WO2014141483A1

WO2014141483A1 - Gas turbine equipment

Info

Publication number: WO2014141483A1
Application number: PCT/JP2013/057553
Authority: WO
Inventors: 高橋　一雄; 尚弘楠見; 日野　徳昭; 智道伊藤; 哲郎森崎; コーテットアウン
Original assignee: 株式会社日立製作所
Priority date: 2013-03-15
Filing date: 2013-03-15
Publication date: 2014-09-18
Also published as: JP5951885B2; JPWO2014141483A1

Abstract

The present invention is equipped with: a compressor (103) that draws in and compresses air; a combustor (105) that burns compressed air (104) from the compressor (103) together with a fuel (107); a turbine (109) driven by combustion gas (112) from the combustor (105); an electric motor (114) that applies torque to the turbine shaft (110); a fluid connector (116) linking the turbine shaft (110) and the electric motor (114); and an electric motor control device (203f) that controls the electric motor (114) to apply torque to the turbine shaft (110) when a limit value for the rate of change according to control of the fuel flow rate is exceeded, thereby changing the turbine output. Thus, the responsiveness to a turbine output command can be improved.

Description

Gas turbine equipment

The present invention relates to gas turbine equipment.

A gas turbine facility is known in which the power generation output is controlled to be constant based on the fuel flow rate to the combustor and the intake air flow rate of the compressor (see Patent Document 1).

JP 2001-123852 A

Renewable energy such as wind power generation and solar power generation greatly fluctuates the power generation output due to the weather, etc., and there is a concern that the system frequency of the power system will become unstable with the introduction of a large amount of renewable energy. In order to stabilize the grid frequency, it is necessary to supply power to the power system by generating power according to the power demand while absorbing fluctuations in renewable energy. Therefore, there is an urgent need to improve the response to the turbine output command.

However, since the turbine output is generally controlled by the fuel flow rate, there is a response delay with respect to the control of the fuel flow rate. In addition, for example, if the fuel flow rate changes during turbine output control, the combustion gas temperature also changes, but if the combustion gas temperature changes suddenly, the temperature distribution of the high-temperature parts exposed to the combustion gas becomes uneven and thermal stress Will increase. Excessive thermal stress can lead to thermal fatigue and thus failure of high temperature parts. Including this example, there are some restrictions on the control of the turbine output by the fuel flow rate or the like from the viewpoint of reliability. For this reason, gas turbine equipment may not be able to cope with sudden changes in turbine output commands due to limitations on fuel flow rate and response delays.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a gas turbine facility capable of improving the response to a turbine output command.

In order to achieve the above object, according to the present invention, an electric motor is connected to a turbine shaft of a gas turbine facility via a fluid coupling.

According to the present invention, the responsiveness to the turbine output command can be improved.

1 is a schematic view of a gas turbine facility according to a first embodiment of the present invention. It is the schematic of the gas turbine installation which concerns on the 2nd Embodiment of this invention. It is a functional block diagram of the gas turbine control apparatus with which the gas turbine equipment which concerns on the 2nd Embodiment of this invention was equipped. It is a flowchart showing the control procedure of the electric motor by the gas turbine control apparatus with which the gas turbine equipment which concerns on the 2nd Embodiment of this invention was equipped. It is a figure showing the behavior of the power generation output by the torque application of an electric motor, etc. It is the schematic of the gas turbine equipment which concerns on the 3rd Embodiment of this invention. It is a functional block diagram of the gas turbine control apparatus with which the gas turbine equipment which concerns on the 3rd Embodiment of this invention was equipped. It is a flowchart showing the control procedure of the oil quantity adjustment valve by the gas turbine control apparatus with which the gas turbine equipment which concerns on the 3rd Embodiment of this invention was equipped. It is the schematic of the gas turbine equipment which concerns on the 4th Embodiment of this invention. It is the schematic of the gas turbine equipment which concerns on the 5th Embodiment of this invention. It is the schematic of the gas turbine equipment which concerns on the 6th Embodiment of this invention. It is a functional block diagram of the gas turbine control apparatus with which the gas turbine equipment which concerns on the 6th Embodiment of this invention was equipped. It is a flowchart showing the control procedure of the oil quantity adjustment valve by the gas turbine control apparatus with which the gas turbine equipment which concerns on the 6th Embodiment of this invention was equipped.

Embodiments of the present invention will be described below with reference to the drawings.

(First embodiment)
1-1. Gas Turbine Equipment FIG. 1 is a schematic view of gas turbine equipment according to the first embodiment of the present invention.

The gas turbine equipment shown in FIG. 1 includes a gas turbine 100, a generator 111, and an electric motor 114. The gas turbine 100 includes a compressor 103, a combustor 105, and a turbine 109. As the gas turbine 100, a uniaxial gas turbine is illustrated, but a biaxial gas turbine may be used.

The compressor 103 sucks and compresses air to generate compressed air 104, and supplies the generated compressed air 104 to the combustor 105. An IGV (InletInGuide Vane: inlet guide vane) 102 is provided at the air intake port of the compressor 103. The IGV 102 changes the amount of air flowing into the compressor 103 by rotating a plurality of vanes (not shown) to change the opening area of the air intake port of the compressor 103.

The combustor 105 burns the compressed air 104 from the compressor 103 together with the fuel 107 to generate combustion gas 108. The flow rate of the fuel 107 combusted by the combustion gas 108 is adjusted by a fuel adjustment valve 106 provided in the fuel pipe.

