EP3092447A1 - Dispositif de conversion d'une énergie thermique - Google Patents

Dispositif de conversion d'une énergie thermique

Info

Publication number
EP3092447A1
EP3092447A1 EP15705481.8A EP15705481A EP3092447A1 EP 3092447 A1 EP3092447 A1 EP 3092447A1 EP 15705481 A EP15705481 A EP 15705481A EP 3092447 A1 EP3092447 A1 EP 3092447A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
axis
heat
rotation
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15705481.8A
Other languages
German (de)
English (en)
Other versions
EP3092447B1 (fr
Inventor
Bernhard Adler
Sebastian Riepl
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.)
Ecop Technologies GmbH
Original Assignee
Ecop Technologies GmbH
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 Ecop Technologies GmbH filed Critical Ecop Technologies GmbH
Publication of EP3092447A1 publication Critical patent/EP3092447A1/fr
Application granted granted Critical
Publication of EP3092447B1 publication Critical patent/EP3092447B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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 outwards and is guided in a relaxation unit for reducing pressure with respect to the axis of rotation in Wesentli ⁇ chen radially inwardly, wherein at least one in Be ⁇ zug on the axis of rotation inner heat exchanger and at least one with respect are provided on the axis of rotation outer heat exchanger for heat exchange between the working fluid 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.
  • a heat pump or boss kraftma ⁇ machine in which the working medium in a piping system of a rotor of a cycle with the working ⁇ steps a) compression of the working medium, b) heat removal from the working medium by means of a heat exchanger, c) Relaxation of the working medium and d) heat supply to the working medium by ei ⁇ nes further heat exchanger passes.
  • the pressure increase or pressure reduction of the working medium adapts by the centering ⁇ rifugalbestructung, wherein the working medium flowing in a radial radial compacting unit with respect to an axis of rotation to the outside and in an expansion unit to the inside.
  • the Wär ⁇ meabschreib from the working medium to a heat exchange medium of the heat exchanger is in an axial or parallel to the rotational axis portion of the piping system, which is assigned a mitro ⁇ animal ender heat exchange medium having Direction heat exchanger.
  • This device allows already an effi cient ⁇ conversion of mechanical energy and heat energy nied- riger temperature in heat energy of higher temperature.
  • 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.
  • 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 rotor has a support body supporting the inner and / or outer heat exchanger over its longitudinal extension for holding the inner and / or outer heat exchanger.
  • the inventive apparatus uses the Zentrifugalbeschleu ⁇ n Trent of the rotating system to generate different pressure and temperature levels; 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. Depending on the direction of flow of the working medium, the apparatus will be thereby selectively operated as if ⁇ mepumpe or motor.
  • a in respect to the rotation axis internal heat exchanger and at least one used in Be ⁇ train to the rotational axis external heat exchanger, which is preferably substantially parallel to the arrival of the rotor axis of rotation are ordered.
  • the internal heat exchanger is provided for heat from ⁇ exchange at a lower temperature and the outdoor heat exchanger for heat exchange at higher temperature.
  • 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 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 by means of the support body in Wesent ⁇ union is provided uniformly in the longitudinal direction of the heat exchanger ⁇ so that only low or uncritical bends along the heat exchanger occur.
  • 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 ⁇ exchanger between the outer tube and the support body has an insulating element made of a thermally insulating material, wherein the inner heat exchanger of an insulating element remains free.
  • the outer or achsfernen heat exchanger which have a higher relative temperature than the inner or achs ⁇ near heat exchanger under normal operation, in particular tubular insulation elements with a compared to the support body substantially lower thermal conductivity of the support body be thermally insulated.
  • the thermally insulating material has be ⁇ vorzugt a tensile strength of at least 10 Mpa, in order to avoid a flow under the load.
  • ther- mixed insulating material have a temperature stability corresponding to the maximum temperature of the heat exchanger. Since ⁇ ago to ordinary polycarbonate has at temperatu ⁇ ren 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.
  • both the off-axis and the near-axis heat exchanger by means of Isolati ⁇ onsettin be thermally insulated from the support body.
  • the support body may be provided with an active cooling (eg over water cooling, heat radiation or convection) to verhin losses in the strength of the support body ⁇ countries.
  • 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 on the inner Ren 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 tempera ⁇ tures supporting this variant is very suitable for high temperature ⁇ temperature applications.
  • the supporting body is made of steel using welded joints can be made, this embodiment particular cost advantages, brings at comparatively high Festtechniksei ⁇ properties with it. Another advantage of a
  • Welded support body is the almost unlimited size ⁇ cal réelle. 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, for example, aluminum plates and aluminum tubes
  • 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 recesses aufwei ⁇ sen to reduce the weight of the support body and / or to change the rigidity de plate elements. This can be used before ⁇ geous enough to achieve uniform deformations in the transition to the edge ⁇ area, which may have an increased weight.
  • the plate elements are arranged at equal intervals before ⁇ Trains t.
  • 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.
  • Advantageously ⁇ example can hereby shearing forces are absorbed.
