KR102566355B1 - Gas Turbine Blower/Pump - Google Patents

Abstract

A low-emission, high-efficiency gas turbine engine operating on a combination of natural gas and biogas as fuel drives a high-efficiency turbo blower or high-efficiency turbo pump system in combination with a heat recovery system, and in other embodiments a generator is provided or from the exhaust gas. provides evaporative cooling from utilizing the remainder of the waste heat.

Description

Gas Turbine Blower/Pump

The present invention relates to aeration blower and pump technology. In particular, the present invention relates to a gas turbine engine fueled by natural gas or biogas, which is a by-product of wastewater treatment, wherein the gas turbine engine directly drives a blower or pump and uses recovered heat from the gas turbine to generate gas. The turbine inlet temperature is increased to 1800 to 2000 degrees Fahrenheit, and the generator system driven by the recuperator cooling system or the downstream system discharges the waste heat.

It is one aspect of the present invention to combine direct mechanical power from a gas turbine fueled by natural gas and biogas to the impeller of a pump or blower through heat recovery from the exhaust gas in the same design; One high-efficiency system.

Blowers and pumps are used in a variety of applications including water and wastewater treatment, food and beverage, oil and gas, power generation, pulp and paper, and pharmaceutical industries. Such blowers typically deliver airflow at high volumes and pressures less than 1.0 atm of discharge pressure. The pump delivers a low or high water flow at the changing head. In the past, blowers and pumps were driven by electric motors. Electric motors demand electricity generated on site by using various electric co-generators or by accessing this electricity from the electric grid. Electric motor driven blowers and pumps require several complex electrical components including variable frequency drives, sine wave filters, line input reactors, harmonic filters and power transformers. These electrical components generate electrical losses and waste heat resulting in an estimated 12 to 15% energy loss.

In some cases, a reciprocating gas or diesel engine drives the blowers and pumps. These reciprocating engines are inefficient, noisy, bulky and produce large amounts of waste heat and it is difficult to retrofit them to meet evolving emission standards. On the other hand, gas turbines have evolved over the years to be highly efficient and low-emissions as they are used in a variety of applications from aerospace, aviation and power generation. In some cases, gas turbine engines are used to drive high-pressure gas compressors that deliver natural gas, oxygen, or nitrogen to pipelines at multiple atmospheric discharge pressures. During compression of the gas, gas turbine exhaust heat and compression thermal energy are produced as by-products and are discharged as waste heat.

Thus, wasted energy in the use of electric motors and wasted energy in the use of reciprocating engines or gas turbine engines, combined with wasted energy as a result of compression, represents a significant energy loss in the operation of compressors, blowers and pumps. In addition, biogas is a free byproduct of waste disposal and is used alone or in combination with natural gas to directly drive blowers or pumps when properly treated instead of being flared or discharged into the atmosphere. It is possible to produce the fuel required for the gas turbine engine, thereby significantly reducing the operating cost of the waste disposal facility. Recently, we are starting to see an emerging global trend of using biogas as a fuel to help wastewater treatment plants achieve their goal of becoming energy neutral.

Various reciprocating engines or gas turbine engines have hitherto been made in the prior art.

For example, US 9140267 discloses a compressor housing defining a gas inlet flow path and a gas outlet and a rotatable impeller wheel between the gas inlet flow path and the gas outlet. The inner wall of the housing defines a surface very close to the radial outer edge of the impeller wheel vane that sweeps across the surface as the wheel rotates. An opening is provided in the inner wall at the surface. A port is provided in the housing in gas communication with an opening for diverting gas away from the inlet flow path during relatively low flow conditions. A gas movement device is disposed outside the inlet flow path and connected to the port, and the pump is operable to selectively remove gas through the opening and port in a direction away from the inlet flow path.

Another device relating to a turbomachine comprising a radial flow impeller and one or more of various features enhancing the performance of the machine in which the turbomachine is employed is disclosed in US Pat. No. 8,506,237. For example, when a turbomachine is used in a dynamometer, one of the features is a variable-restriction intake that allows the flow rate to be adjusted with the impeller. The impeller shroud and shroud guide are each movable relative to the impeller. An exhaust diffuser facilitates an increase in the range of shaft power and a reduction in harmful vibration and noise. The turbomachine may also include a unique impeller blade configuration that cooperates with an adjustable intake and exhaust diffuser to enhance flow through the turbomachine.