The turbine 109 is driven by the combustion gas 108 from the combustor 105 (to obtain the rotational power of the turbine shaft 110). Rotational power obtained by the turbine 109 is transmitted to the compressor 103 and the generator 111 via the turbine shaft 110. The combustion gas 108 whose energy has been recovered by the turbine 109 is discharged as exhaust 112.

The generator 111 is connected to the turbine shaft 110 of the gas turbine 100 and is driven by the rotational power obtained by the turbine 109 to generate AC power. In order to suppress fluctuations in the output frequency of the generator 111, the single-shaft gas turbine 100 rotates with a target rotation speed corresponding to the system frequency of the power system 113 as a target, and increases the fuel flow rate when increasing the power generation output. Thus, the turbine output (torque) is increased, and the load of the generator 111 (current flowing through the stator, etc.) is increased accordingly. When the power generation output is lowered, the fuel flow rate is reduced to reduce the turbine output, and the load on the generator 111 is reduced accordingly. The power generation output of the generator 111 is sent to the power system 113 via a power cable.

The electric motor 114 is provided as an assist motor that changes the turbine output by applying rotational power to the turbine shaft 110 during turbine load operation. The electric motor 114 may be a relatively small one having a smaller capacity than the generator 111. The power source of the electric motor 114 may be electric power from the electric power system 113, a part of the power generation output by the generator 111, or electric power supplied from other power supply equipment in the plant. Further, a motor generator that is also driven as a generator can be used for the motor 114. The power generation output of the motor 114 in this case may be supplied to the power system 113 after controlling the frequency as necessary, or may be used as a power source for various facilities in the plant. The operation of the electric motor 114 may be automatic operation by a control device as in the following embodiment, but may be manual operation by an operator in the case of this embodiment.

Further, the rotating shaft (motor shaft) 115 of the electric motor 114 is connected to the turbine shaft 110 via a fluid coupling 116. The motor shaft 115 is mechanically separated from the turbine shaft 110, and transmits torque to and from the turbine shaft 110 through control oil filled in the fluid coupling 116.

Although FIG. 1 illustrates a configuration in which the generator 111 is connected to the turbine 109 side shaft end of the turbine shaft 110 and the motor 114 is connected to the compressor 103 side shaft end, this arrangement may be reversed. That is, the motor 114 may be connected to the shaft end of the turbine shaft 110 on the turbine 109 side, and the generator 111 may be connected to the shaft end of the compressor 103 side. However, even in this case, the motor shaft 115 is connected to the turbine shaft 110 via the fluid coupling 116.

1-2. Effect (1) Improvement of responsiveness Since the torque of the motor 114 can be controlled by the applied voltage, the responsiveness is better than when the fuel flow and intake flow are controlled to adjust the turbine output. Therefore, according to the present embodiment, for example, a turbine output command (hereinafter referred to as MWD) suddenly rises during turbine load operation, and control of turbine output by fuel flow rate increases demand due to a delay in response or restrictions for machine protection. When the turbine output cannot be caused to follow, the motor output is driven by the motor 114 and torque is applied to the turbine shaft 110 so that the turbine output can follow the sudden increase in MWD. In addition, if a motor generator is used for the motor 114, the MWD is drastically decreased and the turbine output cannot be made to follow the decline in demand due to a delay in response or a limitation for machine protection in the control of the turbine output by the fuel flow rate. By driving the electric motor 114 as a generator to convert a part of the torque of the turbine shaft 110 into electric energy, the turbine output can be caused to follow the sudden decrease in MWD. Therefore, according to the present embodiment, it is possible to improve the response of turbine output to MWD.

If the turbine output can be adjusted by adjusting the turbine output based on the fuel flow rate or the like, the motor 114 does not need to be driven by a motor or generator, and can be driven without load (idling). good. When the motor shaft 115 can be disconnected via the clutch, it may be disconnected from the turbine shaft 110 when not in use. Further, when it is sufficient to improve only the responsiveness to the rapid increase in MWD, the electric motor 114 does not need a generator function.

(2) Ensuring Reliability Here, in the present embodiment, torque is continuously applied externally to the turbine shaft 110 during load operation when the electric motor 114 is driven. Accordingly, torsional stress acts on the turbine shaft 110 that is accelerated or decelerated by the torque applied by the motor shaft 115. In addition, for example, when a renewable energy power generation device is connected via the power system 113, in order to suppress the fluctuation of the frequency of the power system 113, the power generation of the renewable energy power generation apparatus in addition to the fluctuation of the power demand Since it is necessary to adjust the power generation output according to the output fluctuation, the fluctuation of the torque applied by the electric motor 114 to the turbine shaft 110 can be intensified. In particular, when a motor generator is used as the motor 114, the torque applied by the motor 114 to the turbine shaft 110 is reversed in the positive and negative directions. In these cases, pulsation occurs in the torsional stress acting on the turbine shaft 110, and the turbine shaft 110 may be excessively fatigued. Although the strength of the turbine shaft 110 can be improved by changing the material, shape, and the like of the turbine shaft 110, it can lead to an increase in equipment costs. Furthermore, the applied torque of the electric motor 114 is greatly restricted due to the limitation on the strength of the turbine shaft 110, and simply connecting the electric motor shaft 115 to the turbine shaft 110 sufficiently increases the capacity of the electric motor 114 for controlling the turbine output. There is a risk that it cannot be demonstrated.

