EP3919729A1 - Moteur stirling à membrane - Google Patents

Moteur stirling à membrane Download PDF

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Publication number
EP3919729A1
EP3919729A1 EP21182490.9A EP21182490A EP3919729A1 EP 3919729 A1 EP3919729 A1 EP 3919729A1 EP 21182490 A EP21182490 A EP 21182490A EP 3919729 A1 EP3919729 A1 EP 3919729A1
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EP
European Patent Office
Prior art keywords
membrane
heat
gas
hot
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.)
Pending
Application number
EP21182490.9A
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German (de)
English (en)
Inventor
Jürgen KLEINWÄCHTER
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Individual
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Individual
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Filing date
Publication date
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Publication of EP3919729A1 publication Critical patent/EP3919729A1/fr
Pending 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
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • 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
    • F02G1/04—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
    • F02G1/055—Heaters or coolers
    • 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
    • F02G1/057—Regenerators
    • 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
    • F02G2244/02—Single-acting two piston engines
    • F02G2244/06—Single-acting two piston engines of stationary cylinder type
    • F02G2244/10—Single-acting two piston engines of stationary cylinder type having cylinders in V-arrangement

Definitions

  • the invention relates to a membrane Stirling engine.
  • Classic Stirling engines consist of an arrangement of rigid, pressure-resistant, gas-filled cylinders, heat exchangers for heating and cooling the hermetically enclosed working gas, displacement pistons for periodically shifting the working gas from the cold to the hot side and back, an interposed heat generator and working pistons for transferring the thermal pressure fluctuations of the Gas generated work to the outside.
  • the present invention is based on the object of providing an alternative or improvement to the prior art.
  • the inventors have identified a problem from the prior art that the ideal thermodynamic process assumes that the expansion is isothermal. Heat has to be added to the relaxing medium while it is relaxing.
  • a bladder is provided in the invention. The pressure is the same inside and outside, so the required work of deformation approaches zero.
  • the Stirling engine according to the invention has a special, specific design:
  • the working gas of the Stirling machine is located both in its hot part and in its cold part in membrane shells with negligible flexural rigidity, which are hermetically sealed at one end and open tightly with their open end and open into the hot or cold space of a regenerator box.
  • the gas to be heated is in this case, for example, bags that are formed by thin-walled membrane shells of negligible flexural rigidity. These membrane bags hermetically enclose the working gas and each open into the regenerator box on their front side. The membrane bags arranged to the right and left of the regenerator box together with this form a gas-tight unit. As much gas is filled in as corresponds to the gas volume of the regenerator box and half of the maximum volume of both bags.
  • the membrane bags are immersed in hot or cold liquid.
  • the regenerator box separates the hot liquid space from the cold liquid space.
  • the entire unit of gas-filled membrane bags, regenerator box and heat-transferring hot or cold liquid is in turn located in a closed, liquid-tight and pressure-tight housing.
  • the hot liquid space as well as the cold space are provided with hydraulic pistons (or similar technical means such as bellows, hydraulic cushions and the like) that can displace exactly the volume of liquid that corresponds to half of the maximum gas volume in the membrane bags.
  • the hydraulic pistons arranged on both the hot and the cold side of the pressure-tight housing are connected to one another via an eccentric so that they move with a corresponding phase shift (typically: 90 °) to one another.
  • the rotating axis of the eccentric (or an equivalent technical device such as a swash plate or a cam plate) is provided with a flywheel.
  • the configuration described corresponds to a Stirling engine of the alpha design.
  • cylindrical tubes are designed as membrane bags.
  • Fig. 3 the principle of the "pulsating" heat exchanger displacer is visualized on the basis of a single membrane bag.
  • the membrane bag is held on its front sides with spring holders.
  • the machine moves the contents of the membrane bag cleverly, and the membrane bag is also a very good heat exchanger. Because the membrane bag becomes a micro heat exchanger whenever it is laid flat.
  • FIG. 4 schematically shown formation of a membrane bag by
  • Clamping two flat membranes in a frame is particularly advantageous because in this way whole "stacks" of membrane bags can be connected to the regenerator box in the most densely packed form and thus the performance of the machine can be increased ( Fig. 5 ).
  • suitable grids are attached according to the invention between two membrane bags in each case. These are built into the mechanical frame construction that is used to hold the "membrane bag stacks" ( Fig. 6 ).
  • the new membrane design of a Stirling engine is intended to achieve significantly higher Carnot degrees of realization than previous machines, which achieve a maximum of 50% of the Carnot degree of efficiency.
