POWER RECOVERY AND ENERGY CONVERSION SYSTEMS AND METHODS OF USING SAME

• US 20070245733A1
• Filed: 10/05/2005
• Published: 10/25/2007
• Est. Priority Date: 10/05/2005
• Status: Active Grant

• Current Assignee: TAS Energy Incorporated
• Original Assignee: Tas Limited
• Inventors: Penton, John, Pierson, Tom
• Granted Patent: US 7,287,381 B1
• Time in Patent Office: Days
• US Class Current: 60/651
• CPC Class Codes: F01K 25/08 using special vapours

Abstract

In various illustrative examples, the system may include heat recovery heat exchangers, one or more turbines or expanders, a desuperheater heat exchanger, a condenser heat exchanger, a separator, an accumulator, and a liquid circulating pump, etc. In one example, a bypass desuperheater control valve may be employed. The system comprises a first heat exchanger adapted to receive a heating stream from a heat source after passing through a second heat exchanger and a second portion of a working fluid, wherein, the second portion of working fluid is converted to a hot liquid via heat transfer. An economizer heat exchanger that is adapted to receive a first portion of the working fluid and the hot discharge vapor from at least one turbine may also be provided. The first and second portions of the working fluid are recombined in a first flow mixer after passing through the economizer heat exchanger and first heat exchanger, respectively. A second heat exchanger is provided that receives the working fluid from the first flow mixer and a hot heating stream from a heat source and convert the working fluid to a hot vapor. The hot vapor from the second heat exchanger is supplied to at least one turbine after passing through a separator designed to insure no liquid enters the said at least one turbine or expander. The hot, high pressure vapor is expanded in the turbine to produce mechanical power on a shaft and is discharged as a hot, low pressure vapor.

Claims

1. A system, comprising:

a flow divider adapted to receive a working fluid and divide said working fluid into at least first and second portions;

a first heat exchanger adapted to receive a hot heating stream from a heat source after said hot heating stream passes through a second heat exchanger and said first portion of a working fluid, wherein, when the first portion of said working fluid is passed through the first heat exchanger, the first portion of said working fluid is converted to a first hot liquid stream via heat transfer with said hot heating stream from said heat source;

an economizer heat exchanger adapted to receive a hot vapor discharged from at least one turbine and said second portion of said working fluid, wherein, when the second portion of said working fluid is passed through the economizer heat exchanger, the second portion of said working fluid is converted to a second hot liquid stream via heat transfer with said hot vapor discharged from said at least one turbine;

a first flow mixer adapted to receive at least said first hot liquid stream and said second hot liquid stream and discharge said at least first hot liquid stream and said second hot liquid stream as a combined hot liquid working fluid;

a second heat exchanger adapted to receive a hot heating stream from a heat source and said combined hot liquid working fluid, wherein, when the combined hot liquid working fluid is passed through the second heat exchanger, the combined hot liquid working fluid is converted to a hot vapor via heat transfer with said hot heating stream from said heat source;

at least one separator adapted to receive said hot vapor from said second heat exchanger and separate said hot vapor into its liquid and gaseous phases for the purpose of preventing liquid from entering said at least one turbine;

at least one liquid control valve to relieve said liquid from said at least one separator, wherein said at least one turbine is adapted to receive said hot vapor from said separator and produce rotational, mechanical power at a shaft that is adapted to transmit said power to at least one device adapted to receive said power;

a second flow mixer that is adapted to receive and combine said vapor discharged from said at least one turbine after said vapor passes through said economizer heat exchanger and a fluid from the discharge of said liquid control valve into a single stream to be condensed;

a condenser heat exchanger that is adapted to receive said single stream to be condensed and a cooling fluid, wherein the temperature of said single stream to be condensed is reduced via heat transfer with said cooling fluid;

a liquid accumulator that is adapted to receive said cooled working fluid, provide storage for said cooled working fluid, and provide a surge volume for said system; and

,

at least one pump that is adapted to circulate said cooled working fluid to said first heat exchanger and said economizer heat exchanger via said flow divider.

