EP1285160A1 - Heissgasmotor - Google Patents
HeissgasmotorInfo
- Publication number
- EP1285160A1 EP1285160A1 EP01940002A EP01940002A EP1285160A1 EP 1285160 A1 EP1285160 A1 EP 1285160A1 EP 01940002 A EP01940002 A EP 01940002A EP 01940002 A EP01940002 A EP 01940002A EP 1285160 A1 EP1285160 A1 EP 1285160A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hot gas
- gas engine
- engine according
- piston
- lever
- 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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
-
- 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
- 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
-
- 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
- F02G2270/42—Displacer drives
- F02G2270/425—Displacer drives the displacer being driven by a four-bar mechanism, e.g. a rhombic mechanism
Definitions
- the invention relates to a hot gas engine with at least one working piston and at least one displacement piston.
- the aim of the invention is to provide a hot gas engine of the type mentioned in the introduction, in which rapid power control is possible without reducing the efficiency.
- the hot gas engine according to the invention of the type mentioned at the outset is characterized in that for power control by means of the transmission of the linear movement of a drive part into the linear movement of an output part, a lever which is articulated to the drive and output part is provided, the one Adjustable pivot point is assigned, wherein the bearing point of the lever at the pivot point moves according to a curve during the movement transmission.
- This curve can have any shape - depending on the requirements of the transmission of motion or the type of the respective hot gas engine.
- P m mean effective pressure ⁇ pressure ratio of the motor
- a power control can be carried out without loss of efficiency by means of the lever device according to the characterizing part of claim 1, since preferably the maximum compression volume V c , raax and thus the pressure ratios ⁇ of the engine can be controlled very well.
- the lever has a backdrop defining the given curve, which during the transmission of movement via the pivot point, e.g. a role defining this pivot point slides.
- the curve or backdrop runs in a circular arc; of course there are of course other curve shapes, e.g. two circular arc segments connected tangentially or an elliptical shape, conceivable for certain purposes.
- the pivot point is attached to a pivot arm.
- the pivot point can be adjusted in a structurally particularly simple manner if the pivot arm is connected to an adjusting device.
- the adjusting device is connected to a swivel arm via a linkage and is provided symmetrically between at least two levers.
- a spindle drive is provided as the actuating device.
- a link guide in which the end of the linkage opposite the swivel arm is slidably and fixably received, the position of the swivel arm can be changed in a simple and quick manner and thus the output of the hot gas engine can be adjusted.
- Displacement piston and the working piston in a common cylinder which in theory makes it possible for the entire gas mass to be in the hot space during the expansion phase and in the cold space during the compression phase.
- the working piston is assigned to the lever with an adjustable pivot point and the displacement piston is assigned to a lever with a non-adjustable pivot point.
- the drive part is articulated to a piston rod which is connected to the displacement piston or the working piston and is linearly guided in a straight guide.
- the displacement piston has a wave profile on both sides and the work piston on one side, which can engage in adjacent heater or cooler surfaces. In this way, compared to flat surfaces, much larger surfaces can come into contact with the working gas.
- the lamellar wave profiles of the displacer are arranged rotated by 90 ° to one another. It is also advantageous for high strength if the lamellar, thin-walled wave profiles of the working piston or heater head are supported on the burner side or coolant side by stiffening ribs.
- Particularly advantageous with regard to efficiency and minimizing the harmful volumes of a hot gas engine is an integration of heater, regenerator and cooler surfaces directly into the work space.
- Figure 1 is a schematic view of a device for the controlled implementation of linear movements, wherein a drive part, the linear movement is implemented via a lever, the bearing point at the pivot point according to a curve, is in its lower end position.
