US3796045A - Method and apparatus for increasing power output and/or thermal efficiency of a gas turbine power plant - Google Patents
Method and apparatus for increasing power output and/or thermal efficiency of a gas turbine power plant Download PDFInfo
- Publication number
- US3796045A US3796045A US00162911A US3796045DA US3796045A US 3796045 A US3796045 A US 3796045A US 00162911 A US00162911 A US 00162911A US 3796045D A US3796045D A US 3796045DA US 3796045 A US3796045 A US 3796045A
- Authority
- US
- United States
- Prior art keywords
- gas
- compressor
- turbine
- energy
- gas turbine
- 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 - Lifetime
Links
Images
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
- F02C7/12—Cooling of plants
- F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
- F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
- F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
- F01K27/02—Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat
-
- 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
- F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
- F02C7/10—Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers
Definitions
- the present invention broadly relates to a modified gas turbine cycle for a gas turbine power plant. More particularly, the invention relates to a modified gas turbine cycle wherein the compressor inlet air is superchilled to increase the power output and/or the thermal efficiency of the gas turbine power plant.
- Gas turbine power plants have been used for many years to generate electrical power, particularly during periods when demand for electrical power is greatest.
- the peak demand periods generally occur during the hottest weather when the ambient temperature of the air is high.
- the high temperature of the compressor inlet air at these times significantly reduces the performance of a gas turbine power plant by decreasing the power output and/or thermal efficiency of the turbine. Consequently, during periods of more moderate or normal ambient air temperatures, the power required of the stationary gas turbine may be substantiallybelow that which the turbine is capable of producing at these conditions so that adequate capacity is available when the ambient'temperature of the air is high.
- stationary gas turbine power plants occasionally include various means for modifying the basic gas turbine cycle such as intercoolers, regenerators and recuperators which increase the power output and/or thermal efficiency of the gas turbine power plant.
- intercoolers regenerators and recuperators which increase the power output and/or thermal efficiency of the gas turbine power plant.
- recuperators which increase the power output and/or thermal efficiency of the gas turbine power plant.
- limited use has been made of supercharging the compressor inlet air and cooling the supercharged air to increase the power output of the gas turbine power plant.
- such uses extend only to supercharging with electric motor driven fans and to cooling with evaporative coolers.
- a gas turbine power plant having a basic 7 gas turbine cycle comprising the following steps: compressing the inlet air from the atmosphere in a compressor; heating the compressed air in a combustor; and expanding the heated, compressed air through a turbine.
- the power output and/or the thermal efficiency of the basic gas turbine cycle described above are significantly improved by the additional step of Superchilling the ambient inlet air before it enters the compressor of the gas turbine power plant.
- Superchilling means supercharging the inlet air to the compressor of the gas turbine to increase the pressure thereof to a pressure level moderately greater than the atmospheric pressure by means of a low pressure ratio device and chilling the supercharged inlet air to reduce the temperature thereof to a temperature at least as low as the temperature that could be obtained with an evaporative cooler cooling the supercharged air under ambient conditions then present. Chilling is accomplished by the direct transfer of heat from the supercharged inlet air to the refrigerant of a refrigeration system.
- refrigerant is used herein in a broad and not a restriction senseof the word.
- refrigerant includes all fluids (such as liquids, vapors, and gas) to which heat from the inlet air can be transferred to chill the air.
- the term refrigerant is not limited to those liquids which produce refrigeration by their evaporation from a liquid to a gaseous under reduced pressure.
- the term refrigerant can include liquid, such as a brine, which serves as an intermediate refrigerant between a primary refrigerant used to cool the fluid and the inlet air which is chilled by the direct transfer of heat to the fluid.
- the term refrigerant includes ice which may be used to chill the inlet air directly or to cool an intermediate refrigerant such as a brine.
- the compressor inlet air is preferably supercharged to increase the pressure thereof in accordance with a supercharging pressure ratio in the range of pressure ratios extending from about 1.1 to about 1.75.
- One preferred low pressure ratio device for increasing the pressure of the compressor inlet air is a fan device, for example, a conventional single stage, dual flow centrifugal blower. Supercharging pressure ratios above those obtainable with a single stage fan device can be obtained by two stages of supercharging with such a fan device.
- the lower temperature limit for the chilling of the supercharged gas is a temperature in the vicinity of the temperature at which concomitant chilling of the moisture in the inlet air could form ice accumulations on heat transfer surfaces used to chill the inlet air.
- the temperature of a heat transfer surface used to chill the inlet air should be maintained at a temperature at least as high as the freezing temperature of the moisture in the inlet air.
- a chilling temperature level in the vicinity of the range of temperatures extending from about 35 degrees Fahrenheit to about 40 Fahrenheit is preferred.
- chilling temperatures are possible.
- a means for removing the ice formed on the heat transfer surfaces can be provided thus enabling the compressor inlet air to be chilled to a temperature significantly below the preferred range of temperatures.
- the chilling temperature can also extend considerablybelow the preferred range of temperatures.
- the energy required to chill the inlet air is increased by moisture contained in the air. Since the supercharged inlet air is generally chilled to a temperature below the dew point of the inlet air, moisture in the inlet air in excess of the saturated moisture content of the air at the chilling temperature will be condensed in the chilling means. Accordingly, under humid conditions, the total cooling requirement for the chilling means significantly exceeds the sensible heat cooling that would be required for dry air alone.
- the compressor inlet air can be chilled both before and after the inlet air has been supercharged, or the inlet air can be chilled only after it has been supercharged. Although chilling both before and after supercharging can result in increased capital expenditures, it can be advantageous under certain circumstances.
- Initial chilling of the inlet air reduces the power required to supercharge a given inlet air mass flow rate, and thus reduces the total power required to chill the inlet air before it enters the compressor since the heat input to the inlet air caused by supercharging is reduced.
- the reduction of power to supercharge the inlet air results from the lower temperature of the air entering the supercharging means and from the decreased mass flow rate through the supercharging means caused by the moisture condensed from the inlet air during the initial chilling thereof.
- the reduced power required to charge the inlet air to a given pressure permits a higher supercharge pressure to be obtained when a heat recovery cycle, to be discussed hereinafter, is provided to drive the supercharging means and the chilling means.
- a heat recovery cycle is provided to supply the energy necessary to superchill the compressor inlet air.
- a waste-heat boiler can be provided to generate steam by utilizing the waste-heat in the turbine exhaust gases.
- the steam is subsequently expanded through a first and a second steam turbine.
- the output shaft of the first steam turbine is coupled to drive the low pressure ratio device for supercharging the compressor inlet air.
- the output shaft of the second steam turbine is coupled to drive a compression refrigeration unit for chilling the compressor inlet air.
- Another object is to increase the power output and- /or the thermal efficiency of the gas r turbine power plant when the ambient temperature of the air is high.
- Still another object is to provide a gas turbine power plant wherein ambient inlet air is superchilled before it enters the compressor of the gas turbine for increasing the power output and/or the thermal efficiency of the turbine cycle.
- a further object is to provide a gas turbine power plant wherein waste-heat in the turbine exhaust gases is utilized to supply the energy for superchilling the compressor inlet air.
- a still further object is to provide a gas turbine power plant for driving an electric generator wherein the compressor inlet air is superchilled before it enters the compressor, and the electric generator cooling medium is chilled for simultaneously increasing the power output and/or the thermal efficiency of the gas turbine and the generating capacity of the electric generator.
- a still further object is to provide a gas turbine power plant wherein the waste-heat in the turbine exhaust gases is utilized to supply the energy for superchilling the compressor inlet air and for chilling the electric generator cooling medium.
- FIG. '1 is a schematic diagram of one embodiment of the present invention wherein the compressor inlet air is supercharged and subsequently chilled before the air enters the compression stage of the gas turbine.
- FIG. 2 is a schematic diagram of another embodiment of the present invention wherein the supercharger and chiller are driven by waste-heat energy recovered from the turbine exhaust gases.
- FIG. 3 is a schematic diagram of still another embodiment of the present invention showing selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
- FIG. 4 is a graph showing the power output of the embodiment of the gas turbine power plant illustrated in FIG. 3 as a function of the degree of superchilling of the compressor inlet air.
- FIG. 5 is a graph showing the heat rate of the embodiment of the gas turbine power plant illustrated in FIG. 3 as a function of the degree of superchilling of the compressor inlet air.
- FIG. 6 is a schematic diagram of the embodiment of the gas turbine power plant of FIG. 2 showing selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
- FIG. 7 is a schematic diagram of still another embodiment of the present invention wherein the compressor inlet air is chilled before and after it is supercharged.
- FIG. 8 is a schematic diagram of the embodiment of the gas turbine power plant illustrated in FIG. 2 showing a second set of selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
- FIG. 9 is a schematic diagram of still another embodiment of the present invention showing selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
- FIG. 1 one preferred embodiment of the improved gas turbine power plant is schematically illustrated in FIG. 1.
- the improvement of the present invention is schematically shown in conjunction with-a conventional open-cycle, single shaft gas turbine power plant.
- the gas turbine power plant comprises a compressor 10 for compressing the inlet air from the atmosphere, a combustor 11 for heating the compressed air, and a turbine 12 for expanding the heated, compressed air.
- the turbine 12 is operably coupled to drive the compressor 10 and an electric generator 13 by means of shaft 14.
- the power output and/or the thermal efficiency of the gas turbine described above are significantly increased by superchilling the inlet air before it enters the compressor of the gas turbine.
- a supercharging means 15 which comprises a low pressure ratio device, conveniently shown as a fan 16, driven by an electric motor 17. Inlet air is drawn through the fan 16 thereby increasing the pressure thereof to a pressure level moderately greater than the atmospheric pressure. Once the inlet air has been supercharged, it is ducted to a chilling means 18.
- the chilling means 18 is conveniently shown as a compression refrigeration unit 19 which comprises an evaporator coil 20 in which a liquid refrigerant boils at a low temperature, a compressor 21 driven by an electric motor 22 for raising the pressure and temperature of the gaseous refrigerant from the evaporator coil 20, a condenser 23 in which the refrigerant from the compressor 21 discharges heat to a secondary cooling medium such as water, and an expansion valve 24 for expanding the liquid refrigerant from the high pressure level in the condenser 21 to the low pressure level in the evaporator coil 20.
- the supercharged inlet air is ducted across the evaporator coil 20 where the air is chilled as heat from the air is transferred to the expanded gaseous refrigerant therein.
- the secondary cooling medium is circulated through the coil 25 of the condenser 23 by a circulating pump 26 where the gaseous refrigerant condenses to a liquid and releases heat to the cooling medium.
- the cooling medium subsequently circulates through a cooling coil 27 of a cooling tower 28 where the cooling medium discharges heat to air circulated across the cooling coil 27 by a cooling fan 29, driven by an electric motor 30.
- the ideal gas turbine power plant assumed for some of the comparisonsis a 25 megawatt gas turbine power plant having an ideal gas turbine cycle (Brayton Cycle) rated at a compressor inlet temperature of about F. and a compressor inlet pressure of about 392 inches of water which corresponds to the pressure at about a 1,000 foot elevation.
- the ideal cycle has no inlet or exhaust pressure losses.
- the ideal gas turbine power plant would produce about 25 megawatts (rated power output) at a heat rate of about 12,000 Btu/Kwh LI-IV.
- the performance of the ideal 25 megawatt gas turbine power plant is significantly reduced when the gas turbine is operated under warm weather conditions. If the ideal gas turbine were operated at high ambient inlet air temperatures of about F. dry bulb and 80F. wet bulb at about a 1,000 foot elevation with an inlet pressure loss of about 2 inches of water and an exhaust pressure loss of about 4 inches of water, the ideal gas turbine would produce about 87.5 per cent of the rated power output (21.6 megawatts) at a heat rate of about 13,000 Btu/Kwh LI-IV.
- the power output and heat rate calculations are based upon a compressor mass flow rate of about 0.954 X 10 pounds of air per hour, a combustor fuel requirement of about 281.7 X 10 Btu/hr Ll-IV, and a turbine exhaust pressure of about 396 inches of water.
- the ideal 25 megawatt gas turbine having the above assumed inlet and exhaust pressure losses will hereinafter be referred to as the standard gas turbine.
- FIG. 2 Another preferred embodiment of' the present invention is schematically illustrated in FIG. 2.
- the supercharging means 15 and the chilling means 18 of the present invention are shown in conjunction with a conventional open cycle, single shaft gas turbine power plant.
- the compressedair from the compressor is heated in a regenerator'by waste heat in the turbine exhaust gases.
- the compressed air is ducted through the coil 35 of a regenerative heat exchanger 36 before it enters the combustor 11.
- Most of the turbine exhaust gas is ducted across the heat exchanger coil 35 for heating the compressed air passing therethrough.
- the power output and/or thermal efficiency of the gas turbine power plant are still more significantly increased by the addition of a heat recovery cycle wherein residual wasteheat in the turbine exhaust gases is recovered and converted into mechanical energy for driving the supercharging means and the chilling means 18.
- a closed steam cycle is provided wherein a waste-heat boiler 37 generates steam from the residual waste-heat in the turbine exhaust gases. The steam generated thereby is expanded through a first steam turbine 38, operably coupled to drive the supercharging means 15, and a second steam turbine 39, operably coupled to drive the chilling means 18.
- the turbine exhaust gases from the regenerative heat exchanger 36 are ducted through the waste-heat boiler 37.
- the residual waste-heat in the exhaust gas generates steam from water pumped through the coils 40- of the waste-heat boiler 37.
- the steam generated thereby is subsequently circulated through the coil 41 of a steam heat exchanger 42 where the waste-heat in the remainder of the turbine exhaust gases superheats the steam.
- the remainder of the exhaust gases is then ducted through the waste-heat boiler 37 to supplement the waste-heating by the turbine exhaust gases from the regenerative heater 36.
- a portion of the superheated steam generated by the waste-heat boiler is expanded in'the first steam turbine 38 which is operably coupled to drive the fan 16 of the supercharging means 15.
- the remainder of the superheated steam is expanded in the second steam turbine 39 which is operably coupled to drive the compressor 21 of the compression cycle refrigeration unit 19.
- the steam discharged from the steam turbines 38 and 39 is condensed in condensors 43 and 44 and is recycled to the waste-heat boiler 37 by return pumps 45 and 46.
- the cooling medium for the condensers 43 and 44 is conveniently provided from the secondary cooling medium for the condenser coil 23.
- the circulating pump also circulates the cooling medium from the cooling coil 26 through the condenser coil 23 of the refrigeration unit 19 and through the coils 47 and 48 of the condensers 43 and 44.
- An electric generator cooling means 50 is provided to chill the generator cooling medium.
- the cooling means 50 comprises a generator cooling coil 51 disposed within the electric generator 13 in a heattransfer relationship withthe generator cooling circuit 52.
- the liquid refrigerant from the chilling means 18 is circulates through the coil 51 to substantially chill the generator cooling medium flowing in the circuit 52.
- the generator cooling coil 51 and the evaporator coil 20 are connected in parallel between the expansion valve 24 and the compressor 21.
- the liquid refrigerant expands through the expansion valve 24 and is circulated through the generator cooling coil 51 where the refrigerant boils to chill the generator cooling medium.
- FIG. 3 Another embodiment of the present invention is illustrated in FIG. 3.
- the embodiment of the gas turbine power plant of FIG. 3 is similar to the gas turbine power plant illustrated in FIG. 2, however, the compressed air from the compressor 10 is not regeneratively heated by a regenerative heat exchanger 36.
- the operating characteristics of the gas turbine power plant listed in FIG. 3 are calculated on the'basis of a compressor inlet pressure loss of about 2 inches of water and a turbine exhaust pressure loss of about 4 inches of water.
