Gas turbine engine running on lean fuel mix

FIELD: engines and pumps.

SUBSTANCE: proposed engine comprises compressor, catalytic combustion chamber, turbine, regenerative heat exchanger, burner and valve. Compressor serves to compress working gas, said gas being of combustible component concentration smaller than that of its inflammability. Catalytic combustion chamber is designed to combust compressed air by catalytic reaction with the help of catalyst arranged therein to produce gaseous combustion products. Said products fed from catalytic combustion chamber drive the turbine. Regenerative heat exchanger serves to heat compressed air fed from compressor into said combustion chamber via used gas fed into turbine via used gas channel into regenerative heat exchanger. Burned serves to combust the gas forced from compressor along with fuel for forming the heating gas and feeding heating gas into used gas channel. Valve is designed to control the amount of gas to be fed to the burner.

EFFECT: ruled out loss of power output or discharge system pressure loss, compact design.

5 cl, 3 dwg

 

The technical FIELD TO WHICH the INVENTION RELATES.

The present invention relates to gas turbine engine operating on a lean fuel mixture, which uses low-calorie gas fuel, such as coal mine methane (CMM)that is extracted from coal mines or gas from organic waste in landfills.

BACKGROUND of INVENTION

Has traditionally been known gas turbine engine operating on a lean fuel mixture, which receives the low-calorie gas with a methane concentration of less than limit of its Flammability, burning methane component. In accordance with the design of gas turbine engine working gas with a low concentration of methane is compressed by the compressor for the education of compressed gas. Compressed gas is combusted in the catalytic combustor through a catalytic reaction for the formation of gaseous products of combustion. Then the gaseous products of combustion are used to drive a turbine. While the compressed gas discharged from the turbine is moved in a regenerative heat exchanger or a heat exchanger in which it is used to preheat the compressed gas displaced from the compressor in the catalytic combustor. In the channel for upcoming gas between the output channel of the turbine and BX is dnim channel generator is provided by a tubular burner, into which fuel such as natural gas, and then burned at the start or at low load, in which exhaust gas has a low temperature. This leads to an increase in the temperature of the exhaust gas to ensure sufficient heating of the compressed gas to be supplied from the compressor in a regenerative heat exchanger, and to activate the catalytic combustion chamber and thereby actuate the motor in an efficient manner. Cm. JP 2010-19247 (A).

Gas turbine engine made use of ventilation air with low concentrations of methane (WNCM), representing the low-calorie gas with a low concentration of methane coming out of the coal mines. Ventilation air with low concentrations of methane (WNCM) has a concentration of methane, which is only 1% or less. Therefore, usually the ventilation air with low concentrations of methane (WNCM) is released into the air without burning. However, the use of ventilation air with low concentrations of methane (WNCM) as fuel for the generation of electric energy through the gas turbine will require a certain amount of rights to carbon dioxide emissions.

Since the tubular burner is installed in the discharge channel at the outlet of the turbine, the above gazoturbinnyie causes pressure loss and reducing the power output of the engine due to the fact, that exhaust gas passes through the channel of the turbine, even at rated operating conditions under which the tubular burner off. Additionally, there is no possibility of regulating the flow rate of combustion air entering the tubular burner, which makes re-ignition of the tubular burner in conditions in which there is a poisoning of the catalyst in the catalytic combustion chamber. In addition, since the tubular burner is installed in the channel for the exhaust gas channel and the resulting gas turbine must have a large size.

The present invention is to develop a gas turbine engine operating on a lean fuel mixture without any reduction in the output power of the engine or any loss of pressure in the exhaust system, which ensures the production of gas turbines small size.

