the high-temperature superheated steam generation part, the temperature of the combustion gas in the combustion part casing is, for example, 1500-1700 ° C. The engine output can be improved by raising the temperature to a high temperature range. In addition, since the high-temperature high-pressure water obtained by cooling the combustion section is injected into the combustion chamber and brought into contact with the high-temperature combustion gas, a large amount of water vapor is instantaneously generated to generate the high-temperature combustion gas and the high-pressure water vapor. It is possible to expand the working fluid composed of the mixed fluid with the expander unit and increase the power generation output. In addition, since the high-temperature superheated steam is supplied to the combustion section, the pressure of the high-temperature combustion gas can be further increased, and the power generation efficiency of the engine can be dramatically improved. In addition, the amount of NOx generated can be suppressed by injecting the high-temperature high-pressure water and the high-temperature superheated steam into the combustion chamber.

  In the configuration according to claim 10, the exhaust heat energy of the high heat parts including the engine housing, the end face wall portion, and the first and second piston rotor bodies that have become high temperature in the expansion stroke of the high-temperature combustion gas is used as intake air and pressurized water. It is made to collect | recover in a suction | inhalation / compression process using the mixed fluid. Since the pressurized water contained in the mixed fluid evaporates in the suction / compression process, not only the mixed fluid itself is cooled, but also the exhaust heat energy of the high heat component can be recovered and cooled. Therefore, the power required for the compression process is reduced, the net power that can be extracted from the output shaft is increased, and the exhaust heat energy of the high heat components is recovered via the mixed fluid, so that the engine efficiency is further improved. In addition, high-temperature components that have become hot due to high-temperature combustion gas during the expansion stroke are cooled in each intake and compression process, so the temperature of the combustion gas can be raised to 1700 ° C, further increasing engine efficiency, This makes it possible to put to practical use a long-life rotary heat engine drive power generator.

The block diagram of the rotary heat engine drive electric power generating apparatus using the rotary heat engine by the Example of this invention is shown. 2 shows a cross-sectional view of the combustor of the rotary heat engine of FIG. 2 shows a cross-sectional view of the rotary heat engine of FIG. FIG. 4 shows a cross-sectional view of IVA-IVA of the rotary heat engine of FIG. 3. FIG. 4 shows a cross-sectional view of the rotary heat engine of FIG. 3 taken along IVB-IVB. The perspective view of the rotary piston part which is a part of rotary heat engine of FIG. 3 is shown. FIG. 4 shows a VIA-VIA cross-sectional view of the rotary heat engine of FIG. 3. FIG. 4 shows a VIB-VIB cross-sectional view of the rotary heat engine of FIG. 1. An example of the retainer of the one-way clutch for a 1st sleeve part fastening shown to FIG. 6A is shown. An example of the spring member of the one-way clutch for fastening the first sleeve shown in FIG. 6A is shown. It is a schematic diagram for demonstrating the effect | action of the rotary heat engine of FIG. 3, and shows the initial position of a 1st piston and a 2nd piston. It is a schematic diagram for demonstrating the effect | action of the rotary heat engine shown in FIG. 3, and shows the intermediate position in the expansion stroke of a 1st piston and a 2nd piston. It is a schematic diagram for demonstrating the effect | action of the rotary heat engine shown in FIG. 3, and shows the vicinity of the last position in the 1st cycle of a 1st piston and a 2nd piston. It is a schematic diagram for demonstrating the effect | action of the rotary heat engine shown in FIG. 3, and shows the start position of the 2nd cycle of a 1st piston and a 2nd piston.

  Hereinafter, a power generator incorporating a rotary heat engine according to an embodiment of the present invention (hereinafter referred to as a “rotary heat engine drive power generator”) will be described in detail with reference to the drawings. In the rotary heat engine drive power generation device 10, the rotary heat engine 100 includes a compressor / expander 11 that performs the steps of suction, compression, expansion, and exhaust. The compressor and expander 11 has a compressor part and an expander (expander) part, as will be described later. The compressor section has an intake port 126 and a compressed air discharge port 130. The intake port 126 is connected to an air duct 500 having an air filter (not shown) attached to the air intake port. In the air duct 500, an intake air cooling / exhaust heat energy recovery spraying device (hereinafter referred to as “spraying device”) 508 connected to a water supply tank 506 through a water supply pipe 502 and a pressure pump 504 is disposed. The spraying device 508 sprays the pressurized water Pwt in the air duct 500 through a number of spray nozzles 508a and mixes it with the intake air to form the intake mixed fluid AWF, and supplies it to the compressor unit from the intake port 126. The compressor unit Compressed air CA generated in step 1 is discharged from the compressed air discharge port 130. The expander unit expands the high-temperature and high-pressure combustion gas to generate power on the output shaft 132. A combustor 13 is connected to the compressor / expander 11 via a gas guide path member 12 that functions as a spacer. The generator 14 is connected to the compressor / expander 11 via a gas guide path member 12 and the combustor 13 with bolts and nuts. It connects by connection members (not shown), such as. In FIG. 1, the compressor / expander 11 is schematically illustrated.

  The compressed air discharge port 130 of the compressor portion of the compressor / expander 11 is connected to the inlet side of the starter accumulator 514 via an inlet valve 512 formed of a three-way switching valve. The outlet side of the starter accumulator 514 is connected to an outlet valve 516. Outlet valve 516 is connected to compressed air supply line 518. An inlet valve 512 is also connected to the compressed air supply line 518, and is connected to the air supply unit 50 of the combustor 13 via an intake flow rate control valve 519. The starter accumulator 514 is configured such that when the pressure in the compressed air supply line 518 exceeds a predetermined value, the intake flow rate of the intake flow rate control valve 519 is reduced, while the outlet valve 516 is closed and the inlet valve 512 is closed at the same time. Is switched to store the compressed air CA. When the pressure of the compressed air supply line 518 becomes equal to or lower than a predetermined value, the intake flow rate control valve 519 is controlled so as to reach the maximum flow rate, and the flow path of the inlet valve 512 is switched so that the compressed air discharged from the compressed air discharge port 130 is discharged. The entire amount of CA is supplied to the air supply unit 50 of the combustor 13. The starter accumulator 514 opens the outlet valve 516 when the rotary heat engine 100 is started, and supplies the compressed air CA stored in the combustor 13 as combustion air.