- An additional inlet pressure loss of about 2 inches of water is assumed for the chilling means 19 and an additional exhaust pressure loss of about 4 inches of water is assumed for the waste heat boiler 37.
- the gas turbine of FIG. 3 having the compressor inlet air supercharged to increase the compressor inlet pressure by about 58 inches of water and chilled to reduce the temperature of the compressor inlet air to about 40F. would produce about 15 l per cent of the rated power output (37.8 megawatts) at a heat rate of about 10,130 Btu/Kwh LHV.
- FIGS. 4 and 5 the performance of the standard gas turbine power plant described above is compared with the performance of the gas turbine power plant of FIG. 3 under varying levels'of supercharging and chilling.
- the performances are compared for high ambient inlet air temperatures of about 100F. dry bulb and about F. web bulb at about a 1,000 foot elevation.
- An inlet pressure loss of about 2 inches of water and an exhaust pressure loss of about 4 inches of water are assumed for the standard gas turbine power plant.
- An additional inlet pressure loss of about 2 inches of water is assumed for the chilling means and an additional exhaust pressure loss of about 4 inches'of water is assumed for the heat recoverycycle.
- FIGS. 3 and 4 The performance of the standard gas turbine power plant is represented in FIGS. 3 and 4 by the points marked A on the F. line (no chilling) corresponding to zero pressure increase (no supercharging).
- the standard gas turbine power plant would produce about 87.5 per cent of the rated powerv output (21.6 megawatts) at a heat rate of about 13,000 Btu/Kwh LI-IV.
- the performance of the gas turbine power plant of FIG. 3 is indicated by the I points marked 8.
- the increase in power output and/or thermal efficiency of a gas turbine power plant having superchilled compressor inlet air is still more significant when the gas turbine cycle includes regenerative heating of the compressor outlet air, as shown in FIG. 6.
- the embodiment of the present invention illustrated in FIG. 6 is the same as the embodiment illustrated in FIG. 2.
- selected characteristics of the gas turbine power plant for one set of operating conditions are listed adjacent the individual components thereof.
- the same ambient conditions and pressure losses assumed for the calculations presented in FIGS. 4 and 5 were applied to the calculations for FIG. 6.
- the power output for the superchilled gas turbine powerplant of FIG. 6 is about 39.6 megawatts at a heat rate about 8,480 Btu/Kwh LHV.
- the power output of a conventional regenerative gas turbine power plant would be about 26.1 megawatts at a heat rate of about 9,850 Btu/Kwh Ll-IV.
- air temperature, pressure and mass flow rates of about 80F., about 388 inches of water, and about 0.96 X 10 pounds of air per hour and about 13.3 X 10 pounds of water per hour, respectively; a compressor compression ratio of about.9.0 and a turbine expansion ratio of about 7.8; a compressor outlet temperature of about 543F., a combustor inlet temperature of about 839F.
- the chilling means 18 comprises a compression refrigeration unit 19, as described above with respect to FIG. 1, but having a first evaporator coil 20a and a second evaporator coil 20b.
- the inlet air is initially drawn across the first evaporator coil 20a where the air is chilled as heat from the air is transferred to the coil.
- the inlet air is next drawn through the fan 16 where the air is supercharged.
- the supercharged inlet air which has been heated by the work applied to the airby the fan 16 is again chilled as it is ducted across the second evaporator coil 20b before it enters the compressor 10.
- FIG. 7 Selected characteristics for the gas turbine power plant'for one set of operating conditions are listed in FIG. 7.
- the power output for the gas turbine is about 42.8 megawatts at a heat rate of about 9,180 Btu/Kwh Ll-IV.
- FIG. 8 A further example of the significant increase in thermal efficiency and/or power output obtained through superchilling is illustrated in FIG. 8.
- the embodiment of the gas turbine power plant illustrated therein is similar to the embodiment of FIG. 2; however, the individual components are considerably larger to accommodate the increased air mass flow rate necessary to generate sufficient power to drive the larger generator 13.
- the same pressure losses are assumed for the calculations listed in FIG. 8, it will be noted that the assumed ambient air temperatures are lower than the ambient air temperatures assumed above. At these conditions, the superchilled gas turbine power plant would produce about 77.0 megawatts of power at a heat rate of about 7,060 Btu/Kwh LI-IV.
- the heat rate of the superchilled gas turbine power plant of FIG. 8 is remarkably low for a gas turbine power plant and it is highly competitive with the heat rates obtained with steam turbine power plants.
- the waste-heat boiler can include an economizer and/or a combination low pressure boiler and deaerator.
- FIG. 9 still another embodiment of the present invention is illustrated wherein a regenerator bypass circuit 49 is provided to duct the turbine exhaust gases around the regenerator 36 and directly into the waste-heat boiler 37 of the heat recovery cycle thereby increasing the energy available for superchilling the inlet air.
- An adjustable bypassvalve 50 in the circuit 49 permits the power output and/or thermal efficiency of the gas turbine power plant to be modulated in a controlled manner.
- Power output of the gas turbine power plant below the point of maximum efficiency can also be effectively modulated.
- this modulation would be accomplished by reducing the degree of supercharging, for example, throttling the first steam turbine 38 coupled to drive the fan 16, while maintaining the same degree of chilling.
- Still lower power outputs could be obtained by controlled exhausting to the atmosphere of the turbine exhaust gases from the regenerator 36 to reduce the energy input to the heat recovery cycle thus reducing the degree of chilling.
- the gas turbine power plant With complete exhausting of the turbine exhaust gases, the gas turbine power plant operates in the conventional manner without any supercharging or chilling of the compressor inlet air.
- a second adjustable bypass valve 51 is provided to permit selective venting to the atmosphere of the turbine exhaust gases from the regenerative heat exchanger 36 and/or the bypass circuit 49. Adjustment of the second bypass valve 51 provides selective reduction of the energy available to the heat recovery cycle which in turn reduces the degree of superchilling of the compressor inlet air.
- the operating characteristics for the embodiment of the gas turbine power plant of FIG. 9 are listed therein.
- the superchilled gas turbine power plant would produce about 39.6 megawatts of power at a heat rate of about 8480 Btu/Kwh LI-IV.
- fan 16 can be replaced by a moderately low pressure rise compressor or blower.
- other means are also available to chill the inlet air.
- the compression refrigeration unit 19 can be replaced by an absorption refrigeration unit.
- the compressor 21 and motor 22 in the compression refrigeration unit would be replaced by an absorber, a generator, a pump, a heat exchanger and a reducing valve. Waste-heat in the turbine exhaust gases would provide the heat input to the absorption refrigeration unit.
- gas turbine power plant of the present invention has been describedas a power source for an electrical generator, it is to be understood that the improved gas turbine power plant has other applications.
- the gas turbine power plant has application as a natural gas pipeline compressor drive.
- An improved gas turbine having increased performance including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising;
- b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto; and e 0. means for regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means; and v (1. means for recovering a portion of.the waste-heat energy from the exhaust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means; and v e. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
- An improved gas turbine having increased performance including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising:
- the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto;
- An improved gas turbine having increased performance, the gas'turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising: v v
- An improved gas turbine according to claim 3 further comprising means 'for regneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means.
- a method for increasing the performance of a gas turbine including a compressor for receiving inlet gas and compressing-the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas to extract work therefrom, the method comprising the steps of:
- the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto;
- c. means for regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means;
Landscapes
- 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
A gas turbine power plant having a modified gas turbine cycle (Brayton cycle) wherein the compressor inlet air is super-chilled before it enters the compressor. Superchilling, as defined herein, means to supercharge the inlet air to increase the pressure thereof to a pressure level moderately greater than the atmospheric pressure and to chill the supercharged air to decrease the temperature thereof, the preferred temperature level being in the vicinity of about 40* Fahrenheit. A heat recovery cycle is provided to supply the energy necessary to superchill the compressor inlet air.
Description
United States Patent F oster-Pegg Mar. 12, 1974 [5 METHOD AND APPARATUS FOR 3,500,636 3/1970 Craig 60/39.]8 B X INCREASING POWER OUTPUT AND/OR FOREIGN PATENTS OR APPLICATIONS THERMAL EFFICIENCY OF A GAS URBINE POWER PLANT 505,044 8 1954 Canada 60/39.18 B T 679,007 9/1952 Great Britain 60/3918 B [75] Inventor: Richard W. Foster-Pegg, Warren,
Primary Examiner-A1 Lawrence Smith [73] Assignee: Turbo-Development, Inc., New Assistant Exammer Mlchael K0020 York, Attorney, Agent, or F1rml(enyon and Kenyon Rellly Carr and Chapin [22] Filed: July 15, 1971 [21] App]. No.: 162,911 57 ABSTRACT A gas turbine power plant having a modified gas tur- [52] US. Cl 60/39.02, 60/3918 B, 60/39.67 i Cycle (Brayton cycle) wherein the compressor [51] Int. Cl F02c 3/06, F020 7/10 inlet air is supepchilled b f it enters the commas- [58] Fleld of Search 60/39'18 R, 39-18 39-18 sor. Superchilling, as defined herein, means to super- 60/39-18 C1 39-67; 415/179 v charge the inlet air to increase the pressure thereof to a pressure level moderately greater than the atmo- 1 I References Clted spheric pressure and to chill the supercharged air to UNITED STATES PATENTS decrease the temperature thereof, the preferred tem- 3,631,673 1/1972 Charrier 60/39.18 c Peratufe level being in h vicinity Of about Fahr- 2,663,144 12/1953 Nordstrom et a1. 1. 60/39.18 B enheit. A heat recovery cycle is provided to supply the 2,633,707 4/1953 Hermitte etal. 60/39.18 B X energy necessary to superchill the compressor inlet 2,322,717 6/1943 air. 3,479,541 11/1969 3,153,442 10/1964 Silvern 62/467 UX 6 Claims, 9 Drawing Figures Vase/Var 30/454 Facade/mu: f/ex r cvmesssoe PATENTEB m 12 m4 SHEET 8 OF 8 KEQQ W lk 8v? EMA/86$ V Army/yam PATENTEBm 12 1914 SHEEI 7 OF 8 wav 4 P/vas PATENTEI] IIAR 1 2 I974 sum 3 or 8"" METHOD AND APPARATUS FOR INCREASING POWER OUTPUT AND/OR THERMAL EFFICIENCY OF A GAS TURBINE POWER PLANT BACKGROUND OF THE INVENTION The present invention broadly relates to a modified gas turbine cycle for a gas turbine power plant. More particularly, the invention relates to a modified gas turbine cycle wherein the compressor inlet air is superchilled to increase the power output and/or the thermal efficiency of the gas turbine power plant.
Gas turbine power plants have been used for many years to generate electrical power, particularly during periods when demand for electrical power is greatest. The peak demand periods generally occur during the hottest weather when the ambient temperature of the air is high. The high temperature of the compressor inlet air at these times significantly reduces the performance of a gas turbine power plant by decreasing the power output and/or thermal efficiency of the turbine. Consequently, during periods of more moderate or normal ambient air temperatures, the power required of the stationary gas turbine may be substantiallybelow that which the turbine is capable of producing at these conditions so that adequate capacity is available when the ambient'temperature of the air is high.
Electrical utilities and gas turbine manufacturers have considerable incentives to increase the power output and/or thermal efficiency of stationary gas turbine power plants, and much effort has been expended to reap the rewards occasioned by each increase therein. Thus, stationary gas turbine power plants occasionally include various means for modifying the basic gas turbine cycle such as intercoolers, regenerators and recuperators which increase the power output and/or thermal efficiency of the gas turbine power plant. In. addition, limited use has been made of supercharging the compressor inlet air and cooling the supercharged air to increase the power output of the gas turbine power plant. However, at the present time such uses extend only to supercharging with electric motor driven fans and to cooling with evaporative coolers. For example, see Foster-Pegg, R.W., supercharging of Gas Turbines by Forced Draft Fans with Evaporative Intercooling," American Society of Mechanical Engineers, Paper No. 65-GTP 8 (1965). Thus, the prior art does not disclose supercharging compressor inlet air with waste heat energy from the gas turbine exhaust gases. Further, chilling the compressor inlet air to low tem peratures is also known. For example, see US. Pat. No. 2,322,717 for Apparatus For Combustion Turbines issued June 22, 1943. However, chilling of the compressor inlet air has not been adopted by electrical utilities and gas turbine manufacturers, except when a means for chilling the intake air is already available or is being installed for another purpose.
At present, no gas turbine power plant has been installed with a chilling means provided for the primary purpose of chilling the compressor inlet-air. Thus, the prior art does not disclose chilling the compressor inlet air with a refrigeration system having a compressor driven by waste-heat energy from the exhaust gases of the gas turbine. Further, the prior art does not include supercharging and chilling the compressor inlet air.
Despite the incentives to increase the power output and/or thermal efficiency of gas turbine power plants and the efforts that have been expended in this regard, present gas turbine power plants generally remain uneconomical for continuous base load electrical power generation when compared to steam turbine power plants or combined steam and gas turbine power plants.
SUMMARY OF THE INVENTION A gas turbine power plant is provided having a basic 7 gas turbine cycle comprising the following steps: compressing the inlet air from the atmosphere in a compressor; heating the compressed air in a combustor; and expanding the heated, compressed air through a turbine.
According to one embodiment of the present invention, the power output and/or the thermal efficiency of the basic gas turbine cycle described above are significantly improved by the additional step of Superchilling the ambient inlet air before it enters the compressor of the gas turbine power plant. Superchilling, as used herein, means supercharging the inlet air to the compressor of the gas turbine to increase the pressure thereof to a pressure level moderately greater than the atmospheric pressure by means of a low pressure ratio device and chilling the supercharged inlet air to reduce the temperature thereof to a temperature at least as low as the temperature that could be obtained with an evaporative cooler cooling the supercharged air under ambient conditions then present. Chilling is accomplished by the direct transfer of heat from the supercharged inlet air to the refrigerant of a refrigeration system.
The term refrigerant is used herein in a broad and not a restriction senseof the word. The term refrigerant includes all fluids (such as liquids, vapors, and gas) to which heat from the inlet air can be transferred to chill the air. Thus, the term refrigerant is not limited to those liquids which produce refrigeration by their evaporation from a liquid to a gaseous under reduced pressure. By way of example, the term refrigerant can include liquid, such as a brine, which serves as an intermediate refrigerant between a primary refrigerant used to cool the fluid and the inlet air which is chilled by the direct transfer of heat to the fluid. F urther, the term refrigerant" includes ice which may be used to chill the inlet air directly or to cool an intermediate refrigerant such as a brine.
The compressor inlet air is preferably supercharged to increase the pressure thereof in accordance with a supercharging pressure ratio in the range of pressure ratios extending from about 1.1 to about 1.75. One preferred low pressure ratio device for increasing the pressure of the compressor inlet air is a fan device, for example, a conventional single stage, dual flow centrifugal blower. Supercharging pressure ratios above those obtainable with a single stage fan device can be obtained by two stages of supercharging with such a fan device.
Generally speaking, since ambient air usually contains some moisture, the lower temperature limit for the chilling of the supercharged gas is a temperature in the vicinity of the temperature at which concomitant chilling of the moisture in the inlet air could form ice accumulations on heat transfer surfaces used to chill the inlet air. To avoid ice accumulations, the temperature of a heat transfer surface used to chill the inlet air should be maintained at a temperature at least as high as the freezing temperature of the moisture in the inlet air. Thus, as the chilling temperature level of the inlet air approaches the freezing temperature of the moisture in the inlet air, an extensive heat transfer surface is required to chill the air. Accordingly, a chilling temperature level in the vicinity of the range of temperatures extending from about 35 degrees Fahrenheit to about 40 Fahrenheit is preferred.