  • a profiled body extended in the direction of the axis of rotation is provided as the supporting body, which has an inner element with at least one inner recess for the at least one inner heat exchanger and at least one outer element with 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.
  • 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 external element of the support body is designed as a cylindrical receptacle for the äuße ⁇ ren heat exchanger.
  • the intake can be partly open inwards. Due to the not circumferentially supported achsfernen heat exchanger can at a
  • Casting a core per heat exchanger accounts. Furthermore, the introduction of force in the off-axis heat exchanger can be improved, whereby the stresses due to the centrifugal forces can be redu ⁇ sheet.
  • the support body has an outer elements surrounding cylindrical ⁇ A jack.
  • the outer elements are in this case attached to the inner ⁇ side of the cylindrical enclosure. Through the cylindrical shell, the frictional losses in rotating Be ⁇ operating state of the apparatus 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 shows a cross section through a heat exchanger for a rotor device according to the invention for the transmission of thermal energy, wherein between a inner tube and an outer tube, a heat transfer tube is arranged.
  • Figure 2 shows a detail of the heat exchanger shown in Figure 1 in contrast enlarged scale.
  • FIG. 3 shows a further enlarged detail of the heat exchanger according to FIG. 1 or FIG. 2, whereby in particular outer fins of the heat transfer tube can be seen;
  • FIG. 4 shows an alternative embodiment of a heat transfer tube produced in the extrusion process, which is provided for arrangement in egg ⁇ nem heat exchanger according to Figures 1 to 3 ..;
  • Fig. 5 is a modified embodiment of the heat transfer tube shown in Fig. 4, in which the surfaces of the fins are undulating;
  • Fig. 6 is a detail of the heat transfer tube shown in Fig. 5, on the contrary, on an enlarged scale;
  • Fig. 7 is a view of a rotary apparatus for converting low temperature thermal energy to higher temperature thermal energy, in which a working fluid in a rotor undergoes a closed loop process;
  • Fig. 8 is another view of the device shown in Fig. 7;
  • FIG. 9 is a longitudinal section through an alternative embodiment of the device in the region of the heat exchanger, wherein the flow of the working medium and the flow of the heat exchange medium are shown schematically (here in countercurrent);
  • Figure 11 is a sectional view of the device in the region of an annular gap to achieve a circular flow of the working medium before entering the heat exchanger.
  • FIG. 12 is a perspective view of an embodiment of the heat ⁇ transmission tube of the heat exchanger, in which the Stirnflä ⁇ surfaces of the outer fins are inclined in the direction of flow forward;
  • FIG. 13 is a perspective view of a distributor device with which a linear flow of the heat exchange medium is divided into a plurality of annularly arranged partial flows;
  • FIG. 14 shows various sectional views of the distributor device according to FIG. 13;
  • FIG. 15 shows an embodiment of the device in which a support body with a plurality of plate elements is provided for mounting the heat exchanger;
  • FIG. 16 shows a detail of the support body with a gela ⁇ siege heat exchanger therein;
  • 17 is a perspective view of another embodiment of the support body with substantially parallel connecting webs.
  • FIG. 18 is a view of a further embodiment of the support body with running in the radial direction of the rotor and thus diverging outwardly connecting webs.
  • Fig. 19 is a perspective view of another embodiment of the support body.
  • Fig. 20 is a perspective view of another embodiment of the support body.
  • a heat exchanger 1 for installation in a rotary device 20 for converting thermal energy by means of mechanical energy and vice versa (see Fig. 7, 8) is shown.
  • the heat exchanger 1 has an inner longitudinal member 2 and an outer tube ⁇ 3, surrounding the inner elongate member. 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 with the outer tube 3 and the inner tube 4 in the longitudinal direction of the heat exchanger.
  • the Heat Transf ⁇ confining tube 6 has a wall 7 with an outer surface 8 and an inner lateral surface 9, protruding from the outer fins 10 or inner fins 11.
  • the fins 10, 11 extend in the direction of the longitudinal axis of extension 5 of the Heat Transf ⁇ confining tube 6.
  • the outer lamellae 10 project from the outer surface 8 in the radial direction outwardly to an inner surface 12 of the outer tube 3.
  • the inner disk 11 to jump from the inner circumferential surface 9 of the wall 7 of the heat transfer Pipe 6 to an outer surface 13 of the inner tube 4 before.
  • the heat exchange channels 15 form for a first Wär ⁇ meternum.
  • spaces 16 between the inner fins 11 form heat exchange channels 17 for a second heat exchange medium.
  • a multiplicity, for example 250, of outer plates 10 or inner plates 11 are provided, so that at regular angular intervals in the circumferential direction of the heat transfer tube 6, spaced outer heat exchange channels 15 for the first heat exchange medium or inner heat exchange channels 17 are formed for the second heat exchange medium.
  • the heat exchange ⁇ medium flows at the lower absolute pressure in the outer heat exchanging passages 15 between the outer laminations 10, wherein the second heat exchange medium with considerably higher pressure through the heat exchange channels 17 between the inner fins can flow.
  • the bilateral support of the heat transfer tube 6 made it ⁇ light that caused by the differential pressure stresses in the region of the wall 7 of the heat transfer tube 6 are transmitted via externa ⁇ ßeren blades 10 to the outer tube. 3
  • 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.
  • a mechanically very stable arrangement of the heat transfer tube 6 is achieved, which can be made thin-walled for Op ⁇ timing of 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 ei ⁇ ner wall thickness s '' of the inner tube 4 is about 0.3.
