EP4339534A1 - Rotor - Google Patents

Rotor Download PDF

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Publication number
EP4339534A1
EP4339534A1 EP22195656.8A EP22195656A EP4339534A1 EP 4339534 A1 EP4339534 A1 EP 4339534A1 EP 22195656 A EP22195656 A EP 22195656A EP 4339534 A1 EP4339534 A1 EP 4339534A1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
channels
rotor
rotor plates
working medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22195656.8A
Other languages
German (de)
English (en)
Inventor
Bernhard Adler
Christian RAKUSCH
Andreas LÄNGAUER
Johannes Erhard
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
Priority to EP22195656.8A priority Critical patent/EP4339534A1/fr
Priority to PCT/EP2023/075263 priority patent/WO2024056788A1/fr
Publication of EP4339534A1 publication Critical patent/EP4339534A1/fr
Pending legal-status Critical Current

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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

Definitions

  • a rotary heat pump is known in which the centrifugal acceleration of the rotor is used to generate different pressure or temperature levels. Heat at a high temperature is removed from the compressed working medium and heat at a comparatively low temperature is supplied to the expanded working medium.
  • the rotary heat pump has internal heat exchangers and external heat exchangers, which are arranged essentially parallel to the axis of rotation of the rotor. The inner heat exchangers are set up for heat exchange at a lower temperature and the outer heat exchangers are set up for heat exchange at a higher temperature.
  • This type of rotary heat pump has significant advantages over stationary heat pumps. The disadvantage, however, is the high design effort of the known rotary heat pump. In addition, there is a need for improvement with regard to the rotor dynamics, which in the prior art is impaired by the mechanical connection of the individual components. Finally, there are always efforts to further increase the efficiency of such rotary heat pumps (COP - Coefficient of Performance).
  • the present invention therefore sets itself the task of alleviating or eliminating at least individual disadvantages of the prior art.
  • the aim of the invention is preferably to create a rotor which combines low design effort with high efficiency.
  • first and second rotor plates are provided, wherein the first and / or the second rotor plates have the compression channels, the expansion channels, the first heat transfer channels for the working medium and the second heat transfer channels for the heat transfer medium, the first and the second rotor plates along their Main extension levels are connected to each other.
  • the arrangement of the first and second rotor plates forms a compact rotor element that is particularly stable in relation to rotational forces, which combines the functions separated into individual components such as inner and outer heat exchangers as well as expansion and compression channels in the prior art.
  • the first and second rotor plates are stacked in contact with one another and connected to one another at their meeting main extension planes.
  • the working medium flows through flow channels, which form the first heat transfer channels, the compression channels and the expansion channels. Accordingly, the heat transfer medium flows through the second heat transfer channels of the first and/or second rotor plates in order to enable heat transfer with the working medium.
  • a rotor in particular a rotary heat pump or a heat-power machine for providing electrical current from a heat flow, in which the essential process steps are integrated into the interior of the package consisting of the first and second rotor plates.
  • This design achieves particularly favorable rotor dynamics. What has proven to be particularly advantageous is that the first and second rotor plates virtually cannot move against each other, so that the number of balancing runs can be significantly reduced or balancing runs can be avoided entirely.
  • the rotor element can be realized from the first and second rotor elements in different designs, in particular also with smaller dimensions. This has the advantage that production can be simplified and a weaker drive machine can be used. Compared to the discrete heat exchangers in the prior art, the heat exchanger surfaces available during operation of the rotor can also be increased. The integral design of the rotor element also allows the number of sealing points to be significantly reduced.
  • the location and direction information relates to the intended use state of the rotor, with “radial”, “axial” and “circumferential” referring to the axis of rotation.
  • “inside” means closer to the axis of rotation of the rotor and “outside” means further from the axis of rotation.
  • the Main extension planes of the first and second rotor plates ie their plate planes, in which the first and second rotor plates each have their greatest extent, are each arranged essentially perpendicular to the axis of rotation.
  • the axis of rotation preferably passes through the centers of the first and second axes of rotation.
  • the first and second rotor plates are arranged essentially congruently when viewed in the direction of the axis of rotation.
  • the first rotor plates each have at least one of the compression channels, at least one of the expansion channels and at least one of the first heat transfer channels for the working medium and the number of second rotor plates each have at least one of the second heat transfer channels for the heat transfer medium.