SUMMARY of the INVENTION

For this gas turbine engine operating on a lean fuel contains a compressor designed to compress the working gas to create a compressed gas, the working gas has a concentration of the combustible component which is less than its Flammability limit; catalytic combustion chamber, designed for the combustion of compressed gas by a catalytic reaction using rolled atora, posted by in it, for the formation of gaseous products of combustion; a turbine made with the possibility of bringing it into effect by combustion gases supplied from the catalytic combustor; a regenerative heat exchanger that is designed to heat the compressed gas fed from the compressor in the catalytic combustion chamber through the exhaust gas fed from the turbine channel for the exhaust gas in the regenerative heat exchanger, the burner is designed for burning gas taken from the compressor, together with the fuel for the formation of the heating gas and the supply of the heating gas in the channel for the exhaust gas; and a valve for controlling the amount of selected gas to be fed through the burner.

In accordance with the design of gas turbine engine working gas concentration of the combustible component which is less than the limit of its Flammability, is compressed by the compressor for the education of compressed gas. The compressed gas is burned by a catalytic reaction in the catalytic combustion chamber for the formation of high temperature gaseous products of combustion, which are used to drive a turbine. In the case when the temperature at the inlet to the catalytic combustion chamber is less than the temperature, clean the Dima to initiate a catalytic reaction, for example, during startup or operation at low load, the heating burner provides education heating gas by burning a mixture of fuel and gas taken from the compressor, while the heating gas is fed into the channel for the exhaust gas to heat the exhaust gas. Heated exhaust gas then undergoes heat exchange with the compressed gas from the compressor in the regenerative heat exchanger. The heated compressed gas increases the temperature at the inlet of the catalytic combustion chamber to initiate catalytic combustion that provides a stable supply of high temperature gaseous products of combustion in the turbine. In addition, the heating burner is provided outside of the channel for the exhaust gas, resulting in low pressure drop in the exhaust system or to the absence of deterioration of the engine. In addition, the use of the poor of gas, such as coal mine methane (CMM), ventilation air with low concentrations of methane (WNCM) or gas from organic waste, with a lower concentration of fuel or methane concentration to actuate the gas turbine engine or the use of catalytic reaction does not cause the formation of oxides of nitrogen (NOx) at a nominal mode of operation in which gorakana is actuated, reduces emissions of gaseous methane, which contributes to the prevention of global warming.

In addition, the heating burner is not provided in the channel for the exhaust gas, while the placement of the burner does not cause any pressure loss in the exhaust system or deterioration of performance characteristics of the engine and, therefore, ensures efficient operation of the engine. In addition, due to the fact that the channel for the exhaust gas no heat gun, do not require any increase in channel or dimensions of the gas turbine engine. In addition, the control valve selection regulates the amount of selected gas fed into the heating burner that ensures the proper regulation of the amount of selected gas when re-ignition burners for education of a certain number of heating gas required from the burner. This facilitates the ignition of the burner.

In a preferred embodiment, the control valve selection is made with the possibility of continuous increase or decrease the number of selected gas to be fed into the heating burner. In accordance with this embodiment provides a continuous regulation of the amount of selected gas to be fed into the heating is on the burner, through control valve selection. This ensures that there would be a reliable regulation of the quantities of the selected gas and the fuel to be fed into the heating cylinder, and, as a consequence, reliable temperature control of the heating gas emerging from the burner. This ensures stable temperature control at the inlet of the catalytic combustor.

In another preferred embodiment, the heating burner is actuated when the operation start gas turbine engine. In accordance with this embodiment of the heating burner is driven at the operation starting the engine for the revitalization of the catalytic combustion chamber and subsequent smooth casting engine in action, despite the fact that in normal operation start temperature of exhaust gas leaving the turbine, is still low and, therefore, the catalytic combustor will not be activated to the extent necessary to supply high pressure and high temperature compressed gas to the turbine and increasing thereby the number of revolutions of the engine.

In another preferred embodiment, the heating burner operates in a state where the gas turbine engine operates in non-work mode is s, when the number of revolutions is less than the number of revolutions at rated operation of the gas turbine engine. In accordance with this embodiment, the total quantity of the working gas passing through the gas turbine engine during non-operation mode, less than the total amount of the working gas passing through the gas turbine engine at the rated operation mode. This means that the heating burner requires less fuel, allowing use for engine heating burner with a smaller size.

