Cooling system for recuperated gas turbine engines

Abstract

A cooling system for cooling hot components of a radial or axial gas turbine engine, which includes a recuperator heat exchanger, provides engine cooling without loss of thermal efficiency. Air flow leaving a compressor is split between a recuperator flow path and a bleed flow path. Air in the bleed flow path flows through the hot parts of the engine, thereby cooling the engine and heating the air. The air in the bleed flow path is combined with the output flow from a combustor and directed into a turbine inlet. A reduction of air flow in the recuperator flow path increases the thermal effectiveness of the recuperator heat exchanger by increasing a ratio of hot and cold flows inside the heat exchanger. The increase in thermal effectiveness of the heat exchanger compensates for energy losses incurred by diverting a portion of the compressor air flow for cooling.

Claims

1. A cooling system for cooling hot components of a recuperated gas turbine engine, the cooling system comprising: a compressor comprising a compressor outlet; a turbine comprising a turbine inlet and a turbine outlet; a recuperator heat exchanger; a recuperator flow path in fluid communication with the compressor outlet and the recuperator heat exchanger; and a bleed flow path in fluid communication with the compressor outlet, the hot components of the recuperated gas turbine engine, and the turbine inlet; wherein the hot components of the recuperated gas turbine engine comprise a turbine volute in fluid communication with the bleed flow path; the bleed flow path injects cooling air into a main inlet of the turbine volute; and wherein a ratio of a mass flow in the bleed flow path to a mass flow in the compressor outlet is equal to a bleed fraction which is greater than or equal to zero and less than or equal to one.

2. The cooling system of claim 1 wherein a mass flow in the recuperator flow path is approximately equal to the mass flow in the compressor outlet minus the mass flow in the bleed flow path.

3. The cooling system of claim 1 wherein the bleed fraction is less than or equal to one-half.

4. The cooling system of claim 1 wherein the bleed flow path and/or recuperator heat exchanger are configured to compensate for energy losses incurred by cooling the hot components.

5. The cooling system of claim 1 wherein the bleed flow path and/or recuperator heat exchanger are configured to maintain substantially constant values of cycle efficiency and/or thermal power of the turbine.

6. The cooling system of claim 1 wherein a thermal effectiveness of the recuperator heat exchanger increases with increasing values of the bleed fraction.

7. The cooling system of claim 1 wherein said turbine volute further comprises a cooling insert in fluid communication with the bleed flow path.

8. The cooling system of claim 7 wherein said cooling insert comprises a gap having a width of between 0.5 mm. and 2.0 mm.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention is described herein, by way of example only, with reference to the accompanying drawings, wherein:

(2) FIG. 1: A cycle flow diagram for a gas turbine, according to an embodiment of the invention.

(3) FIGS. 2(a) and 2(b): Perspective drawings of a turbine volute with a cooling insert, according to an embodiment of the invention.

(4) FIG. 3: A graph showing thermal effectiveness of a cross-flow recuperator heat exchanger.

(5) FIG. 4: A schematic diagram showing gas turbine station points used in thermodynamic calculations.

(6) FIG. 5: Thermodynamic results for an exemplary 40 kW gas turbine with a bleed fraction of zero.

(7) FIG. 6: Thermodynamic results for an exemplary 40 kW gas turbine with a bleed fraction of 0.1.

(8) FIG. 7: Thermodynamic results for an exemplary 40 kW gas turbine with a bleed fraction of 0.2.

(9) FIG. 8: Thermodynamic results for an exemplary 40 kW gas turbine with a bleed fraction of 0.3.

DETAILED DESCRIPTION

(10) FIG. 1 shows a cycle flow diagram for a gas turbine 100, according to an embodiment of the invention. Turbo-shaft 110 mechanically links compressor C to turbine T and to a load. Air leaving compressor C, at temperature T1, is split into a bleed path 130 and a recuperator path 140.

(11) A bleed fraction, denoted by m.sub.0, is defined as the ratio of the mass flow in the bleed path to the total mass flow from the compressor output. The value of m.sub.0 is typically greater than or equal to zero and less than or equal one. In an exemplary embodiment of the invention, the bleed fraction is 0.3. The air flowing in the bleed path increases in temperature from T1 to T4 as it flows around hot components of the turbine engine. The bleed air flow is combined with the output flow of the combustor at temperature T3, and the combined flow arrives at the inlet of turbine T with a temperature T4 which is typically slightly less than T3.

(12) In recuperator path 140, air flows from an outlet of compressor C into a recuperator heat exchanger (HX). The outlet of the compressor may be a diffuser. The mass flow in the recuperator flow path 140 is approximately equal to the mass flow in the compressor outlet minus the mass flow in the bleed flow path. Thus, the mass flow in path 140 is approximately equal to (1−m.sub.0) multiplied by the mass flow from the compressor outlet. The air flow leaving the recuperator and entering the combustor has a temperature T2, which is greater than T1. On leaving the combustor, the air flow temperature is further increased to T3.