However, lower chilling temperatures are possible. For example, a means for removing the ice formed on the heat transfer surfaces can be provided thus enabling the compressor inlet air to be chilled to a temperature significantly below the preferred range of temperatures. Further, if a significant degree of moisture is not present in the compressor inlet air, the chilling temperature can also extend considerablybelow the preferred range of temperatures.
The energy required to chill the inlet air is increased by moisture contained in the air. Since the supercharged inlet air is generally chilled to a temperature below the dew point of the inlet air, moisture in the inlet air in excess of the saturated moisture content of the air at the chilling temperature will be condensed in the chilling means. Accordingly, under humid conditions, the total cooling requirement for the chilling means significantly exceeds the sensible heat cooling that would be required for dry air alone.
The compressor inlet air can be chilled both before and after the inlet air has been supercharged, or the inlet air can be chilled only after it has been supercharged. Although chilling both before and after supercharging can result in increased capital expenditures, it can be advantageous under certain circumstances. Initial chilling of the inlet air reduces the power required to supercharge a given inlet air mass flow rate, and thus reduces the total power required to chill the inlet air before it enters the compressor since the heat input to the inlet air caused by supercharging is reduced. The reduction of power to supercharge the inlet air results from the lower temperature of the air entering the supercharging means and from the decreased mass flow rate through the supercharging means caused by the moisture condensed from the inlet air during the initial chilling thereof. Further, the reduced power required to charge the inlet air to a given pressure permits a higher supercharge pressure to be obtained when a heat recovery cycle, to be discussed hereinafter, is provided to drive the supercharging means and the chilling means.
According to another embodiment of the present invention, a heat recovery cycle is provided to supply the energy necessary to superchill the compressor inlet air. For example, a waste-heat boiler can be provided to generate steam by utilizing the waste-heat in the turbine exhaust gases. The steam is subsequently expanded through a first and a second steam turbine. The output shaft of the first steam turbine is coupled to drive the low pressure ratio device for supercharging the compressor inlet air. The output shaft of the second steam turbine is coupled to drive a compression refrigeration unit for chilling the compressor inlet air.
As will be more fully illustrated below, significant and heretofore unforeseen benefits result from superchilling the compressor inlet air. Superchilling the compressor inlet air significantly increases the air mass flow rate to the compressor of the gas turbine power plant at a fixed volume flow rate by increasing the pressure and decreasing the temperature of the inlet air. Superchilling also increases the gas turbine inlet pressure thereby increasing the expansion ratio across the gas turbine. The increased air mass flow rate through the gas turbine power plant and the increased expansion ratio across the turbine provide a significant increase in the poweroutput of the gas turbine power plant. F urther, the lower compressor inlet air temperature permits the gas turbine power plant to be operated at near optimum power output irrespective of the ambient air temperature. When the heat recoverycycle is provided to superchill the compressor inlet air, an additional significant increase in the power, output results as well as an improvement in the thermal efficiency of the gas turbine.
Accordingly, it is an objective of the present invention to provide a gas turbine power plant having increased power output and/or thermal efficiency.
Another object is to increase the power output and- /or the thermal efficiency of the gas r turbine power plant when the ambient temperature of the air is high.
Still another object is to provide a gas turbine power plant wherein ambient inlet air is superchilled before it enters the compressor of the gas turbine for increasing the power output and/or the thermal efficiency of the turbine cycle.
A further object is to provide a gas turbine power plant wherein waste-heat in the turbine exhaust gases is utilized to supply the energy for superchilling the compressor inlet air.
A still further object is to provide a gas turbine power plant for driving an electric generator wherein the compressor inlet air is superchilled before it enters the compressor, and the electric generator cooling medium is chilled for simultaneously increasing the power output and/or the thermal efficiency of the gas turbine and the generating capacity of the electric generator.
A still further object is to provide a gas turbine power plant wherein the waste-heat in the turbine exhaust gases is utilized to supply the energy for superchilling the compressor inlet air and for chilling the electric generator cooling medium.
These and other objects and advantages of the gas turbine power plant of the present invention will become more apparent from the following description, when read in conjunction with the accompanying drawings, wherein corresponding parts of each figure have corresponding numbers.
FIG. '1 is a schematic diagram of one embodiment of the present invention wherein the compressor inlet air is supercharged and subsequently chilled before the air enters the compression stage of the gas turbine.
FIG. 2 is a schematic diagram of another embodiment of the present invention wherein the supercharger and chiller are driven by waste-heat energy recovered from the turbine exhaust gases.
FIG. 3 is a schematic diagram of still another embodiment of the present invention showing selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
FIG. 4 is a graph showing the power output of the embodiment of the gas turbine power plant illustrated in FIG. 3 as a function of the degree of superchilling of the compressor inlet air.
FIG. 5 is a graph showing the heat rate of the embodiment of the gas turbine power plant illustrated in FIG. 3 as a function of the degree of superchilling of the compressor inlet air.
FIG. 6 is a schematic diagram of the embodiment of the gas turbine power plant of FIG. 2 showing selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
FIG. 7 is a schematic diagram of still another embodiment of the present invention wherein the compressor inlet air is chilled before and after it is supercharged.
FIG. 8 is a schematic diagram of the embodiment of the gas turbine power plant illustrated in FIG. 2 showing a second set of selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
FIG. 9 is a schematic diagram of still another embodiment of the present invention showing selected operating characteristics for a complete gas turbine cycle adjacent the individual components.
DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to the drawings, one preferred embodiment of the improved gas turbine power plant is schematically illustrated in FIG. 1. The improvement of the present invention is schematically shown in conjunction with-a conventional open-cycle, single shaft gas turbine power plant. The gas turbine power plant comprises a compressor 10 for compressing the inlet air from the atmosphere, a combustor 11 for heating the compressed air, and a turbine 12 for expanding the heated, compressed air. The turbine 12 is operably coupled to drive the compressor 10 and an electric generator 13 by means of shaft 14.
According to the present invention, the power output and/or the thermal efficiency of the gas turbine described above are significantly increased by superchilling the inlet air before it enters the compressor of the gas turbine.
Thus, referring to FIG. 1, a supercharging means 15 is provided which comprises a low pressure ratio device, conveniently shown as a fan 16, driven by an electric motor 17. Inlet air is drawn through the fan 16 thereby increasing the pressure thereof to a pressure level moderately greater than the atmospheric pressure. Once the inlet air has been supercharged, it is ducted to a chilling means 18.
The chilling means 18 is conveniently shown as a compression refrigeration unit 19 which comprises an evaporator coil 20 in which a liquid refrigerant boils at a low temperature, a compressor 21 driven by an electric motor 22 for raising the pressure and temperature of the gaseous refrigerant from the evaporator coil 20, a condenser 23 in which the refrigerant from the compressor 21 discharges heat to a secondary cooling medium such as water, and an expansion valve 24 for expanding the liquid refrigerant from the high pressure level in the condenser 21 to the low pressure level in the evaporator coil 20. The supercharged inlet air is ducted across the evaporator coil 20 where the air is chilled as heat from the air is transferred to the expanded gaseous refrigerant therein.
The secondary cooling medium is circulated through the coil 25 of the condenser 23 by a circulating pump 26 where the gaseous refrigerant condenses to a liquid and releases heat to the cooling medium. The cooling medium subsequently circulates through a cooling coil 27 of a cooling tower 28 where the cooling medium discharges heat to air circulated across the cooling coil 27 by a cooling fan 29, driven by an electric motor 30.
To illustrate the increased performance of a gas turbine power plant obtained by superchilling the compressor inlet air, the power output and thermal efficiency of various embodiments of the gas turbine power plant are described below. The ideal gas turbine power plant assumed for some of the comparisonsis a 25 megawatt gas turbine power plant having an ideal gas turbine cycle (Brayton Cycle) rated at a compressor inlet temperature of about F. and a compressor inlet pressure of about 392 inches of water which corresponds to the pressure at about a 1,000 foot elevation. The ideal cycle has no inlet or exhaust pressure losses. Assuming a compressorinlet mass flow rate of about 1 X 10 pounds of air per hour, a combustor fuel requirement of about 300 X 10 Btu/Hr LI-IV (Lower Heating Value), and a gas turbine exhaust temperature and pressure of about 895F. and about 392 inches of water, respectively, the ideal gas turbine power plant would produce about 25 megawatts (rated power output) at a heat rate of about 12,000 Btu/Kwh LI-IV.
The performance of the ideal 25 megawatt gas turbine power plant is significantly reduced when the gas turbine is operated under warm weather conditions. If the ideal gas turbine were operated at high ambient inlet air temperatures of about F. dry bulb and 80F. wet bulb at about a 1,000 foot elevation with an inlet pressure loss of about 2 inches of water and an exhaust pressure loss of about 4 inches of water, the ideal gas turbine would produce about 87.5 per cent of the rated power output (21.6 megawatts) at a heat rate of about 13,000 Btu/Kwh LI-IV. The power output and heat rate calculations are based upon a compressor mass flow rate of about 0.954 X 10 pounds of air per hour, a combustor fuel requirement of about 281.7 X 10 Btu/hr Ll-IV, and a turbine exhaust pressure of about 396 inches of water. The ideal 25 megawatt gas turbine having the above assumed inlet and exhaust pressure losses will hereinafter be referred to as the standard gas turbine.
Superchilling the compressor inlet air of the standard gas turbine described above, as shown in FIG. 1, significantly increases the power output and/or thermal efficiency of the gas turbine. For example, assume the following operating conditions: inlet air temperatures, pressure and mass flow rates of about 100F. dry bulb,
about 80F. wet bulb, about 390 inches of water, about 1.223 X 10 pounds of air per hour and about 21.4 x 10 pounds of water per hour; a combustor fuel requirement of about 382.3 X 10 Btu/hr LI-IV; and a turbine exhaust temperature of about 823F. Supercharg ing the compressor inlet air of the standard gas turbine to moderately raise the pressure thereof from about 390 inches of water to about 448 inches of water with a motor driven fan 16, and chilling the supercharged compressor inlet air to about 40F. with a motor driven compression refrigeration unit 19 increases the net power output of the standard gas turbine to about 125 per cent of rated power output (31.17 megawatts) at a heat rate of about 12,300 Btu/Kwh Ll-IV. The motor driven fan 16 would require about 2,750 kilowatts to supercharge the inlet air. The refrigeration unit 19 would require about 3,892 kilowatts to chill the supercharged air. Thus, of the about 37.8 megawatts of electrical power generated by the standard gas turbine, about 6,642 kilowatts are consumed by the superchilling thereby providing a net power output of about 31.17 megawatts.
Another preferred embodiment of' the present invention is schematically illustrated in FIG. 2. As described above, the supercharging means 15 and the chilling means 18 of the present invention are shown in conjunction with a conventional open cycle, single shaft gas turbine power plant. However, in FIG. 2, the compressedair from the compressor is heated in a regenerator'by waste heat in the turbine exhaust gases. Thus, the compressed air is ducted through the coil 35 of a regenerative heat exchanger 36 before it enters the combustor 11. Most of the turbine exhaust gas is ducted across the heat exchanger coil 35 for heating the compressed air passing therethrough.
According to the present invention, the power output and/or thermal efficiency of the gas turbine power plant are still more significantly increased by the addition of a heat recovery cycle wherein residual wasteheat in the turbine exhaust gases is recovered and converted into mechanical energy for driving the supercharging means and the chilling means 18. Thus, referring to FIG. 2, a closed steam cycle is provided wherein a waste-heat boiler 37 generates steam from the residual waste-heat in the turbine exhaust gases. The steam generated thereby is expanded through a first steam turbine 38, operably coupled to drive the supercharging means 15, and a second steam turbine 39, operably coupled to drive the chilling means 18.
The turbine exhaust gases from the regenerative heat exchanger 36 are ducted through the waste-heat boiler 37. The residual waste-heat in the exhaust gas generates steam from water pumped through the coils 40- of the waste-heat boiler 37. The steam generated thereby is subsequently circulated through the coil 41 of a steam heat exchanger 42 where the waste-heat in the remainder of the turbine exhaust gases superheats the steam. The remainder of the exhaust gases is then ducted through the waste-heat boiler 37 to supplement the waste-heating by the turbine exhaust gases from the regenerative heater 36.
A portion of the superheated steam generated by the waste-heat boiler is expanded in'the first steam turbine 38 which is operably coupled to drive the fan 16 of the supercharging means 15. The remainder of the superheated steam is expanded in the second steam turbine 39 which is operably coupled to drive the compressor 21 of the compression cycle refrigeration unit 19. The steam discharged from the steam turbines 38 and 39 is condensed in condensors 43 and 44 and is recycled to the waste-heat boiler 37 by return pumps 45 and 46. The cooling medium for the condensers 43 and 44 is conveniently provided from the secondary cooling medium for the condenser coil 23. Thus, the circulating pump also circulates the cooling medium from the cooling coil 26 through the condenser coil 23 of the refrigeration unit 19 and through the coils 47 and 48 of the condensers 43 and 44.
The performance of the gas turbine power plant is still further improved when the electric generating capacity of the electric generator is increased to complement the increased shaft output of the gas turbine power plant. An electric generator cooling means 50 is provided to chill the generator cooling medium. The cooling means 50 comprises a generator cooling coil 51 disposed within the electric generator 13 in a heattransfer relationship withthe generator cooling circuit 52. The liquid refrigerant from the chilling means 18 is circulates through the coil 51 to substantially chill the generator cooling medium flowing in the circuit 52. As illustrated in FIG. 3, the generator cooling coil 51 and the evaporator coil 20 are connected in parallel between the expansion valve 24 and the compressor 21.
The liquid refrigerant expands through the expansion valve 24 and is circulated through the generator cooling coil 51 where the refrigerant boils to chill the generator cooling medium.
As noted above, superchilling the compressor inlet air according to the present invention significantly increases the power output and/or thermal efficiency of a gas turbine power plant. For example, another embodiment of the present invention is illustrated in FIG. 3. The embodiment of the gas turbine power plant of FIG. 3 is similar to the gas turbine power plant illustrated in FIG. 2, however, the compressed air from the compressor 10 is not regeneratively heated by a regenerative heat exchanger 36.
The operating characteristics of the gas turbine power plant listed in FIG. 3 are calculated on the'basis of a compressor inlet pressure loss of about 2 inches of water and a turbine exhaust pressure loss of about 4 inches of water. An additional inlet pressure loss of about 2 inches of water is assumed for the chilling means 19 and an additional exhaust pressure loss of about 4 inches of water is assumed for the waste heat boiler 37. Thus, the gas turbine of FIG. 3 having the compressor inlet air supercharged to increase the compressor inlet pressure by about 58 inches of water and chilled to reduce the temperature of the compressor inlet air to about 40F. would produce about 15 l per cent of the rated power output (37.8 megawatts) at a heat rate of about 10,130 Btu/Kwh LHV.
Now, referring to FIGS. 4 and 5, the performance of the standard gas turbine power plant described above is compared with the performance of the gas turbine power plant of FIG. 3 under varying levels'of supercharging and chilling. The performances are compared for high ambient inlet air temperatures of about 100F. dry bulb and about F. web bulb at about a 1,000 foot elevation. An inlet pressure loss of about 2 inches of water and an exhaust pressure loss of about 4 inches of water are assumed for the standard gas turbine power plant. An additional inlet pressure loss of about 2 inches of water is assumed for the chilling means and an additional exhaust pressure loss of about 4 inches'of water is assumed for the heat recoverycycle.