2. The system of claim 1 wherein said working fluid enters said second heat exchanger as a supercritical liquid and via heat transfer with the fluid from the heat source changes state from a supercritical liquid to a supercritical vapor.

3. The system of claim 1 wherein said cooling fluid for said condenser heat exchanger comprises at least one of a liquid and a gas.

4. The system of claim 1 wherein said cooling fluid for said condenser heat exchanger is a partially or fully vaporized liquid as it passes through said condenser heat exchanger.

5. The system of claim 1 wherein said condenser heat exchanger is adapted to condense the exhaust vapor from said at least one turbine or expander to a liquid at a temperature between approximately 0-250°

F.

6. The system of claim 1, wherein said working fluid is R-123 or one of its derivatives and said fluid from said heat source has a temperature of between approximately 450-1500°

F., the maximum temperature of the working fluid is between approximately 363-700°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 550 psia.

7. The system of claim 1, wherein said working fluid is R-134A or one of its derivatives and said fluid from said heat source has a temperature of between approximately 275-1500°

F., the maximum temperature of the working fluid is between approximately 214-650°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 600 psia.

8. The system of claim 1, wherein said working fluid is methyl alcohol (methanol) or one of its derivatives and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 463-963°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 1070 psia.

9. The system of claim 1, wherein said working fluid is bromine and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 592-1092°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 1500 psia.

10. The system of claim 1, wherein said working fluid is carbon tetrachloride and said fluid from said heat source has a temperature of between approximately 600-2500°

F., the maximum temperature of the working fluid is between approximately 542-1042°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 1000 psia.

11. The system of claim 1, wherein said working fluid is ethyl alcohol or one of its derivatives and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 470-970°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 920 psia.

12. The system of claim 1, wherein said working fluid is R-150A and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 482-982°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 730 psia.

13. The system of claim 1, wherein said working fluid is thiophene and said fluid from said heat source has a temperature of between approximately 600-2500°

F., the maximum temperature of the working fluid is between approximately 583-1083°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 730 psia.

14. The system of claim 1, wherein said working fluid is a mixture of hydrocarbons containing ten or fewer carbon atoms per molecule, said fluid from said heat source has a temperature of between approximately 400-2500°

F., the maximum temperature of the working fluid is between approximately 400-1000°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 300 psia.

15. The system of claim 1, wherein said at least one turbine drives at least one electrical generator to produce electrical power.

16. The system of claim 1, wherein said at least one turbine drives at least one compressor.

17. The system of claim 1, wherein said at least one turbine drives said at least one pump.

18. The system of claim 1, wherein said at least one turbine drives at least one electrical generator to produce electrical power and drives said at least one pump.

19. A system, comprising:

a flow divider adapted to receive a working fluid and divide said working fluid into at least three portions;

a first heat exchanger adapted to receive a hot heating stream from a heat source after said hot heating stream passes through a second heat exchanger and a first portion of a working fluid, wherein, when the first portion of said working fluid is passed through the first heat exchanger, the first portion of said working fluid is converted to a first hot liquid stream via heat transfer with said heating stream from said heat source;

an economizer heat exchanger adapted to receive a hot vapor discharged from at least one turbine and a second portion of said working fluid, wherein, when the second portion of said working fluid is passed through the economizer heat exchanger, the second portion of said working fluid is converted to a second hot liquid stream via heat transfer from the heat contained in said hot vapor discharged from at least one turbine;

a bypass desuperheater liquid control valve to regulate the flow of a third portion of said working fluid to a second flow mixer or desuperheater;

a first flow mixer adapted to receive said first hot liquid stream and said second hot liquid stream and discharge said first and second hot liquid streams as a combined hot liquid working fluid stream;

said second heat exchanger being adapted to receive said hot heating stream from said heat source and said combined hot liquid working fluid, wherein, when the combined hot liquid working fluid is passed through the second heat exchanger, the combined hot liquid working fluid is converted to a vapor via heat transfer with said hot heating stream from said heat source;