(13) Exhaust air from the turbine T, at temperature T5, is used to increase the efficiency of the recuperator heat exchanger HX, before being released to the ambient environment.

(14) FIG. 2(a) is a perspective drawing of a turbine volute 200 with a cooling insert 220, according to an embodiment of the invention. Details of the cooling insert 220 are shown in FIG. 2(b). Arrow 240 shows the direction of cooling air flow, entering volute 200 through a gap 230 having a width typically in a range of 0.5 to 2.0 millimeters (mm).

(15) The following thermodynamic equation relates the value of temperature T3 to the values of temperatures T1 and T4:
m.sub.0*[Cp(T4)*T4−Cp(T1)*T1]=(1−m.sub.0)*[Cp(T3)*T3−Cp(T4)*T4]  Eqn. (1)
All temperatures are in units of degrees Kelvin (° K) and Cp(T) denotes the specific heat of air at constant pressure and temperature T, in units of Joule per kilogram per ° K.

(16) The thermal energy Q required to heat air from temperature T2 to T3 in the combustion chamber is given by:
Q=(1−m.sub.0)*[Cp(T3)*T3−Cp(T2)*T2]  Eqn. (2)

(17) The thermal effectiveness of a cross-flow recuperator heat exchanger, Eff, is given by:
Eff=(T2−T1)/(T5−T1)  Eqn. (3)
The value of Eff also depends on the hot-to-cold flow ratio, denoted by Rhc, and on the number of transfer units, NTU. FIG. 3 shows an exemplary graph of Eff versus NTU, for various ratios Rhc. Note that Eff increases with increasing NTU and with decreasing Rhc.

(18) FIG. 4 is a schematic diagram showing gas turbine station points in an exemplary 40 kW gas turbine according to the present invention. The station point numbers and their locations inside the gas turbine engine are explained in TABLE 1.

(19) TABLE-US-00001 TABLE 1 Station # Turbine Location  2 Compressor outlet  3 Compressor inlet  4 Combustor outlet  5 Turbine outlet  6 Recuperator hot inlet  7 Recuperator hot outlet  8 Exhaust outlet 31 Recuperator cold inlet 35 Recuperator cold outlet 41 Turbine inlet 49 Turbine outlet

(20) Results of exemplary thermodynamic simulations, carried out using GasTurb simulation software developed by Joachim Kurzke and available from GasTurb GmbH (http://www.gasturb.de), are summarized in TABLE 2. In the exemplary simulations, the gas turbine engine provides a nominal output power of 40 kW, and turbine inlet temperature. T4, is approximately 1277 degrees Kelvin (° K). TABLE 2 presents results for values of the bleed fraction, m.sub.0, ranging from 0 to 0.3.

(21) TABLE-US-00002 TABLE 2 Bleed Heat Combustor fraction Cycle Exchanger Outlet m.sub.0 Efficiency Efficiency Temperature ° K. 0 32.0% 83% 1277 0.1 35.2% 88% 1310 0.2 36.4% 91% 1348 0.3 36.3% 91% 1395

(22) Further details of the thermodynamic simulations, corresponding to bleed fractions of m.sub.0=0, 0.1, 0.2, and 0.3, are found in FIGS. 5, 6, 7, and 8, respectively. In each figure, the values of the combustor outlet temperature (T3 in FIG. 1), the recuperator HX thermal effectiveness (Eff), and the overall cycle thermal efficiency are indicated.

(23) Referring to Table 2, the cycle and heat exchanger efficiencies increase monotonically with increasing values of m.sub.0. Most of the improvement is found in going from m.sub.0=0 to m.sub.0=0.2, which accounts for an increase in cycle efficiency from 32.0% to 36.4%, which is a relative increase of (36.4−32.0)/32.0=13.8%. The corresponding relative increase in heat exchanger efficiency is (91−83)/83=9.6%. A further increase of m.sub.0 from 0.2 to 0.3 does not appear to be worthwhile, as there is no further increase in cycle and heat exchanger efficiencies.

(24) Maintaining constant power increases the combustor outlet temperature to 1348° K at the optimal bleed fraction of m.sub.0=0.2. However, after mixing the gas from the combustor with the cooling bleed air, the gas temperature (T4) at the inlet to the turbine drops to 1277° K.

(25) The improved efficiency of the heat exchanger when m.sub.0=0.2 is a consequence of a decrease in the hot-to-cold flow ratio. Rhc, in accordance with the graph in FIG. 3. The improved efficiency compensates for energy losses incurred by use of the cooling air.

(26) In addition, the use of compressor bleeding air for cooling obviates the need for an external ventilation system, which would require additional energy input, as well as the need for isolation of the external envelope of the turbine in order to reduce radiation losses.

(27) Although the invention has been described in conjunction with specific embodiments, it is evident that many alternatives, modifications, and variations will be apparent to those skilled in the art. Accordingly, the invention is intended to embrace all such alternatives, modifications, and variations that fall within the spirit and broad scope of this disclosure.