EP0101565A1 - Thermocompressor with pressure actuated heating chamber bypass - Google Patents

Thermocompressor with pressure actuated heating chamber bypass Download PDF

Info

Publication number
EP0101565A1
EP0101565A1 EP83107126A EP83107126A EP0101565A1 EP 0101565 A1 EP0101565 A1 EP 0101565A1 EP 83107126 A EP83107126 A EP 83107126A EP 83107126 A EP83107126 A EP 83107126A EP 0101565 A1 EP0101565 A1 EP 0101565A1
Authority
EP
European Patent Office
Prior art keywords
heating chamber
cylinder
bypass
hot
thermocompressor
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Withdrawn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
EP83107126A
Other languages
German (de)
English (en)
French (fr)
Inventor
Mark Schuman
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 EP0101565A1 publication Critical patent/EP0101565A1/en
Withdrawn legal-status Critical Current

Links

Images

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
    • F02G1/053—Component parts or details
    • 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
    • F02G1/0435—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 the engine being of the free piston type
    • 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
    • F02G2255/00—Heater tubes
    • 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
    • F02G2270/80—Engines without crankshafts
    • 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
    • F02G2270/90—Valves
    • 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
    • F02G2280/00—Output delivery
    • F02G2280/50—Compressors or pumps

Definitions

  • the present invention relates generally to energy converters, more particularly to heat engines utilizing a regenerative fluid cycle, and still more particularly to a Stirling type free piston thermocompressor for pumping fluid or otherwise supplying a differential or cyclical pressure to a load.
  • the present invention is basically similar to my just-mentioned prior patent except for the addition, within the nipple in the hot end of the cylinder, of a short conduit and check valve, the check valve being optionally double-acting and optionally spring-biased, providing automatically a heating chamber bypass during Stirling cycle .cooling so that most or virtually all of the gas or compressible fluid between the nipple and the piston as the piston is coasting downward toward and eventually over the nipple can take the easier (lower impedance) and cooler path through the short vertical conduit and thence through a short segment of the heating chamber inlet conduit toward the hot end of the cylinder bypass for cooling, and very little gas, ten per cent or even less if desired, will have to take the higher impedance and hotter path through the heating chamber toward the hot (lower) end of the cylinder bypass for subsequent cooling.
  • thermocompressor of my above-mentioned prior patent wherein, depending partly on the chosen thickness of the annular region between the nipple and the cylinder sidewall, a substantial fraction of such gas, typically perhaps more than one-half, returns to the hot end of the cylinder bypass via the heating chamber.
  • gas flowing from the hot (expansion) space to the cold (compression) space for Stirling cycle cooling virtually all such gas must return through the heating chamber, i.e., gas flowing from the hot (expansion) space to the cold (compression) space for Stirling cycle cooling.
  • the heating chamber can be smaller and require less heat, and thus produce less fluid drag, while the regenerator can also be smaller and produce less thermal and viscous losses (fluid drag).
  • the present invention facilitates the use of a thermocompressor or Stirling type engine of smaller size, higher efficiency, and greater specific power output than prior art devices of this type, e.g., free piston, Stirling cycle engines.
  • FIG. 1 is a partly schematic, elevational, cross-sectional view of a free piston Stirling type thermocompressor employing the principles of the present invention.
  • a thermocompressor, or thermally driven oscillating piston apparatus designed for utilizing thermal energy to cyclically heat and cool a compressible fluid, such as a gas, thereby developing a cyclical pressure for driving a load.
  • the apparatus includes a substantially closed cylinder I having a side-wall 2 of circular cross-section and end-walls or end-plates 3 and 4 at the upper and lower ends of the cylinder.
  • the lower or hot end wall 4 includes a nipple or plug or projection 5 of circular cross-section projecting upwardly toward the free piston 6.
  • Piston side- wall 7 forms a loose sliding seal with the sidewall 2 of cylinder 1, thereby dividing the cylinder into variable volume hot and cold ends of the cylinder below and above the piston.
  • the free piston 6 is cup-shaped with the open end of the cup facing downward toward the nipple 5 so that the piston can pass almost completely over the outer cylindrical surface 9 of the nipple.
  • Cylinder 1 has a cylinder bypass means 10 connecting the hot and cold cylinder ends thereby providing a bypass region of the cylinder for the coasting of the free piston as the piston oscillates along the cylinder axis.