Considering this point, in the present embodiment, the motor shaft 115 is connected to the turbine shaft 110 through the fluid coupling 116. Inside the fluid coupling 116, the motor shaft 115 and the turbine shaft 110 are separated mechanically, and the torque applied by the motor 114 is converted into the fluid motion of the control oil filled in the fluid coupling 116, and then the turbine. It is transmitted to the shaft 110. Thereby, the torsional stress which acts on the turbine shaft 110 with the fluctuation | variation of the applied torque of the electric motor 114 can be suppressed. Further, the fine pulsation of the torque component acting on the turbine shaft 110 is attenuated. This point also contributes to suppression of torsional stress.

Further, since the electric motor shaft 115 and the turbine shaft 110 are separated inside the fluid coupling 116, a deviation in the rotational speed between the electric motor shaft 115 and the turbine shaft 110 is allowed. As a result, torsional stress can be suppressed even when there is a rotational speed deviation between the motor shaft 115 and the turbine shaft 110.

(3) Efficiency improvement Since a rotational speed deviation between the motor shaft 115 and the turbine shaft 110 is allowed, a highly efficient system can be constructed. For example, when the maximum efficiency rotation speeds of the electric motor 114 and the gas turbine 100 are different, the electric motor 114 and the gas turbine 100 can be operated at different maximum efficiency rotation speeds.

(4) Suppressing the generator capacity Generally, the greater the torque transmitted, the lower the torque transmission efficiency and the more difficult the management of the control oil temperature during operation, and the greater the change in performance due to the temperature of the control oil. It has been known. On the other hand, in the case of the present embodiment, the electric motor 114 has a relatively small capacity, for example, a capacity of about several percent of the generator 111, and a certain effect can be expected. Therefore, transmission between the electric motor shaft 115 and the turbine shaft 110 is possible. Torque can be suppressed, and good torque transmission efficiency can be ensured. If a fluid coupling is used to connect the rotating shaft of the generator 111 to the turbine shaft 110, the torque transmission efficiency is significantly reduced because the transmission torque is significantly larger than that of the present embodiment.

(Second Embodiment)
2-1. Gas Turbine Equipment FIG. 2 is a schematic view of gas turbine equipment according to the second embodiment of the present invention. In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals as those in the previous drawings, and the description thereof is omitted.

This embodiment shows a specific configuration example for automatically operating the electric motor 114. The gas turbine equipment shown in the figure has a configuration in which measuring

instruments

201 and 202 and a gas turbine control device 203 are added to the gas turbine equipment of FIG. The measuring instrument 201 measures the power generation output of the gas turbine facility, and the measuring instrument 202 measures the rotational speed of the turbine shaft 110 and outputs it to the gas turbine control device 203. The gas turbine control device 203 uses, as an input signal, a power generation output command (MWD) 204 from the outside (for example, a higher-level control device) together with the measurement signals of the measuring

instruments

201 and 202, and based on these input signals, the IGV 102 and the fuel adjustment valve 106, the generator 111 and the motor 114 are controlled. Other hardware configurations are the same as those in the first embodiment.

2-2. Control Device FIG. 3 is a functional block diagram of the gas turbine control device 203 of FIG.

As shown in the figure, the gas turbine control device 203 includes an input unit 203a, a storage device 203b, a fuel flow control device 203c, an intake flow control device 203d, a generator control device 203e, an electric motor control device 203f, and an output unit. 203g. The input unit 203a inputs the power generation output measured by the measuring instrument 201, the turbine rotational speed measured by the measuring instrument 202, and the MWD 204 as input signals, and appropriately converts them into digital signals. The storage device 203b includes a plurality of areas for storing input signals input via the input unit 203a, programs and thresholds necessary for various controls, and various calculation values. The fuel flow control device 203c calculates a fuel flow rate corresponding to the MWD 204 and generates an opening degree control signal 205 to the fuel adjustment valve 106. The opening degree control signal 205 is calculated as a value that brings the measured value of the power generation output close to the MWD 204, for example. The intake air flow rate control device 203d generates an opening degree control signal 206 to the IGV 102. The opening degree control signal 206 is calculated as a value that keeps the intake air flow rate of the compressor 103 constant based on, for example, a measured value of the turbine speed. The generator control device 203e generates a load control signal 208 for the generator 111. The load control signal 208 is calculated as a value that brings the turbine rotational speed close to the set rotational speed based on, for example, the measured value of the turbine rotational speed. The motor control device 203f generates a torque control signal 207 to the motor 114 as necessary.

2-3. Control Procedure FIG. 4 is a flowchart showing a control procedure of the electric motor 114 by the gas turbine control device 203. The gas turbine control device 203 repeatedly executes the procedure shown in FIG.

Step S101
When the procedure of FIG. 4 is started, the gas turbine control device 203 first calculates the change rate (time change) of the MWD 204 by differentiation, and determines whether or not the calculated change rate (absolute value) is equal to or greater than the limit value. As this limit value, for example, the maximum change rate of the power generation output that can be followed by the fuel flow rate control (or a value set lower than that with allowance) can be used. If the rate of change of the MWD 204 is below the limit value, the gas turbine control device 203 ends the procedure of FIG. This is because when the power generation output is allowed to follow the MWD 204 by the fuel flow control, the assist by the electric motor 114 is unnecessary. If the rate of change of the MWD 204 is equal to or greater than the limit value, the gas turbine control device 203 moves the procedure to step S102.

Steps S102 and S103
When the change rate of the MWD 204 is equal to or greater than the limit value, the gas turbine control device 203 calculates a torque control signal 207 for the motor 114 by the motor control device 203f (step S102) and outputs the torque control signal 207 to the motor 114 via the output unit 203g. (Step S103). The torque control signal 207 is generated, for example, as a motor drive command value that compensates for the shortage of torque based on the difference between the turbine output change rate according to the MWD 204 and the limit value (turbine output change rate by fuel flow control). Is done. When the motor 114 is a motor generator, it is generated as a generator drive command value that recovers surplus torque as electric energy.

