US3813882A - Hot-gas engines - Google Patents

Hot-gas engines Download PDF

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Publication number
US3813882A
US3813882A US00306558A US30655872A US3813882A US 3813882 A US3813882 A US 3813882A US 00306558 A US00306558 A US 00306558A US 30655872 A US30655872 A US 30655872A US 3813882 A US3813882 A US 3813882A
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United States
Prior art keywords
cylinders
pair
cylinder
overflow path
overflow
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Expired - Lifetime
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US00306558A
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English (en)
Inventor
K Hubschmann
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Caterpillar Energy Solutions GmbH
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Motoren Werke Mannheim AG
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    • 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
    • F02G1/044—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
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines

Definitions

  • a double-acting hot gas engine includes four or a higher even number of cylinders which comprise pairs 30 Foreign Application priority Data whereof the cylinders are phase-displaced through a 180 crank angle.
  • An expanslon chamber of each cyl- Nov. 16, l97l Germany 2156773 mder 15 connected, by way of a heater, a regenerator and a cooler arranged in series, to a compression (gl. chamber of another cylinden At least for partial load 58 Field 615651611IIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIII'6o/24, 525 P Chambers Of each.
  • the invention relates to a method of obtaining loadresponsive regulation of the power of a double-acting hot-gas engine comprising four or a higher even number of cylinders, in which each cylinder contains an expansion chamber and a compression chamber separated by a working piston.
  • each expansion chamber is connected to a compression chamber of another, phasedisplaced cylinder by way of a flowpath which contains a heater, a regenerator and a cooler arranged in series.
  • An object of the present invention is to provide a method of regulation which results in a change of the aforementioned ratio.
  • a method of obtaining load-responsive regulation of the power of a double-acting hot-gas engine which comprises four or a higher even number of cylinders each of which contains an expansion chamber and a compression chamber separated by a working piston and which comprise pairs of cylinders whereof the cylinders of each pair are phase-displaced with respect to each other through a 180 crank angle, the expansion chamber of each cylinder being connected, by way of a flow path containing a heater, a regenerator and a cooler arranged in series with one another, to the compression chamber of another cylinder which is phasedisplaced with respect to the first-mentioned cylinder through a crank angle which is a fraction 180 and the compression chambers of each said pair being intermittently interconnectable by way of an overflow path, comprising, at least for partial load, interconnecting the compression chambers of each said pair by way of the relevant overflow path for a time period extending throughout part of each of successiv working cycles of each said pair, and increasing said time period if the load
  • a combination comprising four or a higher even number of cylinders each of which contains an expansion chamber and a compression chamber separated by a working piston and which comprise pairs of cylinders whereof the cylinders of each pair are phase-displaced with respect to each other through a 180 crank angle, a flow path connecting the expansion chamber of each cylinder to the compression chamber of another cylinder which is phase-displaced with respect to the firstmentioned cylinder, each flow path comprising a heater, a regenerator and a cooler arranged in series with one another, an overflow path whereby the compression chambers of each said pair are interconnectable intermittently, and valve means in each overflow path arranged to open and close the overflow path at intervals.
  • An overflow of working medium thus occurs during each working cycle at least in the range of reduced power.
  • the indicator diagram area and thus the ratio of the maximum pressure to the minimum pressure in the compression chamber and therefore in the associated expansion chamber, is thereby reduced.
  • the change in the area of the diagram may be completed in one working cycle, provided that each overflow path is of a cross-section which permits a virtually unrestricted overflow of working medium between the two compression chambers. Assuming that this is so, the regulation takes place with the same low degree of inertia as in a Diesel engine.
  • a further advantage of this invention resides in the fact that neither additional regulating vessels nor an auxiliary compressor are required for the working medium. When the overflow paths are unrestricted regulation occurs in a virtually loss-free manner.
  • valve means in each overflow path as two shut-off valves disposed one behind the other in the path.
  • FIG. 1 is a diagrammatic illustration of four cylinders of a six-cylinder hot-gas engine
  • FIG. 2 is a diagram showing qualitatively the relationship between the pressures (P) in two interconnectible compression chambers of the engine and the crank DESCRIPTION OF THE PREFERRED EMBODIMENT
  • FIG. I shows only four cylinders I, 2, 3 and 4 of a double-acting six-cylinder hot-gas engine.
  • Each cylinder contains a compression chamber and an expansion chamber 6 separated from each other by a working piston 7.
