EP1126153A2 - Moteur Stirling - Google Patents

Moteur Stirling Download PDF

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Publication number
EP1126153A2
EP1126153A2 EP01890034A EP01890034A EP1126153A2 EP 1126153 A2 EP1126153 A2 EP 1126153A2 EP 01890034 A EP01890034 A EP 01890034A EP 01890034 A EP01890034 A EP 01890034A EP 1126153 A2 EP1126153 A2 EP 1126153A2
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EP
European Patent Office
Prior art keywords
piston
cylinder
pistons
stirling engine
cold
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Withdrawn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
EP01890034A
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German (de)
English (en)
Other versions
EP1126153A3 (fr
Inventor
Josef Ing. Frauscher
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Individual
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Individual
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Publication date
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Publication of EP1126153A2 publication Critical patent/EP1126153A2/fr
Publication of EP1126153A3 publication Critical patent/EP1126153A3/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • 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
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • F02G2243/04—Crank-connecting-rod drives
    • 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
    • F02G2270/45—Piston rods

Definitions

  • the invention relates to a Stirling engine, working as a two-piston engine, consisting of a closed on all sides against the environment Cylinder whose ends are connected via a connection outside the cylinder have a cooler, a regenerator and a heater for the working gas and form a cold and a hot cylinder side, in the interior of which a compression piston on the cold side of the cylinder and an expansion piston are located on the hot cylinder side on a common axis that over Piston rods connected to an engine located outside the cylinder are and are driven out of phase with each other.
  • the Stirling engine is in the circle of thermodynamic machines So far, hardly implemented, although the implementation of the Stirling process is just the case offers enormous scope for design, like countless designs, IP applications, models, prototypes and small series versions demonstrate.
  • the working gas is under Pressured. Variants with internal pressures of more than 100 bar are known.
  • noble gases are used to reduce flow losses in the heater, cooler and regenerator.
  • Monatomic gases, such as hydrogen or helium have proven to be effective in high-performance machines Working gases prevail over air.
  • Stirling machines are essentially in the literature in the displacement machines (beta and gamma type), two-piston machines (Alpha type) and double-acting machines (Siemens type) divided (Lit .: Stirling machine technology, publisher Fritz Steimle, Müller Verlag Heidelberg, Stirling machines, Martin Werdich, Kuno Kübler, ⁇ KOBUCH, Staufen near Freiburg).
  • Displacement machines of the beta type have the advantage that the working piston and the displacer inexpensively arranged in a common cylinder are.
  • the heat exchangers and the regenerator are usually centered around the cylinder, which is the prerequisite for one offers optimal gas flow.
  • only the working piston has to be be sealed towards the cylinder, which is due to the low temperatures the cold side of the cylinder is not a big problem.
  • the Dead space losses due to the absence of manifolds or collectors are minimized become. This advantageously leads to the highest possible, efficiency-increasing Compression ratio.
  • crankcase, rod seal and rod guides the same problem arises with two-piston machines of the type Alpha.
  • such machines have the disadvantage that two separate ones Cylinders are required and two pistons must be sealed, one even on the hot side.
  • the heat exchangers and the regenerator must be placed between the two cylinders, which is usually not without manifolds and collectors with the well-known disadvantages of a high Dead volume is possible.
  • the Alpha type machines which have arranged the cylinders in a V-shape. The angle between the cylinders are usually around 90 degrees. This arrangement allows use a simple crankshaft with only one crank pin to which the two connecting rods of the pistons are articulated.
  • the angle between the cylinders is thus synonymous with the phase shift of the piston movements.
  • the Advantages of the simple crank drive are the high effort for the Arrangement of two cylinders and the seals to the pistons and Crankcase largely canceled.
  • the power to weight ratio of the machine is unfavorable, no matter whether it is a pressure-free or pressurized Crankcase.
  • the area of application is therefore essentially limited on stationary applications.
  • the piston rods are either articulated to ordinary crankshafts via cross heads and connecting rods or via spherical bearings directly to a swashplate, parallel to the axis the piston rods.
  • WO 99/01655 A shows such a machine that has already reached series maturity.
  • the object of the invention is to create a Stirling engine at the outset mentioned type, which is characterized by a simple design and high operational reliability and low efficiency as well as a homogeneous Exhibits operational behavior.
  • each piston a variable by its strokes Space for the working gas between it and the respective cylinder end forms and that these spaces sealed against the space between the pistons are.
  • the inventive design of a Stirling engine avoids one Series of disadvantages of the recorded design variants on the other hand, advantages of individual construction methods. So it's a extremely simple construction with a cylinder similar to the beta type, at where the piston rods are passed through on the cold side. Both pistons move in the manner known for the beta type, namely out of phase by a crank angle of approximately 90 degrees.
  • the main difference to a Beta Stirling engine is that instead of the displacer an expansion piston is arranged.
  • the work process is the same as for a two-piston machine of the alpha type.
  • Characteristic of the invention Training is that according to a preferred embodiment of the Compression piston leads the expansion piston by the phase angle.
