US3744938A - Alternating vane type rotary engine with planetary gear system - Google Patents

Alternating vane type rotary engine with planetary gear system Download PDF

Info

Publication number
US3744938A
US3744938A US00094122A US3744938DA US3744938A US 3744938 A US3744938 A US 3744938A US 00094122 A US00094122 A US 00094122A US 3744938D A US3744938D A US 3744938DA US 3744938 A US3744938 A US 3744938A
Authority
US
United States
Prior art keywords
vapor
vanes
engine
radial
condenser
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00094122A
Other languages
English (en)
Inventor
A Matvey
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3744938A publication Critical patent/US3744938A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F28B1/08—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium employing moving walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/04—Plants characterised by the engines being structurally combined with boilers or condensers the boilers or condensers being rotated in use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B27/00—Instantaneous or flash steam boilers
    • F22B27/12—Instantaneous or flash steam boilers built-up from rotary heat-exchange elements, e.g. from tube assemblies

Definitions

  • the en- 1'095O34 4/1914 418/36 ergy convertor preferably is a rotary vapor engine in- 2:349: 43 5 1944 Davidsuu 41 3 eluding three sets each 0f three radial vanes located 3,396,632 8/1968 L bl n 413 3 120 apart which are operatively connected to a 3,476,056 11/1969 Bright 418/36 hypocycloidal planetary gear system for progressive 2,576,284 11/1951 Crocchi 60/108 movement of the sets toward and away from each FOREIGN PATENTS OR APPLICATIONS other, the gear system being adjustable to vary the 746,350 3/1956 01661 England 418/36 mrque of the 873,495 3/1942 France 418/36 3 Claims, 16 Drawing Figures Patented July 10, 1973 3,744,938
  • This invention relates generally to new and useful improvements in power generating systems and particularly seeks to provide a completely closed system that includes (1) a novel rotary vapor generator and condenser assembly that is operatively connected to (2) an energy converter that may be, for example, a novel rotary vane-type engine or to a high speed turbine that receives high pressure vapor from the generator and returns the expanded vapor to the condenser, (3) a novel combustion unit therefor and (4) a novel vapor process therefor.
  • Atmospheric pollution particularly in metropolitan areas, has become a serious problem and it is well known that the exhaust gases from automobile internal combustion engines operating on either the Otto or Diesel cycles are substantial contributors to such pollution.
  • Many efforts have been made to reduce these pollutants as by recycling crankcase vapors and catalytically treating the exhaust gases, but a major reduction in such pollutants is not believed to be either technically or economically possible because all such engines operate under conditions of incomplete combustion and result in a relatively low thermodynamic efficiency.
  • Such engines also have a high noise level.
  • noise can be reduced and atmospheric pollution can be prevented through the use of a closed cycle external combustion engine system in which an energy converter receives high pressure vapor from a vapor generator and exhausts expanded low pressure vapor into a condenser that is operatively connected to the vapor generator.
  • the combustion unit or burner that is used to supply heat to the vapor generator is operated with hot walls and an excess of air to assure complete combustion of the fuel.
  • the energy converter for an external combustion engine system could be a steam engine, but up to the present time at least there are too many limitations in the use of steam engines or steam turbines for this purpose to make them practical. For example, the overall efficiency is quite low; the boilers are too bulky; transfer pumps are needed; and the systerms are complex.
  • thermodynamic properties of water make it inefficient and undesirable for energy conversion.
  • the latent heat of evaporation of water is extremely high, when compared to the useful converted heat, thus requiring considerable energy just to evaporate it once the boiling point is reached and most of this energy will also have to be extracted from the expanded steam in the condenser in a closed cycle system, and therefore is wasted energy.
  • the slope of the saturation line of steam is such that the expansion of saturated or moderately superheated steam will always create moist steam which is inefficient and damaging to engine components, unless pressures and temperatures are very high. To avoid this effect superheating is necessary and reheating is mandatory in turbines or piston engines with multiple stages.
  • Such fluids should have a specific gravity greater than 1.4; a molecular weight less than the 190; a boiling point less than C at atmospheric conditions; the slope of the saturated vapor line on an estropy-enthalpy diagram should be negative; and the ratio between the latent heat of vaporization and the heat available during adiabatic expension (when operating between the normal limits of temperature, i.e., 500 C and the ambient temperature) should be less than 2.
  • Examples of commercially available fluids that are usable for this purpose are trichloroethylene, carbon tetrachloride and the following halogenated hydrocarbons, trichlorofluoromethane, dichlorodifluoromethane, chlorotrifluoromethane, chlorodifluoromethane, 11,11,Z-trichloro-1,2,2-trifluoroethane and sym-dichlorotetrafluoroethane.
  • a power system constructed in accordance with this invention can operate with such fluids in a unique manner with high efficiency and without causing any substantial air pollution.
  • the system also contemplates the use of a novel rotary vane-type engine that is particularly adapted for use with vehicles whose operation require wide variations in torque and speed.
