ROTATING MACHINE CONTROL DEVICE, ROTATING MACHINE EQUIPMENT AND ROTATING MACHINE CONTROL METHOD

Abstract

Control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) comprising a rotating rotor (2, 71) and a housing (5, 48, 78) for covering an outer circumferential side of the rotor (2, 71), wherein the control device (100, 100a, 100b, 100c) comprises: an operating terminal (36, 92) that changes a parameter which is a rotational speed or an output of the rotating machine (2, 71); a distance measuring device (101) that measures a distance between the rotor (2, 71) and the housing (5, 48, 78); a parameter change rate setting unit (120, 140, 140a) that determines a change rate of the parameter in accordance with the distance amount in order to change the change rate of the parameter; and an operating quantity delivery unit (160, 160a) that determines an operating quantity of the operating terminal (36, 92) in accordance with the rate of change of the parameter and delivers the operating quantity to the operating terminal (36, 92), wherein the parameter rate change setting unit (120, 140, 140a) determines the rate of change of the parameter such that the rate of change of the parameter in a case of obtaining a second distance amount that is greater than a first distance amount is higher than the rate of change of the parameter in a case of obtaining the first distance amount.

Description

Technical field

[0001] The present invention relates to a control device for a rotating machine, comprising a rotating rotor and a housing covering an outer circumferential side of the rotor, a rotating machine equipment, a control method for the rotating machine and a control program for the rotating machine. State of the art

[0002] A gas turbine is a type of rotating machine. It includes a compressor that compresses atmospheric air to produce compressed air, a combustion chamber that burns fuel in the compressed air to produce combustion gas, and a turbine that is driven by the combustion gas. The compressor has a compressor rotor that rotates around an axis and a compressor casing that covers the rotor, allowing it to rotate. The turbine has a turbine rotor that rotates around an axis and a turbine casing that covers the rotating rotor. The turbine rotor and the compressor rotor are connected to form a gas turbine rotor. For example, a generator is connected to the gas turbine rotor. A fuel line is connected to the combustion chamber.The fuel line has a fuel control valve that controls the flow rate of the fuel supplied to the combustion chamber.

[0003] In the event of an increase or decrease in the power output or rotational speed of the gas turbine, the operating quantity of the fuel control valve, which serves as one of the operating terminals, is changed. That is, the flow rate of the fuel supplied to the combustion chamber is altered. The operating quantity of the fuel control valve is determined by an external charging command, as disclosed, for example, in PTL 1 below.

[0004] If the operating quantity of the fuel control valve is suddenly changed, the power output or speed of the gas turbine also changes suddenly. Thus, if the power output or speed of the gas turbine is suddenly altered by a sudden change in the operating quantity, the possibility of damage to the gas turbine increases. Therefore, according to a technique disclosed in PTL 1, the operating quantity of the fuel control valve is determined by an external generator output or charge command. A limiter is then provided for the rate of change of the operating quantity, so that the rate of change of the operating quantity does not increase to a predetermined value or higher. The operating quantity obtained beyond the limiter is delivered to the fuel control valve.

[0005] PTL 2 discloses systems, processes, and material, non-volatile, machine-readable media. A system comprises a gas turbine system configured to generate energy by burning a fuel. The system further comprises a controller configured to control the gas turbine system via a two-dimensional operating area and a setpoint. The two-dimensional operating area comprises a plurality of boundaries that define limits for the two-dimensional operating area. The setpoint is configured to be located within the two-dimensional operating area or on the boundaries.

[0006] PTL 3 discloses that the temperature at each point of a part of the gas turbine structure is acquired by the temperature sensing units and input into a simulator. The pressure value near the distance between a moving blade tip and a static blade retaining ring is also input into the simulator by the pressure sensing units. The number of revolutions of a gas turbine is input into the simulator, and the simulator calculates the deformation data of the static and rotor sides of the corresponding structure due to thermal expansion from the structural data of a gas turbine in a structural data file. It then derives a distance from these two deformation data points, inputs it into a storage device, and simultaneously displays it in a display device.The distance can be accurately estimated using the simply structured temperature and pressure sensing units, without the need for a distance sensor.

