APPARATUS AND METHOD FOR CONVERTING THERMAL ENERGY

Abstract

An apparatus for converting thermal energy into mechanical energy by a cycle, having a heat exchanger, a reservoir for an operating medium, a feed line, a turbine, and a return line having at least one recovery device. To utilize waste heat for the generation of electrical energy, the turbine is embodied as a disc rotor turbine with full condensation of the operating medium, whereby a separate condenser can be eliminated.

Claims

1. An apparatus for converting thermal energy into mechanical energy by a cycle, comprising: a heat exchanger, a reservoir for an operating medium, a feed line, a turbine, and a return line having at least one recovery device, wherein the turbine is embodied as a disc rotor turbine with full condensation of the operating medium, whereby a separate condenser can be eliminated.

2. The apparatus according to claim 1, wherein the disc rotor turbine comprises multiple discs rotatably arranged next to one another on an axle in a casing, and wherein surfaces of the multiple discs are provided with microstructures.

3. The apparatus according to claim 1, wherein the disc rotor turbine comprises multiple discs rotatably arranged next to one another on an axle in a casing, and the casing comprises an inlet nozzle holder having a geometry that enables an injection of the operating medium between the multiple discs.

4. The apparatus according to claim 1, wherein the disc rotor turbine comprises multiple discs rotatably arranged next to one another on an axle in a casing and the casing comprises an inlet nozzle holder having a geometry that enables a generation of a rotating stream of the operating medium.

5. The apparatus according to claim 1, wherein a structure-borne noise measurement is integrated into the disc rotor turbine for identifying laminar and turbulent flow.

6. The apparatus according to claim 1, wherein a valve is provided for regulating a flow rate.

7. The apparatus according to claim 1, wherein the reservoir for the operating medium is connectable to a heat source via a heat exchanger.

8. The apparatus according to claim 1, wherein the operating medium comprises CO.sub.2.

9. The apparatus according to claim 1, wherein the apparatus is designed for a pressure of the operating medium at the disc rotor turbine of more than 74 bar to enable a supercritical state of the operating medium in the turbine.

10. The apparatus according to claim 9, wherein the apparatus is designed for a pressure of the operating medium at the disc rotor turbine of more than 100 bar to enable a supercritical state of the operating medium in the turbine.

11. The apparatus according to claim 1, wherein at least one valve is provided between the turbine and the reservoir, and the recovery device is embodied to generate a chronologically alternating force on the operating medium, in order to generate a pressure vibration in the operating medium.

12. The apparatus according to claim 1, wherein the recovery device is embodied as a resonant tube.

13. The apparatus according to claim 1, wherein the recovery device comprises a spring-loaded, undamped mass.

14. The apparatus according to claim 13, wherein the spring-loaded, undamped mass comprises a piston or a membrane.

15. The apparatus according to claim 1, wherein the recovery device comprises a spring-loaded, damped mass.

16. The apparatus according to claim 15, wherein the spring-loaded, damped mass comprises a piston or a membrane.

17. The apparatus according to claim 1, wherein the recovery device comprises field coils which generate a magnetic field.

18. The apparatus according to claim 17, wherein the field coils are arranged in an interior of a closed volume.

19. The apparatus according to claim 17, wherein the field coils are arranged outside of a closed volume.

20. The apparatus according to claim 1, wherein at least one valve, which is arranged between a turbine outlet and the reservoir, is configured to enable a flow of the operating medium from the turbine outlet to the reservoir and to prevent a flow in the opposite direction.

21. The apparatus according to claim 20, wherein the at least one valve is embodied as a valve without moving parts.

22. The apparatus according to claim 20, wherein the at least one valve comprises a Tesla valve.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0068] The present invention is further described in the detailed description which follows, in reference to the noted plurality of drawings by way of non-limiting examples of exemplary embodiments of the present invention, in which like reference numerals represent similar parts throughout the several views of the drawings, and wherein:

[0069] FIG. 1 shows an apparatus according to the invention;

[0070] FIG. 2 shows an apparatus according to the invention with a resonant tube system;

[0071] FIG. 3 shows an apparatus according to the invention with a spring-loaded, undamped mass;

[0072] FIG. 4 shows an apparatus according to the invention with a spring-loaded and damped mass;

[0073] FIG. 5 shows an apparatus according to the invention with field coils inside a closed volume;

[0074] FIG. 6 shows an apparatus according to the invention with field coils outside a closed volume.

