EP0162868A1 - Stirling cycle engine and heat pump. - Google Patents
Stirling cycle engine and heat pump.Info
- Publication number
- EP0162868A1 EP0162868A1 EP84904048A EP84904048A EP0162868A1 EP 0162868 A1 EP0162868 A1 EP 0162868A1 EP 84904048 A EP84904048 A EP 84904048A EP 84904048 A EP84904048 A EP 84904048A EP 0162868 A1 EP0162868 A1 EP 0162868A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- heat
- exchanger assembly
- gas
- cylinder
- 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.)
- Granted
Links
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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
-
- 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
-
- 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
- F02G2254/00—Heat inputs
- F02G2254/30—Heat inputs using solar radiation
-
- 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
- F02G2270/50—Crosshead guiding pistons
Definitions
- the present invention is directed to novel forms of a hot gas engine and heat pump in which heat to be converted to work or to be pumped is applied external to cylinders containing the working gas.
- the present invention is directed to improved forms of a Stirling cycle engine and heat pump.
- the term "heat pump” is used in its generic sense desig ⁇ nating a device which may be used either for heating or refrigeration.
- the present invention is directed to a novel machine utilizing a modified "Stirling cycle".
- the first Stirling cycle machine was invented in 1816 by Robert Stirling. It ran as an engine, turning heat into mechanical energy. Subsequent development has shown that Stirling cycle machines can also be run in reverse, being driven by mechanical energy to act as heat pumps in refrigeration applications. Practical problems, discussed below, have prevented Stirling cycle machines from coming into widespread use in any of their potential applications.
- Conventional Stirling cycle machines operate with working gas such as air, hydrogen or helium. When the Stirling cycle machine is run as an engine, the working gas is compressed while being cooled in the cold space of the engine during the "compression" phase of the cycle.
- the working gas is then permitted to expand into the hot space of the engine where it is heated as it expands during the power stroke phase of the cycle.
- the working gas is then transferred out of the hot space and into the cold space of the engine at constant volume during the "regeneration" phase of the cycle. The cycle then repeats.
- the expansion of the working gas in the hot space of the Stirling cycle machine during the power stroke of the cycle produces work when the machine is run as an engine.
- the compression phase of the cycle absorbs work when the Stirling machine is run as an engine, but it absorbs less work than is generated in the expansion phase of the cycle.
- the excess work is absorbed in part by mechanical and gas friction (including that involved in the transfer/regeneration phase) .
- the remainder of the work is useful work.
- a Stirling cycle machine When run as a heat pump, a Stirling cycle machine requires more energy to compress the working gas during the compression phase of the cycle than is returned during the expansion phase of the cycle because the part of the machine that is absorbing heat from the surroundings (i.e., the expansion space) is colder than the part of the machine where the working gas is com ⁇ pressed (i.e., the compression space).
- the present invention is described below as an engine, with reference to the compression space as the "cold space” and the expansion space as the “hot space”. If the machine were operated as a refrigerator (heat pump) rather than as an engine, temperatures of the compression and expansion space would be reversed. Both when the inyention is used as an engine and as a heat pump, gas entering the expansion space is sub- jected to external heating, and gas entering the compression space is subjected to external cooling.
- Stirling engines normally employ a "regenerator" of knitted wire, wire mesh, or some similar material between the sets of hot and cold tubes.
- the regener ⁇ ator functions by absorbing heat from the gas at.one ti e and returning the heat to the gas at a later time.
- the -regenerator also produces substantial gas friction as the working gas passes back and forth through it, dissipating energy.
- the conventional arrangement also creates a ther odynamic problem in that the working gas is passed through the hot heat-exchanger at times during the cycle when it would be desirable for the working gas to be cooled and through the cold heat exchanger at times when it would be desirable for the working gas to be heated.
- the present invention accomplishes improvements in all of these areas, producing an efficient thermo ⁇ dynamic cycle with mechanical apparatus employing si - pie harmonic motion with reduced gas friction.
