WO1982004098A1 - Fluides thermodynamiques de travail pour machines thermiques, a cycle stirling, a mouvement alternatif - Google Patents

Fluides thermodynamiques de travail pour machines thermiques, a cycle stirling, a mouvement alternatif Download PDF

Info

Publication number
WO1982004098A1
WO1982004098A1 PCT/US1982/000648 US8200648W WO8204098A1 WO 1982004098 A1 WO1982004098 A1 WO 1982004098A1 US 8200648 W US8200648 W US 8200648W WO 8204098 A1 WO8204098 A1 WO 8204098A1
Authority
WO
WIPO (PCT)
Prior art keywords
working fluid
cycle
stirling
working
fluid
Prior art date
Application number
PCT/US1982/000648
Other languages
English (en)
Inventor
William Matthew Moscrip
Original Assignee
William Matthew Moscrip
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 William Matthew Moscrip filed Critical William Matthew Moscrip
Priority to DE8282902015T priority Critical patent/DE3275577D1/de
Priority to AU85840/82A priority patent/AU8584082A/en
Priority to AT82902015T priority patent/ATE25746T1/de
Publication of WO1982004098A1 publication Critical patent/WO1982004098A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • 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
    • F02G1/044—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 having at least two working members, e.g. pistons, delivering power output
    • 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
    • F02G1/06—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
    • F02G2244/00—Machines having two pistons
    • F02G2244/02—Single-acting two piston engines
    • F02G2244/06—Single-acting two piston engines of stationary cylinder type
    • F02G2244/12—Single-acting two piston engines of stationary cylinder type having opposed pistons
    • 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
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines

Definitions

  • This invention relates to Stirling-cycle engines, also known as regenerative thermal machines, and more particularly to a new family of thermodynamic working fluids for such machines.
  • the working fluids of the present invention are specifically selected with regard to whether or not they possess a high dynamic heat transfer coefficient, as defined by knovm empirical relations for heat transfer in turbulent flows, in addition to other requisite thermophysical properties such as chemical inertness and thermal stability.
  • a Stirling-cycle engine is a machine which operates on a closed regenerative thermodynamic cycle, with periodic compression and expansion of a gaseous working fluid at different temperature levels, and where the flow is controlled by volume changes in such a way as to produce a net conversion of heat to work, or vice versa.
  • the regenerator is a device which in prior art takes the forta of a porous mass of metal in an insulated duct. This mass takes up heat from the working fluid during one part of the cycle, temporarily stores it within the machine until a later part of the cycle, and subsequently returns it to the working fluid prior to the start of the next cycle.
  • the regenerator may be thought of as an oscillatory thermodynamic sponge, alternately absorbing and releasing heat with complete reversibility and no loss.
  • thermodynamic system A reversible process for a thermodynamic system is an ideal process, which once having taken place, can be reversed without causing a change in either the system or its surroundings.
  • Regenerative processes are reversible in that they involve reversible heat transfer and storage; their importance derives from the fact that idealized reversible heat transfer is closely approximated by the regenerators of actual machines.
  • the Stirling engine is the only practical example of reversible heat engine which can be operated either as a prime mover or as a heat pump. Background
  • the invention comprises fundamental concepts and material properties which are used in combination to form a new and less complicated technology base for the development of improved Stirling-Cycle machines, specifically including the following: (1) working fluids other than hydrogen, helium, or air, namely certain fluorine compounds exemplified by by sulfur hexafluoride, perfluorobutane, perfluoropropane, and octafluorocyclobutane, which provide an increased dynamic heat transfer coefficient yet are nonflammable, nontoxic, and easily liquefied; and (2) an engine power level control subsystem by which the r ⁇ e-an system working pressure, and thereby the instantaneous power level of the engine, is conveniently varied by the hydraulic injection or ejection of condensed working fluid through a special heat exchanger to be known as the reservoir cooler.
  • working fluids other than hydrogen, helium, or air namely certain fluorine compounds exemplified by by sulfur hexafluoride, perfluorobutane, perfluoropropan
  • thermodynamic working fluids for Stirling-cycle, reciprocating, thermal machines other than the usual hydrogen, helium, or air which possess increased dynamic heat transfer coefficients; have a critical temperature somewhat above the minimum ambient temperature of the available heat sink yet somewhat below the designated heat rejection temperature of the cycle as maintained within the engine cooler; and which are also nonflammable, nontoxic, and inexpensive, inert, and of low viscosity.
  • FIG. 1 is an illustration of the operational sequence of events during one complete cycle of an idealized singleacting two-piston Stirling engine used in the prime mover mode;
  • FIG. 2(a) and FIG. 2(b) are schematics which illustrate the idealized pressure-volume and temperature-entropy diagrams of the then ⁇ odynaraic cycle of the working fluid in the same machine depicted by FIG. 1;
  • FIG. 2(c) is a pressure volume diagram which depicts the working of an actual machine;
  • FIG. 3 is a bar graph comparison of the dynamic heat transfer coefficient calculated for various gaseous working fluids relative to air.
  • FIG. 4 is a schematic representation of means for controlling the instantaneous power level of a Stirling-cycle machine by adjusting the mean operating pressure.
  • numeral 1 designates an idealized version of a two-piston Stirling-cycle prime mover.
  • a conceptually constant mass of pressurized gaseous working fluid occupies the working volume between the compression piston 2 and the expansion piston 3.
  • the total working volume is comprised by compression space 4, regenerator 5, and expansion space 6.
  • a portion of compression space 4 is continually cooled by cooler 7, while a portion of expansion space 6 is continually heated by heater 8.
  • Arrows 9 are intended to represent the input of heat by conduction, convection, or radiation. Escape of fluid from the working volume is prevented by the piston seals 10.
  • regenerator 5 yields stored heat to the working fluid as it is transferred to expansion space 6 with the volume remaining constant. The temperature and pressure rise to their maximum levels.
  • regenerator 5 recovers heat from the working fluid as it is transferred to compression space 4 with the volume remain ing constant. The temperature and pressure return to the starting levels of the cycle.
  • FIG. 2(a) and FIG. 2(b) wherein the same complete cycle is presented in terms of the pressure-volume diagram and the temperature entropy diagram for the working fluid.
  • the area under a curve on the P-V diagram is a representative measure of the mechanical work added to or removed from the system during the ,,procesp.
  • the area under a curve on a T-S diagram is a measure of the heat transferred to or rejected from the working fluid during the process.
  • One favorable embodiment of the present invention is the utilization of alternative working fluids which provide increased performance, greater safety, and improved reliability. From a historical standpoint there appear to be only three working fluids of significant interest for appli cation in regenerative thermal machines: air, helium, and hydrogen. Air was and still is of interest primarily because of its universal availability. But helium and hydrogen are the normal working fluids of choice in the prior art because their thermophysical properties are such as to permit high rates of heat transfer and flow to occur, with relatively low viscous flow losses, compared to air.