  • the cylinder bypass includes, in seriatim, cold cylinder bypass ports 11 defined in the cylinder sidewall in the cold cylinder end; cooling chamber means 13, possibly including a fan, for cooling the working gas by external cooling means; thermal regenerator 15 for conserving heat by storing heat from and releasing heat to the working gas each cycle (e. g., stainless steel wool); and hot bypass conduits 16 which terminate in hot bypass ports 17 defined in cylinder sidewall 2 in the hot end of the cylinder.
  • Figure 1 illustrates the thermocompressor as being symmetrical with respect to the cylinder axis, and thus having two of each off-axis port or conduit, but it should be understood that one of each would be sufficient; alternatively, more than two of each off-axis port or conduit can also be used.
  • Figure 1 shows the piston coasting upward in the bypass region of the cylinder during the first coasting portion, or first power portion, of the oscillatory cycle, forcing cool gas from the cold cylinder end downward through the cylinder bypass (see arrows) for heating and build-up of pressure.
  • the gas exits the hot end of the cylinder bypass in a substantially defined stream flowing out of each hot cylinder bypass conduit 16 via each hot cylinder bypass port 17 into the hot cylinder end after being partially heated by the annular-shaped regenerator 15 in the annular-shaped cylinder bypass 10.
  • heating cham-21 ber inlet conduit passes through the nipple 5 and terminates in heating chamber inlet ports 20 in the outer cylindrical surface 9 of the nipple in the hot cylinder end.
  • Inlet ports 20 are positioned directly in the paths of the fluid streams flowing out of hot cylinder bypass ports 17, at a distance from ports 17 equal to a very small fraction, such as one-tenth or less, of the cylinder radius, and the conduit portions adjoining each pair of ports 17 and 20 are in-line or coaxial, as described in my above-mentioned U.S. Patent No.
  • cylinder hot end-wall 4 has a cup-shaped projection 26 projecting downward toward the heat source 25, which can be almost any reasonably hot source of heat, and around the projection 26 is a double-walled, cup-shaped envelope or can 27 heated by the heat source 25 and forming hot passageways with cup 26 for heating the fluid stream flowing through or into the heating chamber 24.
  • the heating chamber 24 as well as the cooling chamber can have internal/external fins (not shown).
  • the can 27 extends upwardly around the thermocompressor to provide a good, low temperature seal at the cold cylinder end for sealing in the high pressure working fluid, e.g., helium, for a long period of time.
  • the cylinder hot end-plate 4, with its two projections 5 and 26, is heated only indirectly by the heat source, and thus is not quite as hot as the hottest portions of can 27.
  • the gas stream after being heated in the heating chamber, flows upward through ports 28 of heating chamber outlet conduits 29 and thence into the hot cylinder end below the piston, via outlet ports in the upper face 30 of the nipple. Conduits 29 pass behind T-arm conduits 22.
  • thermocompressor The pressure increase throughout the thermocompressor during the first power portion of the cycle allows some of the working gas to be fed via load ports 46 of load conduits 45 in cylinder cold endwall 3 to a fluid driven load (not shown).
  • This pressure increase which results from raising the average temperature of the working gas in the thermocompressor by heating as much of the gas as possible, is facilitated by labyrinth grooves 36 on the upper portion of the outer cylindrical surface 9 of the nipple, just below upper nipple face 30, which grooves reduce leakage of gas upward along annular region 18 from the above-mentioned gas stream or jet flowing out of hot cylinder bypass conduit or nozzle 16 toward the heating chamber 24.
  • thin-walled piston segment 37 which serves as the thin wall of the upside down cup formed by the cup-shaped free piston 6.
  • Thin-walled piston segment 37 is needed later in the cycle to block the hot bypass ports 17 of the cylinder bypass 10 during a hot rebound portion of the cycle following the second power portion of the cycle.
  • thermocompressor bypass conduit 50 leading from port 51 in upper nipple face 30 downward along the cylinder axis to port 52, by check valve wafer 60.
  • Port 52 connects the short, vertical, low impedance, heating chamber bypass conduit 50 with the mid-point or node of T-shaped heating chamber inlet conduit 21.
  • the upward movement of the piston and the pressure drop through the heating chamber means due to fluid drag on the gas stream result in a greater pressure in inlet conduit 21 than in the heating chamber bypass conduit 50 and in the cylinder space between conduit 50 and the upward moving free piston.
  • This differential fluid pressure across check valve wafer 60 holds the - wafer upward against port 52 of the short heating chamber bypass conduit 50 during upward movement of the free piston 6, thereby blocking port 52 and conduit 50 and thus facilitating the flow of the fluid stream into the heating chamber for heating therein during the first coasting portion of the cycle and even during an initial portion of the cold rebound portion of the cycle.