  • Isothermally operating machines with low temperature storage between the working gas and the heater or cooler fluid, with minimal dead volume and the lowest possible displacement drive line (through hydrostatic deformation of thin membranes), should allow degrees of realization of 80% and more. This makes it possible to achieve good mechanical efficiencies even at relatively low heater temperatures.
  • Another advantage of the relatively low temperature level opens up the possibility of using simple pressurized water heat accumulators for inexpensive storage of solar heat and thus for solar around the clock operation of such machines (power and electricity autonomy).
  • thermodynamics such machines are fundamentally superior to the compression refrigeration machines used today in terms of refrigeration and performance figures.
  • Another advantage compared to the state of the art is based on the fact that such refrigeration machines / heat pumps manage without climate-damaging refrigerants and only use air, water, antifreeze and conventional structural materials (steel or fiber-reinforced plastics).
  • the advantage of the membrane Stirling machines is that they are only abundantly available, inexpensive and environmentally friendly materials and, in the case of storage, use pressureless (T ⁇ 100 ° C) or pressurized water storage tanks (T> 100 ° C).
  • thermal machines In contrast to photovoltaics, which basically only provides electrical energy, the use of thermal machines has the further advantage of automatically providing power, electricity, cold or heat and waste heat (combined heat and power) and thus much better the entire range of decentralized requirements To provide forms of energy.
  • solar thermal machines will only have the potential to compete with the inherently wear-free solar semiconductors (photovoltaics, thermoelectrics) if they can be manufactured inexpensively and are extremely durable and low-maintenance.
  • the price target can be achieved through the choice of material.
  • the principle of the hydrostatic, gentle deformation of thin, elastic membranes with relatively low working frequencies (a few Hertz) offers fundamentally - in contrast to the established technologies with classic mechanically moved displacers and the necessary seals, the potential for extreme longevity.
  • the principle of the membrane Stirling engine is not limited to the described, preferred topology of membrane film bags. How out Fig.7 It can be seen, for example, thin-walled hoses in various configurations can also be used. According to the invention, these can be wrapped with fibers in such a way that they are pressure-resistant in the unfolded state with a circular cross-section, and nonetheless (due to their negligible flexural rigidity) can be deformed hydrostatically without force.
  • the space between the plates is filled with water that has been doped with a gel former in such a way that no heat convection occurs in this intermediate zone.
  • Such an embodiment of the diaphragm Stirling engine is particularly suitable for pressureless, large machines built into the earth.
  • FIG. 10 such a machine is shown schematically.
  • a square pit is made in the earth.
  • the walls of this pit are thermally insulated - typically with a rot-proof, closed-cell insulation material such as foam glass.
  • the intermediate channel installed in the middle of the pit, consisting of two vertical foam glass walls, divides the pit into two identical large chambers, one of which is filled with hot water and the other with cold water.
  • the intermediate channel is also filled with water, which is doped with a gel former in such a way that the water becomes a gel.
  • the gel-like water mechanically stabilizes the intermediate channel against the pressure fluctuations generated by the Stirling cycle in the two working chambers, but no longer transports heat by convection. This is important so that the linear temperature coefficient, the builds up in the regenerators during operation, is not destroyed.
  • Two mechanically stable, heat-insulated circular working pistons are arranged on the upper sides of the hot and cold working chambers. These hang in a large tire, one lip of which is tightly connected to the piston at its periphery, while the other lip is tightly connected to a likewise circular profile of the hot or cold chamber.
  • the tire fulfills the function of a robust "piston ring", which hermetically seals the oscillating piston between the interior (water) and the exterior (air).
  • the hot and cold sides pump each other through non-return valves due to the internal pressure fluctuating from the positive to the negative pressure, both water from the hot storage tank and from the cold storage tank.
  • Membrane pulsator machines of this type do not require any mechanical decoupling and are very small due to the high working frequencies.
  • the "heart" of the diaphragm Stirling engine is based on flexible, thin-walled bags: the pulsators, which contain the working gas, periodically move and isothermally heating and cooling it. Because of their inherent characteristics, in particular those of isothermal compression or expansion of gases, these pulsators also make it possible, according to the invention, to implement technical units other than those of Stirling engines.
  • a typical application of this type is the "isothermal hydraulic accumulator".
  • Fig. 13 a classic hydraulic accumulator is shown schematically. It is typically used to temporarily store the excess energy that occurs in a system at certain points in time and to supply it again at the point in time when the system needs additional energy.
  • the oil is pumped into the storage tank under pressure and compresses the gas (n 2 ) in the rubber bladder. The process takes place adiabatically.