  • the three alternative working fluids suggested by FIG. 3 are nontoxic, nonflammable, and easily liquefied under pressure at room temperature, which leads to improved safety and ease of handling. They are also chemically and thermally stable, and generally possess a much higher molecular weight corr.pared to hydrogen or helium. According to Graham's Law the rate at which gases tend to diffuse through very small openings is inversely propor tional to the square root of their density. Thus these high molecular weight gases present a far less difficult reciprocating seal design problem compared to either hydrogen or helium, and a far greater quantity of makeup fluid can be stored in a given volume as a liquefied gas than as a pressurized gas.
  • Drag (Speed) exp2 x Density x (Size)exp2.
  • the invention proposes the uuilization of the indicated compounds, and others, as alternative working fluid media in the Stirling-cycle engine.
  • the essence of this concept is the novel recognition that such working fluids should be selected primarily with regard to whether or not they exhibit a high dynamic heat transfer coefficient, outstanding chemical and physical inertness, and the requisite critical properties to facilitate liquefaction under normal operating conditions.
  • Another favorable embodiment of the invention is an engine power level control subsystem, to be used in conjunction with the operation of any regenerative thermal machine, by means of which the mean system operating pressure can be rapidly and automatically varied as a function of power demand.
  • the operating power level is normally controlled by simultaneously adjusting both the quantity of heat input to the heater head and the mean working pressure of the cycle, since it is these variables which most directly influence the power level.
  • the first of these is accomplished by means of a combustion control subsystem quite similar in function to the familiar accelerator/throttle linkage of the automotive internal combustion engine, except that the time response is much slower due to the large thermal mass of the heat transfer components.
  • the second however, currently requires a complex pressure control subsystem consisting of pressurized heavy wall stainless steel hydrogen gas bottles; sophisticated servoactuated high pressure flow control valves; an array of essential and specially designed check valves, stop valves, bypass valves, relief valves, gauges, and the like; and a high-capacity, hydrogen-compatible compressor as described in prior art patents filed under Subclass 521 of Class 60. (see for example U.S. Patent No. 3,699,770; No. 3,827,241; or no. 4,030,297).
  • the control subsystems re quired to vary the power level of prior art Stirling-cycle engines are both complicated and costly, and they represent a critical stumbling block to the economical use and the widespread acceptance of these engines. This is particularly true today with respect to prime movers which might be sold in the highly competitive worldwide automotive market.
  • FIG. 4 Attention is now directed to the schematic illustration of FIG. 4 wherein a novel power level control subsystem is depicted which is deliberately intended to operate in a single-component two—phase mode.
  • This system is similar to the prior art in that it operates on the well-known principie that a change in the steady state power level of a
  • Stirling engine is virtually a direct linear function of a change in the mean operating pressure of the gaseous working fluid contained therein. But it is radically different from previous systems in that the working fluid is intended to undergo a change in phase whenever it is added to or withdrawn from the working volume. Thus it is another impoftiant specific teaching of this invention that a rapid transition from a condition of low power demand to some other condition of high power demand may best be accoraplished by the rapid injection of working fluid into the working volume in the form of a virtually incompressible liquid.
  • a power level control subsystem is comprised by a servoactuated variable displacement hydraulic pump 30, a power demand control mechanism or accelerator 32, free piston 34, fluid reservoir 35, reservoir cooler 36, and a plurality of Stirling cycle engine coolers 24.
  • pump 30 forces hydraulic fluid 31 into reservoir 35 which in turn forces piston 34, sealed by oring 33, to move to the right.
  • This action causes the rapid injection of condensed liquid working fluid 37 into the working volume at points of entry contiguous with coolers 24.
  • the change in mean operating pressure is immediate, because the introduction of nearly incompressible liquid medium in this manner instantly lowers the total working volume available to the gaseous medium.
  • Each engine cooler 24 is maintained at a temperature sufficiently low for good Stirling-cycle thermodynamic efficiency, but at a temperature somewhat above Tc so that its function from the standpoint of power control is always that of an evaporator.
  • reservoir cooler 36 and therefore revervoir 35 must be maintained at a temperature somewhat below Tc so that its function is always that of a condenser.
  • the pressure in reservoir 35 is the saturated vapor pressure of the condensed working fluid at that temperature.
  • the closed cycle Stirling prime mover operates on the basis of the difference in temperature in the working fluid between the hot expansion space and the cold compression space, the development of useful power output is not specific to the source of heat available for use. Therefore the design of the heat source can be any one of a large variety of possible types.
  • a rather simple combustion system can be produced, for example, which will cleanly and efficiently burn various kinds of both liquid fuels and gaseous fuels without any modification whatsoever.
  • a single prime mover may be made to operate on regular or premium gasoline, diesel oil, alcohol, crude oil, lubricating oil, olive oil, vegetable oil, propane, butane, natural gas, and synthetic coal gas.
  • automotive prime movers marine prime movers, aeronautical prime movers, astronautical prime movers, industrial prime movers, military prime movers, agricultural prime movers, multifuel prime movers, nonfuel prime movers, portable prime movers, biomedical prime movers, refrigerators, air conditioners, cryogenic cooling engines, residential heat pumps, industrial heat pumps, military heat pumps, water coolers, air compressors, other gas compressors, re mote electric generators, portable electric generators, stationary electric generators, hydroelectric power converters, nuclear power converters, radioisotope power converters, solar power converters, geothermal power converters, ocean thermal power converters, biomass power converters, solid waste power converters, small cogeneration power plants, large cogeneration power plants, remote fluid pumps, portable fluid pumps, stationary fluid pumps, remote power tools, portable power tools, outdoor power tools, underwater power tools, toys and novelties.