- improvements in Stirling engine type devices are obtained by employing two separate volumes of gas which are expanded and compressed through Stirling type cycles, sequentially sharing expansion and compression chambers with one volume undergoing expansion while the other undergoes compression.
- gas enters and exits the expansion space of the engine through dif- ferent ports and a regenerator at the entrance port retains heat of compression and may permit superheating of the working gas in the regenerator.
- FIGS. 1(a), 1(b) and 1(c) illustrate the pressure changes of the working gas in an engine according to the present invention.
- FIG. 2 illustrates a basic arrangement of the invention.
- FIG. 3 illustrates an embodiment of a single cylinder engine according to the present invention, employing dual regenerators and by-pass.
- FIG. 4A illustrates a perspective view of a gate alve usable with the engine of FIG. 3.
- FIG. 4B illustrates a cross-section of a gate valve usable with the engine of FIG. 3.
- FIG. 4C illustrates a poppet valve assembly usable with the engine of FIG. 3.
- the present invention provides an engine employing at least one cylinder, sealed at both ends, fitted with a double-acting piston, and with two or more heat- exchanger assemblies connecting one end of the cylinder to the other end of the cylinder.
- Each heat exchanger assembly contains at least a heater, a cooler, and a valve at each end where it opens into one or the other end of the cylinder.
- Each heat exchanger may also contain one or more regenerators and/or one or more bypasses and bypass valves.
- each heat exchanger assembly participates in a thermodynamic cycle, sharing, in its turn, the assistance of the pis ⁇ ton for the movement of gas.
- the cycles accomplished by all of the heat exchanger assemblies are identical, but interlocked in time sequence.
- the theoretical operation of the cycle in each heat exchanger assembly may be as follows: Stroke 1 (Compression): The working gas is expelled from the compression space of the cylinder into the heat exchanger assembly and thereby compressed from its lowest pressure level during the cycle to a higher level, being cooled as it passes through the cooler during this stroke to minimize the work required to compress it;
- Stroke 2 (Isolation) : The working gas is confined in the heat exchanger assembly in its compressed state, with no change in volume, and no input or output of mechanical work.
- Stroke 3 (Expansion): The working gas is expanded out of the heat exchanger assembly into the expansion space of the cylinder, dropping from its highest pres ⁇ sure to an intermediate pressure, while being heated during this stroke to minimize the pressure drop and maximize the work done, and;
- Stroke 4 (Regeneration): The working gas is moved, with no change in volume, out of the expansion space of the cylinder, through the heat exchanger assembly and into the compression space of the cylinder with no significant input or output of mechanical work, so that it can be compressed again, repeating stroke 1. During this "regeneration" stroke, the working gas is cooled so that its pressure reaches the lowest point in the cycle at the beginning of the compression stroke, thereby reducing the amount of work required to compress the working gas during stroke 1.
- the rising temperature caused by compression of hot gas that was in the heater at the beginning of the compression stroke more than outweighs the low temperature of gas entering the heater from the cooler (or from the optional regenerator) during
- FIG. 1 looks like two triangles, apex to apex, as shown in FIG. 1(b).
- the temperature rise and drop could cancel out perfectly. That would produce the triangle- shaped P/V diagram of FIG. 1(c) which also results theoretically from perfect, instantaneous heat transfer.
- the P/V diagram in Figure 1 could look like 1(a), 1(b), or 1(c). It is conceivable that the same engine, running at different temperature differentials and/or. different operating speeds might at times reflect each of these three P/V diagrams.
- FIG. 1 the area under the compres ⁇ sion curve (stroke 1) is less than the area under the expansion curve (stroke 3), and the difference is the mechanical work output of the engine.
- An elemental embodiment of the invention is shown schematically in FIG. 2.
- a double acting piston 10 travels within an enclosed cylinder 9.
- the piston is connected to a piston rod 11.