US 8327644 shows a micro gas turbine engine for use in a turbo heater or cogeneration application is described. The micro gas turbine engine includes a fuel delivery system that minimizes the development of deposits in the air fuel passages. To this end, the fuel delivery channel formed between the fuel deflector and the slinger body is formed with a contoured or wavy surface. A fuel deflector ring is interposed between the fuel delivery channel and the slinger impeller to facilitate flow of the air-fuel mixture to the combustion chamber.

Another centrifugal pump includes an axial diffuser having vanes angularly spaced downstream of the impeller by a crossover gap formed in the pump housing and a rotatable impeller having radial blades to drive the fluid affected by the impeller. US 8240976 relates to a centrifugal pump housing which must pass through the crossover gap to the axial diffuser, wherein an improvement is circumferentially mounted with the axial diffuser and guides the fluid flow from the impeller through the crossover gap to the shaft at least a single axial diffuser vane extension extending into the crossover gap driven into the diffuser, the diffuser vane extension imparting a torsional force to the fluid received from the impeller to minimize any turbulence present in the fluid stream; is constructed, designed and formed into a structure with tandem vanes for the fluid stream as it exits the impeller, whereby the pump moves flat or positive as the flow head curve continues to rise towards shut-off. This is because it shows the pump head curve modified to remove the slope.

US 8096127 is misalignment of the center of the rotating shaft of the supercharger turbine and the center of the rotating shaft of the supercharger compressor, or the center of the rotating shaft of the supercharger turbine due to the heat of the exhaust gas, the center of the rotating shaft of the supercharger compressor, and the center of the rotating shaft of the generator can prevent misalignment of; can reduce vibrations of these rotational axes; An exhaust turbocharger that can improve the reliability of the entire supercharger is described. An exhaust turbocharger has a casing supporting a turbine unit and a compressor unit. The lower end of the casing constitutes a leg portion, and the leg portion is fixed to a base disposed on the floor. A generator with a rotating shaft is connected to the rotating shafts of the turbine unit and the compressor unit.

Moreover, US 8931291 shows a system comprising a gas compressor comprising an engine, a compressor driven by the engine, and a vapor absorption cycle (VAC) system driven by waste heat from the compressor, the VAC system comprising at least one medium configured to cool. In another embodiment, a method is provided that includes generating waste heat while compressing a gas, driving a vapor absorption cycle (VAC) system with the waste heat, and cooling at least one medium through the VAC system. .

Finally, US 746813 relates to a centrifugal compressor applied as an organic Rankine cycle turbine by operating the machine in reverse. To accommodate the higher pressures when operating as a turbine, suitable refrigerants are selected such that pressures and temperatures are maintained within established limits. This adaptation of existing and relatively inexpensive equipment to applications that would otherwise be uneconomical allows convenient and economical utilization of energy that would otherwise be lost to the atmosphere by waste heat.

It is an object of the present invention to provide an improved gas turbine engine, and in particular an improved aeration blower and pump.

It is one aspect of the present invention to combine direct mechanical power from a gas turbine fueled by natural gas and biogas to the impeller of a pump or blower via heat recovery from the exhaust gas in the same design; One high-efficiency system.

One aspect of the present invention is a first inlet and a first outlet; a second inlet and a second outlet; an impeller disposed between the first inlet and the first outlet; a gas turbine disposed between the second inlet and the second outlet; a combustion mixture introduced into the second inlet to drive the gas turbine and discharged through the second outlet; an impeller disposed between the first inlet and the first outlet; and the gas turbine coupled to the impeller to drive the impeller and move fluid from the first inlet to the first outlet.

