CA1093320A - Plume reduction system for a gas turbine - Google Patents
Plume reduction system for a gas turbineInfo
- Publication number
- CA1093320A CA1093320A CA329,811A CA329811A CA1093320A CA 1093320 A CA1093320 A CA 1093320A CA 329811 A CA329811 A CA 329811A CA 1093320 A CA1093320 A CA 1093320A
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- Canada
- Prior art keywords
- gas
- air
- turbine
- plume
- heat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
There is described a plume reduction system for a compressor driver gas turbine which drives gas through a pipeline. Another turbine is used in a refrigerant system which has a first heat exchange mechanism for extracting heat from the gas and a second heat exchange mechanism which rejects the heat from the refrigerant system. The heat from the condensing coils of the second heat exchange mechanism is used to warm air at the base of a dry-type cooling tower. Air drawn between the con-densing coils by induction is mixed with the over satura-ted air from the exhaust of the gas turbine. This mixing decreases the dew point of the effluents from the tower.
The effluents are propelled into the atmosphere and form a plume only upon reaching their dew point which is above an altitude at which weather inversion conditions effect the plume.
There is described a plume reduction system for a compressor driver gas turbine which drives gas through a pipeline. Another turbine is used in a refrigerant system which has a first heat exchange mechanism for extracting heat from the gas and a second heat exchange mechanism which rejects the heat from the refrigerant system. The heat from the condensing coils of the second heat exchange mechanism is used to warm air at the base of a dry-type cooling tower. Air drawn between the con-densing coils by induction is mixed with the over satura-ted air from the exhaust of the gas turbine. This mixing decreases the dew point of the effluents from the tower.
The effluents are propelled into the atmosphere and form a plume only upon reaching their dew point which is above an altitude at which weather inversion conditions effect the plume.
Description
~9~ 3 ~
PLUME REDUCTION SYSTEM
FOR A GAS TURBIN~
~s~a~
l~is invention relates to a plume reduction system for a gas turbine. More partlcularly the system is for use in temperate or arc~ic climates.
Compressor gas turbines used to p~p gas exhaust a large quantity of water vapour which is a product of the turbines spent fuel. During certain weather inversion con-ditions such as, for example 9 a change in the local weather pattern~ the exhausked water vapour may create fog condi-tionsc The fog conditions are the result of a plume devel-oping ~hen the temperature o~ the effluents from the gas turbine exhaust falls below dew point. Fog conditions are more prominent in colder climates and may play havoc with the weather in the immediate vicinity of the gas turbine.
Northern pipeline stations which pump gas through a pipeline also make use of some form of refrigeration or cooling after gas compression which prevents the pipeline from becoming warm enough to melt the permafrost and sink~
~uch refrigeration systems may comprise a compressor driven by a gas turblne, a first heat exchanger for extracting heat ' from the pipeline gas and absorbing it into the refri~er-ant gas and a second heat exchanger for rejecting the ex-tracted heat from the refrigerant gas. The second heat exchanger rejects the heat into the atmosphere and the refrigerant gas is coupled via an expansion valve to the first heat exchanger. However, the use o~ a gas turbine in the refrigerant system introduces an additional quan-tity of water vapour to the exhaust which increases the probability of plume formation or fog in the vicinity of the pipeline station during weather inversion conditions.
;~UMIr~ ~7 '~3 ~ O
In accordance with this inven~ion, there is provided a plume reduction system for a gas turbine driv-ing gas through a gas pipeline. The system comprises a refrigerant system includin~ a first hea~ exchange mechan-ism operable with the gas pipeline which cools gas in the pipeline by extracting heat there~rom. The refrigerant system includes a second heat exchange mechanism which rejects the heat from the re~rigerant system. An exhaust means is provided which mixes air with e~fluents ~rom the gas tur~ine to form a mixture and to exhaust the mixture to atmosphere. There is provided means associated with the second heat exchange mechanism for using the rejected heat to wa~m the air to be mixed with the e~fluents in the exhaust means.
