System for providing power from heat

Abstract

A system for providing mechanical and / or electric power from heat power. A heat medium is arranged in a flow circuit comprising: a condensation channel, a pump channel, an evaporation channel and a turbine channel, substantially in a Rankine cycle. Heating power is provided for evaporation of the heat medium and cooling power is provided for condensation of the heat medium. The pump channel is arranged in the liquid phase portion and a turbine device is arranged in the gas phase portion. The pump channel generates a pressure due to the rotation. The turbine channel comprises a turbine device. The flow circuit is closed so that no heat medium may escape to the surroundings.

Description

[0001] TITLE: SYSTEM FOR PROVIDING POWER FROM HEAT

[0002] FIELD OF INVENTION

[0003] The present invention relates to a system for producing mechanical or electrical power from heat power and for providing a heat pump, for example using the Rankine cycle.

[0004] BACKGROUND

[0005] The Rankine cycle is used for producing mechanical or electrical power from heat power, see for example US9494056B2. However, such machines for using the Rankine cycle tends to be very large and cannot easily be adapted for different conditions.

[0006] Thus, there is a need for a Rankine cycle machine with small dimensions and which is versatile.

[0007] SUMMARY OF THE INVENTION

[0008] Accordingly, an object of the present invention is to mitigate, alleviate or eliminate one or more of the above-identified and below mentioned or other deficiencies and disadvantages singly or in any combination.

[0009] In a first aspect, there is provided a system for providing mechanical and / or electric power from heat power, comprising: a cooling path for cooling a heat medium in the cooling path by a cooling power source for condensing the heat medium; a heating path for heating heat medium by a heating power source for evaporate the heat medium; a pressurizing path for increasing pressure in heat medium of the heating path relative to heat medium of the cooling path, wherein the heat medium in the pressurizing path is in a liquid state; a power path for deriving mechanical power from heat medium from the heating path to the cooling path, wherein the heat medium in the power path is in a gaseous state; said cooling path, pressurizing path, heating path and power path being connected in a circulation circuit comprising the heat medium circulating in the circuit, wherein the circulation circuit is arranged in a closed body, so that no heat medium is able to escape from the closed body; wherein the pressurizing path and at least a part of the heating path and at least a part of the cooling path being arranged in a first rotating body, which rotates at a first rotation rate around a rotational axis for generating pressures in the heat medium by centripetal forces; and wherein the power path comprises turbine channels, which are arranged in a second rotating body, which rotates at a second rotation rate around the rotational axis.

[0010] The second rotation rate may be smaller than the first rotation rate, for example by braking the rotation of the second rotating body, such as by a generator. The rotation of the second body may be in a direction opposite relative to the rotation of the first body. The second rotate rate may be substantially zero, for example by maintaining the second rotating body still in relation to the rotational axis so that it does not rotate.

[0011] According to an embodiment, the heating path comprises an evaporation channel, which extends from an outlet of the pressurizing channel to an inlet of the turbine channels, wherein the evaporation channel comprises: a first portion adjacent the outlet of the pressurizing channel, in which the heat medium is in a liquid phase, a second portion in which the heat medium is in a mixed gaseous and liquid phase, and a third portion in which the heat medium is in a gaseous phase. The evaporation channel may be inclined so that there is a first distance from the rotational axis adjacent an outlet from the pressurizing channel and there is a second distance from the rotational axis adjacent an inlet to the power path, whereby the first distance is larger than the second distance.

[0012] In another embodiment, the cooling path comprises a condensation channel, which extends from an outlet of the power path to an inlet of the pressurizing path, wherein the condensation channel comprises: a first portion adjacent the outlet of the power path, in which the heat medium is in a gaseous phase, a second portion in which the heat medium is in a mixed gaseous and liquid phase, and a third portion in which the heat medium is in a liquid phase, adjacent an inlet to the pressurizing path. The condensation channel may be inclined so that there is a third distance from the rotational axis adjacent an outlet of the power path and there is a fourth distance from the rotational axis adjacent an inlet to the pressurizing path, whereby the fourth distance is larger than the third distance.

[0013] In a further embodiment, the first rotating body performs a transformation of the heat medium, initially in a gas phase at low pressure and low temperature, to a heat medium eventually in gas phase at high pressure and high temperature. The transformation may take place by converting the heat medium, initially in a gas phase at low pressure and low temperature, to a liquid phase by condensing the heat medium by removing heat energy from the heat medium, to a high pressure by exposing the liquid heat medium for centrifugal forces in the pressurizing path, to a high temperature by evaporating the heat medium by supplying heat energy to the heat medium.

[0014] In still another embodiment, the first rotating body may comprise a plurality of evaporation channels and a plurality of condensation channels, and wherein the second rotating body comprises a plurality of turbine channels, whereby heat medium is transferred from the first rotating body to the second rotating body and vice versa, via interfaces, which rotate in relation to each other.

[0015] In yet another embodiment, the second rotating body may be fully enclosed in the first rotating body. The second rotating body may be arranged in a circular recess of the first rotating body.

[0016] In a still further embodiment, the system may be operated as a heat pump, in which the pressurizing path comprises a compressor device in a rotating body, which is driven by mechanical power, and the power path comprising an expanding device in another rotating body. The system may be operated as a heat pump, in which the power part is replaced by a compressor device and the pressurizing part is replaced by an expanding device.

[0017] In a yet further embodiment, the rotation of the first body may be driven by the second body. The second body may rotate at a second rotation rate and the first body may rotate at a first rotation rate and the ratio between the first rotation rate and the second rotation rate may be constant. A mechanical gear device may be arranged between the first rotation body and the second rotation body, wherein the gear device has fixed ratio of for example 1:3, 1:5, 1:10, 1:50, 1:100, 1:200, 1:500, 1:1000 or even larger, between the second rotation rate and the first rotation rate. The first rotation rate is in a direction opposite the second rotation rate.

[0018] The circulation circuit of the heat medium may be arranged according to a Rankine cycle.

[0019] BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Further objects, features and advantages of the invention will become apparent from the following detailed description of embodiments of the invention with reference to the drawings, in which:

[0021] Fig. l is a schematic diagram of a Rankine cycle.

[0022] Fig. 2 is a general diagram showing enthalpy h at the x-axis and pressure at the y-axis and is used for explaining a Rankine cycle or other thermodynamic conditions.

[0023] Fig. 3 is a diagram similar to Fig. 2 and discloses a first Rankine cycle.

[0024] Fig. 4 is a diagram similar to Fig. 3 and discloses a second Rankine cycle.

[0025] Fig. 5 is a perspective view showing a first transformer according to a first embodiment of the invention.

[0026] Fig. 6 is a partially cut cross-sectional view in perspective of the transformer embodiment according to Fig. 5.

[0027] Fig. 7 is a schematic view of a first embodiment of the invention.

[0028] Figs. 8 is a schematic view in perspective of a second embodiment of the invention. Fig. 9 is a schematic cross-sectional view of a turbine portion of a third embodiment, similar to the embodiment according to Fig. 7.

[0029] Fig. 10 is a schematic view in perspective of a fourth embodiment similar to the embodiment according to Fig. 7.

[0030] Fig. 1 la is a schematic view of a heat medium flow in a fifth embodiment.

[0031] Fig. 1 lb is a cross-section of a heat medium flow path in the fifth embodiment.

[0032] Figs. 12a, 12, b, 12c and 12d are perspective views of a second transformer according to a sixth embodiment and in successive cross-sections. Fig. 13 is an exploded view in cross-section and perspective of a third transformer according to a seventh embodiment.

[0033] Fig. 14a is a perspective schematic view of a further embodiment and shows a plurality of flow paths.

[0034] Fig. 14b is side view of the embodiment according to Fig. 14a.

[0035] Fig. 15 is a schematic cross-sectional view of a further embodiment of the transformer.

[0036] Fig 16 is a schematic view similar to Fig. 15.

[0037] Fig. 17 is a schematic view of a transformer explaining power flow.

[0038] Fig. 18 is a schematic view of a sector of a transformer showing flow paths for the heat medium.

[0039] Fig. 19 is a diagram similar to Fig. 4 and illustrating connection of several transformers or several different heat medium circuits.

[0040] Fig. 20 is a schematic view similar to Fig. 18 and showing several sectors.

[0041] Fig. 21 is a schematic view similar to Fig. 20 and showing several sectors.

[0042] Fig. 22 is a cross-sectional view through a portion of a fourth transformer similar to the third transformer according to Fig. 13.

[0043] Fig. 23 is a schematic view showing flow paths for the heat medium in an embodiment.

[0044] Fig. 24 is a diagram showing pressures, temperatures and densities for the heat medium in the embodiment according to Fig. 23.

[0045] Fig. 25 is a schematic view showing flow paths for the heat medium flowing in the opposite direction as shown in Fig. 23.

[0046] Fig. 26 is a diagram similar to Fig. 24 showing pressures, temperatures and densities for the heat medium in the embodiment according to Fig. 25.

[0047] Fig. 27 is a partially cut perspective view of a fourth transformer according to a further embodiment of the invention.

[0048] Fig. 28 is a schematic cross-sectional view of fifth transformer according to a further embodiment of the invention.

[0049] Fig. 29 is a diagram similar to Fig. 4 of a heat pump configuration.

[0050] Figs. 30a and 30 b are schematic views of a portion of the transformer showing interface angles.

[0051] Fig. 31 is a schematic view showing different rotation orientations besteen interfaces of a transformer or body of a transformer.

[0052] Fig. 32 is a schematic view showing division of channels in different interfaces. Fig. 33a is a schematic view of a transformer showing different interfaces.