Another aspect of the present invention is to provide an integrated gas turbine unit comprising: a working fluid inlet and a working fluid outlet; an impeller disposed between the working fluid inlet and the working fluid outlet; a combustor disposed between the inlet and outlet to burn a mixture of air and biofuel to drive the turbine; and a shaft having a rotation axis, wherein the turbine and impeller are coaxially connected to the shaft to move the working fluid.
Another aspect of the present invention relates to a method of driving an impeller in a gas turbine, the method comprising: coaxially connecting the impeller and the turbine; rotationally driving the turbine by rotatably driving the turbine and impeller and burning a mixture of air and fuel to produce exhaust gas; and capturing waste heat from the exhaust gas to preheat the air and move a working fluid by the impeller.

Another aspect of the present invention is to provide a method of driving an impeller in a gas turbine, the method comprising: coaxially connecting the impeller and the turbine; rotationally driving the gas turbine by rotatably driving the turbine and impeller and burning a mixture of air and fuel to produce exhaust gas; and preheating the air by capturing waste heat from the exhaust gas as it re-enters the gas turbine at a higher pressure ratio of 4.5 at higher temperatures of 1800 and 2000 degrees Fahrenheit compared to the inlet; It expands through the turbine to further move the working fluid by the impeller. The gas expanding through the gas turbine enters the power turbine at high pressure and high temperature to rotate the power turbine, which in turn variably rotates the shaft directly connected to the pump and the impeller of the blower to change the operating air of the fluid. convey
The higher pressure ratio of 4.5 mentioned above is the same as compared to atmospheric and is given as an example. Moreover, when considering the embodiments shown in FIGS. 14 to 19 of this specification, pressure ratios of 4.4 and 10 or more (compared to atmospheric) appear and are given as examples; This range is due, at least in part, to a configuration change utilizing the three shafts 2, 3 and 17 and the intercooler 31 described below. Further, the example temperature range of 1800 to 2000 degrees Fahrenheit mentioned above may extend to 1700 to 2100 degrees or more in the examples mentioned in the embodiments of FIGS. 14 to 19 .
Another aspect of the present invention is a first inlet and a first outlet; a second inlet and a second outlet; an impeller disposed between the first inlet and the first outlet; a compressor for increasing air pressure; a recuperator for increasing the temperature of the air at the elevated pressure; a gas turbine disposed between the second inlet and the second outlet; a combustor for receiving a combustion mixture comprising air at the elevated temperature and at the elevated pressure and fuel introduced into the second inlet to drive the gas turbine and discharged through the second outlet; an impeller disposed between the first inlet and the first outlet; A unit having the gas turbine and the impeller coupled directly to a shaft to drive the impeller and move fluid from the first inlet to the first outlet. In one embodiment, a gas turbine includes a high-pressure turbine and a free-running turbine, the free-running turbine and the impeller being coupled to a common shaft. In another embodiment, a gas turbine includes a high-pressure turbine, a low-pressure turbine, and a free-running turbine, wherein the free-running turbine and the impeller are coupled to a common shaft.
Another aspect of the invention relates to an integrated gas turbine unit comprising: a working fluid inlet and a working fluid outlet; an impeller disposed between the working fluid inlet and the working fluid outlet; first and second compressors for increasing air pressure; an intercooler disposed between the first and second compressors to reduce the temperature of the air before the second compressor; a heat exchanger for increasing the temperature of the air at the elevated pressure; a combustor disposed between the inlet and outlet to combust the mixture of air and biofuel at the elevated pressure and elevated temperature to drive a gas turbine with exhaust gas from the gas turbine; the recuperator for recovering heat from the exhaust gas from the gas turbine to preheat the mixture of air and biofuel at the elevated pressure and temperature; and a shaft having a rotational axis coupled to the shaft such that a free power turbine and an impeller move a working fluid between the working fluid inlet and the working fluid outlet.
Another aspect of the invention relates to a method of driving an impeller with a gas turbine, the method comprising: cooling air with an intercooler heat exchanger; compressing the cooled air in a compressor; coaxially coupling the impeller and the free-running turbine to a shaft; rotationally driving the gas turbine by rotatably driving the gas turbine and impeller and burning the mixture of cooled compressed air and fuel to produce exhaust gas; and capturing waste heat from the exhaust gas with a recuperator to preheat the air.

These and other objects and features of the present invention will be explained in conjunction with the following figures.

