Rotor

Abstract

The invention relates to a rotor (1), in particular a rotation heat pump, comprising: an axis of rotation (2); a number of compression channels (15), in which a working medium, in particular a gas, preferably a noble gas, is conducted away from the axis of rotation (2) as a result of the centrifugal acceleration for the purpose of increasing pressure; a number of expansion channels (20), in which the working medium is conducted toward the axis of rotation (2) as a result of the centrifugal acceleration for the purpose of decreasing pressure; a number of first heat transfer channels (18) for the working medium and a number of second heat transfer channels (22) for a heat transfer medium, in particular a liquid, so that heat is transferred between the working medium flowing in the first heat transfer channels (18) and the heat transfer medium flowing in the second heat transfer channels (22); a number of first (10) and second rotor plates (11), which comprise the compression channels (15), the expansion channels (20), the first heat transfer channels (18) for the working medium and the second heat transfer channels (22) for the heat transfer medium; wherein the first (10) and the second rotor plates (11) are connected to one another along their main planes of extension.

Description

[0001] rotor

[0002] The invention relates to a rotor, in particular a rotary heat pump, comprising: an axis of rotation, a number of compression channels in which a working medium, in particular a gas, preferably a noble gas, is guided away from the axis of rotation to increase the pressure due to the centrifugal force, a number of expansion channels in which the working medium is guided towards the axis of rotation to reduce the pressure due to the centrifugal force, a number of first heat transfer channels for the working medium and a number of second heat transfer channels for a heat transfer medium, in particular a liquid, so that heat is transferred between the working medium flowing in the first heat transfer channels and the heat transfer medium flowing in the second heat transfer channels.

[0003] From WO 2015 / 103656 a rotary heat pump is known in which the centrifugal acceleration of the rotor is used to generate different pressure and temperature levels. Heat at a high temperature is extracted from the compressed working medium and heat at a comparatively low temperature is added to the expanded working medium. For this purpose 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 internal heat exchangers are designed for heat exchange at a lower temperature and the external heat exchangers for heat exchange at a higher temperature. This type of rotary heat pump has significant advantages over stationary heat pumps. A disadvantage, however, is the high construction complexity of the known rotary heat pump.Furthermore, there is a need for improvement in rotor dynamics, which in the current state of the art is compromised 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).

[0004] The present invention therefore aims to alleviate or eliminate at least some of the disadvantages of the prior art. The invention preferably aims to create a rotor that combines low design complexity with high efficiency.

[0005] This object is achieved by a rotor according to claim 1 and a method according to claim 13. Preferred embodiments are specified in the dependent claims.

[0006] According to the invention, a number of 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, wherein the first and the second rotor plates are connected to one another along their main extension planes.

[0007] The arrangement of the first and second rotor plates forms a compact rotor element that is particularly stable with respect to rotational forces and combines the individual components of the prior art, such as internal and external heat exchangers and expansion and compression channels, with separate functions. To form the rotor element, the first and second rotor plates are stacked in contact with one another and connected to one another at their intersecting main extension planes. In the first and / or second rotor plates, the working medium flows through flow channels that 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.So-called “micro channel diffusion bonded heat exchangers” were already known in the prior art (cf., for example, EP 3 885 691 A1), in which a stack of heat exchanger plates with integrated flow passages are connected to one another by diffusion bonds. The invention not only replaces the inner and outer heat exchangers of known rotary heat pumps with this type of heat exchanger, but also integrates the expansion and compression channels into the first and second rotor plates of the rotor element. This means that not only the heat transfer between the working medium and the heat transfer medium takes place in the flow channels of the rotor element, but also the compression of the working medium as it flows away from the axis of rotation and the expansion of the working medium as it flows towards the axis of rotation.This makes it possible to create a rotor, in particular a rotary heat pump or a heat engine for providing electrical power from a heat flow, in which the essential process steps are integrated into the interior of the package comprising the first and second rotor plates. This design achieves particularly favorable rotor dynamics. It has been found to be particularly advantageous that the first and second rotor plates can virtually not move against one another, so that the number of balancing runs can be significantly reduced or balancing runs can be avoided altogether. Furthermore, the rotor element can be made from the first and second rotor elements in different designs, in particular with smaller dimensions. This has the advantage that production can be simplified and a less powerful drive machine can be used.Compared to discrete heat exchangers in the state of the art, the available heat exchanger surfaces can be increased during rotor operation. The integral design of the rotor element also allows the number of sealing points to be significantly reduced.

