Abstract

The compressor is a key component in the supercritical carbon dioxide (SCO2) Brayton cycle. In this paper, the authors designed a series of supercritical CO2 compressors with different parameters. These compressors are designed for 100 MWe, 10 MWe and 1 MWe scale power systems, respectively. For the 100 MWe SCO2 Brayton cycle, an axial compressor has been designed by the Smith chart to test whether an axial compressor is suitable for the SCO2 Brayton cycle. Using a specific speed and a specific diameter, the remaining two compressors were designed as centrifugal compressors with different pressure ratios to examine whether models used for air in the past are applicable to SCO2. All compressors were generated and analyzed with internal MATLAB programs coupled with the NIST REFPROP database. Finally, the design results are all checked by numerical simulations due to the lack of reliable experimental data. Research has found that in order to meet the de Haller stall criterion, axial compressors require a considerable number of stages, which introduces many additional problems. Thus, a centrifugal compressor is more suitable for the SCO2 Brayton cycle, even for a 100 MWe scale system. For the performance prediction model of a centrifugal compressor, the stall predictions are compared with steady numerical calculation, which indicates that past stall criteria may also be suitable for SCO2 compressors, but more validations are needed. However, the accuracy of original loss models is found to be inadequate, particularly for lower flow and higher pressure ratio cases. Deviations may be attributed to the underestimation of clearance loss according to the result of steady simulation. A modified model is adopted which can improve the precision to a certain extent, but more general and reasonable loss models are needed to improve design accuracy in the future.

Highlights

  • The concept of the supercritical CO2 Brayton cycle was first proposed in the 1960s [1,2], but research progressed slowly at that time for various reasons

  • The design method for centrifugal compressors is based on the specific speed and specific diameter which are commonly used by industry for radial turbomachinery

  • Since the external losses cannot be considered in the CFD calculation, only the internal loss models are added into 1-D code

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Summary

Introduction

The concept of the supercritical CO2 Brayton cycle was first proposed in the 1960s [1,2], but research progressed slowly at that time for various reasons. In 2014, Monje and his colleagues applied the Aungier’s one-dimensional model to design a compressor of the 10 MW central receiver type for solar plants [17] Results of their 1-D model are in good agreement with the simulation of Fluent software. These experimental results have verified the feasibility of the one-dimensional design method of the SCO2 compressor and pointed out that windage loss is an important cause of low cycle efficiency. A series of mass flow rate situations will be studied to find out the limitations of the conventional models

Axial-Flow Compressor Design
Mass Flow Rate Estimation
Centrifugal Compressor Design
Models for Centrifugal Compressor
A Centrifugal Compressor for a 10 MWe System
10. Centrifugal Compressor for a 1 MWe System
11. Simplified Model
Findings
12. Conclusions

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