[0053] Fig. 33b is an enlargement of the area encircled by circle 334 in Fig. 33a. Figs. 34a, 34b, 34c, 34d, 34e and 34f are schematic views showing embodiments of different enclosures.

[0054] Figs. 35a and 35b are schematic views of another embodiment comprising a turbine rotating around a separate axis.

[0055] Figs. 36 and 37 are a schematic partial view showing successive evaporation and condensation of a heat medium.

[0056] Fig. 38a is a cross-sectional view of a portion of an evaporator body according to a further embodiment.

[0057] Fig. 38b is an isometric view of the embodiment according to Fig. 38a.

[0058] Fig. 39a is is a cross-sectional view of a portion of an evaporator and condensation body according to a further embodiment.

[0059] Fig. 39b is an isometric view of the embodiment according to Fig. 39a.

[0060] Fig. 40a is a cross-sectional view of a portion of a turbine device according to the embodiment of Fig. 38a.

[0061] Fig. 40b is an isometric view of the embodiment of Fig. 401.

[0062] Fig. 40c is a partial plan view taken according to line C-C in Fig. 40a.

[0063] Fig. 40d is a partial side view taken according to line D-D in Fig. 40a.

[0064] Fig. 41a is a cross-sectional view similar to Fig. 39a showing critical positions during axis rotation.

[0065] Fig. 41b is a cross-sectional view showing balancing weights.

[0066] Fig. 41c is a cross-sectional view showing another embodiment of balancing weights. Fig. 42a is a schematic view illustration a use scenario of the system.

[0067] Fig. 42b is a schematic view illustration another use scenario of the system.

[0068] Fig. 43a is a schematic view showing an axis passing a support with a small distance. Fig. 43b is a schematic view showing an axis passing a support with a fixed sealing device.

[0069] Fig. 43c is a schematic view showing an axis passing a support with a flexible sealing device.

[0070] DETAILED DESCRIPTION OF EMBODIMENTS

[0071] Below, several embodiments of the invention will be described. These embodiments are described in illustrating purpose in order to enable a skilled person to carry out the invention and to disclose the best mode. However, such embodiments do not limit the scope of the invention. Moreover, certain combinations of features are shown and discussed.

[0072] However, other combinations of the different features are possible within the scope of the invention.

[0073] In the drawings, all reference numbers start with the number of the relevant figure. Thus, all reference numerals starting with “6” belongs to Fig. 6. As far as possible, the reference number of the same component appearing in different figures starts with the figure number and ends with a specific digit and letter.

[0074] Fig. l is a diagram of a Rankine-cycle.

[0075] At the top of Fig. 1, there is disclosed an evaporator Ila, which evaporates a heat medium. The evaporation is mediated by heating power provided by a heating source 1 lb.

[0076] The heat medium is enclosed in channels 12a, 12b, 12c and 12d. The channels form a closed circuit.

[0077] After evaporation into gas state in evaporator Ila, the heat medium is transferred to a turbine 13a via channel 12a. In the turbine, the heat medium is expanded and causes the turbine to rotate. The rotation movement can be used as mechanical energy or be used to drive a generator 13b to produce electric energy.

[0078] From the output from the turbine 13a, the heat medium in gas form is transferred to a condenser 14a via channel 12b. The cooling is mediated by cooling power from a cooling source 14b. The heat medium is cooled until it condense into a (partially) liquid state.

[0079] The condensed heat medium is transferred to a pump 15a via channel 12c. The pump drives the heat medium to the left in the channel 12c while increasing the pressure. The pump 15a is driven by a power unit 15b.

[0080] The pump transfers the heat medium to an evaporator Ila via channel 12d for evaporation into gas form.

[0081] The power produced at the turbine 13a or generator 13b is larger than the power 15b required to drive the pump 15a.

[0082] The Rankine cycle can also be used as a heat pump, for example a common refrigerator. In this case, the turbine is replace by a compressor and the pump is replaced by an expansion valve.

[0083] The heat medium is tailored according to the heating and cooling sources. One example is water / steam or ammonia. Another example is Freon (or replacement fluids) previously used in a heat pump. The organic Rankine cycle (OCR) uses an organic fluid, such as n-pentane or toulene.

[0084] Other examples are: mono-ethylene-glucol, propyl en-glucol, silicone-oil, synthetic and aromatic heat transfer fluids, molten salts, vegetable oils. Further examples are: CFC (ChloroFluoroCarbons), HCFC (HydroChloroFluoroCarbons, HFC (HydroFluoroCarbons), Carbon Dioxide.

[0085] Fig. 2 is a pressure-enthalpy diagram of a heat medium. Such a pressure-enthalpy diagram is often used to explain thermo-dynamic processes. The diagram has enthalpy h in kJ / kg at the x-axis 21b and absolute pressure p in Pascal at the y-axis 21a. The diagram comprises a partially elliptic area encircled by lines 23a, 26, 23b and the x-axis. To the left of this area, the heat medium is in its liquid state and to the right of the area, the heat medium is in its gas state. Inside the area, the heat medium is in a state of mixed gas and liquid. A critical point 26 is indicated in which the heat medium can exists in both liquid and gas phase simultaneously.

[0086] The mixed area is constructed of lines or generatrices having constant gas quality, one such line being shown at 25 having approximately 80% gas and 20% liquid. Line 23b is consequently indicating 100% gas and line 23a is indicating 0% gas.

[0087] Line 24a indicates constant pressure, or iso-pressure.

[0088] Line 24b indicates constant temperature, or iso-temperature (temperature in °K). Line 24d indicates constant enthalpy, or iso-enthalpy (kJ / kg).

[0089] Lines 24d and 24e indicate constant entropy, or iso-entropy (kJ / kg°K).

[0090] Fig. 3 discloses a Rankine cycle in which the heat medium is never in its fully liquid state.

[0091] Fig. 4 discloses another Rankine cycle. An explanation of the diagram may start at point 41a in which the heat medium has been cooled and is in its liquid state at a low pressure. The heat medium enters a pump and the pressure is increased as indicated by line 42a, while there is no heat transfer to or from the heat medium, i.e. the process is adiabatic. The pressure increases to point 41b and the enthalpy increases as indicated by arrow 43a. The temperature may also increases slightly. The starting point 41a may be slightly to the left of the line 23a indicating 100% liquid as indicated by 41a’ or slightly to the right of the line 23 a indicating a large percentage of liquid, for example more than 95%, as indicated by point 41a”. A pump is often more efficient in pumping liquid compared to gas, and therefor, point 41a or point 41a’ are often preferred.

[0092] When the heat medium leaves the pump at point 41b it enters an evaporator 42b in which heating power is supplied to increase the temperature and evaporate the heat medium. The heat medium is heated, normally until it has passed into 100% gas state as indicated by point 41c. Often, additional heating power is supplied until the heat medium has passed further into the gas phase. The evaporation takes place at constant pressure and temperature. After the evaporation, to the right of line 23b, there is a slight expansion, which is not shown. The enthalpy increases as indicated by arrow 43b.

[0093] After the evaporation step 42b, the heat medium enters the turbine 42c in point 41c, in which the gaseous heat medium produces mechanical energy. At the same time, the pressure decreases and normally the temperature also decreases, while the heat medium is still in its gas phase. The enthalpy decreases as indicated by arrow 43c.

[0094] After the turbine at point 4 Id, the heat medium enters the condenser 42d and the heat medium is cooled until it returns to liquid state at point 41a. The pressure and temperature are substantially constant. The enthalpy decreases as indicated by arrow 43d.

[0095] The temperature during the evaporation stage is larger than the temperature during the condensation stage, since the evaporation temperature and the condensation temperature are dependent on the pressure. The mechanical power produced by turbine 42c is approximately proportional to the decrease in enthalpy 43c and the power consumed by the pump is approximately proportional to the increase in enthalpy 43a. As appears from Fig. 4, the mechanical power produced by turbine 42c is larger than the power consumed by the pump 42a. This surplus power may be used for driving the pump and the rest can be delivered by the system, for example to a generator for producing electric energy. The surplus mechanical power is provided by the heating power provided by the evaporator 42b minus the heating power removed by condenser 42d.

[0096] Fig. 3 discloses a Rankine cycle in which the gas is not fully condensed by the condenser but the pump operates on a mixture of gas and liquid. The turbine operates on gas only. At point 31a, there is a mixture of liquid and gas and a pump 32a increases the pressure until point 31b. The enthalpy increases as shown by arrow 33a. The heat medium is evaporated by evaporator 32b until in gas form at point 31c. The enthalpy increases as shown by arrow 33b. A turbine 32c decreases the pressure until point 3 Id. The enthalpy decreases as shown by arrow 33c. Finally, the heat medium is partially condensed by condenser 32d. The enthalpy decreases as shown by arrow 33d.

[0097] It is also possible to arrange the Rankine cycle entirely inside the mixed area or around the borderline between liquid and gas phase.

[0098] In another embodiment it is possible to arrange the Rankine cycle between mixed and gas phase, also when pressure is above critical point 46. In another embodiment it is possible to arrange the Rankine cycle in gas phase, also with a pressure higher than a pressure in the critical point 46.

[0099] Fig. 5 discloses a transformer according to a first embodiment. The transformer comprises two brackets 54 attached to a fixed support (not shown). An enclosure 56 is attached to the brackets. The enclosure comprises an inlet 51a and an outlet 51b for a heating power fluid for heating the transformer as further explained below. Electric wires 53 for delivering electric power are shown. Inlets 52a and 52a’ and outlets 52b and 52b’ are shown for a cooling power fluid as further explained below. Bearings 55 are arranged for enabling a shaft to rotate in relation to the enclosure.