[0008] For the purposes of this disclosure, the location and direction specifications refer to the intended use of the rotor, where "radial", "axial" and "in the circumferential direction" refer to the axis of rotation. With regard to the flow of the working or heat transfer medium, "inside" means closer to the axis of rotation of the rotor and "outside" means further away from the axis of rotation. In a preferred embodiment, the main extension planes of the first and second rotor plates, i.e. their plate planes in which the first and second rotor plates each have their greatest extent, are each arranged substantially perpendicular to the axis of rotation. The axis of rotation preferably passes through the centers of the first and second axes of rotation. Furthermore, it is advantageous if the first and second rotor plates are arranged substantially congruently when viewed in the direction of the axis of rotation.

[0009] In a preferred embodiment, 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.

[0010] In a preferred embodiment, the first rotor plates each have at least one flow channel for the working medium, wherein the at least one flow channel has an inlet opening for the working medium at a first end and an outlet opening for the working medium at a second end. In a preferred embodiment, the flow channel has a flow channel section that preferably runs essentially radially outwards for forming one of the compression channels and / or a flow channel section that preferably runs essentially radially inwards for forming one of the expansion channels and / or a flow channel section that preferably runs essentially in the circumferential direction for forming 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, where the working medium is led out of the rotor element. In the outward-leading flow channel section, the working medium can be compressed by the effect of centrifugal acceleration when the rotor is rotating. In the inward-leading flow channel section, the working medium can be expanded, also due to centrifugal force. Heat can be transferred between the working medium and the heat transfer medium in the flow channel cross-section, which 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.

[0011] In a preferred embodiment, the inlet openings and / or the outlet openings of the first rotor plates are each aligned, i.e., arranged in a line parallel to the rotation axis. Preferably, the inlet openings and / or the outlet openings are each congruent, viewed in the direction parallel to the rotation axis.

[0012] To enable the passage of the working medium through the second rotor plates, the second rotor plates in this embodiment preferably each have through-openings arranged in alignment with the inlet openings and in alignment with the outlet openings. Thus, the working medium can be supplied on one side of the rotor element and distributed to the first rotor plates via the inlet openings, with second rotor plates arranged therebetween being passed through the through-openings.

[0013] In order to keep the number of connections as low as possible, the outlet openings in a preferred embodiment 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 discharged from the first rotor plates via the outlet openings, which are preferably arranged in alignment. Advantageously, several flow channels of the first rotor plate can share the same outlet opening in the central region. To maintain the flow of the working medium, a fan is preferably provided. The fan is preferably arranged in the axial direction outside the rotor element comprising the first and second rotor plates.With the help of the fan, a circular flow of the working medium can be achieved 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 allows the working medium to undergo a cyclic process. Depending on the arrangement of the flow channels in the first rotor plates, various types of cyclic processes can be achieved, for example, a Joule process with essentially isobaric heat transfer.

[0014] Depending on the design, the fan can be connected to a fan drive, which can be used to rotate a fan impeller. The fan drive can rotate the impeller relative to the rotor element, which is preferably driven by a motor separate from the fan drive.

[0015] To achieve the circular flow of the working medium, 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.

[0016] In order to improve the heat transfer between the working medium and the heat transfer medium, in a preferred embodiment the first rotor plates each have a plurality of flow channels, each with at least one flow channel section that preferably runs essentially radially outwards and / or with at least one flow channel section that preferably runs essentially radially inwards and / or with at least one flow channel section that preferably runs essentially in the circumferential direction. Thus, a plurality of flow channels can be formed on each of the first rotor plates, through which the working medium can flow in parallel. The flow channels can be distributed over the surface of the first rotor plate. Preferably, more than three, in particular more than six, for example twelve, flow channels are provided at different angular positions per first rotor plate.

[0017] In a preferred embodiment, the flow channels of the first rotor plates each have a plurality of flow channel sections, preferably running essentially in the circumferential direction, at different radial distances from the axis of rotation to form a plurality of first heat transfer channels. The flow channel sections running in the circumferential direction are preferably arranged in loops. Preferably, a plurality of inner, for example S-shaped, loops for heat exchange with the heat transfer medium are provided 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 are provided in outer loops of one of the second heat transfer channels of one of the second rotor plates. In this embodiment, intermediate compression or expansion can be brought about during the heat exchange with the heat transfer medium.This makes it possible to raise the temperature again after heat transfer, either to transfer the heat at an essentially 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.