  • the first rotor plates each have at least one flow channel for the working medium, the at least one flow channel having an inlet opening for the working medium at a first end and an outlet opening for the working medium at a second end.
  • the flow channel has a preferably substantially radially outwardly extending flow channel section for forming one of the compression channels and/or a preferably substantially radially inwardly extending flow channel section for forming one of the expansion channels and/or a preferably substantially circumferentially extending flow channel section Formation of one of the first heat transfer channels.
  • the working medium can thus be distributed via the inlet openings to the flow channels within the first rotor plates.
  • the working medium then flows along the flow channels to the outlet openings, at which the working medium is led out of the rotor element.
  • the working medium In the flow channel section leading to the outside, the working medium can be compressed by the effect of centrifugal acceleration in the rotating state of the rotor. In the inwardly leading flow channel section, the working medium, also due to the centrifugal force. Heat can be transferred between the working medium and the heat transfer medium in the flow channel cross section that runs essentially in the circumferential direction.
  • the individual flow channel sections are connected so that the working medium can flow through the flow channel within the first rotor plate from the inlet to the outlet opening.
  • the inlet openings and/or the outlet openings of the first rotor plates are each arranged in alignment, i.e. in a line parallel to the axis of rotation.
  • the inlet openings and/or the outlet openings are preferably congruent when viewed in the direction parallel to the axis of rotation.
  • the second rotor plates in this embodiment preferably each have through openings arranged in alignment with the inlet openings or in alignment with the outlet openings.
  • the working medium can thus be supplied to one side of the rotor element and distributed to the first rotor plates via the inlet openings, with second rotor plates arranged in between being passed through the through openings.
  • the outlet openings are arranged in central regions of the first rotor plates through which the axis of rotation passes.
  • the axis of rotation preferably passes through the centers of the outlet openings.
  • the working medium can be guided along the flow channels to the outlet openings in the central regions of the first rotor plates and can be drained out of the first rotor plates via the outlet openings, which are preferably arranged in alignment.
  • several flow channels of the first rotor plate can share the same outlet opening in the central area.
  • a fan is provided.
  • the fan is preferably arranged in the axial direction outside the rotor element made up of the first and second rotor plates.
  • a circular flow of the working medium can be effected from the fan via the inlet openings through the flow channels within the rotor element, via the outlet openings back to the fan and finally back to the inlet openings in the flow channels within the rotor element.
  • This means that the working medium can go through a circular process.
  • different types of cycle processes can be achieved, for example a Joule process with essentially isobaric heat transfer.
  • the fan can be connected to a fan drive, with which a blade wheel of the fan can be set in rotation.
  • the blade wheel can be rotated relative to the rotor element, which is preferably set in rotation with a motor that is different from the fan drive.
  • the inlet openings of the first rotor plates can be connected to an outlet of the fan and/or the outlet openings of the first rotor plates can be connected to an inlet of the fan.
  • the first rotor plates each have a plurality of flow channels, each with at least one preferably substantially radially outwardly extending flow channel section and/or with at least one preferably substantially substantially radially inwardly extending flow channel section and/or with at least one flow channel section that preferably runs essentially in the circumferential direction.
  • several flow channels can be formed on the first rotor plates, through which the working medium can flow in parallel.
  • the flow channels can cover the surface of the first Rotor plate be distributed.
  • more than three, in particular more than six, for example twelve, flow channels are provided at different angular positions per first rotor plate.
  • the flow channels of the first rotor plates each have a plurality of flow channel sections, which preferably run essentially in the circumferential direction, at different radial distances from the axis of rotation in order to form a plurality of first heat transfer channels.
  • the flow channel sections running in the circumferential direction are preferably arranged in loops.
  • there are a plurality of inner, for example S-shaped, loops for heat exchange with the heat transfer medium in inner loops of one of the second heat transfer channels of one of the second rotor plates and/or a plurality of outer, for example S-shaped, loops for heat exchange with the heat transfer medium in outer loops of one of the second Heat transfer channels of one of the second rotor plates are provided.
  • intermediate compression or expansion can be effected during the heat exchange with the heat transfer medium. This can ensure that the temperature is raised again after heat transfer in order to either transfer the heat at a substantially constant temperature or to increase efficiency if an application with a small temperature difference between the inlet and outlet of the heat transfer medium is intended.