The first heat exchanger which extracts heat from the gas in the pipeline slightly reduces the pressure of the gas in the pipeline and it also provides a conven-;ient source of heat which ~ia the second heat exchanger is ~ ' ., -:
' --l,0a333z~
used to warm air entering the exhaust means Hea~ed air entering the exhaust means increases the wa~er holding capacity of this air. The heated air when mixed with the effluents from the gas turbine results in the mixture having a lower dew point than -the dew point of the efflu-ents themselvesq The exhaust means propels the mixture up into the atmosphere where it cools as it rises. Once the mixture cools to its dew point a plume develops, buk the plume of the mixture will develop well above that at which a plume for the effluents alone would develop~ Hence, weather inversion conditions will have reduced effect and the plum~ of the mixture will not be restricted to the immediate vicinity of the system.
In one emkodiment the gas turbine is a regener-ative turbine which includes a vapour cycle to recover waste heat and use the heat to power a vapour or steam turbine. The stea~ turbine is used to compress the fluid in the refrigerant system~
In accordance with another embodiment, the refrigerant compressor is driven by an auxiliary gas tur-bine.
In both embodiments the exhaust from the turbines is directed into a dry-type cooling tower where the warm : gases cause an updraft projecting the effluen~ to a height well above the top of the tower. In accordance with this in~ention, ambient air is directed into the tower to re-duce the dew poin~ of the mixture and this further air is heated by the heat reJected from the heat exchanger of the ~.3~
refrigerat-ion system. Thus ~he gases in ~he tower have a dew point lower than that of the exhaust gase.s alone and are sufficiently hot 9 even with the admixture of ambient air, to ensure that they attain a sufficient velocity and height before cooling to prevent the formation of a plume close to ground level~
An eleckrically driven fan may be added at the base of the tower if required to provide the n~cessary gas velocity.
BRIE~l DESCRIPTION OF THE DRAIr~NGS
The preferred embodiments of the invention will now be described by way of example, with reference ko the accompanying diagrammatic drawings in which:
Figure 1 is a schematic representation of a plume reduction system having two gas turbines;
Figure 2 is a schematic representation of a plume reduction s~stem having a gas turbine with a vapour recov-ery cycle which fuels a vapour turbine; and Figure 3 is a ps~chrome~ric chart~
Figure 1 depicts a plume reduction system for a pipeline station 12, In this embodiment station 12 has a refrigeration compressor gas turbine 14 and a gas com-pressor driver turbine 1~. Gas turbine 1~ compresses the ga~ in pipeline 20 and drives the compressed gas through heat exchanger 22. Heat exchanger 22 extracts heat ~rom the gas in pipeline 20 and transfers it to a ~luid ~lo~nng through line 24 which is coupled to the compressor 26 of compressor gas turbine 140 The fluid in line 24 then enters a second hea~ exchanger comprising coils 36 at the ' ~ , ' base of cooling tower ~2 where the heat is rejected.
I,~Hth the heat rejected the fluid is cooled and flows through line 30 ~nd expansion valve 32 back into the first heat exchanger 22. The refrigerant gas turbine 14, com-pressor 26, heat exchangers 22 and 36, and expansion valve 32 comprise refrigerant system 40. The refrigerant sys~em 40 is required for stations operating in the permafrost conditions so that the pipeline 20 remains cool enough not to rnelt the permafrost and sink. Cooling tower 42 is shown in Figure 1 as a hyperbolic dr~-type cooling tower.