[0018] To reduce the number of necessary connections for the working medium, in a preferred embodiment, two adjacent flow channels of the first rotor plates are arranged mirror-symmetrically with respect to a plane of symmetry spanned in the axial and radial directions, with the two adjacent flow channels sharing a common inlet and a common outlet opening for the working medium. If, for example, 12 flow channels are provided at different angular positions per first rotor plate, only six connections are required for the inlet of the working medium in this embodiment.

[0019] In a preferred embodiment, the second rotor plates each have at least one inner flow channel and at least one outer flow channel, each for forming one of the second heat transfer channels, wherein the outer flow channel is arranged further outwards in the radial direction than the inner flow channel. When used as a rotary heat pump, 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, transfers heat to the working medium. Alternatively, the rotor can be designed as a heat engine.

[0020] In a further embodiment, the first rotor plates have the second heat transfer channels for the heat transfer medium. In this embodiment, the second rotor plates can be designed as separating plates for the first rotor plates, wherein the second separating plates are preferably free of flow channels for both the working medium and the heat transfer medium.

[0021] For the integral formation of the individual flow channels, it is advantageous if the compression channels, the expansion channels and the first heat transfer channels for the working medium are designed as depressions starting from preferably essentially planar first outer surfaces of the first rotor plates, wherein the second heat transfer channels for the heat transfer medium are designed i . as depressions starting from preferably essentially planar outer surfaces of the second rotor plates or ii . as depressions starting from preferably essentially planar second outer surfaces of the first rotor plates. The first and the second rotor plates preferably have essentially planar outer surfaces parallel to their main extension planes. In the first embodiment variant, the working medium flows in the depressions of the first rotor plates, wherein the heat transfer medium flows in the depressions of the second rotor plates.By connecting the first and second rotor plates along their main extension surfaces, the recesses of the first rotor plate and the adjacent outer surfaces of the second rotor plates form closed-section flow channels. In the second embodiment, the working medium and the heat transfer medium each flow in separate recesses of the first rotor plates, which are formed on the opposite first and second outer surfaces of the first rotor plates. These recesses, together with the adjacent outer surfaces of the second rotor plates, form closed-section flow channels for the working medium and the heat transfer medium.

[0022] In a preferred embodiment, the first rotor plates and the second rotor plates are connected to one another via diffusion bonds, ie by diffusion bonding.

[0023] Depending on the design, preferably at least 50, in particular at least 200, for example from 300 to 800, first rotor plates and / or at least 50, in particular at least 200, for example from 300 to 800, second rotor plates are 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, of 0.2 mm to 5 mm, in particular from 0.5 mm to 4 mm, for example from 2 mm to 3 mm. The flow channels can have a width, i.e. an extension 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, ie 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.In a first preferred embodiment, the first and second rotor plates are each circular in plan view, i.e., viewed in the axial direction. In this embodiment, the heat transfer surfaces can be optimized for a given length, i.e., axial extent, of the rotor element comprising the first and second rotor plates.

[0024] In a second preferred embodiment, the first and second rotor plates are each non-circular, i.e., non-circular, in particular substantially rectangular, when viewed in the direction of the rotation axis. This design can be advantageous when manufacturing the rotor element by diffusion bonding of the first and second rotor plates, since rectangular vacuum presses can be used for diffusion bonding. Advantageously, this allows the manufacturing process to be optimized; moreover, larger radial extensions can be achieved.

[0025] For heat transfer between the working medium and the heat transfer medium, 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 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 one another. If 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 one another on the first rotor plates.

[0026] In a preferred embodiment, the first rotor plates and / or the second rotor plates each have at least one recess. This allows, on the one hand, a weight saving to be achieved. Furthermore, insulation can be achieved in regions where undesired heat transfer is to be minimized. Thus, the recess can, for example, form an insulation region 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.

[0027] In a preferred embodiment, the first and second rotor plates are formed from a material selected from austenite, duplex steel, copper, titanium and aluminum.

[0028] The invention further relates to a method for heat transfer between a working medium, in particular a noble gas, and a heat transfer medium, in particular a liquid, comprising the steps:

[0029] Providing a rotor in one of the embodiments described above, feeding the working medium into the rotor, feeding the heat transfer medium into the rotor, and rotating the rotor about the axis of rotation.