  • Discharge The compressed gas (n 2 ) expands and pushes the oil out of the reservoir. This pressurized oil can then drive actuators such as cylinders and hydraulic motors.
  • a hydraulic accumulator is a vehicle whose drive shaft is coupled to a hydraulic pump in such a way that when the vehicle is braked, oil is pumped, thereby compressing the gas in the accumulator.
  • the energy temporarily stored in the "gas spring” in this way can then, when the vehicle is to be accelerated in succession, be recovered via the pump, which now works as a hydraulic motor, and fed to the drive shaft.
  • the process of gas compression described can now be isothermalized by creating a large surface area for heat exchange between the pressurized oil and the gas to be compressed.
  • an actuator (5) pressures the fluid (2) (preferably hydraulic oil) into a pressure vessel in which there is a sufficiently large number of hermetically sealed pulsator membrane bags filled with gas (N 2 , air, other gases) ( 1) are located.
  • “Sufficiently large number” here refers to the surface of the pulsator bag. This is measured in such a way that the pressure generated by hydrostatic compression Compression heat in gas is transferred well to the fluid around it, with its heat capacity which is orders of magnitude higher, and thus the desired, quasi-isothermal compression takes place.
  • the "gas springs" implemented by the pulsators push the fluid in the opposite direction through the actuator, which now does not act as a pump, as in the previous work cycle, but as an expander (machine) and converts the pneumohydraulically stored energy back into mechanical energy with a high degree of efficiency converts back.
  • the gas compression heat absorbed in the fluid is withdrawn from the circuit with each work cycle via coolers (3 and 4).
  • the pulsator bags are not hermetically sealed but are periodically filled with ambient air at atmospheric pressure by means of an auxiliary pump whenever the fluid does not exert any pressure on them.
  • the fluid which is ideally water for this application, compresses the air in the pulsator bags in the next work cycle, which flows through a check valve into a compressed air reservoir.
  • the heat given off to the water via the pulsator surface during compression is recooled by a cooler (active or passive) when the water is pumped back into the now sucking instead of pressing pump.
  • the arrangement can according to the invention in the following manner in a, from the
  • flywheel energy is used to pump the water back into the pulsator chamber after the expansion (this process requires minimal energy, because at this point the pulsator bags blow their air off into the environment).
  • the isothermally working air (gas) compressor with integrated compressed air storage and isothermally working actuator power machine is particularly a good possibility for lossless long-term storage of solar energy. Only if this is realized with good economy and using ecologically harmless and abundant material resources can, it will become possible to realize the inherent strength of solar systems, the realization of decentralized autonomous base load power plants of adapted size.
  • the drive energy of the isothermal compressor can come from photovoltaic modules, for example.
  • the mechanical energy that can then be withdrawn from the compressed air storage system via the actuator when required has, in addition to the advantages listed above in comparison to the electrochemical storage system, other specific advantages: no inverters are required to generate alternating and electric current - the rotating generator generates this automatically; If necessary, mechanical energy can be drawn directly from the unit.
  • a solar-powered diaphragm Stirling engine such as the one on which this application is based is particularly suitable for driving the compressor unit.
  • solar-to-electricity efficiency 34%.
  • solar compressed air filling stations can also be implemented with the technology described.
  • Fig. 16 is shown schematically how solar concentrators (1) on the roof of the garage drive the described isothermal compressor (3) and fill large, fixed compressed air reservoirs (4).
  • compressed air reservoirs preferably lightweight fiber composite containers shaped as load-bearing structural elements.
  • These vehicle storage tanks can be "refueled” very quickly with compressed air from the fixed storage tanks via compressed air lines (5).
  • Isothermal actuators as in the are assigned to the vehicle storage system Fig.16b shown. These preferably operate four individually controllable hydraulic motors integrated in the vehicle wheels.
  • a main feature of the membrane Stirling engine presented here (which the applicant plans to market as a "pulsator machine") is that the heat exchange and displacement bodies installed in the transfer fluid, i.e. the pulsators, consist of elastic, deformable membrane structures.
  • the pulsators consist of elastic, deformable membrane structures.
  • a suitable single or multi-layer film can in particular serve as the “membrane”.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Separation Using Semi-Permeable Membranes (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP21182490.9A 2015-03-13 2016-03-14 Moteur stirling à membrane Pending EP3919729A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102015003147 2015-03-13
PCT/DE2016/000108 WO2016146096A2 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP16736768.9A EP3280900B1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP16736768.9A Division EP3280900B1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Publications (1)