The performance of the standard gas turbine power plant is represented in FIGS. 3 and 4 by the points marked A on the F. line (no chilling) corresponding to zero pressure increase (no supercharging). As
indicated therein, the standard gas turbine power plant would produce about 87.5 per cent of the rated powerv output (21.6 megawatts) at a heat rate of about 13,000 Btu/Kwh LI-IV. In comparison, the performance of the gas turbine power plant of FIG. 3 is indicated by the I points marked 8.
The increase in power output and/or thermal efficiency of a gas turbine power plant having superchilled compressor inlet air is still more significant when the gas turbine cycle includes regenerative heating of the compressor outlet air, as shown in FIG. 6.'The embodiment of the present invention illustrated in FIG. 6 is the same as the embodiment illustrated in FIG. 2. Referring to FIG. 6, selected characteristics of the gas turbine power plant for one set of operating conditions are listed adjacent the individual components thereof. The same ambient conditions and pressure losses assumed for the calculations presented in FIGS. 4 and 5 were applied to the calculations for FIG. 6. The power output for the superchilled gas turbine powerplant of FIG. 6 is about 39.6 megawatts at a heat rate about 8,480 Btu/Kwh LHV.
By way of comparison, the power output of a conventional regenerative gas turbine power plant would be about 26.1 megawatts at a heat rate of about 9,850 Btu/Kwh Ll-IV. These calculations are based upon the following conditions: air temperature, pressure and mass flow rates of about 80F., about 388 inches of water, and about 0.96 X 10 pounds of air per hour and about 13.3 X 10 pounds of water per hour, respectively; a compressor compression ratio of about.9.0 and a turbine expansion ratio of about 7.8; a compressor outlet temperature of about 543F., a combustor inlet temperature of about 839F. and a turbine inlet tempe rature of about 1750F.p a combustor fuel requirement of about 257.3 X 10 Btu/Hr LHL; gas turbine exhaust temperature and pressure of about 963F.'and about 404 inches of water, respectively; and regenerator exhaust temperature and pressure of about 743F. and about 396 inches of water, respectively.
As indicated above, the compressor inlet air can also be chilled both before and-after the air is supercharged. An embodiment of the gas turbine power plant having such dual chilling is illustrated in FIG. 7. The chilling means 18 comprises a compression refrigeration unit 19, as described above with respect to FIG. 1, but having a first evaporator coil 20a and a second evaporator coil 20b. The inlet air is initially drawn across the first evaporator coil 20a where the air is chilled as heat from the air is transferred to the coil. The inlet air is next drawn through the fan 16 where the air is supercharged. The supercharged inlet air which has been heated by the work applied to the airby the fan 16 is again chilled as it is ducted across the second evaporator coil 20b before it enters the compressor 10.
Selected characteristics for the gas turbine power plant'for one set of operating conditions are listed in FIG. 7. The power output for the gas turbine is about 42.8 megawatts at a heat rate of about 9,180 Btu/Kwh Ll-IV.
A further example of the significant increase in thermal efficiency and/or power output obtained through superchilling is illustrated in FIG. 8. The embodiment of the gas turbine power plant illustrated therein is similar to the embodiment of FIG. 2; however, the individual components are considerably larger to accommodate the increased air mass flow rate necessary to generate sufficient power to drive the larger generator 13. Although the same pressure losses are assumed for the calculations listed in FIG. 8, it will be noted that the assumed ambient air temperatures are lower than the ambient air temperatures assumed above. At these conditions, the superchilled gas turbine power plant would produce about 77.0 megawatts of power at a heat rate of about 7,060 Btu/Kwh LI-IV.
The heat rate of the superchilled gas turbine power plant of FIG. 8 is remarkably low for a gas turbine power plant and it is highly competitive with the heat rates obtained with steam turbine power plants.
Superchilling the compressor inlet air with energy provided by a heat recovery cycle and regeneratively heating the compressed air before it enters the combustor can utilize substantially all of the waste-heat in the turbine exhaust gases. As a practical matter, maximum regenerator efficiency would commonly be on the order of about seventy-five per cent so that some waste-heat would always be available for the heat recovery cycle. The waste-heat boiler can include an economizer and/or a combination low pressure boiler and deaerator.
Maximum efficiency of superchilling will generally occur at maximum regenerator efficiency with as much of the residual waste-heat leaving the re generator being utilized for the heat recovery cycle. The ability of superchilling to operate at maximum efficiency can be coupled with high power capability by selectively increasing the energy input to the recuperative cycle thereby increasing the degree of superchilling. Thus, referring to FIG. 9, still another embodiment of the present invention is illustrated wherein a regenerator bypass circuit 49 is provided to duct the turbine exhaust gases around the regenerator 36 and directly into the waste-heat boiler 37 of the heat recovery cycle thereby increasing the energy available for superchilling the inlet air. An adjustable bypassvalve 50 in the circuit 49 permits the power output and/or thermal efficiency of the gas turbine power plant to be modulated in a controlled manner.
Power output of the gas turbine power plant below the point of maximum efficiency can also be effectively modulated. Preferably, this modulation would be accomplished by reducing the degree of supercharging, for example, throttling the first steam turbine 38 coupled to drive the fan 16, while maintaining the same degree of chilling. Still lower power outputs could be obtained by controlled exhausting to the atmosphere of the turbine exhaust gases from the regenerator 36 to reduce the energy input to the heat recovery cycle thus reducing the degree of chilling. With complete exhausting of the turbine exhaust gases, the gas turbine power plant operates in the conventional manner without any supercharging or chilling of the compressor inlet air.
Accordingly, referring again to FIG. 9, a second adjustable bypass valve 51 is provided to permit selective venting to the atmosphere of the turbine exhaust gases from the regenerative heat exchanger 36 and/or the bypass circuit 49. Adjustment of the second bypass valve 51 provides selective reduction of the energy available to the heat recovery cycle which in turn reduces the degree of superchilling of the compressor inlet air.
By way of further example, the operating characteristics for the embodiment of the gas turbine power plant of FIG. 9 are listed therein. The superchilled gas turbine power plant would produce about 39.6 megawatts of power at a heat rate of about 8480 Btu/Kwh LI-IV.
Other means are available to supercharge the ambient-inlet air. For example, fan 16 can be replaced by a moderately low pressure rise compressor or blower. Similarly, other means are also available to chill the inlet air. For example, the compression refrigeration unit 19 can be replaced by an absorption refrigeration unit. Generally speaking, in an absorption refrigeration unit, the compressor 21 and motor 22 in the compression refrigeration unit would be replaced by an absorber, a generator, a pump, a heat exchanger and a reducing valve. Waste-heat in the turbine exhaust gases would provide the heat input to the absorption refrigeration unit.
Although the gas turbine power plant of the present invention has been describedas a power source for an electrical generator, it is to be understood that the improved gas turbine power plant has other applications. For example, the gas turbine power plant has application as a natural gas pipeline compressor drive.
The embodiments of the gas turbine power plant described above are for the purpose, of illustrating the broader aspects of the present invention, and the advantages attendant therein. Other modifications and variations of the embodiments will-be apparent to those skilled in mean, and they may be made without de- 1. An improved gas turbine having increased performance, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising;
a. means for supercharging the inlet gas before it is received by the compressor; and
b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto; and e 0. means for regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means; and v (1. means for recovering a portion of.the waste-heat energy from the exhaust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means; and v e. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
2. An improved gas turbine having increased performance, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising:
a. means for supercharging the inlet gas before it is received by the compressor; and
b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto; and
c. means for recovering a portion of the wasteheat energy from the exhaust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means; and
d. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chill ing means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
3. An improved gas turbine having increased performance, the gas'turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising: v v
a. means for supercharging the inlet gas before it is received by the compressor; and
b. means for chilling the supercharged inlet gas before it is received by the compressor; and
c. means for recovering a portion of the wasteheat energy from the exhaust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means;
d. means for selectively controlling the portion of the waste-heat energy converted to energy for-driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
, 4. An improved gas turbine according to claim 3, further comprising means 'for regneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means.
5. A method for increasing the performance of a gas turbine, the gas -turbine including a compressor for receiving inlet gas and compressing-the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas to extract work therefrom, the method comprising the steps of:
a. supercharging the inlet gas by a fan or a blower device before it is received by the compressor by increasing the pressure of the inlet gas in accordance with a supercharging pressure ratio in a range of pressure ratios extending from about 1.1 to about 1.75; i
b. chilling the supercharged inlet gas before it is received by the-compressor by the direct transfer of heat from the supercharged gas to the refrigerant of a refrigeration system;
c. regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine;
d. recovering a portion of the waste-heat energy from the exhaust gases of the turbine and converting the waste-heat energy into energy for superchilling the compressor inlet air; and I e. selectively controlling the portion of the wasteheat energy converted to energy for superchilling the compressor inlet air thereby selectively controlling the performance of the gas turbine.
before it is received by the compressor by increasing the pressure of the inlet gas in accordance with a supercharging pressure ratio in a range of pressure ratios extending from about 1.1 to about 1.75;
b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto;
c. means for regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means;
d. means for recovering a portion of the waste-heat energy from the exhaust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means; and
. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
Claims (6)
1. An improved gas turbine having increased performance, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising; a. means for supercharging the inlet gas before it is received by the compressor; and b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto; and c. means for regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means; and d. means for recovering a portion of the waste-heat energy from the exhaust gases of the turbine and for converting the wasteheat energy into energy for driving the supercharging means and for driving the chilling means; and e. means for selectively controlling the portion of the wasteheat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
2. An improved gas turbine having increased performance, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising: a. means for supercharging the inlet gas before it is received by the compressor; and b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto; and c. means for recovering a portion of the wasteheat energy from the exhaust gases of the turbine and for converting the waste-heat energy intO energy for driving the supercharging means and for driving the chilling means; and d. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
3. An improved gas turbine having increased performance, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising: a. means for supercharging the inlet gas before it is received by the compressor; and b. means for chilling the supercharged inlet gas before it is received by the compressor; and c. means for recovering a portion of the waste-heat energy from the exhaust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means; d. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
4. An improved gas turbine according to claim 3, further comprising means for regneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means.
5. A method for increasing the performance of a gas turbine, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas to extract work therefrom, the method comprising the steps of: a. supercharging the inlet gas by a fan or a blower device before it is received by the compressor by increasing the pressure of the inlet gas in accordance with a supercharging pressure ratio in a range of pressure ratios extending from about 1.1 to about 1.75; b. chilling the supercharged inlet gas before it is received by the compressor by the direct transfer of heat from the supercharged gas to the refrigerant of a refrigeration system; c. regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine; d. recovering a portion of the waste-heat energy from the exhaust gases of the turbine and converting the waste-heat energy into energy for superchilling the compressor inlet air; and e. selectively controlling the portion of the waste-heat energy converted to energy for superchilling the compressor inlet air thereby selectively controlling the performance of the gas turbine.
6. An improved gas turbine having increased performance, the gas turbine including a compressor for receiving inlet gas and compressing the same, means for heating the compressed gas, and a turbine for expanding the heated compressed gas, the improvement comprising: a. fan or blower means for supercharging the inlet gas before it is received by the compressor by increasing the pressure of the inlet gas in accordance with a supercharging pressure ratio in a range of pressure ratios extending from about 1.1 to about 1.75; b. means for chilling the supercharged inlet gas before it is received by the compressor, the chilling means including a refrigerant for the direct transfer of heat from the supercharged gas thereto; c. means for regeneratively heating the compressed gas from the compressor with waste-heat from the exhaust gases of the turbine before the compressed gas passes to the compressed gas heating means; d. means for recovering a portion of the waste-heat energy from the exhAust gases of the turbine and for converting the waste-heat energy into energy for driving the supercharging means and for driving the chilling means; and e. means for selectively controlling the portion of the waste-heat energy converted to energy for driving the supercharging means and for driving the chilling means for providing selective control over the amount of energy available to superchill the inlet gas thereby providing for selective control of the performance of the gas turbine.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16291171A | 1971-07-15 | 1971-07-15 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3796045A true US3796045A (en) | 1974-03-12 |