In another preferred embodiment, gas turbine engine is made such that the heating burner is triggered when there is a disruption of the normal process of catalytic combustion in the combustion chamber. In accordance with this embodiment, even when there is any violation of the normal combustion process due to poisoning of the catalyst, heating the burner can be re-lit for the activation of the catalytic combustion chamber and thereby prevent deterioration of the operating characteristics of the engine.

In conclusion, it should be noted that the gas turbine engine can be powered by the poor gas having a lower concentration of t is Pliva, for example, the concentration of methane. In addition, the catalytic reaction does not cause the formation of oxides of nitrogen (NOx) at the rated operation mode, and also allows to reduce the emission of gaseous methane. In addition, since the heating burner is not provided in the channel for the exhaust gas, can be used channelfor the exhaust gas having smaller dimensions, which allows to reduce the dimensions of the gas turbine engine. In addition, this design eliminates pressure loss in the channel for the exhaust gas or to prevent deterioration of the operating characteristics of the engine.

BRIEF DESCRIPTION of DRAWINGS

Figure 1 is a schematic diagram showing the construction of a gas turbine engine running on poor gas, in accordance with one embodiment of the invention;

figure 2 is a schematic showing of the required design elements of gas turbine engine in accordance with the embodiment of the invention; and

figure 3 represents a timing diagram showing the operation when the start/stop of a gas turbine engine in accordance with the embodiment of the invention.

The PREFERRED embodiment of the INVENTION

The preferred embodiment of the invention will be about the Isan below with reference to the accompanying drawings. Figure 1 is a schematic diagram showing the construction of gas turbine engine operating on a lean fuel mixture, in accordance with one embodiment of the invention, in which the gas turbine, indicated generally by the reference position GT has a compressor 1, a catalytic combustion chamber 2 containing a catalyst, such as platinum or palladium, and a rotary machine 4, which uses the power of the gas turbine (GT) to operate as an electric generator or starter.

In a gas turbine uses a working gas G1, which is a mixture of air and fuel. The working gas may be a low-calorie gas, such as ventilation air with low concentrations of methane (WNCM), formed in coal mines or coal mine methane (CMM), in which the concentration of the combustible component (methane) is greater than the concentration of the combustible component in the ventilation air with low concentrations of methane (WNCM), extracted from coal mines or gas from organic waste in a landfill. Working gas G1 is compressed by the compressor 1 to the education of compressed gas G2 having a high pressure, which moves in the catalytic combustion chamber 2, in which it is burnt by a catalytic reaction using a catalyst, is such as platinum or palladium, for the formation of high temperature and high pressure gaseous products G3 combustion. Gaseous products G3 combustion served in the turbine 3 to drive a turbine. The turbine 3 is connected to the compressor 1 through the rotating shaft 5, so that the compressor 1 receives energy from the turbine 3. As described above, the gas turbine GT and rotary machine 4 form an electrical generator 50.

Since the concentration of fuel or fuel component in the working gas G1 is less than its limit of ignition and the fuel temperature is less than the minimum temperature required for combustion ignition, the working gas does not ignite when the temperature increases when it is compressed in the compressor 1. In the working gas G1 can be added to the combustible gas with high concentration to increase the concentration of fuel.

The gas turbine GT further comprises a regenerative heat exchanger or the heat exchanger 6, is designed to heat the compressed gas G2 supplied from the compressor 1 in the catalytic combustion chamber 2, through the use of gas G4, leaving the turbine 3, and the burner 7, for the formation of gas G5, to be used for heating gas G2. In particular, the burner 7 is adding fuel to the gas G20 taken from the compressor 1, and the combustion mixture for the formation of the heating gas G5, the cat is who mixed with the exhaust gas G4, supplied from the turbine 3 in the regenerative heat exchanger 6. The burner 7 is connected to the valve 8 of the regulation selection intended for throttling selected gas G20 to be feed to the burner 7. Gas G4 of the regenerative heat exchanger is served in the muffler not shown, which provides the reduction of noise, and then is released into the atmosphere.