[0030] The method according to the invention for producing a rotor, in particular a rotary heat pump, comprises at least the following steps:

[0031] Provision of first rotor plates,

[0032] Provision of second rotor plates,

[0033] Forming compression channels, expansion channels, first heat transfer channels for a working medium and second heat transfer channels for a heat transfer medium in the first and / or in the second rotor plates, stacking the first and second rotor plates,

[0034] Connecting the first rotor plates to the second rotor plates along their main extension planes, and

[0035] Rotary bearing of a rotor element formed from the first and second rotor plates about a rotation axis.

[0036] If the flow channels for the working medium are to be formed in the first rotor plates and the second heat transfer channels for the heat transfer medium are to be formed in the second rotor plates, the method for producing the rotor, in particular a rotary heat pump, preferably comprises at least the following steps:

[0037] Providing the first rotor plates,

[0038] Providing the second rotor plates,

[0039] Formation of the compression channels, expansion channels and first heat transfer channels for the working medium in the first rotor plates,

[0040] Forming the second heat transfer channels for the heat transfer medium in the second rotor plates,

[0041] Stacking the first and second rotor plates, connecting the first rotor plates to the second rotor plates along their main extension planes, and

[0042] Rotary bearing of the rotor element formed from the first and second rotor plates about the rotation axis.

[0043] If the flow channels for the working medium and the second heat transfer channels for the heat transfer medium are to be formed in the first rotor plates, the method for producing the rotor, in particular of a rotary heat pump, preferably comprises at least the following steps:

[0044] Providing the first rotor plates,

[0045] Providing the second rotor plates,

[0046] Forming the compression channels, the expansion channels and the first heat transfer channels for the working medium in the first rotor plates, preferably as depressions of first outer surfaces of the first rotor plates,

[0047] Forming the second heat transfer channels for the heat transfer medium in the first rotor plates, preferably as recesses of second outer surfaces of the first rotor plates,

[0048] Stacking the first and second rotor plates, connecting the first rotor plates to the second rotor plates along their main extension planes, and

[0049] Rotary bearing of the rotor element formed from the first and second rotor plates about the rotation axis.

[0050] In a preferred embodiment, the first rotor plates and the second rotor plates are joined together by diffusion bonding, in particular in a vacuum press.

[0051] The compression, the expansion, the first heat transfer channels and / or the second heat transfer channels are preferably formed by etching or milling in the first and / or second rotor plates.

[0052] The design of the rotor element comprising the first and second rotor plates enables application with high pressures. In a preferred embodiment, the maximum pressure of the working medium within the first rotor plates when the rotor is rotating is at least 80 bar, in particular at least 120 bar, for example, from 160 bar to 240 bar. These pressures advantageously result in lower pressure losses for the same mass flow and thus higher efficiency, which is determined by the "Coefficient of Performance" (COP) when the rotor is designed as a heat pump.

[0053] The invention is further explained below with reference to an embodiment shown in the drawings.

[0054] Fig. 1 shows a rotor according to the invention for use as a rotary heat pump.

[0055] Fig. 2A, Fig. 2B and Fig. 3 show views of a rotor element of the rotary heat pump according to Fig. 1, formed from first and second rotor plates.

[0056] Fig. 4 to 9 each show a further embodiment of parts of the rotor element.

[0057] Fig. 10A shows a first rectangular embodiment, Fig. 10B and Fig. 10C show a second rectangular embodiment.

[0058] Fig. 11 and Fig. 12 show a further embodiment of the rotor element, in which the working medium and the heat transfer medium are each guided in micro-channels of the first and second rotor plates, respectively.

[0059] Fig. 13 and Fig. 14 show a further embodiment of the rotor element, in which the working medium and the heat transfer medium are guided in channels of the first rotor plates, wherein the second rotor plates are arranged as separating plates between the first rotor plates.

[0060] 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. Depending on the embodiment, the rotor 1 can be accommodated in a stationary housing in which a negative pressure can prevail. The rotor 1 has an axis of rotation 2 which is preferably horizontal in the operating state and about which the rotor 1 is rotated with the aid of a motor 37. To form the axis of rotation 2, the rotor 1 has two pivot bearings 3. The rotor 1 has a rotor element 4 which is only symbolically shown in Fig. 1 and which is connected on one side to connections 5 for a heat transfer medium, in particular water, and on the other side to connections 6 for a working medium, for example a noble gas.Furthermore, a fan 7 is provided for maintaining 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, which is set in rotation by the motor 37. Furthermore, rotary unions 9 for the water connections 5 are visible in Fig. 1.