[0007] PTL 4 discloses that a thrust requirement signal is sent to a processor of a gas turbine engine and modified according to the growth time constants of a rotor and / or a casing of the machine in order to control the rotational speed or the rate of change of rotational speed of the machine and thus prevent contact between the rotor and the casing.

[0008] PTL 5 discloses that the exhaust air from a compressor is partially extracted and fed into a chiller, where the air is cooled by a refrigerant flowing in a refrigerant line. The cooled air is then directed by a fan to a rotor cooling air inlet, thereby cooling a gas turbine rotor. A distance sensor and a temperature sensor are provided on a fixed side opposite a two-stage impeller and a cooler outlet line, respectively. These sensors detect the distance at the tip of an impeller and the temperature of the cooling air, and the results are then fed into a controller. The controller adjusts the degree of valve opening, reducing the temperature of the cooling air at startup, decreasing the strain, and increasing the distance; conversely, it increases the temperature and strain and decreases the distance at rating.The control system regulates the distance to maintain the optimal distance according to the operating conditions. List of citations from patent literature [PTL 1] JP 2016 - 37 882 A [PTL 2] JP 2015 - 190 469 A [PTL 3] JP 2000 - 27 606 A [PTL 4] US 2015 / 0 159 499 A1 [PTL 5] JP H11 - 50 809 A Summary of the invention: Technical problem

[0009] As described above, limiting the rate of change of the operating output at the operating terminal is a necessary technique to prevent damage to the gas turbine. On the other hand, in a power generation industry, it is preferable for the power output or rotational speed of the gas turbine to reach a setpoint quickly. In particular, when a solar or wind power plant, whose power output is influenced by weather conditions, is connected to a power grid, it is preferable for the power output or rotational speed of the gas turbine to reach the setpoint quickly in order to cope with sudden changes in power output.

[0010] Therefore, the present invention aims to provide a technique that enables the rotational speed or power output of a rotating machine to reach a setpoint in a short time, while preventing damage to the rotating machine. Solutions to the problem

[0011] According to one aspect of the invention, to achieve the object described above, a control device for a rotating machine is provided, comprising a rotating rotor and a housing for covering an outer circumferential side of the rotor. The control device includes an operating terminal that changes a parameter, which is a rotational speed or a power output of the rotating machine; a distance measuring device that measures a distance between the rotor and the housing; a parameter change rate setting unit that determines a change rate of the parameter in accordance with the distance in order to change the parameter change rate; and an operating quantity delivery unit that determines an operating quantity for the operating terminal in accordance with the parameter change rate and delivers the operating quantity to the operating terminal.

[0012] If the parameter, such as the rotational speed or power output of the rotating machine, increases or decreases, the distance between the rotor and the housing may temporarily decrease in some cases. When this distance decreases, the rotor and housing come into contact, potentially causing partial damage to either the rotor or the housing.

[0013] According to this aspect, the rate of change is determined so that the parameter's rate of change is adjusted in accordance with the distance amount. Subsequently, the operating quantity of the operating terminal is determined in accordance with the rate of change, and the operating quantity is delivered to the operating terminal. Therefore, according to this aspect, the parameter's rate of change is adjusted in accordance with the distance amount.

[0014] Here, in the control device of the rotating machine, the parameter change rate setting unit can determine the rate of change of the parameter, so that the rate of change of the parameter in a case of obtaining a second distance amount that is greater than a first distance amount is higher than the rate of change of the parameter in a case of obtaining the first distance amount.

[0015] Furthermore, the parameter change rate setting unit in the control device of one of the rotating machines described above may include a basic change rate calculation unit, which obtains a basic change rate of the parameter in accordance with a deviation between a setpoint value of the parameter and a measured value of the parameter; a change value calculation unit, which obtains a change value to change the basic change rate in accordance with the distance amount; and a change rate change unit, which changes the basic change rate using the change value.