  The combustor 13 includes a premixed gas generation unit 40 that generates a premixed gas of combustion air and fuel. The premixed gas generator 40 is supplied with fuel from a fuel tank 520 via a fuel flow rate control valve 524 and a fuel pump 522. As the fuel, a fossil fuel such as OL, heavy oil, 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. Here, a case where shale oil is used as a carbonaceous fuel will be described. The shale oil OL in the fuel tank 520 is supplied to the fuel supply unit 60 of the premixed gas generation unit 40 via the fuel pump 522 and the fuel flow rate control valve 524. The fuel OL is premixed with compressed air CA in the presence of high-temperature superheated steam, which will be described later, and this premixed gas is ignited by the ignition unit 42 to generate high-temperature combustion gas HPG. At this time, since the fuel OL comes into contact with the high-temperature superheated steam, the shale oil is completely vaporized and a uniform premixed gas is generated. The high-temperature combustion gas HPG is supplied to the high-temperature gas introduction port 124 of the expander section of the compressor / expander 11 to expand and transmit power to the output shaft 132. The exhaust gas is exhausted from the exhaust port 128 to the outside.

  When the rotary heat engine 100 is started, as described above, the compressed air CA discharged from the starter accumulator 514 through the outlet valve 516 is supplied to the air supply unit 50 of the combustor 13, and the fuel OL and the preheated fuel are preliminarily stored in the combustor 13. After being mixed and combusted, high-temperature combustion gas HPG is generated and supplied to the compressor / expander 11 to perform an expansion / exhaust stroke. In the expansion / exhaust process of the compressor / expander 11, the compressor unit and the expander unit operate in synchronization. That is, the suction / compression process is executed simultaneously with the expansion / exhaust stroke. Therefore, in the expansion / exhaust process of the expander unit, the compressor unit compresses the ambient air, the pressurized water, and the intake mixed fluid AWF supplied from the air duct 500 to generate compressed air CA. At this time, the moisture in the compressed air CA evaporates as the suction / compression process proceeds in the compressor section. Since the mixed fluid is cooled by evaporation of moisture in the compressor section, the power required for the compression process is reduced, and the net power output of the compressor / expander 11 is increased. Further, the intake mixed fluid plays a role of recovering the exhaust heat energy of the compressor / expander 11, which will be described later.

  As shown in FIG. 2, the combustor 13 includes a cylindrical combustion section casing 36. A spiral wall portion 37 is formed on the radially inner side of the combustion portion 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 heat 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 combustion section casing 36 and the spiral wall section 37 so as to extend spirally to the inner sleeve 37 </ b> S in a planar region perpendicular to the center axis of the output shaft 132. The spiral combustion chamber 38 has an effect of promoting complete combustion of the premixed gas by extending the contact time and residence time between the fuel and air.

A premixed gas generation unit 40 that generates a premixed gas of compressed air CA and fuel OL is disposed upstream of the spiral combustion chamber 38. An ignition unit 42 made of a spark plug or a ceramic heater is disposed adjacent to the premixed gas generation unit 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 combustion unit casing 36, and a fuel supply unit 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 OL 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 unit 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. A high-temperature high-pressure water injection nozzle 542 is attached to the high-temperature combustion unit 540, and high-temperature high-pressure water is injected from the high-temperature high-pressure water injection nozzle 542 toward the spiral wall portion 37 in the high-temperature combustion unit 540. The turbulent flow generation baffle member 67 has a central portion in which a combustion gas ejection opening 67a is formed. Part of the high-temperature combustion gas HPG collides with the wall surface of the turbulent flow generation baffle member 67, reverses to the swirl flow collision portion 54 side, becomes a reversal flow, and contacts and mixes with the premixed gas ejected from the swirl flow collision portion 54. Combustion is promoted, and high-pressure steam is generated in a large amount by colliding with high-temperature high-pressure water injected into the high-temperature combustion unit 540.

  The high-pressure water Pwt supplied from the water supply tank 506 via the pressure pump 504 is supplied to the spraying device 508 via the water supply pipe 502, while the high-temperature high-pressure water generator 550 via the high-pressure water flow rate control valve 544. It is supplied to the high pressure water injection nozzle 528. The high-temperature and high-pressure water generating unit 550 extends in an arc shape in the circumferential direction along the combustion unit casing 36, and generates high-temperature and high-pressure water HTPwt from the high-pressure water Pwt while cooling the combustion unit casing 36. Discharge. The high temperature / high pressure water port 554 is connected to the high temperature / high pressure water injection nozzle 542 via a high temperature / high pressure water supply line 556. Similarly, the high-temperature superheated steam generation unit 560 extends in an arc shape in the circumferential direction along the combustion unit casing 36 at a position adjacent to the high-temperature high-pressure water generation unit 550. The high-temperature superheated steam generation unit 560 includes a high-temperature / high-pressure water injection nozzle 562 connected to the high-temperature / high-pressure water discharge port 554 via a high-temperature / high-pressure water supply line 556, and converts the high-temperature / high-pressure water into saturated steam to combust the combustion section casing 36 The high-temperature superheated steam SpSpst is generated while cooling, and discharged from the high-temperature superheated steam outlet 564. The high temperature superheated steam Spst is supplied to the compressed air supply unit 50 of the combustor 13 through the high temperature superheated steam supply line 566.

  In FIG. 2, the high-temperature and high-pressure water generation unit 550 and the high-temperature superheated steam generation unit 560 are arranged in a common arcuate cooling disposed along the combustion zone 38 a of the spiral combustion chamber 38 on the radial inner side of the cylindrical combustion unit casing 36. A heat transfer member 570 is provided. The arc-shaped cooling 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 in the position adjacent to the turbulent flow generation baffle member 67 and the arc-shaped cooling heat transfer member. A high pressure water introduction portion 572 formed between the member 570 and the high pressure water injection nozzle 552 to inject high pressure water Pwt, and a plurality of openings 574a formed on the downstream side of the high pressure water introduction portion 572. A plurality of turbulent flow paths comprising a radial partition wall 574, a high-temperature and high-pressure water generation chamber 576, and a commercially available stainless steel ball, tungsten ball, or ceramic ball having a diameter of 1 to 25 mm filled in the high-temperature and high-pressure water generation chamber 576. A plurality of heat transfer spheres 578 having 578a and a radial partition wall 574 formed at the rear edge side end of the high-temperature and high-pressure water generator 550 Having.