Regulation of the flow rate of gas G20 supplied to the burner 7, through valve 8 control selection in response to the output signal from block 21 run control in the control unit 20 that controls the entire operation of the system which will be described below.

Regulation of the flow rate of coal mine methane coming from the source 13 of CMM, such as coal mines, and passing to the burner 7, through the first valve 9 speed control of the fuel pump, which is driven in response to the control signal from block 21 run control provided in the control unit 20. Working gas G1 is prepared by mixing ventilation air with low concentrations of methane (WNCM) from such a source 12 of ventilation air with low concentrations of methane (WNCM), as the ventilation of coal mines, coal mine methane (CMM) from the source 13 of coal mine methane as not bhodemon, while the number of coal mine methane (CMM) is controlled through the second valve 10 speed control fuel supply. Coal mine methane (CMM) contains approximately 10-30% methane and ventilation air with low concentrations of methane (WNCM) contains less than 1% methane. Regulation of the flow rate of coal mine methane (CMM) through a second valve 10 controlling the speed of feed of the fuel is performed in response to a signal from block 22 regulation load/stopping control of the control device 20. Source 19 purge air is connected to the channel extends from the source 12 ventilation air with low concentrations of methane (WNCM) to the compressor 1, to perform the purge operation performed during startup.

The first sensor 31 temperature is provided near the entrance of the catalytic chamber 2 combustion to determine the temperature of the gas flowing into the catalytic combustion chamber 2, and the second sensor 32, the temperature is provided near the catalytic combustion chamber 2 to determine the temperature of gas leaving the catalytic chamber 2 chamber. The temperature on the input received by the first sensor 31 temperature, is transmitted in the form of a signal characterizing the first measured temperature, in block 21 of the control run, and the temperature at the outlet, received by the second sensor 32 so is the temperature, is transmitted in the form of a signal characterizing the second measured temperature, in block 21 of the control run and in block 22 of the load control/stopping control.

In addition, the third sensor 33, the temperature is provided near the outlet of the turbine 3 to determine the temperature of the gas leaving the turbine 3. Outlet temperature, "received" by the third sensor 33 temperature is passed as the third measured temperature in block 22 of the load control/stopping control of the control device 20. The fourth sensor 34 temperature is provided near the inlet of the regenerative heat exchanger 6 for determining the temperature of the gas coming into the regenerative heat exchanger 6. The temperature at the inlet, received the fourth temperature sensor is passed as the fourth measured temperature in block 21 of the run control in the control unit 20.

The rotating shaft 5 connecting the compressor 1 and the turbine 3 and formed from a single element, a represents a shaft, is connected via a gearbox 17 rotary machine 4. The rotating shaft 5 serves as a support for the sensor 36 rotation, intended to determine the number of revolutions of the rotating shaft 5, which is then passed to the block 22 regulation load/stopping control of the control device 20.

The signal characterizing the electric the energy/power, created rotary machine 4, is passed to block 22 of the load control/stopping control of the control device 20. System 11 energy conversion is made such that the block 22 regulation load/stopping control leads rotary machine 4 in action as a starter in the startup operation.

As shown in figure 2, a turbine 3 and a regenerative heat exchanger 6 are connected to each other through a pipe or channel 25 to the exhaust gas. The channel 25 to the exhaust gas has a cylindrical part 25A near the turbine and the expanding portion 25b located next to the regenerative heat exchanger 6 and extending in the direction of the regenerative heat exchanger 6, and the burner 7 is connected with the expanding part 25b for the supply of heating gas G5 in the inner space of the channel 25 to the exhaust gas. Expanding the design of the expanding portion 25b provides a uniform supply of the heating gas G5 in the inner space of the regenerative heat exchanger 6 is large in size, so that the heat exchange between the gases G2 and G5 is carried out using only the internal space of the regenerative heat exchanger 6.