  • the expansion chamber 6 of each cylinder is connected to a compression chamber 5 of another cylinder which when operating is phase-displaced with respect to the first-mentioned cylinder through a 60 crank angle, the connections being by way of a flow path which contains a heater 8, a regenerator 9 and a cooler It) arranged in series with one another.
  • each cylinder pair I-2, 2-3, 3-4, 4-5 and 6'-l there is connections between the expansion chamber 6 and the compression chamber 5 in the case of each cylinder pair I-2, 2-3, 3-4, 4-5 and 6'-l, the cylinders 5 and 6' not being shown in the drawings.
  • the compression chambers 5 of each pair of cylinders of which the cylinders, when operating, are phase-displaced with respect to each other through a 180 crank angle, are interconnectible through overflow paths, only one of these paths, designated by the numeral II and between the cylinder I and the cylinder 4, being illustrated.
  • the overflow path II can be intermittently closed by shut-off members I2 which are operated in synchronism with the associated pistons '7.
  • the engine contains two further overflow paths, not illustrated, which can be intermittently closed in a corresponding manner and which establish connections between the compression chambers 5 of the cylinder pairs 2-5 and 3-6.
  • the cylinders I, 2, 3 and 4 illustrated, as well as the cylinders 5' and 6 which are not illustrated, are filled with a suitable pressurised medium, usually helium.
  • a suitable pressurised medium usually helium.
  • the compression chambers S are also called cold chambers.
  • the heaters 8 are heated in a manner not illustrated by an external source of heat, e.g., an oil burner.
  • an external source of heat e.g., an oil burner.
  • the operating medium is forced from one of the compression chambers 5 into the communicating expansion chamber 6 by the phase-displaced movement of the two associated pistons 7, it first absorbs the heat stored in the regenerator 9 and then is further heated in the heater 8.
  • the expansion chambers 6 are also called hot chambers.
  • the phase displacement between the movements of the individual pistons 7 has the effect of intermittently reducing and increasing the chambers 5 and 6 interconnected in each case through the elements 8, 9 and 10,
  • FIG. 3 shows what is meant by the crank angle (1).
  • the shut-off members 12 are closed.
  • the shut-off members I2 are opened in the regions of the points A (FIG. 2) in the piston travel during each working cycle.
  • the resultant confluence pressure does not necessarily occur about midway between the pressures at points I and 4 as shown in FIGS. 2 and'4, but depends upon the ratio of the energy contents of the operating medium in the interconnected chambers 5.
  • the shut-off members remain open as far as the points designated I and 4" on the curves I and IV, so that a change in pressure corresponding to the curves I and IV now occurs.
  • the total diagram area is smaller than at full load, i.e., the power provided by the hot-gas engine is adapted to suit a reduced load.
  • the points I, 4 and 4", 4 move progressively nearer to the points A until, at full load, they coincide with them.
  • a method of obtaining load-responsive regulation of the power of a double-acting hot-gas engine comprising an even number of cylinders of at least four, each cylinder containing an expansion chamber and a compression chamber separated by a working piston, grouping said cylinders in pairs of cylinders, phasedisplacing the cylinders of each pair with respect to each other through a crank angle, connecting the expansion chamber of each cylinder, by way of a flow path containing a heater, a regenerator and a cooler arranged in series with one another, to the compression chamber of another cylinder which is phase-displaced with respect to the first-mentioned cylinder through a crank angle which is a fraction of 180, the compression chambers of each pair being intermittently interconnectable by way of an overflow path, at least for partial load, interconnecting the compression chambers of each pair of cylinders by way of the respective overflow path for a time period extending throughout part of each of successive working cycles of each pair, and increasing said time period if the load decreases.
  • a combination comprising an even number of cylinders of at least four, each cylinder containing an expansion chamber and a compression chamber separated by a working piston, said cylinders being grouped in pairs of cylinders, the cylinders of each pair being phase-displaced with respect to each other through a 180 crank angle, a flow path connecting the expansion chamber of each cylinder to the compression chamber of another cylinder which is phase-displaced with respect to the firstmentioned cylinder through a crank angle which is a fraction of 180, each flow path comprising a heater, a regenerator and a cooler arranged in series, an overflow path for interconnecting intermittently the compression chambers of each pair, and valve means in each overflow path for opening and closing the overflow path at intervals.
  • valve means in each overflow path comprises first and second valve means adjacent the respective compression chambers interconnectable via said overflow path.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
US00306558A 1971-11-16 1972-11-14 Hot-gas engines Expired - Lifetime US3813882A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2156773A DE2156773C3 (de) 1971-11-16 1971-11-16 Verfahren zur lastabhängigen Regelung der Leistung eines doppeltwirkenden Heißgasmotors