  The high-temperature superheated steam generation unit 560 is formed on the downstream side of the high-temperature and high-pressure water injection unit 590, and functions as a flow rate limiting member. It consists of a radial partition wall 592 having a plurality of orifices 592a, a high-temperature superheated steam generation chamber 594, a commercially available stainless steel ball, tungsten ball, ceramic ball or the like having a diameter of 1 to 25 mm filled in the high-temperature superheated steam generation chamber 594. And a plurality of heat transfer spheres 596 having a turbulent flow generation path 596a, and a radial partition wall 574 formed at the rear edge side end of the high-temperature superheated steam generator 560. The spray-like high-temperature and high-pressure water HTPwt sprayed on the hot / high-pressure water injection unit 590 comes into contact with the cooling heat transfer member 570 and the plurality of heat transfer spheres 596 to become saturated steam, and the saturated steam is turbulent in the heat transfer sphere 596. The combustion section casing 36 is efficiently cooled while passing through the generation path 596a, and heat is received from the cooling heat transfer member 570 and the plurality of heat transfer spheres 596 to form the high temperature superheated steam Spst. After being supplied from the superheated steam discharge port 564 to the compressed air supply unit 50 via the high temperature superheated steam supply line 566, it is returned to the premixed gas generation unit 40 of the combustor 13.

  Returning to FIG. 1, the rotary heat engine 100 detects the pressure of the accumulator 514 and outputs a pressure signal, and detects the pressure of the high-temperature combustion gas HPG in the combustor 13 and outputs the pressure signal. A sensor S2, a temperature sensor S3 for detecting the operating temperature of the combustor 13 and outputting a temperature signal, an intake air temperature sensor S4 for detecting the intake air temperature, and a NOx sensor S4 for detecting the concentration of NOx in the exhaust gas The pressure sensor S5 for detecting the pressure of the compressed air supply line 518, the calendar data of the rotary heat engine 100, the control operating temperature of the combustor 13, the control pressure of the high-temperature combustion gas HPG, the control pressure of the compressed air supply line 518, etc. It has an input device 17 for inputting input parameters such as setting input data and a memory storing various control programs. And a controller 19.

  Next, the compressor / expander 11 will be described with reference to FIGS. 3 to 8, the compressor / expander 11 includes an engine housing 18 having side wall portions 102 and 104 that are spaced apart in the axial direction and an annular working chamber 114 formed between the side wall portions. And inner peripheral wall portions 108 and 110 extending in the axial direction from the side wall portions 102 and 104, respectively. A center housing 112 is disposed between the side walls 102 and 104, and the side walls 102 and 104 and the center housing 112 are fixedly supported at predetermined positions by bolts or other fixing means (not shown). Although the center housing 112 is shown as being formed of a thin cylindrical case, the center housing 112 is formed with coolant passages at a plurality of locations inside the center housing 112 as necessary, and sucks the above-described high-temperature superheated steam Spst. Before being introduced into the port 126, the engine housing 112 may be cooled by the high-temperature superheated steam Spst by supplying it to the coolant and passage of the engine housing 112.

  In the compressor / expander 11, a high temperature gas introduction port 124 for introducing a high temperature combustion gas HPG, an exhaust port 128, an intake port 126, and a compressed air discharge port 130 are formed in the center housing 112. The intake port 126, the exhaust port 128, and the compressed air discharge port 130 are arranged at positions facing each other in the radial direction. The hot gas introduction port 124, the compressed air discharge port 130, the exhaust port 128, and the intake port 126 are formed at positions adjacent to each other in the center housing 112. The hot gas introduction port 124, the intake port 126, the exhaust port 128, and the compressed air discharge port 130 are arranged at positions facing each other in the radial direction. The annular working chamber 114 includes an expansion chamber 116 that communicates with the hot gas introduction port 124, an exhaust chamber 120 that communicates with the exhaust port 128, an intake chamber 118 that communicates with the intake port 126, and a compression that communicates with the compressed air discharge port 130. A chamber 122 is defined. As shown in FIGS. 3, 4 </ b> A, and 4 </ b> B, an output shaft 132 of the compressor / expander 11 extends in the axial direction of the annular working chamber 114 and is disposed at the center of the annular working chamber 114. Joint portions 132a and 132b are provided. The clutch engaging portions 132a and 132b of the output shaft 132 have first and second piston rotor main bodies 150 and 152 comprising first and second rotor pistons 15050452p each having a pair of pistons arranged symmetrically in the radial direction. Is provided. As described above, the first and second piston rotor bodies 150 and 152 have functions as an expander section for expanding the high-temperature combustion gas and a compressor section for compressing the intake air, and sequentially perform the suction, compression, expansion, and exhaust processes. ,Run.

  Fluid guide portions 150g and 152g for guiding the high-temperature combustion gas HPG are formed on the outer peripheral edges of the first and second rotor pistons 15050452p. The first and second piston rotor bodies 150 and 152 include first and second boss portions 154 and 156 that respectively support the first and second rotor pistons 15050452p, and first and second first and second boss portions 154. 156 have first and second sleeve portions 158 and 160 extending outward in the axial direction. The first and second boss portions 154 and 156 have inner wall portions 154a and 156a, respectively. Note that a plurality of seal members are disposed on the outer peripheral surface and both side surfaces of the piston 15050452p, but these seal members are omitted in the drawings for the sake of simplification of the drawings.

  In the engine housing 18, the output shaft 132 extends in the axial direction along the central axis of the annular working chamber 114, and is rotatably supported by bearings 134 and 136 mounted on the side walls 102 and 104 of the engine housing 18. ing. A rotary piston part 200 is rotatably accommodated in the annular working chamber 114, and the rotary piston part 200 is supported by the output shaft 132 through the needle bearings 142 and 144 so as to be rotatable in the circumferential direction.

