EP2291583A2 - Moteur stirling - Google Patents

Moteur stirling

Info

Publication number
EP2291583A2
EP2291583A2 EP09711433A EP09711433A EP2291583A2 EP 2291583 A2 EP2291583 A2 EP 2291583A2 EP 09711433 A EP09711433 A EP 09711433A EP 09711433 A EP09711433 A EP 09711433A EP 2291583 A2 EP2291583 A2 EP 2291583A2
Authority
EP
European Patent Office
Prior art keywords
subsystem
working gas
cylinder
compression
expansion
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.)
Withdrawn
Application number
EP09711433A
Other languages
German (de)
English (en)
Inventor
Lutz Pasemann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP2291583A2 publication Critical patent/EP2291583A2/fr
Withdrawn legal-status Critical Current

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
    • 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

Definitions

  • the Stirling engine is the heat-power machine that has the highest efficiency with ideal cycle.
  • the invention relates to a Stirling engine without conventional regenerator, which consists of two or more subsystems containing a working gas, and in which in ideal cycle each one Stirling cycle with the state changes isothermal compression, isochoric heating, isothermal expansion and isochoric cooling is feasible.
  • the first subsystem such a countercurrent heat exchanger with the last subsystem that in operation in the cold working gas of the first subsystem necessary for its isochore heating amount of heat over the countercurrent heat exchanger from the hot working gas of the last Subsystem is transmitted so that the working gas of the last subsystem isochronously cooled by the delivery of this amount of heat through the countercurrent heat exchanger, and that all other subsystems are connected via valve closable by-pass lines with the respective preceding subsystem such that they are in operation Isochor be heated by that in the open bypass lines, the hot working gas of the respective preceding subsystem is pushed, and simultaneously in the respective preceding subsystem their own cold working gas of the same amount and the same volume Gesc is lifted, whereby the respective preceding subsystem isochoric cooled.
  • FIGS. 1a to 4b schematically show an embodiment of a Stirling engine according to the invention comprising two subsystems in the different states of a cyclic process.
  • the first subsystem consists of a first expansion cylinder 10 and a first compression cylinder 11
  • the second subsystem consists of a second expansion cylinder 20 and a second compression cylinder 21.
  • the volumes of the expansion cylinders 10 and 20 and the compression cylinders 11 and 21 of the first and second subsystem are to be chosen so that the volume of the working gas at the end of its hot gas expansion in the expansion cylinder 10 of the first subsystem is equal to both the volume of the working gas at the beginning of its hot gas expansion in the expansion cylinder 20 of the second subsystem and the volume of the cards Working gas at the end of its cold gas compression in the compression cylinder 21 of the second subsystem, and that this volume is in turn equal to the volume of cold working gas at the beginning of its cold gas compression in Kompress ⁇ onszylinder 11 of the first subsystem.
  • the working gas quantities and the compression ratios of the two subsystems are the same size to choose, the compression ratio is formed in each case from the ratio of the volumes of cold working gas at the beginning and at the end of its compression.
  • the equality of the compression ratios of the first and second subsystems is equivalent to the fact that the ratio of the stroke volumes of the two subsystems is equal to the compression ratio of the first subsystem.
  • the expansion cylinder 10 of the first subsystem is connected to a heater 33 and to the compression cylinder 11 of the first subsystem through a first connection line 12, and the compression cylinder 21 of the second subsystem is connected to a radiator 34 and the expansion cylinder 20 of the second subsystem through a second connection line 22 connected, wherein the two connecting lines 12 and 22 are guided past each other so that they form a countercurrent heat exchanger 30, and the connecting lines 12 and 22 through a valve V3, in front of the inlet to the countercurrent heat exchanger 30 on the of the expansion cylinders 10 and 20 and the heater 33 formed hot room side of the Stirling engine is positioned, and by a valve V4, which is positioned in front of the inlet to the countercurrent heat exchanger 30 on the formed by the compression cylinders 11 and 21 and the cooler 34 cold room side, are closed, and in addition the Wegsleitu ng 12 between the expansion cylinder 10 of the first subsystem and the heater 33 by a valve V5 and the connecting line 22 between the compression cylinder 21 of the second subsystem and the
  • a closable by a valve V1 first bypass line 31 connects the expansion cylinder 20 of the second subsystem with the heater 33 and the Expansio ⁇ szylinder 10 of the first subsystem and thus bridges the connecting lines 12 and 22 on the hot room side in front of the counterflow heat exchanger 30, and a through a valve V2 closable second bypass line 32 connects the compression cylinder 11 of the first subsystem with the radiator 34 and the compression cylinder 21 of the second subsystem and thus bridges the connecting lines 12 and 22 on the cold side in front of the counterflow heat exchanger 30th
  • Fig. 1a shows schematically this embodiment of the Stirling engine according to the invention at the beginning of the hot gas expansion of the first subsystem and at the beginning of the simultaneously proceeding cold gas compression of the second subsystem, and in Fig. 1b the end of these state changes is shown.