  • Novel features of such an engine include; the capability of operating without separate lubricants for many of the moving parts; zero head space; no valves; time control of full pressure vapor admission, rather than variations in orifice size, to avoid throttling effect; built-in torque controlled vapor admission to vary output power and speed; easy reversing or power braking; and pedal actuation of an analog hydraulic control circuit to regulate the amount of air and fuel supplied to the combustion unit for heating the vapor to be supplied to the engine and to control the duration of vapor admission into the engine.
  • an object of this invention is to provide a novel vapor cycle and power plant which will enable the extraction, from the vapor, of all of the available energy in a single stage without requiring reheating or regeneration.
  • Another object of this invention is to provide a power plant of the character stated that includes a novel rotary condenser.
  • Another object of this invention is to provide a power plant of the character stated that includes a novel rotary combined condenser and vapor generator.
  • Another object of this invention is to provide a power plant of the character stated in which the combined condenser-generator is operably connected to an energy converter that receives high pressure vapor from the generator and returns the expanded low pressure vapor to the condenser.
  • Another object of this invention is to provide a power plant of the character stated in which the energy con-.
  • verter is a rotary vane-type engine or a turbine.
  • Another object of this invention is to provide a power plant of the character stated in which the combined condenser-generator is driven by the high pressure vapor during idling and from the output shaft of the engine at other times.
  • a further object of this invention is to provide a power system of the character stated that is compact, light weight, has no external piping for working fluid, operates under a high thermal and mechanical efficiency, has low transfer losses and has a high engine efficiency due to very low chamber residual volume and high expansion ratio.
  • Another object of this invention is to provide a thermal power system of the character stated that operates on a thermodynamic cycle along polytropic lines.
  • Another object of this invention is to provide a power system of the character stated that employs only a small predetermined amount of fluid in the fluid-vapor-fluid cycle.
  • Another object of this invention is to provide a power system of the character stated in which the drive for the combined rotary vapor generator and condenser is also used to drive certain items of auxiliary equipment.
  • Another object of this invention is to provide a rotary engine that includes three power rotors having three vanes each and assembled within a cylinder or cage to form three sets of chambers of variable volumes.
  • a further object of this invention is to provide a rotary engine of the character stated in which the relative positions of the rotors are controlled by three crankpins attached to three satellite gears of a hypocyclic gear train that includes an internal ring gear and may include a sun gear.
  • a further object of this invention is to provide a rotary engine of the character stated in which the rotor vanes themselves control vapor admission and exhaust, and the cut off points therefor, andthus the torque, may be varied either by changing the angular position of the vane cage or that of the internal ring gear of the hypocyclic gear train.
  • a further object of this invention is to provide a novel combustion unit for supplying heat to a vapor genera-
  • a further object of this invention is to provide a novel method for generating power in a closed cycle fluid system.
  • FIG. 1 is a longitudinal vertical section of the condenser and vapor generator portion of a vehicle propulsion system constructed in accordance with this invention
  • FIG. 2 is an extension to the right of FIG. 1 and is a longitudinal vertical section of the rotary vane engine portion of the vehicle propulsion system;
  • FIG. 3 is a top plan view of the mechanism shown in FIG. 1; I
  • FIG. 4 is an enlarged vertical transverse section of the combustion chamber for the vapor generator
  • FIG. 5 is an enlarged vertical transverse section of the fuel nozzle for the combustion chamber
  • FIG. 6 is an enlarged detail perspective of the air control vanes for the combustion chamber
  • FIG. 7 is an exploded isometric view of the three sets of engine vanes
  • FIG. 8-10 are schematic views showing the successive relative positions of the planetary gears during one cycle of operation of the engine vanes
  • FIGS. 11-13 are schematic views corresponding to FIGS. 8-l0 and show the relative positions of the engine vanes during one cycle of operation thereof;
  • FIG. 14 is a schematic flow sheet for the hydraulic, fuel and lubricating systems
  • FIG. 15 is a representative pressure-enthalpy diagram and shows the vapor cycles for this power system.
  • FIG. 16 is a somewhat schematic longitudinal vertical section of the condenser and vapor generator portion of a vehicle propulsion system constructed in accordance with this invention but adapted for use with aircraft or other types of turbine energy convertors.
  • the invention as illustrated, is embodied in a closed cycle system and includes a rotary vapor condenser generally indicated A, an annular vapor generator generally indicated B that surrounds the condenser A and rotates therewith, and a vane type rotary engine generally indicated C that operates on high pressure vapor from the generator B and exhausts the expanded vapor back to the condenser A.
  • the condenser-generator assembly A and B includes a base casing 5 provided on its top with an upstanding tubular casing 6 having upper and lower ball or roller bearings 7, 7 that rotatably support a tube 8 that carries the condenser-generator assembly.