  First and second sleeve portion fastening clutches 170 and 172 are disposed between the inner peripheral wall portions 108 and 110 of the side wall portions 102 and 104 of the engine housing 18 and the first and second rotor piston main bodies 150 and 152, respectively. The In FIG. 6A, the first sleeve portion fastening clutch 170 is integral with the sleeve portion fastening outer race portion 108a integral with the inner peripheral wall portion 108 and the sleeve portion 158 of the boss portion 154 of the first rotor piston body 150. And an inner race portion 158a for fastening the sleeve portion. The sleeve portion fastening outer race portion 108a has a hexagonal cam surface 108b. Between the sleeve portion fastening outer race portion 108a and the sleeve portion fastening inner race portion 158a, a plurality of sleeve portion fastening wedge 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.

  Further, an annular retainer 178 is accommodated between the inner peripheral wall portion 108 and the sleeve portion 158. 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 periphery 178c of the retainer body 178b is the sleeve. It is set slightly larger than the outer periphery of the 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. 6A, the anti-backlash mechanism 180 protrudes radially outward from the outer periphery of the anti-backlash suppression groove 180a formed on the inner peripheral wall 108 at a position facing the radial direction and the retainer 178. And an operating protrusion 178d accommodated in the anti-backlash suppressing groove 180a. The S-shaped spring member 184 (see FIG. 6) urges the operating protrusion 178d to the anti-backlash position in the anti-backlash suppressing groove 182a to minimize backlash (play) of the sleeve portion fastening cam roller 176. . Therefore, when the sleeve portion 158 of the piston 150p is counterclockwise in FIG. 4A, the sleeve portion 158 is quickly locked to the side wall portion 102 via the stationary inner race portion 108, and the sleeve portion fastening cam roller 176 The machine conversion efficiency is improved because of less play.

  On the other hand, as shown in FIG. 6B, the second sleeve portion fastening clutch 172 includes a sleeve portion fastening outer race portion 110a integral with the inner peripheral wall portion 110 and a sleeve extending from the boss portion 156 of the second rotor piston main body 152. An inner race portion 160a integrated with the portion 160 is provided. The outer race portion 110a for fastening the sleeve portion has a hexagonal cam surface 110b. A plurality of sleeve portion fastening wedge-shaped cam space portions 174A are formed between the sleeve portion fastening outer race portion 110a and the inner race portion 160a at intervals in the circumferential direction. Accommodates a sleeve portion fastening cam roller 176A as a plurality of cam elements.

Further, an annular retainer 178 </ b> A is accommodated between the inner peripheral wall portion 110 and the sleeve portion 160. 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. 6B, the anti-backlash mechanism 182 protrudes radially outward from the outer periphery of the anti-backlash suppression groove 182a formed in the radially opposing position on the inner peripheral wall 110 and the retainer 178A. And an actuating protrusion 178d accommodated in the anti-backlash suppressing groove 182a. The S-shaped spring member 184 (see FIG. 6) biases the operating protrusion 178d to the anti-backlash position in the anti-backlash suppression groove 182a, thereby minimizing backlash (play) of the sleeve portion fastening cam roller 176A. . Therefore, when the sleeve portion 160 of the piston 152p is counterclockwise in FIG. 4B, the sleeve portion 160 is quickly locked to the side wall portion 110 via the stationary inner race portion 110a. Since the retainer 178A has the same structure as the retainer 178, the illustration is omitted.

  3, 4A, and 4B, the first and second boss portions are fastened between the clutch engaging portions 132a and 132b of the output shaft 132 and the first and second rotor piston bodies 150 and 152, respectively. 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 boss portion fastening wedge-shaped cam space portion 186d is formed between the annular inner wall portion 154a and the clutch engaging portion 132b of the output shaft 132 at a circumferential interval, and the boss portion fastening wedge-shaped cam space portion 186d includes Boss portion fastening cam rollers 186e as a plurality of cam elements are housed. 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.

  3 and 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 rotor 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. As shown in FIG. 4B, the outer race portion 188a for fastening the boss portion has a hexagonal cam surface 188c. 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 groove 190a formed in the annular inner wall portion 154a of the boss portion 154 so as to face the radial direction, and the annular retainer 186f. And an actuating member 186h housed in the lash suppressing groove 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 groove 190a. The S-shaped spring member 194 has a similar structure to that of FIG. 4B, the anti-backlash mechanism 192 is provided on the outer periphery of the anti-backlash suppression groove 192a formed in the annular inner wall portion 156a of the boss portion 156 so as to face the radial direction, and the retainer 188f. And an actuating member 188h housed in the suppression groove 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 groove 192a. The S-shaped spring member 194 has a similar structure to that of FIG.

  Returning to FIG. 3, a main lubricating oil supply path 132L is formed along the central axis of the output shaft 132, and a plurality of lubricating oil guide paths 132L1, 132L2, and 132L3 are formed so as to extend in the radial direction from the main lubricating oil supply path 132L. The first and second sleeve portion fastening clutches 170 and 172 and the first and second boss portion fastening clutches 186 and 188 are supplied with lubricating oil from a lubricating oil pump 250 described later. That is, in FIG. 3, the lubricating oil guide path 132L1 and the lubricating oil guide path 132L2 communicate with the wedge-shaped cam space portions 174 and 174A of the first and second sleeve portion fastening clutches 170 and 172, and these wedge-shaped cam space portions. The lubricant is supplied to the contact surface between the retainer and the cam roller, the contact surface between the cam roller and the output shaft, the contact surface between the cam roller and the boss portion of the piston, and the anti-backlash mechanisms 180 and 182. Similarly, as is apparent from FIGS. 3 and 4A, the lubricating oil guide path 132L1 communicates with the boss portion fastening wedge-shaped cam spaces 186d and 188d of the first and second boss portion fastening clutches 186 and 188, respectively. The contact surfaces of the retainers and the cam rollers of the first and second boss portion fastening clutches 186 and 188, the contact surfaces of the cam rollers and the output shaft, the cam rollers and the boss portions of the pistons via the wedge-shaped cam space portions. Lubricating oil is supplied to the contact surface and anti-backlash mechanism 190, 192. As described above, since the lubricating oil is effectively supplied to the first and second sleeve portion fastening clutches 170 and 172 and the first and second boss portion fastening clutches 186 and 188, smooth rotation of the rotary heat engine is facilitated. Operation, low noise and long life can be achieved.