Steps S104 and S105
When the torque control signal 207 is output to the electric motor 114, the gas turbine control device 203 determines whether or not the rate of change of the MWD 204 is below the limit value (step S104). If the change rate of the MWD 204 is still greater than or equal to the limit value, it is necessary to continuously apply torque to the turbine shaft 110 by the electric motor 114, and the gas turbine control device 203 returns the procedure to step S102. If the change rate of the MWD 204 is below the limit value, it is not necessary to apply torque by the electric motor 114, so the gas turbine control device 203 reduces the torque control signal 207 at a predetermined rate by the electric motor control device 203f and releases the torque application. (Step S105), and the procedure of FIG.

2-4. Effect In this embodiment, the same effect as in the first embodiment can be obtained. This point will be described with reference to the drawings.

FIG. 5 is a diagram showing the behavior of the power generation output due to the torque application of the electric motor 114.

Suppose that the MWD 204 shown in the first stage of FIG. The MWD 204 increases at a large change rate at times a and b. Looking at the output of the generator 111 shown in the second stage, when the electric motor 114 is not used, the sudden change of the MWD 204 at times a and b cannot be followed (see the dotted line). On the other hand, as shown in the third stage, the responsiveness of the power generation output is improved by temporarily applying torque to the turbine shaft 110 by the motor 114 at the times a and b, and the power generation output follows the MWD 204 well. (Refer to the second solid line).

However, it has already been described that torsional stress can be generated in the turbine shaft 110 by applying torque by the electric motor 114. In the fourth stage, when torque is applied by the electric motor 114 as in this example, the torsional stress (see the solid line) generated in the turbine shaft 110 connected to the electric motor shaft 115 via the fluid coupling 116, and the electric motor shaft 115 are The simulation results of torsional stress (see dotted lines) that can be generated in the mechanically (rigidly) connected turbine shaft 110 are shown. As can be seen from the simulation results, the torsional stress of the turbine shaft 110 can be suppressed by connecting the motor shaft 115 via the fluid coupling 116 as compared to the case where the motor shaft 115 is mechanically coupled via a normal coupling.

(Third embodiment)
The third embodiment differs from the above-described embodiments in that the torque transmission efficiency between the motor shaft 115 and the turbine shaft 110 is controlled by controlling the amount of oil charged in the fluid coupling 116. is there.

3-1. Gas Turbine Equipment FIG. 6 is a schematic view of gas turbine equipment according to the third embodiment of the present invention. In the present embodiment, the same parts as those in the already described embodiment are denoted by the same reference numerals as those in the previous drawings, and the description thereof is omitted.

The gas turbine equipment shown in the figure includes an oil amount adjustment valve 401. The oil amount adjustment valve 401 is a control valve that adjusts the amount of control oil from a supply source (not shown) that fills the fluid coupling 116. The opening degree of the oil amount adjustment valve 401 is controlled by the gas turbine control device 203A. Other hardware configurations are the same as those of the gas turbine facility (see FIG. 2) according to the second embodiment.

3-2. Control Device FIG. 7 is a functional block diagram of the gas turbine control device 203A. In the present embodiment, the same parts as those in the already described embodiment are denoted by the same reference numerals as those in the previous drawings, and the description thereof is omitted.

The gas turbine control device 203A shown in FIG. 7 includes an oil amount control device 203h. The oil amount control device 203h functions to change the torque transmission efficiency of the fluid coupling 116 by controlling the oil amount adjustment valve 401 in accordance with the deviation between the power generation output measured by the measuring instrument 201 and the MWD 204. The configuration and functions of other functional units of the gas turbine control device 203A are the same as those of the gas turbine control device 203 (see FIG. 3) in the second embodiment.

3-3. Control Procedure FIG. 8 is a flowchart showing a control procedure of the oil amount adjustment valve 401 by the gas turbine control device 203A. The gas turbine control device 203A repeatedly executes the procedure shown in the figure by the oil amount control device 203h during the turbine load operation.

Step S201
When the procedure of FIG. 8 is started, the oil amount control device 203h determines whether or not the setting of the automatic control mode of the oil amount adjusting valve 401 is ON based on the mode signal (step S201), and when the setting is OFF. Sets the target pressure of the control oil in the oil amount adjustment valve 401 to a set value (step S207). If the setting is ON, the oil amount control device 203h moves the procedure from step S201 to step S202. The mode signal is a signal that is input from an operation panel (not shown) or the like of the gas turbine control device 203 in accordance with the operation of the operator.

Steps S202 and S203
When the setting is ON, the oil amount control device 203h calculates the change rate (time change) of the MWD 204 by differential calculation processing or the like, and determines whether the calculated change rate (absolute value) is equal to or greater than the limit value. (Step S202). This procedure is the same as step S101 (see FIG. 4) in the control procedure of the electric motor 114. If the MWD change rate is below the limit value, the oil amount control device 203h moves the procedure to step S207. If the MWD change rate is equal to or greater than the limit value, the oil amount control device 203h calculates a deviation between the measured value of the measuring instrument 201 and the MWD 204 (power generation output excess or deficiency with respect to the MWD 204) (step S203). Move.

