Reducing the load consumed by gas turbine compressor and maximizing turbine mass flow

Abstract

The invention is applicable to industrial gas turbines to reduce the load consumed by the gas turbine compressor and to maximize the turbine mass flow.

Description

CROSS REFERENCE TO RELATED APPLICATION

This application is a national stage entry of PCT/IB2013/054458 filed May 30, 2013, under the International Convention claiming priority over European Union Patent Application No. GC 2012-22727 filed Nov. 6, 2012.

TECHNICAL FIELD

This invention is applicable to industrial gas turbines, and looking into reducing the load consumed by gas turbine COMPRESSOR and maximizing turbine MASS FLOW.

BACKGROUND ART

Improving gas turbines overall efficiency efforts have no limit, and more efforts are taking placed in this field, as this will lead to increase in power generated by gas turbine and reduces fuel consumption for that power.

The main problem avoiding gas turbine overall efficiency improvement is that, air compressor alone consumes most of the power being generated by the turbine. Moreover gas turbine air mass flow cannot be maximized without increasing compressor load consumption.

SUMMARY OF THE INVENTION

From example below and from steam table, it can be seen that air at compressor outlet is superheated. Excess superheating increases compressor load consumption. Therefore reducing compressor air outlet temperature and pressure safely above saturation point before leaving the compressor will reduce compressor load consumption, and will increase gas turbine overall efficiency. This can be done by injection high pressure water relatively cold into air compressor as shown in FIG. 1.

Moreover, gas turbine mass flow rate can be maximized by increasing the temperature of the high pressure water being injected into the compressor as shown in the example. Increase in gas turbine mass flow will further increase gas turbine overall efficiency.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a schematic view of the system of the present invention including a gas turbine main parts, air compressor, combustion chamber, turbine, electrical generator, and high pressure water injection system.

DETAILED DESCRIPTION OF THE DRAWINGS

FIG. 1 shows gas turbine main parts and contains, an air compressor (C), a combustion chamber (C/C), a turbine (T), a temperature adjustment means (E/H) and, a high pressure water injection system (HP Injection water).

For the invention implementation the High-pressure water is introduced into the gas turbine (T). The temperature controlling device (E/H) is connected to the high pressure injection system (HP Injection water). The temperature controlling means controls the temperature of the water being injected into the compressor (C).

FIG. 2 shows the water injection WI high pressure nozzles at and between the blades of the last stages or rows near the outlet of an exemplary turbine Compressor according to one embodiment of the present invention.

DESCRIPTION OF ONE SPECIFIC EXAMPLE OR EMBODIMENT OF THE INVENTION

For a Gas turbine having the followings:—

T1: Compressor-air inlet temperature ° K=283° K

T2: Compressor-air outlet temperature ° K=547° K

P2: compressor air outlet pressure=12 bar

T3: Gas turbine inlet temperature ° K=1258° K

T4: Gas turbine outlet temperature ° K=768° K

nad: adiabatic efficiency

Calculation

1^st: improving gas turbine efficiency by reducing energy consumed by air compressor.

From steam table the following can be extracted:

Water vapor at 12 bar and compressor outlet temperature of (274° C.)=547° K is in the superheated zone.

Saturation Temperature=192° C.=465° K

Degree of Superheat=547−465=82 degree

Therefore compressor air outlet temperature can be reduced by 70 degrees from 547° K to 477° K without de-superheating it.Turbine adiabatic efficiency ηad=1−(T4−T1)/(T3−T2)  (Brighton cycle)

The adiabatic efficiency of the gas turbine ηad=32%

Table below shows the improvement in the adiabatic efficiency from 32% to 38% in relation to drop in compressor outlet temperature from 547° K to 477° K.

	T2 ° K
	547	537	527	517	507	497	487	477
ηad %	32	33	34	35	35	36	37	38

2^nd: Improvement gas turbine overall efficiency by increasing turbine mass flow.

From gas turbine overall thermal efficiency equation where

ηt: Turbine thermal efficiency

Wt: Work done by gas turbine=(Ma+Mf) (h3−h4)

Wc: Load consumed by compressor=Ma (h2−h1)

h: air specific heat

Ma: Air mass flow rate from compressor

Mf: Fuel mass

Mw: Mass of high pressure water injected in compressorηt=[(Wt−Wc)/Wt]×100=1−[Ma(h2−h1)/Ma+Mw+Mf(h3−h4)]×100

From the above equation it can be seen that the increase in injected water mass (Mw) will increase gas turbine overall efficiency.

3^rd: Improving gas turbine overall efficiency by maximizing turbine mass flow.

From fluid mixture equationTaw=(Ma Ta+Mw Tw)/(Ma+Mw)Therefore Mw=Ma(Ta−Taw)/(Taw−Tw)

Where:—

Taw: Required air water mixture temperature=477° K

Ta: Compressor air outlet temperature=547° K

Tw: Injected water temperature=288° K

Mw/Ma=Water mass to air mass

Therefore the required mass of high pressure water injected to reduce compressor outlet temperature from 547° K to 477° K is Mw=0.37 Ma.

The below table shows the increase in injected water mass rate in relation to air mass flow rate corresponding to increase in injected water inlet temperature.

	Tw ° K
	288	300	350	400	450	460	470	475	477
Mw/	0.37	0.40	0.55	0.91	2.59	4.11	10	35	Infinity
Ma

Claims

1. A process for injecting water into the compressor of a gas turbine, comprising the steps of: injecting high pressure water into an outlet of a compressor to provide superheated outlet air, with the temperature and pressure of the outlet air of the compressor is reduced above a saturation point;wherein the high pressure water is injected by using injectors located only at air compressor last stages between stationary blades or only at last rows between stationary blades, and the high pressure nozzles are connected to a high pressure water injection system.

2. A process for injecting water into the compressor of a gas turbine, comprising the steps of: injecting high pressure water into an outlet of a compressor to provide superheated outlet air, with the temperature and pressure of the outlet air of the compressor is reduced above a saturation point; andadjusting the temperature of the injected high pressure water by using a temperature adjusting means; wherein the high pressure water is injected by using injectors located only at air compressor last stages between stationary blades or only at last rows between stationary blades, and the high pressure nozzles are connected to a high pressure water injection system.

3. The process of claim 2, wherein said injecting high pressure water comprises injecting high pressure water within a range of temperature from atmospheric temperature up to compressor outlet air saturation point temperature into said compressor outlet air.