The detailed description that follows will be better understood in conjunction with the accompanying drawings.
1 is a perspective view taken from a right front side view of a gas turbine unit 10;
2 is a perspective view taken from a rear right view of the gas turbine unit 10;
3 is a front view of the gas turbine unit 10;
4 is a left side view of the gas turbine blower unit 10;
5 is a right side view of the gas turbine blower unit 10;
6 is a rear view of the gas turbine unit 10;
7 is a top plan view of the gas turbine unit 10;
8 is a bottom plan view of the gas turbine unit 10;
FIG. 9 is a cross-sectional view of one embodiment of the present invention relating to a gas turbine blower unit 12 taken along line 9-9 of FIG. 4 showing the rotor mounted in the device with its major components.
10 shows a gas turbine compressor driven by a high-pressure gas turbine, a combustor of natural gas or biogas, a single blower impeller driven by a free-running turbine, and a system for recovering heat from the exhaust gas to be used to increase the gas turbine inlet temperature. A schematic diagram of one embodiment of a blower system, the gas turbine blower unit shown in FIG. 9 having a heat exchanger.
11 is a cross-sectional view of another embodiment of the present invention relating to gas turbine pump unit 16 taken along line 11-11 of FIG. 7;
12 shows a gas turbine compressor driven by a high-pressure gas turbine, a combustor of natural gas or biogas, a single pump impeller driven by a free-running turbine, and a system for recovering heat from the exhaust gas to be used to increase the gas turbine inlet temperature. Schematic diagram of another embodiment of a gas turbine pump unit, device, system shown in FIG. 11 with a recuperator.
13 is a chart showing one example of efficiency and cost reduction of the present invention.
14 shows a high gas turbine compressor driven by a high-pressure gas turbine, a combustor of natural gas or biogas, a single pump impeller driven by a free-running turbine, and recovering heat from the exhaust gas to be used to increase the gas turbine inlet temperature. Schematic diagram of another embodiment of a gas turbine blower unit, having a recuperator and an intercooler before the high pressure gas turbine compressor.
Fig. 15 is a cross-sectional view of the embodiment shown in the schematic diagram of Fig. 14;
Fig. 16 is a perspective sectional view of Fig. 15;
Fig. 17 is a front view of Fig. 15;
Fig. 18 is a perspective view of another embodiment shown in Figs. 14-17 taken from above and from one side of the unit;
Fig. 19 is a perspective view of another embodiment shown in Figs. 14-17 taken from above and from one side of the unit;

Like parts are denoted by like reference numerals throughout the drawings.

Two specific embodiments of the present invention will be described below. These examples are merely illustrative of the present invention. It should be understood that in the development of any such actual implementation, such as in an engineering or design project, many detailed decisions must be made to achieve the developer's specific goals, which may vary from embodiment to embodiment.

The embodiments discussed below include an optional gearbox 13 for reducing or increasing the rotor speed driven by the free power turbine, an optional heat exchanger 27 and an exhaust gas downstream from the recuperator 60. may include an optional generator or refrigerant chiller 29 to recover waste heat from the

1-8 show a gas turbine module 12, combustion air inlet 14, blower or pump module 16, exhaust plenum 18, exhaust outlet 20 and inlet 22. It generally illustrates one embodiment of the present invention relating to a gas turbine unit or device 10 having In one embodiment, inlet 22 is an air inlet or primary inlet to blower 26, or a working fluid inlet 24. In the second embodiment described herein, the inlet 22 is the water inlet 28 for the pump 40 described herein.

The gas turbine device 10 also includes an outlet or first outlet or working fluid outlet 32 .

In one embodiment, the first outlet or working fluid outlet 32 is an air outlet 34 . More specifically, air through the blower inlet 24 is compressed by the blower impeller 37 and then expelled through the blower scroll or volute channel 36 .

For example, in another embodiment shown in FIG. 7 , the gas turbine unit 10 includes a water inlet 28 , a pump impeller 40 and a water outlet 42 .

Integration of assemblies as described herein not only produces an energy efficient blower/pump system 10, but also provides a unit 10 that is compact in size and design. In one embodiment, for example, a unit as shown in FIG. 9 may be 39 inches wide and 37 inches high. However, these dimensions are given only as examples as other smaller sizes may be experienced depending on the size requirements to achieve rated flow rates in the range of 1,000 to 50,000 SCFM and discharge pressures of 0.5 to 1.2 atm.