  In FIG. 3, the lubricating oil pump 250 is housed in a part of the side wall portion 104 of the compressor / expander 11 and is driven by being connected to the vicinity of the rear end portion of the output shaft 132 to lubricate the main lubricating oil supply passage 132L. Supply oil. More specifically, the lubricating oil pump 250 is structurally similar to a so-called trochoid pump (eg, an internal gear pump disclosed in US Pat. No. 4,080,018), and is a pump supported on the back surface of the side wall 104. A casing 252 is provided. The pump casing 252 is fixedly supported on the back surface of the side wall portion 104 via the cover member 254, and an oil sump 256 is formed on the back surface of the side wall portion 104 and below the pump casing 252 and the cover member 254. Is stored. If necessary, the oil sump 256 may be taken out of the compressor / expander 11 and used as a lubricating oil tank.

  A pump main body 258 is accommodated in the pump casing 252. The pump main body 258 is a main lubricant for the pump working chamber 260, an inlet 262 for guiding the lubricating oil to the pump working chamber 260, and the lubricating oil discharged from the pump working chamber 260. And an outlet port 264 leading to the oil supply path 132L. A ring-shaped outer rotor 266 is accommodated in the pump working chamber 260 so as to be rotatable in the circumferential direction. An inner rotor 268 is accommodated in the outer rotor 266 in an inscribed state, and the inner rotor 268 is connected to the output shaft 132 and driven. The outer teeth of the inner rotor 268 are housed so as to be in contact with the inner teeth of the outer rotor 266. The central axis of the pump working chamber 260 and the central axis of the outer rotor 266 are accommodated with respect to the central axis of the inner rotor 268. When the inner rotor 268 rotates, the outer rotor 266 is rotated in the circumferential direction in the pump working chamber 260 while the outer teeth of the inner rotor 268 are inscribed in the inner teeth of the outer rotor 266. When the volume between the inner rotor 268 and the outer rotor 266 increases, a negative pressure is generated to generate a suction pressure, and the lubricating oil is sucked from the oil sump 256. When the two rotors further rotate, the volume decreases and the discharge side volume chamber discharges high pressure, and the sucked lubricating oil passes through the oil port 270 formed in the vicinity of the rear end portion of the output shaft 132, and the main lubricating oil. It is supplied to the supply path 132L.

  Next, the operation of the rotary heat engine 100 will be described based on FIGS. 9 to 12 are schematic diagrams of a rotary heat engine. For easy understanding, a hatched piston is in a locked state, and a white (no hatched portion) piston is in an unlocked state, that is, free rotation. Indicates that it is in a state.

  In FIG. 1, when a start command is output from the controller 19, the outlet valve 516 and the intake flow control valve 519 are opened. At this time, the compressed air CA in the start-up accumulator 514 is supplied to the premixed gas generator 40 via the compressed air supply line 518. On the other hand, the fuel pump 522 is activated, the fuel flow control valve 524 is opened, and the shale oil OL is supplied from the fuel tank 520 to the fuel spray nozzle 52 a of the premixed gas generation unit 40. At this time, the fuel OL and the compressed air CA are mixed and agitated by the swirl flow collision unit 54 of the premixed gas generation unit 40 to become the premixed gas AFM, and the premixed gas AFM is ignited by the ignition unit 42 to be ignited by the high temperature combustion unit 540. To generate high-temperature combustion gas HPG. The high-temperature combustion gas HPG is discharged from the high-pressure gas discharge port 44 of the combustor 13 and then supplied to the compressor / expander 11 from the gas introduction port 124 through the flow path 44a of the gas guide path member 12, and obtained by expanding here. The power is transmitted to the output shaft 132, and the generator 14 is driven to obtain a power generation output.

  When the temperature signal from the combustor temperature sensor S3 reaches a predetermined temperature, for example, 1200 ° C., a water supply command is output from the controller 19, the pressurizing pump 504 is activated, and the high-pressure water flow rate control valve 526 is opened. I speak. At this time, the pressurized water Pwt is sprayed from the spray nozzle 508a of the intake air cooling / waste heat energy recovery device 508 into the air duct 500 to generate an intake mixed fluid AWF of intake air and spray water. The intake mixed fluid AWF is supplied from the intake port 126 to the compressor unit. 4A and 4B, the intake mixed fluid AWF contacts the surfaces of the first and second rotor pistons 150p, 152p to cool the pistons. Since the water in the mixed fluid AWF evaporates due to heat generated in the compression process, the mixed fluid itself is cooled, so that the power required for the compression process is reduced and the net power of the output shaft 132 is increased. Further, since the mixed fluid AWF recovers exhaust heat energy of the engine housing 18 and the first and second rotor pistons 150p and 152p heated by the high-temperature combustion gas in the expansion stroke, the net output power of the output shaft 132 further increases. As described above, the engine housing 18 and the first and second rotor pistons 150p and 152p are effectively cooled, and the waste heat energy of these components is recovered to improve the engine efficiency.

  On the other hand, the pressurized water Pwt is supplied to the high-temperature / high-pressure water generation unit 550, generates high-temperature / high-pressure water HTPwt while cooling the combustion unit casing 36, and discharges it from the high-temperature / high-pressure water discharge port 556. The high-temperature and high-pressure water HTPwt is supplied to the high-temperature and high-pressure water injection nozzle 542 via the high-temperature and high-pressure water supply line 556 and is injected into the high-temperature combustion unit 540. At this time, the high-temperature high-pressure water collides with the spiral wall portion 37 of the combustor 13 and cools it, and at the same time, comes into contact with the high-temperature combustion gas. As a result, the high-temperature and high-pressure water instantaneously becomes a large amount of high-pressure steam in the high-temperature combustion unit 540 and is mixed with the high-temperature combustion gas to become a high-temperature and high-pressure working fluid HPG. Further, the high-temperature and high-pressure water HTPwt is supplied to the high-temperature and high-pressure water injection nozzle 562 via the high-temperature and high-pressure water supply line 556 and becomes saturated steam at the high-temperature and high-pressure water injection unit 590, and then the turbulent flow generation path 596a of the heat transfer sphere 596. The combustion section casing 36 is cooled while passing through and is converted into high-temperature superheated steam Spst and discharged from the high-temperature superheated steam outlet 564. The high-temperature superheated steam Spst is collided, stirred, and mixed with the fuel injected from the fuel injection nozzle 52a by the swirl flow generation unit 59 of the premixed gas generation unit 40 from the air supply unit 50 via the high-temperature superheated steam supply line 566. At this time, the fuel is completely vaporized by the high-temperature superheated steam, and a uniform premixed gas is generated. In addition, the engine efficiency is improved by introducing high-temperature superheated steam into the combustor 13.