  • the wovennwandi ⁇ ge embodiment of the heat transfer tube 6 allows a Heat transfer with high efficiency, whereby in particular the extension of the heat exchanger can be shortened in the longitudinal direction, which has proven to be advantageous for example in the embodiment explained with reference to FIGS. 7 and 8.
  • the outer disc 10 have a height h, that is an extension in the radial direction, which is preferably greater than a height h 'of the inner La ⁇ mellen. 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 with 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 ⁇ transmission pipe 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
  • outer and inner plates 10 and 11 shown in FIGS. 1 to 3 are expediently provided as milling, which can be introduced into a preform with high accuracy.
  • FIGS. 4 and 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 laminations 11 and takes a wall thickness ⁇ a 'of the outer disc 10 in the radially inward direction or in the radial direction to the outside. 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 lamellae 10 and the inner lamellae 11 have contoured surfaces which have valleys 19 'or mountains 19 "extending in the direction of the longitudinal axis 5, so that a wave-shaped course is achieved. In this way, the heat exchange surface available for heat exchange is considerably increased.
  • Figs. 7 and 8 show the arrangement of the heat exchanger 1 in an apparatus 20 for converting mechanical
  • 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 flashing unit 24, which form a Rohr Oberssys ⁇ tem.
  • 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 Ent ⁇ voltage 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
  • the heat exchangers 1 'and 1'' are fluidly connected to each other via lines 27, 28 and 29, respectively.
  • the ratio techme ⁇ dium is supplied to the pipe system via an inlet 31 of a static distributor 32; via a co-rotating distributor 33, the heat exchange medium is then supplied via the line 27 to the heat exchanger 1 ', in which it heats up
  • 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, promoted with ei ⁇ nem further co-rotating manifold 36 in the co-rotating line 29 to the low-pressure heat exchanger 1 '', where heat is released to the gaseous working fluid. 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 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''to ensure proper recycling 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 nenrohrs 4 a tie rod 38. To the inner tube 4 from the projecting ends of the tie rod 38 head parts 38 'buildin ⁇ Untitled which cover the end faces of the heat exchanger. 1
  • the device 20 further includes a supply line 39 for the working fluid.
  • the Zulei ⁇ tung 39 is connected to an annular gap 40 in which the linear flow in the supply line 39 is converted to the longitudinal axis of varnishtau ⁇ exchanger 1 in a circular flow of the working medium (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 heat transfer tube 6 has end openings 42 for the heat exchange medium between end faces 42 of the outer lamellae.
  • 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 plate 10 and the longitudinal axis of the heat transfer tube 6 is preferably selected depending on the Strömungsge ⁇ speed.
  • Steeper angle GroE ⁇ SSER 45 ° at flow rates of less than 2 meters per second (m / s) are possible. At speeds greater than 2 m / s, flatter angles are an advantage.
  • 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 device 45, wherein FIG. 14a shows the inlet side of the distributor device 45 and FIG. 14f shows the outlet side of the distributor device 45.
  • 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 exit-side manifold members 46 of the manifold 45 are arranged such that a circular annular ⁇ exit surface 48 is formed having in Wesent ⁇ union at equal angular intervals outlet openings 49th
  • 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 essentially passes the same flow paths between the feed 44 and the outlet openings 49 of the distributor device 45. From Fig. 14 also fastener 50 can be seen, with wel ⁇ Chen the distributor elements 46 are held in a defined position 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 longitudinal axes of the heat exchangers 1 ', 1'' are arranged substantially parallel to the axis of rotation of the rotor 21.
  • the rotor 21 has a common support body 51 for holding the inner heat exchangers 1 '' and the outer heat exchanger 1 '.
  • the support body 51 has a plurality of plate elements 52, which are arranged substantially perpendicular to the axis of rotation and are spaced apart in the direction of the axis of rotation (cf., also FIG. 16), which have recesses for the passage of the heat exchangers 1 ', 1''.
  • the heat exchanger 1 ', 1'' are in this case coated with support tubes 53, wel ⁇ che gradations 54 for supporting the plate members 52 have.
  • the outer heat exchangers 1 'between the outer tubes 3 and the support body 51 each have an insulation element 55 made of a thermally insulating material.
  • the inner heat exchanger 1 '' remain free of such insulation elements, so that the support body 51 in operation substantially the temperature of the inner heat exchanger 1 '' assumes.
  • FIG. 17 shows an alternative embodiment of the supporting body 51, which according to FIG. 17 is designed as a profile body 56 which is rotationally symmetrical with respect to the axis of rotation.
  • the profile body 56 has an inner member 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 '.
  • the outer elements 59 in the circumferential direction closed cylindrical seats' pre ⁇ see 59, which include the outer recesses 60.
  • the inner member 57 is connected to each ⁇ the outer member 59 through exactly two duri ⁇ Fende in the radial direction connecting bars 61.
  • the distance between the connecting webs 61 advantageously increases radially outward (see Fig. 18).
  • the wall thickness of the connecting webs advantageously decreases in the radial direction.
  • the outer elements 59 are connected to the connecting webs 61 via welded connections 62.
  • 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 of ⁇ fene outer recesses 60 has.
  • FIG. 20 shows a further embodiment of the support body 51, wel ⁇ cher according to FIG. 20 has a fixed to the outside of the outer elements 59, cylindrical enclosure 63.