[0100] Fig. 6 is a cross-sectional view through the enclosure 63b (56), which is attached to the brackets 63a (54) and is fixed. Inside the enclosure 63b there is arranged a rotating body 64a, which will be describe in further details below. The rotating body us supported by bearings 68 (55). The enclosure 63b further comprises a ridge 63c.

[0101] The rotating body 64a is sealed in relation to the enclosure 63b at both sides by sealing members 67.

[0102] The inlet 61a and the outlet 61b of heating power circuit 61c are provided with a heating power fluid from a source (not shown), such as hot water. There may be arranged other sources for heating power as explained below. The cooling power inlets 62a and 62a’ may be provided with cold water which circulates though cooling power circuit 62c and out via cooling power outlets 62b and 62b’.

[0103] A generator 65a is shown schematically having a stator 65c which is fixed, and a rotor 65b attached to the rotating body. The generator produces electric power, which is delivered via electric wires 53, see Fig. 5.

[0104] The rotating body 64a may be sealed in relation to the shaft by seal members 66a, 66b.

[0105] Fig. 7 shows an interior of the rotating body, which comprises channels as shown in more details. In the embodiment according to Fig. 7, the rotating body is rotating in the clockwise direction, but rotation in counter-clock-wise direction is possible.

[0106] A first inner ring channel 74b is arranged close to the center of the rotating body with a small radius. The first inner ring channel 74b comprising a heat medium. The heat medium in the first inner ring channel may be cooled by a cooling power fluid, for example arranged in the center of the first ring channel 74b, see cooling power fluid 62c in Fig. 6.

[0107] A cooling channel 72d is attached to the first ring channel 74b at interface 71d and receives heat medium from the first ring channel 74b. The cooling channel 72d may extend in a spiral having substantially constant radius and an axial extension. The spiral may extend in a clock-wise direction. The heat medium in the cooling channel may also be cooled by the cooling power fluid. The cooling channel 72d forms at least a portion of a condenser. At the end 71a of the cooling channel 72d, the heat medium is in a liquid state (or a partially liquid state).

[0108] The cooling channel extends axially, i.e. the distance (radius) to a rotational axis is substantially constant, but the distance may differ in that part of the cooling channel spiral is arranged at a smaller or larger distance from the axis. In particular, the distance from the axis may be smaller at the interface 71d and increase slightly.

[0109] Since the spiral extends in a clock-wise direction, any flow of heat medium inside the cooling channel from the inlet 71d will produce a torque in the clock-wise direction by friction towards the channel walls. However, the spiral may extend in the other direction or in both directions.

[0110] A pump channel 72a is attached to the cooling channel at pump channel input 71a. The pump channel extends radially out from the rotational axis until pump channel output 71b. The pump channel may extend in a bend (part of a spiral) in a counter-clockwise direction. When the rotating body rotates clockwise, the liquid fluid in the pump channel will tend to move more or less radially outwards towards the periphery. The pressure in the pump channel 72a increases due to the centripetal forces exerted by the rotation.

[0111] A heating channel 72b is connected to the pump channel output 71b. The heating channel 72b may extend in a spiral having substantially constant radius, which is larger than the radius of the cooling channel 72d. The spiral extends in a counter-clockwise direction, (but may extend in the other direction, or both). The heat medium in the heating channel may be heated by a heating power fluid (61c, see Fig. 6). The heating channel 72b forms at least a portion of an evaporator. At the end 71c of the heating channel 72b, the heat medium may be at least partially in a gas state. The pump channel 72d end 71c is connected to a second outer ring channel 73, arranged at a periphery of the rotating body having a radius which is larger than the radius of the first ring channel 74b.

[0112] The heating channel extends axially, i.e. the distance (radius) to the rotational axis is substantially constant, but the distance may differ in that part of the heating channel spiral is arranged at a smaller or larger distance from the axis. In particular, the distance from the axis may be larger at the pump outlet 71b and decrease slightly.

[0113] Fig. 7 also shows a turbine channel 75 which is connected tangentially to the outer ring channel 73 (not shown) and extend in a clock-wise spiral to the inner ring channel 74b and is connected tangentially to the inner ring channel at 75b.

[0114] The arrangement is disclosed in more details in Fig. 9. The outer ring channel 92a comprises an axial flow 93a from inlet 71c. The axial flow 93a is bent 90° to become a radial and partly tangential flow to an interface 93b. A turbine channel 93c is arranged in a rotating body, which can rotate in relation to the ring channel. The turbine channel 93c extends from an inlet 93b’ adjacent the interface 93b in the outer ring to an outlet 93d’ adjacent the inner ring. The inner ring comprises an interface 93d which receives heat medium from outlet 93d’. The operation will be further described with reference to Fig. 12.

[0115] If the embodiment according to Fig. 7 is compared with Fig. 4, it appears that the cooling channel 72d forms a condenser 42d, the pump channel 72a forms a pump 42a and the heating channel 72b forms an evaporator 42b according to the Rankine cycle and the turbine channel 75 forms a turbine 42c. Because the rotating body is rotating, the cooling channel 72d having a small radius is at a low pressure and at a low temperature and the heating channel 72b having a large radius is at a high pressure and a high temperature, consistent with the Rankine cycle, although the operation of the transformer may differ from a conventional Rankine cycle.

[0116] Fig. 9 shows the turbine channel in more details. The ring channel 92a comprises heating channel 93a which makes a bend over 90° and becomes radial and partly tangential and ends in interface 93b. Interface 93b mates with a turbine channel 93c in a turbine body 92b, which rotates around a symmetry shaft 91a. The heat medium flows over a small space 94 tangentially and radially inwardly in a spiral path to outlet interface 93d. Outlet interface 93d is connected to the inner ring 74b. When the heat medium flows in the turbine channel 93c, the frictional forces against the walls of the channel generates a torque around axis 91a. Other embodiments of the turbine will be described in more details below.

[0117] The initial portion of the turbine channel 93c extends at a distance from the rotational axis 91a as shown by broken line 95, from a large radius 95’ to a smaller radius 95”, which is about two third of the total radius. The frictional force generating torque is large at such radiuses. The end portion of the turbine channel extends at at a distance from the rotational axis 91a as shown by broken line 94, from a large radius 95’ to a smaller radius 95”, which is about one third of the total radius. What is said above of the radial distance of the cooling channel and the heating channel have similar properties, in that the distance may vary as shown by broken lines 95 and 94.

[0118] Fig. 10 shows that the rotating body may comprise several channel circuits. Fig. 10 discloses three pump channels 101a, 101b, 101c, three heating channels 102, three turbine channels 103 and three cooling channels 104. There may be any number of circuits.

[0119] Figs. 12a, 12b, 12c, 12d and 13 disclose a second embodiment of the transformer. The transformer comprises a symmetry axis 121 and a first rotating body 122a which is arranged to rotate around the axis 121, for example with a rotation rate of 500 revolutions per second (rps). The rotation rate may be between 10 - 1000 rps, such as 50 - 500 rps.

[0120] As shown in Fig. 12b, the rotating body comprises a pump channel 124b extending radially. However, the pump channel may extend partly in a spiral as shown in Fig. 7 so that the heat medium flow will become radial during rotation. It may be an advantage to have the flow radial, since friction forces will be minimized. Otherwise, the pump channel may extend spirally both in clock-wise or counter-clock-wise direction. If so, friction forces due to the flow in pump channel will generate a torque on the rotating body around the symmetry axis.

[0121] The pump channel may have a constant cross-section over at least a portion so that the flow in the pump channel has the same speed from the inlet to the outlet. This will minimize any losses due to viscosity.

[0122] A second pump channel 128b is shown in Fig. 12b. It is noted that the rotating body 122a comprises several circuits, for example 24 circuits arranged with a mutual angle of 15°.

[0123] As shown in Fig. 12c, the pump channel 124b extends from a radially inner end 124a to a radially outer end 124c, at which the pump channel turns 90° and becomes axial heating channel 124d. The heating channel may extend at a substantially constant radius. As shown in Fig. 7, the heating channel may extend in a spiral in order to increase the length thereof. The heating channel extends adjacent a periphery of the rotating body. Heating power may be transferred from outside the rotating body in order to heat and evaporate the heat medium in the heating channel. The heating channel has a length which is sufficient for evaporating the heat medium.

[0124] The heating channel 124d may have a slight inclination in that the radius of the heating channel decreases as the distance from the pump channel increases. By this feature, any liquid inside heating channel tend to be returned towards the pump channel. In addition any liquid in the heating channel is urged radially outward and becomes closer to the heat energy source, which is advantageous for the evaporation. As shown in Fig. 12b, a second rotating body 122b is arranged in a circular recess 122d in the first rotating body. The second rotating body has a radial extension so that it fills the radial space with a small gap to the first rotating body, so that the second rotating body may rotate freely in relation to the first rotating body. The second rotating body has an axial extension so that it fills only a portion of the axial extension of the circular recess 122d. As further shown in Fig. 12b, a third rotating body 122c is arranged and fills the rest of the circular recess 122d.

[0125] Fig. 13 is an exploded view of the embodiment according to Figs. 12a - 12 d. The same component as in Figs. 12a - 12d has the same reference number but starting with “13” (as far as possible). Thus, the second rotating body 122b in Fig. 12 is the same as the second rotating body 132b in Fig. 13 and is arranged in the circular recess 132d (122d). As seen in Fig. 13, the second rotating body 132b (122b) has a circular recess 132e (122e) with a smaller radius than circular recess 132d. An axial extension 132f (122f) of the third rotating body 132c (122c) fits into the second circular recess 132e so that the third rotating body may rotate in relation to the second rotating body.