Family
ID=22587631
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US00162911A Expired - Lifetime US3796045A (en) | 1971-07-15 | 1971-07-15 | Method and apparatus for increasing power output and/or thermal efficiency of a gas turbine power plant |
Country Status (1)
Country | Link |
---|---|
US (1) | US3796045A (en) |
Cited By (144)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3882671A (en) * | 1971-09-14 | 1975-05-13 | Brayton Cycle Improvement Ass | Gasification method with fuel gas cooling |
US3971211A (en) * | 1974-04-02 | 1976-07-27 | Mcdonnell Douglas Corporation | Thermodynamic cycles with supercritical CO2 cycle topping |
US3974642A (en) * | 1973-01-26 | 1976-08-17 | Fives-Cail Babcock Societe Anonyme | Hybrid cycle power plant with heat accumulator for storing heat exchange fluid transferring heat between cycles |
US3978663A (en) * | 1974-01-11 | 1976-09-07 | Sulzer Brothers Limited | Process and apparatus for evaporating and heating liquified natural gas |
FR2344715A1 (en) * | 1976-03-15 | 1977-10-14 | Gen Atomic Co | COOLING CIRCUIT FOR ENERGY GENERATION PLANT |
US4178754A (en) * | 1976-07-19 | 1979-12-18 | The Hydragon Corporation | Throttleable turbine engine |
FR2434265A1 (en) * | 1978-07-24 | 1980-03-21 | Svenska Flaektfabriken Ab | PROCESS FOR CONVERTING THERMAL ENERGY OF LOWER QUALITY INTO MECHANICAL ENERGY IN A TURBINE FOR FURTHER USE, AND INSTALLATION FOR IMPLEMENTING THE PROCESS |
US4204401A (en) * | 1976-07-19 | 1980-05-27 | The Hydragon Corporation | Turbine engine with exhaust gas recirculation |
US4244191A (en) * | 1978-01-03 | 1981-01-13 | Thomassen Holland B.V. | Gas turbine plant |
US4907405A (en) * | 1989-01-24 | 1990-03-13 | Union Carbide Corporation | Process to cool gas |
US5193337A (en) * | 1988-07-25 | 1993-03-16 | Abb Stal Ab | Method for operating gas turbine unit for combined production of electricity and heat |
US5203161A (en) * | 1990-10-30 | 1993-04-20 | Lehto John M | Method and arrangement for cooling air to gas turbine inlet |
US5212942A (en) * | 1990-11-09 | 1993-05-25 | Tiernay Turbines, Inc. | Cogeneration system with recuperated gas turbine engine |
US5241817A (en) * | 1991-04-09 | 1993-09-07 | George Jr Leslie C | Screw engine with regenerative braking |
US5321944A (en) * | 1992-01-08 | 1994-06-21 | Ormat, Inc. | Power augmentation of a gas turbine by inlet air chilling |
US5323603A (en) * | 1990-11-09 | 1994-06-28 | Tiernay Turbines | Integrated air cycle-gas turbine engine |
GB2280224A (en) * | 1993-07-22 | 1995-01-25 | Ormat Ind Ltd | Method of and apparatus for augmenting power produced from gas turbines |
US5388395A (en) * | 1993-04-27 | 1995-02-14 | Air Products And Chemicals, Inc. | Use of nitrogen from an air separation unit as gas turbine air compressor feed refrigerant to improve power output |
ES2068781A2 (en) * | 1992-11-09 | 1995-04-16 | Ormat Ind Ltd | Method and apparatus to increase the power of a gas turbine. (Machine-translation by Google Translate, not legally binding) |
US5444971A (en) * | 1993-04-28 | 1995-08-29 | Holenberger; Charles R. | Method and apparatus for cooling the inlet air of gas turbine and internal combustion engine prime movers |
US5463873A (en) * | 1993-12-06 | 1995-11-07 | Cool Fog Systems, Inc. | Method and apparatus for evaporative cooling of air leading to a gas turbine engine |
US5537813A (en) * | 1992-12-08 | 1996-07-23 | Carolina Power & Light Company | Gas turbine inlet air combined pressure boost and cooling method and apparatus |
ES2088719A2 (en) * | 1992-05-12 | 1996-08-16 | Ormat Inc | Method and apparatus for increasing the power produced by a gas turbine |
US5622044A (en) * | 1992-11-09 | 1997-04-22 | Ormat Industries Ltd. | Apparatus for augmenting power produced from gas turbines |
US5632148A (en) * | 1992-01-08 | 1997-05-27 | Ormat Industries Ltd. | Power augmentation of a gas turbine by inlet air chilling |
US5655373A (en) * | 1994-09-28 | 1997-08-12 | Kabushiki Kaisha Toshiba | Gas turbine intake air cooling apparatus |
US5666800A (en) * | 1994-06-14 | 1997-09-16 | Air Products And Chemicals, Inc. | Gasification combined cycle power generation process with heat-integrated chemical production |
GB2311824A (en) * | 1996-04-01 | 1997-10-08 | Asea Brown Boveri | Gas turbine power plant |
GB2316133A (en) * | 1996-08-02 | 1998-02-18 | Gen Electric | Gas turbine engine with liquid nitrogen chilling of inlet air, NOx control and power augmentaion. |
EP0846220A2 (en) * | 1995-08-24 | 1998-06-10 | Charles R. Kohlenberger | Method and apparatus for cooling the inlet air of gas turbine and internal combustion engine prime movers |
US5806298A (en) * | 1996-09-20 | 1998-09-15 | Air Products And Chemicals, Inc. | Gas turbine operation with liquid fuel vaporization |
US5839270A (en) * | 1996-12-20 | 1998-11-24 | Jirnov; Olga | Sliding-blade rotary air-heat engine with isothermal compression of air |
US6050083A (en) * | 1995-04-24 | 2000-04-18 | Meckler; Milton | Gas turbine and steam turbine powered chiller system |
US6119445A (en) * | 1993-07-22 | 2000-09-19 | Ormat Industries Ltd. | Method of and apparatus for augmenting power produced from gas turbines |
WO2001000975A1 (en) * | 1999-06-10 | 2001-01-04 | Enhanced Turbine Output Holding, Llc | Supercharging system for gas turbines |
US6209307B1 (en) | 1999-05-05 | 2001-04-03 | Fpl Energy, Inc. | Thermodynamic process for generating work using absorption and regeneration |
US6308512B1 (en) | 1999-06-10 | 2001-10-30 | Enhanced Turbine Output Holding, Llc | Supercharging system for gas turbines |
EP0945607A3 (en) * | 1998-03-24 | 2001-12-19 | Mitsubishi Heavy Industries, Ltd. | Intake-air cooling for a gas turbine of a combined power plant |
US6332321B1 (en) * | 1992-11-09 | 2001-12-25 | Ormat Industries Ltd. | Apparatus for augmenting power produced from gas turbines |
ES2168986A1 (en) * | 2000-09-12 | 2002-06-16 | Univ Madrid Politecnica | Supercharged gas turbine with the steam turbine of a power generator plant of combined cycle |
US6430931B1 (en) * | 1997-10-22 | 2002-08-13 | General Electric Company | Gas turbine in-line intercooler |
US6499303B1 (en) * | 2001-04-18 | 2002-12-31 | General Electric Company | Method and system for gas turbine power augmentation |
US6530224B1 (en) * | 2001-03-28 | 2003-03-11 | General Electric Company | Gas turbine compressor inlet pressurization system and method for power augmentation |
US6536229B1 (en) * | 2000-08-29 | 2003-03-25 | Kawasaki Thermal Engineering Co., Ltd. | Absorption refrigerator |
US6539720B2 (en) * | 2000-11-06 | 2003-04-01 | Capstone Turbine Corporation | Generated system bottoming cycle |
US20030106319A1 (en) * | 2001-12-06 | 2003-06-12 | Kopko William L. | Supercharged gas turbine with improved control |
US20030182944A1 (en) * | 2002-04-02 | 2003-10-02 | Hoffman John S. | Highly supercharged gas-turbine generating system |
JP2003529701A (en) * | 1999-06-10 | 2003-10-07 | エンハンスド タービン アウトプット ホールディング エル エル シー | Supercharged gas turbine device, supercharged auxiliary device, supercharged gas turbine device operating method, high-pressure fluid transfer duct, and power generation facility |
US6651443B1 (en) * | 2000-10-20 | 2003-11-25 | Milton Meckler | Integrated absorption cogeneration |
US20040007878A1 (en) * | 2002-07-11 | 2004-01-15 | Siemens Westinghouse Power Corporation | Turbine power generator including supplemental parallel cooling and related methods |
US6688136B1 (en) * | 2002-11-27 | 2004-02-10 | General Electric Company | Generator system including an electric generator and a centrifugal chiller |
US6694772B2 (en) * | 2001-08-09 | 2004-02-24 | Ebara Corporation | Absorption chiller-heater and generator for use in such absorption chiller-heater |
EP0990801B1 (en) * | 1998-09-30 | 2004-02-25 | ALSTOM Technology Ltd | Method for isothermal compression of air and nozzle arrangement for carrying out the method |
US20040088993A1 (en) * | 2002-11-13 | 2004-05-13 | Radcliff Thomas D. | Combined rankine and vapor compression cycles |
US20040088992A1 (en) * | 2002-11-13 | 2004-05-13 | Carrier Corporation | Combined rankine and vapor compression cycles |
US20040098966A1 (en) * | 2002-11-27 | 2004-05-27 | Dewis David W. | Microturbine exhaust heat augmentation system |
US20040163536A1 (en) * | 2000-06-21 | 2004-08-26 | Baudat Ned P. | Direct turbine air chiller/scrubber system |
US20040255593A1 (en) * | 2002-11-13 | 2004-12-23 | Carrier Corporation | Combined rankine and vapor compression cycles |
EP1528239A1 (en) * | 2003-10-31 | 2005-05-04 | General Electric Company | Methods and apparatus for operating gas turbine engines with intercoolers between compressors |
US20050121532A1 (en) * | 2003-12-05 | 2005-06-09 | Reale Michael J. | System and method for district heating with intercooled gas turbine engine |
US20050223712A1 (en) * | 2003-12-13 | 2005-10-13 | Siemens Westinghouse Power Corporation | Vaporization of liquefied natural gas for increased efficiency in power cycles |
US20060078034A1 (en) * | 2004-06-18 | 2006-04-13 | Coffinberry George A | Cryogenic liquid oxidizer cooled high energy system |
US7065953B1 (en) * | 1999-06-10 | 2006-06-27 | Enhanced Turbine Output Holding | Supercharging system for gas turbines |
WO2006068832A1 (en) * | 2004-12-20 | 2006-06-29 | Fluor Technologies Corporation | Configurations and methods for lng fueled power plants |
US20060185366A1 (en) * | 2005-02-22 | 2006-08-24 | Siemens Aktiengesellschaft | Thermal power plant |
US7168233B1 (en) * | 2005-12-12 | 2007-01-30 | General Electric Company | System for controlling steam temperature |
US20070035137A1 (en) * | 2005-08-11 | 2007-02-15 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Electric power generating device |
US20070095072A1 (en) * | 2005-10-12 | 2007-05-03 | Alstom Technology Ltd. | Gas turbine with cooling air |
US20070137216A1 (en) * | 2005-12-20 | 2007-06-21 | General Electric Company | Gas turbine engine assembly and method of assembling same |
US20080078178A1 (en) * | 2006-07-20 | 2008-04-03 | Jay Johnson | Use of exhaust in thermal devices |
US20090193812A1 (en) * | 2008-01-31 | 2009-08-06 | General Electric Company, A New York Corporation | Reheat Gas And Exhaust Gas Regenerator System For A Combined Cycle Power Plant |
EP2149765A2 (en) * | 2008-07-31 | 2010-02-03 | General Electric Company | Heat Recovery System |
CN101638999A (en) * | 2008-07-31 | 2010-02-03 | 通用电气公司 | Heat recovery system for a turbomachine and method of operating a heat recovery steam system for a turbomachine |
US20100095681A1 (en) * | 2008-10-07 | 2010-04-22 | Enis Ben M | Method and apparatus for using compressed air to increase the efficiency of a fuel driven turbine generator |
US20100146930A1 (en) * | 2008-12-11 | 2010-06-17 | General Electric Company | Low Grade Heat Recovery System for Turbine Air Inlet |
US7762054B2 (en) | 2007-08-21 | 2010-07-27 | Donald Charles Erickson | Thermally powered turbine inlet air chiller heater |
US20100229594A1 (en) * | 2008-12-04 | 2010-09-16 | Donald Charles Erickson | Chilling economizer |
US20100242429A1 (en) * | 2009-03-25 | 2010-09-30 | General Electric Company | Split flow regenerative power cycle |
US20100257837A1 (en) * | 2009-04-14 | 2010-10-14 | General Electric Company | Systems involving hybrid power plants |
CN1841885B (en) * | 2005-03-29 | 2010-10-27 | 中国科学院电工研究所 | Self-circulation cooling loop of heavy current fixture wire |
US20100285413A1 (en) * | 2009-05-06 | 2010-11-11 | General Vortex Energy, Inc. | Apparatus and Methods For Providing Uniformly Volume Distributed Combustion of Fuel |
US7980092B2 (en) | 2006-11-30 | 2011-07-19 | Husky Injection Molding Systems Ltd. | Compressor |
US20110193346A1 (en) * | 2010-02-08 | 2011-08-11 | Carlos Guzman | Method and apparatus to recover and convert waste heat to mechanical energy |
US20110277476A1 (en) * | 2010-05-14 | 2011-11-17 | Michael Andrew Minovitch | Low Temperature High Efficiency Condensing Heat Engine for Propelling Road Vehicles |
US20120111025A1 (en) * | 2010-10-22 | 2012-05-10 | Man Diesel & Turbo Se | System For The Generation Of Mechanical And/Or Electrical Energy |
ES2387724A1 (en) * | 2010-03-05 | 2012-09-28 | Universidad Nacional De Educación A Distancia | Partial regeneration system in gas turbines of cycles combined with one or several sources of heat. (Machine-translation by Google Translate, not legally binding) |
US20130098313A1 (en) * | 2011-10-21 | 2013-04-25 | General Electric Company | System and apparatus for controlling temperature in a heat recovery steam generator |
US8468830B2 (en) * | 2008-12-11 | 2013-06-25 | General Electric Company | Inlet air heating and cooling system |
US20130318987A1 (en) * | 2012-05-31 | 2013-12-05 | General Electric Company | Supercharged combined cycle system with air flow bypass to hrsg and fan |
US8616005B1 (en) | 2009-09-09 | 2013-12-31 | Dennis James Cousino, Sr. | Method and apparatus for boosting gas turbine engine performance |
US20140208765A1 (en) * | 2013-01-28 | 2014-07-31 | General Electric Company | Systems And Methods To Extend Gas Turbine Hot Gas Path Parts With Supercharged Air Flow Bypass |
US20140225372A1 (en) * | 2013-02-08 | 2014-08-14 | Alstom Technology Ltd | Power generating unit and method for operating such a power generating unit |
US20150315927A1 (en) * | 2014-05-01 | 2015-11-05 | General Electric Company | Enhanced generator capability in hot ambient temperatures |
US20150369129A1 (en) * | 2013-02-04 | 2015-12-24 | Dalkia | Facility with a gas turbine and method for regulating said facility |
US20160010551A1 (en) * | 2014-07-08 | 2016-01-14 | 8 Rivers Capital, Llc | Method and system for power production wtih improved efficiency |
US20160138431A1 (en) * | 2014-11-14 | 2016-05-19 | University Of Florida Research Foundation, Inc. | Humid Air Turbine Power, Water Extraction, and Refrigeration Cycle |
WO2016126372A1 (en) * | 2015-02-05 | 2016-08-11 | Powerphase Llc | Turbocooled vane of a gas turbine engine |
US9470149B2 (en) * | 2008-12-11 | 2016-10-18 | General Electric Company | Turbine inlet air heat pump-type system |
US20180045080A1 (en) * | 2015-03-17 | 2018-02-15 | Mitsubishi Heavy Industries, Ltd. | Intake air cooling method, intake air cooling device executing said method, and waste heat recovery facility and gas turbine plant each comprising said intake air cooling device |
WO2018146509A3 (en) * | 2016-10-11 | 2018-10-25 | Perry Van Der Bogt | System and method for sustainable generation of energy |
US10443501B2 (en) | 2015-02-05 | 2019-10-15 | Powerphase Llc | Turbocooled vane of a gas turbine engine |
US10731554B2 (en) | 2017-09-12 | 2020-08-04 | University Of Florida Research Foundation, Inc. | Humid air turbine power, water extraction, and refrigeration cycle |
US10815764B1 (en) | 2019-09-13 | 2020-10-27 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US10895202B1 (en) | 2019-09-13 | 2021-01-19 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US10914232B2 (en) | 2018-03-02 | 2021-02-09 | 8 Rivers Capital, Llc | Systems and methods for power production using a carbon dioxide working fluid |
US10954770B1 (en) | 2020-06-09 | 2021-03-23 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US10961908B1 (en) | 2020-06-05 | 2021-03-30 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US10968837B1 (en) | 2020-05-14 | 2021-04-06 | Bj Energy Solutions, Llc | Systems and methods utilizing turbine compressor discharge for hydrostatic manifold purge |