  • the condenser A includes a plurality of sets of helically arranged tubes 9 that extend generally radially from the tube 8 to an annular shell 10 that is concentric with the tube.
  • Low pressure expanded vapor from the engine C is admitted through the open bottom of the tube 8 and passes upwardly therealong and hence radially outwardly through the tubes 9 where it not only condenses but becomes subjected to progressively increasing pressure as the condensate approaches the outer ends of the tubes due to the centrifugal force developed as the result of the rotation of the condensergenerator. Cooling air passes around the exteriors of the condenser tubes as will be hereinafter more fully described.
  • the condensate from the tubes 9 is thrown rapidly by centrifugal force into an annular void 11, defined by the shell 10 and a complementary outer shell 12, which preheats the condensate, as a thin layer which did not become undercooled within the condenser area, from which it is directed into a multiplicity of radially extending pre-heater tubes 13, the outer ends of which are connected to an annular header tube 13a, and superheater tubes 14, the inner ends of which are connected to an annular collector tube 14a, of the vapor generator B (see FIG. 1 and 3) which are heated by the hot gases from a fuel burner to revaporize the liquid as will be hereinafter more fully described.
  • the condenser is self-purging and a very rapid circulation of the vapor liquid L vapor is established and maintained.
  • the collector tube 14a connects with a plurality of inwardly extending insulated radial tubes 15 that extend into open communication with an insulated vertical duct 16 that delivers the high pressure vapor to the engine C and to a single wheel turbine for driving the condenser-generator at its desired speed of rotation.
  • the upper end of the duct 16 is supported by a plug 17 that closes the upper end of the tube 8 and its lower end is closed by a rotary seal in a directional valve generally indicated at 18.
  • the condenser-generator assembly A and B is power driven from a single wheel turbine 19, mounted in the base casing 5, and reduction gears generally indicated which in turn drive a gear 211 rigidly affixed to the tube 8 adjacent the lower end thereof.
  • the reduction gears 20 may also be used to drive certain auxiliary pumps such as a motor-pump indicated 22 and fuel pump 22a that may be mounted on the top of the base casing 5.
  • the condenser and generator tubes 9, l3 and lid, are enclosed by a fixed housing generally indicated D (see FIG. l and 3) that somewhat resembles an oblate spheroid in shape and includes a radially extending air intake 26, a generally convex upper portion 27 and a generally convex lower portion 28.
  • a fixed heat shield 29 is carried beneath the upper portion 27 and surrounds the generator tubes 13 and 14. Forced circulation of air for the burner and heating system is assured by the provision of a scroll 30 and a multiplicity of radially extending fan blades 31 that are secured to and project downwardly from the lower inner portion of the generator B.
  • Cooling air for the condenser A passes from the intake 26, across the condenser tubes 9 and leaves the unit through a suitably large aperture in the top of the housing D.
  • the helical arrangement of the condenser tubes 9 assists this movement of the air.
  • Vaporizing and superheating heat is supplied to the generator B from a combustor that includes a generally cylindrical vertical combustion chamber indicated E having an inner refractory lined sleeve 32 to keep the inside wall at high temperature for complete combustion and an outer spaced concentric sleeve 33 with the void therebetween defining an air jacket 34 for insulation, preheating and cooling purposes.
  • Air is admitted from the scroll 30 at 35 and is further preheated by circulation around the sleeve 32 which is assured by the provision of a circumferential spiral baffle 36 interposed between the sleeves 32 and 33.
  • the bottom of the sleeve 32 is provided with a two piece inverted conical air control valve that includes a stationary element 37 secured to the sleeve 32 and provided with a plurality of upstanding radial wedgeshaped vales 38 struck from the material of the element 37 and bent upwardly at a substantial angle to create turbulence, thus leaving a corresponding number of radially extending wedge-shaped openings 39 in that element.
  • a complementary element 40 is positioned beneath the element 37 for oscillation with respect thereto about a vertical axis and is provided with a plu rality of upstanding wedge-shaped vanes 41 that fit within the wedge-shaped openings 39 to form a variable opening register.
  • the bottom of the sleeve 33 is closed by a conical member 432 to which is affixed a depending tube 43 coaxially aligned with the air valve elements 37 and 4d.
  • a closed-end cylinder 44 is rotatably supported within the tube 43 by upper and lower bearings 45, 4 5 and is provided at its bottom with a fuel line connector 4% and a radially extending air control lever 37.
  • a piston 48 is carried within the cylinder 4-41 and supports a tubular upwardly projecting nozzle body 49 provided intermediate its end with an abutment flange 50 adapted to engage the upper end of the cylinder 44 as a limit for the upward projection of the nozzle body when fuel under pressure is admitted to the lower part of the cylinder.
  • a compression spring 511 constantly urges the nozzle body 49 toward its fully retracted position so that it will not get too hot from radiation when the burner is shut down and result in carbonation before restarting.
  • Spring Sll is overcome at a relatively low pressure in cylinder 44, e.g., 10 psi so that flange 50 will be engaged.