[0126] Small spaces are arranged between the rotating bodies so that the rotating bodies may rotate freely in relation to each other.

[0127] Fig. 12c shows that the heating channel 124d extends from the first rotating body via a first interface 124e to an axial heating channel 122e in the second rotating body. The heating channel in the second rotating body extends from 124e to 124f where the heating channel is bent over 90° and extends radially and partly tangentially, see Fig. 14a, and opens into an interface 124g in the third rotating body. As shown in Fig. 12d, the interface 124g is connected to a turbine channel 124h, which ends at interface 124i. From interface 124i, the heat medium flows into a cooling channel 124j of the second rotating body and further via interface 124k (see Fig. 12b) to cooling channel 124m and further to the inlet of the pump channel.

[0128] Fig. 14a shows an arrangement of the mentioned channels. As appears from Fig. 14a and Fig. 14b, there are arranged a plurality of heat medium circuits, of which ten are shown extending over a quarter circle. Thus, there are 40 circuits with a mutual angle of 9°.

[0129] Since the three bodies rotate in relation to each other, the heat medium passes from one circuit in the first rotating body, to another circuit in the second rotating body and to a further circuit in the third rotating body via respective interfaces.

[0130] Fig. 12b further discloses two ring-shaped bodies 123b and 123c. These ring-shaped bodies are arranged outside the first rotating body, while the second and third rotating bodies are arranged inside the first rotating body. First ring body 123b is arranged opposite the second rotating body 122b and second ring body 123c is arranged opposite the third rotating body 122c. The ring bodies may be fixed in relation to the enclosure or the surroundings. As shown in Fig. 22, both the second body and the third body 222 are provided with several magnets 223, which may be permanent magnets (or other type of magnets, such as electromagnets). The ring bodies 222’ are provided with corresponding magnets 223’, which may be electromagnets. The magnets may be part of a magnetization which vary for each portion of the magnet. The magnet forces extend radially or in any combination. In another embodiment, the magnet forces may extend axially or in any desired direction.

[0131] In one embodiment, the second rotating body is maintained still in relation to the symmetry axis 221 or in relation to the enclosure by strong magnets 223, 223’. The second body may perform small pivotal movements back and forth, but cannot rotate. Thus, each magnet 223 in the second body is always cooperating with the same outer magnet 223’.

[0132] The second ring body 123c may comprise electric coils, which cooperates with the magnets 223 of the third rotating body for braking the rotation of the third rotating body. Thus, the electric coils and the magnets operate as a generator, to produce electric current from the rotation of the third rotating body, which is the turbine.

[0133] The electric current produced may be used for rotating the first rotating body and thus produce the pumping action. Since the Rankine cycle produces more mechanical energy than is required for the pump, there will be extra electric energy to be used outside the transformer via electric wires 53 (Fig. 5).

[0134] In another embodiment, the third rotating body is mechanically connected to the first rotating body so that they rotate in unison, for example by having a common shaft, or via any mechanical means, such as a gear box. The electric power obtained from the coils can be used for external purpose. In this embodiment, the generator may be arranged in the shaft connected to the rotating body 64a, as shown in Fig. 6.

[0135] Fig. 13 is an exploded view and shows that the second body 132b is arranged in the recess 132d in the first rotating body 132a, which rotates around symmetry axis 131. The third body 132c is arranged in the recess 132e and the two rotating bodies occupies the recess 132d. Several broken lines 133a, 133b, 133c and 133d indicates the flow of heat medium. The arrangement of the rotating bodies in the axial direction may be another than shown in Fig. 13.

[0136] Fig. 14a and Fig. 14b show the channels for the heat medium. There is a pump channel 142a rotating around a symmetry axis 141a and connected to a heating channel, which ends in an interface 142b to the second rotating body. To the left of broken line 143a is the first rotating body.

[0137] The heating channel 142c continues in the second rotating body, but may be any one of the heating channels that happen to be opposite the interface 142b. The heating channel 142c is bent over 90° and ends in interface 142d. Broken line 143b indicates the second body.

[0138] From interface 142d, the heat medium passes to the third body comprising the turbine channel 142e. Again, any turbine channel that happens to be opposite interface 142d is used. The turbine channel is bent over 90° and becomes axial and ends in an interface 142f. The heat medium flows to a cooling channel in the second rotating body and further to interface 142g, which is connected to the cooling channel of the first rotating body, thus closing the circuit. Broken line 143b indicates the interface between the second rotating body and the third rotating body.

[0139] Fig. 8 shows the heat medium flow in the channels. The first rotating body 64a (see Fig. 6) is rotating around a symmetry axis 81a. The heat medium flow 87b in the pump channel 72a flows essentially radially. The heat medium flow 87c in the heating channel 72b is shown to flow axially, although it may be arranged in a spiral with constant radius. The heat medium is then arranged to bend 90° at area 88a to become tangential in the outer ring channel 73. The heat medium flows radially inwards in a spiral flow 87d and is arranged to turn 90° at area 88b to become an axial flow 87a in the cooling channel 72d.

[0140] Fig. 10 discloses that several pump channels 101a, 101b, 101c and several turbine channels 103 may be arranged.

[0141] Fig. Ila discloses schematically a Rankine cycle according to any one of the embodiments. In the figure the coordinate system rotates together with the rotating body so that the pump channel extends according to the y-axis and the heating and cooling channels extend according to the x-axis. There is shown a pump channel 113a starting at input 112a at a small radius of rotation and ending 112b at a large radius of rotation, whereby the pressure increases due to the rotation. A heating channel 113b extends between points 112b and 112c. A turbine channel 113c extends in a spiral between end points 112c and 112d. A cooling channel 113d extends between end points 112d and 112a closing the circuit.

[0142] Fig. Ila indicates that the different channels in the heating channel circuit may have different areas as shown at 11 la and 11 lb. As shown in Fig. 1 lb, the heating channels crosssection 117 can have a rectangular shape with a width 116b and a height 116a and a tilt 116c in relation to a center of rotation 115. Each channel may have surfaces which may be treated for reduced friction or flow resistance, and for maximum or minimum thermal resistance depending on the position in the Rankine cycle. For example, there is a high flow speed of the heat medium 114b in the turbine and the channel surfaces in the turbine should be treated for low friction. On the other hand, the channel surfaces of the heating channels and the cooling channels should have low thermal resistance.

[0143] Fig. 15 discloses a fixed enclosure 153a, which is arranged outside and protects a first rotating body 152a, which may rotate around symmetry axis 151. The enclosure 153a may be sealed 153b in relation to the first rotating body, whereby fluid 154a inside the enclosure and outside the first rotating body cannot escape to the surroundings 154e as indicated by broken line 154d.

[0144] The first rotating body 152a may comprise a second rotating body 152c, which may rotate in relation to the first rotating body. There may be arranged magnets 152b or electric coils interacting with the second rotating body. Any fluid 154b inside the first rotating body, for example between the first rotating body 152a and the second rotating body 152c needs to stay inside the first rotating body and cannot escape to the surroundings 154e since the first rotating body is closed.

[0145] Fig. 16 discloses that a fluid 163a between a third rotating body 162b and a second rotating body 164 all inside a first rotating body 162a (rotating around symmetry axis 161) cannot escape to the surroundings 163c as indicated by broken line 163b.

[0146] Fig. 17 shows energy flow in a transformer according to any of the previous embodiments. An enclosure or similar 171 encloses a heating power source 172 and a cooling power source 172’. The heating power source 172 and the cooling power source 172’ exchange heating power with rotating bodies 173, 174a, 174b as shown by lines 175a and 175a’. Heating power may also be exchanged between the rotating bodies as shown by broken line 175b. Heating power may also be exchanged between transformers.

[0147] The heating power source may be hot water and the cooling power source may be cold water. However, alternative energy sources may be used, such as nuclear power 172”, which may be arranged inside any one of the rotating bodies.

[0148] Fig. 18 discloses one heat medium circuit arranged in a sector 182 of a rotating body or several rotating bodies, rotating around symmetry axis 181. A pump flow may start at point 183a and the liquid may flow in a radial flow 183b to radially outward point 183c, whereby the pressure increases. The increase of pressure is dependent on the rotational speed and the radius of the end points. The pressure increase is counteracted by friction forces in the pump channel due to the heat medium flow. The flow area is substantially constant at least over a portion of the pump channel. The volume and temperature are substantially constant (adiabatic).

[0149] From 183c and to point 183e, the heat medium passes in a flow wherein heating power is provided for evaporation of the heat medium. Thus, the liquid heat medium at 183c is evaporated. The pressure and temperature are substantially constant. Since the heat medium in gaseous phase has a larger volume than the liquid phase, the cross-sectional area of the heating channel may increase, as shown at 183e. At the same time, the flow speed may increase.

[0150] At 183e, the heat medium change direction and passes partially radially in a turbine flow 183f to 183g. The area of the flow channel may be relatively constant.

[0151] At 183g, the heat medium is cooled 183h until the heat medium is in a liquid state. Now, the cross-sectional are of the flow decreases.

[0152] Fig. 19 discloses that two transformers may be arranged in series. A heating power fluid 192a exchanges 192b heating power with a first transformer 191a in an evaporation channel 192c. During this process, the heating power fluid is cooled but can still act as heating power fluid for a second transformer 191b via energy path 192d to an evaporator 192e of the second transformer, which operates at a lower evaporation temperature. There may be required to supply further power 192d’ to the evaporator 192e of the second transformer. The used heating power fluid may be used in a third transformer via power path 192f or may be discarded 192g. The heating and / or cooling power sources may be used in the same manner. The transformers may be arranged in series or in parallel or any combination.