Publication Number Publication Date
EP3919729A1 true EP3919729A1 (fr) 2021-12-08

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Family Applications (3)

Application Number Title Priority Date Filing Date
EP16736768.9A Active EP3280900B1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182490.9A Pending EP3919729A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182497.4A Pending EP3919730A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

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EP16736768.9A Active EP3280900B1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

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EP21182497.4A Pending EP3919730A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Country Status (9)

Country Link
US (1) US11047335B2 (fr)
EP (3) EP3280900B1 (fr)
CN (1) CN107532541B (fr)
DE (1) DE112016001190A5 (fr)
ES (1) ES2891796T3 (fr)
MA (1) MA41914A (fr)
MX (1) MX2017011696A (fr)
PT (1) PT3280900T (fr)
WO (1) WO2016146096A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11035596B2 (en) 2019-07-12 2021-06-15 King Abdulaziz University Solar energy powered Stirling duplex machine with thermal storage tank
CN111692056A (zh) * 2020-07-01 2020-09-22 中国石化集团胜利石油管理局有限公司新能源开发中心 一种地热发电装置
CA3212585A1 (fr) 2021-03-19 2022-09-22 Ronald Alan HURST Moteurs thermiques et pompes a chaleur dotees de separateurs et deplaceurs
WO2023249505A2 (fr) * 2022-06-21 2023-12-28 Arpad Torok Nouveau procédé pour les compression et détente isothermes de gaz et dispositifs pour son application

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2296047A (en) * 1994-12-15 1996-06-19 Jonathan Maxwell Boardman Stirling cycle engine
WO2001063186A1 (fr) * 2000-02-25 2001-08-30 586925 B.C. Inc. Appareil et procede de transmission de chaleur utilisant un cycle a recuperation de chaleur actif
WO2011153979A2 (fr) * 2010-06-12 2011-12-15 Forschungszentrum Jülich GmbH Mécanisme d'entraînement en poussée discontinu et moteur stirling

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US1007422A (en) * 1911-02-16 1911-10-31 Otto Berger Lubricator for elevator-guides.
FR1007422A (fr) * 1948-12-27 1952-05-06 Philips Nv Machine à gaz chaud
US3478695A (en) * 1968-02-13 1969-11-18 Mc Donnell Douglas Corp Pulsatile heart pump
US3597766A (en) * 1968-07-11 1971-08-10 Atomic Energy Commission Artificial heart pumping system powered by a modified stirling cycle engine-compressor having a freely reciprocable displacer piston
FR2417653A1 (fr) * 1978-02-15 1979-09-14 Cloup Jean Capsule isotherme et machines thermiques realisees a partir de ladite capsule
US4490974A (en) * 1981-09-14 1985-01-01 Colgate Thermodynamics Co. Isothermal positive displacement machinery
US6591609B2 (en) * 1997-07-15 2003-07-15 New Power Concepts Llc Regenerator for a Stirling Engine
US6725670B2 (en) * 2002-04-10 2004-04-27 The Penn State Research Foundation Thermoacoustic device
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JP4867635B2 (ja) * 2006-12-20 2012-02-01 有富 奥野 スターリングエンジン用体積変動部材
CN101498290A (zh) * 2009-02-20 2009-08-05 武汉工程大学 外激励双驱动行波热声热机
WO2014005229A1 (fr) * 2012-07-04 2014-01-09 Kairama Inc. Gestion de température pour compression et expansion de gaz
CN103629009B (zh) * 2013-11-26 2015-04-22 万斌 一种基于液体放射性废料浓缩物的斯特林热机

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2296047A (en) * 1994-12-15 1996-06-19 Jonathan Maxwell Boardman Stirling cycle engine
WO2001063186A1 (fr) * 2000-02-25 2001-08-30 586925 B.C. Inc. Appareil et procede de transmission de chaleur utilisant un cycle a recuperation de chaleur actif
WO2011153979A2 (fr) * 2010-06-12 2011-12-15 Forschungszentrum Jülich GmbH Mécanisme d'entraînement en poussée discontinu et moteur stirling

Also Published As

Publication number Publication date
ES2891796T3 (es) 2022-01-31
EP3280900B1 (fr) 2021-06-30
MA41914A (fr) 2018-02-13
WO2016146096A9 (fr) 2017-04-06
DE112016001190A5 (de) 2017-11-30
US20180119638A1 (en) 2018-05-03
US11047335B2 (en) 2021-06-29
EP3919730A1 (fr) 2021-12-08
MX2017011696A (es) 2018-06-15
WO2016146096A2 (fr) 2016-09-22
EP3280900A2 (fr) 2018-02-14
CN107532541A (zh) 2018-01-02
PT3280900T (pt) 2021-10-01
WO2016146096A3 (fr) 2016-12-08
CN107532541B (zh) 2020-11-20

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