[0016] In the control device of the rotating machine with the change-value calculation unit, the change-value calculation unit can have a first calculation unit that uses a relationship between the distance amount and a first change value to modify the base rate of change in order to obtain the first change value corresponding to the distance amount. In this case, the rate-of-change unit can use the first change value to modify the base rate of change.

[0017] In the control device of the rotating machine with the first calculation unit, the change value calculation unit can have a second calculation unit that receives a second change value for changing the basic rate of change in accordance with a deviation between the distance amount and a predetermined allowable minimum distance amount. In this case, the rate of change change unit can use the first change value and the second change value to change the basic rate of change.

[0018] In the control device of a rotating machine, following one of the rotating machines with the first change calculation unit, the relationship can be a relationship in which the first change value increases with increasing distance amount.

[0019] According to another aspect of the invention, a rotating machine equipment is provided to achieve the object described above, which includes one of the control devices described above and the rotating machine.

[0020] In rotating machinery equipment, the rotating machine can be a gas turbine, comprising a compressor that generates compressed air by compressing air, a combustion chamber that produces combustion gas by burning fuel in the compressed air, and a turbine driven by the combustion gas. The compressor can have a rotating compressor rotor and a compressor casing that covers the compressor rotor. The turbine can have a rotating turbine rotor and a turbine casing that covers the turbine rotor. The compressor rotor and the turbine rotor can be mechanically connected to form a gas turbine rotor. The operating terminal can be a fuel control valve that controls the flow rate of fuel supplied to the combustion chamber. The distance measuring device can measure the gas turbine distance between the turbine rotor and the turbine casing.In this case, the parameter change rate setting unit can determine the rate of change of the parameter, so that the rate of change of the parameter is changed in accordance with the gas turbine spacing amount, at least when the parameter increases, when the parameter increases, and when the parameter decreases.

[0021] The gas turbine clearance temporarily decreases when the parameter increases, and conversely, it temporarily increases when the parameter decreases. Based on this, the rate of change is determined so that the parameter's rate of change is adjusted in accordance with the gas turbine clearance when the parameter increases. Subsequently, the fuel control valve's operating quantity is maintained and delivered to the fuel control valve in accordance with the rate of change. Therefore, even if the gas turbine parameter increases, the parameter can reach its setpoint quickly, while preventing the gas turbine clearance from becoming excessively small.

[0022] In rotating machinery, where the rotating machine is the gas turbine, the compressor can be located within the compressor housing and may include an inlet guide vane that controls the flow rate of the air entering the compressor housing. In this case, the control device may include an inlet air flow rate setting unit, which determines the operating rate of the inlet guide vane in accordance with the gas turbine clearance, and an inlet air flow rate delivery unit, which delivers the operating rate of the inlet guide vane to the inlet guide vane.

[0023] If the intake air flow rate, that is, the flow rate of air entering the compressor housing, increases without a change in the fuel flow rate, the temperature of the combustion gas flowing in the combustion gas path decreases, and the gas turbine clearance is altered. Accordingly, the intake air flow rate is adjusted in line with the gas turbine clearance. This prevents the gas turbine clearance from becoming excessively small.

[0024] In any rotating machinery setup described above, where the rotating machine is the gas turbine, the gas turbine may include a vent line that vents the air compressed by the compressor so that the vented air is directed to a rotor blade of the turbine rotor, a cooler that cools the air flowing in the vent line, and a cooling control that regulates the amount of cooling applied to the air cooled by the cooler. In this case, the control device may include a cooling rate setting unit that determines an operating rate of the cooling control in accordance with the gas turbine clearance amount, and a cooling rate delivery unit that delivers the operating rate of the cooling control to the cooling control.

[0025] If the cooling volume of the air cooled by the cooler is changed, the cooling volume of the rotor blades cooled by the air is also changed, and the gas turbine clearance is adjusted accordingly. Therefore, the cooling volume of the air is adjusted in line with the gas turbine clearance. This prevents the gas turbine clearance from becoming excessively small.

