EP3137821B1 - Vorrichtung und verfahren zum umwandeln thermischer energie - Google Patents

Vorrichtung und verfahren zum umwandeln thermischer energie Download PDF

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Publication number
EP3137821B1
EP3137821B1 EP15724506.9A EP15724506A EP3137821B1 EP 3137821 B1 EP3137821 B1 EP 3137821B1 EP 15724506 A EP15724506 A EP 15724506A EP 3137821 B1 EP3137821 B1 EP 3137821B1
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EP
European Patent Office
Prior art keywords
working medium
impeller
rotational axis
rotor
channels
Prior art date
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Active
Application number
EP15724506.9A
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German (de)
English (en)
French (fr)
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EP3137821A1 (de
Inventor
Bernhard Adler
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Ecop Technologies GmbH
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Ecop Technologies GmbH
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Publication date
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Priority to PL15724506T priority Critical patent/PL3137821T3/pl
Publication of EP3137821A1 publication Critical patent/EP3137821A1/de
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Publication of EP3137821B1 publication Critical patent/EP3137821B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B3/00—Self-contained rotary compression machines, i.e. with compressor, condenser and evaporator rotating as a single unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point

Definitions

  • the invention relates to a device according to the preamble of claim 1.
  • the invention relates to a method according to the preamble of claim 14.
  • EP 2567158 A1 discloses a device according to the preamble of claim 1 and a method according to the preamble of claim 12.
  • This document describes an apparatus for converting low temperature thermal energy into higher temperature thermal energy by means of mechanical energy and vice versa, with a rotatably mounted rotor in which Flow channel is provided for a closed loop process continuous working medium.
  • the flow channel has a compression channel, in which a working medium for pressure increase is feasible, and a relaxation channel, in which a working medium for pressure reduction can be guided on.
  • heat exchangers are provided, which extend adjacent and substantially parallel to the compression or expansion channel.
  • the EP 0119777 A2 discloses a compression heat pump consisting of an evaporator, a compressor and a condenser, wherein at least the evaporator or the condenser has rotating plates through which heat exchange takes place. In this case, a fluid is accelerated radially outwards by the centrifugal force along the plates.
  • a heat pump in which the working fluid in a piping system of a rotor a cycle with the steps a) compression of the working fluid, b) heat removal from the working fluid by means of a heat exchanger, c) relaxation of the working medium and d) heat supply to the working fluid passes through another heat exchanger ,
  • the pressure increase or pressure reduction of the working medium adjusts itself mainly by the centrifugal acceleration, wherein the working medium in a compression unit with respect to a rotation axis radially outwards and in a Relaxation unit flows radially inward.
  • the heat dissipation from the working fluid to a heat exchange medium of the heat exchanger takes place in an axial or parallel to the axis of rotation extending portion of the piping system, which is associated with a co-rotating, the heat exchange medium exhibiting heat exchanger.
  • a paddle wheel has been used, which is used in particular to maintain the flow of the working fluid in the rotating operation.
  • the impeller may be arranged on the one hand rotationally fixed, resulting in a relative movement to the medium leading the piping system due to the rotationally fixed arrangement.
  • the impeller is associated with a motor for generating a relative movement to the piping system.
  • the impeller may be connected to a generator in order to convert the shaft power generated by the relative movement of the impeller into electrical energy.
  • paddle wheels for maintaining a fluid flow are known, wherein such paddle wheels can be designed as a compressor, expansion turbines or guide wheels.
  • axial and, on the other hand, radial designs are known as boundary forms for the flow-through type of paddle wheels.
  • axial or axial flow component In mixed forms such as diagonally flowed paddle wheels largely the same considerations apply to the radial or axial flow component.
  • so-called axial fans (or generally axial compressor) or axial turbines so-called axial fans (or generally axial compressor) or axial turbines, a conventional dimensioning can be applied substantially.
  • the axial design has the disadvantage that in comparison to the radial design lower pressure increases can be effected, whereby the axial paddle wheels usually have to be constructed in multiple stages.
  • the object of the present invention is therefore to provide a rotary device for converting thermal energy, as stated above, in which the disadvantages of the prior art are eliminated or at least significantly alleviated. Accordingly, the invention is in particular the goal of maintaining the flow of the working medium about the axis of rotation with the lowest possible energy losses.