The exhausts from turbines 14 and 1~ induce air flow in the cooling tower as shown by flow path arrows 46 and 4 respectively. The effluents are saturated with water vapour which is produced as a product of the fuel used to fire the turbines. The heated air, shown by arrows, L~
rlses within cooling tower 4~ and is mixed ~th the e~flu-ents of the turbine in the upper portion of the dry~type cooling tower. The air dra~ be~ween coils 36 i3 warmed and its water holding capacity is increased. This air is unsaturated and, when it is mixed with the saturated air of the turbine effluents, the resultant mixture propelled into the atmosphere has a reduced dew point~ The reduced dew point results in the ef~luents rising to greater alt-itude before a plume is formed where the weather in~ersion conditions will not produce the plume in the immediate vicinity of the station As an ex~mple of the operation of this embodi-ment of the invention, assume ~hat the ambient temperature outside the station is about ~10F. Assume the output of ", ~3~.~3~
gas turbine l~ to be in the order of l~0,000 HP for ~/hich a gas turbine would exhaust about 1,019,1~00 lbs of' air/hr at a temperature of 602F in addition to 26,400 lbs of water vapour/hr. Gas turbine 14 would have an output of about 6,000 HP at -10F ambien-t temperature to refrlger-ate the gas passing throuOh coils 22. Gas turbine 14 would then exhaust abou~ 225,000 lbs of air/hr along wi~h ~,600 lbs o~ water vapour/hr. The total amount of water vapour being introduced to the tower ~2 by the turbine would be 31,020 lbs/hr. The total water capaclty of the gas turbines exhausts would be (1,019,L~00 ~ 225,000) x .000~6 = 572 lbs/hr, ~7here the moisture content lbs/lb of water to dry air at -10F and 100% relative humidity (wet bulb) is given at point A of the psychrometric chart (Fig. 3) as .00046. The exhaust from both gas turbines exhausting by flow path 50 IFig. l) will be a point at 602F and .02494 (- 31,020 `0 (1~019,400 ~ 225,000)) lbs of water/lb of dry air. This point is well off to the right of the psychrometric chart, Figure 3t and is not shownO ~owever, ~hen this point is connec~ed by a straight line 75 to point A at 10F, the intersection o~
line 75 with the wet bulb and dew point saturation temp-erature indicates a temperature of 6F or less at which moisture forms as fog or ice ~og~
It should be understood that by a ratio of triangles line 75 at 100F would inter~ect point B which shows that as the exhaust mixes wlth the a~,mosphere ice fog will form when the gases are cooled to ~6F at .0011 lbs of water/lb of air. The amount of ice or vapour ~ , . . . .
3~ 3 3 ~
~7enerated would be (~0011 - .ooo46) (1,019,400 ~ 225,000) = 796 lbs/hr. A gas ~urbine operating at -10F ambient temperature ~Jould have its exhausts turned to ice or vapour when the temperature of its exhausts dropped to 6F. Even if the exhausts were propelled from a 60 foot tower, it would be unlikely that the ex~aust would clear a height o~ 500 feet before the temperature of' the gases in the exhausk fell to 6F and a plume formed. Plume forrnation below 500 feet will result in fog or ice fog conditions in the immediate vicinity of the stakion.
However, for the embodiment sho~ in Figure 1, about 9,545,000 lbs/hr of air i5 in~roduced into ~he base of tower 42 between coils 36. The temperature of the air rises about 50F from -10F to 40F after extracting heat from coils 36. The total amount of air entering the tower then becomes:
225,000 lbs/hr from turbine 14 1,019 9 400 lbs/hr from turbine 16 9,545,000 lbs/hr past coils 36 2010,7~7,000 lbs/hr This amount of air when multiplied by the moist-ure content o~ air at -10F and wet bulb (.00046) approx-imately equals 496 lbs/hr of water vapour. Therefore, the to~al amount o~ water vapour leaving tower 42 is now:
495 lbs/hr whîch enters tower 42 26 9 400 lbs/hr from turbine 1~
4,600 l~s/hr from turbine 14 -: 31,496 lbs/hr water vapour The 9,545,Q00 lbs/hr of air passing between condensing coils 36 in the re~rigera~ion cycle shown by arr~ows 44 of Figure 1 is sho~m as point C on Figure 3. Ilhen ~his , : :
wal~ed air is mixed ~rith the exhaust gases, the resultin~
mixing point is point ~ on Figure 3~ Point ~ is found at about 104F because the cooling tower reduces the temper-ature of the -turbine exhausts to 104F. The introduction of the warm air has raised t:he ~rater holding capacity of the exhaust to about .0032 lbs o~ water/lb of dry air (31,496 . 9~545,000) which gives ~he okher coordina~e for point E. From point E a s~raight line ~0 may be connected to point A at -10F. Since this does not cross the wet bulb and dew point saturation line no plume ~,~11 form and the exhausts from the ~ower will rise well above 500 fee~
before coolingO
Referring now to Figure 2, a system similar to Figure 1 is sho~m except that a h~a-t (energy) recovery cycle is used, The cycle comprises a vapour boiler 52 ~hich feeds ~he l~ater vapour heated by the exhaust of gas turbine 1~ back via line 54 to vapour turbine 16. Vapour turbine 16 drives the refrigerant compressor or other plant a~xiliaries (not shown) to improve the overall plant 20 efficiency. Vapour boiler 52 removes the heat in the exhaust of gas tur~ine 1~ to a temperature of about 1~F.