[0026] Here, in the rotating machinery equipment, the rotating machine can be a steam turbine driven by steam. The steam turbine can have a rotating steam turbine rotor and a steam turbine casing that covers the steam turbine rotor. The operating terminal can be a steam control valve that controls the flow rate of the steam supplied to the steam turbine. The distance measuring device can measure the steam turbine distance between the steam turbine rotor and the steam turbine casing. In this case, the parameter change rate setting unit can determine the rate of change of the parameter in accordance with the steam turbine distance, so that the rate of change of the parameter is adjusted at least when the parameter increases, when the parameter increases, and when the parameter decreases.

[0027] The steam turbine clearance temporarily decreases when the parameter decreases, and temporarily increases when the parameter increases. Based on this, the rate of change is determined so that the rate of change of the parameter is adjusted in accordance with the steam turbine clearance when the parameter decreases. Subsequently, the operating flow rate of the steam control valve is maintained and delivered to the steam control valve in accordance with the rate of change. Therefore, even with a decreasing steam turbine parameter, the parameter can reach the setpoint quickly, while preventing the steam turbine clearance from becoming excessively small.

[0028] Furthermore, depending on the aspect, the rotating machinery equipment can include a first rotating machine and a second rotating machine. The first rotating machine can be a gas turbine.

[0029] The second rotating machine can be a steam turbine. The rotating machinery equipment can include a heat recovery system that generates steam using exhaust gas from the gas turbine and feeds the steam to the steam turbine. The gas turbine can have a compressor that generates compressed air by compressing air, a combustion chamber that generates combustion gas by burning a fuel in the compressed air, and a turbine that is driven by the combustion gas. The compressor can have a rotating compressor rotor and a compressor casing that covers the compressor rotor. The turbine can have a rotating turbine rotor and a turbine casing that covers the turbine rotor. The compressor rotor and the turbine rotor can be mechanically connected to form a gas turbine rotor.The operating terminal of the gas turbine can be a fuel control valve that controls the flow rate of fuel to be supplied to the combustion chamber. The gas turbine distance meter can be a gas turbine distance meter that measures the distance between the turbine rotor and the turbine casing. The steam turbine can have a rotating steam turbine rotor and a steam turbine casing that covers the steam turbine rotor. The operating terminal of the steam turbine can be a steam control valve that controls the flow rate of steam to be supplied to the steam turbine from the heat recovery system. The steam turbine distance meter can be a steam turbine distance meter that measures the distance between the steam turbine rotor and the steam turbine casing.In this case, the gas turbine parameter rate adjustment unit can determine the rate of change of a gas turbine parameter, which is the parameter relating to the gas turbine, so that the rate of change of the gas turbine parameter is adjusted in accordance with the gas turbine clearance amount when the gas turbine parameter increases, and determine the rate of change of the gas turbine parameter so that the rate of change of the gas turbine parameter is adjusted in accordance with the steam turbine clearance amount when the gas turbine parameter decreases. The gas turbine operating quantity delivery unit can determine an operating quantity of the fuel control valve in accordance with the rate of change of the gas turbine parameter determined by the gas turbine parameter rate adjustment unit and can deliver the operating quantity of the fuel control valve to the fuel control valve.The steam turbine parameter rate adjustment unit can determine the rate of change of a steam turbine parameter, which is the parameter relating to the steam turbine, so that the rate of change of the steam turbine parameter is modified in accordance with the gas turbine clearance amount when the steam turbine parameter increases, and can determine the rate of change of the steam turbine parameter so that the rate of change of the steam turbine parameter is modified in accordance with the steam turbine clearance amount when the steam turbine parameter decreases. The steam turbine operating quantity delivery unit can determine an operating quantity of the steam control valve in accordance with the rate of change of the steam turbine parameter determined by the steam turbine parameter rate adjustment unit and can deliver the operating quantity of the steam control valve to the steam control valve.