  • the space between the pistons as Buffer space used.
  • the pistons are for this pot-shaped and have different diameters, the Seals smaller pistons on the inside of the larger pistons.
  • the expansion piston will have the larger diameter and be longer than the compression piston. It is essentially only a functional dynamic piston seal is required.
  • the one already mentioned is located within the two pistons Buffer space for the compression and expansion phase of the process.
  • the largest part of the buffer volume is taken up by the space inside the expansion piston a, since this piston is advantageously relatively long to accommodate the high Reduce the temperature of the expansion room to the cold compression room to be able to keep the heat loss small.
  • the whole Buffer space takes an average pressure, which is usually identical to that Boost pressure of the machine. Another buffer space is not necessary.
  • both pistons have the same diameter. They slide along the cold surface of the cylinder and seal there. This shows the advantage Compared to known designs, especially in that no additional Measures must be taken to keep the cylinder tread in mind to cool for a long service life of the sliding surfaces and the piston rings.
  • the cooler - heat exchanger is located in the area of this tread anyway and there is no need to create additional cold rooms for the cylinder cooling.
  • the device according to the invention is also optional with one, the State of the art applicable pressurized gearbox applicable.
  • the piston rod seals only need the differential pressures record between working and boost pressure and it's a rotating Seal required for the crankshaft leading to the outside. Such seals are available in a gas-tight version on the market. About that in addition, the known arrangement when used as a generator drive Generator in the pressure chamber possible.
  • Fig. 1 the cylinder 1 is shown as a closed vessel, the is only broken through to the outside by the piston rod guide 9.
  • the Cylinder 1 consists of a cold side 11 and a hot side 12.
  • the two Rooms 11, 12 are by a cooler 2, a regenerator 3 and a heater 4 connected.
  • Both the heater 4 and the cooler 2 are exemplary as Tubular heat exchanger drawn in the form that the cooler 2 with liquid is cooled and the heater 4 hot gases in an unspecified Form are fed.
  • Both the cooler 2 and the heater 4 can also be designed differently, for example with fine ribs or fans.
  • An expansion piston is located within the hot side 12 of the cylinder 1 5, which is connected to a piston rod 6, which to the outside a crank mechanism 10 leads.
  • a crank mechanism 10 There is a inside the cold cylinder side Compression piston 7, according to FIGS. 1 and 2, on a hollow piston rod 8 is attached, which leads to the crank mechanism 10 via connecting rods.
  • the illustration shows that the expansion piston 5 and the compression piston 7 are cup-shaped.
  • the expansion piston 5 has a larger diameter than the compression piston and the latter seals on the inner wall of the expansion piston 5.
  • a piston seal 14 is the only working seal to separate the cylinder rooms 11, 12 and the buffer space 16.
  • the expansion piston 5 carries on his lower end also a seal 15, which separates the hot cylinder side 12 caused by the cold cylinder side 11. There are none on this seal high demands, since it only causes the pressure difference has to be sealed by flow resistances in the heat exchangers 2, 3, 4.
  • the cooler 2 is advantageously designed such that the cooling water in a jacket around the cold side 11 of the cylinder 1, wherein both the cooler 2 and the cylinder wall of the cold cylinder side 11 flows around and is cooled. Due to the heat transfer is for the seals 15 and 14th a relatively cool operation is possible, which is the use of plastics enabled as piston seals. Shielding plates 13 also provide to ensure that the high temperature on the upper side of the expansion piston 5 acts, does not reach the inside of the compression piston 7.
  • the piston rods 6, 8 are connected to the crankshaft 10 of the connecting rods Articulated crank drive.
  • FIGS. 1 and 2 are in the embodiment of FIGS. 1 and 2 here for the implementation of Piston rod 6 tubular piston rod 8 of the compression cylinder 7 articulated by means of two connecting rods to two crank pins of the crankshaft 10.
  • 3 are for the compression piston 7 two diagonally with the same Piston rods arranged at a center distance and sealed off by 9a 8 available.
  • crank pin for the compression cylinder 7 are opposite Crank pin for expansion cylinder 5 offset in a rotating circle by approx. 90 degrees.
  • the picture to the left of the crankshaft 10 schematically shows the view of the crankshaft 10 from the left. In relation to the direction of rotation 17 it can be seen that the crank pin 7a for the compression piston 7 the crank pin 5a for the expansion piston 5 leads 90 degrees.
  • Choosing a crankshaft 10 with is only three crank pins as a gear for the device according to the invention exemplary and useful for the functional explanation. They are just as good other constructions corresponding to the state of the art, e.g. on Rhombus engine as described in WO 99/04152 or engines as they are explained in DE 19722036 A1, DE 19616256 A1, WO 99/04153 A.
  • FIG. 2 and 3 A further development of the idea according to the invention is shown in FIG. 2 and 3. Since the basic mode of operation is completely identical to that of Fig. 1, in the following description of Fig. 2 only on the executed difference to Fig. 1 received.
  • the compression piston 7 and the expansion piston 5 have the same diameter and slide one behind the other along the inner surface the cold cylinder side 11 of the cylinder 1.
  • the cold cylinder side is advantageous 11 dimensioned in length so that both piston seals 14,15 along their Do not leave the cold cylinder area.
  • the expansion piston 5 is on its bottom open. Its inner volume forms together with the volume above the compression cylinder 7, the buffer space 16. The relatively long Design of the expansion piston 5 ensures the formation of a sufficient Buffer space 16 that sufficient distance and shielding between the hot cylinder side 12 and the cold cylinder side 11 is present.

