EP3092447B1 - Vorrichtung zum umwandeln thermischer energie - Google Patents

Vorrichtung zum umwandeln thermischer energie Download PDF

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Publication number
EP3092447B1
EP3092447B1 EP15705481.8A EP15705481A EP3092447B1 EP 3092447 B1 EP3092447 B1 EP 3092447B1 EP 15705481 A EP15705481 A EP 15705481A EP 3092447 B1 EP3092447 B1 EP 3092447B1
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EP
European Patent Office
Prior art keywords
heat exchanger
axis
rotation
heat
support body
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Active
Application number
EP15705481.8A
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German (de)
English (en)
French (fr)
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EP3092447A1 (de
Inventor
Bernhard Adler
Sebastian Riepl
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Ecop Technologies GmbH
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Ecop Technologies GmbH
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Publication of EP3092447A1 publication Critical patent/EP3092447A1/de
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    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically

Definitions

  • the invention relates to a device for converting thermal energy of low temperature into thermal energy of higher temperature by means of mechanical energy and vice versa with a rotatably mounted about a rotation axis rotor, in which a flow channel is provided for a closed loop process continuous working fluid in a compressor unit for pressure increase is guided with respect to the axis of rotation substantially radially outwardly and is guided in a relaxation unit for depressurizing with respect to the axis of rotation substantially radially inwardly, wherein 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 exchangers are provided for a heat exchange between the working medium and a heat exchange medium, wherein the heat exchangers are preferably arranged substantially parallel to the axis of rotation of the rotor.
  • Rotary heat pumps or heat engines are already known from the prior art, in which a gaseous working medium is guided in a closed thermodynamic cycle.
  • WO 2009/015402 A1 is a heat pump or heat engine described according to the preamble of claim 1, wherein 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 ) Passes through heat supply to the working medium by means of another heat exchanger.
  • the pressure increase or pressure reduction of the working medium adjusts itself by the centrifugal acceleration, wherein the working medium in a compression unit with respect to a rotation axis flows radially outward and in a relaxation unit radially inwardly.
  • 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.
  • This device already enables efficient conversion of mechanical energy and low-temperature thermal energy into higher-temperature thermal energy.
  • the heat exchangers were clamped in the region of the front ends of the heat exchanger.
  • the heat exchangers in this embodiment can flex in operation between the grips at the ends, whereby the stability of the arrangement is impaired.
  • the reliability can not be guaranteed hereby.
  • WO 98/30846 A1 a generic rotor device for converting thermal energy is disclosed.
  • the US 3,846,302 describes a different type of apparatus for heat treatment of sludges.
  • the US 4,420,944 refers to a rotor for different types of cooling equipment.
  • the device is driven by a shaft.
  • two pairs of cylinder-piston units are disposed on opposite sides of the shaft.
  • the cylinder-piston units are attached via cylindrical head parts to mounting bodies.
  • the cooled gas is passed through outlets of the cylinder-piston units via the headers and a conduit into a heat exchanger. In the heat exchanger, the cooled gas is heated by the supplied room air.
  • the object of the present invention is to provide a rotary device for converting thermal energy, as stated above, which can reliably withstand high forces during operation of the device.
  • the device of the invention utilizes the centrifugal acceleration of the rotating system to different pressure or temperature levels to create; In this case, the high-temperature heat is removed or supplied to the compressed working medium, and the relaxed working medium is supplied or withdrawn with heat at a comparatively low temperature.
  • the device will be operated either as a heat pump or motor.
  • an inner heat exchanger with respect to the axis of rotation and at least one outer heat exchanger with respect to the axis of rotation is used, which preferably is arranged substantially parallel to the axis of rotation of the rotor are.
  • the inner heat exchanger is provided for a lower temperature heat exchange and the outer heat exchanger for higher temperature heat exchange.
  • the rotor has a supporting body, which supports the inner or outer heat exchanger over the length of the heat exchanger between the end faces relative to radial forces occurring during operation.
  • the rotor has a support body which supports the inner or outer heat exchanger over the length of the heat exchanger between the end faces relative to radial forces occurring during operation.