- FIG. 2 shows a view of a device according to FIG. 1, the drive part being in a central or zero position;
- FIGS. 1 and 2 shows a view of the device according to FIGS. 1 and 2, the drive part being in an upper end position;
- FIG. 4 shows a view of a Stirling engine with two displacement units and in each case a device for controlling the reciprocating movement of a displacement piston;
- FIG. 5 shows a side view of the Stirling engine according to arrow V in FIG. 4;
- Fig. 6 is a sectional view along the line VI-VI in Fig. 5;
- FIGS. 4 to 6 shows a perspective view of the Stirling engine according to FIGS. 4 to 6;
- FIG. 9 shows a perspective view of a displacement piston for reciprocating movement in a displacement unit according to FIG. 8;
- FIG. 10 is an exploded view of the displacement piston according to FIG. 9;
- FIGS. 11a to 11d show various graphic representations of the Stirling engine shown in FIGS. 4 to 7, each with a different position of the pivot point of the lever for controlling the back and forth movement of the drive part;
- FIG. 12 shows a view of a ⁇ -Stirling two-cylinder engine with two displacement units and in each case one device for controlling the stroke movement and the time sequence of a working piston; 13 shows a partially broken side view of the ⁇ motor according to FIG. 12;
- FIG. 14 shows a sectional illustration along the line XIV-XIV in FIG. 13, the pivot points being in their maximum power position and the working pistons reaching their maximum stroke value;
- FIG. 15 shows a side view of the ⁇ motor according to FIG. 14, the pivot points being in a central position
- FIGS. 14 and 15 shows a view of the ⁇ motor according to FIGS. 14 and 15, the pivot points being in a position which minimizes power;
- FIG. 17 shows a perspective view of the sectional illustration according to FIGS. 14 to 16;
- FIGS. 18 shows an exploded view of the ⁇ motor according to FIGS. 12 to 17;
- FIGS. 19a to 19d show various graphic representations of the ⁇ -Stirling engine shown in FIGS. 12 to 18, each with a different position of the pivot point of the lever for controlling the reciprocation of the drive shaft;
- 20 is a view of a double-acting Stirling engine with a device for the controlled implementation of linear movements
- FIG. 21 shows a sectional illustration along the line XXI-XXI in FIG. 20.
- FIG. 1 to 3 show a device 1 for the controlled implementation of linear movements, a connecting rod 2 operating as a drive part being provided, which is connected in an articulated manner to a piston rod 3 of a displacement piston 4 of a Stirling engine (see FIG. 6). Furthermore, the connecting rod 2 is articulated about an axis 2 'with a lever 5, which has a predetermined control curve in the form of a link 6, in which a roller 7 freely rotatable about an axis 7' as a pivot point for the lever 5 (hereinafter also therefore "Roll lever" designated) is provided.
- the other end of the lever 5, which is essentially angled by 90 °, is connected in an articulated manner about an axis 8 ′ to an output rod 8, to which the linear movement of the displacement piston rod 3 is transmitted.
- the output rod 8 is in turn mounted linearly, but rotated by 90 ° with respect to the linear movement of the displacement piston rod 3.
- One of the essential variables for determining the transmission of movement between the displacer piston rod 3 and the output rod 8 is the distance LR (see FIG. 2) between the axis of rotation 8 'between the lever 5 and the output rod 8 and the axis of rotation 7' on which the roller 7 is rotatably mounted.
- This distance LR can be expressed as
- y x indicates the vertical distance between the axes of rotation 8 'and 7' and z__ the horizontal distance between the two axes of rotation 8 ', 7'.
- angle ⁇ between the connecting line between the axes of rotation 7 ', 8' and the connecting line between the axes of rotation 7 ', 2' is of importance for the transmission of movement, wherein
- R represents the adjustable rolling radius of the roller 7 and a represents the vertical distance of the imaginary center of the rolling radius from the center line of the output rod 8.
- a represents the vertical distance of the imaginary center of the rolling radius from the center line of the output rod 8.
- ⁇ (0) arctan R + a
- b is the horizontal distance between the imaginary center of the rolling circle R and the axis 2 'in the central position.
- LR ' is the distance between the axes of rotation 8' and 2 ', and can therefore be used as
- the position of the displacement piston rod 3 can be as with the help of the axis of rotation 3 'between the displacement piston rod 3 and the connecting rod 2 write, the axis of rotation in the position shown in Fig. 2 in the position
- 1 represents the length of the connecting rod 2 and c indicates the horizontal distance of the axis 8 'in the reference position from the central axis of the displacer piston rod 3.
- the Stirling engine 10 has two displacement units 11, in each of which a displacement piston 4 is moved back and forth.
- the movement described by the respective lever 5 can be changed by adjusting the position of the roller 7, which can be adjusted via a swivel arm 12.
- a linkage 13 is provided, which can be adjusted by means of a common spindle drive 14 via an adjusting wheel 15.
- the position of the rollers 7 can be changed by turning up the adjusting wheel 15 such that there is a change in performance, as can be seen from FIGS. 11a to 11d.
- the side view of the Stirling engine 10 shown in FIG. 5 shows the working cylinder 16, which is fed via a line 17.