  • check valve wafer 60 is positioned centrally within nipple 5 and four-way horizontal T-shaped at the A intersection of the two arms 22 of heating chamber inlet conduit 21; the vertical, common flow, axial, trunk portion of T-shaped heating chamber inlet conduit 21, extending from the intersection downwardly toward the heat source; and, lastly, the short, vertical, axial (along the cylinder axis), low impedance, heating chamber bypass conduit 50 extending upwardly from the intersection.
  • Check valve wafer 60 sees, therefore, the above-mentioned higher pressure above it in conduit 50, and the lower pressure below it in conduit 21, and responds to this differential fluid pressure by moving downward away from port 52 toward the trunk portion of conduit 21, thereby unblocking heating chamber bypass conduit 50 and allowing most of the gas in the hot cylinder end to flow through conduits 50 and 22, thereby bypassing the higher fluid flow impedance and hotter paths through the heating chamber, as it travels to the hot cylinder bypass ports 17 for cooling in the cylinder bypass.
  • conduit 50 and check valve wafer 60 combine to form a pressure actuated heating chamber bypass, having the advantages discussed earlier.
  • Thin-walled piston segment 37 after passing as a sleeve over the upper portion of the outer cylindrical surface 9 of the nipple including the labyrinth grooves 36, begins blocking the hot end of the cylinder bypass by passing over and thus blocking the hot cylinder bypass ports 17, whereby the second coasting portion, or second power portion, of the cycle ends and the hot rebound portion of the cycle begins, wherein gas trapped in the hot cylinder end below the piston is compressed and forced by the piston into the nipple and heating chamber for thermal lag heating of the gas and thus a thermally augmented spring effect which drives the free piston back toward the cold cylinder end with a greater speed and momentum when the piston unblocks hot cylinder bypass ports 17 at the end of the hot rebound portion of the cycle than the speed and momentum of the piston when it blocked ports 17 at the beginning of the hot rebound.
  • Thermal lag means that the times of occurrence of the maximum instantaneous temperature and pressure of the trapped gas will lag the time of occurrence of the maximum instantaneous compression ratio (bottom of the piston stroke), thereby producing a greater average pressure on the piston face after maximum compression ratio than before maximum compression ratio occurs (averaged over equal portions of the stroke, chosen symmetrically with respect to the point of maximum instantaneous compression ratio).
  • Thermal lag driving of an oscillatory wall of a closed chamber is discussed in various of my patents, including my U.S. Patent No. 3,807,904 issued April 30, 1974, entitled"Oscillating Piston Apparatus".
  • Heating chamber means 24 can combine the qualities needed for both Stirling cycle type heating of fluid and thermal lag driving of a free piston.
  • Cold rebound chamber 40 being warmer than the gas in the cold cylinder end in general, may also provide some thermal lag driving of the free piston.
  • I have built a thermally driven partial model which demonstrates coasting of a free piston in a cylinder bypass region, and thermal lag driving of the free piston. The model is powered by waste thermal energy from a standard 200 watt incandescent light bulb.
  • heating chamber bypass conduit 50 would be blocked by check valve wafer 60 by the time cylinder bypass ports 17 at the hot end of the cylinder bypass become unblocked by the piston segment 37, and conduit 50 will remain blocked, for reasons of pressure difference discussed earlier, during at least the first coasting portion of the cycle, and also during at least an initial portion of the first half of the subsequent cold rebound portion of the cycle.
  • Check valve wafer 60 is guided by its loose fit in the nipple housing, which allows relatively free fluid flow around the wafer 60 when the wafer moves away from port 52. If desired, the wafer can be guided, or supported, or even spring-biased, by means such as spring-arm 61 of spring 62 mounted in a slightly enlarged upper section 64 of the axial, common flow, trunk portion of T-shaped inlet conduit 21 of the heating chamber means 24.
  • spring 62 is not required.
  • the check valve can be considered to be the wafer 60 plus the adjoining or proximate structure of the nipple acting as the walls or housing of the check valve, and including the four conduit ports of the four-way intersection at which the check valve wafer 60 is located. If four hot cylinder bypass conduits are used instead of two, check valve wafer 60 can be centrally disposed at a six-way intersection of conduits on the cylinder axis within the nipple 5. Other combinations are of course possible.
  • the enlarged but very short cylinder section in which wafer 60 is loosely fit can be extended either upward or downward to get the wafer out of the way of the main body of fluid flow by forming a recessed valve seat at either port 52 of conduit 50 or at the top of the axial portion of inlet conduit 21, or at both of these locations, in which latter case it is evident that wafer 60 is being utilized as a moving member of a double-acting check valve within the nipple (which can be true whether or not the - valve seats are recessed). However, it is not necessary for wafer 60 to block the lower or trunk portion of the T-shaped inlet conduit 21.
