US3657877A - Tidal regenerator heat engine - Google Patents

Tidal regenerator heat engine Download PDF

Info

Publication number
US3657877A
US3657877A US111331A US3657877DA US3657877A US 3657877 A US3657877 A US 3657877A US 111331 A US111331 A US 111331A US 3657877D A US3657877D A US 3657877DA US 3657877 A US3657877 A US 3657877A
Authority
US
United States
Prior art keywords
piston
level
cylinder
working fluid
pressure
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
US111331A
Other languages
English (en)
Inventor
Fred N Huffman
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.)
Thermo Fisher Scientific Inc
Original Assignee
Thermo Electron Corp
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 Thermo Electron Corp filed Critical Thermo Electron Corp
Application granted granted Critical
Publication of US3657877A publication Critical patent/US3657877A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/0435—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines the engine being of the free piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/045—Controlling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/057—Regenerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
    • F02G2243/38—External regenerators having parallel cylinders, e.g. "Heinrici" engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/70—Liquid pistons
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • AppL NO: 1,331 A heat engine of modified Stirling cycle: configuration utilizing condensable vapor as a working fluid in a variable liquid level regenerator. Condensation and evaporation of the working "60/5053, fluid take place in the Variable liquid level regeneramr Com '2 g tinuously and in a controlled manner.
  • Operation of a conventional Stirling cycle engine is basically dependent upon the contraction and compression of a given quantity of gas at low temperature and its expansion at high temperature.
  • a displacer piston is used to transfer the working gas back and forth between a fixed high temperature zone and a fixed low temperature zone. The gas is heated in the hot zone and, as it expands and flows into the cold zone, it actuates a power piston.
  • the gas In its passage to the cold zone, the gas gives up a large quantity of heat to a regenerator. In the cold zone, the gas contracts and is compressed as the power piston reverses its stroke. The displacer piston then moves the gas back through the regenerator where it picks up heat stored from its previous passage. Because compression takes place at a lower temperature than expansion, a net surplus of work results.
  • the present invention may be considered a form of Rankine cycle engine modified to the extent that it has both vapor and liquid regeneration and neither mechanical valves nor feedpump.
  • one end of each of three parallel cylinders is connected to a common manifold.
  • a power piston reciprocates in one of the cylinders; a displacer piston reciprocates in another of the cylinders; and a tidal regenerator containing working fluid is disposed in the third cylinder.
  • a vaporizer to which heat is applied is disposed at the top of the regenerator, and a condenser from which heat is extracted is disposed at the bottom of the regenerator.
  • thermal storage is provided for by means of a bed of heat retaining elements spaced far enough apart to prevent capillary action.
  • the vapor regenerator is similar to the gas regenerator of a Stirling engine.
  • the condenser is in communication with the so-called cold zone in the displacer piston cylinder below the displacer piston.
  • the vaporizer is connected, preferably through a superheater, to the displacer cylinder hot zone above the displacer piston.
  • the hot zone is actually formed in the manifold which connects the three cylinders and the manifold may incorporate a superheater.
  • the tidal regenerator is a key element of the engine and may consist of a bed of thermal storage elements retained in the cylinder through which the working fluid passes.
  • the level of working fluid in the liquid phase is controlled by the position of the displacer piston.
  • Each level of the bed has a substantially constant characteristic temperature and, if the pressure in the system is higher than the saturation pressure of the fluid corresponding to the temperature at a given level, the working fluid will condense at the liquid surface until the system pressure matches the saturation pressure. If system pressure is lower than the saturation pressure at a given pressure-temperature level, liquid at that level will vaporize until the system pressure matches the saturation pressure.
  • heat may be stored or supplied by the tidal regenerator, and net work output may be derived from the power piston as it is actuated by the large difference (relative to a gas cycle engine such as the Stirling) between vaporizer and condenser pressure.
  • the sequence of operations in the engine may be understood by considering the displacer piston to have been set in a position such that the level of liquid working fluid, or the tidal level, in the regenerator is adjacent the lower or condenser end of the regenerator, (the cold zone).
  • the displacer piston at this time is at the top of its cylinder, and the power pistonis commencing its return stroke toward the top of its cylinder. Pressure within the system corresponds to the relatively low saturation temperature of the condenser.