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)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

Nouveaux fluides thermodynamiques de travail avec application principale aux machines thermiques a cycle Stirling, a mouvement alternatif, lesquels fluides possedent un plus grand coefficient de transfert de chaleur dynamique que l'hydrogene ou l'helium, et sont a la fois chimiquement inertes et facilement liquefies. Un nouveau sous-systeme de commande du niveau de puissance (Fig. 4) base sur les proprietes thermodynamiques de ces fluides est decrit, et est destine a etre utilise conjointement avec des machines a cycle Stirling; cette nouvelle conception simplifie considerablement les procedures de changement de la pression moyenne de travail du systeme, et par consequent le niveau instantane de puissance de telles machines pendant leur fonctionnement.
PCT/US1982/000648 1981-05-14 1982-05-14 Fluides thermodynamiques de travail pour machines thermiques, a cycle stirling, a mouvement alternatif WO1982004098A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE8282902015T DE3275577D1 (en) 1981-05-14 1982-05-14 Thermodynamic working fluids for stirling-cycle, reciprocating, thermal machines
AU85840/82A AU8584082A (en) 1981-05-14 1982-05-14 Thermodynamic working fluids for stirling-cycle, reciprocating, thermal machines
AT82902015T ATE25746T1 (de) 1981-05-14 1982-05-14 Thermodynamische arbeitsmedien fuer stirlingmotoren.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US26369181A 1981-05-14 1981-05-14
US263691810514 1981-05-14

Publications (1)

Publication Number Publication Date
WO1982004098A1 true WO1982004098A1 (fr) 1982-11-25

Family

ID=23002858

Family Applications (4)

Application Number Title Priority Date Filing Date
PCT/US1982/000648 WO1982004098A1 (fr) 1981-05-14 1982-05-14 Fluides thermodynamiques de travail pour machines thermiques, a cycle stirling, a mouvement alternatif
PCT/US1982/000650 WO1982004100A1 (fr) 1981-05-14 1982-05-14 Structure regeneratrice pour machines thermiques, a mouvement de va-et-vient, a cycle de stirling
PCT/US1982/000649 WO1982004099A1 (fr) 1981-05-14 1982-05-14 Agencements mecaniques pour des machines thermiques, a cycle stirling, a mouvement de va-et-vient
PCT/US1982/000651 WO1982004101A1 (fr) 1981-05-14 1982-05-14 Composants de transfert de chaleur pour machines thermiques, a mouvement de va-et-vient, a cycle de stirling

Family Applications After (3)

Application Number Title Priority Date Filing Date
PCT/US1982/000650 WO1982004100A1 (fr) 1981-05-14 1982-05-14 Structure regeneratrice pour machines thermiques, a mouvement de va-et-vient, a cycle de stirling
PCT/US1982/000649 WO1982004099A1 (fr) 1981-05-14 1982-05-14 Agencements mecaniques pour des machines thermiques, a cycle stirling, a mouvement de va-et-vient
PCT/US1982/000651 WO1982004101A1 (fr) 1981-05-14 1982-05-14 Composants de transfert de chaleur pour machines thermiques, a mouvement de va-et-vient, a cycle de stirling

Country Status (3)