  • small raised portions or standoffs can be provided on top of the trunk portion of conduit 21, underneath wafer 60, to keep the wafer from seating against the trunk portion and blocking flow in the trunk portion.
  • the standoffs could be provided to allow a small flow of gas through the heating chamber in parallel with the flow through heating chamber bypass conduit 50 during the second power portion of the cycle in order to further reduce fluid drag; or the standoffs could improve the thermal lag driving of the free piston during the subsequent hot rebound; or, the standoffs could facilitate the timely and proper blocking of port 52 and conduit 50 by the wafer upon subsequent upward movement of the free piston during the hot rebound. It is, after all, the main purpose of the check valve wafer to block and unblock the heating chamber bypass conduit at the proper times in the cycle without restricting fluid flow in the required or critical portions of the heating chamber inlet conduit in the nipple.
  • the device can be easily started by either a single pressure pulse or an oscillatory pressure, applied below the piston, i.e., to any portion of the gas volume below the free piston, as illustrated in my U.S. Patents 3,489,335 and 3,807,904. Or a suction pulse or oscillatory suction can be applied above the piston.
  • a voltage applied to a coil of the alternator could produce such a suction.
  • such an alternator is likely to be self-starting, if suitably designed.
  • thermocompressor having a thermal lag driven (self-oscillating), coasting free piston is particularly suited to the pressure actuated, heating chamber bypass of the present invention, for the following reasons.
  • a good size conduit is needed between the regenerator and heating chamber to easily and rapidly carry fluid between the two in order to facilitate good Stirling cycle heating and cooling of the working fluid.
  • the heating chamber bypass of the present invention also needs such a conduit to easily and rapidly conduct fluid directly from the cylinder hot space to the regenerator during Stirling cycle cooling.
  • the heater-regenerator conduit (conduits 16 and 21 in Figure 1) serves both purposes simultaneously.
  • the heater-regenerator conduit preferably passes through the hot end of the cylinder, whereby it passes very close to the gas in the cylinder hot space below the piston.
  • This closeness also benefits the heating chamber bypass of the present invention, since the heating chamber bypass conduit (conduit 50) can thus be very short and therefore be of very low fluid flow impedance and add very little dead volume to the hot cylinder end.
  • the passage of the heater-regenerator conduit through the hot end of the cylinder also serves two purposes at once.
  • the thermal lag driven, coasting free piston apparatus preferably includes a projection or nipple in the hot cylinder end to provide a convenient housing through which both the heater-regenerator conduit and a heating chamber outlet conduit may pass, to reduce loss of fluid from the fluid stream flowing across the gap in the heater-regenerator conduit (the gap between ports 17 and 20), and to fill up odd-shaped dead space in the hot cylinder end adjacent the two just-mentioned conduits, filling up the dead space with an axially symmetric form over which a simple, cup-shaped free piston can pass.
  • nipple provides a convenient housing, at just the right location, for the check valve and short heating chamber bypass conduit of the present invention, without requiring fittings and conduits external to the cylinder, and without introducing significant fluid drag or dead space or new thermal losses. Therefore, in these respects, the nipple, too, serves multiple purposes at once.
  • thermocompressor or engine would not benefit nearly as much, if indeed at all, from a heating chamber bypass synchronized with the cycle, such as the pressure actuated heating chamber bypass of the present invention.
  • thermodynamic cycle may deviate substantially from the Stirling cycle.
  • thermodynamic efficiency can still be very high, and should be significantly higher with the inclusion of the automatically synchronized heating chamber bypass of the present invention than without it, for virtually any type of load.
  • the cycle can be considered a modified Stirling cycle with a very high thermal efficiency and a variable Stirling lag angle between the phases of the two pistons. The lag angle would automatically shift to increase power as the magnitude of the load increases. I was able to determine this by analogy with an RLC circuit (resistance-inductance-capacitance).
  • the heating chamber inlet conduit 21 would be basically Y-shaped rather than T-shaped.
  • each hot cylinder bypass conduit had its own heating chamber inlet conduit, there could be one or more elbow- shaped heating chamber inlet conduits, each with a heating chamber bypass conduit and check valve.
  • the check valve might be replaced by another form of pressure sensitive valve or valve suitably synchronized to the cycle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Fluid-Pressure Circuits (AREA)
EP83107126A 1982-07-23 1983-07-20 Thermocompressor with pressure actuated heating chamber bypass Withdrawn EP0101565A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US40140682A 1982-07-23 1982-07-23
US401406 1982-07-23