The amount of water in the exhaust remains constan~ at 26,400 lbs/hr~ On a dry air bases, this is 496 ~ 269400 26, ~96 lbs/hr o~ water9 Then" 26,~46 lbs/hr of water = ,~0264 lbs of water/lb o~ dry air~
l~is point of 1~F and ,0~64 lbs ~rater/lb OI dry air is above the psychrometric chart Figure 3 and is not shown.
,:, , ~ .
. .
.
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Connecting this point with point C is sho1~m by dotted line ~5. Assuming,as before,the air hea~ed by colls 36 equals 9,51~5,000 lbs/hr the conderlsing requirement of the vapour turbine 16 add 3,665,000 lbs/hr of /~0F air at the ba~e of tower 420 The total air to be mixed with the exhaust gases may be given as follows:
9,545,000 lbs/hr coils 36 3,665,000 lbs/hr vapour turbine 16 13,210,000 lbs/hr ~en this air is mixed with the gas tur~ine exhaust~ the final mixing point will be at point F on Figure 3, because a ratio of triangles scales the mixin~ point down do~ted line ~5 to point F at about ~0023 lbs of water/lb of dry air (26~46 ~ 13,210,000). Connecting point F with point A gives dotted line 90 on Fig. 3 which is below the we~
bulb tempera~ure and re~ults in a little or no ice fog being formed.
It should be understood khat without the mixing of the warm condenser air passed between coils 36 ice fog would probably form at approxi~ately +55F down to -10F, because i~ a line were dra~m from a point at 1~F and .026~ lbs water/lb dry air on Fig. 3 to point A, this line would intersect the curved wet bulb saturation temperature line at 55F and -10~ In other words~ the more efficient the gas turbine c~cle becomes the more prone the station will be to ice fog or plume generation.
PLUME REDUCTION SYSTEM
FOR A GAS TURBIN~
~s~a~
l~is invention relates to a plume reduction system for a gas turbine. More partlcularly the system is for use in temperate or arc~ic climates.
Compressor gas turbines used to p~p gas exhaust a large quantity of water vapour which is a product of the turbines spent fuel. During certain weather inversion con-ditions such as, for example 9 a change in the local weather pattern~ the exhausked water vapour may create fog condi-tionsc The fog conditions are the result of a plume devel-oping ~hen the temperature o~ the effluents from the gas turbine exhaust falls below dew point. Fog conditions are more prominent in colder climates and may play havoc with the weather in the immediate vicinity of the gas turbine.
Northern pipeline stations which pump gas through a pipeline also make use of some form of refrigeration or cooling after gas compression which prevents the pipeline from becoming warm enough to melt the permafrost and sink~
~uch refrigeration systems may comprise a compressor driven by a gas turblne, a first heat exchanger for extracting heat ' from the pipeline gas and absorbing it into the refri~er-ant gas and a second heat exchanger for rejecting the ex-tracted heat from the refrigerant gas. The second heat exchanger rejects the heat into the atmosphere and the refrigerant gas is coupled via an expansion valve to the first heat exchanger. However, the use o~ a gas turbine in the refrigerant system introduces an additional quan-tity of water vapour to the exhaust which increases the probability of plume formation or fog in the vicinity of the pipeline station during weather inversion conditions.
;~UMIr~ ~7 '~3 ~ O
In accordance with this inven~ion, there is provided a plume reduction system for a gas turbine driv-ing gas through a gas pipeline. The system comprises a refrigerant system includin~ a first hea~ exchange mechan-ism operable with the gas pipeline which cools gas in the pipeline by extracting heat there~rom. The refrigerant system includes a second heat exchange mechanism which rejects the heat from the re~rigerant system. An exhaust means is provided which mixes air with e~fluents ~rom the gas tur~ine to form a mixture and to exhaust the mixture to atmosphere. There is provided means associated with the second heat exchange mechanism for using the rejected heat to wa~m the air to be mixed with the e~fluents in the exhaust means.