[0061] Fig. 2A, Fig. 2B and Fig. 3 schematically show an embodiment of the rotor element 4, which is constructed from a plurality of first rotor plates 10 and second rotor plates 11. For the sake of clarity, only two first rotor plates 10 and two second rotor plates 11 are shown in Fig. 2. In Fig. 3, the flow of the working medium is illustrated by solid lines and the flow of the heat transfer medium by dashed lines. The first rotor plates 10 and the second rotor plates 11 are connected to one another at their outer surfaces parallel to their main extension or plate planes (which are oriented vertically during operation). The first 10 and the second rotor plates 11 alternate with one another in the axial direction. In this embodiment, 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. In the embodiment shown, several adjacent flow channels 12 running parallel to one another are provided for each inlet opening 13, cf. detail B of Fig. 2B highlighted with a circle in Fig. 2A. The inlet openings 13 are connected to an outlet of the fan 7. The outlet openings 14 are connected to an inlet of the fan 7. In the example shown, the outlet openings 14 are arranged in the central regions of the first rotor plates 10 through which the rotation axis 2 passes.To form a compression channel 15, the flow channel 12 has a flow channel section 16 which leads essentially radially outwards and in which the working medium is guided away from the axis of rotation 2 to increase the pressure due to the centrifugal acceleration. The flow channel section 16 which leads essentially radially outwards is followed by at least one flow channel section 17 which runs essentially in the circumferential direction and forms a first heat transfer channel 18 for the heat exchange with the heat transfer medium. The circumferential flow channel section 17 is followed by a flow channel section 19 which leads essentially radially inwards and which, as an expansion channel 20, brings about a pressure reduction in the working medium due to the centrifugal acceleration.Adjoining the flow channel section 19, which leads essentially radially inward, is at least one further flow channel section 21, which extends essentially in the circumferential direction and 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.

[0062] In this embodiment, the second rotor plates 11 each have second heat transfer channels 22 through which the heat transfer medium flows. As second heat transfer channels 22, 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 for forming an inner heat exchanger and at least one outer flow channel 25 with a section 26 running in the circumferential direction for forming an outer heat exchanger. The outer flow channel 25 is arranged further outwards in the radial direction than the inner flow channel 23. The section 24 running in the circumferential direction of the inner heat exchanger of the second rotor plate 11 runs next to the flow channel section 21 running in the circumferential direction of the first rotor plate 10.The circumferentially extending section 26 of the outer heat exchanger of the second rotor plate 11 runs alongside 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 inlet of the heat transfer medium and an outlet opening 28 for the outlet of the heat transfer medium. Correspondingly, the outer flow channel 25 has a further inlet opening 29 for the inlet of the heat transfer medium and a further outlet opening 30 for the outlet of the heat transfer medium. The inlet openings 27, the outlet openings 28, the further inlet openings 29 and the further outlet 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.

[0063] In the embodiment of Fig. 2A, Fig. 2B and Fig. 3, the first 10 and the second rotor plates 11 are circular in the direction of the rotation axis 2. Each of the first rotor plates 10 has a plurality of, for example 12, flow channels 12, which are identically designed and distributed at different angular positions across the first rotor plates 10. As mentioned above, a plurality of flow channels 12 can also be provided at each angular position, which flow channels extend side by side from the inlet opening 13 to the outlet opening 14.In the embodiment shown, the flow channels 12 each have, in a radially inner region of the first rotor plate 10, a plurality of flow channel sections 21 running in the circumferential direction and, in a radially outer region of the first rotor plate 10, a plurality of flow channel sections 17 running in the circumferential direction, which are each arranged in loops at different radii RI, R2, R3 to the axis of rotation 2. Correspondingly, the second rotor plates 11 have a plurality of, for example, 12, inner flow channels 23 and a plurality of, for example, 12, outer flow channels 24.In the embodiment shown, the inner flow channels 23 of the second rotor plates 11 each have a plurality of circumferentially extending sections 24 as an inner heat exchanger and a plurality of circumferentially extending sections 26 as an outer heat exchanger, which run next to the circumferentially extending flow channel sections 21 in the radially inner region of the first rotor plate 10 or next to the circumferentially extending flow channel sections 17 in the radially outer region of the first rotor plate 10. In the embodiment of Fig. 2A, 2B and Fig. 3, the working medium is compressed or expanded during heat transfer.

