Supercritical CO2 generation system for parallel recuperative type

Patent metadata

Field	Value
Publication number	US-10371015-B2
Application number	US-201715698436-A
Country	US
Kind code	B2
Filing date	Sep 7, 2017
Priority date	Nov 24, 2016
Publication date	Aug 6, 2019
Grant date	Aug 6, 2019

Abstract

A supercritical CO2 generation system for a parallel recuperative type capable of improving generation efficiency and saving costs is disclosed. According to the supercritical CO2 generation system according to the exemplary embodiment, a compression ratio of a turbine can be increased by arranging recuperators in parallel, thereby maximizing work of the turbine.

First claim

What is claimed is:

1. A supercritical CO 2 generation system comprising:
a compressor compressing a working fluid;
a pre-cooler for cooling the working fluid and supplying pre-cooled working fluid to the compressor;
a heat exchanger unit including first and second heaters configured to heat the working fluid;
first and second turbines respectively driven by the working fluid; and
a recuperator unit including a first recuperator and a second recuperator installed in parallel to each other such that the working fluids cooled by passing through the first and second recuperators are mixed with each other at a downstream side of the recuperator unit and supplied to the pre-cooler, the recuperator unit exchanging heat between the working fluid having passed through the first and second turbines and the working fluid having passed through the compressor to cool the working fluid having passed through the first and second turbines,
wherein the working fluids having passed through the second heater and the second recuperator, respectively, are mixed at an upstream side of the first heater, and
wherein the mixed working fluids are heated by the first heater and then supplied to the first turbine.

2. The supercritical CO 2 generation system of claim 1 , wherein the working fluid having passed through the compressor is branched to the heat exchanger unit and the recuperator unit from a downstream side of the compressor, respectively.

3. The supercritical CO 2 generation system of claim 1 ,
wherein the working fluid having passed through the first turbine is transmitted to the first recuperator to be cooled, and
wherein the working fluid having passed through the second turbine is transmitted to the second recuperator to be cooled.

4. The supercritical CO 2 generation system of claim 1 ,
wherein the first heater is arranged on a high temperature side of the system and the second heater is arranged on a low temperature side of the system,
wherein the first recuperator includes a high temperature recuperator and the second recuperator includes a low temperature recuperator, and
wherein the working fluid branched from a downstream side of the compressor is transmitted to the second heater and the first and second recuperators, respectively.

5. The supercritical CO 2 generation system of claim 1 , wherein the working fluid transmitted to the first recuperator exchanges heat with the working fluid having passed through the first turbine to be heated and then is supplied to the second turbine.

6. The supercritical CO 2 generation system of claim 1 ,
wherein the first turbine is arranged on a high pressure side of the system, and the second turbine is arranged on a low pressure side of the system, and
wherein the working fluid is supplied to the first turbine at a flow rate greater than that of the working fluid supplied to the second turbine.

7. The supercritical CO 2 generation system of claim 6 , wherein the flow rate of the working fluid supplied to the first turbine is a sum of the flow rates of the working fluids supplied to the second heater and the second recuperator.

8. The supercritical CO 2 generation system of claim 1 , wherein each of the first and second heaters and the first and second recuperators includes a heat exchanger having a high temperature operation region and a low temperature operation region, and wherein each heat exchanger is controlled to keep constant a temperature difference between the high and low temperature operation regions.

9. The supercritical CO 2 generation system of claim 2 , wherein the working fluid branched to the recuperator unit from the downstream side of the compressor is branched to the first and second recuperators, respectively.

10. A supercritical CO 2 generation system comprising:
a compressor compressing a working fluid;
a low temperature heater and a high temperature heater supplied heat from an external heat source to heat the working fluid;
a high pressure turbine driven by the working fluid heated by passing through the low temperature heater and the high temperature heater;
a low temperature recuperator and a high temperature recuperator installed in parallel to each other and configured to recuperate the working fluid passing through the compressor;
a low pressure turbine driven by the working fluid recuperated by the high temperature recuperator;
a pre-cooler cooling the working fluid primarily cooled by the high temperature recuperator and the low temperature recuperator and supplying the pre-cooled working fluid to the compressor; and
a separator branching the working fluid passing through the compressor to the low temperature heater, the low temperature recuperator and the high temperature recuperator, respectively,
wherein the working fluids having passed through the low temperature heater and the high temperature recuperator, respectively, are mixed at an upstream side of the high temperature heater and then are heated by the high temperature heater to be supplied to the high pressure turbine.

11. A supercritical CO 2 generation system comprising:
a compressor compressing a working fluid;
a low temperature heater and a high temperature heater supplied heat from an external heat source to heat the working fluid;
a high pressure turbine driven by the working fluid heated by passing through the low temperature heater and the high temperature heater;
a low temperature recuperator and a high temperature recuperator installed in parallel to each other and configured to recuperate the working fluid passing through the compressor;
a low pressure turbine driven by the working fluid recuperated by the high temperature recuperator;
a pre-cooler cooling the working fluid primarily cooled by the high temperature recuperator and the low temperature recuperator and supplying the pre-cooled working fluid to the compressor;
a first separator branching the working fluid passing through the compressor to the low temperature heater, the low temperature recuperator, and the high temperature recuperator, respectively; and
a second separator branching the working fluid branched to the low temperature recuperator and the high temperature recuperator from the first separator, respectively,
wherein the working fluids having passed through the low temperature heater and the high temperature recuperator, respectively, are mixed at an upstream side of the high temperature heater and then are heated by the high temperature heater to be supplied to the high pressure turbine.

12. The supercritical CO 2 generation system of claim 11 , wherein the working fluid having passed through the high pressure turbine is transmitted to the high temperature recuperator to be cooled and the working fluid having passed through the low pressure turbine is transmitted to the low temperature recuperator to be cooled.

13. The supercritical CO 2 generation system of claim 11 , wherein the working fluid branched from a downstream side of the compressor is transmitted to the low temperature heater and the low temperature and high temperature recuperators, respectively.

14. The supercritical CO 2 generation system of claim 13 , wherein the working fluid transmitted to the high temperature recuperator exchanges heat with the working fluid having passed through the high pressure turbine to be heated and then is supplied to the low pressure turbine.

15. The supercritical CO 2 generation system of claim 14 , wherein the working fluid is supplied to the high pressure turbine at a flow rate greater than that of the working fluid supplied to the low pressure turbine.

Assignees

• Doosan Heavy Ind & Construction Co Ltd
• Doosan Heavy Ind Constr Co Ltd

Inventors

• Jeong Cheol Rae
• Kang Seung Gyu
• Hwang Jeong Ho
• Bak Byoung Gu
• Lee Eung Chan

Classifications

• F01D15/10

  Adaptations for driving, or combinations with, electric generators · CPC title

• F01K25/103 Primary

  Carbon dioxide (F01K25/065 takes precedence) · CPC title

• F01K13/006

  Auxiliaries or details not otherwise provided for · CPC title

• F01K21/00

  Steam engine plants not otherwise provided for · CPC title