[0153] Fig. 20 discloses an embodiment similar to the embodiment of Fig. 18 and shows two circuit 202a and 202b out of many circuits. In the embodiment, there is a pump channel 204a, which rotates around a symmetry axis 201. The pump channel 204a extends radially and is at the radially outward end bent 90° into a heating channel 204b extending axially. The pump channel 204a and part of the heating channel 204b are arranged in a first rotating body 203a. The main portion of the heating channel 204b is arranged in a second body 203b. The heating channel 204b is bent 90° into a turbine channel 204c which extends into an axial cooling channel 204d. The turbine channel is arranged in a third rotating body 203c.

[0154] As is indicated by broken lines in Fig. 20, heating power may pass from one heating channel to another heating channel in the second rotating body, as indicated by broken line 205a. As indicated by broken line 207c, heating power may pass from a heating channel to a cooling channel (adjacent). As indicated by broken line 207a, heating power may pass from the heating channel to the second rotating body as indicated by 206. As indicated by broken line 205b, heating power may pass from the turbine channel to the second body. As indicated by broken line 207d, heating power may pass from the second body to the third body. As indicated by broken line 207b, heating power may pass inside the second rotating body (also inside the first rotating body and inside the third rotating body). As indicated by broken line 204e, heating power may leak from turbine channel 204d to the second rotating body.

[0155] There may be further exchange of heating power.

[0156] Fig. 21 is a view similar to Fig. 20 and shows interfaces. There is a first rotating body 212a, a second rotating body 212b and a third rotating body 212c, which all may rotate around a common symmetry axis 211. There is arranged a small space 215a between the first rotating body and the second rotating body, and a small space 215b between the second rotating body and the third rotating body. The broken line 216 indicates a flow path for the heat medium, flowing in a clock-wise direction.

[0157] The pump channel 214b extends from an inlet 214a at a radially inner end to an outlet 214c at a radially outer end and extends over a bend of 90° to an axial portion until interface 213a. In the interface 213a, the heat medium may flow to a heating channel 214d in the second body, which is opposite the interface 213a. The heat medium is heated and evaporates in the heating channel 214d and flows to an interface 213b. In the interface 213b, the heat medium may pass from the heating channel to a turbine channel 214e opposite the interface 213b. The heat medium flows from the interface 213b via the turbine channel 214e to an interface 213b’. In the interface 213b’, the heat medium flows to a cooling channel 214f opposite the interface 213b’. The cooling channel ends in an interface 213a’ wherein the heat medium may flow to a pump inlet 214a opposite the interface 213a’.

[0158] As is evident, the heat medium may “jump” between different heat circuit in each interface. Thus a heat medium volume leaving the pump channel 214b may end up in a pump channel in another heat circuit, because the rotating bodies rotate in relation to each other. The heat circuits are arranged close to each other in the peripheral direction, so there will be virtually no interruption of flow in the interfaces. The interfaces may act as parasitic flow paths that are unintended. By arranging the distances small between the rotating bodies, the parasitic flows may be small.

[0159] Fig. 23 is a schematic view of a heat circuit, without showing the interfaces. The arrows 234 indicated that the heat medium flow in a clock-wise direction. There is a radial pump flow 233a that bends at 90° at 232b into an axial evaporation flow 233b, which bends at 90° at 232c into a radial turbine radial flow 233c, which bends at 90° at 232d into an axial condensation flow 233d and back to the pump flow via a bend over 90° at 232a. The heat circuit rotates around a symmetry axis 231. The different flow portions may extend seamlessly into each other.

[0160] Fig. 24 is a diagram 241a having distance at the x-axis 241b. The y-axis 241c shows the size of pressure 245, temperature 246 and density 244 of the heat medium in the heat circuit. The diagram is computer-generated for the heat medium always in a gas state.

[0161] The diagram starts at the left in the middle of a cooling flow 243d’. The reference numeral 242a corresponds to reference numeral 232a and the same is true for all reference numerals 243, 242b, 243b, 242s, 243c, 242d. Reference numeral 243d is half of the cooling flow.

[0162] Fig. 25 is a schematic view similar to Fig. 23, but the heat medium flow is counter-clock-wise. The heat medium flow 253c is a compression and the heat medium flow 253a is an expansion. The flow 253b is a condensation and the flow 253d is an evaporation Thus, the heat circuit is a heat pump circuit or a refrigeration system.

[0163] Fig. 26 is a diagram similar to Fig. 24.

[0164] Fig. 27 discloses a further embodiment of a transformer in which the rotating bodies rotate around different symmetry axes. Two heat circuits 273, 273’ similar to Figs. 18, 20, 21 are shown. A first rotating body 272a is enclosed in a recess 275a in a second rotating body 272b. The first rotating body encloses a pump channel 274a extending from an interface 276b at small radius and low pressure to an interface 276a at a large radius and high pressure. A heating channel 274b extends in the second body 272b between interface 276a and interface 276d’. The first and second bodies may rotate around a first symmetry axis 271a.

[0165] A turbine channel 274c extends in a third rotating body 272c, 272c’. The third rotating body may rotate around a second symmetry axis 271c, 271c’, which each are perpendicular to the first symmetry axis 271a. The flow of heat medium influences upon vanes or similar in the third rotating body to impart a rotation to the third rotating body. The heat medium flows from interface 276d’ to interface 276c’ where the flow passes to the second rotating body at a cooling channel 274d. The cooling channel ends at interface 276b. The heat medium is condensed in the cooling channel. The turbine may be a conventional gas turbine. In another embodiment, the turbine is a Wankel device arranged to work as a turbine.

[0166] There is a small space between the first rotating body 272a and the second rotating body 272b. Heat medium at high pressure at interface 276a may leak to low pressure interface 276b, which is a parasitic flow decreasing the efficiency of the transformer.

[0167] There is a small space 275b’ between the third rotating body 272c’ and the second rotating body 272b in which heat medium may form a parasitic flow.

[0168] Mechanical rotational power obtained by the turbine in the third rotating body may be transferred to the second rotating body as indicated by broken line between point 277a” and point 277a, for example by permanent magnets in the third rotating body and electric coils in the second rotating body. Such electric power may be used to drive the pump as indicated by the broken line between point 277a and point 277a’. The rest of the power may be transferred to the surroundings as indicated by the broken line between point 277a and point 277b. The surrounding may provide power for driving the pump in the first rotating body as indicated by the broken line 277 between point 277b and point 277a’ . Power may also be transferred directly from the third rotating body to the surroundings as shown by the broken line between point 277a” and point 277b.

[0169] Fig. 28 is a schematic view showing possible flow paths of the heat medium. A transformer 281 may comprise an enclosure 283a, which is non-rotating. The enclosure encloses several rotating bodies such as a first rotating body 283b. There may be another rotating body 283c. The rotating bodies may rotate around different symmetry axis 282b and 282c. Many fluid components may be arranged in a loop 284. A portion of a Fluid may be passed between a domain 288' through a Channel 286 to many Media Supplies 285. There may be different fluid components 287a, 287b, 287c. There may be small portions 288 of any small Domain inside or on a surface of a Transformer where Fluid may be passed. As an example, a few Domains are marked with a circle. A portion of many heating and cooling fluids (called Fluid) may be passed 289 between various spaces in combination between Domains in a Transformer.

[0170] Fig. 29 shows a Rankine cycle which is operated as a heat pump (or refrigerator) in which the heat medium flows in a counter-clock- wise direction.

[0171] A compressor 292c compresses a heat medium in gas state from point 29 Id to 291c whereby the pressure increases and the enthalpy increases as shown by arrow 293c. The heat medium at a high pressure and high temperature is cooled in a condenser 292b to condense the heat medium. The enthalpy decreases as shown by arrow 293b. At point 291b, the liquid heat medium is transferred to an expansion member 292a (for example a valve) in which the heat medium is expanded, whereby the pressure and temperature decreases until point 291a. The enthalpy decreases as shown by arrow 293a. The heat medium at a low pressure and a low temperature is heated in an evaporator 292d to evaporate the heat medium until point 29 Id. The enthalpy increases as shown by arrow 293d. The transformer according to embodiments can be modified to work as a heat pump.

[0172] Figs. 30a and 30b show a rotating body 301, rotating around rotating axis 303’, having a heat medium channel 306. The heat medium channel opens into an interface 302 where channel towards 302” has an orientation described by angles 305a and 305b and where the surface 302’ around the opening have a second direction described by angles 304a and 304b, where each angle is related to the surface 303, passing through the rotating axis 303’. Each possible combination of angles 304a, 304b, 305a, 305b are included in the respective embodiments described previously.

[0173] Fig. 31 discloses two rotating bodies 312, 312’ that may have different rotation symmetry axes 311, 311’. A heat medium in one rotating body may pass via interface 314, 315, 316, wherein 306 is another heat interface.

[0174] Fig. 32 shows a symmetry axis 322a and a rotating body 322 comprising a heat medium circuit 322b, 322c, 322d, 322e. Any portion of the heat medium circuit can be divided in several segments or branches 323 and node points 328b. Any branch can be divided in several serial branches 324a, 324b, 324c. Another node point 328, 328a, may be connected. Any serial branch 325 can be divided in many parallel branches 326a, 326b, 326c etc.

[0175] Fig. 33a discloses a first rotating body 332a rotating around a symmetry axis 331. A second body 332b and a third body 332c are arranged in a recess in the first rotating body as described with reference to Figs. 12a, b, c, d and Fig. 13.