[0064] Fig. 4 shows a further embodiment, using one of the first rotor plates 10 as an example, in which two adjacent flow channels 12 are arranged mirror-symmetrically with respect to a plane of symmetry S stretched 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. In this embodiment, the flow channels of the second rotor plates 11 run congruently with the flow channels 12 of the first rotor plates 10 in the region of the heat transfer channels and are preferably flowed through in countercurrent.

[0065] In Fig . 5 , Fig . 6 and Fig . 7 is each a further

[0066] An embodiment is shown in which the working medium is compressed or expanded during heat transfer.

[0067] According to Fig. 5, 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.

[0068] Furthermore, during internal heat transfer, the working medium expands in order to achieve a low temperature difference between the working medium and the heat transfer medium on the source side, with low spreads or an essentially 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 a high efficiency (COP) for the entire system. The prerequisite is that the respective heat transfer medium is guided through the channels with the working medium using the countercurrent principle.

[0069] According to Fig. 6, 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.

[0070] Furthermore, the working medium is compressed during internal heat transfer in order to achieve a low temperature difference between the working medium and the heat transfer medium on the source side, even with high temperature spreads of the heat transfer medium on the source side. The respective heat transfer medium and the working medium are guided through the channels according to the countercurrent principle.

[0071] According to Fig. 7, the working medium is expanded during external heat transfer in order to achieve low temperature differences between the working medium and the heat transfer medium on the sink side when the heat transfer medium has a high spread on the sink side. Furthermore, the working medium is compressed during internal heat transfer in order to achieve a low temperature difference between the working medium and the heat transfer medium on the source side when the heat transfer medium has a high spread on the source side. The respective heat transfer medium and the working medium are guided through the channels according to the countercurrent principle.

[0072] Fig. 8 shows a further embodiment in which no intermediate compression or expansion of the working medium takes place. For this purpose, in the radially inner region of the first rotor plate 10, the working medium flows through only one flow channel section 21 running in the circumferential direction per flow channel 12, i.e. not through a plurality of flow sections 21 connected to one another in loops as in Fig. 2A, Fig. 2B and Fig. 3. Accordingly, in the radially outer region of the first rotor plate 10, the working medium flows through only one flow channel section 17 running in the circumferential direction per flow channel 12, i.e. not through a plurality of flow channel sections 17 connected to one another in loops as in Fig. 2A, Fig. 2B and Fig. 3.

[0073] Fig. 9 shows a further embodiment 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 such 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 substantially prevented. Furthermore, the recesses 33 can be used to reduce, in particular substantially prevented, the heat transfer of the heat transfer media in the flow channels of the second rotor plates 11 at adjacent channels. Furthermore, the recesses 33 can be arranged such that heat transfer between the working medium and the heat transfer medium can take place essentially only at those points at which heat transfer is desired.

[0074] Fig. 10A shows a first embodiment variant in which the first 10 and the second rotor plates 11 are non-circular, here essentially rectangular, as viewed in the direction of the rotation axis 2. In the embodiment shown, the two shorter sides of the first 10 and the second rotor plates 11 are curved, and the two longer sides of the first 10 and the second rotor plates 11 are straight.

[0075] Fig. 10B and Fig. 10C show another substantially rectangular embodiment of the rotor element. Fig. 10B shows one of the first rotor plates 10, with the channels of the adjacent second rotor plate 11 shown in dashed lines. Fig. 10C shows the second rotor plate 11. This embodiment results in the following differences from the embodiments described above.

[0076] As can be seen from Fig. 10B, in this embodiment the first rotor plate 10 has a plurality of, preferably between 10 and 200, preferably substantially 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. For the sake of clarity, Fig. 10B shows seven flow channels 12 per quarter of the first rotor plate 10, i.e. a total of 28 flow channels 12. The flow channels 12 each have one of the compression channels 15 leading outwards away from the axis of rotation 2, 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 rotation axis 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 rotation axis 2 are essentially the same. Thus, for example, the innermost channel of the parallel, essentially circumferentially leading first heat transfer channels 18 of the inner heat transfer is also connected to the innermost channel of the parallel, essentially circumferentially leading first heat transfer channels 18 of the outer heat transfer.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 identical temperature profiles and constant heat transfer performance in all parallel heat transfer channels, thereby keeping exergy losses low and preventing preferential flow due to increased or decreased pressure difference.