Steps S204 and S205
After calculating the excess / deficiency of the power generation output, the oil amount control device 203h determines whether the excess / deficiency (absolute value) exceeds the threshold (step S204). The threshold value is a setting value stored in the storage device 203b. If the excess or deficiency is less than or equal to the threshold value, the oil amount control device 203h moves the procedure to step S207. If the excess / deficiency exceeds the limit value, the oil amount control device 203h calculates the target pressure of the control oil inside the oil amount adjustment valve 401 based on the excess / deficiency magnitude. For example, the target pressure is set higher with respect to the set pressure as the power generation output is larger or deficient.

Step S206
If the target pressure of the control oil of the oil amount adjustment valve 401 is set in step S205 or S207, the oil amount control device 203h generates an opening degree control signal 402 corresponding to the target pressure and outputs it to the oil amount adjustment valve 401. The procedure of FIG. 8 is terminated.

3-4. Effects According to the present embodiment, the following effects are obtained in addition to the same effects as those of the second embodiment.

Here, in the fluid coupling 116, the torque transmission rate becomes higher as the filling amount of the internal control oil is larger (the pressure is higher). On the other hand, the smaller the amount of control oil filled (the lower the pressure), the lower the torque transmission rate and the greater the allowable deviation in the rotational speed between the turbine shaft 110 and the motor shaft 115. Therefore, in the present embodiment, the procedure of FIG. 8 is repeatedly executed during the turbine load operation. That is, when it is desired to improve the followability of the power generation output to the MWD 204, the control hydraulic pressure of the fluid coupling 116 is increased. Specifically, when the oil amount adjustment valve 401 is provided in the discharge line for the control oil from the fluid coupling 116, an opening degree control signal 402 for reducing the opening degree of the oil amount adjustment valve 401 is generated. Output. On the contrary, when the oil amount adjustment valve 401 is provided in the control oil supply pipe to the fluid coupling 116, an opening degree control signal 402 for increasing the opening degree of the oil amount adjustment valve 401 is generated and output. Further, when it is desired to suppress the torsional stress and pulsation of the turbine shaft 110, or when it is desired to ensure a wide allowable deviation between the rotational speeds of the turbine shaft 110 and the motor shaft 115, the control hydraulic pressure of the fluid coupling 116 is decreased. The procedure for decreasing the control oil pressure is the reverse of the procedure for increasing the control oil pressure.

Note that the target pressure is set when the rate of change of the MWD 204 is small and the motor 114 allows the MWD 204 to follow the power generation output without applying torque to the turn bin shaft 110, or when the power generation output with respect to the MWD 204 is small or insufficient. The value is set to a value (for example, a predetermined minimum value or zero), and the control oil inside the fluid coupling 116 is reduced or completely discharged. The operation procedure of the oil amount adjustment valve 401 at that time is the same as that for lowering the control oil pressure of the fluid coupling 116.

Therefore, according to the present embodiment, by controlling the torque transmission efficiency between the electric motor 114 and the turbine shaft 110, the follow-up performance of the power generation output with respect to, for example, the MWD 204 can be further improved or the turbine shaft 110 can be twisted. The stress can be further suppressed. Further, if necessary, the allowable pressure deviation of the turbine shaft 110 and the motor shaft 115 is increased by reducing the pressure of the control oil, so that the motor 114 can be operated or stopped at a low speed, and the economy is improved.

In the present embodiment, the case where the oil amount adjustment valve 401 is automatically adjusted according to the change rate of the MWD 204 is described as an example. However, the operator manually operates according to the operation state of the gas turbine power generation facility. A configuration in which the opening of the oil amount adjustment valve 401 is adjusted may be employed.

(Fourth embodiment)
The fourth embodiment is different from the above-described embodiments in that it includes a plurality of turbines that can rotate at different rotational speeds. In this embodiment, a case where a two-shaft gas turbine is employed is illustrated.

FIG. 9 is a schematic view of the gas turbine equipment according to the fourth embodiment of the present invention. In the present embodiment, the same parts as those in the already described embodiment are denoted by the same reference numerals as those in the previous drawings, and the description thereof is omitted.

As shown in the figure, the gas turbine 100A in the present embodiment includes two turbines, a high-pressure turbine 109a and a low-pressure turbine 109b. The high-pressure turbine 109a and the low-pressure turbine 109b can be rotated at different rotational speeds because the

turbine shafts

110a and 110b are separated from each other. The high-pressure turbine 109 a is connected to the compressor 103 via the turbine shaft 110 a and constitutes a gas generator together with the compressor 103 and the combustor 105. The electric motor 114 is connected to the turbine shaft 110a of the gas generator through a fluid coupling 116. The low-pressure turbine 109b is connected to the generator 111 via the turbine shaft 110b, and serves as a power turbine that generates the power output of the generator 111. The exhaust 112a of the high-pressure turbine 109a becomes the working gas of the low-pressure turbine 109b, gives rotational power to the low-pressure turbine 109b, and is discharged as the exhaust 112b. Further, since the

turbine shafts

110a and 110b can rotate at different rotational speeds, measuring

instruments

202a and 202b for measuring the turbine rotational speed are provided in the

turbine shafts

110a and 110b, respectively. The turbine rotational speed measured by the measuring

instruments

202 a and 202 b is input to the gas turbine control device 203.

Other hardware configurations are the same as those of the gas turbine equipment (see FIG. 2) according to the second embodiment. In the present embodiment, the compressor 103 is not divided. However, the compressor 103 may be divided and connected to separate turbine shafts in some cases.