[0030] The rotating machinery equipment according to the embodiment is a so-called combined power plant. In the combined power plant, if the parameter of the gas turbine increases, the parameter of the steam turbine increases in response. Furthermore, in the gas turbine, if the parameter increases, the gas turbine distance temporarily decreases. If the parameter decreases, the gas turbine distance temporarily increases. Similarly, in the steam turbine, if the parameter increases, the steam turbine distance temporarily increases. If the parameter decreases, the steam turbine distance temporarily decreases.

[0031] Therefore, according to this aspect, in a case where the gas turbine parameter and the steam turbine parameter increase, the operating quantity of the gas turbine and steam turbine operating terminal is determined based on the temporarily decreasing gas turbine clearance amount. Furthermore, according to this aspect, in a case where the gas turbine parameter and the steam turbine parameter decrease, the operating quantity of the gas turbine and steam turbine operating terminal is determined based on the steam turbine clearance amount, which also temporarily decreases. Therefore, according to this aspect, even if the gas turbine and steam turbine parameters increase or decrease, the parameter can reach the setpoint in a short time, while each gas turbine clearance amount and steam turbine clearance amount is prevented from becoming extremely small.

[0032] According to a further aspect of the invention, a control method for a rotating machine is provided to achieve the problem described above. This method includes a rotating rotor and a housing for covering an outer circumferential side of the rotor. The control method comprises a step of receiving a distance value between the rotor and the housing, a step of determining a rate of change of a parameter, which is either the rotational speed or the power output of the rotating machine, such that the rate of change of the parameter is modified in accordance with the distance value, and a step of determining an operating quantity from an operating terminal to modify the parameter in accordance with the rate of change of the parameter and supplying the operating quantity to the operating terminal.

[0033] Here, in the control procedure of the rotating machine, in the step of determining the rate of change of the parameter, the rate of change of the parameter can be determined such that the rate of change of the parameter in the case of obtaining a second distance amount that is greater than a first distance amount is higher than the rate of change of the parameter in the case of obtaining the first distance amount.

[0034] Furthermore, in the control procedure described above, for each of the rotating machines, the step of determining the rate of change of the parameter may include a step of obtaining a basic rate of change of the parameter in accordance with a deviation between a setpoint of the parameter and a measured value of the parameter, a step of obtaining a change value to change the basic rate of change in accordance with the distance amount, and a step to change the basic rate of change using the change value.

[0035] In the control procedure of the rotating machine, where the step to obtain the change value is performed, this step can include a step where a relationship between the distance amount and an initial change value is used to modify the base rate of change in order to obtain the initial change value that corresponds to the distance amount. In this case, the initial change value can be used to modify the base rate of change in the step to modify the base rate of change.

[0036] In the control procedure of the rotating machine, where the step to obtain the first change value is performed, this step can include a step to obtain a second change value for modifying the base rate of change in accordance with a deviation between the distance amount and a predetermined minimum permissible distance amount. In this case, the first change value can be used to modify the base rate of change in the step to modify the base rate of change.

[0037] In the control procedure of one of the rotating machines described above, where the step to obtain the first change value is performed, the relationship can be one in which the first change value increases with increasing distance amount. Advantageous effects of the invention