DETAILED DESCRIPTION

[0075] FIG. 1 shows a diagram of an apparatus 1 according to the invention for carrying out a cycle according to the invention, wherein heat is converted into mechanical energy and further into electrical energy.

[0076] The apparatus 1 is essentially composed of a turbine 2, a reservoir 3 for the operating medium, a heat exchanger 4, a feed line 5 between the reservoir 3 and turbine 2 in order to convey an operating medium from the reservoir 3 to the turbine 2, a return line 6 after the turbine 2 in order to convey the operating medium from a turbine outlet back to the reservoir 3, a valve 7 for regulating a flow.

[0077] Furthermore, a pressure sensor 8 is provided with which the valve 7 can be controlled.

[0078] In order to convey the operating medium from the turbine outlet to the reservoir 3, wherein a higher pressure prevails in the reservoir 3 than at the turbine outlet, a recovery device 9 is provided in the return line 6.

[0079] CO.sub.2 is preferably used as an operating medium, since it has a low boiling point. The critical point is at 31? C. and 73.9 bar. For CO.sub.2, a phase transition between liquid and gaseous already occurs at a pressure of approximately 72 bar at a temperature of only 30? C., whereby a phase transition can be utilized for energy absorption and release even with a heat supplied at low temperatures. Thus, the operating medium in the reservoir can be present, for example, at a pressure of 72 bar, wherein waste heat is supplied thereto at a temperature of 40? C. by the heat exchange, wherein the operating medium evaporates, whereupon it is depressurized to a pressure of approximately 64 bar in the turbine, thereby cooling to an ambient temperature of 20? C., for example, and fully condensing, wherein work is outputted via the turbine.

[0080] Alternatively, it can also be provided that the operating medium is present in the reservoir (3) at a pressure of more than 74 bar, for example at approximately 100 bar, and reaches a supercritical state through a supply of heat, from which state it fully condenses to a gaseous state and, simultaneously or subsequently, to a liquid state in the turbine (2).

[0081] With corresponding pressure conditions in the apparatus (1), it can also be provided that an at least partial phase transition of the operating medium to a solid state takes place in the turbine at a temperature of 20? C., for example, so that dry ice particles form which are also unproblematic for the turbine (2) due to the use of a disc rotor turbine. As a result, heat accumulating at a low temperature of only 40? C., for example, can also be utilized to generate electricity.

[0082] Of course, other operating media such as refrigerants can also be used, for example R744 or R134a.

[0083] The heat from a heat source 10 is supplied to the operating medium via a heat exchanger 4 arranged in the reservoir 3. Either primary energy or preferably waste heat, for example from an industrial process, with a temperature of approximately 40? C. can thereby be used. Heat sources 10 with a lower temperature can also be used, however. It is thus especially beneficial that solar energy can also be utilized.

[0084] A disc rotor turbine is used as a turbine 2. This is also known as a boundary-layer turbine 2 or Tesla turbine 2. This disc rotor turbine comprises multiple discs rotatably arranged next to one another on an axle, which are arranged in a casing with side walls, an inlet opening, and an outlet opening. A stream of the operating medium, up to now usually water, is conducted parallel to the discs onto said discs through the inflow opening. Due to an adhesion force, the discs are then set in motion about the axle. The stream is decelerated by a friction. The stream is redirected onto a circular path by the side walls and thereby continues to drive the discs. Since only the bearings of the axle need to have low tolerances and no highly resilient materials are required, the production costs are also low and a long service life can be expected. Because a higher viscosity arises due to the condensation of the operating medium in the turbine 2, the discs are also driven more powerfully as a result. In typical turbines 2 with blades, a condensation would severely damage said blades. The energy extraction then subsequently takes place by a pressure reduction in the operating medium in the turbine 2.