As described above, coal mine methane (CMM) from a source of coal mine methane (CMM) (figure 1) is supplied to the burner 7. In addition, the channel 27 to select what about the gas branched from the channel 24, designed for compressed gas G2 from the compressor 1 in a regenerative heat exchanger 6 on which are mounted the burner 7 and the valve 8.

Basic operation of the gas turbine GT, including operations management, start-up, load control and stopping control will be described with reference to figure 3, showing the operation of the gas turbine when the start/stop depending on time. On this drawing the characteristic curves a-E show, respectively, the number of revolutions of the rotating shaft of the gas turbine (GT)produced electrical energy/power, the degree of opening of the first valve 9 speed control of fuel supply, the degree of opening of the second valve 10 speed control fuel supply and the degree of opening of the valve 8 of the regulation of the selection.

First will be considered the operation of the control run. In this operation, when receiving the start command block 21 run control provides actuation system 11 energy conversion of figure 1 to supply power to the rotary machine 4. In addition, the valve 18 takes the open position. This leads to the fact that gas turbine engine (GT) will suck the air for operation at a lower speed, for example, constitutes 20-30% of the nominal speed (blowing). After that, the valve 18 takes the open position the tion, which causes the absorption of ventilation air with low concentrations of methane (WNCM) from source 2 ventilation air with low concentrations of methane (WNCM) in the gas turbine (GT) to increase the number of revolutions, for example, up to 60% of rated speed for ignition of the burner 7 of figure 1 for heating a heat exchanger 6, and also for heating the inner space of the catalytic chamber 2 combustion to a temperature necessary for the catalytic reaction. As shown in figure 3, the valve 8 of the regulation selection is gradually opened after completion of the purge operation. The degree of opening of the valve 8 is maintained constant after ignition of the burner 7. After that, the second valve 10 speed control fuel supply is opened by the control signal from block 22 regulation load/stopping control during catalytic combustion in the catalytic combustion chamber 2 of figure 1 for initiating the supply of coal mine methane (CMM) from the source 13 coal mine methane (CMM) in the compressor 1 (supply of coal mine methane). After that regulate combustion in the burner 7 to prevent excessive temperature increase at the inlet of the catalytic chamber 2 combustion, which otherwise would be caused by the supply of coal mine methane (CMM).

For example, as shown in figure 3, this maintains the air of combustion is carried out through the gradual reduction of degrees E and the valve opening 8 of the regulation and selection of the first valve 9 speed control of fuel supply and the resulting quantities gas G20 and coal mine methane (CMM), supplied to the burner 7. The temperature at the inlet of the catalytic chamber 2 of the combustion is determined by the sensor 31, the temperature, and the signal characterizing the measured temperature, is passed to block 21 run control in the control unit 20. During signal reception unit 21 of the control run transmits control signals to the valve 8 of the regulation of the selection and the first valve 9 speed control of fuel supply to regulate according to their degrees F and With the opening. As shown in figure 3, when the generated electric energy/power will be greater than zero kW, that is initiated by the generation of electric energy, the degree of F and the valve opening 8 of the regulation selection and valve 9 speed control of the fuel supply is reduced to zero to stop the flow of sampled gas G20 and coal mine methane (CMM) in the burner 7 and thereby eliminate the flame.