  • the valves V1 and V2 of the first 31 and second bypass line 32 are closed to prevent mixing of the working gas of the first and second subsystem.
  • a Mixing would be possible with real process flow via non-closed bypass lines 31 and 32, if the position of the expansion piston K21 of the second subsystem and the compression piston K12 of the first subsystem of the ideal position shown in Fig. 1a and Fig. 1b during hot gas expansion deviates from the first subsystem or the cold gas compression of the second subsystem.
  • valves V3 and V4 of the connection lines 12 and 22 are closed so that no hot working gas of the hot room side can mix with the cold working gas of the cold room side.
  • the valve V5 is open, so that in operation by the supplied via the heater 33 external heat, the working gas expands in the expansion cylinder 10 of the first subsystem - isothermal - and shifts the expansion piston K11 by the stroke of the first subsystem.
  • the cold working gas in the compression cylinder 21 of the second subsystem is compressed by the movement of the compression piston K22 by the stroke of the second subsystem - ideally isothermal.
  • the radiator 34 is connected through the second connecting line 22 to the compression cylinder 21 of the second subsystem with the valve V6 open.
  • the cooling of the first subsystem and the simultaneous heating of the second subsystem which are ideally isochoric in each case, wherein in Fig. 2a the beginning and in FIG 2b shows the end of the isochoric heating of the second subsystem and the isochoric cooling of the first subsystem.
  • the valves V3 and V4 of the lines 12 and 22 remain closed, so that the hot room side is still separated from the cold room side.
  • the valves V1 and V2 of the two subsystems connecting bypass lines 31 and 32 are open.
  • the piston K11 of the expansion cylinder 10 of the first subsystem and the piston K21 of the expansion cylinder 20 of the second subsystem are moved simultaneously such that the hot working gas isochoric from the expansion cylinder 10 of the first subsystem via the heater 33 and the bypass line 31 in the expansion cylinder 20th of the second subsystem, and the piston K22 of the compression cylinder 21 of the second subsystem and the piston K12 of the compression cylinder 11 of the first subsystem are moved simultaneously such that the cold working gas isochoric from the compression cylinder 21 of the second subsystem via the radiator 34 and the bypass Line 32 in the Compression cylinder 11 of the first subsystem is pushed.
  • the isochoric cooling of the first subsystem and the simultaneous isochore heating of the second subsystem are followed in operation by the cold gas compression of the first subsystem and the simultaneous hot gas expansion of the second subsystem, the beginning of which is shown in FIG. 3a and whose end is shown in FIG Ideally, run isothermally.
  • the valves V3 and V4 of the hot room side to the cold room side connecting lines 12 and 22 are closed as well as the valves V5 and V6, so that the connection between the expansion cylinder 10 of the first subsystem and the heater 33 and the connection between the compression cylinder 21 of the second subsystem and the radiator 34 are interrupted.
  • valves V1 and V2 of the Bypass-Lertepteptept 31 and 32 are open, so that in operation expands the working gas in the expansion cylinder 20 of the second subsystem through the supplied heat through the heater 33 and 33 moves the piston K21 to the stroke of the second subsystem.
  • the cold working gas in the compression cylinder 11 of the first subsystem is compressed by the movement of the compression piston K12 by the stroke of the first subsystem while dissipating the heat of compression via the radiator 34 during operation.
  • This - in the ideal case isothermal state changes - is followed by the isochoric state changes shown in FIG. 4a and FIG. 4b, with the completion of which the cyclic process of the Stirling engine is completed.
  • FIG. 4a shows the beginning of the isochoric heating of the first subsystem and the beginning of the simultaneous isochoric cooling of the second subsystem
  • FIG. 4b shows the end point of these state changes.
  • the valves V1 and V2 of the bypass lines 31 and 32 are closed, ie, the two subsystems are separated from each other with respect to the working gas.
  • the valves V3 and V4 of the connection lines 12 and 22 and the valves V5 and V6 are opened, so that there is a heat exchange between the two subsystems via the countercurrent heat exchanger 30 during operation.
  • FIGS 1a to 4b illustrated embodiment in that on the valve
  • V4 is omitted, making the construction effort is smaller. Due to the now open from the cold room side countercurrent heat exchanger 30 there are with respect to the cold gas compressions of the first and second subsystem and with respect to the isochoric cold gas displacement of the compression cylinder 21 of the second subsystem in the compression cylinder 11 of the first subsystem in this second embodiment compared to the first additional dead space.
  • a third embodiment is obtained by modifying the embodiment shown in FIGS. 1a to 4b in that the valves V5 and V6 are dispensed with, which reduces the structural complexity.
  • the control of the working gas flow, which takes place in the embodiment shown in Fig. 1a to Fig. 4b through the valves V5 and V6, is in this modification of the expansion piston K11 of the first
  • a fourth embodiment is obtained by modifying the embodiment shown in FIGS. 1a to 4b by omitting the valves V4, V5 and V6. The consequences are in summary from those of the second and third embodiments.