  • the upper end of the nozzle body 439 preferably is hemispherical in shape (see FIG. 5) and is provided with an inverted conical orifice 52 through which a valve needle 53, having an enlarged conical tip 54 complementary to the orifice 52, passes.
  • the intermediate portion of the nozzle 53 is reciprocably supported by a perforated disc 55 and its lower end is affixed to a perforated piston 56.
  • a compression spring 5'7 is interposed between the disc 55 and piston 56 to constantly urge the needle 53 toward its fully retracted position with the tip 54 thereof seated against the walls of the orifice 52.
  • Spring 57 is barely overcome at an intermediate pressure, e.g., E00 psi, but overcome to completely open orifice 52 at a higher pressure, e.g., 1,000 psi to thus provide a variable fuel rate to the chamber.
  • the top of the cylinder 44 is provided with a tubular neck 53 that is affixed to and supports the lower air valve element 410 so that when the air control lever 47 is oscillated in either direction, a corresponding oscillation of the air valve element will take place.
  • the neck 58 preferably is provided with a plurality of radial apertures 59 located above the conical closure 42, so that air may also pass around and along the upper part of the nozzle body $9 for cooling purposes.
  • a spark'plug bill which extends upwardly through the members 42, 40 and 37 provides ignition at start up.
  • the hot gases from the combustion pass along a generally convolute duct 61 which confines the gases to contact with the various tubes of the vapor generator B in counter flow fashion and exhausts and cooled gases through an exhaust outlet 62 (see FIGS. 1 and 3).
  • the baffle 12a isolates the preheater tubes from the superheater tubes.
  • the vane engine C is mounted to one side of the condenser-generator assembly (see FIG. 2) for rotation about a horizontal axis and includes a vane cage or casing 63 having a cylindrical chamber 64 within which are fitted three horizontal concentric rotor shafts respectively designated 65, 66 and 67.
  • the shaft 65 carries at its left end three radial vanes 68 (see FIG. 7) mounted 120 apart on a hub 69; the shaft 66 similarly carries three radial vanes 70 mounted 120 apart on a hub 71; and the shaft 67 carries three radial vanes 72 mounted 120 apart on a hub 73.
  • vanes 68 are axially offset from the hub 69 in one direction
  • the vanes 70 are symmetrical with respect to the hub 71
  • the vanes 73 are axially offset from the hub 73 in a direction opposite to that of the vanes 68 so that when the hubs 69, 71 and 73 are brought together along their common axis the vanes will interfit and smoothly rotate as a unit within a cylindrical chamber 64.
  • the shafts 65-67 in addition to being bodily rotatable, are oscillatable with respect to each other whereby to vary the relative positions of the vanes and thus create variable volume vapor chambers therebetween.
  • the right end of the rotor shaft 65 is provided with a radial crank arm 74 and has formed therein an open face radial slot 75; the intermediate rotor shaft 66 is provided with a similar crank arm 76 and radial slot 77, and the outer rotor shaft is similarly provided with a slotted crank arm (not shown).
  • a gear housing 78 encloses the above described crank arms and contains a hypocycloidal planetary gear system comprising an internal ring gear 79, a central sun gear 80 mounted on an output shaft 81 and three satellite gears 82, 83 and 84 interposed between the ring and sum gears (all three satellite gears are schematically indicated in FIGS. 8-10 and are rotatable in carrier 810 at 120 of each other).
  • the satellite gear 82 carries a crank shaft 85 provided with a balanced crank arm 86 having an offset crank pin 87 that is operably received within the slot 75 of the rotor shaft crank arm 74.
  • Similar crank pin connections 88 and 89 are provided between the other two satellite gears and their respectively associated rotor shaft crank arms.
  • the vane cage 63 is provided with a set of radial inlet ports (indicated at 90 in FIGS. 11-13) spaced 120 apart for receiving high pressure vapor from the directional valve 18 through suitable piping (not shown) and a companion set of exhaust ports (indicated at 91 in FIGS. 11-13) that are angularly offset a predetermined distance from the inlet ports.
  • FIG. 11 shows that the vanes 68 and 70 are closed together each time the vanes 68 block off the inlet ports 90, and as their rotational movement continues they progressively separate (see FIG. 12) so that a first variable volume chamber 92 is formed between the vanes 68 and 70-to receive high pressure vapor from 90 until it is closed by the vane 70 and then (see FIG. 13) a second variable volume chamber 93 is formed between the vanes 70, 72, etc.
  • FIGS. 8-10 indicate the corresponding positions of the crank pins 87-89 during one cycle of vane movements and show how the satellite gears 82-84 consequently drive the sun gear and its associated output shaft 81, while the ring gear 79 remains fixed.
  • the relative sizes of the ring, sun and satellite gears are such that the satellite gears make three complete turns per revolution of the engine shaft and the output shaft makes four turns per revolution of the engine shaft.
  • the expanded low pressure vapor from the exhaust ports 91 enters the condenser-generator casing and then passes into the bottom of the vertical rotating tube 8 and is conducted therethrough into the condenser A to commence a repetition of the vapor cycle.
  • the rotary engine C has been described as running in one direction and as if at a constant speed and torque.
  • means should be provided for varying the torque and/or stopping or reversing the engine without having to employ a clutch or a reversing gear box.
  • a portion of the ring gear 79 is provided with external gear teeth 96 that mesh with the teeth of a rack 97 that is adapted to be reciprocated by a double acting hydraulic cylinder 98.