  • the power piston moves toward the top of its cylinder operating against only low pressure to terminate its return stroke.
  • the displacer piston moves to the bottom of its cylinder, the liquid level is raised through the tidal generator to the vaporizer at the top of the regenerator, (the hot zone).
  • Pressure in the system is now the saturation pressure corresponding to the vaporizer temperature.
  • the difference between the vaporizer pressure and condenser pressure is quite large, as compared to a gas cycle operating between the same source and sink temperatures.
  • the power piston then commences its downward or power stroke. The expansion work of the power piston during its power stroke is much greater than its compression work.
  • FIG. 1 is a semi-schematic outline of an engine in which key components are outlined;
  • FIGS. 2A through 2F are outline drawings of operational stages
  • FIG. 3 is an idealized temperature-entropy diagram of the tidal regenerator heat engine
  • FIGS. 4 through 6 are outlines of alternative engine structures
  • FIG. 7 is a practical tidal regenerator engine incorporating the present invention.
  • FIG. 1 there may be seen three parallel cylinders, a tidal regenerator cylinder 12, a displacement piston cylinder 14 and a power piston cylinder 16 whose upper ends are connected together by a manifold 18.
  • a bed of thermal storage elements 20 consisting, for example, of metal balls held in position throughout the length of the cylinder 12, by means of support layers of open mesh or screening.
  • a displacement piston 22 Within the cylinder 14, and arranged to reciprocate in response to externally applied force, is a displacement piston 22 having a piston rod 24 passing through the bottom wall of the cylinder 14.
  • the displacement piston serves the dual functions of liquid displacement and thermally isolating the vapor and liquid regions of the engine. Suitable: seals would surround the shaft 24 in a practical structure to permit its reciprocating motion without leakage.
  • a con denser 30 At the base of the tidal regenerator cylinder 12, is a con denser 30, and at the top of the cylinder 12 is a vaporizer 32. As indicated by the Qnf and Om symbols, heat is applied to the vaporizer 32 and extracted from the condenser 30. Accordingly, a temperature gradient is established along the length of the cylinder 12.
  • a working fluid which may be simply water, or preferably a fluid mix such as water-ammonia or water-trichloroethanol, is present in the cylinder 12 and its tidal or liquid level is as shown at 34. Above that level, the fluid is in the vapor phase, as is explained in greater detail below.
  • vapor regenerating elements 36 which may be loosely packed or wound metal wire of small diameter or other material having high surface area-low axial conduction characteristics. These elements may be restrained from migration by small bore sleeves comprising the superheater 38 in the manifold 18 and may also be kept from the vaporizer 32 by any suitable barrier which does not interfere with vapor passage.
  • the power piston 26 rises to the top of its cylinder doing little compression work because system pressure is low and vapor swept out of the power piston cylinder 16 and manifold 18 passes through the regenerator cylinder 12 to be condensed in large measure in the condenser 30.
  • the tidal level 34 is in the condenser 30
  • the low system pressure corresponds to the saturation temperature of the condenser.
  • thermodynamic path of the tidal regenerator engine on a temperature-entropy diagram is correlated with the piston configurations in FIG. 3.
  • the somewhat modified engine configuration shown in FIG. 2 is thermodynamically equivalent to that shown in FIG. 1.
  • the combined displacement and vapor-liquid segregation functions of the displacement piston in FIG. 1 are divided between the displacer piston and interface piston in FIG. 2.
  • FIG. 2A shows the positions of the displacer piston 22, interface piston 94 and power piston 26 at the end of the return stroke.
  • the displacer piston 22 is at the bottom of its stroke and the power piston 26 is at the top of its stroke. Note that in all cases the motion of the interface piston 94 is hydraulically coupled to that of the power piston 26.
  • the tidal level is in the condenser 30, and the low system pressure corresponds to the saturation temperature of the condenser 30. These conditions correspond to state point A in FIG. 3.
  • FIG. 2B illustrates the beginning of the power stroke initiated by the transition of the displacer piston 22 to the top of its stroke.
  • the transition moves the tidal level from the condenser 30 to the boiler (or vaporizer) 32.
  • the system pressure throughout the entire engine is the saturation pressure corresponding to the temperature of the boiler 32.
  • FIG. 2F illustrates the return or compression stroke of the power piston 26, as it sweeps the vapor from the interface cylinder, doing very little work against low system pressure. This condensation process, indicated by the line F in F IG. 3, is terminated in FIG. 2A thus recommencing the cycle.
  • FIGS. 4 through 6 various configurations of the tidal regenerator engine are shown. These may be broadly classified into two groups: (I) doubly loaded piston machines and (2) displacement piston machines.