Here, in general, the operating characteristics such as pressure, temperature, flow rate, and efficiency vary depending on the rotational speed of the compressor. In a single-shaft gas turbine, the rotational speed of the compressor matches the rotational speed of the turbine shaft. The operating characteristics of the machine depend on the turbine speed. On the other hand, in the case of the present embodiment, the turbine shaft 110a of the gas generator to which the compressor 103 is connected is disconnected from the turbine shaft 110b of the power turbine, so the rotation speed is selected regardless of the rotation speed of the power turbine. be able to. Therefore, the rotation speed that makes the compressor 103 efficient is set as an operating condition, and for example, the deviation between the rotation speed of the gas generator measured by the measuring instrument 202a and the set rotation speed exceeds a threshold value (set value). In this case, the efficiency of the gas turbine equipment can be improved by causing the rotation speed of the gas generator to approach the set rotation speed by applying torque of the electric motor 114. If a motor generator is used as the motor 114, the applied torque can be reversed in the positive and negative directions, so that the rotation speed of the compressor 103 can be adjusted not only on the rising side but also on the lowering side.

Even in the two-shaft gas turbine 100A, problems related to the torsional stress of the turbine shaft 110a when the electric motor 114 is connected can occur, so that the motor shaft 115 can be connected to the turbine shaft 110a via the fluid coupling 116. Meaningful. By connecting the motor shaft 115 via the fluid coupling 116, the torsional stress and torque pulsation generated in the turbine shaft 110a can be suppressed, and the selection range of the rotational speed of the turbine shaft 110a can be expanded. Since the rotational speed at which the efficiency of the compressor 103 is improved varies depending on the atmospheric conditions and the MWD 204, the range of selection of the rotational speed can be widened to fully exhibit the performance of the compressor 103.

In addition, although the specific effect when the invention is applied to the two-shaft gas turbine 100A has been described in advance, according to the present embodiment, it is also possible to obtain the same effect as each of the above-described embodiments. . For example, if the motor 114 is driven by a part of the power generation output of the power generator 111, if the power generation output cannot follow the sudden decrease of the MWD 204, a part of the power generation output of the power generator 111 is reduced by the motor 114. By converting the rotational energy of the gas generator, the power generation output sent to the power system 113 can follow the sudden decrease of the MWD 204. Furthermore, if a motor generator is used for the motor 114, when the MWD 204 increases rapidly, the motor 114 is driven as a generator, and the rotational power of the gas generator is partially converted into electric energy to generate the power output of the generator 111. By compensating, the power generation output sent to the electric power system 113 can follow the rapid increase of the MWD 204.

(Fifth embodiment)
FIG. 10 is a schematic view of a gas turbine facility according to the fifth embodiment of the present invention. In the present embodiment, the same parts as those of the embodiment already described are denoted by the same reference numerals as those in the above-described drawings, and the description thereof is omitted.

This embodiment is a specific example of the fourth embodiment. In the gas turbine facility shown in FIG. 10, an inverter 602 is interposed between a power turbine generator 111 and an electric motor 114a. The electric motor 114 a is a motor generator, and is connected to the turbine shaft 110 a of the gas generator via the fluid coupling 116 and connected to the inverter 602 via the circuit 603. The inverter 602 is connected via a circuit 601 to a power transmission line that connects the generator 111 to the power system 113. In this configuration, the generator 111 and the motor 114a are connected via a circuit 601, an inverter 602, and a circuit 603. Further, at the inlet of the compressor 103, measuring devices 605-607 are provided for measuring the atmospheric temperature, atmospheric pressure, and atmospheric humidity and outputting them to the gas turbine control device 203B.

The gas turbine equipment of the present embodiment is provided with an oil amount adjustment valve 401. The configuration and control mode of the oil amount adjustment valve 401 are the same as those of the third embodiment (see FIGS. 6 to 8). It is the same. Other hardware configurations are the same as those of the gas turbine equipment (see FIG. 9) according to the fourth embodiment.

10, the motor 114a can be driven as a motor by receiving a part of the power generation output of the power generator 111 via the circuit 601, the inverter 602, and the circuit 603. Further, by driving the electric motor 114a as a generator, a part of the rotational power of the gas generator can be converted into electric energy and compensated for the output of the generator 111 via the circuit 603, the inverter 602, and the circuit 601. The operation mode (generator mode / motor mode), the power generation load, and the motor load of the motor 114a are controlled by the inverter 602. The inverter 602 controls the electric motor 114a in accordance with a control signal 604 from the electric motor control device 203f (see FIG. 3 or FIG. 7) of the gas turbine control device 203B. The control signal 604 includes the atmospheric temperature, atmospheric pressure and atmospheric humidity measured by the measuring instruments 605-607, the turbine rotation speed measured by the measuring

instruments

202a and 202b, the power generation output measured by the measuring instrument 201, and the MWD 204 as arguments. Is calculated as For example, if a table of combinations of arguments and the control signal 604 is created, the control signal 604 can be generated based on each input signal. Further, the control signal 604 can be expressed by a function having each argument as a variable, and the control signal 604 can be generated based on each input signal. The temperature of the exhaust 112b can also be used as an argument for calculating the control signal 604. The control signal 604 is not limited to these examples, and may be calculated by other methods.

With this configuration, torque can be applied to the turbine shaft 110a as necessary, and the power generation output sent to the power system 113 can be changed following the sudden change of the MWD 204. Further, the efficiency can be optimized by controlling the rotation speed of the compressor 103 according to the situation. In addition, since the torsional stress and torque pulsation of the turbine shaft 110a at that time are suppressed by the fluid coupling 116, the follow-up control of the power generation output can be realized satisfactorily. Needless to say, the same effects as those of the embodiment described in common in terms of structure can also be obtained.