  • two adjacent flow channels of the first rotor plates are arranged mirrored with respect to a plane of symmetry spanned in the axial and radial directions, with the two adjacent flow channels having a common inlet and a common outlet opening for the working medium split.
  • 12 flow channels are provided at different angular positions per first rotor plate, in this embodiment only six connections are required for the Entry of the working medium is required.
  • the second rotor plates each have at least one inner flow channel and at least one outer flow channel each to form one of the second heat transfer channels, the outer flow channel being arranged further out in the radial direction than the inner flow channel.
  • the outer flow channel can be designed as an external heat exchanger, in which the heat transfer medium, here the sink medium, absorbs heat from the working medium.
  • the inner flow channel can be designed as an internal heat exchanger, in which the heat transfer medium, here the source medium, releases heat to the working medium.
  • the rotor can be designed as a heat-power machine.
  • the first rotor plates have the second heat transfer channels for the heat transfer medium.
  • the second rotor plates can be designed as separating plates for the first rotor plates, with the second separating plates preferably being free of flow channels for both the working medium and the heat transfer medium.
  • first rotor plates and the second rotor plates are connected to one another via diffusion connections, i.e. by diffusion bonding.
  • first rotor plates and/or at least 50, in particular at least 200, for example from 300 to 800, second rotor plates are preferably provided.
  • the first and/or the second rotor plates can have a wall thickness, i.e. an extension perpendicular to the main extension or plate plane from one outer surface to the other, from 0.2 mm to 5 mm, in particular from 0.5 mm to 4 mm, for example 2 mm to 3 mm.
  • the flow channels can have a width, i.e. an extent on the outer surface of the respective first or second rotor plate transverse to the flow direction, of 0.5 mm to 5 mm, in particular from 1 mm to 3 mm.
  • the depth of the flow channels, i.e. their extension perpendicular to the main extension plane at the deepest point can be from 0.2 mm to 3 mm, in particular from 1 mm to 2 mm.
  • the first and second rotor plates are in plan view, ie looking in axial direction, each circular.
  • the heat transfer surfaces can be optimized at a predetermined length, ie axial extent, of the rotor element consisting of the first and second rotor plates.
  • the first and second rotor plates are each non-round when viewed in the direction of the axis of rotation, i.e. not circular, in particular essentially rectangular.
  • This embodiment can be favorable when producing the rotor element by diffusion bonding of the first and second rotor plates, since rectangular vacuum presses can be used for diffusion bonding.
  • the manufacturing process can be optimized in this way; In addition, larger radial extents can be achieved.
  • one of the first rotor plates and one of the second rotor plates are preferably arranged alternately. If the working medium is guided in the first rotor plates and the heat transfer medium is guided in the second rotor plates, the first heat transfer channels of the first rotor plates and the second heat transfer channels of the second rotor plates run essentially at the same radial distances and along the same sections in the circumferential direction, i.e. next to each other. When the working medium and the heat transfer medium are guided in the first rotor plates, the first heat transfer channels and the second heat transfer channels run essentially at the same radial distances and along the same sections in the circumferential direction opposite each other on the first rotor plates.
  • the first rotor plates and/or the second rotor plates each have at least one recess.
  • this can achieve weight savings. Insulation can also be achieved in areas where unwanted heat transfer needs to be minimized. Thus, it can Recess, for example, form an insulation area between the compression and expansion channels or between the outer heat exchanger, in particular with a comparatively high temperature, and the inner heat exchanger, in particular with a comparatively low temperature.
  • the first and second rotor plates are formed from a material selected from austenite, duplex steel, copper, titanium and aluminum.
  • first rotor plates and the second rotor plates are connected to one another by diffusion bonding, in particular in a vacuum press.
  • the compression, the expansion, the first heat transfer channels and/or the second heat transfer channels are preferably formed in the first and/or second rotor plates by etching or milling.
  • the design of the rotor element from the first and second rotor plates enables application with high pressures.
  • the maximum pressure of the working medium in the rotating state of the rotor within the first rotor plates is at least 80 bar, in particular at least 120 bar, for example from 160 bar to 240 bar.
  • these pressures result in lower pressure losses for the same mass flow and thus higher efficiency, which is determined with the “Coefficient of Performance” (COP) when the rotor is designed as a heat pump.
  • COP Coefficient of Performance