  • FIG. 4 illustrates a doubly loaded piston machine in which the top of the vaporizer 32 is connected only to a power piston cylinder 16, and the condenser 30 is connected to another power piston cylinder 16a. Between the vaporizer and the condenser is the tidal regenerator 12. Both power pistons are connected to a common crankshaft in the manner of a Stirling engine alpha configuration, as defined by Rider.
  • FIG. 5 a displacement piston machine is illustrated.
  • both the displacer piston 22 and the power piston 26 operate in the same cylinder, the vaporizer 32 communicating with the cylinder 16 above the displacer piston 22, and the condenser 30 communicating with the same cylinder below the displacement piston but above the power piston 26.
  • the power output and timing of the pistons are completely analgous to those of the beta configuration of the Stirling engine.
  • FIG. 7 illustrates a practical embodiment of the present invention which combines mechanical simplicity and efficiency of operation.
  • a tidal regenerator assembly is provided, and it includes liquid regenerator 72 which is made of relatively small-bore, thin-wall, low-thermal conductivity tubing, interposed between a boiler or vaporizer 74 and a condenser 76. It is desirable that the liquid regenerator 72 have such characteristics and be of the design mentioned in order that heat losses may be limited.
  • liquid regenerator tube 72 Within the liquid regenerator tube 72, a quantity of material such as metal wool is packed to enhance cooling and heating of the working fluid which passes through the regenerator as is explained in greater detail below.
  • a quantity of brazed balls Within the boiler 74, there may be disposed a quantity of brazed balls to enlarge hot surface area from which better vaporization of the working fluid may be had.
  • the condenser 76 may contain a similar quantity of brazed balls 82 which similarly enhance condensation of the vapor.
  • a U-shaped vapor regenerator 84 Connected to the top of the boiler is a U-shaped vapor regenerator 84 containing a quantity of high surface-area, low axial-conduction material such as loosely wound, smalldiameter wire 86.
  • the purpose of the wire is to economize on overall thermal input by conserving a portion of the vapor superheat from previous cycles for use in a given cycle, as will also be explained in greater detail.
  • a superheater 88 At the right hand extremity of the vapor regenerator 84, is a superheater 88 which may also contain brazed balls for improving cycle efficiency by superheating the vapor.
  • a generally dumb-bell shaped interface piston assembly is connected to the superheater. At the top of the assembly is a cylinder 89 of relatively large bore to the interior upper surface of which a vapor bellows 90 is sealed. The superheater 88 is in communication with the interior of the vapor bellows 90,
  • the large bore cylinder 89 is connected to a concentric cylinder 92 of smaller bore within which a thermal isthmus piston 94 reciprocates. Hydraulic coupling of displacement of the end of the bellows 90 to the thermal isthmus piston 94 is effected by an interface fluid 95 of low vapor pressure and good thermal stability which fills the cylinder 89 and the upper portion of the cylinder 92. The same fluid 95 pressure-balances the bellows 90, thereby adding to its life and reliability.
  • Another large bore cylinder 96 is connected to the lower end of the smaller cylinder 92.
  • a fluid bellows 98 is sealed, and another interface liquid 99 is provided between the piston 94 and the bellows 98, serving a function similar to that of the fluid 95.
  • fluids 9S and 99 will be of the same composition.
  • a pressure balance line 100 connects the lower portion of the cylinder 96 with a cylinder 102 within which there is sealed a displacer diaphragm 104.
  • a binary solenoid 106 is mechanically connected directly to the center of the displacer diaphragm 104 by means of a shaft 108. Action of the binary solenoid 106 may be controlled electrically by an electronic logic module 112. Working fluid in the regenerator section is visible above the diaphragm 104.
  • bellows and diaphragm instead of sliding piston seals eliminates leakage losses. Scale factors are such that leakage losses are particularly severe in small engines.
  • a hydraulic line 114 is connected at the base of the cylinder 98 to exemplify one of the mechanisms by which power takeoff may be effected.
  • the line may be coupled to any suitable utilization or other hydraulically actuatable element.
  • Other power take-offs are feasible, but the illustrated system has features such as sealed coupling to the engine which make it attractive.
  • the electronic logic module 112 may be a conventional solid state circuit to provide current pulses to the solenoid 106.
  • the solenoid 106 in turn operates upon the displacer diaphragm 104 to move the level of liquid working fluid back and forth between the condenser 76 and the boiler 74.
  • the pressure balance line 100 provides gross pressure balance within the system except for the relatively small pressure differentials which result from the small fluid flow forces.