Publications (1)

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US3813882A true US3813882A (en) 1974-06-04

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US00306558A Expired - Lifetime US3813882A (en) 1971-11-16 1972-11-14 Hot-gas engines

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US (1) US3813882A (de)
DE (1) DE2156773C3 (de)
SE (1) SE374413B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4026114A (en) * 1976-07-09 1977-05-31 Ford Motor Company Reducing the starting torque of double-acting Stirling engines
US20030074882A1 (en) * 2001-10-24 2003-04-24 Andreas Gimsa Two-cycle hot-gas engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19502190C2 (de) * 1995-01-25 1998-03-19 Bosch Gmbh Robert Wärme- und Kältemaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2480525A (en) * 1943-01-23 1949-08-30 Hartford Nat Bank & Trust Co Multicylinder hot-gas engine
US2486081A (en) * 1944-07-27 1949-10-25 Hartford Nat Bank & Trust Co Multicylinder refrigerating machine
US2611235A (en) * 1948-10-12 1952-09-23 Hartford Nat Bank & Trust Co Multicylinder hot gas reciprocating piston engine of the doubleacting type
US2643507A (en) * 1948-12-30 1953-06-30 Hartford Nat Bank & Trust Co Hot-gas reciprocating engine in which a plurality of closed thermodynamic cycles are performed simultaneously and which includes a compressor means
US2664699A (en) * 1950-11-24 1954-01-05 Hartford Nat Bank & Trust Co Multicylinder double-acting hotgas reciprocating engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2480525A (en) * 1943-01-23 1949-08-30 Hartford Nat Bank & Trust Co Multicylinder hot-gas engine
US2486081A (en) * 1944-07-27 1949-10-25 Hartford Nat Bank & Trust Co Multicylinder refrigerating machine
US2611235A (en) * 1948-10-12 1952-09-23 Hartford Nat Bank & Trust Co Multicylinder hot gas reciprocating piston engine of the doubleacting type
US2643507A (en) * 1948-12-30 1953-06-30 Hartford Nat Bank & Trust Co Hot-gas reciprocating engine in which a plurality of closed thermodynamic cycles are performed simultaneously and which includes a compressor means
US2664699A (en) * 1950-11-24 1954-01-05 Hartford Nat Bank & Trust Co Multicylinder double-acting hotgas reciprocating engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4026114A (en) * 1976-07-09 1977-05-31 Ford Motor Company Reducing the starting torque of double-acting Stirling engines
US20030074882A1 (en) * 2001-10-24 2003-04-24 Andreas Gimsa Two-cycle hot-gas engine
US6968688B2 (en) * 2001-10-24 2005-11-29 Enerlyt Potsdam Gmbh Two-cycle hot-gas engine

Also Published As

Publication number Publication date
DE2156773C3 (de) 1974-09-19
SE374413B (de) 1975-03-03
DE2156773B2 (de) 1974-02-21
DE2156773A1 (de) 1973-05-30

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