- a combustion chamber 18 (cf. FIG. 6) of the displacement unit 11 fresh air heated for combustion is introduced via a line 19 via a heat exchanger 20 with the aid of the heat of the exhaust gas supplied via a line 21, which air after it has passed through the heat exchanger 20 , can escape into the environment via line 22.
- FIG. 6 shows a section of the Stirling engine 10 along the line VI-VI in FIG. 5; a wave-like profile 23 of the cooler surfaces 24 or heater surfaces 25 can be seen, in the case of these heat exchange surfaces 24, 25 can consist, for example, of ceramic.
- the heater surfaces 25 connect to the combustion chambers 18, in each of which a burner 26 is provided for heating or burning the freshly preheated fresh air introduced via the lines 19.
- the displacer 4 displaces the working gas between a hot chamber 27 and a cool chamber 28, the middle part 37 of the displacer 4 containing the regenerator (cf. FIG. 5).
- crank mechanism 32 (FIG. 6) is provided for transmitting motion from the output rod 8 to a crankshaft 31 (see FIG. 5).
- FIG. 7 shows a perspective view of the Stirling engine 10 with the devices 1 assigned to the displacement units 11 for the controlled transmission of the linear movements of the connecting rods 3. Furthermore, the adjustment mechanism for the rollers 7 can be seen via the rods 13, which enables the position of the rollers 7 to be adjusted by rotating the adjusting wheel 15, which in turn controls the power control of the Stirling engine 10 by the changed reciprocating movement of the displacement piston 4 , becomes.
- the radiator cover area shows an exploded view of the displacement unit 11.
- the straight guide 30 for receiving the articulated connection between the displacer piston rod 3 and the connecting rod 2 is shown, which is screwed onto the radiator cover 33.
- the heat exchange surface 24 provided for cooling is connected to the cooler-side cover 33 by means of several screws 34.
- a cylinder 35 is provided, on which the line 17 is provided for spatial connection with the working cylinder 16.
- the hot heat exchange surface 25, like the cool heat exchange surface 24, has a wave-like surface profile on both sides for stability reasons, preferably twisted by 90 °, in order to achieve the largest possible surface which favors heat exchange between the hot or the cool surface and the displacement chamber.
- the displacement piston 10 consists of three individual parts, profile halves 38 each being screwed onto a regenerator disc 37 and having the aforementioned wave profile, which is provided for mutual engagement with the wave profiles of the heat exchange surfaces 24 and 25, respectively.
- the regenerator disk 37 which can be made of ceramic, for example, has slot-shaped cavities 37 'in which a regenerator material, for example sintered steel wool with an approximately 60-70% porosity, is embedded.
- FIGS. 11a to 11d four different settings of the position of the roller 7 supporting the roller lever 5 are shown in four diagrams.
- Each of FIGS. 11a to 11d has a pV diagram I, a representation II of the changing volumes during a full reciprocation of the working or displacement piston, a representation III of the piston positions of the working piston and of the displacement piston over a full cycle and a standardized representation IV of the piston position of the working and displacement piston with respect to the extreme positions possible according to the setting of the roller 7.
- FIG. 11a It can be seen from FIG. 11a that an increase in performance is possible when the position of the roller 7 is pivoted very strongly from the vertical, in which the phase shift between the course 40 of the working piston and the course 41 of the displacer piston from 90 ° to approximately 85 ° (see illustration III) is reduced, as a result of which a maximum pressure 45 (see diagram I) which is the same as that of a normal sine curve 42 is achieved and the power in the example shown in FIG. 11a is 102.6 kW (see computer-simulated one pV curve 44 with roller lever control) compared to 97.6 kW (cf. computer-simulated pV curve 43) can be increased with a conventional sine curve of the displacer 42.
- FIG. 12 shows a view of a ⁇ -Stirling engine 50 with a device 1 for the controlled implementation of linear movements, fresh air being introduced into a combustion chamber 18 via a line 19 via two blowers 51, said combustion chamber 18 being introduced via a heat exchanger 20 with the aid of Warmth of over. the line 21 supplied exhaust gas is heated. The exhaust gas supplied to the heat exchanger 20 then leaves the ⁇ -Stirling engine 50 in the direction of the environment via lines 22.