  • the presence of the pressure balance line 100 is particularly advantageous in that it allows the tidal level to be shifted with a minimum expenditure of energy by the binary solenoid.
  • the binary solenoid may be of the latching type or equipped with a permanent magnet to hold it in either of the positions which it assumes without power expenditure.
  • the electronic module 112 supplies programmed pulses to energize the solenoid 106 which moves the diaphragm 104 upwardly or downwardly.
  • the diaphragm 104 is made preferably of sheet metal or an elastomer, and its size and length of throw in the relatively large cylinder 102 is sufficient to move the tidal level from one end of the relatively small tidal regenerator cylinder 72 to the other end, or, from the boiler or vaporizer 74 to the condenser 76 and vice versa.
  • Heat is, of course, applied to the vaporizer 74 and to the superheater 88 and extracted from the condenser 76.
  • the working fluid is cycled to create minimum and maximum pressure alternately with resultant flexing of the bellows 90 and reciprocation of the isthmus piston 94. That reciprocation is connected into useful work output through the bellows 98 to the hydraulic line 114.
  • the working fluid may be any one of numerous materials or mixtures of materials. For example, a mix of 61 percent ammonia and 39' percent water can be used with greater efficiency than water alone. Various liquid metals and organics are also suitable. In some instances, working fluid may be utilized in the supercritical region for improved efiiciency.
  • the tidal regenerator engine would be especially suitable for: (l) circulating heated water through a divers suit, (2) underwater propulsion (either propeller or jet), (3) underwater hydraulic tool power supply, (4) power generators, (5) implantable circulatory support systems and (6) remote pumping and terrestrial propulsion.
  • a heat engine comprising a closed system, a condensable vapor serving as a working fluid in said closed system, a tidal regenerator, forming a part of said closed system, means for establishing a temperature gradient across said regenerator, means for alternately establishing the level of said working fluid in its liquid phase at points of high temperature and at points of low temperature in said tidal regenerator, pressure in said closed system being relatively high when said level is at said points of high temperature and relatively low when said level is at said points of low temperature, and means responsive to changes of said pressure communicating with said system for converting said changes to mechanical energy.
  • a heat engine as defined in claim 1 wherein said closed system includes a vaporizer to which heat is applied and a condenser from which heat is extracted disposed at opposite ends of said tidal regenerator, whereby said temperature gradient is established, said system further comprising a control system for actuating said means for alternately establishing the level of said working fluid in its liquid phase, whereby said level is alternately substantially in said vaporizer and substantially in said condenser, pressure in said closed system being relatively high when said level is in said vaporizer and relatively low when said level is in said condenser.
  • a heat engine as defined in claim 1 wherein said means for alternately establishing the level of said working fluid in its liquid phase at points of high temperature and at points of low temperature comprises a displacement cylinder for said work ing fluid, a displacement piston reciprocable in said displacement cylinder, and means for actuating said displacement piston to move said working fluid through said engine.
  • a heat engine as defined in claim 4 wherein said means for actuating said displacement piston comprises means for generating electrical pulses and an electromechanical converter responsive to said pulse generating means connected to and driving said piston.
  • a heat engine as defined in claim 1 wherein said means responsive to changes of said pressure communicating with said system for converting said changes to mechanical energy comprises a power cylinder and a power piston reciprocable therein, said power piston being driven in one direction by said relatively high pressure in said system and returning in the other direction against said relatively low pressure in said system.
  • said means for alternately establishing the level of said working fluid in its liquid phase at points of high temperature and at points of low temperature includes an interface cylinder and an interface piston reciprocable in said interface cylinder, a displacement cylinder and a displacement piston reciprocable in said displacement cylinder, and said means responsive to changes of original positions in their respective cylinders generating output power from said power piston, means for actuating said displacement piston in the opposite directions to move said level of working fluid to a point of low temperature and low pressure, whereby said interface piston and said power piston move in the other direction against low pressure in their respective cylinder to resume their original positions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
US111331A 1971-02-01 1971-02-01 Tidal regenerator heat engine Expired - Lifetime US3657877A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11133171A 1971-02-01 1971-02-01