  • the impeller between between the heat pump operating state, the flow of the working medium supplying supply channels and at least one in Heat pump operating state, the flow of the working medium laxative discharge channel of the rotor arranged, wherein the supply channels substantially parallel to the axis of rotation, extending to immediately in front of an inlet opening of the impeller outlet sections, so that individual flows of the working medium from the supply ducts substantially parallel to the axis of rotation in the paddle wheel feasible are.
  • the invention is based on the surprising finding that the efficiency of the paddle wheel can be significantly improved by the fact that the working medium before entering the paddle wheel in individual flows parallel to the axis of rotation, ie in the axial direction, out.
  • the extension of the exit sections of the supply ducts to immediately before the impeller means that the flows of the working medium in the supply ducts are not brought together but are supplied to the impeller separately from one another.
  • the outlet sections of the feed channels are preferably arranged at regular angular intervals and at the same radial distance around the axis of rotation. Accordingly, a plurality of axial flows of the working medium are introduced into the impeller. Thereafter, the working fluid flows into the at least one discharge channel of the rotor.
  • the working medium from the paddle wheel is guided directly, ie without the interposition of a stationary housing in the rotor.
  • the rotor therefore forms a rotating housing for the paddle wheel, which preferably completely surrounds the paddle wheel.
  • the working medium is thus guided by the paddle wheel located in the interior of the rotor, wherein the working medium is not performed in a stationary housing unlike the prior art.
  • the flow energy of the working medium when passing through the cyclic process can be substantially maintained.
  • dynamic seals of the working medium to the environment are not required.
  • a stationary housing was provided.
  • a rotor is provided in the apparatus according to the invention, so that the components surrounding the impeller rotate during operation.
  • the working medium is led out in the axial direction from the feed ducts conveying the working medium.
  • This advantageously has the consequence that the Coriolis acceleration becomes almost zero and no or no substantial twist sets.
  • the passage into the paddle wheel is easier to calculate and advantageously also not dependent on the rotational speeds of the paddle wheel and the surrounding housing of the rotor and not on the relative flow rate.
  • the impeller is connected to at least three discharge channels. Preferably, no more than twelve discharge channels are connected to the paddle wheel.
  • the described embodiment relates only to the number of directly radially away from the impeller leading away discharge channels. However, it is quite possible that a radial discharge channel in the region remote from the axis, preferably after a deflection in the axial direction, is divided into a plurality of heat exchanger channels.
  • the supply ducts have substantially extending in the radial direction supply line sections, which between the outlet sections and are arranged with respect to the axis of rotation of internal heat exchangers.
  • the lead portions are preferably longer than the exit portions of the lead channels.
  • the at least one discharge channel is connected to the compression channels, which are connected to outer heat exchangers with respect to the axis of rotation.
  • the impeller is arranged in the radial direction closer to the axis of rotation than the inner heat exchanger, wherein the impeller is preferably arranged concentrically around the axis of rotation of the rotor. Accordingly, the axes of rotation of the rotor and the impeller are preferably arranged in alignment. As a result, a particularly efficient mode of operation can be achieved.
  • the supply ducts have arcuately curved walls at the exit sections, which deflect the working medium substantially 90 ° from the supply sections cause the exit sections. Due to the arcuate walls of the expansion channels at the outlet end, the working medium can be continuously deflected into an axial flow, wherein the currents of the working medium are not or only slightly disturbed by the deflection.
  • the outlet sections of the supply ducts between essentially in the radial and axial direction to the axis of rotation extending separating elements, in particular substantially planar partitions, are formed.
  • the arrangement of partitions can be achieved in a particularly simple manner that the axial flows of the working medium in the outlet sections of the supply channels are unmixed and substantially free of twist with respect to the rotating rotor, which is the housing for the paddle wheel, guided in the paddle wheel.
  • the separating elements are adjustable in front of the paddle wheel.
  • a defined entrance swirl can be generated, which can be adjusted via the separating elements.
  • this defined entry twist can be calculated or simulated in the design of the device.
  • the device according to the invention is usually designed for a specific operating point.