[0176] There are two interface 333a, 333b between the first rotating body and the second rotating body. The two interfaces are connected to each other via a small distance necessary to have the two bodies rotatable in relation to each other. The connection is indicated by broken line 335. Two interfaces 333d and 333c between the second rotating body and the third rotating body also comprises a small distance necessary to have the two bodies rotatable in relation to each other. An area within a circle 334 is shown in enlarged scale in Fig. 33b.

[0177] From interface 333a, there is a small first radial space 336a extending radially to a larger second space 336b arranged in the first rotating body. Another small third radial space 336f extends between the second space and the interface 333b. Heat medium in the second space 336b may flow in the radial direction as a parasitic flow as indicated by line 335. The dotted line 336c indicates that the surface of the second radial space 336b may have a surface treatment, such as friction reducing matter. Line 336e indicated that heat medium may be supplied to the second radial space 336b, for example at the end close to the interface 333b. The oval 336d indicates that heating power of cooling power may be supplied to the second radial space 336b. All these measures may reduce the parasitical flow in the second radial space. The same measures may be arranged in all other spaces having parasitic flow, such as indicated by partially broken line 335b and line 335a.

[0178] In the same way, from interface 333d, there is a small fourth axial space extending axially to a larger fifth space arranged in the second rotating body. Another small sixth radial space extends between the fifth space and the interface 333c. Heat medium in the fifth space may flow in the radial direction as a parasitic flow as shown by line 335b. Lines 335a and 335c indicates that there may be further small parasitic flows of heat medium as indicated by these lines.

[0179] There may be seal members for reducing such parasitic flows. On the other hand, such parasitic flows do not greatly disturb the operation, since they cannot flow out of the first rotating body, or any other enclosure.

[0180] Figs. 34a, 34b, 34c, 34d, 34e and 34f show different options of enclosing features. Fig. 34a discloses an enclosure 343a which may be rotating around a symmetry axis 341a or may be fixed. A first rotating body 344a encloses a heat medium circuit 342a and may be rotating around symmetry axis 341a or may be fixed.

[0181] Fig. 34b discloses an enclosure 343b which may be rotating around a symmetry axis 341b or may be fixed. A first rotating body 344b and a second rotating body 344b’ encloses a heat medium circuit 342b. Each of the rotating bodies may be rotating around a symmetry axis 341b or may be fixed.

[0182] Fig. 34c discloses an enclosure 343c which may be rotating around a symmetry axis 341c or may be fixed. A first rotating body 344c and a second rotating body 344c’ and a third rotating body 344c” encloses a heat medium circuit 342c. Each of the rotating bodies may be rotating around symmetry axis 341c or may be fixed.

[0183] Fig. 34d discloses an enclosure 343d which may be rotating around a symmetry axis or may be fixed. A first rotating body 344d and a second rotating body 344d’ and a third rotating body 344d” encloses a heat medium circuit 342d. Each of the rotating bodies may be rotating around one of symmetry axis 34 Id, 34 Id’ and 34 Id” or may be fixed. The symmetry axes may be non-parallel.

[0184] Fig. 34e discloses an enclosure 343e which may be rotating around a symmetry axis or may be fixed. A first rotating body 344e may rotate around first symmetry axis 34 le. A second rotating body 344e’ may rotate around second symmetry axis 34 le’. A third rotating body 344e” is enclosed inside the second rotating body 344e’ and may be rotating around a third symmetry axis 34 le”. A heat medium circuit 342e may extend through the rotating bodies. The three symmetry axes may be non-parallel. Heating power source 345 may provide heating power to the rotating bodies via connection paths and as indicated by broken lines 346. Alternatively or additionally, cooling power may be supplied as shown by the broken lines. The broken lines may alternatively or additionally symbolize magnetic interaction. Fig. 34f discloses an enclosure 343f which may be rotating around a symmetry axis or may be fixed. A first rotating body 344f may rotate around first symmetry axis 34 If. A second rotating body 344f may rotate around second symmetry axis 341f . A third rotating body 344f ’ is enclosed inside the second rotating body 344f and may be rotating around a third symmetry axis 34 If ’. A heat medium circuit 342f may extend through the rotating bodies. The three symmetry axes may be non-parallel. The third symmetry axis 341f ’ may be perpendicular to the first symmetry axis 34 If.

[0185] It is mentioned that there may be several heat medium circuits in each of Fig. 34 a-f. Fig. 35a discloses a heat medium circuit according to any one of the previous embodiments. A first rotating body is rotating around symmetry axis 351a. A pump channel 352n is at an outlet connected to an evaporator channel 352a and at an inlet connected to a cooling channel 352m, all included in the first rotating body.

[0186] The evaporator channel 352a is arranged for receiving heating power for evaporation of the heat medium inside the evaporation channel so that the heat medium exiting evaporation channel at interface 352b is an a gas phase. The heat medium in the pump channel 352n is in a liquid phase.

[0187] The evaporated heat medium passes via an interface 352b to a further portion of the evaporation channel 352c arranged in a second rotating body, rotating around symmetry axis 351a. The heat medium may be further heated for producing overheated heat medium. In another embodiment, the heat medium is not further heated but may have time to equalize.

[0188] In a further interface 352d, the heat medium flows to a turbine device 352e, which may rotate around a symmetry axis 351b, which may be perpendicular to axis 351a. The turbine may be any of the turbine devices previously described. Alternatively or additionally, the turbine may be a previously known gas turbine, which produces mechanical power.

[0189] In a further interface 352f, the heat medium may flow to a condensation channel 352g wherein the heat medium is still in a gas phase until an interface 352h. A pre-cooling of the heat medium may take place.

[0190] From interface 352h, the heat medium, still in gas phase, flows to a cooling channel 352m, in which the heat medium condensates until liquid phase.

[0191] Consequently, the heat medium in first body enters at interface 352h in gas phase and is transformed from gas phase to liquid phase in the cooling channel 352m at a low temperature before reaching the pump channel 352n, in which the pressure increases, and is transformed from liquid phase into gas phase at a high temperature before flowing out via interphase 352b. Thus, the first rotating body performs a transformation of the heat medium in gas phase at a low pressure and low temperature to a heat medium in gas phase at high pressure and high temperature.

[0192] Fig. 35b discloses a further embodiment in which the turbine is arranged rotating around a symmetry axis 351b’, which is parallel with symmetry axis 351a’. Fig. 36 discloses a portion of a circuit. There is disclosed a pump channel 363 extending from an inlet 363a’ to an outlet 363a. The outlet is connected to an evaporator channel 364e, in which the heat medium evaporates by receiving heating power from a heating power source. The heat medium is in liquid phase in pump channel 363 and further in the outlet 363a and up to line 364a, which indicates that all heat medium to the left of this line is in liquid phase. In the space between lines 364a and line 365, the heat medium is in a mixed phase. To the right of line 365, the heat medium is in gas phase. The heat medium at outlet 362a may be pre-heated for increasing the temperature towards the evaporation temperature. As shown by line 366, the evaporation channel forms a slight angle between the evaporation channel and the rotation axis, which means that any liquid in space 364 will tend to flow to the left for entering the liquid phase to the left of line 364a.

[0193] In a similar manner, the inlet 363a’ comprises heat medium in a liquid phase and line 364a’ indicates the borderline between liquid phase to the left of line 364a’ and mixed phase 364’ between line 364a’and line 365’. To the right of line 365’, the heat medium is in a gas phase. The condensation channel is inclined in relation to the rotational axis as shown at 366’. When the heat medium is cooled in the condensation channel, any liquid in mixed space 364’ will tend to move to the left into the inlet 363a to the pump channel.

[0194] The line 362a indicates an interphase between the first rotation body and the second rotation body. The interphase may be arranged in the mixed phase space or in the gas phase space.

[0195] In a similar manner, as shown in Fig. 37, the turbine channel 373 may comprise heat medium in gas phase. The heat medium at inlet 373a may be further heated for ensuring that the heat medium is in a gas phase. In space 374, the heat medium is in a mixed phase and in space 375, the heat medium is in a liquid phase.

[0196] In a similar manner, the heat medium in the outlet 377a’ from the turbine may be in gas phase. In space 374’, the heat medium has been cooled into a mixed phase and in space 375’, the heat medium is in liquid phase. The evaporation channel and the cooling channel are inclined to facilitate that liquid is transferred to the left and gas is transferred to the right.

[0197] A further embodiment is disclosed in Figs. 38a, 38b, 39a, 39b, 40a, 40b, 40c, 40d, 41a, 41b and 41c.

[0198] With reference to Fig. 39b, the embodiment comprises an evaporator portion 394 and a condensation portion 395, rotating around a rotation axis 397 supported by several bearings 398a, 398b, 398c, 398d all arranged on a first rotating body.

[0199] In addition, there is a power portion 396, which is arranged on a second rotating body, which may be non-rotating.

[0200] The bearings may be conventional ball bearings or roller bearings, but may alternatively be any type of bearings, such as magnetic bearings. Fig. 38b shows the evaporator portion 384 (same as 394). Fig. 38a shows a radial sector of the evaporator portion in cross-section. A plurality of such radial sectors are arranged symmetrically around the symmetry axis, for example 8 sectors (45°) or 36 sectors (10°) or 96 sectors (3.75°) or any number of sectors. The isometric view of Fig. 38b shows two such sectors for a pressurizing channel.