Country Link
EP (4) EP0078849B1 (fr)
DE (4) DE3275577D1 (fr)
WO (4) WO1982004098A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003044355A1 (fr) * 2001-11-19 2003-05-30 Caterpillar Inc. Regenerateur fixe, moteur a pistons alternatifs a regeneration de chaleur
WO2005090770A1 (fr) * 2004-03-19 2005-09-29 Rak Miroslav Machine hydrothermique a recirculation a gaz chaud
CN101988443A (zh) * 2010-10-27 2011-03-23 靳北彪 非共轭零距高低温热源热气机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BG63221B1 (bg) 1997-03-14 2001-06-29 Боян БАХНЕВ Гърбичен двигател
US6282895B1 (en) * 1997-07-14 2001-09-04 Stm Power, Inc. Heat engine heater head assembly

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999388A (en) * 1975-10-08 1976-12-28 Forenade Fabriksverken Power control device
US4030297A (en) * 1976-06-28 1977-06-21 Ford Motor Company Hydrogen compression system for Stirling engine power control
DE2820526A1 (de) * 1978-05-11 1979-11-15 Schneider Christian Dipl Ing Verfahren zum steuern und regeln eines auch mit freischwingendem kolben arbeitenden heissgasmotors

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US766410A (en) * 1903-11-19 1904-08-02 Marshall Alger Motor.
US1229009A (en) * 1915-06-07 1917-06-05 Joseph F Allison Pumping-engine.
US2616668A (en) * 1947-05-30 1952-11-04 Hartford Nat Bank & Trust Co Regenerator
GB715594A (en) * 1951-11-27 1954-09-15 Philips Nv Improvements in thermal regenerators
BE669418A (fr) * 1964-09-11
DE1451156A1 (de) * 1964-09-16 1969-02-06 Linde Ag Waerme- und Stoffaustauschelement
US3403508A (en) * 1966-12-09 1968-10-01 Donald A. Kelly Stirling cycle engine with wave-cam means interconnecting pistons and drive shaft thereof
US3385051A (en) * 1967-02-10 1968-05-28 Donald A. Kelly Stirling cycle engine with two wave cam means, two piston banks and driveshaft
US3407593A (en) * 1967-04-10 1968-10-29 Donald A. Kelly Reciprocating stirling cycle engine with dual wave cam drive
US4084376A (en) * 1969-10-30 1978-04-18 U.S. Philips Corporation Heating system
US3950947A (en) * 1969-12-24 1976-04-20 U.S. Philips Corporation Hot-gas machine comprising a heat transfer device
US3678992A (en) * 1970-08-06 1972-07-25 Philips Corp Thermal regenerator
US3710572A (en) * 1971-01-04 1973-01-16 Textron Inc Thrust chamber
US3913666A (en) * 1972-03-20 1975-10-21 Peter Bayliss Heat resistant wall construction
US3994136A (en) * 1975-07-03 1976-11-30 Josam Manufacturing Co. Hot gas engine
NL7705363A (nl) * 1977-05-16 1978-11-20 Philips Nv Heetgasmotor.
US4183213A (en) * 1977-07-18 1980-01-15 Ford Motor Company Heat exchanger for Stirling engine
SE417448B (sv) * 1979-06-19 1981-03-16 Cmc Ab Modul for uppbyggnad av en dubbelverkande, fyrcylindrig stirling-motor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999388A (en) * 1975-10-08 1976-12-28 Forenade Fabriksverken Power control device
US4030297A (en) * 1976-06-28 1977-06-21 Ford Motor Company Hydrogen compression system for Stirling engine power control
DE2820526A1 (de) * 1978-05-11 1979-11-15 Schneider Christian Dipl Ing Verfahren zum steuern und regeln eines auch mit freischwingendem kolben arbeitenden heissgasmotors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0078847A4 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003044355A1 (fr) * 2001-11-19 2003-05-30 Caterpillar Inc. Regenerateur fixe, moteur a pistons alternatifs a regeneration de chaleur
GB2396665A (en) * 2001-11-19 2004-06-30 Caterpillar Inc Stationary regenerator, regenerated, reciprocating engine
GB2396665B (en) * 2001-11-19 2005-08-10 Caterpillar Inc Stationary regenerator, regenerated, reciprocating engine
WO2005090770A1 (fr) * 2004-03-19 2005-09-29 Rak Miroslav Machine hydrothermique a recirculation a gaz chaud
US7395666B2 (en) 2004-03-19 2008-07-08 Rak Miroslav Thermal hydro-machine on hot gas with recirculation
HRP20040269B1 (en) * 2004-03-19 2010-03-31 Rak Miroslav Thermal hydro-machine on hot gas with recirculation
CN101988443A (zh) * 2010-10-27 2011-03-23 靳北彪 非共轭零距高低温热源热气机