  • the entry angle of the separating elements can be dimensioned such that the flow when viewed in the relative rotating impeller system has a steady transition, ie an inflow without substantial change in direction, in the blade region of the impeller.
  • the inflow angles of the flow usually change, whereby a discontinuous inflow would occur in the blade region of the blade wheel.
  • This effect reduces the efficiency of the impeller when operating outside the design point.
  • the separating elements for operation outside the design point can be adjusted such that the working medium, based on the relative rotating impeller system, flows in a steady manner upon entry into the blade region of the impeller. As a result, the efficiency can be increased.
  • the paddle wheel can also generate by this measure, a higher pressure and a higher maximum flow, whereby the application area is extended.
  • the impeller has a plurality of, in particular arcuately curved blades.
  • the working medium is accelerated in the circumferential direction with respect to the axis of rotation, before the working medium via outlet openings between the outer edges of the blades of the blade wheel in the compression channels is performed.
  • the impeller on the side facing the axis of rotation on a free radial blades on blades.
  • the flows of the working medium which are guided separately in the supply ducts, are brought together.
  • the working medium in the radial section can be homogenized before the working medium flowing radially outward from the radial section is accelerated by the rotating blades and then discharged into the discharge channels.
  • the blade wheel In order to supply the working medium flowing in the axial direction to the blades, it is favorable if the blade wheel has an arcuately curved deflecting wall at the radial portion, with which the working medium can be deflected by substantially 90 ° in the radial direction.
  • the at least one discharge channel has an inlet section arranged obliquely to the radial direction, which is connected to a discharge section extending essentially in the radial direction.
  • the inlet section of the drainage channel preferably extends in the direction in which a steady transition of the flow, i. in which there is an inflow without significant change in direction results. This is achieved in the design by vector addition.
  • the working medium is introduced in the tangential direction, relative to a substantially circular in cross-section envelope or outer surface of the impeller, in the inlet sections, which are connected to the substantially extending in the radial direction discharge sections.
  • the inlet sections and the compression sections are preferably connected to each other via arcuately curved transition sections.
  • the impeller has a particular rotatable parallel to the axis of rotation of the rotor Schaufelradwelle, which is connected to a motor or to a generator. Accordingly, the paddle wheel can be connected on the one hand to a motor in order to generate a relative movement between the rotor and the paddle wheel. In this embodiment, the paddle wheel is set in a heat pump operating condition for maintaining the circulation of the working fluid. On the other hand, the impeller may be connected to a generator in order to convert the shaft power present at the Schaufelradwelle by the relative movement of the impeller into electrical energy.
  • a flow in the nature of a natural circulation is obtained due to the different temperature levels at the heat exchangers.
  • the energy of the flow is then converted into shaft power in the impeller acting as a turbine, which is subsequently converted into electrical power by means of a generator.
  • part of this energy is spent on a motor which drives the rotor.
  • the terms "inlet” and “exit” refer to the function of the paddle wheel to maintain the flow of the working fluid about the axis of rotation, ie, when the paddle wheel is used as a fan in a heat pump operating condition.
  • the flow direction of the working medium is reversed, so that, for example, the outlet portions of the supply lines to the inlet portions of the discharges.
  • the axes of rotation of the paddle wheel and the rotor coincide.
  • a separate motor / generator for the Schaufelradwelle is provided, so that the impeller regardless of the Compressing and relaxation channels having rotor can be driven; in this case, the rotor is connected to a second motor.
  • the same motor for driving the impeller and the rotor or the same generator for the utilization of the rotational energy of the impeller and the rotor can be used.
  • the motor is set up to rotate the impeller in the same direction of rotation as the rotor with the expansion and compression channels for the working medium.
  • the acceleration field of the main rotor can be utilized.
  • the apparatus of the invention utilizes centrifugal acceleration as it flows through the compression and expansion passages of the rotor to produce various pressure or temperature levels of the working fluid.
  • it is favorable if at least one with respect to the axis of rotation inner heat exchanger and at least one with respect to the axis of rotation outer heat exchanger for heat exchange between the working medium and a heat exchange medium are provided.
  • the heat exchangers are arranged co-rotating in the rotor.