(Sixth embodiment)
The sixth embodiment is different from the above-described embodiments in that a renewable energy power generation device is provided.

6-1. Gas Turbine Equipment FIG. 11 is a schematic view of gas turbine equipment according to the sixth embodiment of the present invention. In the present embodiment, the same parts as those in the already described embodiment are denoted by the same reference numerals as those in the previous drawings, and the description thereof is omitted.

The gas turbine equipment shown in the figure includes a wind power generator 701 and measuring

instruments

702 and 703. The wind power generator 701 is connected to a power transmission line that connects the generator 111 to the power system 113, and transmits power to the power system 113 together with the generator 111. The measuring

instruments

702 and 703 measure the wind direction and wind speed of natural wind, which is renewable energy converted into electric energy by the wind power generator 701, and output the measured wind direction and wind speed to the gas turbine controller 203C. These measuring

instruments

702 and 703 are installed at predetermined points (may be a plurality of points) that can be windward of the wind power generator 701. Further, the power generation output 704 of the wind power generator 701 measured by a power meter (not shown) is also input to the gas turbine control device 203C.

Other hardware configurations can be the same as those in the fifth embodiment (see FIG. 10). Moreover, although the case where the wind power generator 701 is used as a power generator using renewable energy is illustrated in the present embodiment, the present invention is not limited to this, and other renewable energy such as a solar power generator or a wave power generator. A power generation device or a renewable energy power generation system combining them can also be substituted. For example, when using a solar power generation device, a sunshine meter or the like can be used for the measuring

instruments

702 and 703. Further, in the sense of supplying a signal that can be used to predict fluctuations in power generation output of the renewable energy power generation apparatus to the gas turbine control apparatus 203C, a receiving apparatus that receives weather information from a weather information provider is provided with measuring

instruments

702 and 703. It can also be used.

6-2. Control Device FIG. 12 is a functional block diagram of the gas turbine control device 203C. In the present embodiment, the same parts as those in the already described embodiment are denoted by the same reference numerals as those in the previous drawings, and the description thereof is omitted.

The gas turbine control device 203C shown in Fig. 12 includes an output prediction device 203i. The output prediction device 203i predicts the power generation output fluctuation of the wind power generation device 701 using the wind direction and the wind speed measured by the measuring

devices

702 and 703 as arguments. For example, the wind direction and wind speed measured by the measuring

instruments

702 and 703, and the power generation output data after the set time of the wind power generator 701 are collected in advance, and the wind power generation output after the set time and the combination of the measured wind direction and wind speed If the above relationship is tabulated, the wind power generation output after the set time can be predicted based on the measurement values of the measuring

instruments

702 and 703 according to the table. Therefore, by calculating the difference between the predicted value of the wind power generation output after the set time and the wind power output 704, the fluctuation range of the wind power output after the set time with respect to the current wind power output 704 of the wind power generation device 701 is predicted. The value can be calculated. Based on the measured wind direction and wind speed, the wind power generation output after a set time can be predicted by a physical model of the characteristics of the wind power generation apparatus 701, and the fluctuation of the wind power generation output can also be predicted.

In the present embodiment, the fuel flow control device 203c calculates the fuel flow rate so that the power generation output of the gas turbine equipment measured by the measuring instrument 201 approaches the MWD 204 as in the previous embodiments, and the opening control signal 205 Is output to the fuel adjustment valve 106. The generator control device 203e controls the load of the generator 111 so as to suppress the change in the rotational speed of the power turbine according to the output torque (fuel flow rate) of the power turbine. In the fuel flow control, when the power generation output does not follow the MWD 204, the motor control device 203f gives a command to the inverter 602 to control the motor 114 and absorb the excess or deficiency of the power generation output (the same procedure as in FIG. 8). Then, the intake flow control device 203d outputs an opening degree control signal 206 to the IGV 102 so as to suppress fluctuations in the intake flow rate of the compressor 103. With these controls, the power generation output follows the MWD 204.

At this time, when the predicted value of the power generation output fluctuation of the wind power generator 701 calculated by the output predicting device 203i exceeds the set value, the gas turbine control device 203C of the present embodiment uses the oil amount control device 203h to determine the predicted value. Based on this, the oil amount adjusting valve 401 is controlled to control the torque transmission efficiency of the fluid coupling 116 (see FIG. 13).

6-3. Control Procedure FIG. 13 is a flowchart showing a control procedure of the oil amount adjustment valve 401 by the gas turbine control device 203C. The gas turbine control device 203C repeatedly executes the procedure shown in the figure during the turbine load operation by the oil amount control device 203h.

Steps S301-S304, S307-S309
Steps S301-S304 and S307-S309 are similar to the steps S201-S207 (see FIG. 8) described in the third embodiment. The difference is that steps S305 and S306 are added between steps S304 and S307, and step S310 is further added between steps S306 and S308.

Steps S305, S306, S310
When the deviation of the power generation output with respect to the MWD 204 exceeds the threshold (step S304), the oil amount control device 203h predicts the fluctuation of the wind power generation output by the output prediction device 203i (step S305). After calculating the predicted value of the wind power generation output fluctuation, the oil amount control device 203h determines whether or not the predicted value (absolute value) is less than or equal to the threshold (set value) (step S306), and the predicted value is less than or equal to the threshold. If there is, the target pressure of the control oil to be filled in the fluid coupling 116 is set in accordance with the deviation from the current power generation output MWD 204 in the same manner as in step S205 in FIG. 8 (step S307). If the predicted value exceeds the threshold value, the oil amount control device 203h sets the target pressure of the control oil that fills the fluid coupling 116 based on the predicted value (step S310). For example, when the predicted value of the fluctuation of the wind power generation output exceeds the threshold value, and the fluctuation of the wind power generation output in the future (after the set time) can cause a significant excess or deficiency of the power generation output with respect to the MWD 204, further follow-up The target pressure of the control oil of the fluid coupling 116 is increased with the aim of improving the performance. For example, a value obtained by adding a deviation (relative value) of a predicted value after a set time with respect to the current value of the wind power generation output 704 to a deviation (relative value) of the current power generation output (measured value of the measuring instrument 201) from the MWD 204 (absolute Value) based on the target value.