- the piston rod 11 is in turn supported against lateral movement by a crosshead (not shown).
- the piston rod 11 connects through a conventional connecting rod (not shown) to a crankshaft (not shown).
- the piston rod passes through a seal 22.
- One end of the cylinder 9 is connected to the other end of the cylinder through heat exchanger assemblies 12 and 13, consisting of, in each instance, a heater (12A, 13A) and a cooler (12B, 13B).
- the heat exchanger assemblies communicate into the expansion space of the cylinder through ports 16, 17 and into the compression space of the cylinder through other ports 18, 19.
- Between each port 16, 17 into the expansion space and its associated heater 12A, 13A is a valve (16A, 17A).
- a valve 18A, 19A Between each port into the compression space and its associated cooler 12B, 13B is a valve 18A, 19A.
- Regenerators 14 located between each heater and cooler are optional.
- the quantity of work ⁇ ing gas that passes through valves 16A and 18A is at all times separated from the quantity of gas that passes through valves 17A and 19A.
- FIG. 3 A preferred embodiment of an engine is shown in FIG. 3.
- a double-acting piston 10 travels within an 25 enclosed cylinder.
- the piston is connected to a piston rod 11.
- the piston rod 11 is in turn connected to a . conventional connecting rod (not shown) which connects to a crankpin and crankshaft (not shown), and is preferably supported against lateral motion by a 30 conventional cross-head (also not shown).
- each heat exchanger 35 assembly consisting of a cooler 12B, 13B, a heater 12A, 13A and a regenerator 14A, 14B, connected in series.
- the regenerator end of each heat exchanger 35 assembly is connected to the hot end of the cylinder through valved ports 16 and 17, accommodating valve means 16A and 17A, respectively.
- the other end of each heat exchanger assembly is connected to the compression valve cylinder ports 18 and 19 accommodating valve means 18A and 19A, respectively.
- Bypass ports 20 and 21 accommodating valve means 20A and 21A, respectively, are provided, connecting the expansion space of the cylinder to each heater exchanger assembly 12, 13, between the cooler 12B, 13B and the heater 12A, 13A.
- a second pair of regenerators 23 and 23B may be provided between the valves 20A and 21A and the cooling sections 12B and 13B.
- working gas flows through the heat exchanger assemblies into the expansion space through valves 16A and 17A, but flows out of the expansion space into the heat exchanger assemblies through valves 20A and 20B.
- the valving sequence is as follows:
- the heaters 12A, 13A are heated by heating means (not shown), such as a combustor, solar energy, and the like.
- the coolers 12B, 13B are cooled by water jackets, air, or other suitable heat sink.
- the cycle of an engine according to the present invention differs from the traditional Stirling cycle in that much higher compression ratios are possible. Since an entire volume of working gas is swept into a heat exchanger assembly and locked there under com ⁇ pression by the valves at each end, the ratio of the swept volume of the cylinder to the volume of the heat exchanger assembly determines the compression ratio. By using a relatively small volume in the heat exchanger assembly high compression may be obtained.
- the high compression attainable with the present engine is desirable in that it permits the engine to generate great power relative to its size.
- the high compression ratio carries with it a penalty in the form of very high pressures in the machine at the conclusion of the compression stroke. This high pressure tends to raise the temperature of the working gas as the compression stroke progresses, increasing the amount of work consumed in compressing the working gas *
- each heat exchanger assembly is arranged to limit the compression heating of the working gas.
- each heat exchanger assembly is accomplished by arranging each heat exchanger assembly so that cold gas from the cold heat exchanger (or center regenerator, if any) is not immediately warmed as it enters the heater, such as, by using heater tubes substantially larger in diameter than those that would be used in a conventional Stirling cycle machine, or even a single heater tube.
- the regenerator and cooler tubes may be designed for rapid heat transfer so that gas enter ⁇ ing either will assume the temperature of the regener ⁇ ator or cooler tubes almost immediately.