[0201] The heat medium enters the evaporator portion at line 382a, which may be arranged in the rotating axis 383a, which rotates around symmetry axis 381. The heat medium is in a substantially condensed liquid phase. The heat medium passes from line 382a to a (plurality of) radial channel 382c via inlet 382b. The heat medium passes to a liquid collection chamber 383b, in which possible gases phase is separated and condensed into liquid phase, as shown by dotted lines 382d and 382e. A grid 383c may be arranged for guiding the flow. The liquid collection chamber is arranged as a ring-shaped or toroid-shaped chamber extending 360° around the rotation axis.

[0202] The liquid heat medium passes to an inlet 382f of a pressure channel, which is arranged radially. The pressure of the heat medium increases in the pressure channel, because of the rotation of the pressure channel.

[0203] There may be arranged a preheating member 383 d for preheating of the heat medium as it passes in the pressure channel. The preheating is small so that the heat medium is still in a liquid phase at the radially outer end of the pressure channel.

[0204] The heat medium exits the pressure channel at outlet 382g (in liquid phase) and passes an equilibration chamber 383 e to be explained below and enters an evaporation channel inlet 382h.

[0205] The evaporation channel slopes towards the symmetry axis 381 and has a bend over almost 180° and returns to a gaseous collection chamber at an inlet 382i. During the extension of the evaporation channel from inlet 382h to outlet 382i, heat is supplied to the heat medium, for example via flanges 383g from a heat source (not shown), which may be arranged radially outward of the flanges 383g or elsewhere. The heat medium is evaporated and reaches the gaseous collection chamber 383f in substantially gaseous phase.

[0206] The evaporation channel extends into the gaseous collection chamber 383f and is provided with several holes (not shown) for passing heat medium from the evaporation channel into the gaseous collection chamber as indicated by broken lines 382j . The heat medium is mixed in the gaseous collection chamber as shown by broken line 383k.

[0207] Possible non-evaporated portions of the heat medium exit the gaseous collection chamber via a radial tube, as shown by broken lines 382m, to the equilibration chamber 383e arranged radially outward of the gaseous collection chamber and reenters the evaporation channel for evaporation.

[0208] Evaporated heat medium exits the gaseous collection chamber as shown by broken lines 382n via inlet 382o to a post-evaporation channel 382p. The post-evaporation channel may be provided with a restriction device 383h, such as a nozzle or a valve, in order to decrease the pressure and thereby further ensure that the heat medium is in a gaseous phase. Heat power may be added by several flanges 383g for overheating of the heat medium in the post-evaporation channel.

[0209] The gaseous collection chamber may additionally comprise a particle filter for removing particles and dirt, for preventing clogging of following restriction devices, such as valves or nozzles.

[0210] However, in another embodiment, no overheating is performed.

[0211] The flanges 383g also serve the purpose of mechanically stabilize the heat medium channels as shown in Fig. 38b.

[0212] The gaseous (and possibly overheated) heat medium passes to an outlet nozzle 382q. Before reaching the outlet nozzle, the post-evaporation channel is bent over an angle of for example 45° (between 30° and 89°) so that the post-evaporation channel extends in a partially tangential direction in a spiral manner, with substantially constant (or slightly decreasing) radius.

[0213] The outlet nozzle 382q increases the flow rate of the heat medium and lowers the pressure as the heat medium flows through the outlet nozzle. The increase of flow rate may be at least 5 times, at least 10 times, at least 20 times, at least 30 times such as 50 times or more. The heat medium flows out of the nozzle in a partially tangential and partially axial flow.

[0214] The post-evaporation channel may be slightly inclined, at least over a portion, as shown adjacent the outlet 382q, so that the outlet is in a position radially inward of the inlet of the post-evaporation channel.

[0215] During the flow through the outlet nozzle 382q, the pressure of the heat medium decreases in the outlet from the post-evaporation channel (and the flow rate increases), which means that a substantial tangential force is exerted on outlet nozzle 382q and the rotating body attached to the nozzle. Such tangential force will cause the rotating body to rotate. If the heat medium exits the nozzle in a tangential direction into the paper of Fig. 38a, the rotating body will rotate in the opposite direction.

[0216] The liquid collection chamber 383b, the equilibration chamber 383e and the gaseous collection chamber 383f extend over 360° in relation to the rotation axis, so that they form three ring-shaped or toroid-shaped chambers arranged radially outward of each other. There are several pressurizing channels extending from inlet 382f to outlet 382g, for example 18 channels divided in 20°. There are several evaporation channels, for example 36 channels divided in 10°. There may be several post-evaporation channels, for example 24 channels divided in 15°. Any desired number of channels may be used depending on the space and dimensions.

[0217] The evaporated heat medium exiting the nozzle 382q enters the power portion 396 shown in Fig. 39b and in more details in Figs. 40b, 40c and 40d and the cross-sectional view in Fig. 40a. The power portion comprises a turbine ring, extending over 360° around the rotation axis. The turbine ring is supported by several bearings 408c (398c) and 408d (398d) and a support structure 403 at a distance from the symmetry axis 401, which forms the center of the turbine ring. The turbine ring and the entire power portion may rotate freely from the first rotating body and forms a second rotating body.

[0218] The turbine ring 402 comprises an inlet 404 (392n) arranged opposite the outlet nozzle 409 (382q) from the evaporator. The turbine ring further comprises an outlet 405 (392o) arranged opposite an inlet 402 (392p) to the condensation portion. Between the inlet och the outlet, a plurality of turbine channels are arranged, which are bent in a U-shape so that the inlet 404 faces in a direction opposite to the outlet 405 in the tangential direction.

[0219] The turbine ring 402 is arranged standing still, i.e. non-moving, in relation to the surrounding space or the symmetry axis. This may be arranged by an inertia device 406 connected to a portion or sector of the turbine ring as shown in Fig. 40d. The inertia device may comprise a heavy mass 406, such as several flanges. In Figs. 40b and 40d the gravity force is acting upwards in the Figure and urges the inertia device constant in this direction, which means that the turbine ring is standing still in relation to the surrounding space. Thus, the turbine ring acts for preventing rotation of the heat medium inside the power portion.

[0220] Instead of the inertia device, there may be arranged magnets for preventing rotation of the turbine ring. The turbine ring may pivot slightly back and forth, but is prevented from performing a complete rotation or revolution.

[0221] Alternatively, the turbine ring is braked, so that it may rotate with a small second rotation rate. The brake energy may be collected by a generator.

[0222] Fig. 40c is a view taken according to lines C - C in Fig. 40a. Fig 40c discloses the turbine ring with the U-shaped turbine channels. The nozzles 409 (382q) from a plurality of (post)evaporation channels are directed partially tangential and partially axial towards inlets 404 (392n) to the U-shaped turbine channels. The heat medium from the nozzles flows in the U-shaped channels and leaves the U-shaped channels via outlets 405 (392o) into the inlets 402 (392p) to the condensation channels, possibly via an optional space 407 (392t).

[0223] Since the heat medium exits the nozzles 409 with a high flow rate, a torque is generated on the evaporator body (first body) directed downward in Fig. 40c. This torque will cause the first body to rotate with a high first rotation rate.

[0224] The heat medium entering (404) the turbine channels will generate a torque directed upwards in Fig. 40c. Consequently, the turbine ring will tend to rotate in an opposite direction relative to the evaporator body (first body).

[0225] The turbine ring is prevented from rotation by the inertia body 406, which means that the inertia body is displaced slightly in the direction upwards in Fig 40c, which is clock-wise in Fig. 40d. However, the gravity (acting upwards in Fig. 40d) will counteract further rotation in the clock-wise direction. There may be a locking device (not shown) preventing the inertia mass from rotating more than 90° clock-wise, as seen according to Fig. 40d. Consequently, the turbine ring may pivot up to 90° but cannot perform a complete revolution, i.e. the turbine ring cannot rotate.

[0226] The turbine ring may also be prevented from rotation, but allowing small pivoting, by means of a magnet device.

[0227] The turbine ring is prevented from rotation without influencing upon the first rotating body.

[0228] In some embodiments, there is a relationship between the rotation rate of the first body and the rotation rate of the second body in that the faster the first body rotates, the slower the second body rotates and vice versa. Since it is desired to maximize the centripetal forces of the first body pressure channels, it is an advantage that the first body rotates with a high rotation rate and the second body rotates with a small rotation rate, and also zero rotation rate. In this manner, the centripetal operation of the evaporator pressure channels is maximized.

[0229] The second body may rotate with a slow rotation rate, which drives a generator, which (heavily) brakes the second body (turbine).

[0230] A generator may be arranged at the first rotation body for deriving electric power from the first rotation body. This is because too high rotation rate of the first body may cause excessive losses in the device. The generator slows down the rotation rate of the first body, and delivers electric energy to the surroundings.

[0231] Moreover, the system is optimized for a specific rotation rate and the system is operated for achieving such optimized rotation rate.

[0232] Alternatively, the rotation of the first body and the rotation axis may be used for providing mechanical energy for driving any mechanical device in the surroundings.

[0233] The second rotating body may drive the rotation of the first rotating body. This may be accomplished by deriving electric power by a generator from a small rotation of the second body, which drives an electric motor of the first rotating body. The electric motor may also operate as a generator in other embodiments.

[0234] Alternatively or additionally, there may be arranged a mechanical power transmission device, that drives the first rotation body by the second rotating body.

[0235] The transmission device may be a gearbox having gear wheels having a desired rotation ratio, such as 1:3, 1:5, 1:10, 1:50, 1:100, 1:200, 1:500, 1:1000 or even larger. The first rotating body rotates with a larger rotation rate than the second rotation body. The arrangement of the transmission device may facilitate the operation and control of the system and device.