  • the heat exchanger is supported by the support body substantially uniformly in the longitudinal direction of the heat exchanger, so that only small or uncritical bends occur along the heat exchanger.
  • all heat exchangers are mounted on a common support body, which is arranged as a component of the rotor rotating about the axis of rotation.
  • the support body may consist of one or more components spaced apart in the longitudinal direction of the heat exchanger.
  • the at least one outer heat exchanger between the outer tube and the support body has an insulation element made of a thermally insulating material, wherein the inner heat exchanger remains free of an insulation element.
  • the outer or achsfernen heat exchangers which have a higher relative temperature than the inner or near-axis heat exchanger under normal operation, in particular thermally insulated by tubular insulating elements with a compared to the supporting body substantially lower thermal conductivity of the support body ,
  • the thermal insulating material preferably has a tensile strength of at least 10 MPa to avoid flow under the load.
  • the thermally insulating material have a temperature stability corresponding to the maximum temperature of the heat exchanger. Therefore, ordinary polycarbonate offers at service temperatures up to max. 120 ° C on. At higher temperatures up to about 200 ° C polyetheretherketone, in particular with fillers such as carbon fiber or glass fiber, polyamide, in particular with various fillers, hardboard materials or other high temperature materials are used with low thermal conductivity. Due to the heat insulation of the support body from the outer heat exchanger on the one hand in the absence of such an insulating element on the inner heat exchanger on the other hand, the temperatures of the inner heat exchanger are essentially decisive for the support body. As a result, advantageously no or lower strength losses occur in the support body.
  • this has an effect on the use of aluminum or aluminum alloys, since these generally show strength reductions starting at about 50.degree.
  • Another advantage of this embodiment is that set lower temperature gradients within the support body, since the temperature of the near-axis heat exchanger is set substantially to the insulation layer to the off-axis heat exchanger. This leads to lower residual stresses in the support body. At particularly high temperatures, however, it is also conceivable that both the off-axis and the near-axis heat exchanger by means of insulating elements of the support body are thermally insulated.
  • the support body can be equipped with an active cooling (for example via water cooling, heat radiation or convection) in order to prevent losses in the strength of the support body.
  • the support body is produced as a cast body, in particular made of aluminum, wherein preferably high-strength aluminum alloys, for example AlCu4Ti, are used. Due to the high thermal conductivity of aluminum, the arrangement of the insulating element at least at the inner heat exchanger is advantageous.
  • the support body can be made of (for example bainitic) cast iron. Due to the low thermal conductivity can in a support body produced in this way the insulation element of the off-axis heat exchanger omitted. Due to the low strength reductions at higher temperatures, this support variant is very well suited for high-temperature applications.
  • the support body can be made of steel using welded joints, this embodiment brings special cost advantages, with relatively high strength properties, with it.
  • Another advantage of a welded support body is the almost unlimited size scaling. In this case, the diameter of the rotor of at least 4m are conceivable.
  • This variant also has the advantage that due to the low thermal conductivity of steel can be dispensed with an insulation element on the outer heat exchanger.
  • the support body can be made of fiber composites, which are advantageously very light and have a high rigidity.
  • the support body can be assembled from semi-finished products, wherein, for example, aluminum plates and aluminum tubes and / or steel plates and steel tubes can be used.
  • all materials can be used, which are available in plate or tube form as a semi-finished product.
  • the support body has a plurality of plate elements which are arranged substantially perpendicular to the axis of rotation and spaced in the direction of the axis of rotation, which have recesses for mounting the heat exchangers.
  • the plate elements may have cutouts or depressions in order to reduce the weight of the support body and / or to change the rigidity of the plate elements. This can be used advantageously to achieve uniform deformations in the transition to the edge region, which may have an increased weight.
  • the plate elements are preferably arranged at equal intervals.
  • the plate elements are preferred disc-shaped.
  • the heat exchangers between the plates are slightly deflected due to the centrifugal acceleration and there are additional bending stresses that must be absorbed by the heat exchanger.
  • the advantage of this design is that when manufactured from semi-finished products, increased strength in the raw materials can be achieved.
  • the heat exchanger on the outside has a support tube which has recesses extending in the circumferential direction for receiving the plate elements.