  • the device can be operated on the one hand as a heat pump, in which the rotor is rotated by a drive and the circulation flow is generated by a fan.
  • the reverse flow direction corresponds to operation as a heat-power machine for generating electric current, wherein different temperature levels are used to generate a flow, which is converted in the acting as a turbine paddle wheel into mechanical energy, which is finally converted into electrical energy in a generator.
  • the rotor is driven by a motor which is supplied, for example, by the recovered electrical energy from the turbine.
  • the heat exchangers are arranged substantially parallel to the axis of rotation of the rotor.
  • the heat exchangers are in this case connected between the compression and expansion channels.
  • the inner heat exchanger is provided for a lower temperature heat exchange and the outer heat exchanger for higher temperature heat exchange.
  • the inner heat exchanger on the one hand and the outer heat exchanger on the other hand arranged at regular angular intervals with respect to the axis of rotation.
  • as many inner and outer heat exchangers as compression and expansion channels are provided. Accordingly, the inner and outer heat exchangers are connected in pairs via one compression and one expansion channel.
  • the number of supply and discharge channels for the impeller corresponds to the number of inner and outer heat exchangers.
  • the number of internal heat exchangers corresponds to a multiple of the external heat exchangers or vice versa.
  • the heat exchange can be made particularly efficient if the at least one inner heat exchanger and the at least one outer heat exchanger are substantially parallel to the axis of rotation, wherein the compression and expansion channels between the inner heat exchanger and the run outside heat exchanger.
  • a plurality of inner heat exchangers and a plurality of outer heat exchangers are provided, which are each arranged at equal radial distances from the axis of rotation.
  • the impeller has a plurality of successively flowed through by the working medium Schaufelradkyn.
  • the supply ducts have outlet sections extending substantially parallel to the axis of rotation and extending to just in front of the inlet opening of the first blade wheel stage, as viewed in the flow direction.
  • the successive Schaufelradkyn are each connected to one another via a deflection, with which the working medium is deflected between the Schaufelradmen.
  • the deflection preferably has outlet sections which extend essentially parallel to the axis of rotation and which extend as far as directly in front of the inlet opening of the impeller stage following in the flow direction.
  • the problem underlying the invention is also achieved by a method of the type mentioned, in which individual flows of the working medium in the heat pump operating state to be performed directly in front of the impeller and introduced into the impeller substantially parallel to the axis of rotation. Accordingly, the flows of the working medium are guided individually or separately from each other and in the axial direction in the impeller.
  • the impeller is rotated in the same direction of rotation and at a higher absolute speed as the rotor with the expansion and compression channels.
  • a higher absolute speed of the impeller is provided which causes a correspondingly higher centrifugal acceleration and thus a more efficient compression of the working medium.
  • the centrifugal compression effect is proportionally increased, thereby increasing the efficiency.
  • Fig. 1 shows a device 20 for the conversion of heat energy by means of mechanical energy and vice versa, which is used in the embodiment shown as a heat pump.
  • the device 20 comprises a rotor 21 which is rotatable about a rotation axis 22 by means of a motor (not shown).
  • the rotor 21 has a compressor unit 23 and a relaxation unit 24, which have flow channels for a working medium.
  • the working medium for example a noble gas
  • the compressor unit 23 in a substantially radially extending compression channels 25, in which the working fluid with respect to the axis of rotation 22 in the radial direction flows outward the centrifugal acceleration compresses the working medium in the compression channels 25.
  • the working medium for pressure reduction in expansion channels 26 of the expansion unit 24 is guided substantially radially inwards.
  • the compressor unit 23 and the expansion unit 24 are interconnected by axially, ie in the direction of the axis of rotation 22, extending flow channels in which a heat exchange between the working medium and a heat exchange medium, for example water, takes place.
  • outer heat exchangers 1 'and inner heat exchangers 1 "are provided with respect to the rotation axis, which are substantially parallel to the axis of rotation 22.
  • the centrifugal acceleration acting on the working medium is exploited to produce different pressure levels or temperature levels.
  • High-temperature heat is removed from the compressed working medium, and heat is supplied to the relaxed working medium at a comparatively low temperature.
  • the flow channels are flowed through by the working medium in the reverse direction. Accordingly, the heat exchange changes, wherein at the outer heat exchanger 1 'heat supplied to the working fluid and the inner heat exchanger 1 "heat is removed from the working fluid.