- the heater may have heat transfer characteristics such that the gas that is in the heater (12A, 13A) at the beginning of the compression stroke will have approached the temperature of the heater tube by the time that compression begins. Referring to FIG. 3, as the compression stroke progresses, that hot gas will be progressively forced towards the expansion valve (16A or 17A), and, through compression, further heated. To mitigate that effect, the expansion end regenerators (14A, 14B) are interposed between the heater and the ports into the expansion space so that heat from gas that is forced out of the heaters into the expansion end regenerators will be absorbed by the regenerators and the temperature rise will be miti ⁇ gated. With sufficient thermal mass of the regener ⁇ ators, minimal temperature rise will occur in the regenerator during any single cycle.
- gas will be heated to expansion end regenerator temperature as it expands into the expansion space in the cylinder.
- the temperature of that gas will, at least initially, exceed heater temperature. While the gas in the heater will drop in temperature as the expansion stroke progresses, it must pass through the expansion end regenerator on its way into the cylinder and will be heated in that process to a temperature close to or even above maximum heater tube temperature.
- a bypass arrangement similar to that shown for the expansion end may be incorporated into the compression end. If that is done, working gas should enter the compression space through the coolers 12B, 13B, but leave the compression space through bypasses communicating directly with the center-mounted regenerators 23A, 23B.
- valves in direct communication with the expansion space of a high pressure version of the engine will be pressure- sealing in both directions.
- a simple gate valve (FIGS. 4A and 4B) may be used.
- the gate 30 intersects the flow of working gas.
- a hole 31 in the gate lines up with the path of flow, and the gas flows unimpeded.
- a flat plate cuts off the gas flow.
- timing of " valve movements may be synchronized to piston movements by conventional mechanical, electrical or electronic means that sense crankshaft position.
- tubes sets More than two heat exchanger assemblies
- tubes may be used.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Un moteur de type à cycle Stirling est doté d'une pluralité de montages d'échangeur thermique (12 et 13). Chaque montage se compose d'un refroidisseur (12B, 13B), d'un régénérateur (23A, 23B), d'un réchauffeur (12A, 13A) et d'un régénérateur monté en position terminale (14A, 14B) reliés en série. Grâce à l'utilisation de vannes (18A, 19A, 20A, 21A) synchronisées pour s'ouvrir et se fermer dans un ordre spécifique en fonction du mouvement d'un piston (10), deux volumes séparés de gaz sont comprimés, dilatés et transférés à travers des cycles de type Stirling, partageant séquentiellement des chambres de dilatation et de compression, un volume étant soumis à la dilatation pendant que l'autre est soumis à la compression, et un volume étant isolé dans un montage d'échangeur thermique alors que l'autre est transféré à travers l'autre montage d'échangeur thermique d'une extrémité du cylindre à l'autre.A Stirling cycle type engine has a plurality of heat exchanger assemblies (12 and 13). Each assembly consists of a cooler (12B, 13B), a regenerator (23A, 23B), a heater (12A, 13A) and a regenerator mounted in the end position (14A, 14B) connected in series . Thanks to the use of valves (18A, 19A, 20A, 21A) synchronized to open and close in a specific order according to the movement of a piston (10), two separate volumes of gas are compressed, expanded and transferred through Stirling-type cycles, sequentially sharing expansion and compression chambers, one volume being subjected to expansion while the other is subjected to compression, and a volume being isolated in a heat exchanger assembly then that the other is transferred through the other heat exchanger assembly from one end of the cylinder to the other.