[0038] According to one aspect of the present invention, the rotational speed or power output of a rotating machine can reach a setpoint in a short time, while preventing damage to the rotating machine. Brief description of the drawings Fig. Figure 1 is a concept diagram representing a configuration of a gas turbine power plant according to a first embodiment of the present invention. Fig. Figure 2 is a sectional view showing a main part of a gas turbine according to the first embodiment of the present invention. Fig. 3 is an enlarged view showing Part III in Fig. 2 represents. Fig. Figure 4 is a view describing an arrangement of several distance measuring devices according to the first embodiment of the present invention. Fig. Figure 5 is a functional block diagram representing a configuration of a control device according to the first embodiment of the present invention. Fig. Figure 6 is a functional block diagram representing a configuration of a power output rate of change adjustment unit according to the first embodiment of the present invention. Fig. Figure 7 is a functional block diagram representing a configuration of a speed-rate-of-change control unit according to the first embodiment of the present invention. Fig. Figure 8 is a switching block diagram representing a hardware configuration of the control device according to the first embodiment of the present invention. Fig. Figure 9 is a flowchart illustrating the operation of the control device according to the first embodiment of the present invention. Fig. Figure 10 is a diagram showing a change in power output, a change in rotational speed and a change in distance over time in a case where the rate of change control based on a distance amount is not carried out in the gas turbine according to the first embodiment of the present invention. Fig. Figure 11 is a diagram showing a change in rotational speed and a change in distance over time in a case where rate of change control based on a distance amount is carried out in the gas turbine according to the first embodiment of the present invention. Fig. Figure 12 is a diagram showing a change in power output and a change in distance over time in a case where rate of change control based on a distance amount is performed in a gas turbine according to a second embodiment of the present invention. Fig. Figure 13 is a concept diagram illustrating a configuration of a steam turbine power plant according to the second embodiment of the present invention. Fig. Figure 14 is a functional block diagram representing a configuration of a control device according to the second embodiment of the present invention. Fig. Figure 15 is a concept diagram representing a configuration of a gas compression system according to a third embodiment of the present invention. Fig. Figure 16 is a functional block diagram representing a configuration of a control device according to the third embodiment of the present invention. Fig. Figure 17 is a concept diagram representing a configuration of a combined power plant according to a fourth embodiment of the present invention. Fig. Figure 18 is a functional block diagram representing a configuration of a control device according to the fourth embodiment of the present invention. Description of the embodiments

[0039] Below, various embodiments according to the present invention are described in detail with reference to the drawings. [First embodiment]

[0040] Below, a first embodiment of the rotating machine equipment according to the present invention is described with reference to the Fig. 1 to 11 described.

[0041] The rotating machinery equipment according to the present embodiment is a gas turbine power plant, as described in Fig. Figure 1 shows the gas turbine power plant system comprising a gas turbine 1, a generator 9 that generates energy by driving the gas turbine 1, a cooling device 60 that cools some of the configuration components of the gas turbine 1, and a control device 100.

[0042] The gas turbine 1 includes a compressor 10 that compresses air, a combustion chamber 30 that generates combustion gas by burning a fuel in the air compressed by the compressor 10, and a turbine 40 that is driven using the combustion gas.

[0043] As in the Fig. 1 and Fig. As shown in Figure 2, the compressor 10 includes a compressor rotor 11 which rotates about an axis Ar, a compressor housing 18 which covers the compressor rotor 11, several stator blade rows 14, an inlet guide vane (IGV) 21 which controls a flow rate which flows into the compressor housing 18.

[0044] In the following description, a direction in which the axis Ar extends is referred to as the axial direction Da, one side in the axial direction Da as the axial upstream side Dau, and the other side as the axial downstream side Dad.

[0045] The axial upstream side Dau is the upstream side of an airflow within the compressor 10 and the upstream side of a combustion gas flow within the turbine 40. The axial downstream side Dad is the downstream side of the airflow within the compressor 10 and the downstream side of the combustion gas flow within the turbine 40. Furthermore, a circumferential direction around the axis Ar is simply called the circumferential direction Dc, and a direction perpendicular to the axis Ar is called the radial direction Dr. In the radial direction Dr, a side closer to the axis Ar is called the radial inner side Dri, and a side farther from the axis Ar is called the radial outer side Dro.