[0077] Furthermore, in the embodiment of Fig. 10B, 10C the working medium flows transversely to the heat transfer medium in the heat transfer area, although low temperature differences (and thus low exergy losses) still occur. In Fig. 10A this is shown using the external heat transfer method, whereby the working medium in each of the parallel channels is compressed during heat exchange in such a way that a constant temperature is established in this channel. The temperature spread for the transversely 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 large number of parallel channels (with the same radial extension as in the designs with loops described above) and the comparatively short channel length, the pressure loss is reduced compared to the other designs.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.

[0078] In Fig. 11 and Fig. 12, part of the rotor element 4 of the embodiment according to Fig. 2A, Fig. 2B and Fig. 3 is shown in greater detail. Accordingly, several, in the example shown six, flow channel sections 21 extending essentially in the circumferential direction extend next to one another in the radially inner region, flow channel sections 17 extending essentially in the circumferential direction in the radially outer region of the first rotor plates 10, sections 24 of the inner heat exchanger extending essentially in the circumferential direction and sections 26 of the outer heat exchanger of the second rotor plates 11 extending essentially in the circumferential direction. Furthermore, an end plate 34 without channels can be seen in Fig. 9 and Fig. 10.

[0079] As Fig. 11 and Fig. 12 show, 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 are sunk relative to the flat outer or connecting surfaces 36 of the first 10 and second rotor plates 11. By stacking 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 connections are described, for example, in EP 3 885 691.

[0080] Fig. 13 and the detailed view of Fig. 14 marked with a rectangle in Fig. 13 show a further embodiment of the rotor, only the differences from the previous embodiments being discussed below. In the embodiment of Fig. 13 and Fig. 14, 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. For this purpose, 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. The second rotor plates 11 are designed as from the recesses

[0081] 35 free separating plates are arranged between the first rotor plates 10 in order to close off the recesses 35 of the first rotor plates 10 in order to form the flow channels 12 and the second heat transfer channels 22.

[0082] Reference number for the long-distance list:

[0083] 1 rotor

[0084] 2 rotation axis

[0085] 3 pivot bearings

[0086] 4 Rotor element

[0087] 5 water connections

[0088] 6 gas connections

[0089] 7 Fan

[0090] 8 Fan drive

[0091] 9 rotary unions

[0092] 10 first rotor plates

[0093] 11 second rotor plates

[0094] 12 flow channels of the first rotor plates 10

[0095] 13 Inlet openings of the flow channels 12

[0096] 14 Outlet openings of the flow channels 12

[0097] 15 compression channel

[0098] 16 radially outward flow channel section

[0099] 17 circumferential flow channel section

[0100] 18 first heat transfer channel

[0101] 19 radially inward flow channel section

[0102] 20 relaxation channel

[0103] 21 circumferential flow channel sections

[0104] 22 second heat transfer channels

[0105] 23 inner flow channels of the second rotor plates 11

[0106] 24 circumferential sections of the inner flow channels 23

[0107] 25 outer flow channels of the second rotor plates 11

[0108] 26 circumferential sections of the outer flow channels 25

[0109] 27 entrance openings

[0110] 28 exit openings

[0111] 29 additional entrance openings

[0112] 30 additional exit openings

[0113] 31 passage openings of the first rotor plates 10

[0114] 32 through holes of the second rotor plates 11

[0115] 33 recesses

[0116] 34 End plate

[0117] 35 Recesses 36 External or connecting surfaces

[0118] 37 Engine

Claims

Claims:

1. Rotor (1), in particular a rotary heat pump, comprising: a rotational axis (2), a number of compression channels (15) in which a working medium, in particular a gas, preferably a noble gas, is guided away from the rotational axis (2) to increase the pressure due to centrifugal acceleration, a number of expansion channels (20) in which the working medium is guided towards the rotational axis (2) to reduce the pressure due to centrifugal acceleration, a number of first heat transfer channels (18) for the working medium and a number of second heat transfer channels (22) for a heat transfer medium, in particular a liquid, so that heat is transferred between the working medium flowing in the first heat transfer channels (18) and the heat transfer medium flowing in the second heat transfer channels (22), characterized by a number of first (10) and second rotor plates (11) which form the compression channels (15),the expansion channels (20), the first heat transfer channels (18) for the working medium and the second heat transfer channels (22) for the heat transfer medium, wherein the first (10) and the second rotor plates (11) are connected to one another along their main extension planes., 2. Rotor (1) according to claim 1, characterized in that the number of first rotor plates (10) each have at least one of the compression channels (15), at least one of the expansion channels (20) and at least one of the first heat transfer channels (18) for the working medium and the number of second rotor plates (11) each have at least one of the second heat transfer channels (22) for the heat transfer medium.