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT84904048T ATE43680T1 (en) | 1983-11-02 | 1984-10-29 | STIRLING ENGINE AND HEAT PUMP. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US54819883A | 1983-11-02 | 1983-11-02 | |
US548198 | 1983-11-02 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0162868A1 true EP0162868A1 (en) | 1985-12-04 |
EP0162868A4 EP0162868A4 (en) | 1986-08-21 |
EP0162868B1 EP0162868B1 (en) | 1989-05-31 |
Family
ID=24187817
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19840904048 Expired EP0162868B1 (en) | 1983-11-02 | 1984-10-29 | Stirling cycle engine and heat pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0162868B1 (en) |
JP (1) | JPH071028B2 (en) |
DE (1) | DE3478486D1 (en) |
WO (1) | WO1985001988A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
PL371689A1 (en) * | 2004-12-10 | 2006-06-12 | Piotr Hardt | Multi-valve piston engine with external combustion and inner pressure cooling system as well as method for controlling operation of the piston engine with external combustion and inner pressure cooling system |
JP4520527B2 (en) * | 2009-01-19 | 2010-08-04 | 横浜製機株式会社 | External combustion type closed cycle heat engine |
JP5317942B2 (en) * | 2009-12-07 | 2013-10-16 | 横浜製機株式会社 | External combustion type closed cycle heat engine |
DE102010020325B4 (en) | 2010-05-12 | 2012-09-06 | Christian Daublebsky von Eichhain | Heat engine |
WO2011151888A1 (en) * | 2010-06-01 | 2011-12-08 | 横浜製機株式会社 | External-combustion, closed-cycle thermal engine |
JP5525371B2 (en) * | 2010-08-02 | 2014-06-18 | 横浜製機株式会社 | External combustion type closed cycle heat engine |
SE538808C2 (en) * | 2012-11-20 | 2016-12-06 | Dulob Ab | Hot gas engine |
CN106089612B (en) * | 2016-08-08 | 2018-09-07 | 浙江大学 | A kind of rotating jet flow device, Stirling engine and the operation method of characteristic absorption spectrum |
CN215109061U (en) * | 2019-11-29 | 2021-12-10 | 钟学斌 | Prime mover and water turbine set |
GB2611027B (en) * | 2021-09-17 | 2023-09-27 | Fetu Ltd | Thermodynamic cycle |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1378880A (en) * | 1963-07-29 | 1964-11-20 | Cleveland Pneumatic Ind | piston-cylinder assembly for fluid engines |
FR1453381A (en) * | 1965-07-23 | 1966-06-03 | Philips Nv | Hot gas piston machine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3145527A (en) * | 1962-06-22 | 1964-08-25 | Morgenroth Henri | Scavenging flow circuit for stirling cycle engine |
GB1259653A (en) * | 1969-02-14 | 1972-01-12 | ||
JPS5215947A (en) * | 1975-07-25 | 1977-02-05 | Nissan Motor Co Ltd | External heat thermal engine |
JPS5225952A (en) * | 1975-08-25 | 1977-02-26 | Daihatsu Diesel Kk | Sealing cycle hot gas engine |
JPS5738772A (en) * | 1980-08-20 | 1982-03-03 | Otsuka Pharmaceut Co Ltd | Carbostyril derivative |
-
1984
- 1984-10-29 JP JP59504068A patent/JPH071028B2/en not_active Expired - Lifetime
- 1984-10-29 DE DE8484904048T patent/DE3478486D1/en not_active Expired
- 1984-10-29 EP EP19840904048 patent/EP0162868B1/en not_active Expired
- 1984-10-29 WO PCT/US1984/001731 patent/WO1985001988A1/en active IP Right Grant
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1378880A (en) * | 1963-07-29 | 1964-11-20 | Cleveland Pneumatic Ind | piston-cylinder assembly for fluid engines |
FR1453381A (en) * | 1965-07-23 | 1966-06-03 | Philips Nv | Hot gas piston machine |
Non-Patent Citations (1)
Title |
---|
See also references of WO8501988A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE3478486D1 (en) | 1989-07-06 |
EP0162868A4 (en) | 1986-08-21 |
JPH071028B2 (en) | 1995-01-11 |
WO1985001988A1 (en) | 1985-05-09 |
JPS61500272A (en) | 1986-02-20 |
EP0162868B1 (en) | 1989-05-31 |
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