  Next, the operation cycle of the compressor / expander 11 will be described with reference to FIGS. 4A and 4B, FIGS. 6A and 6B, and FIGS. In FIG. 9, when high-temperature combustion gas HPG is introduced into the expansion chamber 116 of the compressor / expander 11, a counterclockwise pressing force acts on the first piston 150p, and a clockwise CW pressing force acts on the second piston 152p. Act. Then, as shown in FIG. 6A, the sleeve portion 158 integrated with the boss portion 154 of the first piston 150p acts counterclockwise with respect to the sleeve portion fastening cam roller 176. At this time, the sleeve portion fastening cam roller 176 is engaged with the cam surface 108 b, and the first piston 150 p is locked with respect to the engine housing 112. On the other hand, as shown in FIG. 6B, since the clockwise force CW is applied to the sleeve portion 160 of the second piston 152p, the sleeve portion fastening cam roller 176A is separated from the cam surface 110b, and the second piston 152p is unlocked with respect to the engine housing 112, that is, in a free rotation state.

  Even if the sleeve portion 158 of the first piston 150p is held locked to the side wall portion 104 by the cam roller 176 for fastening the sleeve portion, the left end portion (see FIG. 3) of the output shaft 132 is the output shaft 132 and the first piston. A needle bearing 144 disposed between the sleeve portion 158 of 150p is supported so as to be freely rotatable. Further, when the output shaft 132 tries to rotate clockwise, the cam roller 186e of the first boss portion fastening clutch 150 is detached from the cam surface 186c. Therefore, the first boss portion fastening clutch 150 is unlocked, and the output shaft 132 is freely rotated with respect to the clockwise direction CW. At this time, the boss portion fastening cam roller 188e of the second boss portion fastening clutch 188 is engaged with the cam surface 188c by the clockwise action of the boss portion 156 of the second piston 152p, and the clutch engaging portion of the output shaft 132 is engaged. 132b is locked. Accordingly, in FIG. 9, the second piston 152p rotates integrally with the output shaft 132 while expanding the high-temperature combustion gas, and the output torque generated in the expansion stroke is generated via the output shaft 132 by the generator 14 (see FIG. 1). Is transmitted to. In this expansion stroke, the exhaust gas in the exhaust chamber 120 is discharged from the exhaust port 128 by the clockwise rotation of the second piston 152.

  As shown in FIG. 9, in the expansion stroke of the compressor / expander 11, when the second piston 152p rotates and moves in the clockwise direction, the capacity of the intake chamber 118 increases in synchronization with this, so that the mixed fluid AWF becomes the intake chamber. The mixed fluid AWF in the compression chamber 122 is compressed by the clockwise movement of the second piston 152p with respect to the first piston 150p in the locked state. The compressed air CA is discharged from the discharge port 130 and flows through the check valve 512 and the inlet valve 512. At this time, the flow rate of the compressed air CA is controlled by the flow rate control valve 519 and supplied to the premixed gas generator 40 of the combustor 13.

  FIG. 10 shows the positional relationship of the second piston 152p in the expansion / exhaust stroke of the compressor / expander 11 and the middle open position of the intake / compression process. As is apparent from FIG. 10, the high-temperature and high-pressure combustion gas HPG in the expansion / exhaust strokes in the expansion chamber 116 and the exhaust chamber 120 is the first, second rotor piston, and first of the first and second piston rotor bodies 150 and 152. In contact with the second boss portion and the engine housing 18, a part of the heat energy is absorbed by these components and becomes high temperature. On the other hand, in the suction / compression process performed in synchronization with the expansion / exhaust stroke, the mixed fluid AWF contains sprayed water in a saturated state or a supersaturated state. The first and second rotor pistons of the two-piston rotor main bodies 150 and 152, the first and second boss portions, and the engine housing 18 evaporate in contact with each other to cool the exhaust heat energy while collecting it. The compressed air CA becomes a working fluid that recovers the exhaust heat energy, and brings various advantages as described above.

  When the second piston 152p further rotates clockwise CW from the intermediate position shown in FIG. 10 by the high-temperature combustion gas HPG introduced into the expansion chamber 116, the second piston 152p comes into contact with the back surface of the first piston 150p. At this time, the first piston 150p receives a clockwise pressing force by the second piston 152p. Therefore, as apparent from FIG. 6A, the first sleeve portion fastening clutch 170 is unlocked (released), the sleeve portion fastening cam roller 176 is detached from the cam surface 108b, and the sleeve of the first rotor piston main body 150 is removed. The unit 158 is unlocked. Therefore, in FIG. 11, the first piston 150p and the second piston 152p are integrally rotated in the clockwise direction CW, and both pistons reach the position shown in FIG.

  In the rotational positions of the first piston 150p and the second piston 152p shown in FIG. 12, the space of the contact portion between the first piston 150p and the second piston 152p communicates with the expansion chamber 116 and the intake chamber 118, respectively. At this time, in FIG. 12, a clockwise CW force acts on the first piston 150p, and a counterclockwise force acts on the second piston 152p. Therefore, in FIG. 6B, a counterclockwise force is applied to the sleeve portion 160 of the second piston 152p, the sleeve portion fastening cam roller 176A engages with the cam surface 110b, and the second piston 152p is connected to the engine housing. 112 is locked. Accordingly, in the operation cycle shown in FIG. 12, the second piston 152p is stationary (locked state), whereas the first piston 150 is subjected to the action in the clockwise direction CW. At this time, in FIG. 4A, the first boss portion fastening clutch 186 of the first piston 150 is engaged, and the boss portion 154 of the first piston 150 is locked with the clutch engaging portion 132 a of the output shaft 132. Therefore, the output shaft 132 is driven clockwise through the boss portion 154 of the first piston 150, and an output torque is obtained. As described above, the first and second rotor piston main bodies 150 and 152 continuously output the output torque from the output shaft 132 while alternately repeating the locked state and the unlocked state. Thereafter, the expansion process and the compression process described above are sequentially repeated, and the generator 14 (see FIG. 1) is driven to obtain a power generation output.