  • the rack 97 will have rotated the ring gear 79 sufficiently to change the positions of the satellite gears 82-84 enough that the vanes 68, 70, 72 will no longer properly receive vapor from the inlet ports 90 for forward drive and will be in positions for reverse drive.
  • the vapor piping to the engine includes the valve 18 that shuts off the vapor flow to the inlet ports 90 and admits vapor to a second set of inlet ports (not shown) that are symmetrically located on the opposite sides of the exhaust ports to drive the vanes and their associated elements in the reverse direction.
  • the same exhaust ports are used for both directions of rotation.
  • the output torque of the engine is imposed on the ring gear 79 which is arrested in a given position by the prevailing oil pressure in the cylinder 98.
  • the ring gear is rotated by the satellite gears against the piston, thus modifying the relationship between the positions of the vanes and the vane cage 63 into which the inlet and exhaust ports are incorporated. This tends to close the admission of vapor ahead of the originally preset position and reduce the pressure in the variable capacity vapor chambers between the vanes of the engine rotor.
  • the position of the accelerator pedal is changed to vary the output torque, the above described reactions modify the vapor admission and therefor the torque. If the response of this analog control is made to be fast enough, the system is capable of dampening the pulses of the engine as the vapor is admitted into each set of chambers, thus resulting in smooth operation of the engine.
  • All controls and accessories for this embodiment of the invention preferably are hydraulic. From an inspection of FIG. 14 which is a schematic flow sheet for the hydraulic, fuel and lubrication systems, it will be seen that a single source of hydraulic oil is used for all functions.
  • a power system of this type naturally requires certain auxiliary equipment such as a stater for the condensergenerator, torque control, direction control, vapor throttle control, fuel feed control, power steering, power brakes, and windshield wipers if it is mounted on a vehicle, and for these purposes in addition to the dual pumps 22 and 22a on top of the casing 5, a pair of internally driven hydraulic pumps 94 and 95 (see FIG. 2) may be mounted in association with the engine shaft 81a and operatively driven thereby at a slower speed than output shaft 81.
  • the pump 95 is supplied with oil from the pump in the casing 78 and delivers oil to all control circuits: direction control, vapor control, torque control and air and fuel delivery controls.
  • the pressure in this circuit is essentially variable and is determined by the relief valve 102 operated by the accelerator pedal ltll.
  • Exhaust oil from valve 102 is directed to the lubrication circuit.
  • the pump 95 is also supplying pressurized oil to a second stage hydraulic pump 94 which feeds the oil to the power circuits.
  • the first function of the pump 94 is to charge or recharge the accumulator 99 at high pressure controlled by the sequence and relief value 104 and to operate the motor pump 22, acting as a motor, to drive the condenser-generator-fan assembly A and B and to drive pump 220 through a flow control valve 105 which controls the speed of the condenser-generator.
  • the sequence relief valve 104 is set for lower pressure limit to supply the motor-pump 22 and accessories such as power steering, windshield wipers, etc. It will be noted that in this flow circuit the pumps 94 and 95 are Illlll operated by the engine shaft and do not operate while the engine is standing still.
  • the condensengenerator assembly and the fuel pump 22a are driven by the turbine li and the motor pump 22, acting as a pump, supplies oil to all accessories, control circuits and lubrication.
  • the motor pump 22 rotates the condensergenerator at higher speed for full power than does the turbine M which is operative only during idling periods.
  • a normally closed solenoid valve 100 is opened for a short time to permit oil from the accumulator to operate the motor-pump 22, which drives the fuel pump 22a and the condenser-generator assembly.
  • the accumulator could be replaced by an electric starter to drive the motor-pump 22.
  • the nozzle extends, the fuel becomes ignited in the flow of air to commence vapor generation in the then rotating condenser-generator assembly.
  • the motor-pump 22, the fuel pump 22a and the condenser-generator assembly becomes driven from the turbine i9 and the solenoid valve me has been closed.
  • the pump 94 When the engine C is running, the pump 94; recharges the accumulator 99 and drives the motor-pump 22 rotate the condenser-generator assembly, and the turbine 19 is disconnected by a one way clutch (not shown). Under these running conditions vapor to the turbine 19 is shut off by valve 18.
  • the pump 95 supplies oil to the torque control cylinder and to the general lubricating system.
  • the turbine 119 When the engine C is stopped, the turbine 119 is reactivated to drive the motor-pump 22, the fuel pump 22a and the condenser-generator assembly.
  • Fuel feed and air flow to the burner E are automatically regulated in accordance with variations in torque demand of the engine C and the fuel-air mixture is always maintained at the proper ratios for high combustion efficiency with a minimum of pollutants in the exhaust gases.
  • a pedal Elli acting through a valve W2, controls the hydraulic cylinder 98 to vary the torque of the engine by oscillating the ring gear 79; and the direction of rotation of the engine is controlled by a three-position selector valve lltlllil that includes a neutral position to stop indirectly vapor flow to the engine, a forward position to permit vapor to flow only to the forward drive inlet ports of the engine and a reverse position to permit vapor to flow only to the reverse drive inlet ports of the engine.