1, 2, 3, 4, 5, 6, 8, 9 and 10 generally show a centrifugal blower impeller 37, a gas turbine axial and/or centrifugal compressor 50, A gas turbine blower comprising a natural gas or biogas combustor (70), a high pressure axial and/or radial gas turbine (80), an axial and/or radial free power turbine (90) and a recuperator or heat exchanger (60). One embodiment of system 12 is shown.

On the blower side, the air through the blower inlet 24 is compressed by the blower impeller 37 and then it exits the blower scroll 36 and then exits the outlet 34 . The blower impeller 37 is driven by a free power turbine 90 via a common shaft or shaft 17.

On the gas turbine side, air passes through the inlet 14; It is compressed by compressor 50 to a pressure above ambient pressure of, for example, a pressure ratio of 4 to 5, at which point the air enters a recuperator 60 which increases the air temperature. The heated air is combusted with fuel of natural gas/biogas in a combustor (70), the high pressure and temperature gas is expanded in a high pressure gas turbine (80) and then the gas is expanded again in a free power turbine (90). . Finally, the gas exits the recuperator 60 which recovers heat to the air prior to the combustor 70. Compressor 50 is driven by high-pressure gas turbine 80 via a common shaft or shaft 2.

FIG. 10 illustrates one embodiment of the gas turbine blower system 12 shown in FIGS. 1, 2, 3, 4, 5, 6, 8 and 9 . The air flow inlet 24 of the blower 37 is, in one example, approximately 3000 to 15000 cubic feet per minute (CFM). In one example, the exhaust air through outlet 34 has a pressure ratio of 1.2 to 1.5 for the wastewater treatment system.

Free power turbine 90 provides power to meet the requirements of the working fluid. As shown in the figure, free turbine 90 is a single stage axial turbine, but it may be a single radial turbine or may have multiple expansion stages.

A controller 21 such as a computer or the like is used to adjust the fuel in the air flow inlet 14 of the compressor 50 and the natural gas/biogas 25 depending on the requirements of the exhaust air 34 . To reduce or increase the speed of the blower impeller 37, an optional gearbox 13 may be installed on the shaft or axis of rotation 17 between the blower 37 and the free power turbine 90. To further increase energy efficiency, an optional heat exchanger (27) and an optional generator or chiller system (29) may be installed at the outlet of the heat exchanger (60).

1, 2, 3, 4, 6, 7, 8, 11 and 12 generally show a pump impeller 40, a gas turbine axial and/or centrifugal compressor 50, a natural Gas turbine pump units, devices and systems comprising a gas or biogas combustor (70), a high pressure axial and/or radial turbine (80), an axial and/or radial free power turbine (90) and a recuperator (60). Another embodiment of the present invention relating to (16) is shown.

On the pump side, water through the pump inlet 28 is compressed by the pump impeller 40 and then it exits the pump scroll or volute passage 36 and then exits the outlet 42 . The pump impeller 40 is driven by a free power turbine 90 via a common shaft or shaft 17.

FIG. 12 shows the present invention described in FIGS. 1 , 2 , 3 , 4 , 6 , 7 , 8 , 11 of a gas turbine pump unit, device and system 16 with different options on a block diagram. An embodiment of the invention is shown. The water flow inlet 28 of pump impeller 40 may be, for example, approximately 15,000 to 50,000 gallons per minute (GPM), and the discharge through outlet 42 may have a variable pressure to meet the requirements of the wastewater treatment system. Rain is provided. The controller 21 is used to regulate the fuel in the air flow inlet 14 of the compressor 50 and the natural gas/biogas 25 depending on the requirements of the discharge water through the outlet 42 . To reduce or increase the speed of the pump impeller 40, an optional gearbox 13 may be installed on the shaft or shaft 17 between the pump 40 and the free-power turbine 90. To further increase energy efficiency, an optional heat exchanger 27 and an optional electric generator or chiller system 29 may be installed at the outlet of the recuperator 60.

13 is a chart illustrating efficiency and cost savings by utilizing the traditional electric motor option of a conventional method previously employed versus a gas turbine system 10 as described herein.