Next will be considered the load regulation. As shown in figure 3, will be started as soon as electric energy, the degree D of the opening of the second valve 10 speed control fuel supply increases in response to the control signal from block 22 regulation load/stopping control, which ensures an increase in the number of coal mine methane (CMM)to be supplied from source 13 coal mine methane (CMM) is the compressor 1. In addition, after complete shutdown of the burner 7 continues catalytic catalytic combustion in the combustion chamber 2. In addition, as shown in figure 3, the degree D of the opening of the second valve 10 speed control fuel supply is gradually increased to increase the number of coal mine methane (CMM)to be fed into the compressor 1, as long as the number And speed of the engine will not reach rated number (100%) to produce a nominal electric capacity (rated load). When the load reaches the rated load, the concentration of coal mine methane (CMM) in the working gas G1 is regulated by regulating the number of coal mine methane (CMM)to be fed into the compressor 1 through the second valve 10 of figure 1, designed for speed control of fuel supply.

When the stop control when receiving the stop signal, as shown in figure 3, the block 21 run control functions for the gradual reduction of electric power In the subject development, as well as a gradual decrease in the degree D of the opening of the second valve 10 speed control fuel supply to reduce the number of coal mine methane (CMM)to be fed into the catalytic combustion chamber 2, which reduces the number of revolutions of the engine and the generated electric mo the values to zero (no load). This condition is maintained for a certain period of time, during which the entire engine is cooled (and subsequent cooling). The engine has cooled down sufficiently, the second valve 10 speed control fuel supply is completely closed to stop the flow in the gas turbine (GT), which, in turn, provides the translation of a gas turbine (GT) in the state of free rotation of idling.

The burner 7 is driven not only when the engine is running, but also if you have any problems with catalytic combustion in the combustion chamber 2. For example, when the outlet temperature of the catalytic combustion chamber defined by the second sensor 32, the temperature is reduced to values less than the set temperature, it is determined that took place some violation of the normal combustion process, for example, due to catalyst poisoning, and as a result, the controller 20 opens the valve 8 of the regulation and selection of the first valve 9 speed control of fuel and ignition of the burner 7. This ensures that the temperature rise of the exhaust gas G4 entering the regenerative heat exchanger 6, and the compressed gas G2 to be fed into the catalytic combustion chamber 2, resulting in kataliticheskaya 2 combustion will be supplied with energy sufficient to prevent any decrease in the output power of the engine.

In accordance with the variants of the implementation of the gas turbine can be actuated smoothly. In particular, the temperature of the exhaust gas G4, leaving the turbine 3 operation starting the engine is low, and therefore, is unlikely to be satisfactory activation of the catalytic work of the camera 2 combustion, which makes it difficult to supply with high pressure and high temperature compressed gas to the turbine and a smooth increase of the rotation frequency. However, in accordance with the embodiment of the burner 7 is driven in the operation of starting the engine to raise the temperature of the exhaust gas G4 entering the regenerative heat exchanger 6. This ensures that by means of regenerative heat exchange in the heat exchanger 6, the temperature of the compressed gas G2 to be fed into the catalytic combustion chamber 2, will increase, providing a more effective activation of the work of the catalytic combustion chamber to ensure a smooth running engine.

In addition, since the heating burner 7 is provided outside the channel 25 to the exhaust gas, and not within the channel 25, there is no pressure loss or the output energy in the channel for the exhaust gas and there is no reduction in power output, which ensures efficient operation of the gas turbine (GT. In addition, since the heating burner is not provided in the channel 25 to the exhaust gas channel can be made with smaller dimensions, the result can be obtained a compact gas turbine (GT).

In addition, the valve 8 of the regulation of the selection is provided to the input side of the heating burner 7 to ensure a continuous increase or decrease the number of selected gas G20 to be feed to the burner 7. This ensures that adequate regulation of quantities of selected gas G20 and fuel to be fed through the burner 7, depending on the number of revolutions of the engine, which, in turn, guarantees the regulation of the flow rate and temperature of the heating gas G5 coming out of the burner 7, and thereby regulating the temperature at the inlet of the catalytic chamber 2 chamber.

When the engine is running in non-operation mode, the quantity of the working gas passing through the gas turbine will be less than the quantity of the working gas passing through the gas turbine at the rated operation mode. This leads to the fact that the heating of the burner 7 will require less fuel, which, in turn, means that the burner 7 can be smaller in size.