  • shear forces can be absorbed hereby.
  • a supporting body extending in the direction of the axis of rotation profile body having an inner member having at least one inner recess for the at least one inner heat exchanger and at least one Au ⁇ enelement having at least one outer recess for the at least one outer heat exchanger.
  • the profile body is rotationally symmetrical with respect to the axis of rotation in an arrangement of at least two outer and two inner heat exchangers.
  • the inner element and the outer element are connected to one another via connecting webs running essentially in the radial direction.
  • a plurality of outer elements are provided, wherein preferably exactly two connecting webs are provided between the inner element and each outer element.
  • the connecting webs with the outer elements are preferably arranged in a star shape around the inner element.
  • the power transmission it is favorable if the distance between the connecting webs in the radial direction increases continuously outwards.
  • the width of the connecting web can decrease in the radial direction to the outside.
  • the at least one outer element of the support body is designed as a cylindrical receptacle for the outer heat exchanger.
  • the intake can be partly open inwards. Due to the non-circumferentially supported, off-axis heat exchanger, one core per heat exchanger can be dispensed with during casting production. Furthermore, the introduction of force in the off-axis heat exchanger can be improved, whereby the stresses due to the centrifugal forces can be reduced.
  • the support body has a cylindrical enclosure surrounding the outer elements.
  • the outer elements are in this case attached to the inside of the cylindrical enclosure. Due to the cylindrical jacket, the friction losses in the rotating operating state of the device are significantly reduced.
  • the rotor is operated in a room with an ambient pressure of less than 50 mbar absolute pressure, in particular less than 5 mbar absolute pressure.
  • Fig. 1 is a heat exchanger 1 for installation in a rotary device 20 for the conversion of heat energy by means of mechanical energy and vice versa (see. Fig. 7 . 8th ).
  • the heat exchanger 1 has an inner longitudinal element 2 and an outer tube 3, which surrounds the inner longitudinal element 2.
  • inner longitudinal element 2 a hollow inner tube 4 is provided.
  • the outer tube 3 and the inner tube 4 are arranged coaxially with respect to a central longitudinal axis 5.
  • a heat transfer tube 6 is arranged, which extends coaxially to the outer tube 3 and to the inner tube 4 in the longitudinal direction of the heat exchanger 1.
  • the heat transfer tube 6 has a wall 7 with an outer circumferential surface 8 and an inner circumferential surface 9, projecting from the outer fins 10 and inner 11 fins.
  • the lamellae 10, 11 extend in the direction of the longitudinal axis 5 of the heat transfer tube 6.
  • the outer lamellae 10 protrude from the outer circumferential surface 8 in the radial outward direction to an inner surface 12 of the outer tube 3.
  • the inner lamellae 11 jump from the inner Lateral surface 9 of the wall 7 of the heat transfer tube 6 to an outer surface 13 of the inner tube 4 before. Accordingly, the heat transfer tube 6 is held between the inner tube 4 and the outer tube 3, wherein the outer plates 10 are supported on the outer tube 3 and the inner plates 11 on the inner tube 4.
  • Between the outer fins 10 intermediate spaces 14 are formed, which form heat exchange channels 15 for a first heat exchange medium.
  • spaces 16 between the inner fins 11 form heat exchange channels 17 for a second heat exchange medium.
  • the heat exchange medium having the lower absolute pressure flows in the outer heat exchange channels 15 between the outer fins 10, whereby the second heat exchange medium can flow through the heat exchange channels 17 between the inner fins 11 at a considerably higher pressure.
  • the two-sided support of the heat transfer tube 6 allows that caused by the differential pressure voltages in the region of the wall 7 of the heat transfer tube 6 are transmitted via the outer fins 10 to the outer tube 3. Conversely, forces introduced into the wall 7 can be transmitted to the inner tube 4 via the inner lamellae 11 when the heat exchange medium at the higher pressure flows in the outer heat exchange channels 15. Thus, a mechanically very stable arrangement of the heat transfer tube 6 is achieved, which can be made thin-walled to optimize the heat transfer between the heat exchange media.
  • the ratio between a wall thickness s of the wall 7 of the heat transfer tube 6 and a wall thickness s' of the outer tube 3 is approximately 0.2.
  • the ratio between the wall thickness s of the heat transfer tube 6 and a wall thickness s "of the inner tube 4 is about 0.3.
  • the thin-walled construction of the heat transfer tube 6 permits Heat transfer with high efficiency, whereby in particular the extension of the heat exchanger can be shortened in the longitudinal direction, which, for example, in the reference to the Fig. 7 and 8th explained embodiment has proved advantageous.
  • the outer lamellae 10 have a height h, ie an extension in the radial direction, which is preferably greater than a height h 'of the inner lamellae 11.