  • Fig. 1 Furthermore, in each case a plurality, twelve in the embodiment shown, inner heat exchanger 1 'and a plurality, in the embodiment shown twelve, outer heat exchanger 1' are provided, which are arranged at regular angular intervals with respect to the axis of rotation.
  • the inner heat exchangers 1 'and the outer heat exchangers 1' are each substantially parallel to the axis of rotation 22, wherein the compression and expansion channels 23 run between the inner heat exchangers 1 'and the outer heat exchangers 1'.
  • Fig. 2 Parts of the device 20 are shown in longitudinal section, with only one of the inner heat exchanger 1 '' and one of the outer heat exchanger 1 'are located.
  • a paddle wheel 30 can be seen, with which in the embodiment shown, the flow of the working medium is maintained about the axis of rotation 22.
  • the impeller 30 is connected, on the one hand, to supply ducts 31, which take over the working medium from the inner heat exchangers 1 ".Furthermore, the impeller 30 is connected to discharge ducts 32, with which the working medium is guided into the compression ducts 25 of the compressor unit 23.
  • the compression ducts 25 are connected to the outer heat exchanger 1 '.
  • the paddle wheel 30 is closer to the axis of rotation 22 in the radial direction than the inner
  • the axis of rotation of the paddle wheel 30 is arranged in alignment with the axis of rotation 22 of the rotor 21 in order to reduce the stresses due to the centrifugal acceleration on the bearing of the shaft of the paddle wheel 30.
  • the supply channels 31 extend substantially radially in the direction of the feed line sections 35 which are arranged between the discharge sections 34 opening into the impeller 30 and the inner heat exchangers 1 "
  • the discharge channels 32 are connected to the compression channels 25 which supply the working medium lead the outer heat exchangers 1 '.
  • the supply channels 31 at the outlet portions 34 arcuately curved walls 36, which cause a deflection of the working medium by substantially 90 ° from the radial feed line portions 35 in the axial outlet sections 34.
  • the outlet sections 34 of the feed channels 31 are delimited by dividing elements 37 which extend substantially in the radial and axial direction relative to the axis of rotation 22 and which are formed in the embodiment shown by substantially planar partitions.
  • the separating elements 37 have a radial extension and are arranged in a star shape. In the embodiment shown, the outlet sections 34 are therefore arranged regularly and at constant radial distances about the axis of rotation 22 of the rotor 21.
  • Fig. 4 is further seen that the paddle wheel 30th a plurality of arcuately curved blades 38, with which the working fluid is accelerated when flowing through the impeller 30 in the direction of rotation 39 of the impeller 30.
  • the paddle wheel 30 has, on the side facing the axis of rotation 22, a radial section 40 which is free of blades 38, in which the flows of the working medium from the supply channels 31 are brought together and homogenized.
  • an arcuately curved deflection wall 41 is provided (see. Fig. 3 ), with which the working medium is deflected by substantially 90 ° from the axial flow on entry into the impeller 30 in a radial flow in front of the blades 38.
  • the paddle wheel 30 a Schaufelradwelle 44, which is connected to a motor (not shown).
  • the motor is configured to rotate the paddle wheel 30 in the direction of rotation 45 of the rotor 21.
  • the axis of rotation of the paddle wheel 44 and the axis of rotation 22 of the rotor 21 coincide.
  • a generator is connected to the paddle wheel 30, which then works as a turbine.
  • the turbine converts a resulting differential pressure into shaft power during a flow with a corresponding mass flow.
  • the apparatus 20 has dynamic sealing gaps 46 which are intended to minimize backflow due to increased pressure at the exit of the impeller 30 from the inlet.
  • the sealing gaps 46 engage counter blades 47 of the paddle wheel 30 in order to produce several small column as possible.
  • Fig. 7 1 shows an alternative embodiment in which the individual impeller 30 has a plurality of impeller stages 30 ', 30 ", which can be flowed through one behind the other in the embodiment shown, and the impeller stages 30', 30" are connected to one another via a deflection 30 ", with which the working medium of a flow radially outward following the first paddle wheel 30 'is first deflected into a flow radially inward and then into a flow in the direction of the rotation axis 22 to immediately before the second paddle wheel 30'.
  • Each paddle wheel stage 30 ', 30'' is according to the single-stage embodiment according to Fig. 1 to 6 built up.
  • the paddlewheel stages 30 ', 30 are disposed on the same paddlewheel shaft 44, which is connected to a motor or to a generator.
  • the paddlewheel stages 30 ', 30 may alternatively be supported on separate paddlewheel shafts, with each paddlewheel stage 30', 30" connected to a motor or generator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)
EP15724506.9A 2014-04-23 2015-04-22 Vorrichtung und verfahren zum umwandeln thermischer energie Active EP3137821B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15724506T PL3137821T3 (pl) 2014-04-23 2015-04-22 Sposób i urządzenie do przemieniania energii termicznej