Despite the fact that coal mine methane and ventilation air with low concentrations of methane (WNC is used as working gas in the above embodiments, implementation, instead, they can be used in other gas in which the concentration of the combustible component is less than its Flammability limit.

Although preferred embodiments of the invention have been described with reference to the accompanying drawings, various modifications may be made without departing from the invention, and are within the scope of the invention.

The REFERENCE LIST of ITEMS

1: compressor

2: catalytic combustor

3: turbine

4: generator

6: regenerative heat exchanger

7: heating burner

8. control valve selection

25: the channel for the exhaust gas

G1: working gas

G2: compressed gas

G3: gaseous combustion products

G4: exhaust gas

G5: heating gas

G20: selected gas

1. Gas turbine engine operating on a lean fuel mixture, containing:
the compressor is designed to compress the working gas to create a compressed gas, the working gas has a concentration of the combustible component which is less than its Flammability limit;
the catalytic combustion chamber is designed for the combustion of compressed gas by a catalytic reaction using a catalyst, placed in it, for the formation of gaseous products of combustion;
turbine made with the possibility of a CR is doing it through the gaseous products of combustion, supplied from the catalytic combustor;
the regenerative heat exchanger used to heat the compressed gas fed from the compressor in the catalytic combustion chamber through the exhaust gas fed from the turbine channel for the exhaust gas in the regenerative heat exchanger;
the burner is designed for burning gas taken from the compressor, together with the fuel for the formation of the heating gas and the supply of the heating gas in the channel for the exhaust gas; and
valve for regulating the amount of selected gas to be fed into the burner.

2. Gas turbine engine according to claim 1, in which the valve is made with the possibility of continuous increase or decrease the number of selected gas to be fed into the heating burner.

3. Gas turbine engine according to claim 1 or 2, in which the heating burner is actuated when the operation start gas turbine engine.

4. Gas turbine engine according to claim 3, in which the heating burner operates in a state where the gas turbine engine operates in a non-operation mode in which the number of revolutions is less than the number of revolutions at rated operation of the gas turbine engine.

5. Gas turbine engine according to claim 1 or 2, in which the heating burner works when imee is a violation of the normal combustion process in a catalytic combustor.



 

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1 dwg

FIELD: power industry.

SUBSTANCE: burner (4) for gas burner includes: swirler (21), plate (58), the first channel (18) via which fuel gas with low calorific value is supplied, and second channel (17) via which combustion air is supplied. The first and the second channels (17, 18) are located concentrically relative to longitudinal axis (2). Output of the first channel (18) is formed with convergent nozzle (50). Swirler (21) is installed at the outlet of the second channel (17). Plate (58) is tightly installed in the first channel (18) upstream nozzle (50) and has many holes (56) with calibrated section of the passage. Holes (56) are inclined in tangential direction relative to longitudinal axis (2) at the specified angle. For fuel gases having flame propagation speed of less than 300 mm/s, plate (58) has 36 to 38 holes (56) the diameter of which is 11.5 to 12.0 mm, and inclination angle of holes (56) is approximately 22. For fuel gases having flame propagation speed of 300 mm/s to 400 mm/s, plate (58) has 80 holes (56) the diameter of which is 8.5 mm to 9.0 mm, and inclination angle of holes (56) is 17 to 22. If calorific value of gas with low calorific value from the first channel (18) is less than 4.0 MJ/kg, then natural gas consumption is assumed from pilot line (46). Burner (5) is used only when gases with low calorific value are not available.

EFFECT: high burner flexibility; operation is possible at the gas used with low calorific value and of any type within the whole working range of gas turbine.

12 cl, 3 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed gas turbine comprises compressor linked up with the drive. In its turn, compressor drive comprises 1st and 2nd stages, inner and outer shafts with blower fitted on inner shaft and compressor fitted on outer shaft. It includes also HP and LP turbines with cooling system, primary combustion chamber arranged between compressor and HP turbine. Gas turbine comprises also outer combustion chamber and heat exchanger-heater arranged behind HP turbine and communicated, via heat carrier circulation lines, with heat exchanger arranged behind outer combustion chamber.