  • the ratio between the height h of the outer fins 10 and the height h 'of the inner fins 11 is between 0.2 and 5, depending on the fluid, mass flow and pressures.
  • the outer heat exchange channels 15 forming gaps 14 have a width b of about 1 mm.
  • a width b 'of the intermediate spaces 16 between the inner slats 11 preferably corresponds to the width b of the intermediate spaces 14.
  • the heat transfer tube 6 is made of a material having a modulus of elasticity which is lower than the modulus of elasticity of the outer tube 3 or of the inner longitudinal element 2.
  • the heat transfer tube 3 is made of an aluminum or copper alloy.
  • the outer tube 3 or the inner longitudinal element 2 is made of a high-strength steel alloy.
  • the in the Fig. 1 to 3 shown outer and inner plates 10 and 11 are suitably provided as a milling, which can be introduced with high accuracy in a preform.
  • the Fig. 4 or 5 and 6 each show an alternative embodiment of the heat transfer tube 6, which was produced in particular by an extrusion molding process.
  • a wall thickness a of the inner fins 11 or a wall thickness a 'of the outer fins 10 decreases in the radial direction inwards or in the radial direction outwards. Accordingly, the extension of the fins 10, 11 in the circumferential direction following the wall 7 of the heat transfer tube 6 is greatest and decreases continuously with the distance to the wall 7.
  • edges of the outer fins 10 and inner lamellae 11 performed rounded.
  • the outer fins 10 and the inner fins 11 contoured surfaces, which in the direction of the longitudinal axis 5 extending valleys 19 'and mountains 19'', so that a wave-shaped course is achieved. In this way, the heat exchange surface available for heat exchange is considerably increased.
  • the Fig. 7 and 8th show the arrangement of the heat exchanger 1 in a device 20 for converting mechanical energy into heat energy and vice versa, which is operated in particular as a heat pump.
  • a device 20 - but with different heat exchangers - is in the AT 505 532 B1 described.
  • the device 20 comprises a rotor 21 which is rotatable about a rotation axis 22 by means of a motor (not shown).
  • a flow channel for a closed loop process continuous working fluid such as a noble gas
  • the rotor 21 has a compressor unit 23 and a relaxation unit 24, which form a piping system.
  • the working fluid flows radially outward with respect to the rotation axis 22, compressing the working fluid due to the centrifugal acceleration. Accordingly, the working medium for pressure reduction in expansion tubes 26 of the expansion unit 24 is guided substantially radially inwards.
  • the compressor unit 23 and the expansion unit 24 are connected to each other by axially extending portions of the piping system, in which a heat exchange with a heat exchange medium, for example water, takes place.
  • a heat exchange medium for example water
  • outer heat exchangers 1 'and inner heat exchangers 1 are provided, in which the working medium compressed in the compression tubes 25 gives off heat to a heat exchange medium at a first temperature or the working medium expanded in the expansion tubes 26 absorbs heat from the heat exchange medium at a second temperature. Accordingly, the centrifugal acceleration acting on the working medium becomes 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 heat exchangers 1 'and 1 are fluidly connected to one another via lines 27, 28 or 29.
  • the heat exchange medium is supplied to the pipeline system via a feed 31 of a static distributor 32, via a co-rotating manifold 33, the heat exchange medium then via the line 27 Heat exchanger 1 'supplied in which it is heated by the line 28 in the co-rotating manifold 33.
  • the heated heat transfer medium is then fed to a heat cycle.
  • the cold heat exchange medium of the heat exchanger 1 is passed through an inlet 34 of a static distributor 35, conveyed with another co-rotating distributor 36 in the co-rotating line 29 to the low-pressure heat exchanger 1", where heat is released to the gaseous working medium. Subsequently, the heat exchange medium is supplied via the co-rotating distributor 36 to the static distributor 35, and finally leaves the device 20 via a drain.
  • the heat exchangers 1 'and 1 "by the basis of Fig. 1 to 6 explained heat exchanger 1 given, being provided as a second heat exchange medium, the working medium, the heat exchange medium as the first heat exchange medium.
  • the working medium and the heat exchange medium flow in countercurrent in the heat exchange channels 15 and 17, wherein in the heat exchangers 1 ', 1 "is to ensure proper return of the heat exchange medium.
  • Fig. 9 shows a longitudinal section through an alternative embodiment of the device 20 in the region of the heat exchanger 1, wherein the flow 20 'of the working medium and the flow 20 "of the heat exchange medium is shown schematically.
  • Fig. 10 shows an enlarged section of the heat exchanger 1. Accordingly the heat exchanger 1 in a central cavity 37 of the inner tube 4, a tie rod 38. At the protruding from the inner tube 4 ends of the tie rod 38 head parts 38 'are attached, which cover the end faces of the heat exchanger 1.
  • the device 20 further comprises a supply line 39 for the working medium.