  • the valve 103 controls oil flow to cylinder 98 and oil actuated by oil-motor 118a directional valve l8.
  • the power plant also may be started up through the use of a battery powered motor-generator geared to the motor-pump 22. After start up the motor-generator serves to recharge the battery during operation'of the power plant. Whenever such a starting system is employed, the accumulator 99 will be unnecessary and may be eliminated.
  • HG. 116 of the drawings somewhat schematically illustrates how a power plant constructed in accordance with this invention may be used for constant speedconstant torque applications such as those required for aircraft propulsion units or for electric generators.
  • an aircraft installation has been shown for convenience.
  • the vapor condenser A and vapor generator B are assemblied into a generally cylindriform structure that is rotated at about 4,000 R.P.M. on a horizontal axis.
  • High pressure vapor from the generator is supplied to a turbine T through which it expands and is exhausted back into the vapor condenser A.
  • the turbine T which operates at 30,000 R.P.M., is reduction gear-connected to the condenser-generator assembly which in turn is reduction gear-connected to the propeller to drive same at about 2,000 R.P.M.
  • the reduction gearing between the turbine and the condenser-generator assembly also provides an 8,000 R.P.M. take off to drive the accessories.
  • an air conditioning auxiliary unit may be operated by tapping high pressure vapor from a suitable location, cooling same in a separate radiator, expanding same through an evaporater in the vehicle cab or other location and then feeding the expanded vapor back into the condenser portion of the system.
  • Exhaust air from the rotary condenser may be used to supply heat to the vehicle cab or other location.
  • thermodynamic efficiency opinions vary in this field and several, very often contradictory, statements are to be found. Many researchers are still inclined to pick fluids with characteristics which require economizers, reheaters, etc., as a result of their deeply entrenched training from steam engines.
  • the ideal fluid temperature limits should be set with an upper limit compatible with the materials employed in the equipment and the lower limit a condensing temperature that is compatible with the existing atmospheric temperature if the condenser is to be aircooled.
  • the condensing temperature should be between F and 100 F, depending on available air temperature (the lower, the better for efficiency).
  • the adiabatic expansion line along which the cycle is operating should run parallel to or into the saturated vapor line at the condensing point and the vapor should be saturated or dry at this point.
  • the operating pressure should be as high as possible or compatible with the allowable stress in the equipment.
  • the fluid should mainly be chosen because of its ability to provide the maximum efficiency within the operating limits of the system. This is measured by the ratio of the available energy during expansion over the energy stored by the fluid during preheating, evaporation and superheating. This ratio is very low with steam, for example, and much higher with many of the fluorocarbons and chlorocarbons.
  • the specific gravity of the liquid should be high enough to achieve the desired pressure at minimum speed and liquid height.
  • the height of the column of liquid in 13 must be maintained short enough to limit the overall diameter of the system and the radius of rotation must be maintained as small as possible for the same reason.
  • the vessels containing the liquid are also subjected to centrifugal forces developed within their walls which creates stress due to the fluid pressure and particularly a high temperatures which reduce their capability to withstand the stresses.
  • the adabiatic expansion line should run parallel to or across the saturation line at the exhaust point.
  • the condensing temperature should be between 0 F and F.
  • the operation should be at a high pressure of about 500 psi and a temperature of about 500 F which will allow a critical point of these conditions at about 600 psi and 600 F.
  • the specific gravity of the fluid should be at a minimum of 1.4 and the molecular weight should be a maximum of 190
  • the molecular limitation does not apply for the turbine type embodiment shown in FIG. 16.
  • carbon tetrachloride which is the desirable fluid for certain aspects has a melting point of approximately 9.5 F, which would create difficulty under many climatic contions.
  • the melting point of the mixture would be appreciably lower than carbon tetrachloride by itself and yet the other desirable characteristics of the carbon tetrachloride would not be changed appreciably. It is thus contemplated that mixture of most of the fluids disclosed herein would be advantageous in certain circumstances.
  • the fluid mixtures are applicable to any flash boiler situation as well as the instant evaporator shown.
  • a rotary vane engine including, a stationary rotor cage having a cylindrical bore; a rotor including a shaft rotatably mounted along the axis of said bore and provided at one end with a set of three radial vanes located apart and provided at its other end with a radial slotted crank arm; a first sleeve shaft rotatably mounted on said first shaft and provided at one end with a second set of three radial vanes located l20 apart and in juxtaposition to the vanes of said first set and provided at its other end with a radial slotted crank arm; a second sleeve shaft rotatably mounted on said first sleeve shaft and provided at one end with a third set of three radial vanes located l20 apart and in juxtaposition to the vanes of said second set and provided at its other end with a radial slotted crank arm; a hypocycloidal planetary gear system positioned adjacent said radial crank arms and including a rotatable internal ring gear and three satellite