  • Fig. 1 shows a rotor 1, which in the embodiment shown is designed as a device for converting mechanical energy into thermal energy (and vice versa).
  • the rotor 1 is used in particular as a rotary heat pump.
  • the rotor 1 can be accommodated in a stationary housing in which a negative pressure can prevail.
  • the rotor 1 has a rotation axis 2, which is preferably horizontal in the operating state, around which the rotor 1 is rotated with the aid of a motor 37.
  • the rotor 1 has two pivot bearings 3.
  • the rotor 1 has an in Fig.
  • rotor element 4 which is connected on one side with connections 5 for a heat transfer medium, in particular water, and on the other side with connections 6 for a working medium, for example a noble gas. Furthermore, a fan 7 is provided to maintain a circular flow of the working medium. The fan 7 is connected to a fan drive 8 in order to rotate a blade wheel of the fan 7 relative to the rotor element 4 rotated by the motor 37. Furthermore are in Fig. 1 Rotary unions 9 for the (water) connections 5 can be seen.
  • Fig. 2A , Fig. 2B and Fig. 3 show schematically an embodiment of the rotor element 4, which is constructed from a plurality of first rotor plates 10 and second rotor plates 11.
  • first rotor plates 10 and second rotor plates 11 are shown.
  • the flow of the working medium is illustrated with solid lines and the flow of the heat transfer medium is illustrated with dashed lines.
  • the first rotor plates 10 and the second rotor plates 11 are connected to one another on their outer surfaces parallel to their main extension or plate planes (which are vertically aligned during operation).
  • the first 10 and the second rotor plates 11 alternate with one another as seen in the axial direction.
  • the first rotor plates 10 each have a plurality of flow channels 12 through which the working medium flows.
  • the working medium flows into an initial section of the flow channel 12 via an inlet opening 13 and out of an end section of the flow channel 12 via an outlet opening 14.
  • several adjacent, parallel flow channels 12 are provided per inlet opening 13, cf Fig. 2A Detail B highlighted with a circle Fig. 2B .
  • the inlet openings 13 are connected to an output of the fan 7.
  • the outlet openings 14 are connected to an input of the fan 7.
  • the outlet openings 14 are arranged in the central regions of the first rotor plates 10 through which the axis of rotation 2 passes.
  • the flow channel 12 has a flow channel section 16 that leads essentially radially outwards, in which the working medium is guided away from the axis of rotation 2 to increase the pressure due to the centrifugal acceleration.
  • the essentially radially outwardly leading flow channel section 16 is adjoined by at least one essentially circumferentially extending flow channel section 17, with which a first heat transfer channel 18 is formed for heat exchange with the heat transfer medium.
  • the peripheral flow channel section 17 is adjoined by a flow channel section 19 which leads essentially radially inwards and, as a relaxation channel 20, causes a pressure reduction in the working medium due to the centrifugal acceleration.
  • Adjacent to the essentially radially inwardly leading flow channel section 19 is at least one further essentially circumferentially extending flow channel section 21, which is designed as a further first heat transfer channel 18 for heat exchange with the heat transfer medium.
  • the inlet openings 13 and the outlet openings 14 of the first rotor plates 10 are each arranged in alignment.
  • the second rotor plates 11 have corresponding through openings 32 for the passage of the working medium.
  • the second rotor plates 11 each have second heat transfer channels 22 through which the heat transfer medium flows.
  • the second rotor plates 11 each have at least one inner flow channel 23 with at least one section 24 running in the circumferential direction to form an inner heat exchanger and at least one outer flow channel 25 with a section 26 running in the circumferential direction to form an outer heat exchanger.
  • the outer flow channel 25 is arranged further outward than the inner flow channel 23 when viewed in the radial direction.
  • the circumferentially extending section 24 of the inner heat exchanger of the second rotor plate 11 runs next to the circumferentially extending flow channel section 21 of the first rotor plate 10.
  • the circumferentially extending section 26 of the outer heat exchanger of the second rotor plate 11 runs next to the circumferentially extending flow channel section 17 of the first rotor plate 10.
  • the inner flow channel 23 of the second rotor plate 11 has an inlet opening 27 for the entry of the heat transfer medium and an outlet opening 28 for the exit of the heat transfer medium.
  • the outer flow channel 25 has a further inlet opening 29 for the entry of the heat transfer medium and a further outlet opening 30 for the exit of the heat transfer medium.
  • the input openings 27, the output openings 28, the further input openings 29 and the further output openings 30 are each arranged in alignment.
  • the first rotor plates 10 have corresponding passage openings 31 for the passage of the heat transfer medium.
  • first 10 and the second rotor plates 11 are circular in the direction of rotation of the axis of rotation 2.
  • Each of the first rotor plates 10 has several, for example 12, flow channels 12, which are identical and distributed at different angular positions over the first rotor plates 10.
  • a plurality of flow channels 12 can also be provided at each angular position, which are located next to one another Extend inlet opening 13 to outlet opening 14.