  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, the generator is described as being connected to a compressor / expander via a gas guideway member and a combustor, but the generator may be connected to the compressor / expander on the opposite side of the combustor position. .

  In the rotary heat engine of the present embodiment, the first and second rotor piston bodies are shown as one-stage type, but the first and second rotor piston bodies and the annular working chamber are arranged in tandem (tandem shape) on the output shaft. ) You may connect. In addition, the first and second rotor piston bodies are shown as having a pair of radially opposed pistons, but include three or three or more rotor pistons arranged at equal intervals in the circumferential direction. The structure may be sufficient. Further, although the sleeve portion fastening clutch and the boss portion fastening clutch are each constituted by a roller type one-way clutch, they may be constituted by a sprag type one-way clutch.

  Further, the outer race part and the inner race part for fastening the sleeve part of the clutch for fastening the sleeve part are illustrated as being integrally formed with the stationary inner wall part of the end face wall part and the sleeve part of the piston rotor body, respectively. Here, the term “integrated” means that the outer race part for fastening the sleeve part and the inner race part itself are configured by independent parts, and these independent parts are respectively attached to the stationary inner wall part and the sleeve part. It is meant that the above configuration is also included. Similarly, in the boss portion fastening clutch, the boss portion fastening outer race portion and the boss portion fastening inner race portion are formed of independent parts, respectively, and these independent parts are connected to the piston rotor body boss part and the output shaft clutch. The same applies to the configuration mounted on each joint.

  In the present embodiment, the high-temperature and high-pressure water generator and the high-temperature eddy heat steam generator are described as being formed inside the combustion section casing, but these components may be formed outside the combustion section casing.

  In this embodiment, the exhaust gas of the rotary heat engine is described as being released into the atmosphere, but the exhaust heat recovery heat exchanger is installed in the exhaust system, and the pump and expander having the same structure as the above compressor and expander is arranged. The high pressure steam is generated by exhaust heat energy in the exhaust heat recovery heat exchanger by pressurizing the feed water by the pump function of the pump and expander, and the output power is increased by the expander function of the pump and expander. Alternatively, a combined cycle method may be used. In this case, the output power of the compressor / expander and the pump / expander may be taken out from a common output shaft, or may be taken out from independent output shafts.

  10. . . 10. Rotary heat engine drive power generator; . . 12. Compressor and expander; gas guideway member; . . Combustor; 14. . . Generator; 17. . . Input device; 18. . . Engine housing; 19. . . Controller; 36. . . Combustion section casing; 38. . . Spiral combustion chamber; 40. . . Premixed gas generator; 44. . . 132. Combustion gas discharge port; . . Output shaft; 150, 152. . . First and second rotor piston bodies; 170, 172. . . Clutches for fastening first and second sleeve portions; 180, 182. . . Anti-backlash mechanism; 186, 188. . . Clutches for fastening the first and second boss parts; 190,192. . . Anti-backlash mechanism; 506. . . Water supply tank; 508. . . 520. Intake air cooling and exhaust heat energy recovery spray device; . . Fuel tank; 542. . . High temperature high pressure water jet nozzle; 550. . . High-temperature high-pressure water generator; 560. . . High-temperature superheated steam generator; 562. . . High temperature high pressure water injection nozzle; 552. . . High pressure injection nozzle

Claims (9)