In particular, FIG. 13 shows the operating cost of an electric motor option in several states, Florida, Texas and California versus the operating cost of a gas turbine system 10 as described herein for the same location in Florida, Texas and California. Illustrating one example, it shows a 31% cost savings in Florida, a 40% cost savings in Texas and a 33% cost savings in California to run a system with natural gas; Based on the historically high level of cost of current electricity costs and natural gas prices. The savings will be significantly higher when biogas is added to natural gas, especially if the system is operated with biogas only.
14 to 19 show another embodiment of the present invention in which like parts are numbered with the same reference numerals as above.
In addition to the components described above, FIG. 14 shows a high pressure gas turbine compressor 51 connected with the high pressure turbine 80 on a common shaft 2 . The embodiment shown in FIG. 14 also includes a low pressure gas turbine compressor 53 , which is connected to the low pressure turbine 81 on a common shaft 3 . The free power turbine 90 is connected to the lower blower impeller 37 by means of a shaft 17 . The embodiment shown in FIG. 14 also includes an intercooler 31 disposed between the low pressure gas turbine compressor 53 and the high pressure gas turbine compressor 51 .
Cooling of the inlet air 14 takes place between the two compressor stages 51 and 53 by means of an intercooler 31 . This improves the efficiency of the unit because the cooled air 14 in the high pressure turbine compressor 51 will be more easily compressed than the heated air. After the high-pressure gas turbine compressor 51, the air is then heated by a recuperator or heat exchanger 60 before the air enters the combustor 70 and thus, if the air is at a higher temperature, the air and Efficiency again improves as less heat input will be required to burn the natural gas (biogas) mixture.
Further, the embodiments shown in FIGS. 14-19 illustrate the optimization of a power turbine with a dual inlet design as shown. The design as shown also shows prioritized cooling flow optimization in the past, as well as flow split optimization.
Moreover, a turbine as shown is a suitable candidate for additive manufacturing (3D printing) for efficient manufacturing.
The embodiment shown in FIGS. 14-19 is a highly efficient intercooled and reheated gas turbine drive that delivers a high volume of air through an intercooler, a heat exchanger and a CMHP (e.g. for a range of 230 KW to 1.2 MW). It shows a turbo blower.
The unit can be operated on biogas (which is a by-product (WWTP)) and/or natural gas instead of electricity or fossil fuel, which has lower emissions, operating costs of up to 80% with biogas and 40% with natural gas. reduces The units shown can also be used to retrofit old and existing technology.
Other advantages of the present invention include:
- The system can replace conventional electric blowers; The unit is powered by a gas turbine engine instead of an electric motor, reducing dependence on the electrical grid.
- reduce energy consumption;
- Utilization of fuel-flexible clean combustors that allow combustion of biogas with low polluting emissions, provide clean power and prevent flaring on WWTPs.
- Reduced operating costs.
as an example
In one embodiment, the low pressure compressor 53 has a compression ratio of about 3 relative to atmospheric, and a temperature rise of about 125K (235F) to an inlet temperature (293K). Intercooler 31 reduces the temperature of -418K (125 + 293) back to the inlet temperature (293K). The high-pressure compressor 51 has a pressure ratio of about 3 and a temperature rise of about 125K (235F) to the inlet temperature. The total pressure ratio PR of the described gas turbine unit PR = 9 is equal to the PR of the low pressure compressor 53 . multiple of the PR of the high-pressure compressor 51; That is, PR = 3 x 3 = 9. The pressure rise is distributed almost evenly between the two pressurizer stages. For the three turbines described in Figures 14-19, similar logic applies. The pressure ratio is equally distributed among the turbine stages. PR single stage = 2.08, and PR machine = 2.08 x 2.08 x 2.08.
The low pressure gas turbine compressor 53 draws air from the atmosphere and delivers air from, for example, three times the atmosphere. The high-pressure gas turbine compressor 51 transfers air from, for example, 3 times the atmosphere to 9 times the atmosphere.
The term free power turbine 90 is a term well known to those skilled in the art and generally refers to the one that powers the blower impeller.