  • the flow channels 12 each have a plurality of circumferentially extending flow channel sections 21 in a radially inner region of the first rotor plate 10 and a plurality of circumferentially extending flow channel sections 17 in a radially outer region of the first rotor plate 10, each in loops at different radii R1 , R2, R3 are arranged to the axis of rotation 2.
  • the second rotor plates 11 have several, for example 12, inner flow channels 23 and several, for example 12, outer flow channels 24.
  • the inner flow channels 23 of the second rotor plates 11 each have a plurality of sections 24 running in the circumferential direction as an inner heat exchanger and a plurality of sections 26 running in the circumferential direction as an outer heat exchanger, which in addition to the flow channel sections 21 running in the circumferential direction in the radially inner region of the first rotor plate 10 or next to the flow channel sections 17 running in the circumferential direction in the radially outer region of the first rotor plate 10.
  • the working medium is compressed or expanded during heat transfer.
  • FIG. 4 A further embodiment is shown, for example using one of the first rotor plates 10, in which two adjacent flow channels 12 are arranged mirrored with respect to a plane of symmetry S spanned in the axial and radial directions.
  • the two adjacent flow channels 12 each share a common inlet opening 13 and a common outlet opening 14 for the working medium.
  • the flow channels of the second rotor plates 11 run congruently with the flow channels 12 of the first rotor plates 10 in the area of the heat transfer channels and are preferably flowed through in countercurrent.
  • FIG. 5 Fig. 6 and Fig. 7 A further embodiment is shown in each case, in which the working medium is compressed or expanded during heat transfer.
  • the working medium is compressed during the external heat transfer, preferably in order to achieve low temperature differences between the working medium and the heat transfer medium on the sink side at low spreads or at a substantially constant temperature of the heat transfer medium on the sink side. Furthermore, the working medium is expanded during the internal heat transfer in order to achieve a low temperature difference between the working medium and the heat transfer medium on the source side at low spreads or at a substantially constant temperature of the heat transfer medium on the source side. Low temperature differences between the working medium and the respective heat transfer medium lead to low exergy losses and high efficiency (COP) of the entire system. The prerequisite is that the respective heat transfer medium and the working medium are guided through the channels in the countercurrent principle.
  • the working medium is compressed during the external heat transfer, preferably in order to achieve low temperature differences between the working medium and the heat transfer medium on the sink side at low spreads or at a substantially constant temperature of the heat transfer medium on the sink side. Furthermore, the working medium is also compressed during the internal heat transfer in order to achieve a low temperature difference between the working medium and the heat transfer medium on the source side with high spreads of the heat transfer medium on the source side.
  • the respective heat transfer medium and the working medium are guided through the channels in the countercurrent principle.
  • the working medium is expanded in order to achieve low temperature differences between the working medium and the heat transfer medium on the sink side with high spreads of the heat transfer medium on the sink side. Furthermore, the working medium is compressed during the internal heat transfer in order to achieve high spreads of the Heat transfer medium on the source side in turn to achieve a low temperature difference between the working medium and the heat transfer medium on the source side.
  • the respective heat transfer medium and the working medium are guided through the channels in the countercurrent principle.
  • FIG. 8 A further embodiment is shown in which no intermediate compression or intermediate expansion of the working medium takes place.
  • the working medium flows through only one flow channel section 21 running in the circumferential direction in the radially inner region of the first rotor plate 10 per flow channel 12, ie not as in Fig. 2A , Fig. 2B and Fig. 3 several flow sections 21 connected to one another in loops.
  • the working medium in the radially outer region of the first rotor plate 10 flows through only one flow channel section 17 running in the circumferential direction per flow channel 12, ie not as in Fig. 2A , Fig. 2B and Fig. 3 several flow channel sections 17 connected to one another in loops.
  • FIG. 9 A further embodiment is shown, in which the first rotor plates 10 and/or the second rotor plates 11 each have at least one recess 33.
  • the recesses 33 can be arranged in such a way that heat transfer between the flows of the working medium in flow channels 12 at different angular positions of the respective first rotor plate 10 is reduced, in particular essentially prevented. Furthermore, the heat transfer of the heat transfer media in the flow channels of the second rotor plates 11 to adjacent channels can be reduced, in particular essentially prevented, with the recesses 33. Furthermore, the recesses 33 can be arranged so that the heat transfer between the working medium and the heat transfer medium can essentially only take place at those points where the heat transfer is desired.