[0085] To control the cycle, pressure and temperature are measured at the turbine outlet in the return line 6 and compared with the pressure and the temperature in the feed line 5. The cycle can thereupon be regulated via a valve 7 arranged in the return line 6 in order to regulate the flow rate. In this manner, a very good load regulation is possible with simultaneously low complexity.

[0086] The operating medium is then supplied to a recovery device 9 after the valve 7, which device is embodied as a pump in this case.

[0087] In the exemplary embodiments illustrated in FIG. 2 through FIG. 6, the recovery device 9 is embodied to set the operating medium in vibration in order to overcome a pressure difference between the turbine outlet and the reservoir 3.

[0088] FIG. 2 shows an apparatus 1 according to the invention with a recovery device 9 embodied as a resonant tube 11. Here, a fluid column of the operating medium can vibrate back and forth in a volume 12 in a pipe-like form, and can thus be in self-resonance, for example, and, in combination with a valve, can therefore overcome the pressure difference between the return line 6 of the turbine 2 and the feed line 5 between the reservoir 3 for the operating medium and the turbine 2. A vibration excitation can, for example, occur by an electromagnetically driven membrane.

[0089] In FIG. 3, a further variant of an apparatus 1 according to the invention is illustrated with a spring-loaded mass 13. Here, using this mass 13, which can be a membrane, for example also a piston, inside a closed volume 12, the vibrations are excited in the operating medium and the operating medium is brought into resonance in the volume, which causes the amplitude to proceed to rise accordingly. In the state of resonance, only a fraction of the excitation energy originally used is required, which leads to an improved efficiency and ensures a particularly efficient transport of the operating medium into the reservoir 3. Here, the closed volume 12 is illustrated as a cylinder in which the mass 13 can vibrate by a spring 14. The vibrations are thereby generated through the use of external energy, for example electromechanical energy.

[0090] FIG. 4 shows an apparatus 1 similar to that illustrated in FIG. 3. Here, however, the mass 13 is hindered from excessive amplitudes, which could have negative effects in the system, by a damper 15. Nevertheless, a pressure difference between the return line 6 of the turbine 2 and the feed line 5 between the reservoir 3 for the operating medium and the turbine 2 can also be overcome easily in this case.

[0091] A further possibility for generating an oscillation is illustrated in FIG. 5. Here, the oscillation is generated by a magnetic fluid which is set in vibration by field coils 16, wherein an alternating electromagnetic field can be generated with the field coils 16.

[0092] To control the flow direction of the operating medium, an additional one-way valve 17 is provided in this case between the valve 7, which is only used here to regulate the flow rate, and the recovery device 9. Alternatively, the flow direction in the apparatus 1 can, of course, also be ensured by a correspondingly embodied valve 7, so that no additional one-way valve 17 is required.

[0093] The one-way valve 17 can, similarly to the valve 7, of course also be provided after the recovery device 9, or between the recovery device 9 and the reservoir 3.

[0094] In the variant according to FIG. 5, the field coils 16 are arranged inside a closed volume 12.

[0095] A similar variant is illustrated in FIG. 6, although here, in contrast to FIG. 5, the field coils 16 are arranged outside the closed volume 12, for example a cylinder. Because the electromagnetic field generated using the field coils 16 can penetrate into the volume 12, a vibration excitement of the magnetic fluid is also possible here.

[0096] With the apparatus 1 described above and the method according to the invention, previously unutilized waste heat can be converted into electrical energy under economically beneficial conditions. For example, industrial waste heat in the temperature range of approximately 40? C. to over 300? C. can thereby be used for conversion into electricity. Solar heat can also be utilized for additional electricity generation. Because the system is inherently closed, it can also be used beneficially and advantageously in remote regions without connection to other power supply lines.