  • the supply line 39 is connected to an annular gap 40, in which the linear flow in the feed line 39 is converted into a circular flow of the working medium about the longitudinal axis of the heat exchanger 1 (see. Fig. 11 ).
  • the annular gap 40 is formed in the embodiment shown between the lateral surface of the protruding from the inner tube 4 end of the tie rod 38 and an inner wall of the head portion 38 '.
  • the inlet openings 43 are connected to a feed 44 for the heat exchange medium.
  • the end faces 42 of the outer slats 10 are inclined forward as viewed in the flow direction.
  • the optimum angle between the end faces 42 of the outer fins 10 and the longitudinal axis of the heat transfer tube 6 is preferably selected as a function of the flow velocity. At flow velocities of less than 2 meters per second (m / s) steeper angles greater than 45 ° are possible. At speeds greater than 2 m / s, flatter angles are an advantage. In general, due to the limited space requirement, flat angles, in particular an angle of 45 °, are to be preferred.
  • each passage opening 47 is connected to exactly one distributor element 46, which is arranged substantially symmetrically with respect to the passage opening 47.
  • the passage openings 47 are arranged here at opposite ends of the circular-arc-shaped distributor elements 46.
  • FIGS. 14a to 14f show sections through the individual stages of the distributor 45, wherein Fig. 14a the entrance side of the manifold 45 and Fig. 14f the exit side of the distributor device 45 shows.
  • the first distributor element 46 viewed in the flow direction, is semicircular, with the distributor elements 46 of the subsequent stages being formed by correspondingly shorter arc elements.
  • the outlet-side distributor elements 46 of the distributor device 45 are arranged in such a way that an annular exit surface 48 is formed which has outlet openings 49 at substantially the same angular intervals.
  • the outlet openings 49 are arranged in the flow direction immediately in front of the inlet openings 43 of the outer heat exchange channels 15. Due to the symmetrical arrangement of the distributor elements 46, the heat exchange medium retains substantially equal flow paths between the feed 44 and the outlet openings 49 of the distributor device 45. Out Fig. 14 In addition, fastening means 50 can be seen with which the distributor elements 46 are held in a defined position relative to each other.
  • Fig. 15 shows a part of the device 20, wherein one of the inner axis of rotation with respect to the heat exchanger 1 "and one with respect to the axis of rotation outer heat exchanger 1 'can be seen are.
  • the rotor 21 has a common supporting body 51 for holding the inner heat exchanger 1 "and the outer heat exchanger 1 ' Fig. 15
  • the support body 51 has a plurality of plate elements 52 arranged substantially perpendicular to the axis of rotation and spaced apart in the direction of the axis of rotation (cf. Fig. 16 which have recesses for the passage of the heat exchangers 1 ', 1 ".
  • the heat exchangers 1', 1" are in this case encased with support tubes 53, which have gradations 54 for mounting the plate elements 52.
  • the outer heat exchanger 1 'between the outer tubes 3 and the support body 51 each have an insulating member 55 made of a thermally insulating material.
  • the inner heat exchanger 1 "remain free of such insulation elements, so that the support body 51 substantially assumes the temperature of the inner heat exchanger 1" during operation.
  • Fig. 17 shows an alternative embodiment of the support body 51, which according to Fig. 17 is formed with respect to the axis of rotation rotationally symmetrical profile body 56.
  • the profile body 56 has an inner element 57 with a plurality of inner recesses 58 for receiving the inner heat exchanger 1 "and a plurality of outer elements 59 with outer recesses 60 for receiving the outer heat exchanger 1 '
  • Fig. 17 are provided as outer elements 59 circumferentially closed, cylindrical receptacles 59 ', which include the outer recesses 60.
  • the inner member 57 is connected to each outer member 59 via exactly two extending in the radial direction connecting webs 61.
  • the distance between the connecting webs 61 advantageously increases radially outwards (cf. Fig. 18 ).
  • the wall thickness of the connecting webs advantageously decreases in the radial direction.
  • the outer elements 59 are connected via welds 62 with the connecting webs 61.
  • Welded joints 62 between the connecting webs 61 and the inner member 57 are provided.
  • the welded joints 62 may also be a positive connection, such as a hammer head or dovetail connection may be provided.
  • Fig. 19 shows an alternative embodiment of the support body 51, wherein the outer elements 59 in the direction of the inner member 57 has open outer recesses 60.
  • Fig. 20 shows a further embodiment of the support body 51, which according to Fig. 20 a fixed to the outside of the outer elements 59, cylindrical enclosure 63 has.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP15705481.8A 2014-01-09 2015-01-08 Vorrichtung zum umwandeln thermischer energie Active EP3092447B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50014/2014A AT515210B1 (de) 2014-01-09 2014-01-09 Vorrichtung zum Umwandeln thermischer Energie
PCT/AT2015/050005 WO2015103656A1 (de) 2014-01-09 2015-01-08 Vorrichtung zum umwandeln thermischer energie