[0046] The compressor rotor 11 has a rotor shaft 12 extending in the axial direction Da around the axis Ar and several rotor blade rows 13 attached to the rotor shaft 12. The several rotor blade rows 13 are aligned with each other in the axial direction Da. Each rotor blade row 13 is configured to contain several rotor blades aligned with each other in the circumferential direction Dc. A stator blade row 14 is located on each axial downstream side Dad of the several rotor blade rows 13. The respective stator blade rows 14 are arranged within the compressor housing 18. Each stator blade row 14 is configured to contain several stator blades aligned with each other in the circumferential direction Dc.A space between the radial outer surface Dro of the rotor shaft 12 and the radial inner surface Dri of the compressor housing 18, that is, an annular space in the region where the stator blade row 14 and the rotor blade row 13 are located in the axial direction Da, forms an air compression flow path 19 in which the air is compressed as it flows. That is, the compressor 10 is a multi-stage axial flow compressor.

[0047] The compressor housing 18 has a compressor body housing 18a and an intermediate housing 18b.

[0048] The compressor body housing 18a covers an outer circumferential side in an area where the stator blade row 14 and the rotor blade row 13 are arranged in the axial direction Da. The intermediate housing 18b is connected to the axial downstream side Dad of the compressor body housing 18a. The compressed air discharged from the compressor body housing 18a flows into the intermediate housing 18b.

[0049] The inlet guide vane (IGV) 21 is arranged in the compressor housing 18a. The IGV 21 has several movable blades 22 and a driver 23 that changes the angle of the several movable blades 22. The several movable blades 22 are arranged furthest upstream on the axial upstream side Dau of the rotor blade row 13.

[0050] The turbine 40 has a turbine rotor 41 rotating about the axis Ar, a turbine casing 48 covering the turbine rotor 41, and several stator blade rows 53. The turbine rotor 41 has a rotor shaft 42 extending axially Da around the axis Ar, and several rotor blade rows 43 attached to the rotor shaft 42. The several rotor blade rows 43 are aligned with each other axially Da. Each rotor blade row 43 is configured to include several rotor blades 44 aligned circumferentially Dc. A stator blade row 53 is located on each axial upstream side Dau of the several rotor blade rows 43. The respective stator blade rows 53 are arranged in the turbine casing 48. The respective stator blade rows 53 are all configured to include several stator blades 54 that are aligned with each other in the circumferential direction Dc.A space between an outer circumferential side of the rotor shaft 42 and an inner circumferential side of the turbine casing 48, that is, an annular space in a region where the stator blade row 53 and the rotor blade row 43 are located in the axial direction Da, forms a combustion gas flow path 49 in which combustion gas flows from the combustion chamber 30. In the following description, of the several rotor blade rows 43, the rotor blade row furthest upstream on the axial side is referred to as the first rotor blade row, and the rotor blade rows on the axial downstream side are referred to as the second rotor blade row, a third rotor blade row, and so on.

[0051] The combustion chamber 30 is arranged in the intermediate housing 18b, as shown in Fig. Figure 2 shows the combustion chamber 30. It has a combustion cylinder (or rear cylinder) 31, which feeds high-temperature and high-pressure combustion gas G into the combustion gas flow path 49 of the turbine 40, and a fuel injector 32, which injects fuel F into the combustion cylinder 31 together with the compressed air supplied by the compressor 10. A fuel line 35, through which the fuel F flows, is connected to the fuel injector 32. The fuel line 35 has a fuel control valve (operating terminal) 36.

[0052] As in Fig. As shown in Figure 1, the compressor rotor 11 and the turbine rotor 41 are located on the same axis Ar and are connected to each other, forming a gas turbine rotor 2. A rotor of the generator 9 is connected to the gas turbine rotor 2. Furthermore, the compressor housing 18 and the turbine housing 48 are connected to each other, thus forming a gas turbine housing 5. The intermediate housing 18b in the compressor housing 18 according to the present embodiment is referred to as the combustion chamber compartment, and a part that does not include the combustion chamber compartment (intermediate housing 18b) in the compressor housing 18 according to the present embodiment is, in some cases, simply referred to as the compressor housing.

[0053] In the present application, however, a part which includes the combustion chamber compartment (intermediate housing 18b) is referred to as the compressor housing 18.