Landscapes

  • 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)

Abstract

L'invention concerne un moteur Stirling composé de deux sous-systèmes ou plus, contenant un gaz de travail et reliés l'un à l'autre. Selon l'invention, le premier sous-système est relié au dernier sous-système par l'intermédiaire d'un échangeur thermique à contre-courant, de sorte qu'en service une quantité de chaleur nécessaire au chauffage isochore du gaz de travail est transférée du gaz de travail chaud du dernier sous-système au gaz de travail froid du premier sous-système par l'intermédiaire d'un échangeur thermique à contre-courant, le gaz de travail du dernier sous-système étant ainsi refroidi de façon isochore, et tous les autres sous-systèmes sont reliés au sous-système placé en amont par l'intermédiaire de conduites de dérivation pouvant être obturées par des soupapes, de sorte qu'en service ces sous-systèmes sont chauffés de façon isochore, par le fait que le gaz de travail chaud du sous-système placé en amont est poussé vers lesdits sous-systèmes par l'intermédiaire des conduites de dérivation ouvertes et, simultanément, une même quantité et un même volume de gaz de travail froid desdits sous-systèmes est poussé vers le sous-système placé en amont, le sous-système placé en amont étant ainsi refroidi de façon isochore.
EP09711433A 2008-02-11 2009-02-11 Moteur stirling Withdrawn EP2291583A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202008001920U DE202008001920U1 (de) 2008-02-11 2008-02-11 Stirlingmaschine mit Gegenstrom-Wärmeübertrager
PCT/DE2009/000178 WO2009100710A2 (fr) 2008-02-11 2009-02-11 Moteur stirling

Publications (1)

Publication Number Publication Date
EP2291583A2 true EP2291583A2 (fr) 2011-03-09

Family

ID=39326881

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09711433A Withdrawn EP2291583A2 (fr) 2008-02-11 2009-02-11 Moteur stirling

Country Status (3)

Country Link
EP (1) EP2291583A2 (fr)
DE (2) DE202008001920U1 (fr)
WO (1) WO2009100710A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008010691U1 (de) 2008-08-12 2008-12-11 Pasemann, Lutz, Dr. Gegenstromwärmetauscher
FR2945327A1 (fr) * 2009-05-07 2010-11-12 Ecoren Procede et equipement de transmission d'energie mecanique par compression et/ou detente quasi-isotherme d'un gaz
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
DE102012213878B4 (de) * 2012-08-06 2017-10-19 István Majoros Wärmekraftmaschine und thermodynamischer Kreisprozess zur Umwandlung von Wärme in Nutzarbeit
GB201304243D0 (en) 2013-03-08 2013-04-24 Bhp Generation Ltd A heat engine, a heat storage device and a power generation system incorporating same
BR102013026634A2 (pt) * 2013-10-16 2015-08-25 Abx En Ltda Máquina térmica diferencial com ciclo de oito transformações termodinâmicas e processo de controle
DE202022001806U1 (de) 2022-08-13 2022-09-12 Thomas Seidenschnur Mehrzylinder-Heißgasmotor-Anlage

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3879945A (en) * 1973-04-16 1975-04-29 John L Summers Hot gas machine
DE19752996C2 (de) * 1996-11-28 1999-07-22 Lutz Dr Pasemann Regeneratorlose Stirlingmaschine
DE102005042744A1 (de) * 2005-08-16 2007-04-26 Enerlyt Potsdam GmbH Energie, Umwelt, Planung und Analytik 4-Zyklen-Universalmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009100710A2 *

Also Published As

Publication number Publication date
DE112009000903A5 (de) 2011-01-20
WO2009100710A4 (fr) 2009-12-23
DE202008001920U1 (de) 2008-04-24
WO2009100710A3 (fr) 2009-11-05
DE112009000903B3 (de) 2020-07-23
WO2009100710A2 (fr) 2009-08-20

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