Claims (20)

For units:
(a) a working fluid inlet and a working fluid outlet;
(b) an air inlet and an exhaust outlet;
(c) an impeller disposed between the working fluid inlet and the working fluid outlet;
(d) a first compressor and a second compressor for raising the pressure of air, the first compressor being driven by a low pressure turbine through a first common shaft and the second compressor being driven by a high pressure turbine through a second common shaft; driven by the first compressor and the second compressor;
(e) a recuperator for increasing the temperature of the air at the elevated pressure;
(f) a gas turbine disposed between the air inlet and the exhaust outlet, the gas turbine including the low pressure turbine, the high pressure turbine and a free powered turbine; and
(g) a combustor receiving a combustion mixture comprising air and fuel at the elevated temperature and pressure, driving the gas turbine and discharging it through the exhaust outlet;
(h) the free power turbine is driven by exhaust gas from the low pressure turbine;
(i) the recuperator recovers heat from the exhaust gas from the free power turbine to preheat the combustion mixture;
(j) the free power turbine and the impeller are coupled to a third common shaft to drive the impeller and move the working fluid from the working fluid inlet to the working fluid outlet. According to claim 1,
wherein the impeller is an air blower when the working fluid is air. According to claim 1,
wherein the impeller is a pump when the working fluid is water. According to claim 1,
and an intercooler disposed between the first and second compressors to cool the air between the first and second compressors. According to claim 4,
wherein the fuel is selected from the group of natural gas and biogas. According to claim 5,
and a gearbox disposed between the impeller and the free power turbine. According to claim 6,
and a heat exchanger disposed downstream of the recuperator. According to claim 7,
and a generator or chiller disposed downstream of the recuperator. In the integrated gas turbine unit:
(a) a working fluid inlet and a working fluid outlet;
(b) an air inlet and an exhaust outlet;
(c) an impeller disposed between the working fluid inlet and the working fluid outlet;
(d) a first compressor and a second compressor for increasing the pressure of air, the first compressor driven by a first compression turbine through a first common shaft and the second compressor through a second common shaft; said first compressor and said second compressor driven by a second compression turbine;
(e) an intercooler disposed between the first and second compressors to reduce the temperature of the air before the second compressor;
(f) a heat exchanger for increasing the temperature of the air at the elevated pressure;
(g) a gas turbine disposed between said air inlet and said exhaust outlet, said gas turbine comprising said first compression turbine, said second compression turbine and a free-running turbine; and
(h) a combustor receiving a combustion mixture comprising air and fuel at the elevated temperature and elevated pressure, driving the gas turbine and discharging it through the exhaust outlet;
(i) the first compression turbine is in communication with the second compression turbine;
(j) the recuperator recovers heat from the exhaust gas from the free power turbine to preheat the combustion mixture;
(k) wherein the free power turbine and the impeller are coupled to a third common shaft to drive the impeller and move the working fluid from the working fluid inlet to the working fluid outlet. A method for driving an impeller with a free power turbine:
coaxially connecting the impeller and the free power turbine through a shaft;
The air pressure is raised in a first compressor connected to a first compression turbine through a first common shaft and then the air pressure is reduced through a second compressor driven by a second compression turbine connected through a second common shaft. elevating step;
driving the free-powered turbine to rotate, rotatably driving the first compression turbine and the second compression turbine by burning a mixture of air and fuel and exhaust from the first compression turbine and the second compression turbine; rotationally driving the free power turbine by directing gas to the free power turbine to rotatably drive the free power turbine and impeller along the shaft;
preheating the air by capturing waste heat from the free power turbine into a recuperator; and
Disposing the impeller between a working fluid inlet and a working fluid outlet. According to claim 10,
cooling the air with an intercooler heat exchanger disposed between the first compressor and the second compressor. According to claim 11,
wherein the impeller is an air blower when the working fluid is air. According to claim 11,
wherein the impeller is a pump when the working fluid is water. According to claim 11,
wherein the fuel is selected from the group of natural gas and biofuels. According to claim 11,
wherein the first compression turbine is a low pressure turbine and the second compression turbine is a high pressure turbine. According to claim 9,
wherein the first compressor is a low pressure compressor and the second compressor is a high pressure compressor.
delete delete delete delete