Also Published As

Publication number Publication date
EP0078850A4 (fr) 1985-02-28
EP0078849A4 (fr) 1985-02-28
EP0078847A1 (fr) 1983-05-18
WO1982004099A1 (fr) 1982-11-25
DE3275848D1 (en) 1987-04-30
EP0078850A1 (fr) 1983-05-18
WO1982004101A1 (fr) 1982-11-25
DE3278913D1 (en) 1988-09-22
EP0078849B1 (fr) 1987-03-25
EP0078850B1 (fr) 1988-08-17
DE3275577D1 (en) 1987-04-09
EP0078848A1 (fr) 1983-05-18
EP0078848A4 (fr) 1984-12-11
WO1982004100A1 (fr) 1982-11-25
DE3279652D1 (en) 1989-06-01
EP0078848B1 (fr) 1989-04-26
EP0078847A4 (fr) 1984-12-11
EP0078847B1 (fr) 1987-03-04
EP0078849A1 (fr) 1983-05-18

Similar Documents

Publication Publication Date Title
US4413475A (en) Thermodynamic working fluids for Stirling-cycle, reciprocating thermal machines
US4413474A (en) Mechanical arrangements for Stirling-cycle, reciprocating thermal machines
EP2406485B1 (fr) Moteur thermique avec régénérateur et échange minuté de gaz
US4429732A (en) Regenerator structure for stirling-cycle, reciprocating thermal machines
US6568169B2 (en) Fluidic-piston engine
US4044558A (en) Thermal oscillator
Beale Free piston Stirling engines-some model tests and simulations
US4794752A (en) Vapor stirling heat machine
CA1063360A (fr) Moteur stirling ameliore, et mode de marche
US4462212A (en) Unitary heat engine/heat pump system
US5924305A (en) Thermodynamic system and process for producing heat, refrigeration, or work
US3971230A (en) Stirling cycle engine and refrigeration systems
US5822964A (en) Hot-gas engine electric heater
JP2023082139A (ja) 効率的熱回収エンジン
US4413473A (en) Heat transfer components for Stirling-cycle, reciprocating thermal machines
JP2005537433A (ja) 熱−流体力増幅器
EP0078847B1 (fr) Fluides thermodynamiques de travail pour machines thermiques, a cycle stirling, a mouvement alternatif
Kwasi-Effah et al. Stirling Engine Technology: A Technical Approach to Balance the Use of Renewable and Non-Renewable Energy Sources
CA1226443A (fr) Machines thermiques de type stirling a mouvement alternatif
Getie Numerical modeling and optimization of a regenerative Stirling refrigerating machine for moderate cooling applications
Thombare Stirling Engine Micro-CHP System
RU2005900C1 (ru) Двигатель стерлинга
Aksoy et al. The Thermodynamic Analysis of a Beta Type Rhombic Drive Stirling Engine
Kentfield et al. A simple coal-fired Stirling engine for use as a village power unit
Hossain et al. Fabrication & Performance Test of a Low Temperature Differential Stirling Engine

Legal Events

Date Code Title Description
AK Designated states

Designated state(s): AU BR DK FI JP NO RO SU US

AL Designated countries for regional patents

Designated state(s): AT BE CF CG CH CM DE FR GA GB LU NL SE SN TD TG

WWE Wipo information: entry into national phase

Ref document number: 1982902015

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 1982902015

Country of ref document: EP

WWG Wipo information: grant in national office

Ref document number: 1982902015

Country of ref document: EP