The first heat exchanger which extracts heat from the gas in the pipeline slightly reduces the pressure of the gas in the pipeline and it also provides a conven-;ient source of heat which ~ia the second heat exchanger is ~ ' ., -:
' --l,0a333z~
used to warm air entering the exhaust means Hea~ed air entering the exhaust means increases the wa~er holding capacity of this air. The heated air when mixed with the effluents from the gas turbine results in the mixture having a lower dew point than -the dew point of the efflu-ents themselvesq The exhaust means propels the mixture up into the atmosphere where it cools as it rises. Once the mixture cools to its dew point a plume develops, buk the plume of the mixture will develop well above that at which a plume for the effluents alone would develop~ Hence, weather inversion conditions will have reduced effect and the plum~ of the mixture will not be restricted to the immediate vicinity of the system.
In one emkodiment the gas turbine is a regener-ative turbine which includes a vapour cycle to recover waste heat and use the heat to power a vapour or steam turbine. The stea~ turbine is used to compress the fluid in the refrigerant system~
In accordance with another embodiment, the refrigerant compressor is driven by an auxiliary gas tur-bine.
In both embodiments the exhaust from the turbines is directed into a dry-type cooling tower where the warm : gases cause an updraft projecting the effluen~ to a height well above the top of the tower. In accordance with this in~ention, ambient air is directed into the tower to re-duce the dew poin~ of the mixture and this further air is heated by the heat reJected from the heat exchanger of the ~.3~
refrigerat-ion system. Thus ~he gases in ~he tower have a dew point lower than that of the exhaust gase.s alone and are sufficiently hot 9 even with the admixture of ambient air, to ensure that they attain a sufficient velocity and height before cooling to prevent the formation of a plume close to ground level~
An eleckrically driven fan may be added at the base of the tower if required to provide the n~cessary gas velocity.
BRIE~l DESCRIPTION OF THE DRAIr~NGS
The preferred embodiments of the invention will now be described by way of example, with reference ko the accompanying diagrammatic drawings in which:
Figure 1 is a schematic representation of a plume reduction system having two gas turbines;
Figure 2 is a schematic representation of a plume reduction s~stem having a gas turbine with a vapour recov-ery cycle which fuels a vapour turbine; and Figure 3 is a ps~chrome~ric chart~
Figure 1 depicts a plume reduction system for a pipeline station 12, In this embodiment station 12 has a refrigeration compressor gas turbine 14 and a gas com-pressor driver turbine 1~. Gas turbine 1~ compresses the ga~ in pipeline 20 and drives the compressed gas through heat exchanger 22. Heat exchanger 22 extracts heat ~rom the gas in pipeline 20 and transfers it to a ~luid ~lo~nng through line 24 which is coupled to the compressor 26 of compressor gas turbine 140 The fluid in line 24 then enters a second hea~ exchanger comprising coils 36 at the ' ~ , ' base of cooling tower ~2 where the heat is rejected.
I,~Hth the heat rejected the fluid is cooled and flows through line 30 ~nd expansion valve 32 back into the first heat exchanger 22. The refrigerant gas turbine 14, com-pressor 26, heat exchangers 22 and 36, and expansion valve 32 comprise refrigerant system 40. The refrigerant sys~em 40 is required for stations operating in the permafrost conditions so that the pipeline 20 remains cool enough not to rnelt the permafrost and sink. Cooling tower 42 is shown in Figure 1 as a hyperbolic dr~-type cooling tower.