US10989180B2 (en) | 2019-09-13 | 2021-04-27 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US10995670B2 (en) | 2012-10-26 | 2021-05-04 | Powerphase International, Llc | Gas turbine energy supplementing systems and heating systems, and methods of making and using the same |
US11002189B2 (en) | 2019-09-13 | 2021-05-11 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11015536B2 (en) | 2019-09-13 | 2021-05-25 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11015594B2 (en) | 2019-09-13 | 2021-05-25 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11022526B1 (en) | 2020-06-09 | 2021-06-01 | Bj Energy Solutions, Llc | Systems and methods for monitoring a condition of a fracturing component section of a hydraulic fracturing unit |
US11028677B1 (en) | 2020-06-22 | 2021-06-08 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US20210207500A1 (en) * | 2018-05-22 | 2021-07-08 | MTU Aero Engines AG | Exhaust-gas treatment device, aircraft propulsion system, and method for treating an exhaust-gas stream |
US11066915B1 (en) | 2020-06-09 | 2021-07-20 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11098651B1 (en) | 2019-09-13 | 2021-08-24 | Bj Energy Solutions, Llc | Turbine engine exhaust duct system and methods for noise dampening and attenuation |
US11109508B1 (en) | 2020-06-05 | 2021-08-31 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11111768B1 (en) | 2020-06-09 | 2021-09-07 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US11125066B1 (en) | 2020-06-22 | 2021-09-21 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11149533B1 (en) | 2020-06-24 | 2021-10-19 | Bj Energy Solutions, Llc | Systems to monitor, detect, and/or intervene relative to cavitation and pulsation events during a hydraulic fracturing operation |
US11156131B2 (en) * | 2016-07-28 | 2021-10-26 | Doosan Heavy Industries & Construction Co., Ltd. | Exhaust gas cooling device and method |
US11193361B1 (en) | 2020-07-17 | 2021-12-07 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11208880B2 (en) | 2020-05-28 | 2021-12-28 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11208953B1 (en) | 2020-06-05 | 2021-12-28 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11220895B1 (en) | 2020-06-24 | 2022-01-11 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11236739B2 (en) | 2019-09-13 | 2022-02-01 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11268346B2 (en) | 2019-09-13 | 2022-03-08 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems |
US11280226B2 (en) * | 2016-12-08 | 2022-03-22 | Atlas Copco Comptec, Llc | Waste heat recovery system |
US11359521B2 (en) * | 2015-11-05 | 2022-06-14 | William M. Conlon | Dispatchable storage combined cycle power plants |
US11408794B2 (en) | 2019-09-13 | 2022-08-09 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11415125B2 (en) | 2020-06-23 | 2022-08-16 | Bj Energy Solutions, Llc | Systems for utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11428165B2 (en) | 2020-05-15 | 2022-08-30 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11448141B2 (en) * | 2017-12-22 | 2022-09-20 | Finno Exergy Oy | System and method for generating power |
US11473413B2 (en) | 2020-06-23 | 2022-10-18 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11560845B2 (en) | 2019-05-15 | 2023-01-24 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11624326B2 (en) | 2017-05-21 | 2023-04-11 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11635074B2 (en) | 2020-05-12 | 2023-04-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US11639654B2 (en) | 2021-05-24 | 2023-05-02 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11867118B2 (en) | 2019-09-13 | 2024-01-09 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11879363B2 (en) * | 2020-03-30 | 2024-01-23 | Xuanhua Guo | Combined system of intercooled recuperative gas turbine and refrigerant compound bottoming cycle |
US11933153B2 (en) | 2020-06-22 | 2024-03-19 | Bj Energy Solutions, Llc | Systems and methods to operate hydraulic fracturing units using automatic flow rate and/or pressure control |
US11939853B2 (en) | 2020-06-22 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods providing a configurable staged rate increase function to operate hydraulic fracturing units |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2322717A (en) * | 1939-08-10 | 1943-06-22 | Nettel Friedrich | Apparatus for combustion turbines |
GB679007A (en) * | 1950-03-13 | 1952-09-10 | Bbc Brown Boveri & Cie | Thermal power plant |
US2633707A (en) * | 1946-12-16 | 1953-04-07 | Rateau Soc | Compound plant for producing mechanical power and heating steam with gas and steam turbines |
US2663144A (en) * | 1948-05-06 | 1953-12-22 | Laval Steam Turbine Co | Combined gas and steam power plant |
CA505044A (en) * | 1954-08-10 | Sulzer Freres | Thermal power generating processes and systems | |
US3153442A (en) * | 1961-06-26 | 1964-10-20 | David H Silvern | Heating and air conditioning apparatus |
US3479541A (en) * | 1962-09-11 | 1969-11-18 | Allis Louis Co | High speed liquid cooled motors |
US3500636A (en) * | 1966-02-18 | 1970-03-17 | Ass Elect Ind | Gas turbine plants |
US3631673A (en) * | 1969-08-08 | 1972-01-04 | Electricite De France | Power generating plant |
-
1971
- 1971-07-15 US US00162911A patent/US3796045A/en not_active Expired - Lifetime
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA505044A (en) * | 1954-08-10 | Sulzer Freres | Thermal power generating processes and systems | |
US2322717A (en) * | 1939-08-10 | 1943-06-22 | Nettel Friedrich | Apparatus for combustion turbines |
US2633707A (en) * | 1946-12-16 | 1953-04-07 | Rateau Soc | Compound plant for producing mechanical power and heating steam with gas and steam turbines |
US2663144A (en) * | 1948-05-06 | 1953-12-22 | Laval Steam Turbine Co | Combined gas and steam power plant |
GB679007A (en) * | 1950-03-13 | 1952-09-10 | Bbc Brown Boveri & Cie | Thermal power plant |
US3153442A (en) * | 1961-06-26 | 1964-10-20 | David H Silvern | Heating and air conditioning apparatus |
US3479541A (en) * | 1962-09-11 | 1969-11-18 | Allis Louis Co | High speed liquid cooled motors |
US3500636A (en) * | 1966-02-18 | 1970-03-17 | Ass Elect Ind | Gas turbine plants |
US3631673A (en) * | 1969-08-08 | 1972-01-04 | Electricite De France | Power generating plant |
Cited By (319)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3882671A (en) * | 1971-09-14 | 1975-05-13 | Brayton Cycle Improvement Ass | Gasification method with fuel gas cooling |
US3974642A (en) * | 1973-01-26 | 1976-08-17 | Fives-Cail Babcock Societe Anonyme | Hybrid cycle power plant with heat accumulator for storing heat exchange fluid transferring heat between cycles |
US3978663A (en) * | 1974-01-11 | 1976-09-07 | Sulzer Brothers Limited | Process and apparatus for evaporating and heating liquified natural gas |
US3971211A (en) * | 1974-04-02 | 1976-07-27 | Mcdonnell Douglas Corporation | Thermodynamic cycles with supercritical CO2 cycle topping |
FR2344715A1 (en) * | 1976-03-15 | 1977-10-14 | Gen Atomic Co | COOLING CIRCUIT FOR ENERGY GENERATION PLANT |
US4204401A (en) * | 1976-07-19 | 1980-05-27 | The Hydragon Corporation | Turbine engine with exhaust gas recirculation |
US4178754A (en) * | 1976-07-19 | 1979-12-18 | The Hydragon Corporation | Throttleable turbine engine |
US4244191A (en) * | 1978-01-03 | 1981-01-13 | Thomassen Holland B.V. | Gas turbine plant |
FR2434265A1 (en) * | 1978-07-24 | 1980-03-21 | Svenska Flaektfabriken Ab | PROCESS FOR CONVERTING THERMAL ENERGY OF LOWER QUALITY INTO MECHANICAL ENERGY IN A TURBINE FOR FURTHER USE, AND INSTALLATION FOR IMPLEMENTING THE PROCESS |
US5193337A (en) * | 1988-07-25 | 1993-03-16 | Abb Stal Ab | Method for operating gas turbine unit for combined production of electricity and heat |
US4907405A (en) * | 1989-01-24 | 1990-03-13 | Union Carbide Corporation | Process to cool gas |
US5203161A (en) * | 1990-10-30 | 1993-04-20 | Lehto John M | Method and arrangement for cooling air to gas turbine inlet |
US5212942A (en) * | 1990-11-09 | 1993-05-25 | Tiernay Turbines, Inc. | Cogeneration system with recuperated gas turbine engine |
US5323603A (en) * | 1990-11-09 | 1994-06-28 | Tiernay Turbines | Integrated air cycle-gas turbine engine |
US5241817A (en) * | 1991-04-09 | 1993-09-07 | George Jr Leslie C | Screw engine with regenerative braking |
US5632148A (en) * | 1992-01-08 | 1997-05-27 | Ormat Industries Ltd. | Power augmentation of a gas turbine by inlet air chilling |
US5321944A (en) * | 1992-01-08 | 1994-06-21 | Ormat, Inc. | Power augmentation of a gas turbine by inlet air chilling |
ES2088719A2 (en) * | 1992-05-12 | 1996-08-16 | Ormat Inc | Method and apparatus for increasing the power produced by a gas turbine |
US6422019B1 (en) * | 1992-11-09 | 2002-07-23 | Ormat Industries Ltd. | Apparatus for augmenting power produced from gas turbines |
US6332321B1 (en) * | 1992-11-09 | 2001-12-25 | Ormat Industries Ltd. | Apparatus for augmenting power produced from gas turbines |
ES2068781A2 (en) * | 1992-11-09 | 1995-04-16 | Ormat Ind Ltd | Method and apparatus to increase the power of a gas turbine. (Machine-translation by Google Translate, not legally binding) |
US5622044A (en) * | 1992-11-09 | 1997-04-22 | Ormat Industries Ltd. | Apparatus for augmenting power produced from gas turbines |
US5537813A (en) * | 1992-12-08 | 1996-07-23 | Carolina Power & Light Company | Gas turbine inlet air combined pressure boost and cooling method and apparatus |
US5388395A (en) * | 1993-04-27 | 1995-02-14 | Air Products And Chemicals, Inc. | Use of nitrogen from an air separation unit as gas turbine air compressor feed refrigerant to improve power output |
US5444971A (en) * | 1993-04-28 | 1995-08-29 | Holenberger; Charles R. | Method and apparatus for cooling the inlet air of gas turbine and internal combustion engine prime movers |
GB2280224A (en) * | 1993-07-22 | 1995-01-25 | Ormat Ind Ltd | Method of and apparatus for augmenting power produced from gas turbines |
US6119445A (en) * | 1993-07-22 | 2000-09-19 | Ormat Industries Ltd. | Method of and apparatus for augmenting power produced from gas turbines |
US5463873A (en) * | 1993-12-06 | 1995-11-07 | Cool Fog Systems, Inc. | Method and apparatus for evaporative cooling of air leading to a gas turbine engine |
US5865023A (en) * | 1994-06-14 | 1999-02-02 | Air Products And Chemicals, Inc. | Gasification combined cycle power generation process with heat-integrated chemical production |
US5666800A (en) * | 1994-06-14 | 1997-09-16 | Air Products And Chemicals, Inc. | Gasification combined cycle power generation process with heat-integrated chemical production |
US5782093A (en) * | 1994-09-28 | 1998-07-21 | Kabushiki Kaisha Toshiba | Gas turbine intake air cooling apparatus |
US5655373A (en) * | 1994-09-28 | 1997-08-12 | Kabushiki Kaisha Toshiba | Gas turbine intake air cooling apparatus |
WO1996035050A1 (en) | 1995-03-07 | 1996-11-07 | Carolina Power & Light Company | Method and apparatus for increasing the operational capacity and efficiency of a combustion turbine |
US6050083A (en) * | 1995-04-24 | 2000-04-18 | Meckler; Milton | Gas turbine and steam turbine powered chiller system |
EP0846220A4 (en) * | 1995-08-24 | 2000-03-22 | Charles R Kohlenberger | Method and apparatus for cooling the inlet air of gas turbine and internal combustion engine prime movers |
EP0846220A2 (en) * | 1995-08-24 | 1998-06-10 | Charles R. Kohlenberger | Method and apparatus for cooling the inlet air of gas turbine and internal combustion engine prime movers |
GB2311824A (en) * | 1996-04-01 | 1997-10-08 | Asea Brown Boveri | Gas turbine power plant |
GB2316133B (en) * | 1996-08-02 | 2000-10-11 | Gen Electric | Combined gas turbine inlet chiller,NOx control device and power augmentation s ystem and methods of operation |
GB2316133A (en) * | 1996-08-02 | 1998-02-18 | Gen Electric | Gas turbine engine with liquid nitrogen chilling of inlet air, NOx control and power augmentaion. |
US5806298A (en) * | 1996-09-20 | 1998-09-15 | Air Products And Chemicals, Inc. | Gas turbine operation with liquid fuel vaporization |
US5839270A (en) * | 1996-12-20 | 1998-11-24 | Jirnov; Olga | Sliding-blade rotary air-heat engine with isothermal compression of air |
US6430931B1 (en) * | 1997-10-22 | 2002-08-13 | General Electric Company | Gas turbine in-line intercooler |
EP0945607A3 (en) * | 1998-03-24 | 2001-12-19 | Mitsubishi Heavy Industries, Ltd. | Intake-air cooling for a gas turbine of a combined power plant |
US6615585B2 (en) | 1998-03-24 | 2003-09-09 | Mitsubishi Heavy Industries, Ltd. | Intake-air cooling type gas turbine power equipment and combined power plant using same |
EP0990801B1 (en) * | 1998-09-30 | 2004-02-25 | ALSTOM Technology Ltd | Method for isothermal compression of air and nozzle arrangement for carrying out the method |
US6209307B1 (en) | 1999-05-05 | 2001-04-03 | Fpl Energy, Inc. | Thermodynamic process for generating work using absorption and regeneration |
WO2001000975A1 (en) * | 1999-06-10 | 2001-01-04 | Enhanced Turbine Output Holding, Llc | Supercharging system for gas turbines |
US7065953B1 (en) * | 1999-06-10 | 2006-06-27 | Enhanced Turbine Output Holding | Supercharging system for gas turbines |
KR100874508B1 (en) * | 1999-06-10 | 2008-12-18 | 인핸스드 터빈 아웃풋 홀딩, 엘엘씨 | Supercharge system for gas turbine |
US6308512B1 (en) | 1999-06-10 | 2001-10-30 | Enhanced Turbine Output Holding, Llc | Supercharging system for gas turbines |
US6442942B1 (en) | 1999-06-10 | 2002-09-03 | Enhanced Turbine Output Holding, Llc | Supercharging system for gas turbines |
CN1304740C (en) * | 1999-06-10 | 2007-03-14 | 涡轮动力输出控股有限责任公司 | Supercharging system for gas turbines |
EA005393B1 (en) * | 1999-06-10 | 2005-02-24 | Инханст Тэрбайн Аутпут Холдинг, Ллс. | Gas turbine unit for generating power and a supercharging system therefor |
AU775318B2 (en) * | 1999-06-10 | 2004-07-29 | Enhanced Turbine Output Holding, Llc | Supercharging system for gas turbines |
JP2003529701A (en) * | 1999-06-10 | 2003-10-07 | エンハンスド タービン アウトプット ホールディング エル エル シー | Supercharged gas turbine device, supercharged auxiliary device, supercharged gas turbine device operating method, high-pressure fluid transfer duct, and power generation facility |
US20040163536A1 (en) * | 2000-06-21 | 2004-08-26 | Baudat Ned P. | Direct turbine air chiller/scrubber system |
US6536229B1 (en) * | 2000-08-29 | 2003-03-25 | Kawasaki Thermal Engineering Co., Ltd. | Absorption refrigerator |
ES2168986A1 (en) * | 2000-09-12 | 2002-06-16 | Univ Madrid Politecnica | Supercharged gas turbine with the steam turbine of a power generator plant of combined cycle |
US6651443B1 (en) * | 2000-10-20 | 2003-11-25 | Milton Meckler | Integrated absorption cogeneration |
US6539720B2 (en) * | 2000-11-06 | 2003-04-01 | Capstone Turbine Corporation | Generated system bottoming cycle |
US6530224B1 (en) * | 2001-03-28 | 2003-03-11 | General Electric Company | Gas turbine compressor inlet pressurization system and method for power augmentation |
US6499303B1 (en) * | 2001-04-18 | 2002-12-31 | General Electric Company | Method and system for gas turbine power augmentation |
US6694772B2 (en) * | 2001-08-09 | 2004-02-24 | Ebara Corporation | Absorption chiller-heater and generator for use in such absorption chiller-heater |
US20030106319A1 (en) * | 2001-12-06 | 2003-06-12 | Kopko William L. | Supercharged gas turbine with improved control |
US6880343B2 (en) * | 2001-12-06 | 2005-04-19 | William L. Kopko | Supercharged gas turbine with improved control |
US20030182944A1 (en) * | 2002-04-02 | 2003-10-02 | Hoffman John S. | Highly supercharged gas-turbine generating system |
WO2003100233A1 (en) * | 2002-05-22 | 2003-12-04 | Enhanced Turbine Output Holding Llc | Highly supercharged gas turbine and power generating system |
US20040007878A1 (en) * | 2002-07-11 | 2004-01-15 | Siemens Westinghouse Power Corporation | Turbine power generator including supplemental parallel cooling and related methods |
US6798079B2 (en) * | 2002-07-11 | 2004-09-28 | Siemens Westinghouse Power Corporation | Turbine power generator including supplemental parallel cooling and related methods |
US20040088992A1 (en) * | 2002-11-13 | 2004-05-13 | Carrier Corporation | Combined rankine and vapor compression cycles |