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US00094122A 1970-12-01 1970-12-01 Alternating vane type rotary engine with planetary gear system Expired - Lifetime US3744938A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US9412270A 1970-12-01 1970-12-01

Publications (1)

Publication Number Publication Date
US3744938A true US3744938A (en) 1973-07-10

Family

ID=22243194

Family Applications (1)

Application Number Title Priority Date Filing Date
US00094122A Expired - Lifetime US3744938A (en) 1970-12-01 1970-12-01 Alternating vane type rotary engine with planetary gear system

Country Status (7)

Country Link
US (1) US3744938A (fr)
CA (1) CA948861A (fr)
DE (1) DE2159548A1 (fr)
FR (1) FR2117243A5 (fr)
GB (1) GB1382264A (fr)
IT (1) IT945232B (fr)
SE (1) SE387702B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6257196B1 (en) * 1999-09-07 2001-07-10 Alfredo Alvarado Rotary disc engine
US20050217636A1 (en) * 2004-04-06 2005-10-06 Turner Mars S Toric pulsating continuous combustion rotary engine compressor or pump
US20080149067A1 (en) * 2006-12-21 2008-06-26 Kimes John W Powertrain including a rotary IC engine and a continuously variable planetary gear unit
US20080251043A1 (en) * 2007-04-13 2008-10-16 Yan Li Housing wheel engine
US20100003121A1 (en) * 2006-10-12 2010-01-07 Berryann Andrew P Variable area fan nozzle for accommodating a foreign object strike event
US20110132309A1 (en) * 2009-12-07 2011-06-09 Mars Sterling Turner Oscillatory rotary engine
US11428156B2 (en) 2020-06-06 2022-08-30 Anatoli Stanetsky Rotary vane internal combustion engine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2141179B (en) * 1983-05-07 1987-11-11 Roger Stuart Brierley Vapour turbine power plant
FR2607581B1 (fr) * 1986-12-02 1989-01-13 Ancet Victor Convertisseur de chaleur ambiante
PL344336A1 (en) * 1998-05-19 2001-11-05 Sure Power Corp Power system

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1095034A (en) * 1912-10-29 1914-04-28 Antonio Sanchez Rotary internal-combustion engine.
DE533780C (de) * 1926-04-16 1931-09-18 Hans Simmon Roehrenwaermeaustauscher
US2211292A (en) * 1938-11-07 1940-08-13 Gerald E Ryerson Split cycle internal combustion engine
FR873495A (fr) * 1940-06-22 1942-07-09 Machine à palettes rotatives
US2349848A (en) * 1942-12-08 1944-05-30 Davids Robert Brewster Relative motion rotative mechanism
GB653935A (en) * 1947-11-06 1951-05-30 Motala Verkstad Ab Improvements in and relating to recuperative heat exchangers
US2576284A (en) * 1948-02-19 1951-11-27 Crocchi Piero Vapor electricity generator set
GB746350A (en) * 1954-07-16 1956-03-14 William Charles Berrisford Improvements relating to rotary engines
US3203405A (en) * 1961-02-03 1965-08-31 Sabet Huschang Rotary engine
GB1018977A (en) * 1962-03-23 1966-02-02 Alfa Laval Ab Improvements in and relating to apparatus for indirect heat transfer between a liquid and a vapour
US3396632A (en) * 1966-04-19 1968-08-13 Leblanc Michel Volumetric maching suitable for operation as pump, engine, or motor pump
US3476056A (en) * 1968-04-01 1969-11-04 Gen Motors Corp Pump with oscillating vanes