Publications (1)

Publication Number Publication Date
US3657877A true US3657877A (en) 1972-04-25

Family

ID=22337884

Family Applications (1)

Application Number Title Priority Date Filing Date
US111331A Expired - Lifetime US3657877A (en) 1971-02-01 1971-02-01 Tidal regenerator heat engine

Country Status (8)

Country Link
US (1) US3657877A (fr)
JP (1) JPS515141B1 (fr)
CA (1) CA938114A (fr)
DE (1) DE2164224C3 (fr)
FR (1) FR2124979A5 (fr)
GB (1) GB1358141A (fr)
IT (1) IT947146B (fr)
SE (1) SE377711B (fr)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3744245A (en) * 1971-06-21 1973-07-10 D Kelly Closed cycle rotary engine system
US3765799A (en) * 1972-05-01 1973-10-16 A Ledner Thermal-gravity fluid pumping method and apparatus
US3984982A (en) * 1975-06-06 1976-10-12 Thermo Electron Corporation Annular tidal regenerator heat engine
US3986360A (en) * 1975-06-06 1976-10-19 Thermo Electron Corporation Expansion tidal regenerator heat engine
US4413475A (en) * 1982-07-28 1983-11-08 Moscrip William M Thermodynamic working fluids for Stirling-cycle, reciprocating thermal machines
US4794752A (en) * 1987-05-14 1989-01-03 Redderson Roy H Vapor stirling heat machine
US20080282707A1 (en) * 2007-05-16 2008-11-20 Raytheon Company Cryocooler with moving piston and moving cylinder
BE1018375A3 (nl) * 2008-10-30 2010-09-07 Smet Erick Johan Verbeterde inrichting voor de omzetting van thermische in mechanische energie.
FR2966203A1 (fr) * 2010-10-15 2012-04-20 Pyraine Dispositif thermodynamique de type stirling
EP2453126A1 (fr) * 2010-11-16 2012-05-16 Ago Ag Energie + Anlagen Procédé de fonctionnement de deux processus de moteurs Stirling et dispositif doté de deux machines à moteurs Stirling
US20120174585A1 (en) * 2009-08-11 2012-07-12 New Malone Company Limited Closed loop thermodynamic machine
CN103470398A (zh) * 2012-08-25 2013-12-25 摩尔动力(北京)技术股份有限公司 差时相循环发动机
US20140345269A1 (en) * 2013-05-27 2014-11-27 Neemat Frem Fluid expansion engine
WO2015188757A1 (fr) * 2014-06-11 2015-12-17 新疆阳光动力能源科技有限公司 Moteur à pistons à liquide à sortie d'air automatique
CN109956509A (zh) * 2017-12-25 2019-07-02 北京佑陆科技有限公司 由风力机驱动的基于开式斯特林循环的海水淡化系统
US10422329B2 (en) 2017-08-14 2019-09-24 Raytheon Company Push-pull compressor having ultra-high efficiency for cryocoolers or other systems

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57144752U (fr) * 1981-03-07 1982-09-11
JPS58112855A (ja) * 1981-12-28 1983-07-05 Nissan Shatai Co Ltd ワイパ駆動モ−ド制御装置
JPS58112854A (ja) * 1981-12-28 1983-07-05 Nissan Shatai Co Ltd 間欠ワイパ駆動制御装置
DE102012111410B4 (de) * 2012-11-26 2014-10-09 Wabco Gmbh Wärmekraftmaschine
DE102017128254A1 (de) * 2017-11-29 2019-05-29 Gesellschaft zur Förderung von Medizin-, Bio- und Umwelttechnologien e.V. Wärmetauscher mit konstruktionsseitiger Anpassung an erhöhte Lastanforderungen, insbesondere für einen Hochleistungsniedrigtemperatur-Stirlingmotor

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3487635A (en) * 1966-04-14 1970-01-06 Philips Corp Device for converting mechanical energy into heat energy or conversely

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3487635A (en) * 1966-04-14 1970-01-06 Philips Corp Device for converting mechanical energy into heat energy or conversely