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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)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP01890034A 2000-02-16 2001-02-13 Moteur Stirling Withdrawn EP1126153A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT2322000 2000-02-16
AT2322000 2000-02-16

Publications (2)

Publication Number Publication Date
EP1126153A2 true EP1126153A2 (fr) 2001-08-22
EP1126153A3 EP1126153A3 (fr) 2002-10-23

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EP01890034A Withdrawn EP1126153A3 (fr) 2000-02-16 2001-02-13 Moteur Stirling

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT500628A3 (de) * 2005-11-04 2006-10-15 Avl List Gmbh Zylinderkopf für eine flüssigkeitsgekühlte brennkraftmaschine
WO2011141508A1 (fr) 2010-05-12 2011-11-17 Christian Daublebsky Von Eichhain Moteur thermique à compression
ITUD20110070A1 (it) * 2011-05-11 2012-11-12 Innovative Technological Systems Di Fontana Claudi Motore a combustione esterna

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612616A1 (de) 1996-03-29 1997-10-02 Herrmann Klaus Ag Stirlingmotor
DE19616256A1 (de) 1996-04-24 1997-11-20 Herrmann Klaus Ag Stirlingmotor-Getriebe
DE19722036A1 (de) 1997-05-27 1998-12-03 Bosch Gmbh Robert Getriebe für eine nach einem regenerativen Gaskreisprozeß arbeitende Wärme- und Kältemaschine
WO1999001655A1 (fr) 1997-07-02 1999-01-14 Stirling Thermal Motors, Inc. Joint de tige a soufflet pour moteur stirling
WO1999004152A1 (fr) 1997-07-15 1999-01-28 New Power Concepts Llc Ameliorations d'une machine a cycle de stirling

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB761122A (en) * 1951-10-03 1956-11-14 Shell Refining & Marketing Co Improvements in machines operating according to a modified stirling cycle
DE3508689A1 (de) * 1985-03-12 1986-10-16 Bomin-Solar GmbH & Co KG, 7850 Lörrach Waermekraftmaschine
JPS61255255A (ja) * 1985-05-07 1986-11-12 Sanden Corp スタ−リングエンジン
KR940010581B1 (ko) * 1992-01-07 1994-10-24 삼성전자 주식회사 열압축식 히트펌프

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612616A1 (de) 1996-03-29 1997-10-02 Herrmann Klaus Ag Stirlingmotor
DE19616256A1 (de) 1996-04-24 1997-11-20 Herrmann Klaus Ag Stirlingmotor-Getriebe
DE19722036A1 (de) 1997-05-27 1998-12-03 Bosch Gmbh Robert Getriebe für eine nach einem regenerativen Gaskreisprozeß arbeitende Wärme- und Kältemaschine
WO1999001655A1 (fr) 1997-07-02 1999-01-14 Stirling Thermal Motors, Inc. Joint de tige a soufflet pour moteur stirling
WO1999004152A1 (fr) 1997-07-15 1999-01-28 New Power Concepts Llc Ameliorations d'une machine a cycle de stirling
WO1999004153A1 (fr) 1997-07-15 1999-01-28 New Power Concepts Llc Machine a cycle stirling a vilebrequin en porte-a-faux

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
HERAUSGEBER;FRITZ STEIMLE,MULLER VERLAG HEIDELBERG, STIRLING-MASCHINEN-TECHNIK
MARTIN WERDICH,KUNO KOBLER: "stirling-maschinen", ÖKOBUCH

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT500628A3 (de) * 2005-11-04 2006-10-15 Avl List Gmbh Zylinderkopf für eine flüssigkeitsgekühlte brennkraftmaschine
WO2011141508A1 (fr) 2010-05-12 2011-11-17 Christian Daublebsky Von Eichhain Moteur thermique à compression
DE102010020325A1 (de) 2010-05-12 2011-11-17 Christian Daublebsky von Eichhain Thermokompressionsmotor
DE102010020325B4 (de) * 2010-05-12 2012-09-06 Christian Daublebsky von Eichhain Wärmekraftmaschine
US8683984B2 (en) 2010-05-12 2014-04-01 Christian Daublebsky von Eichhain Thermocompression motor
ITUD20110070A1 (it) * 2011-05-11 2012-11-12 Innovative Technological Systems Di Fontana Claudi Motore a combustione esterna
WO2013050836A1 (fr) * 2011-05-11 2013-04-11 Innovative Technological Systems S.R.L. Moteur à combustion externe
US9790791B2 (en) 2011-05-11 2017-10-17 Innovative Technological Systems S.R.L. External combustion engine

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Publication number Publication date
EP1126153A3 (fr) 2002-10-23

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