- FIG. 14 shows the ⁇ motor 50, in which the displacement piston 4 and the working piston 52 are provided in a common cylinder 54, whereby it is theoretically possible that almost the entire gas mass during the expansion phase in the hot room 55 or is in cold room 56 during the compression phase.
- Both the displacement piston rods 3 and the working piston rods 3 ' are connected to a roller lever 5, the rollers 7' of the roller lever 5 ', which are assigned to the displacement piston rods 3, being rigidly arranged.
- the rollers 7, which are assigned to the working pistons 52 are arranged so as to be adjustable by means of a link guide 57.
- a disk 59 having two spiral-shaped recesses 58 is provided, in which the ends 13 ′ of the rods 13 opposite the rollers 7 are received.
- This can result in a twist the ends 13 'receiving plate 60, the position of the rollers 7 in the roller levers 5 are adjusted.
- a discontinuous movement of the displacement pistons 5 and the working pistons 52 is thus achieved, as a result of which the thermal cycle can be carried out more ideally than a sinusoidal piston movement.
- the link guide 57 for adjusting the position of the roller 7 of the levers 5 a structurally simple design for dynamic stroke change can thus be obtained, which in particular enables an approximately efficiency-neutral and fast power control.
- FIG. 15 shows a ⁇ -Stirling or hot gas engine 50 according to FIG. 14, but the position of the rollers 7 in the roller levers 5 has been changed with the aid of the link device 57. In this way, an essentially efficiency-neutral and also fast power control of the ⁇ motor 50 can take place (cf. graphical representations in FIGS. 19a to 19d).
- the rollers 7 of the roller levers 5 are in an inner extreme position, which results in a power-minimizing position of the rollers 7.
- FIG. 17 shows a perspective, broken-away view of the ⁇ -Stirling engine according to FIGS. 12 to 16, the compact arrangement of the roller levers 5 and the heat exchanger 20 in particular being evident.
- a linear crank 61 With the aid of a linear crank 61, the linear movements introduced by the output rods 8 of the devices 1 are converted into a rotational movement of the crank shaft 53 implemented.
- FIGS. 19a to 19d four different settings of the position of the roller 7 supporting the roller lever 5 according to the ⁇ -Stirling engine 50 shown in FIGS. 12 to 18 are shown in four diagrams.
- Each of FIGS. 19a to 19d has a pV diagram I, a representation II of the changing volumes during a full back and forth movement of the working or displacement piston 52, 4, a representation in the piston positions of the working piston 52 and the displacing piston 4 over a full cycle, and a representation IV of the torque curve of a single-cylinder ß Stirling engine, a two-cylinder ß engine according to FIGS. 12 to 18, and a four-cylinder ß engine.
- Figure IV shows that doubling the number of cylinders in the ß-Stirling engine makes it possible to achieve a more even torque curve.
- the torque curve 69 of the single-cylinder ß engine has the highest amplitude
- the two-cylinder ß-Stirling engine 50 shown in FIGS. 12 to 18 already has a more uniform torque curve 68, and with the aid of a four-cylinder ß-Stirling engine, a relative uniform torque curve 71 can be obtained.
- FIGS. 19b, 19c show graphics relating to the central positions of the roller 7 of the roller lever 5, which can be adjusted in a simple manner with the aid of the guide 57.
- the output of the ⁇ -Stirling engine 50 decreases, this also being evident from the diagrams II, III of FIGS. 19b, 19c due to a reduction in the piston stroke 68 and thus a reduction in the piston volume 65.
- the computer-simulated p-V curve 63 according to FIG. 19b, this results in an output of approximately 73 kW, in accordance with FIG. 19c an output of approximately 21 kW.
- FIG. 19d shows the corresponding diagrams I, II, III, IV for the performance-minimizing setting of the rollers 7 shown in FIG. 16. In this position, only an output of approx. 4 kW is achieved.
- diagram II it is shown that the working piston volume 65 is greatly reduced compared to the maximum power position shown in FIG. 19a, since - as can be seen in FIG. 19d - the maximum stroke 69 of the working piston 52 is greatly reduced.
- FIGS. 20 and 21 show a double-acting four-cylinder hot gas engine 72 with devices 1 for the controlled implementation of linear movements.
- Rolling levers 5 with adjustable rollers 7 are also shown here as pivot points for adjusting the power, with 72 hot and working pistons being combined in a unit 73 in this structurally particularly simply constructed hot gas engine. Due to the simple construction, the mechanical efficiency is lower than that of the ß-motor and the power control also causes additional efficiency losses.