The exhausts from turbines 14 and 1~ induce air flow in the cooling tower as shown by flow path arrows 46 and 4 respectively. The effluents are saturated with water vapour which is produced as a product of the fuel used to fire the turbines. The heated air, shown by arrows, L~
rlses within cooling tower 4~ and is mixed ~th the e~flu-ents of the turbine in the upper portion of the dry~type cooling tower. The air dra~ be~ween coils 36 i3 warmed and its water holding capacity is increased. This air is unsaturated and, when it is mixed with the saturated air of the turbine effluents, the resultant mixture propelled into the atmosphere has a reduced dew point~ The reduced dew point results in the ef~luents rising to greater alt-itude before a plume is formed where the weather in~ersion conditions will not produce the plume in the immediate vicinity of the station As an ex~mple of the operation of this embodi-ment of the invention, assume ~hat the ambient temperature outside the station is about ~10F. Assume the output of ", ~3~.~3~
gas turbine l~ to be in the order of l~0,000 HP for ~/hich a gas turbine would exhaust about 1,019,1~00 lbs of' air/hr at a temperature of 602F in addition to 26,400 lbs of water vapour/hr. Gas turbine 14 would have an output of about 6,000 HP at -10F ambien-t temperature to refrlger-ate the gas passing throuOh coils 22. Gas turbine 14 would then exhaust abou~ 225,000 lbs of air/hr along wi~h ~,600 lbs o~ water vapour/hr. The total amount of water vapour being introduced to the tower ~2 by the turbine would be 31,020 lbs/hr. The total water capaclty of the gas turbines exhausts would be (1,019,L~00 ~ 225,000) x .000~6 = 572 lbs/hr, ~7here the moisture content lbs/lb of water to dry air at -10F and 100% relative humidity (wet bulb) is given at point A of the psychrometric chart (Fig. 3) as .00046. The exhaust from both gas turbines exhausting by flow path 50 IFig. l) will be a point at 602F and .02494 (- 31,020 `0 (1~019,400 ~ 225,000)) lbs of water/lb of dry air. This point is well off to the right of the psychrometric chart, Figure 3t and is not shownO ~owever, ~hen this point is connec~ed by a straight line 75 to point A at 10F, the intersection o~
line 75 with the wet bulb and dew point saturation temp-erature indicates a temperature of 6F or less at which moisture forms as fog or ice ~og~
It should be understood that by a ratio of triangles line 75 at 100F would inter~ect point B which shows that as the exhaust mixes wlth the a~,mosphere ice fog will form when the gases are cooled to ~6F at .0011 lbs of water/lb of air. The amount of ice or vapour ~ , . . . .
3~ 3 3 ~
~7enerated would be (~0011 - .ooo46) (1,019,400 ~ 225,000) = 796 lbs/hr. A gas ~urbine operating at -10F ambient temperature ~Jould have its exhausts turned to ice or vapour when the temperature of its exhausts dropped to 6F. Even if the exhausts were propelled from a 60 foot tower, it would be unlikely that the ex~aust would clear a height o~ 500 feet before the temperature of' the gases in the exhausk fell to 6F and a plume formed. Plume forrnation below 500 feet will result in fog or ice fog conditions in the immediate vicinity of the stakion.
However, for the embodiment sho~ in Figure 1, about 9,545,000 lbs/hr of air i5 in~roduced into ~he base of tower 42 between coils 36. The temperature of the air rises about 50F from -10F to 40F after extracting heat from coils 36. The total amount of air entering the tower then becomes:
225,000 lbs/hr from turbine 14 1,019 9 400 lbs/hr from turbine 16 9,545,000 lbs/hr past coils 36 2010,7~7,000 lbs/hr This amount of air when multiplied by the moist-ure content o~ air at -10F and wet bulb (.00046) approx-imately equals 496 lbs/hr of water vapour. Therefore, the to~al amount o~ water vapour leaving tower 42 is now:
495 lbs/hr whîch enters tower 42 26 9 400 lbs/hr from turbine 1~
4,600 l~s/hr from turbine 14 -: 31,496 lbs/hr water vapour The 9,545,Q00 lbs/hr of air passing between condensing coils 36 in the re~rigera~ion cycle shown by arr~ows 44 of Figure 1 is sho~m as point C on Figure 3. Ilhen ~his , : :
wal~ed air is mixed ~rith the exhaust gases, the resultin~
mixing point is point ~ on Figure 3~ Point ~ is found at about 104F because the cooling tower reduces the temper-ature of the -turbine exhausts to 104F. The introduction of the warm air has raised t:he ~rater holding capacity of the exhaust to about .0032 lbs o~ water/lb of dry air (31,496 . 9~545,000) which gives ~he okher coordina~e for point E. From point E a s~raight line ~0 may be connected to point A at -10F. Since this does not cross the wet bulb and dew point saturation line no plume ~,~11 form and the exhausts from the ~ower will rise well above 500 fee~
before coolingO
Referring now to Figure 2, a system similar to Figure 1 is sho~m except that a h~a-t (energy) recovery cycle is used, The cycle comprises a vapour boiler 52 ~hich feeds ~he l~ater vapour heated by the exhaust of gas turbine 1~ back via line 54 to vapour turbine 16. Vapour turbine 16 drives the refrigerant compressor or other plant a~xiliaries (not shown) to improve the overall plant 20 efficiency. Vapour boiler 52 removes the heat in the exhaust of gas tur~ine 1~ to a temperature of about 1~F.