  • Fig. 10A shows a first embodiment variant, in which the first 10 and the second rotor plates 11 are out of round when viewed in the direction of rotation axis 2, here essentially rectangular, are.
  • the two shorter sides of the first 10 and second rotor plates 11 are curved and the two longer sides of the first 10 and second rotor plates 11 are straight.
  • Fig 10B and Fig. 10C show another essentially rectangular design of the rotor element.
  • Fig. 10B one of the first rotor plates 10 is shown, the channels of the adjacent second rotor plate 11 being shown in dashed lines.
  • Fig. 10C the second rotor plate 11 is shown. This version results in the following differences from the exemplary embodiments described above.
  • the first rotor plate 10 in this embodiment has several, preferably between 10 and 200, preferably essentially parallel flow channels 12 for the working medium, which extend between the inlet openings 13 and at least one outlet opening 14, here a common outlet opening 14.
  • the flow channels 12 each have one of the compression channels 15 leading away from the axis of rotation 2 to the outside, an outer one of the first heat transfer channels 18, an expansion channel 20 and an inner one of the first heat transfer channels 18.
  • the first heat transfer channels 18 for forming the outer heat exchanger and the first heat transfer channels 18 for forming the inner heat exchanger are each arranged at different distances from the axis of rotation 2.
  • the first heat transfer channels 18 on the outside are each connected to the corresponding first heat transfer channels 18 on the inside, so that the differences in the distances from the axis of rotation 2 are essentially the same.
  • the innermost channel of the parallel, essentially circumferentially leading first heat transfer channels 18 of the internal heat transfer is also connected to the innermost channel of the parallel, essentially in Circumferentially leading first heat transfer channels 18 of the external heat transfer are connected.
  • the two radii of the connected inner and outer heat transfer channels 18 are designed so that the temperature difference between the inner and outer heat transfer channels is essentially the same in all parallel channels. This enables essentially the same temperature curves and constant heat transfer performance in all parallel heat transfer channels, which means that exergy losses are kept low and there is no preferential flow due to increased or reduced pressure differences.
  • Fig. 10A This is shown using the external heat transfer, in which the working medium in each of the parallel channels is compressed during the heat exchange in such a way that a constant temperature is established in this channel.
  • the temperature spread for the cross-flowing heat transfer medium can be adjusted via the number and radius difference in the heat transfer area of the parallel channels. Due to the high number of parallel channels (with the same radial extent as in the versions with loops described above) and the comparatively short channel length, the pressure loss is reduced compared to the other versions. The same effect can be achieved in the area of internal heat transfer if each of the parallel inner channels is expanded during the heat exchange with the heat transfer medium via a radius reduction in the flow direction in such a way that the temperature within a channel is kept constant.
  • Fig. 11 and Fig. 12 is a part of the rotor element 4 according to the embodiment Fig. 2A , Fig. 2B and Fig. 3 shown in greater detail. Accordingly, several flow channel sections 21 extending essentially in the circumferential direction extend next to each other, six in the example shown radially inner region, substantially circumferentially extending flow channel sections 17 in the radially outer region of the first rotor plates 10, substantially circumferentially extending sections 24 of the inner heat exchanger and substantially circumferentially extending sections 26 of the outer heat exchanger of the second rotor plates 11. Furthermore, in the Fig. 9 and Fig. 10 an end plate 34 without channels can be seen.
  • the flow channels 12 of the first rotor plates 10 and the second heat transfer channels 22 of the second rotor plates 11 are each designed as depressions 35, which sink in relation to the flat outer or connecting surfaces 36 of the first 10 and second rotor plates 11.
  • the closed channels for the working or heat transfer medium are formed.
  • the first rotor plates 10 and the second rotor plates 11 can be connected to one another via diffusion connections. These compounds are, for example, in the EP 3 885 691 described.
  • the first rotor plates 10 not only have the compression channels 15, the expansion channels 20 and the first heat transfer channels 18 for the working medium, but also the second heat transfer channels 22 for the heat transfer medium.
  • the first rotor plates 10 have on their first outer surfaces 36A the depressions 35 for forming the compression channels 15, the expansion channels 20 and the first heat transfer channels 18 for the working medium and on their second outer surfaces 36B depressions 35 for forming the second heat transfer channels 22 for the heat transfer medium on.
  • the second rotor plates 11 are separating plates between the first rotor plates 10, free of the recesses 35 arranged to close the depressions 35 of the first rotor plates 10 in order to form the flow channels 12 and the second heat transfer channels 22.