- the movement is transmitted via the output rods 8 using a conventional crank 74.
- the device 1 can also be used for power control in any other hot gas engine. be set.
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT0093600A AT411844B (de) | 2000-05-29 | 2000-05-29 | Heissgasmotor |
AT9362000 | 2000-05-29 | ||
PCT/AT2001/000169 WO2001092708A1 (de) | 2000-05-29 | 2001-05-29 | Heissgasmotor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1285160A1 true EP1285160A1 (de) | 2003-02-26 |
EP1285160B1 EP1285160B1 (de) | 2008-04-16 |
Family
ID=3683251
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01940002A Expired - Lifetime EP1285160B1 (de) | 2000-05-29 | 2001-05-29 | Heissgasmotor |
Country Status (14)
Country | Link |
---|---|
US (1) | US6729131B2 (de) |
EP (1) | EP1285160B1 (de) |
JP (1) | JP2003535262A (de) |
KR (1) | KR100743954B1 (de) |
CN (1) | CN1208544C (de) |
AT (2) | AT411844B (de) |
AU (2) | AU2001273722B2 (de) |
BR (1) | BR0111662A (de) |
CA (1) | CA2405174A1 (de) |
DE (1) | DE50113863D1 (de) |
EA (1) | EA003980B1 (de) |
HK (1) | HK1052956B (de) |
MX (1) | MXPA02011800A (de) |
WO (1) | WO2001092708A1 (de) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004101983A1 (ja) * | 2003-05-13 | 2004-11-25 | Honda Motor Co. Ltd. | 多段スターリング機関 |
FR2881513B1 (fr) * | 2005-02-03 | 2007-04-06 | Sagem | Machine a froid fonctionnant suivant le cycle de stirling |
CN101463775B (zh) * | 2007-12-19 | 2011-06-15 | 孔令斌 | 斯特林可逆热机 |
US8096118B2 (en) * | 2009-01-30 | 2012-01-17 | Williams Jonathan H | Engine for utilizing thermal energy to generate electricity |
DE102012107064B4 (de) | 2011-12-17 | 2014-05-22 | Andre Zimmer | Heißgasmotor |
MD679Z (ro) * | 2013-03-01 | 2014-04-30 | ИНСТИТУТ ЭЛЕКТРОННОЙ ИНЖЕНЕРИИ И НАНОТЕХНОЛОГИЙ "D. Ghitu" АНМ | Maşină termică în baza ciclului Stirling |
WO2015139104A2 (pt) * | 2014-03-21 | 2015-09-24 | Hirosi Suzuki | Motor stirling de configuração delta |
CN103925110B (zh) * | 2014-04-30 | 2015-11-04 | 郭远军 | 一种v型高低压动力设备及其做功方法 |
USD923572S1 (en) * | 2020-11-22 | 2021-06-29 | Yi Zhang | Stirling engine |
USD923573S1 (en) * | 2020-11-22 | 2021-06-29 | Yi Zhang | Stirling engine |
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US273276A (en) * | 1883-03-06 | Feed-water adjustment for pumps | ||
US680237A (en) * | 1900-11-12 | 1901-08-13 | Maurice Auguste Eudelin | Motor for automobiles driven by explosion of inflammable vapors. |
US926564A (en) * | 1907-07-16 | 1909-06-29 | William H Hollopeter | Internal-combustion engine. |
US1909372A (en) * | 1931-05-06 | 1933-05-16 | Mccollum James Harry Keighley | Variable stroke internal combustion engine |
US2776573A (en) | 1954-03-01 | 1957-01-08 | Baldwin Lima Hamilton Corp | Variable reciprocating stroke mechanism |
US2822791A (en) * | 1955-07-01 | 1958-02-11 | Arnold E Biermann | Variable stroke piston engines |
US2873611A (en) * | 1955-07-01 | 1959-02-17 | Arnold E Biermann | Variable stroke mechanisms |
GB1266451A (de) * | 1969-02-21 | 1972-03-08 | ||
US3886744A (en) * | 1974-07-22 | 1975-06-03 | Philips Corp | Power-control system for stirling engines |
FR2465133A1 (fr) * | 1979-09-17 | 1981-03-20 | Bultot Gaston | Dispositif d'entrainement fonctionnel multiplicateur de force |
US4346677A (en) * | 1980-09-02 | 1982-08-31 | Nye Norman H | Combustion engine with substantially constant compression |