Publications (1)

Publication Number Publication Date
EP0101565A1 true EP0101565A1 (en) 1984-02-29

Family

ID=23587621

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83107126A Withdrawn EP0101565A1 (en) 1982-07-23 1983-07-20 Thermocompressor with pressure actuated heating chamber bypass

Country Status (8)

Country Link
EP (1) EP0101565A1 (da)
JP (1) JPS5929784A (da)
AU (1) AU1711083A (da)
BR (1) BR8303891A (da)
DK (1) DK334683A (da)
ES (1) ES8406631A1 (da)
IL (1) IL69312A0 (da)
ZA (1) ZA835293B (da)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7269961B2 (en) * 2005-07-22 2007-09-18 Pendray John R Thermodynamic cycle apparatus and method
WO2012107480A1 (en) * 2011-02-10 2012-08-16 Boostheat Gaseous fluid compression device
US20150159586A1 (en) * 2012-07-26 2015-06-11 Sumitomo (Shi) Cryogenics Of America, Inc. Brayton cycle engine
TWI512190B (zh) * 2014-10-02 2015-12-11 Univ Nat Cheng Kung 熱延遲式史特靈冷熱複合機及其使用方法
CN112576404A (zh) * 2019-09-27 2021-03-30 中国科学院理化技术研究所 自由活塞和气缸组件以及斯特林发动机
US11137181B2 (en) 2015-06-03 2021-10-05 Sumitomo (Shi) Cryogenic Of America, Inc. Gas balanced engine with buffer

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1459453A (fr) * 1965-11-17 1966-04-29 Moteur thermique pouvant fonctionner à basse température
FR2128631A1 (da) * 1971-03-05 1972-10-20 Schuman Mark
FR2363006A1 (fr) * 1976-08-27 1978-03-24 Schuman Mark Thermocompresseur a piston libre
FR2425552A1 (fr) * 1978-05-11 1979-12-07 Schneider Christian Moteur a gaz chaud, fonctionnant aussi avec piston libre
DE3223511A1 (de) * 1981-09-14 1983-03-24 William T. 45701 Athens Ohio Beale Freikolben-stirlingmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1459453A (fr) * 1965-11-17 1966-04-29 Moteur thermique pouvant fonctionner à basse température
FR2128631A1 (da) * 1971-03-05 1972-10-20 Schuman Mark
FR2363006A1 (fr) * 1976-08-27 1978-03-24 Schuman Mark Thermocompresseur a piston libre
FR2425552A1 (fr) * 1978-05-11 1979-12-07 Schneider Christian Moteur a gaz chaud, fonctionnant aussi avec piston libre
DE3223511A1 (de) * 1981-09-14 1983-03-24 William T. 45701 Athens Ohio Beale Freikolben-stirlingmaschine