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50296/2014A AT515217B1 (de) 2014-04-23 2014-04-23 Vorrichtung und Verfahren zum Umwandeln thermischer Energie
PCT/AT2015/050098 WO2015161330A1 (de) 2014-04-23 2015-04-22 Vorrichtung und verfahren zum umwandeln thermischer energie

Publications (2)

Publication Number Publication Date
EP3137821A1 EP3137821A1 (de) 2017-03-08
EP3137821B1 true EP3137821B1 (de) 2018-05-23

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EP15724506.9A Active EP3137821B1 (de) 2014-04-23 2015-04-22 Vorrichtung und verfahren zum umwandeln thermischer energie

Country Status (10)

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US (1) US10247450B2 (zh)
EP (1) EP3137821B1 (zh)
JP (1) JP6496010B2 (zh)
CN (1) CN106415154B (zh)
AT (1) AT515217B1 (zh)
DK (1) DK3137821T3 (zh)
ES (1) ES2684621T3 (zh)
HU (1) HUE038862T2 (zh)
PL (1) PL3137821T3 (zh)
WO (1) WO2015161330A1 (zh)

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Publication number Priority date Publication date Assignee Title
CN107065952A (zh) * 2017-04-19 2017-08-18 中国神华能源股份有限公司 减压装置及具有其的减压系统
JP6935312B2 (ja) * 2017-11-29 2021-09-15 三菱重工コンプレッサ株式会社 多段遠心圧縮機
CN109630466B (zh) * 2018-12-12 2024-01-23 扬州大学 一种用于低扬程泵站出水流道纠偏消涡方法及其应用
DE102019009076A1 (de) * 2019-12-28 2021-07-01 Ingo Tjards Kraftwerk zur Erzeugung elektrischer Energie
DE102020108377A1 (de) 2020-03-26 2021-09-30 Envola GmbH Wärmetauscheranordnung

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AT505532B1 (de) 2007-07-31 2010-08-15 Adler Bernhard Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt
CN102077038B (zh) 2008-07-04 2014-01-22 海利奥斯技术有限公司 用于从第一介质向第二介质传递热量的方法和装置
AT509231B1 (de) 2010-05-07 2011-07-15 Bernhard Adler Vorrichtung und verfahren zum umwandeln thermischer energie

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Also Published As

Publication number Publication date
AT515217B1 (de) 2015-07-15
WO2015161330A1 (de) 2015-10-29
EP3137821A1 (de) 2017-03-08
JP2017514098A (ja) 2017-06-01
ES2684621T3 (es) 2018-10-03
AT515217A4 (de) 2015-07-15
CN106415154A (zh) 2017-02-15
DK3137821T3 (en) 2018-08-27
HUE038862T2 (hu) 2018-12-28
JP6496010B2 (ja) 2019-04-03
US10247450B2 (en) 2019-04-02
PL3137821T3 (pl) 2019-01-31
CN106415154B (zh) 2019-04-30
US20170045270A1 (en) 2017-02-16

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