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1095034A (en) * 1912-10-29 1914-04-28 Antonio Sanchez Rotary internal-combustion engine.
DE533780C (de) * 1926-04-16 1931-09-18 Hans Simmon Roehrenwaermeaustauscher
US2211292A (en) * 1938-11-07 1940-08-13 Gerald E Ryerson Split cycle internal combustion engine
FR873495A (fr) * 1940-06-22 1942-07-09 Machine à palettes rotatives
US2349848A (en) * 1942-12-08 1944-05-30 Davids Robert Brewster Relative motion rotative mechanism
GB653935A (en) * 1947-11-06 1951-05-30 Motala Verkstad Ab Improvements in and relating to recuperative heat exchangers
US2576284A (en) * 1948-02-19 1951-11-27 Crocchi Piero Vapor electricity generator set
GB746350A (en) * 1954-07-16 1956-03-14 William Charles Berrisford Improvements relating to rotary engines
US3203405A (en) * 1961-02-03 1965-08-31 Sabet Huschang Rotary engine
GB1018977A (en) * 1962-03-23 1966-02-02 Alfa Laval Ab Improvements in and relating to apparatus for indirect heat transfer between a liquid and a vapour
US3396632A (en) * 1966-04-19 1968-08-13 Leblanc Michel Volumetric maching suitable for operation as pump, engine, or motor pump
US3476056A (en) * 1968-04-01 1969-11-04 Gen Motors Corp Pump with oscillating vanes

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6257196B1 (en) * 1999-09-07 2001-07-10 Alfredo Alvarado Rotary disc engine
US20050217636A1 (en) * 2004-04-06 2005-10-06 Turner Mars S Toric pulsating continuous combustion rotary engine compressor or pump
US20100003121A1 (en) * 2006-10-12 2010-01-07 Berryann Andrew P Variable area fan nozzle for accommodating a foreign object strike event
US8308423B2 (en) * 2006-10-12 2012-11-13 United Technologies Corporation Variable area fan nozzle for accommodating a foreign object strike event
US20080149067A1 (en) * 2006-12-21 2008-06-26 Kimes John W Powertrain including a rotary IC engine and a continuously variable planetary gear unit
US7461626B2 (en) * 2006-12-21 2008-12-09 Ford Global Technologies, Llc Powertrain including a rotary IC engine and a continuously variable planetary gear unit
US20080251043A1 (en) * 2007-04-13 2008-10-16 Yan Li Housing wheel engine
US7730869B2 (en) * 2007-04-13 2010-06-08 Yan Li Housing wheel engine
US20110132309A1 (en) * 2009-12-07 2011-06-09 Mars Sterling Turner Oscillatory rotary engine
US9157323B2 (en) 2009-12-07 2015-10-13 Mars Sterling Turner Oscillatory rotary engine
US11428156B2 (en) 2020-06-06 2022-08-30 Anatoli Stanetsky Rotary vane internal combustion engine

Also Published As

Publication number Publication date
IT945232B (it) 1973-05-10
FR2117243A5 (fr) 1972-07-21
SE387702B (sv) 1976-09-13
GB1382264A (en) 1975-01-29
DE2159548A1 (de) 1972-06-29
CA948861A (en) 1974-06-11

Similar Documents

Publication Publication Date Title
US3774397A (en) Heat engine
US5839270A (en) Sliding-blade rotary air-heat engine with isothermal compression of air
US4010378A (en) Integrated electric generating and space conditioning system
US3771500A (en) Rotary engine
US4437308A (en) Rotary heat engine
US4201058A (en) Method and apparatus for generating steam
US4212162A (en) Constant combustion engine
US3744938A (en) Alternating vane type rotary engine with planetary gear system
JPH09501214A (ja) 蒸気力機関
EP3414439B1 (fr) Agencement de chambre de combustion et système comprenant ledit agencement
WO1987001414A1 (fr) Generateur a arbre de puissance
US5211017A (en) External combustion rotary engine
US4087974A (en) Method and apparatus for generating steam
US3605406A (en) Combined gas and steam power plant
EP3728815B1 (fr) Système et procédé de production d'énergie
JPS5925850B2 (ja) 推進方法および装置
DE2757913A1 (de) Rotierender dampfgenerator
US6854437B1 (en) Continuous flow expandable chamber and dynamic displacement rotary devices
JP2020525710A (ja) 熱サイクルを実現するように構成された熱機械及びかかる熱機械によって熱サイクルを実現する方法
JP6615347B2 (ja) パワー生成のためのシステム及び方法
US3240017A (en) Liquid piston internal combustion engine
WO2000022286A1 (fr) Moteur, pompe et moteur quantique a pistons rotatifs
RU2362881C2 (ru) Многоцилиндровая турбина объемного расширения
CN103953455B (zh) 一种热能转子动力设备及其做功方法
US1725881A (en) Apparatus for operating liquid turbines by means of combustion machines