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3744245A (en) * 1971-06-21 1973-07-10 D Kelly Closed cycle rotary engine system
US3765799A (en) * 1972-05-01 1973-10-16 A Ledner Thermal-gravity fluid pumping method and apparatus
US3984982A (en) * 1975-06-06 1976-10-12 Thermo Electron Corporation Annular tidal regenerator heat engine
US3986360A (en) * 1975-06-06 1976-10-19 Thermo Electron Corporation Expansion tidal regenerator heat engine
US4413475A (en) * 1982-07-28 1983-11-08 Moscrip William M Thermodynamic working fluids for Stirling-cycle, reciprocating thermal machines
US4794752A (en) * 1987-05-14 1989-01-03 Redderson Roy H Vapor stirling heat machine
US20080282707A1 (en) * 2007-05-16 2008-11-20 Raytheon Company Cryocooler with moving piston and moving cylinder
US8490414B2 (en) * 2007-05-16 2013-07-23 Raytheon Company Cryocooler with moving piston and moving cylinder
BE1018375A3 (nl) * 2008-10-30 2010-09-07 Smet Erick Johan Verbeterde inrichting voor de omzetting van thermische in mechanische energie.
US20120174585A1 (en) * 2009-08-11 2012-07-12 New Malone Company Limited Closed loop thermodynamic machine
FR2966203A1 (fr) * 2010-10-15 2012-04-20 Pyraine Dispositif thermodynamique de type stirling
EP2453126A1 (fr) * 2010-11-16 2012-05-16 Ago Ag Energie + Anlagen Procédé de fonctionnement de deux processus de moteurs Stirling et dispositif doté de deux machines à moteurs Stirling
CN103470398A (zh) * 2012-08-25 2013-12-25 摩尔动力(北京)技术股份有限公司 差时相循环发动机
US20140345269A1 (en) * 2013-05-27 2014-11-27 Neemat Frem Fluid expansion engine
US9598959B2 (en) * 2013-05-27 2017-03-21 Neemat Frem Fluid expansion engine
WO2015188757A1 (fr) * 2014-06-11 2015-12-17 新疆阳光动力能源科技有限公司 Moteur à pistons à liquide à sortie d'air automatique
US10422329B2 (en) 2017-08-14 2019-09-24 Raytheon Company Push-pull compressor having ultra-high efficiency for cryocoolers or other systems
US10738772B2 (en) 2017-08-14 2020-08-11 Raytheon Company Push-pull compressor having ultra-high efficiency for cryocoolers or other systems
CN109956509A (zh) * 2017-12-25 2019-07-02 北京佑陆科技有限公司 由风力机驱动的基于开式斯特林循环的海水淡化系统

Also Published As

Publication number Publication date
SE377711B (fr) 1975-07-21
JPS515141B1 (fr) 1976-02-17
GB1358141A (en) 1974-06-26
DE2164224B2 (de) 1979-07-19
IT947146B (it) 1973-05-21
CA938114A (en) 1973-12-11
FR2124979A5 (fr) 1972-09-22
DE2164224C3 (de) 1980-03-27
DE2164224A1 (de) 1972-08-10

Similar Documents

Publication Publication Date Title
US3657877A (en) Tidal regenerator heat engine
US3604821A (en) Stirling cycle amplifying machine
US8065876B2 (en) Heat engine improvements
US4044558A (en) Thermal oscillator
JP4411829B2 (ja) 蒸気エンジン
US3996745A (en) Stirling cycle type engine and method of operation
US3400281A (en) Stirling cycle drive for an electrokinetic transducer
US4745749A (en) Solar powered free-piston stirling engine
US2484392A (en) Hot-air engine actuated refrigerating apparatus
US4455826A (en) Thermodynamic machine and method
WO2002088536A1 (fr) Moteur a piston fluidique
US3248870A (en) Stirling cycle engine divided into a pressure generating unit and energy converting unit
US3971230A (en) Stirling cycle engine and refrigeration systems
AU2003266179A1 (en) Thermohydrodynamic power amplifier
WO1986006225A1 (fr) Generateur magnetohydrodynamique a metal liquide a action reciproque
JP2005537433A5 (fr)
US3986360A (en) Expansion tidal regenerator heat engine
US4413473A (en) Heat transfer components for Stirling-cycle, reciprocating thermal machines
US4945725A (en) Differential-area piston type mixed-phase motors
US6474058B1 (en) Warren cycle engine
US3478511A (en) Closed-cycle gas engine
US3815363A (en) Multiple cycle tidal regenerator engine
US3220178A (en) Heat engine
US3126348A (en) Gaseous medium for a hot-gas reciprocating apparatus
US3984982A (en) Annular tidal regenerator heat engine