3. Rotor (1) according to claim 2, characterized in that the first rotor plates (10) each have at least one flow channel (12) with a preferably substantially radially outwardly extending flow channel section (16) for forming one of the compression channels (15) and / or with a preferably substantially radially inwardly extending flow channel section (19) for forming one of the expansion channels (20) and / or with a preferably substantially circumferentially extending flow channel section (17, 21) for forming one of the first heat transfer channels (18), wherein the at least one flow channel (12) has an inlet opening (13) for the working medium at a first end and an outlet opening (14) for the working medium at a second end.

4. Rotor (1) according to one of claims 1 to 3, characterized in that a fan (7) is provided to maintain the flow of the working medium, wherein preferably the inlet openings (13) are connected to an outlet of the fan (7) and / or the outlet openings (14) are connected to an inlet of the fan (7).

5. Rotor (1) according to one of claims 2 to 4, characterized in that the first rotor plates (10) each have a plurality of flow channels (12), each with at least one flow channel section (16) extending preferably substantially radially outwards and / or with at least one flow channel section (19) extending preferably substantially radially inwards and / or with at least one flow channel section (17, 21) extending preferably substantially in the circumferential direction.

6. Rotor (1) according to claim 5, characterized in that the flow channels (12) of the first rotor plates (10) each have a plurality of flow channel sections (17, 21) extending preferably substantially in the circumferential direction in different radial distances from the axis of rotation (2).

7. Rotor (1) according to claim 5 or 6, characterized in that two adjacent flow channels (12) of the first rotor plates (10) are arranged mirrored with respect to a plane of symmetry stretched in the axial and radial directions, wherein the two adjacent flow channels (12) share a common inlet (13) and a common outlet opening (14) for the working medium.

8. Rotor (1) according to one of claims 1 to 7, characterized in that the second rotor plates (11) each have at least one inner flow channel (23) and at least one outer flow channel (25) each for forming one of the second heat transfer channels (22), wherein the outer flow channel (25) is arranged further outward in the radial direction than the inner flow channel (23).

9. Rotor (1) according to one of claims 1 to 7, characterized in that the first rotor plates (10) have the second heat transfer channels (22) for the heat transfer medium.

10. Rotor (1) according to one of claims 1 to 9, characterized in that the compression channels (15), the expansion channels (20) and the first heat transfer channels (18) for the working medium are designed as depressions (35) starting from preferably substantially planar first outer surfaces (36A) of the first rotor plates (10), wherein the second heat transfer channels (22) for the heat transfer medium are designed i. as depressions (35) starting from preferably substantially planar outer surfaces (36) of the second rotor plates (11) or ii. as depressions (35) starting from preferably substantially planar second outer surfaces (36B) of the first rotor plates (10).

11. Rotor (1) according to one of claims 1 to 10, characterized in that the first rotor plates (10) and the second rotor plates (11) are connected to each other via diffusion connections.

12. Rotor (1) according to one of claims 1 to 11, characterized in that the first (10) and the second rotor plates (11) are each substantially circular or non-circular, in particular substantially rectangular.

13. Method for producing a rotor (1), in particular a rotary heat pump, comprising the steps: Providing first rotor plates (10), providing second rotor plates (11), forming compression channels (15), expansion channels (20), first heat transfer channels (18) for a working medium and second heat transfer channels (22) for a heat transfer medium in the first (10) and / or in the second rotor plates (11), Stacking the first (10) and second rotor plates (11), connecting the first rotor plates (10) to the second rotor plates (11) along their main extension planes, and pivotally supporting a rotor element (4) formed from the first (10) and the second rotor plates (11) about a rotation axis (2).

14. The method according to claim 13, characterized in that the first rotor plates (10) and the second rotor plates (11) are connected to one another by diffusion bonding.

15. Method according to claim 13 or 14, characterized in that the compression (15), the expansion (20), the first heat transfer channels (18) and / or the second heat transfer channels (22) are preferably formed by etching or milling in the first and / or in the second rotor plates (11).

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