US4387566A (en) | 1981-03-11 | 1983-06-14 | Mechanical Technology Incorporated | Independently variable phase and stroke control for a double acting Stirling engine |
US4392350A (en) * | 1981-03-23 | 1983-07-12 | Mechanical Technology Incorporation | Stirling engine power control and motion conversion mechanism |
US4553392A (en) * | 1984-12-12 | 1985-11-19 | Stirling Technology, Inc. | Self pressurizing, crank-type Stirling engine having reduced loading of displacer drive linkages |
US4917066A (en) * | 1986-06-04 | 1990-04-17 | The Trustees Of Columbia University In The City Of New York | Swing beam internal-combustion engines |
GB2211262B (en) * | 1987-10-20 | 1991-07-24 | David Arthur Pritchard | Reciprocating drive mechanism |
US4970861A (en) * | 1989-11-07 | 1990-11-20 | Northrop Corporation | Geared rotary-to-linear motion converting system for bidirectional pump drive |
GB9008522D0 (en) * | 1990-04-17 | 1990-06-13 | Energy For Suitable Dev Limite | Reciprocatory displacement machine |
US5136987A (en) * | 1991-06-24 | 1992-08-11 | Ford Motor Company | Variable displacement and compression ratio piston engine |
JP2828935B2 (ja) * | 1995-09-19 | 1998-11-25 | 三洋電機株式会社 | ガス圧縮膨張機 |
-
2000
- 2000-05-29 AT AT0093600A patent/AT411844B/de not_active IP Right Cessation
-
2001
- 2001-05-29 CN CNB018100651A patent/CN1208544C/zh not_active Expired - Fee Related
- 2001-05-29 KR KR1020027014378A patent/KR100743954B1/ko not_active IP Right Cessation
- 2001-05-29 WO PCT/AT2001/000169 patent/WO2001092708A1/de active IP Right Grant
- 2001-05-29 US US10/276,958 patent/US6729131B2/en not_active Expired - Fee Related
- 2001-05-29 JP JP2002500089A patent/JP2003535262A/ja not_active Withdrawn
- 2001-05-29 EP EP01940002A patent/EP1285160B1/de not_active Expired - Lifetime
- 2001-05-29 AU AU2001273722A patent/AU2001273722B2/en not_active Ceased
- 2001-05-29 CA CA002405174A patent/CA2405174A1/en not_active Abandoned
- 2001-05-29 AU AU7372201A patent/AU7372201A/xx active Pending
- 2001-05-29 EA EA200201297A patent/EA003980B1/ru not_active IP Right Cessation
- 2001-05-29 BR BR0111662-2A patent/BR0111662A/pt active Search and Examination
- 2001-05-29 DE DE50113863T patent/DE50113863D1/de not_active Expired - Fee Related
- 2001-05-29 AT AT01940002T patent/ATE392545T1/de not_active IP Right Cessation
- 2001-05-29 MX MXPA02011800A patent/MXPA02011800A/es active IP Right Grant
-
2003
- 2003-07-18 HK HK03105200.2A patent/HK1052956B/zh not_active IP Right Cessation
Non-Patent Citations (1)
Title |
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See references of WO0192708A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE50113863D1 (de) | 2008-05-29 |
US20030167766A1 (en) | 2003-09-11 |
EP1285160B1 (de) | 2008-04-16 |
JP2003535262A (ja) | 2003-11-25 |
KR100743954B1 (ko) | 2007-07-30 |
KR20030005302A (ko) | 2003-01-17 |
HK1052956B (zh) | 2008-11-28 |
AT411844B (de) | 2004-06-25 |
HK1052956A1 (en) | 2003-10-03 |
CN1208544C (zh) | 2005-06-29 |
US6729131B2 (en) | 2004-05-04 |
AU2001273722B2 (en) | 2004-10-07 |
MXPA02011800A (es) | 2003-04-25 |
ATE392545T1 (de) | 2008-05-15 |
WO2001092708A1 (de) | 2001-12-06 |
EA200201297A1 (ru) | 2003-04-24 |
ATA9362000A (de) | 2003-11-15 |
CA2405174A1 (en) | 2002-10-07 |
CN1441875A (zh) | 2003-09-10 |
EA003980B1 (ru) | 2003-12-25 |
BR0111662A (pt) | 2003-05-20 |
AU7372201A (en) | 2001-12-11 |
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