Step S308
As described above, step S308 is the same as the procedure of step S206 (see FIG. 8) described in the third embodiment. That is, when the target pressure of the control oil of the oil amount adjustment valve 401 is set in step S307, S309, or S310, the oil amount control device 203h generates an opening degree control signal 402 corresponding to the target pressure, and the oil amount adjustment valve 401. To end the procedure of FIG.

The configuration and functions of the functional units of the gas turbine control device 203C other than those described above are the same as those of the gas turbine control device 203A (see FIG. 7) of the third embodiment.

6-4. Effects According to the present embodiment, in addition to the same effects as those of the fifth embodiment, the following effects can be obtained.

Since the power generation output measured by the measuring instrument 201 includes a wind power generation output 704 that can vary greatly depending on weather conditions, the deviation from the MWD 204 can also change drastically. For this reason, the fluctuation of the applied torque by the electric motor 114a by the gas turbine control device 203C can be intensified. According to the present embodiment, by controlling the torque transmission efficiency of the fluid coupling 116 by adding the fluctuation of the wind power generation output to the deviation of the power generation output with respect to the MWD 204, the power generation output including the fluctuation of the wind power generation output with respect to the MWD 204 is controlled. Be prepared for sudden changes in excess and deficiency and respond flexibly. Of course, operation with reduced torsional stress and improved economic efficiency of the turbine shaft 110a is also possible depending on the situation.

In the present embodiment, the control mode including the control procedure of the oil amount adjustment valve 401 of the third embodiment has been described as an example. However, regardless of the deviation from the MWD 204 of the power generation output, the wind power is simply It is also possible to control to increase or decrease the opening of the oil amount adjustment valve 401 depending on whether or not the predicted fluctuation range of the power generation output exceeds a threshold value. For example, the opening degree control signal is such that if the predicted fluctuation range of the wind power generation output exceeds a threshold value, the internal pressure of the fluid coupling 116 is increased more than the current level, and if it is equal to or less than the threshold value, the internal pressure of the fluid coupling 116 is decreased. 402 can also be generated.

(Other)
The technical scope of the present invention is not limited to the aspect of the above embodiment, and various modifications can be included. For example, not all the constituent elements included in each of the above-described embodiments are essential, and elements that are not essential parts of the invention can be omitted as appropriate. In addition, the constituent elements of each embodiment can be replaced with other elements having a common function and role. The embodiments can be combined with each other or partially.

DESCRIPTION OF SYMBOLS 103 Compressor 104 Compressed air 105 Combustor 107 Fuel 108 Combustion gas 109 Turbine 109a High pressure turbine 109b

Low pressure turbine

110, 110a Turbine shaft 111

Generator

114, 114a Electric motor 116 Fluid coupling 201 Measuring device 203f Electric motor control device 203h Oil quantity control device 203i Output prediction device 204 MWD (gas turbine output command)
401 Oil amount adjusting valve 602 Inverter 701 Wind power generator (renewable energy power generator)
702, 703 Measuring instrument

Claims

A compressor that sucks in air and compresses it;
A combustor for combusting compressed air from the compressor together with fuel;
A turbine driven by combustion gas from the combustor;
An electric motor for applying torque to the turbine shaft;
A gas turbine equipment comprising a fluid coupling connecting the turbine shaft and the electric motor.
2. The gas turbine equipment according to claim 1, wherein the electric motor is a motor generator.
The gas turbine equipment according to claim 1, further comprising an electric motor control device that controls the electric motor and applies torque to the turbine shaft when the turbine output is changed beyond a limit value of a change rate by fuel flow control. Gas turbine equipment characterized by
2. The gas turbine equipment according to claim 1, further comprising an oil amount adjusting valve for adjusting an oil amount filled in the fluid coupling.
The gas turbine equipment according to claim 4,
A generator connected to the turbine shaft;
A measuring instrument for measuring the power generation output of the generator;
An oil amount control device that controls the oil amount adjusting valve in accordance with a deviation between a power generation output measured by the measuring instrument and a gas turbine output command to change a torque transmission efficiency of the fluid coupling. The gas turbine equipment.
The gas turbine equipment according to claim 5,
A renewable energy power generator connected to the generator;
An output prediction device for predicting the power generation output of the renewable energy power generation device,
The gas turbine equipment, wherein the oil amount adjusting device controls the oil amount adjusting valve based on the predicted value when a predicted value by the output predicting device exceeds a set value.
The gas turbine equipment according to claim 6, wherein
The renewable energy device is a wind power generator;
The output prediction device predicts a power generation output of the renewable energy power generation device based on a wind speed measured by an anemometer.
8. The gas turbine equipment according to claim 1, comprising a plurality of turbines capable of rotating at different rotational speeds.
9. The gas turbine equipment according to claim 8, wherein the electric motor is connected to a turbine shaft of a gas generator through the fluid coupling.
10. The gas turbine equipment according to claim 9, further comprising an inverter interposed between a power turbine generator and the electric motor.