at least one separator adapted to receive said hot vapor from said second heat exchanger and separate said hot vapor into its liquid and gaseous phases for the purpose of preventing liquid from entering said at least one turbine;

at least one liquid control valve to relieve said liquid from said at least one separator, wherein said at least one turbine is adapted to receive said hot vapor and produce rotational, mechanical power at a shaft that is adapted to transmit said power to at least one device adapted to receive said power;

a second flow mixer that is adapted to receive and combine said vapor discharged from said at least one turbine after said vapor passes through said economizer heat exchanger, a fluid from the discharge of said liquid control valve, and said third portion of the working fluid from said bypass desuperheater liquid control valve into a single stream to be condensed;

a condenser heat exchanger that is adapted to receive said single stream to be condensed and a cooling fluid, wherein the temperature of said single stream to be condensed is reduced via heat transfer with said cooling fluid;

a liquid accumulator that is adapted to receive said cooled working fluid, provide storage for said cooled working fluid, and provide a surge volume for said system; and

,

at least one pump that is adapted to circulate said cooled working fluid to said first heat exchanger, said economizer heat exchanger, and said second fluid mixer or desuperheater via said bypass desuperheater liquid control valve via said flow divider.

20. The system of claim 19, wherein said working fluid enters said second heat exchanger as a supercritical liquid and via heat transfer with the fluid from the heat source changes state from a supercritical liquid to a supercritical vapor.

21. The system of claim 19, wherein said cooling fluid for said condenser heat exchanger comprises at least one of a liquid and a gas.

22. The system of claim 19, wherein said cooling fluid for said condenser heat exchanger is a partially or fully vaporized liquid as it passes through said condenser heat exchanger.

23. The system of claim 19, wherein said condenser heat exchanger is adapted to condense the exhaust vapor from said at least one turbine or expander to a liquid at a temperature between approximately 0-250°

F.

24. The system of claim 19, wherein said working fluid is R-123 or one of its derivatives and said fluid from said heat source has a temperature of between approximately 450-1500°

F., the maximum temperature of the working fluid is between approximately 363-700°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 550 psia.

25. The system of claim 19, wherein said working fluid is R-134A or one of its derivatives and said fluid from said heat source has a temperature of between approximately 275-1500°

F., the maximum temperature of the working fluid is between approximately 214-650°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 600 psia.

26. The system of claim 19, wherein said working fluid is methyl alcohol (methanol) or one of its derivatives and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 463-963°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 1070 psia.

27. The system of claim 19, wherein said working fluid is bromine and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 592-1092°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 1500 psia.

28. The system of claim 19, wherein said working fluid is carbon tetrachloride and said fluid from said heat source has a temperature of between approximately 600-2500°

F., the maximum temperature of the working fluid is between approximately 542-1042°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 1000 psia.

29. The system of claim 19, wherein said working fluid is ethyl alcohol or one of its derivatives and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 470-970°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 920 psia.

30. The system of claim 19, wherein said working fluid is R-150A and said fluid from said heat source has a temperature of between approximately 500-2500°

F., the maximum temperature of the working fluid is between approximately 482-982°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 730 psia.

31. The system of claim 19, wherein said working fluid is thiophene and said fluid from said heat source has a temperature of between approximately 600-2500°

F., the maximum temperature of the working fluid is between approximately 583-1083°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 730 psia.

32. The system of claim 19, wherein said working fluid is a mixture of hydrocarbons containing ten or fewer carbon atoms per molecule, said fluid from said heat source has a temperature of between approximately 400-2500°

F., the maximum temperature of the working fluid is between approximately 400-1000°

F., and wherein said pump is adapted to operate at a discharge pressure greater than approximately 300 psia.

33. The system of claim 19, wherein said at least one turbine drives at least one electrical generator to produce electrical power.

34. The system of claim 19, wherein said at least one turbine drives at least one compressor.

35. The system of claim 19, wherein said at least one turbine drives said at least one pump.

36. The system of claim 19, wherein said at least one turbine drives at least one electrical generator to produce electrical power and drives said at least one pump.