Abstract

L'invention concerne un dispositif (20) de conversion d'une énergie thermique de basse température en énergie thermique de plus haute température au moyen d'une énergie mécanique et inversement. Ledit dispositif est pourvu d'un rotor (21) monté de manière à pouvoir tourner autour d'un axe de rotation (22), un canal d'écoulement pour un milieu actif parcourant un circuit fermé étant prévu dans ledit rotor. Ledit milieu est guidé vers l'extérieur par rapport à l'axe de rotation dans une unité de compression (23) pour l'augmentation de sa pression et est guidé vers l'intérieur par rapport à l'axe de rotation (22) dans une unité de détente (24) pour la diminution de sa pression. Au moins un échangeur de chaleur (1'') intérieur par rapport à l'axe de rotation et au moins un échangeur de chaleur (1') extérieur par rapport à l'axe de rotation sont destinés à mettre en œuvre un échange de chaleur entre le milieu actif et un milieu d'échange de chaleur, les échangeurs de chaleur (1', 1'') étant disposés de préférence sensiblement parallèlement à l'axe de rotation du rotor (21). Le rotor (21) comporte un élément de support (51) soutenant l'échangeur de chaleur intérieur (1'') et/ou l'échangeur de chaleur extérieur (1') sur toute la longueur de ces derniers, ledit élément de support étant destiné au maintien de l'échangeur de chaleur intérieur (1'') et/ou de l'échangeur de chaleur extérieur (1').
EP15705481.8A 2014-01-09 2015-01-08 Dispositif de conversion d'une énergie thermique Active EP3092447B1 (fr)

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 (fr) 2014-01-09 2015-01-08 Dispositif de conversion d'une énergie thermique

Publications (2)

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

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EP15705481.8A Active EP3092447B1 (fr) 2014-01-09 2015-01-08 Dispositif de conversion d'une énergie thermique

Country Status (5)

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

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WO2017151439A1 (fr) * 2016-02-29 2017-09-08 Nativus, Inc. Échangeur de chaleur rotatif
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 (fr) 2021-12-22 2023-06-28 Ecop Technologies GmbH Échangeur de chaleur, en particulier échangeur de chaleur à faisceau tubulaire, destiné à être agencé dans un rotor doté d'un axe de rotation
EP4339534A1 (fr) 2022-09-14 2024-03-20 Ecop Technologies GmbH Rotor

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US9897348B2 (en) 2018-02-20
CN105934640A (zh) 2016-09-07
CN105934640B (zh) 2018-09-11
AT515210B1 (de) 2015-07-15
EP3092447B1 (fr) 2019-03-06
AT515210A4 (de) 2015-07-15
WO2015103656A1 (fr) 2015-07-16
US20160377327A1 (en) 2016-12-29

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