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7269961B2 (en) * 2005-07-22 2007-09-18 Pendray John R Thermodynamic cycle apparatus and method
RU2581469C2 (ru) * 2011-02-10 2016-04-20 Бустхит Устройство для сжатия газообразных сред
FR2971562A1 (fr) * 2011-02-10 2012-08-17 Jacquet Luc Dispositif de compression de fluide gazeux
CN103502641A (zh) * 2011-02-10 2014-01-08 布斯特赫特公司 气态流体压缩装置
JP2014510865A (ja) * 2011-02-10 2014-05-01 ブーストヒート ガス状流体圧縮デバイス
US9273681B2 (en) 2011-02-10 2016-03-01 Boostheat Gaseous fluid compression device
CN103502641B (zh) * 2011-02-10 2016-03-23 布斯特赫特公司 气态流体压缩装置
WO2012107480A1 (en) * 2011-02-10 2012-08-16 Boostheat Gaseous fluid compression device
US20150159586A1 (en) * 2012-07-26 2015-06-11 Sumitomo (Shi) Cryogenics Of America, Inc. Brayton cycle engine
US10677498B2 (en) * 2012-07-26 2020-06-09 Sumitomo (Shi) Cryogenics Of America, Inc. Brayton cycle engine with high displacement rate and low vibration
TWI512190B (zh) * 2014-10-02 2015-12-11 Univ Nat Cheng Kung 熱延遲式史特靈冷熱複合機及其使用方法
US11137181B2 (en) 2015-06-03 2021-10-05 Sumitomo (Shi) Cryogenic Of America, Inc. Gas balanced engine with buffer
CN112576404A (zh) * 2019-09-27 2021-03-30 中国科学院理化技术研究所 自由活塞和气缸组件以及斯特林发动机

Also Published As

Publication number Publication date
DK334683D0 (da) 1983-07-20
ZA835293B (en) 1984-08-29
DK334683A (da) 1984-01-24
BR8303891A (pt) 1984-02-28
ES524390A0 (es) 1984-07-01
IL69312A0 (en) 1983-11-30
JPS5929784A (ja) 1984-02-17
ES8406631A1 (es) 1984-07-01
AU1711083A (en) 1984-01-26

Similar Documents

Publication Publication Date Title
US4072010A (en) Thermally driven piston apparatus
US4327550A (en) Thermodynamic machine
US3990246A (en) Device for converting thermal energy into mechanical energy
EP2406485B1 (en) Heat engine with regenerator and timed gas exchange
US3767325A (en) Free piston pump
US4490974A (en) Isothermal positive displacement machinery
US4132505A (en) Thermocompressor utilizing a free piston coasting between rebound chambers
US20170030294A1 (en) Energy transfer machines
JPS5852151B2 (ja) 熱ガス往復機械
JP3806185B2 (ja) 流体制御機構付蓄熱型冷凍機及び流体制御機構付パルス管型冷凍機
US4622813A (en) Stirling cycle engine and heat pump
EP0162868B1 (en) Stirling cycle engine and heat pump
US6003312A (en) Engine
EP0055769B1 (en) Stirling engine
JPS5929784A (ja) 熱式圧縮機及びエネルギ−変換機
JPS6331660B2 (da)
GB2273975A (en) Refrigerator for cryogenic temperatures
GB2333131A (en) A externally heated gas engine having two heat loops
CN113701391A (zh) 一种回热式装置及运行方法
US20100064681A1 (en) Method for increasing performance of a stirling or free-piston engine
JPS6220659A (ja) スタ−リングエンジン
JP2718147B2 (ja) スターリング機関及びスターリング機関の出力制御方法
RU2115815C1 (ru) Двигатель стирлинга
SU1224514A1 (ru) Криогенератор
RU2131563C1 (ru) Устройство для нагрева и охлаждения воздуха

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI NL SE

17P Request for examination filed

Effective date: 19840816

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19880218