[0236] The transmission device may also be a belt gear box having rollers generating the transmission rates. The transmission device may have positive or negative transmission rates, i.e. the first body may rotate in the same direction or the opposite direction with reference to the second rotating body. In the embodiment of Fig. 40c, the rotations normally are in opposite directions, but there exist conditions, in which the rotation in Fig. 40c may be in the same direction.

[0237] Fig. 39a discloses the condensation portion 395 also attached to the first rotating body. The condensation portion comprises an inlet 392p (402) arranged opposite to the outlet 392q of the turbine ring. The inlet is directed partly tangentially in a direction opposite to the outlet as shown in Fig. 40c.

[0238] A spiral shaped condensation channel 392r extends from the inlet 392p and is substantially parallel with the symmetry axis 391, but may have a small slope. The heat medium flowing in the condensation channel 393r initially has a higher flow rate than the condensation channel and this motion energy may be transferred to the walls of the condensation channel.

[0239] There may be a plurality of condensation channels supported by several fins 393h. The fins also serves to cool the heat medium in the condensation channels. A heat sink may be arranged, for example adjacent the central shaft (or elsewhere), and heat may be transferred from the condensation channels to the heat sink.

[0240] There may optionally be arranged a relaxation chamber 393i, in which the condensed heat medium in liquid phase may be collected. The relaxation chamber comprises several flanges, which may be non-rotating by being arranged at bearings 393j.

[0241] Finally, the heat medium is transferred from the condensation channels to the inlet of the evaporation device, for example in an axial channel 393a.

[0242] Fig. 41a discloses the heat transformer according to Fig. 39a, comprising a rotating axis 411, supported by bearings 412 and 413. When the axis rotates, critical rotational rates may occur, in which the rotating axis vibrates. Such vibrations may be counteracted by careful balancing of the components, for example the flanges 414. Weights may be added or removed at critical positions. In addition, balancing weights 415 may be added to the rotation axis as shown in Fig. 41b. Such balancing weights may be added at specific positions along the rotation axis, as indicated by broken lines 416a, 416b, 416c, 416d, 416e, 416f and 416g. Another embodiment of balancing weights is shown in Fig. 41c, in which free balancing balls 417 or small items are arranged in a ring-shaped or toroid-shaped space 418 attached to the rotation axis in specific positions along the axis.

[0243] Fig. 42a discloses a heat transformer 421 according to Fig. 39a and a heat storage container 422 connected to the heat transformer, both being arranged on a movable platform 423, for example a ship or a train. The movable platform may be transported to a place with inexpensive heat energy, which is loaded into the heat storage container 422, which may be a large volume of oil. Then the movable platform may be relocated to a place needing electric energy or other power, and the transformer may be operated driven by the energy loaded into the heat storage container. Fig. 43b discloses that the heat storage container 422 is provided with a connection and disconnection device 424. The heat storage container 422 may be arranged on a separate movable platform, which transports the heat storage container 422 to a place with inexpensive energy, which is loaded into the heat storage container, whereupon the heat storage container is transported back to the heat transformer and is connected to the heat transformer for producing electricity or other power required. The heat transformer may be relocated when needed.

[0244] Fig. 43a discloses that the movable axis 431 may pass inside a support 432 with a small space 433. If there is no relative movement between the axis and the support, the space 433 may be filled with a permanent sealing material 434. The permanent sealing material may be an elastic material 435 as shown in Fig. 43c.

[0245] In the claims, the term "comprises / comprising" does not exclude the presence of other elements or steps. Furthermore, although individually listed, a plurality of means, elements or method steps may be implemented by e.g. a single unit. Additionally, although individual features may be included in different claims or embodiments, these may possibly advantageously be combined, and the inclusion in different claims does not imply that a combination of features is not feasible and / or advantageous. In addition, singular references do not exclude a plurality. The terms "a", "an", “first”, “second” etc. do not preclude a plurality. Reference signs in the claims are provided merely as a clarifying example and shall not be construed as limiting the scope of the claims in any way.

[0246] Although the present invention has been described above with reference to specific embodiment, it is not intended to be limited to the specific form set forth herein. Rather, the invention is limited only by the accompanying claims and other embodiments than those specified above are equally possible within the scope of these appended claims.

Claims

1. CLAIMS1. A system for providing mechanical and / or electric power from heat power, comprising:3.a cooling path (12b, 364’) for cooling a heat medium in the cooling path by a cooling power source (1 a, 14b) for condensing the heat medium;4.a heating path (12d, 364) for heating heat medium by a heating power source (Ila, 1 lb) for evaporate the heat medium;5.a pressurizing path (12c, 363) for increasing pressure in heat medium of the heating path relative to heat medium of the cooling path, wherein the heat medium in the pressurizing path is in a liquid state;6.a power path (12a) for deriving mechanical power from heat medium from the heating path to the cooling path, wherein the heat medium in the power path is in a gaseous state;7.said cooling path, pressurizing path, heating path and power path being connected in a circulation circuit comprising the heat medium circulating in the circuit, wherein the circulation circuit is arranged in a closed body (56), so that no heat medium is able to escape from the closed body;8.wherein the pressurizing path and at least a part of the heating path and at least a part of the cooling path being arranged in a first rotating body (122a), which rotates at a first rotation rate around a rotational axis (91a) for generating pressures in the heat medium by centripetal forces; and9.wherein the power path comprises turbine channels, which are arranged in a second rotating body (122b), which rotates at a second rotation rate around the rotational axis.

2. The system according to claim 1, wherein the second rotation rate is smaller than the first rotation rate, for example by braking the rotation of the second rotating body, such as by a generator.

3. The system according to claim 1 or 2, wherein the rotation of the second body is in a direction opposite relative to the rotation of the first body.

4. The system according to claim 1, 2 or 3, wherein the second rotate rate is substantially zero, for example by maintaining the second rotating body still in relation to the rotational axis so that it does not rotate.

5. The system according to any one of the previous claims, wherein the heating path comprises an evaporation channel (364), which extends from an outlet (363 a) of thepressurizing channel to an inlet (364c) of the turbine channels, wherein the evaporation channel comprises:14.a first portion (363 a) adjacent the outlet of the pressurizing channel, in which the heat medium is in a liquid phase,15.a second portion (364e) in which the heat medium is in a mixed gaseous and liquid phase, and16.a third portion(364d) in which the heat medium is in a gaseous phase.

6. The system according to claim 5, wherein: the evaporation channel is inclined (366) so that there is a first distance from the rotational axis adjacent an outlet from the pressurizing channel and there is a second distance from the rotational axis adjacent an inlet to the power path, whereby the first distance is larger than the second distance.

7. The system according any one of the previous claims, wherein the cooling path comprises a condensation channel (364’), which extends from an outlet (364c’) of the power path to an inlet (363a’) of the pressurizing path (363), wherein the condensation channel comprises:19.a first portion (364d’) adjacent the outlet of the power path, in which the heat medium is in a gaseous phase,20.a second portion (364b’) in which the heat medium is in a mixed gaseous and liquid phase, and21.a third portion(363a’) in which the heat medium is in a liquid phase, adjacent an inlet (363a’) to the pressurizing path.

8. The system according to claim 7, wherein the condensation channel is inclined (366’) so that there is a third distance from the rotational axis adjacent an outlet of the power path and there is a fourth distance from the rotational axis adjacent an inlet to the pressurizing path, whereby the fourth distance is larger than the third distance.

9. The system according to any one of the previous claims, wherein the first rotating body (122a) performs a transformation of the heat medium, initially in a gas phase at low pressure and low temperature, to a heat medium eventually in gas phase at high pressure and high temperature.

10. The system according to claim 9, wherein the transformation takes place by converting the heat medium, initially in a gas phase at low pressure and low temperature, to a liquid phase by condensing the heat medium by removing heat energy from the heat medium,to a high pressure by exposing the liquid heat medium for centrifugal forces in the pressurizing path,25.to a high temperature by evaporating the heat medium by supplying heat energy to the heat medium.

11. The system according to any one of the previous claims, wherein:27.the first rotating body comprises a plurality of evaporation channels and a plurality of condensation channels, and wherein28.the second rotating body comprises a plurality of turbine channels,29.whereby heat medium is transferred from the first rotating body to the second rotating body and vice versa, via interfaces (124e, 124g, 124i, 124k) which rotate in relation to each other.

12. The system according to any one of the previous claims, wherein the second rotating body (122b) is fully enclosed in the first rotating body (122a).

13. The system according to claim 12, wherein the second rotating body (122b) is arranged in a circular recess (122d) of the first rotating body (122a).

14. The system according to any one of the previous claims, wherein the system is operated as a heat pump, in which the pressurizing path comprises a compressor device in a rotating body, which is driven by mechanical power, and the power path comprising an expanding device in another rotating body.

15. The system according to any one of the previous claims, wherein the system is operated as a heat pump, in which the power part is replaced by a compressor device and the pressurizing part is replaced by an expanding device.

16. The system according to any one of the previous claims, wherein the rotation of the first body is driven by the second body.

17. The system according to claim 16, wherein the second body rotates at a second rotation rate and the first body rotates at a first rotation rate and the ratio between the first rotation rate and the second rotation rate is constant.

18. The system according to claim 17, wherein a mechanical gear device is arranged between the first rotation body and the second rotation body, wherein the gear device has fixed ratio of for example 1:3, 1:5, 1:10, 1:50, 1:100, 1:200, 1:500, 1:1000 or even larger, between the second rotation rate and the first rotation rate.

19. The system according to claim 16, 17 or 18, wherein the first rotation rate is in a direction opposite the second rotation rate.

20. The system according to any one of the previous claims, wherein the circulation circuit of the heat medium is arranged according to a Rankine cycle.

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