US20040255593A1 (en) * | 2002-11-13 | 2004-12-23 | Carrier Corporation | Combined rankine and vapor compression cycles |
US6880344B2 (en) * | 2002-11-13 | 2005-04-19 | Utc Power, Llc | Combined rankine and vapor compression cycles |
WO2004044386A3 (en) * | 2002-11-13 | 2004-10-28 | Carrier Corp | Combined rankine and vapor compression cycles |
US6892522B2 (en) * | 2002-11-13 | 2005-05-17 | Carrier Corporation | Combined rankine and vapor compression cycles |
US6962056B2 (en) | 2002-11-13 | 2005-11-08 | Carrier Corporation | Combined rankine and vapor compression cycles |
CN101027468B (en) * | 2002-11-13 | 2013-05-29 | 开利公司 | Combined rankine and vapor compression cycles |
US20040088993A1 (en) * | 2002-11-13 | 2004-05-13 | Radcliff Thomas D. | Combined rankine and vapor compression cycles |
US6877323B2 (en) * | 2002-11-27 | 2005-04-12 | Elliott Energy Systems, Inc. | Microturbine exhaust heat augmentation system |
US20040098966A1 (en) * | 2002-11-27 | 2004-05-27 | Dewis David W. | Microturbine exhaust heat augmentation system |
US6688136B1 (en) * | 2002-11-27 | 2004-02-10 | General Electric Company | Generator system including an electric generator and a centrifugal chiller |
EP1528239A1 (en) * | 2003-10-31 | 2005-05-04 | General Electric Company | Methods and apparatus for operating gas turbine engines with intercoolers between compressors |
US20050121532A1 (en) * | 2003-12-05 | 2005-06-09 | Reale Michael J. | System and method for district heating with intercooled gas turbine engine |
US20050223712A1 (en) * | 2003-12-13 | 2005-10-13 | Siemens Westinghouse Power Corporation | Vaporization of liquefied natural gas for increased efficiency in power cycles |
US7299619B2 (en) | 2003-12-13 | 2007-11-27 | Siemens Power Generation, Inc. | Vaporization of liquefied natural gas for increased efficiency in power cycles |
US20060078034A1 (en) * | 2004-06-18 | 2006-04-13 | Coffinberry George A | Cryogenic liquid oxidizer cooled high energy system |
US7406829B2 (en) * | 2004-06-18 | 2008-08-05 | General Electric Company | Cryogenic liquid oxidizer cooled high energy system |
WO2006012406A3 (en) * | 2004-07-22 | 2006-07-06 | Carrier Corp | Combined rankine and vapor compression cycles |
WO2006012406A2 (en) * | 2004-07-22 | 2006-02-02 | Carrier Corporation | Combined rankine and vapor compression cycles |
WO2006068832A1 (en) * | 2004-12-20 | 2006-06-29 | Fluor Technologies Corporation | Configurations and methods for lng fueled power plants |
EA010047B1 (en) * | 2004-12-20 | 2008-06-30 | Флуор Текнолоджиз Корпорейшн | Configurations and methods for lng fueled power plants |
AU2005319548B2 (en) * | 2004-12-20 | 2009-07-09 | Fluor Technologies Corporation | Configurations and methods for LNG fueled power plants |
US7980081B2 (en) | 2004-12-20 | 2011-07-19 | Fluor Technologies Corporation | Configurations and methods for LNG fueled power plants |
US20090282836A1 (en) * | 2004-12-20 | 2009-11-19 | Fluor Technologies Corporation | Configurations And Methods For LNG Fueled Power Plants |
US20060185366A1 (en) * | 2005-02-22 | 2006-08-24 | Siemens Aktiengesellschaft | Thermal power plant |
CN1841885B (en) * | 2005-03-29 | 2010-10-27 | 中国科学院电工研究所 | Self-circulation cooling loop of heavy current fixture wire |
US7405491B2 (en) * | 2005-08-11 | 2008-07-29 | Kobe Steel, Ltd. | Electric power generating device |
US20070035137A1 (en) * | 2005-08-11 | 2007-02-15 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Electric power generating device |
US7810332B2 (en) * | 2005-10-12 | 2010-10-12 | Alstom Technology Ltd | Gas turbine with heat exchanger for cooling compressed air and preheating a fuel |
US20070095072A1 (en) * | 2005-10-12 | 2007-05-03 | Alstom Technology Ltd. | Gas turbine with cooling air |
US7168233B1 (en) * | 2005-12-12 | 2007-01-30 | General Electric Company | System for controlling steam temperature |
US20070137216A1 (en) * | 2005-12-20 | 2007-06-21 | General Electric Company | Gas turbine engine assembly and method of assembling same |
US8584464B2 (en) * | 2005-12-20 | 2013-11-19 | General Electric Company | Gas turbine engine assembly and method of assembling same |
US20080078178A1 (en) * | 2006-07-20 | 2008-04-03 | Jay Johnson | Use of exhaust in thermal devices |
US7980092B2 (en) | 2006-11-30 | 2011-07-19 | Husky Injection Molding Systems Ltd. | Compressor |
US7762054B2 (en) | 2007-08-21 | 2010-07-27 | Donald Charles Erickson | Thermally powered turbine inlet air chiller heater |
US8051654B2 (en) * | 2008-01-31 | 2011-11-08 | General Electric Company | Reheat gas and exhaust gas regenerator system for a combined cycle power plant |
US20090193812A1 (en) * | 2008-01-31 | 2009-08-06 | General Electric Company, A New York Corporation | Reheat Gas And Exhaust Gas Regenerator System For A Combined Cycle Power Plant |
US8037703B2 (en) * | 2008-07-31 | 2011-10-18 | General Electric Company | Heat recovery system for a turbomachine and method of operating a heat recovery steam system for a turbomachine |
US20100024443A1 (en) * | 2008-07-31 | 2010-02-04 | General Electric Company | Heat recovery system |
EP2149765A2 (en) * | 2008-07-31 | 2010-02-03 | General Electric Company | Heat Recovery System |
CN101640449A (en) * | 2008-07-31 | 2010-02-03 | 通用电气公司 | Heat recovery system |
US8074458B2 (en) | 2008-07-31 | 2011-12-13 | General Electric Company | Power plant heat recovery system having heat removal and refrigerator systems |
EP2149765A3 (en) * | 2008-07-31 | 2010-12-15 | General Electric Company | Heat Recovery System |
CN101638999A (en) * | 2008-07-31 | 2010-02-03 | 通用电气公司 | Heat recovery system for a turbomachine and method of operating a heat recovery steam system for a turbomachine |
US20100024444A1 (en) * | 2008-07-31 | 2010-02-04 | General Electric Company | Heat recovery system for a turbomachine and method of operating a heat recovery steam system for a turbomachine |
US8833083B2 (en) * | 2008-10-07 | 2014-09-16 | Ben M. Enis | Method and apparatus for using compressed air to increase the efficiency of a fuel driven turbine generator |
US20100095681A1 (en) * | 2008-10-07 | 2010-04-22 | Enis Ben M | Method and apparatus for using compressed air to increase the efficiency of a fuel driven turbine generator |
US20100229594A1 (en) * | 2008-12-04 | 2010-09-16 | Donald Charles Erickson | Chilling economizer |
CN101749116B (en) * | 2008-12-11 | 2014-01-29 | 通用电气公司 | Low-grade heat recovery system for air inlet of turbine |
US9470149B2 (en) * | 2008-12-11 | 2016-10-18 | General Electric Company | Turbine inlet air heat pump-type system |
EP2196651A3 (en) * | 2008-12-11 | 2011-07-06 | General Electric Company | Low grade heat recovery system for turbine air inlet |
US20100146930A1 (en) * | 2008-12-11 | 2010-06-17 | General Electric Company | Low Grade Heat Recovery System for Turbine Air Inlet |
CN101749116A (en) * | 2008-12-11 | 2010-06-23 | 通用电气公司 | The low-grade heat recovery system that is used for air inlet of turbine |
US8356466B2 (en) | 2008-12-11 | 2013-01-22 | General Electric Company | Low grade heat recovery system for turbine air inlet |
US8468830B2 (en) * | 2008-12-11 | 2013-06-25 | General Electric Company | Inlet air heating and cooling system |
US20100242429A1 (en) * | 2009-03-25 | 2010-09-30 | General Electric Company | Split flow regenerative power cycle |
US20100257837A1 (en) * | 2009-04-14 | 2010-10-14 | General Electric Company | Systems involving hybrid power plants |
US20100285413A1 (en) * | 2009-05-06 | 2010-11-11 | General Vortex Energy, Inc. | Apparatus and Methods For Providing Uniformly Volume Distributed Combustion of Fuel |
US8616005B1 (en) | 2009-09-09 | 2013-12-31 | Dennis James Cousino, Sr. | Method and apparatus for boosting gas turbine engine performance |
US8397504B2 (en) * | 2010-02-08 | 2013-03-19 | Global Alternative Fuels, Llc | Method and apparatus to recover and convert waste heat to mechanical energy |
US20110193346A1 (en) * | 2010-02-08 | 2011-08-11 | Carlos Guzman | Method and apparatus to recover and convert waste heat to mechanical energy |
ES2387724A1 (en) * | 2010-03-05 | 2012-09-28 | Universidad Nacional De Educación A Distancia | Partial regeneration system in gas turbines of cycles combined with one or several sources of heat. (Machine-translation by Google Translate, not legally binding) |
US20110277476A1 (en) * | 2010-05-14 | 2011-11-17 | Michael Andrew Minovitch | Low Temperature High Efficiency Condensing Heat Engine for Propelling Road Vehicles |
US8881528B2 (en) * | 2010-10-22 | 2014-11-11 | Man Diesel & Turbo Se | System for the generation of mechanical and/or electrical energy |
US20120111025A1 (en) * | 2010-10-22 | 2012-05-10 | Man Diesel & Turbo Se | System For The Generation Of Mechanical And/Or Electrical Energy |
US9074494B2 (en) * | 2011-10-21 | 2015-07-07 | General Electric Company | System and apparatus for controlling temperature in a heat recovery steam generator |
US20130098313A1 (en) * | 2011-10-21 | 2013-04-25 | General Electric Company | System and apparatus for controlling temperature in a heat recovery steam generator |
US9140184B2 (en) * | 2012-05-31 | 2015-09-22 | General Electric Company | Supercharged combined cycle system with air flow bypass to HRSG and fan |
US20130318987A1 (en) * | 2012-05-31 | 2013-12-05 | General Electric Company | Supercharged combined cycle system with air flow bypass to hrsg and fan |
US11686250B2 (en) | 2012-10-26 | 2023-06-27 | Powerphase Llc | Gas turbine energy supplementing systems and heating systems, and methods of making and using the same |
US10995670B2 (en) | 2012-10-26 | 2021-05-04 | Powerphase International, Llc | Gas turbine energy supplementing systems and heating systems, and methods of making and using the same |
US9567913B2 (en) * | 2013-01-28 | 2017-02-14 | General Electric Company | Systems and methods to extend gas turbine hot gas path parts with supercharged air flow bypass |
US20140208765A1 (en) * | 2013-01-28 | 2014-07-31 | General Electric Company | Systems And Methods To Extend Gas Turbine Hot Gas Path Parts With Supercharged Air Flow Bypass |
US20150369129A1 (en) * | 2013-02-04 | 2015-12-24 | Dalkia | Facility with a gas turbine and method for regulating said facility |
EP2765283B1 (en) * | 2013-02-08 | 2017-08-09 | Ansaldo Energia Switzerland AG | Power generating unit and method for operating such a power generating unit |
US20140225372A1 (en) * | 2013-02-08 | 2014-08-14 | Alstom Technology Ltd | Power generating unit and method for operating such a power generating unit |
US20150315927A1 (en) * | 2014-05-01 | 2015-11-05 | General Electric Company | Enhanced generator capability in hot ambient temperatures |
US9850815B2 (en) * | 2014-07-08 | 2017-12-26 | 8 Rivers Capital, Llc | Method and system for power production with improved efficiency |
CN106662014A (en) * | 2014-07-08 | 2017-05-10 | 八河流资产有限责任公司 | Method and system for power production with improved efficiency |
US11365679B2 (en) | 2014-07-08 | 2022-06-21 | 8 Rivers Capital, Llc | Method and system for power production with improved efficiency |
KR20210148397A (en) * | 2014-07-08 | 2021-12-07 | 8 리버스 캐피탈, 엘엘씨 | Method and system for power production with improved efficiency |
CN106662014B (en) * | 2014-07-08 | 2018-08-10 | 八河流资产有限责任公司 | The method and system of method and power generation for heating recirculated air |
US20160010551A1 (en) * | 2014-07-08 | 2016-01-14 | 8 Rivers Capital, Llc | Method and system for power production wtih improved efficiency |
AU2019201409B2 (en) * | 2014-07-08 | 2020-07-16 | 8 Rivers Capital, Llc | Method and system for power production with improved efficiency |
US10711695B2 (en) | 2014-07-08 | 2020-07-14 | 8 Rivers Capital, Llc | Method and system for power production with improved efficiency |
US20160138431A1 (en) * | 2014-11-14 | 2016-05-19 | University Of Florida Research Foundation, Inc. | Humid Air Turbine Power, Water Extraction, and Refrigeration Cycle |
US11105498B2 (en) | 2014-11-14 | 2021-08-31 | University Of Florida Research Foundation, Inc. | Humid air turbine power, water extraction, and refrigeration cycle |
US10247408B2 (en) * | 2014-11-14 | 2019-04-02 | University Of Florida Research Foundation, Inc. | Humid air turbine power, water extraction, and refrigeration cycle |
US10443501B2 (en) | 2015-02-05 | 2019-10-15 | Powerphase Llc | Turbocooled vane of a gas turbine engine |
CN107429613B (en) * | 2015-02-05 | 2019-11-15 | 鲍尔法斯有限责任公司 | The turbine cooling blade of gas-turbine unit |
WO2016126372A1 (en) * | 2015-02-05 | 2016-08-11 | Powerphase Llc | Turbocooled vane of a gas turbine engine |
US11073084B2 (en) | 2015-02-05 | 2021-07-27 | Powerphase International, Llc | Turbocooled vane of a gas turbine engine |
US10358979B2 (en) | 2015-02-05 | 2019-07-23 | Powerphase Llc | Turbocooled vane of a gas turbine engine |
CN107429613A (en) * | 2015-02-05 | 2017-12-01 | 鲍尔法斯有限责任公司 | The turbine cooling blade of gas-turbine unit |
US20180045080A1 (en) * | 2015-03-17 | 2018-02-15 | Mitsubishi Heavy Industries, Ltd. | Intake air cooling method, intake air cooling device executing said method, and waste heat recovery facility and gas turbine plant each comprising said intake air cooling device |
US10927713B2 (en) * | 2015-03-17 | 2021-02-23 | Mitsubishi Heavy Industries, Ltd. | Intake air cooling method, intake air cooling device executing said method, and waste heat recovery facility and gas turbine plant each comprising said intake air cooling device |
DE112016001240B4 (en) | 2015-03-17 | 2022-05-25 | Mitsubishi Power, Ltd. | INLET AIR COOLING METHOD, INLET AIR COOLING DEVICE FOR CARRYING OUT THE METHOD, AND WASTE HEAT RECOVERY DEVICE AND GAS TURBINE PLANT EACH COMPRISING THE INLET AIR COOLING DEVICE |
US11359521B2 (en) * | 2015-11-05 | 2022-06-14 | William M. Conlon | Dispatchable storage combined cycle power plants |
US11156131B2 (en) * | 2016-07-28 | 2021-10-26 | Doosan Heavy Industries & Construction Co., Ltd. | Exhaust gas cooling device and method |
CN110073157B (en) * | 2016-10-11 | 2022-02-18 | 佩里·范德伯格特 | System and method for sustainable energy production |
CN110073157A (en) * | 2016-10-11 | 2019-07-30 | 佩里·范德伯格特 | For the sustainable system and method for generating energy |
WO2018146509A3 (en) * | 2016-10-11 | 2018-10-25 | Perry Van Der Bogt | System and method for sustainable generation of energy |
US11280226B2 (en) * | 2016-12-08 | 2022-03-22 | Atlas Copco Comptec, Llc | Waste heat recovery system |
US11739666B2 (en) | 2016-12-08 | 2023-08-29 | Atlas Copco Comptec, Llc | Waste heat recovery system |
US11624326B2 (en) | 2017-05-21 | 2023-04-11 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US10731554B2 (en) | 2017-09-12 | 2020-08-04 | University Of Florida Research Foundation, Inc. | Humid air turbine power, water extraction, and refrigeration cycle |
US11448141B2 (en) * | 2017-12-22 | 2022-09-20 | Finno Exergy Oy | System and method for generating power |
US11560838B2 (en) | 2018-03-02 | 2023-01-24 | 8 Rivers Capital, Llc | Systems and methods for power production using a carbon dioxide working fluid |
US10914232B2 (en) | 2018-03-02 | 2021-02-09 | 8 Rivers Capital, Llc | Systems and methods for power production using a carbon dioxide working fluid |
US20210207500A1 (en) * | 2018-05-22 | 2021-07-08 | MTU Aero Engines AG | Exhaust-gas treatment device, aircraft propulsion system, and method for treating an exhaust-gas stream |
US11560845B2 (en) | 2019-05-15 | 2023-01-24 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11867118B2 (en) | 2019-09-13 | 2024-01-09 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11346280B1 (en) | 2019-09-13 | 2022-05-31 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11060455B1 (en) | 2019-09-13 | 2021-07-13 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11852001B2 (en) | 2019-09-13 | 2023-12-26 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11092152B2 (en) | 2019-09-13 | 2021-08-17 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11098651B1 (en) | 2019-09-13 | 2021-08-24 | Bj Energy Solutions, Llc | Turbine engine exhaust duct system and methods for noise dampening and attenuation |