An engine housing having axially spaced end wall portions;
A combustion section for combusting combustion air and fuel to generate high-temperature combustion gas;
An annular working chamber that is formed between the end wall portions in the engine housing and expands the high-temperature combustion gas to generate the power; and an exhaust chamber that discharges the expansion gas;
An output shaft including a clutch engaging portion that extends in the axial direction of the annular working chamber and is disposed at an intermediate portion of the annular working chamber;
The first and second piston rotor bodies that are rotatably supported by the output shaft and are rotatably accommodated in the annular working chamber, and output torque in an operation cycle, wherein the clutch engaging portion and the radial direction First and second boss parts aligned with each other, first and second rotor pistons extending radially outward of the first and second boss parts and rotatably accommodated in the annular working chamber, First and second piston rotor bodies having first and second sleeve portions extending axially from the first and second boss portions, respectively.
The first and second sleeve portions are disposed between the end face wall portion and the first and second sleeve portions, respectively, and the first and second sleeve portions are respectively disposed between the first and second rotational directions in the respective steps. First and second sleeve portion fastening clutches that switch between a locked state and an unlocked state with respect to the end wall portion;
The clutch engaging portion is disposed between the first and second boss portions, and the first and second boss portions are respectively disposed in the second rotation direction and the first rotation direction in the operation cycle. A first and second boss portion fastening clutch that switches between a locked state and an unlocked state with respect to the clutch engaging portion between
The first and second sleeve portion fastening clutches include a sleeve portion fastening wedge-shaped cam space portion and a sleeve portion fastening cam for locking and unlocking the first and second sleeve portions with respect to the end face wall portion, respectively. On the other hand, the boss portion fastening clutch includes a boss portion fastening cam space portion and a boss portion fastening for drivingly connecting the first and second boss portions to the clutch engaging portion of the output shaft in the same rotational direction. For each cam element ,
A high-temperature and high-pressure water generator that generates high-temperature and high-pressure water by cooling the combustor; a high-temperature superheated steam generator that generates high-temperature superheated steam from the high-temperature and high-pressure water while cooling the combustor; A high-temperature high-pressure water injection nozzle for injecting the high-temperature high-pressure water into the combustion chamber and bringing the high-temperature steam into contact with the high-temperature combustion gas; and a high-temperature superheated steam supply line for supplying the high-temperature superheated steam to the combustor. rotary heat engine, characterized in Rukoto provided. The first and second sleeve portion fastening clutches include first and second sleeve portion fastening outer race portions that are integral with the end surface wall portion, respectively, and first and second sleeve portions that are integral with the first and second sleeve portions, respectively. The sleeve formed between the inner race portion for fastening the first and second sleeve portions, the outer race portion for fastening the first and second sleeve portions, and the inner race portion for fastening the first and second sleeve portions. A sleeve-fastening cam disposed in the first and second sleeve-fastening wedge-shaped cam spaces, and the first and second sleeve-fastening wedge-shaped cam spaces. Comprising first and second sleeve portion fastening cam elements constituting the element,
The first and second boss portion fastening clutches are integral with the first and second boss portions, respectively. The first and second boss portion fastening outer race portions, and the clutch engaging portion are integral with each other. The inner lace part for fastening the first and second boss parts, the outer race part for fastening the first and second boss parts, and the inner race part for fastening the first and second boss parts, respectively. The first and second boss portion fastening wedge-shaped cam space portions constituting the boss portion fastening cam space portion, and the first and second boss portion fastening wedge-shaped cam space portions, respectively. The rotary heat engine according to claim 1, further comprising first and second boss portion fastening cam elements constituting the fastening cam element.   The first and second sleeve portion fastening clutches and the first and second boss portion fastening clutches are respectively connected to the first and second sleeve portion fastening wedge-shaped cam spaces and the first and second boss portions. A retainer that is housed in a fastening wedge-shaped cam space and supports the sleeve portion fastening cam element and the boss portion fastening cam element; and a spring means that urges the retainer to an anti-backlash position. The rotary heat engine according to claim 2, further comprising an anti-backlash mechanism. A main lubricating oil supply passage formed along a central axis of the output shaft; a first and second sleeve portion fastening clutch; and the first and second clutches extending in a radial direction from the main lubricating oil supply passage. A plurality of lubricating oil guide paths for guiding the lubricating oil to the boss portion fastening clutch,
A lubricating oil pump for supplying the lubricating oil to the main lubricating oil supply path;
The rotary heat engine according to any one of claims 1 to 3 , wherein the sleeve portion fastening wedge-shaped cam space portion and the boss portion fastening wedge-shaped cam space portion communicate with the lubricating oil guide path, respectively. . The combustion section includes a combustion section casing, a combustion chamber formed in the combustion section casing, a premixed gas generation section that generates a premixed gas of the fuel and the combustion air in the combustion chamber; and ignition unit for generating the hot combustion gases by igniting the premixed gas, the hot combustion gases to claim 1 or characterized in that it comprises a combustion gas discharge port to be supplied to the expansion chamber The described rotary heat engine. The annular working chamber is formed adjacent to the exhaust chamber and sucks ambient air in the suction process, and generates compressed air from the suction air in the compression process to produce the combustion air in the combustor. A compressor function for compressing the intake air in cooperation with the first and second piston rotor bodies, respectively, the compression chamber for supplying, and the intake chamber and the compression chamber, the expansion chamber and the exhaust chamber, respectively. The rotary heat engine according to claim 1 , wherein the rotary heat engine operates as a compressor / expander having an expander function for expanding the high-temperature combustion gas. Water is sprayed on the intake air, and a mixed fluid of the intake air and the pressurized water is introduced into the suction chamber and the compression chamber, and the engine housing, the end wall portion, and the first and The rotary heat engine according to claim 6 , further comprising an intake air cooling and exhaust heat energy recovery spraying device that recovers exhaust heat energy of a high heat component including the second piston rotor body. Combustion section for combusting combustion air and fuel to generate high-temperature combustion gas, function as a compressor for compressing intake air and generating compressed air as the combustion air, and power by expanding the high-temperature combustion gas A compressor and expander having a function as an expander;
A generator driven by the power,
The compressor and expander
An engine housing having axially spaced end wall portions;
An expansion chamber formed between the end wall portions in the engine housing for expanding the high-temperature combustion gas to generate the power, an exhaust chamber for discharging the expansion gas, and an adjacent to the exhaust chamber. An annular working chamber having an intake chamber that sucks in ambient air, and a compression chamber that is formed adjacent to the intake chamber and generates compressed air from the intake air;
An output shaft including a clutch engaging portion that extends in the axial direction of the annular working chamber and is disposed at an intermediate portion of the annular working chamber;
The suction chamber, the compression chamber, the expansion chamber, and the exhaust chamber are supported by the output shaft so as to be rotatable, and a suction process, a compression process, an expansion stroke, and a discharge process are executed, respectively. 1st and 2nd piston rotor main body, Comprising: The 1st and 2nd boss | hub part which aligns with the said clutch engaging part at radial direction, It extends to the radial direction outer side of the said 1st and 2nd boss | hub part, respectively, First and second piston rotors having first and second rotor pistons rotatably accommodated in an annular working chamber, and first and second sleeve portions extending in the axial direction from the first and second boss portions, respectively. The body,
The first and second sleeve portions are disposed between the end face wall portion and the first and second sleeve portions, respectively, and the first and second sleeve portions are respectively disposed between the first and second rotational directions in the respective steps. First and second sleeve portion fastening clutches that switch between a locked state and an unlocked state with respect to the end wall portion;
The clutch engaging portion is disposed between the first and second boss portions, and the first and second boss portions are respectively disposed in the second rotation direction and the first rotation direction in the operation cycle. A first and second boss portion fastening clutch that switches between a locked state and an unlocked state with respect to the clutch engaging portion between
Equipped with a,
A high-temperature and high-pressure water generator that generates high-temperature and high-pressure water by cooling the combustor; a high-temperature superheated steam generator that generates high-temperature superheated steam from the high-temperature and high-pressure water while cooling the combustor; A high-temperature high-pressure water injection nozzle for injecting the high-temperature high-pressure water into the combustion chamber and bringing the high-temperature steam into contact with the high-temperature combustion gas; and a high-temperature superheated steam supply line for supplying the high-temperature superheated steam to the combustor. rotary heat engine-driven power device, characterized in Rukoto provided. Water is sprayed on the intake air, and a mixed fluid of the intake air and the pressurized water is introduced into the suction chamber and the compression chamber, and the engine housing, the end wall portion, and the first and The rotary heat engine drive power generator according to claim 8 , further comprising an intake air cooling / exhaust heat energy recovery spraying device for recovering exhaust heat energy of a high heat component including the second piston rotor body.

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