Publications (2)

Publication Number Publication Date
EP3092447A1 EP3092447A1 (de) 2016-11-16
EP3092447B1 true EP3092447B1 (de) 2019-03-06

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EP15705481.8A Active EP3092447B1 (de) 2014-01-09 2015-01-08 Vorrichtung zum umwandeln thermischer energie

Country Status (5)

Country Link
US (1) US9897348B2 (zh)
EP (1) EP3092447B1 (zh)
CN (1) CN105934640B (zh)
AT (1) AT515210B1 (zh)
WO (1) WO2015103656A1 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109073338B (zh) * 2016-02-29 2021-11-19 纳提福斯有限公司 旋转热交换器
CN110425913B (zh) * 2019-08-30 2024-02-27 中国科学院理化技术研究所 一种数据中心套管换热结构及其控制方法
US11692745B2 (en) * 2021-04-01 2023-07-04 Richard Stockton TRENBATH Method and apparatus for expelling heat
EP4202342A1 (de) 2021-12-22 2023-06-28 Ecop Technologies GmbH Wärmetauscher, insbesondere rohrbündelwärmetauscher, zur anordnung in einem rotor mit einer drehachse
EP4339534A1 (de) 2022-09-14 2024-03-20 Ecop Technologies GmbH Rotor

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Publication number Priority date Publication date Assignee Title
US3258197A (en) * 1961-04-10 1966-06-28 William H Anderson Space coolers
US3846302A (en) * 1972-08-02 1974-11-05 R Crocker Apparatus for heat treating liquid or semi-liquid material
FR2406718A1 (fr) * 1977-10-20 1979-05-18 Bailly Du Bois Bernard Procede de conversion thermodynamique de l'energie et dispositif pour sa mise en oeuvre
US4420944A (en) * 1982-09-16 1983-12-20 Centrifugal Piston Expander, Inc. Air cooling system
US4433551A (en) * 1982-10-25 1984-02-28 Centrifugal Piston Expander, Inc. Method and apparatus for deriving mechanical energy from a heat source
CN2201628Y (zh) * 1993-07-01 1995-06-21 杨建林 整体旋转式制冷装置及其动力装置
SE511741C2 (sv) * 1997-01-14 1999-11-15 Nowacki Jan Erik Motor, kylmaskin eller värmepump
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
WO2010000840A1 (en) * 2008-07-04 2010-01-07 Heleos Technology Gmbh Process and apparatus for transferring heat from a first medium to a second medium
AT509231B1 (de) * 2010-05-07 2011-07-15 Bernhard Adler Vorrichtung und verfahren zum umwandeln thermischer energie

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Publication number Publication date
US20160377327A1 (en) 2016-12-29
US9897348B2 (en) 2018-02-20
CN105934640A (zh) 2016-09-07
AT515210A4 (de) 2015-07-15
EP3092447A1 (de) 2016-11-16
AT515210B1 (de) 2015-07-15
CN105934640B (zh) 2018-09-11
WO2015103656A1 (de) 2015-07-16

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