EFFECT: higher efficiency and reliability.

3 cl, 4 dwg

Power supply system // 2307946

FIELD: power engineering.

SUBSTANCE: proposed power supply system generating electric power using self-forming gas contains gas motor, gas turbine, gas collector for self-forming gas, device to separate gas and device to control calorific value for selective mixing of gases differing in content of fuel component. Gas separating device continuously separates gas delivering from gas collector whose fuel component content changes in time according to content of fuel component of gas. Calorific value control device for selective mixing of gases differing in content of fuel component which are separated by gas separating device, controls content of fuel component of gas which is to be supplied to gas motor and gas turbine. System control device is provided to control operation of gas motor, gas turbine and calorific value control device.

EFFECT: provision of power supply system maintaining stable generation of power, irrespective of changes of amount of self-forming gas and its calorific value.

13 cl, 8 dwg

The invention relates to a method and evaporator deeply refrigerated liquid working medium

Power supply system // 2307946

FIELD: power engineering.

SUBSTANCE: proposed power supply system generating electric power using self-forming gas contains gas motor, gas turbine, gas collector for self-forming gas, device to separate gas and device to control calorific value for selective mixing of gases differing in content of fuel component. Gas separating device continuously separates gas delivering from gas collector whose fuel component content changes in time according to content of fuel component of gas. Calorific value control device for selective mixing of gases differing in content of fuel component which are separated by gas separating device, controls content of fuel component of gas which is to be supplied to gas motor and gas turbine. System control device is provided to control operation of gas motor, gas turbine and calorific value control device.

EFFECT: provision of power supply system maintaining stable generation of power, irrespective of changes of amount of self-forming gas and its calorific value.

13 cl, 8 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed gas turbine comprises compressor linked up with the drive. In its turn, compressor drive comprises 1st and 2nd stages, inner and outer shafts with blower fitted on inner shaft and compressor fitted on outer shaft. It includes also HP and LP turbines with cooling system, primary combustion chamber arranged between compressor and HP turbine. Gas turbine comprises also outer combustion chamber and heat exchanger-heater arranged behind HP turbine and communicated, via heat carrier circulation lines, with heat exchanger arranged behind outer combustion chamber.

EFFECT: higher efficiency and reliability.

3 cl, 4 dwg

FIELD: power industry.

SUBSTANCE: burner (4) for gas burner includes: swirler (21), plate (58), the first channel (18) via which fuel gas with low calorific value is supplied, and second channel (17) via which combustion air is supplied. The first and the second channels (17, 18) are located concentrically relative to longitudinal axis (2). Output of the first channel (18) is formed with convergent nozzle (50). Swirler (21) is installed at the outlet of the second channel (17). Plate (58) is tightly installed in the first channel (18) upstream nozzle (50) and has many holes (56) with calibrated section of the passage. Holes (56) are inclined in tangential direction relative to longitudinal axis (2) at the specified angle. For fuel gases having flame propagation speed of less than 300 mm/s, plate (58) has 36 to 38 holes (56) the diameter of which is 11.5 to 12.0 mm, and inclination angle of holes (56) is approximately 22. For fuel gases having flame propagation speed of 300 mm/s to 400 mm/s, plate (58) has 80 holes (56) the diameter of which is 8.5 mm to 9.0 mm, and inclination angle of holes (56) is 17 to 22. If calorific value of gas with low calorific value from the first channel (18) is less than 4.0 MJ/kg, then natural gas consumption is assumed from pilot line (46). Burner (5) is used only when gases with low calorific value are not available.

EFFECT: high burner flexibility; operation is possible at the gas used with low calorific value and of any type within the whole working range of gas turbine.

12 cl, 3 dwg

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