US11459954B2 (en) | 2019-09-13 | 2022-10-04 | Bj Energy Solutions, Llc | Turbine engine exhaust duct system and methods for noise dampening and attenuation |
US11767791B2 (en) | 2019-09-13 | 2023-09-26 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11761846B2 (en) | 2019-09-13 | 2023-09-19 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11460368B2 (en) | 2019-09-13 | 2022-10-04 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11725583B2 (en) | 2019-09-13 | 2023-08-15 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11149726B1 (en) | 2019-09-13 | 2021-10-19 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11719234B2 (en) | 2019-09-13 | 2023-08-08 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11015594B2 (en) | 2019-09-13 | 2021-05-25 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11156159B1 (en) | 2019-09-13 | 2021-10-26 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US10815764B1 (en) | 2019-09-13 | 2020-10-27 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11473997B2 (en) | 2019-09-13 | 2022-10-18 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11473503B1 (en) | 2019-09-13 | 2022-10-18 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11015536B2 (en) | 2019-09-13 | 2021-05-25 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11002189B2 (en) | 2019-09-13 | 2021-05-11 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11655763B1 (en) | 2019-09-13 | 2023-05-23 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11649766B1 (en) | 2019-09-13 | 2023-05-16 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11415056B1 (en) | 2019-09-13 | 2022-08-16 | Bj Energy Solutions, Llc | Turbine engine exhaust duct system and methods for noise dampening and attenuation |
US11629584B2 (en) | 2019-09-13 | 2023-04-18 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11408794B2 (en) | 2019-09-13 | 2022-08-09 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11236739B2 (en) | 2019-09-13 | 2022-02-01 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US10989180B2 (en) | 2019-09-13 | 2021-04-27 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US10982596B1 (en) | 2019-09-13 | 2021-04-20 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11619122B2 (en) | 2019-09-13 | 2023-04-04 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11613980B2 (en) | 2019-09-13 | 2023-03-28 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11268346B2 (en) | 2019-09-13 | 2022-03-08 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems |
US11608725B2 (en) | 2019-09-13 | 2023-03-21 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11280266B2 (en) | 2019-09-13 | 2022-03-22 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11280331B2 (en) | 2019-09-13 | 2022-03-22 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11512642B1 (en) | 2019-09-13 | 2022-11-29 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11287350B2 (en) | 2019-09-13 | 2022-03-29 | Bj Energy Solutions, Llc | Fuel, communications, and power connection methods |
US11604113B2 (en) | 2019-09-13 | 2023-03-14 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11598263B2 (en) | 2019-09-13 | 2023-03-07 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11578660B1 (en) | 2019-09-13 | 2023-02-14 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11401865B1 (en) | 2019-09-13 | 2022-08-02 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11319878B2 (en) | 2019-09-13 | 2022-05-03 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11560848B2 (en) | 2019-09-13 | 2023-01-24 | Bj Energy Solutions, Llc | Methods for noise dampening and attenuation of turbine engine |
US10961912B1 (en) | 2019-09-13 | 2021-03-30 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11859482B2 (en) | 2019-09-13 | 2024-01-02 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11971028B2 (en) | 2019-09-13 | 2024-04-30 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US10907459B1 (en) | 2019-09-13 | 2021-02-02 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US10895202B1 (en) | 2019-09-13 | 2021-01-19 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11555756B2 (en) | 2019-09-13 | 2023-01-17 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11530602B2 (en) | 2019-09-13 | 2022-12-20 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11879363B2 (en) * | 2020-03-30 | 2024-01-23 | Xuanhua Guo | Combined system of intercooled recuperative gas turbine and refrigerant compound bottoming cycle |
US11635074B2 (en) | 2020-05-12 | 2023-04-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US11708829B2 (en) | 2020-05-12 | 2023-07-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US10968837B1 (en) | 2020-05-14 | 2021-04-06 | Bj Energy Solutions, Llc | Systems and methods utilizing turbine compressor discharge for hydrostatic manifold purge |
US11898504B2 (en) | 2020-05-14 | 2024-02-13 | Bj Energy Solutions, Llc | Systems and methods utilizing turbine compressor discharge for hydrostatic manifold purge |
US11542868B2 (en) | 2020-05-15 | 2023-01-03 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11959419B2 (en) | 2020-05-15 | 2024-04-16 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11624321B2 (en) | 2020-05-15 | 2023-04-11 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11698028B2 (en) | 2020-05-15 | 2023-07-11 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11428165B2 (en) | 2020-05-15 | 2022-08-30 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11434820B2 (en) | 2020-05-15 | 2022-09-06 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11208880B2 (en) | 2020-05-28 | 2021-12-28 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11365616B1 (en) | 2020-05-28 | 2022-06-21 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11814940B2 (en) | 2020-05-28 | 2023-11-14 | Bj Energy Solutions Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11603745B2 (en) | 2020-05-28 | 2023-03-14 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11313213B2 (en) | 2020-05-28 | 2022-04-26 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11109508B1 (en) | 2020-06-05 | 2021-08-31 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11723171B2 (en) | 2020-06-05 | 2023-08-08 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11129295B1 (en) | 2020-06-05 | 2021-09-21 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11627683B2 (en) | 2020-06-05 | 2023-04-11 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US10961908B1 (en) | 2020-06-05 | 2021-03-30 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11891952B2 (en) | 2020-06-05 | 2024-02-06 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11378008B2 (en) | 2020-06-05 | 2022-07-05 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11746698B2 (en) | 2020-06-05 | 2023-09-05 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11208953B1 (en) | 2020-06-05 | 2021-12-28 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11300050B2 (en) | 2020-06-05 | 2022-04-12 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11598264B2 (en) | 2020-06-05 | 2023-03-07 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11174716B1 (en) | 2020-06-09 | 2021-11-16 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US11643915B2 (en) | 2020-06-09 | 2023-05-09 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US11629583B2 (en) | 2020-06-09 | 2023-04-18 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11085281B1 (en) | 2020-06-09 | 2021-08-10 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11319791B2 (en) | 2020-06-09 | 2022-05-03 | Bj Energy Solutions, Llc | Methods and systems for detection and mitigation of well screen out |
US11066915B1 (en) | 2020-06-09 | 2021-07-20 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11339638B1 (en) | 2020-06-09 | 2022-05-24 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11512570B2 (en) | 2020-06-09 | 2022-11-29 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11867046B2 (en) | 2020-06-09 | 2024-01-09 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11566506B2 (en) | 2020-06-09 | 2023-01-31 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11022526B1 (en) | 2020-06-09 | 2021-06-01 | Bj Energy Solutions, Llc | Systems and methods for monitoring a condition of a fracturing component section of a hydraulic fracturing unit |
US11939854B2 (en) | 2020-06-09 | 2024-03-26 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11261717B2 (en) | 2020-06-09 | 2022-03-01 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11015423B1 (en) | 2020-06-09 | 2021-05-25 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11111768B1 (en) | 2020-06-09 | 2021-09-07 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US11208881B1 (en) | 2020-06-09 | 2021-12-28 | Bj Energy Solutions, Llc | Methods and systems for detection and mitigation of well screen out |
US10954770B1 (en) | 2020-06-09 | 2021-03-23 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11898429B2 (en) | 2020-06-22 | 2024-02-13 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11598188B2 (en) | 2020-06-22 | 2023-03-07 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11933153B2 (en) | 2020-06-22 | 2024-03-19 | Bj Energy Solutions, Llc | Systems and methods to operate hydraulic fracturing units using automatic flow rate and/or pressure control |
US11408263B2 (en) | 2020-06-22 | 2022-08-09 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11639655B2 (en) | 2020-06-22 | 2023-05-02 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11732565B2 (en) | 2020-06-22 | 2023-08-22 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11208879B1 (en) | 2020-06-22 | 2021-12-28 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11125066B1 (en) | 2020-06-22 | 2021-09-21 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11028677B1 (en) | 2020-06-22 | 2021-06-08 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11952878B2 (en) | 2020-06-22 | 2024-04-09 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11939853B2 (en) | 2020-06-22 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods providing a configurable staged rate increase function to operate hydraulic fracturing units |
US11236598B1 (en) | 2020-06-22 | 2022-02-01 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11572774B2 (en) | 2020-06-22 | 2023-02-07 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11428218B2 (en) | 2020-06-23 | 2022-08-30 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11415125B2 (en) | 2020-06-23 | 2022-08-16 | Bj Energy Solutions, Llc | Systems for utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11719085B1 (en) | 2020-06-23 | 2023-08-08 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11466680B2 (en) | 2020-06-23 | 2022-10-11 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11566505B2 (en) | 2020-06-23 | 2023-01-31 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11649820B2 (en) | 2020-06-23 | 2023-05-16 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11473413B2 (en) | 2020-06-23 | 2022-10-18 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11661832B2 (en) | 2020-06-23 | 2023-05-30 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11939974B2 (en) | 2020-06-23 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11299971B2 (en) | 2020-06-24 | 2022-04-12 | Bj Energy Solutions, Llc | System of controlling a hydraulic fracturing pump or blender using cavitation or pulsation detection |
US11255174B2 (en) | 2020-06-24 | 2022-02-22 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11512571B2 (en) | 2020-06-24 | 2022-11-29 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11149533B1 (en) | 2020-06-24 | 2021-10-19 | Bj Energy Solutions, Llc | Systems to monitor, detect, and/or intervene relative to cavitation and pulsation events during a hydraulic fracturing operation |
US11668175B2 (en) | 2020-06-24 | 2023-06-06 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11692422B2 (en) | 2020-06-24 | 2023-07-04 | Bj Energy Solutions, Llc | System to monitor cavitation or pulsation events during a hydraulic fracturing operation |
US11746638B2 (en) | 2020-06-24 | 2023-09-05 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11391137B2 (en) | 2020-06-24 | 2022-07-19 | Bj Energy Solutions, Llc | Systems and methods to monitor, detect, and/or intervene relative to cavitation and pulsation events during a hydraulic fracturing operation |
US11542802B2 (en) | 2020-06-24 | 2023-01-03 | Bj Energy Solutions, Llc | Hydraulic fracturing control assembly to detect pump cavitation or pulsation |
US11506040B2 (en) | 2020-06-24 | 2022-11-22 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11274537B2 (en) | 2020-06-24 | 2022-03-15 | Bj Energy Solutions, Llc | Method to detect and intervene relative to cavitation and pulsation events during a hydraulic fracturing operation |
US11220895B1 (en) | 2020-06-24 | 2022-01-11 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11193360B1 (en) | 2020-07-17 | 2021-12-07 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11255175B1 (en) | 2020-07-17 | 2022-02-22 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11920450B2 (en) | 2020-07-17 | 2024-03-05 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11608727B2 (en) | 2020-07-17 | 2023-03-21 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11603744B2 (en) | 2020-07-17 | 2023-03-14 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11365615B2 (en) | 2020-07-17 | 2022-06-21 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11193361B1 (en) | 2020-07-17 | 2021-12-07 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11994014B2 (en) | 2020-07-17 | 2024-05-28 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11639654B2 (en) | 2021-05-24 | 2023-05-02 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11867045B2 (en) | 2021-05-24 | 2024-01-09 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11732563B2 (en) | 2021-05-24 | 2023-08-22 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US3796045A (en) | Method and apparatus for increasing power output and/or thermal efficiency of a gas turbine power plant | |
US5622044A (en) | Apparatus for augmenting power produced from gas turbines | |
US2115338A (en) | Gas turbine system | |
US6422019B1 (en) | Apparatus for augmenting power produced from gas turbines | |
US6615585B2 (en) | Intake-air cooling type gas turbine power equipment and combined power plant using same | |
US6745574B1 (en) | Microturbine direct fired absorption chiller | |
US6718771B1 (en) | Gas turbine operative at high ambient temperatures | |
US20030182944A1 (en) | Highly supercharged gas-turbine generating system | |
CN101368767B (en) | Indirect air cooling method and system for working medium adopting parallel-connection positive and reverse refrigeration cycle | |
US4093868A (en) | Method and system utilizing steam turbine and heat pump | |
KR19990044175A (en) | Method and apparatus for intake cooling of gas turbine and internal combustion engine starter | |
US20020053196A1 (en) | Gas pipeline compressor stations with kalina cycles | |
US4271665A (en) | Installation for generating pressure gas or mechanical energy | |
GB2280224A (en) | Method of and apparatus for augmenting power produced from gas turbines | |
US3006146A (en) | Closed-cycle power plant | |
CN103775148A (en) | Self-cooled thermal power acting method | |
US6119445A (en) | Method of and apparatus for augmenting power produced from gas turbines | |
US4212168A (en) | Power producing dry-type cooling system | |
US4311010A (en) | Gas-powered engine adapted to utilize stored solar heat energy and compressed gas power system | |
US4445639A (en) | Heat pump systems for residential use | |
CN113074093B (en) | Wind generating set with heat pump self-deicing system and working method thereof | |
Erickson et al. | Absorption refrigeration cycle turbine inlet conditioning | |
Bassily | Performance improvements of the recuperated gas turbine cycle using absorption inlet cooling and evaporative aftercooling | |
US4444021A (en) | Heat pump systems for residential use | |
US4444018A (en) | Heat pump systems for residential use |