The amount of water in the exhaust remains constan~ at 26,400 lbs/hr~ On a dry air bases, this is 496 ~ 269400 26, ~96 lbs/hr o~ water9 Then" 26,~46 lbs/hr of water = ,~0264 lbs of water/lb o~ dry air~
l~is point of 1~F and ,0~64 lbs ~rater/lb OI dry air is above the psychrometric chart Figure 3 and is not shown.
,:, , ~ .
. .
.
g333~2~
Connecting this point with point C is sho1~m by dotted line ~5. Assuming,as before,the air hea~ed by colls 36 equals 9,51~5,000 lbs/hr the conderlsing requirement of the vapour turbine 16 add 3,665,000 lbs/hr of /~0F air at the ba~e of tower 420 The total air to be mixed with the exhaust gases may be given as follows:
9,545,000 lbs/hr coils 36 3,665,000 lbs/hr vapour turbine 16 13,210,000 lbs/hr ~en this air is mixed with the gas tur~ine exhaust~ the final mixing point will be at point F on Figure 3, because a ratio of triangles scales the mixin~ point down do~ted line ~5 to point F at about ~0023 lbs of water/lb of dry air (26~46 ~ 13,210,000). Connecting point F with point A gives dotted line 90 on Fig. 3 which is below the we~
bulb tempera~ure and re~ults in a little or no ice fog being formed.
It should be understood khat without the mixing of the warm condenser air passed between coils 36 ice fog would probably form at approxi~ately +55F down to -10F, because i~ a line were dra~m from a point at 1~F and .026~ lbs water/lb dry air on Fig. 3 to point A, this line would intersect the curved wet bulb saturation temperature line at 55F and -10~ In other words~ the more efficient the gas turbine c~cle becomes the more prone the station will be to ice fog or plume generation.
Claims (6)
1. A plume reduction system for a gas turbine driving gas through a gas pipeline, the system comprising:
a refrigerant system including a first heat exchange mechanism operable with the gas pipeline which cools the gas by extracting heat therefrom;
a second heat exchange mechanism which rejects the heat from the refrigerant system;
an exhaustion means mixing air with effluents from the gas turbine to form a mixture and to exhaust the mixture;
wherein the second heat exchange mechanism uses the rejected heat to warm the air mixed with the effluents in the exhaustion means.
a refrigerant system including a first heat exchange mechanism operable with the gas pipeline which cools the gas by extracting heat therefrom;
a second heat exchange mechanism which rejects the heat from the refrigerant system;
an exhaustion means mixing air with effluents from the gas turbine to form a mixture and to exhaust the mixture;
wherein the second heat exchange mechanism uses the rejected heat to warm the air mixed with the effluents in the exhaustion means.
2. The plume reduction system of claim l wherein the second heat exchange mechanism includes condensing coils placed below the exhaustion means which draws air between the coils by means of induction.
3. The plume reduction system of claim 2 wherein the exhaustion means includes a dry-type cooling tower where the air drawn between the condensing coils is introduced into the base of the tower.
4. The plume reduction system of claim 2 wherein the exhaustion means includes at least one motor-driven fan for inducing air flow through the coils.
5. The plume reduction system of claim 3 or 4 wherein the refrigerant system includes a gas turbine refrigerant compressor driver whose effluents are exhausted into said exhaustion means.
6. The plume reduction system of claim 3 or 4 wherein the gas turbine is a regenerative turbine which includes a vapour recovery cycle to drive a vapour turbine wherein the vapour turbine drives the refrigerant system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA329,811A CA1093320A (en) | 1979-06-14 | 1979-06-14 | Plume reduction system for a gas turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA329,811A CA1093320A (en) | 1979-06-14 | 1979-06-14 | Plume reduction system for a gas turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1093320A true CA1093320A (en) | 1981-01-13 |
Family
ID=4114459
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA329,811A Expired CA1093320A (en) | 1979-06-14 | 1979-06-14 | Plume reduction system for a gas turbine |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1093320A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2483327A (en) * | 2010-08-30 | 2012-03-07 | Bke Comb Controls Co Ltd | Cooling tower plume abatement |
-
1979
- 1979-06-14 CA CA329,811A patent/CA1093320A/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2483327A (en) * | 2010-08-30 | 2012-03-07 | Bke Comb Controls Co Ltd | Cooling tower plume abatement |
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| Date | Code | Title | Description |
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| MKEX | Expiry |