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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)
EP22195656.8A 2022-09-14 2022-09-14 Rotor Pending EP4339534A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP22195656.8A EP4339534A1 (fr) 2022-09-14 2022-09-14 Rotor
PCT/EP2023/075263 WO2024056788A1 (fr) 2022-09-14 2023-09-14 Rotor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP22195656.8A EP4339534A1 (fr) 2022-09-14 2022-09-14 Rotor

Publications (1)

Publication Number Publication Date
EP4339534A1 true EP4339534A1 (fr) 2024-03-20

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ID=83318960

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22195656.8A Pending EP4339534A1 (fr) 2022-09-14 2022-09-14 Rotor

Country Status (2)

Country Link
EP (1) EP4339534A1 (fr)
WO (1) WO2024056788A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3895491A (en) * 1973-10-11 1975-07-22 Michael Eskeli Turbine with dual rotors
US3937034A (en) * 1973-09-20 1976-02-10 Michael Eskeli Gas compressor-expander
WO2015103656A1 (fr) 2014-01-09 2015-07-16 Ecop Technologies Gmbh Dispositif de conversion d'une énergie thermique
EP3885691A1 (fr) 2018-11-22 2021-09-29 Sumitomo Precision Products Co., Ltd. Échangeur de chaleur lié par diffusion

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3937034A (en) * 1973-09-20 1976-02-10 Michael Eskeli Gas compressor-expander
US3895491A (en) * 1973-10-11 1975-07-22 Michael Eskeli Turbine with dual rotors
WO2015103656A1 (fr) 2014-01-09 2015-07-16 Ecop Technologies Gmbh Dispositif de conversion d'une énergie thermique
EP3885691A1 (fr) 2018-11-22 2021-09-29 Sumitomo Precision Products Co., Ltd. Échangeur de chaleur lié par diffusion

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Publication number Publication date
WO2024056788A1 (fr) 2024-03-21

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