[0054] In the present embodiment, the gas turbine 1, which includes the gas turbine rotor 2 rotating about the axis Ar, and the gas turbine casing 5 covering the gas turbine rotor 2, forms a rotating machine of the axial flow type.

[0055] As in the Fig. 1 and Fig. As shown in Figure 2, the cooling device 60 comprises a vent line 61, a cooler 62, and a cooling control unit 64. The vent line 61 has a first terminal and a second terminal. The first terminal of the vent line 61 is connected to the intermediate housing 18b, and the second terminal is connected via the rotor shaft 42 of the turbine rotor 41 to the rotor blade rows 44a, which are multiple rotor blades that configure the first rotor blade row. The vent line 61 carries the compressed air discharged from the compressor housing 18a and flowing into the intermediate housing 18b to the multiple rotor blade rows 44a. The cooler 62 is a heat exchanger that cools the compressed air by heat exchange between the compressed air flowing into the vent line 61 and a cooling medium. A media line 63, through which the cooling medium flows, is connected to the cooler 62. The cooling control 64 is arranged in the medium line 63.The cooling control 64 is a flow control valve that controls the amount of cooling of the compressed air by controlling the flow rate of the coolant flowing in the medium line 63.

[0056] As in the Fig. 2 and Fig. As shown in Figure 3, the vent line 61 is connected to a first stepped shaft section 42a, to which the first row of rotor blades is attached in the rotor shaft 42 of the turbine rotor 41. The first stepped shaft section 42a has a cooling channel 42c that is connected to the vent line 61. Furthermore, a cooling channel 44c, which is connected to the cooling channel 42c of the first stepped shaft section 42a, is formed within the multiple rows of rotor blades 44a of the first row that constitute the first rotor blade row. The cooling channel 44c of the first rotor blade row 44a is open in a section that comes into contact with the combustion gas G on a surface of the first rotor blade row 44a. Therefore, the compressed air supplied by the compressor 10 is cooled by the cooler in a process of flowing in the vent line 61.The compressed air is then discharged into the combustion gas flow path 49 via the cooling channel 42c formed in the first step shaft section 42a and the cooling channel 44c formed in the first rotor blade row 44a.

[0057] Of the configuration components of the gas turbine 1, the rotor blade 44, the stator blade 54, components forming the inner circumferential surface in the turbine casing 48, and the combustion cylinder 31 are all high-temperature components that come into contact with the high-temperature combustion gas G. According to the present embodiment, the first rotor blade row 44a is cooled by cooling air Am, which is the compressed air cooled from the high-temperature components by the cooler 62.

[0058] The cooler 62 according to the present embodiment is a heat exchanger. However, the cooler 62 can, for example, be of a type in which the compressed air is cooled by a blower directing the air to a duct through which the compressed air flows. In this case, for example, the cooling control is a motor equipped with an inverter for changing the speed (RPM) of the blower.

[0059] As in Fig. As shown in Figure 1, the control device 100 comprises a fuel control valve 36, a distance sensor 101, a tachometer 102, a power output meter 103, and a control device body 110. The distance sensor 101 measures a distance CL between the turbine housing 48 and the turbine rotor 41. The tachometer 102 measures the rotational speed RPM of the gas turbine rotor 2. The power output meter 103 measures the power output PW of the gas turbine 1, that is, the amount of energy generated by the generator. Both the tachometer 102 and the power output meter 103 are examples of parameter counters.

[0060] As in Fig. As shown in Figure 3, there is a distance between the rotor blade 44 of the turbine rotor 41, which rotates about the axis Ar, and the turbine housing 48, which covers the turbine rotor 41. The distance measuring device 101, according to the present embodiment, measures the distance CL between the first row of rotor blades 44a and the turbine housing 48. The distance measuring device 101 is attached to the turbine housing 48. For example, the distance measuring device 101 is a capacitive measuring device that measures capacitance between the first row of rotor blades 44a and the turbine housing 48 in order to convert a measured capacitance value into the distance. For example, the distance measuring device 101 can be a measuring device that detects a temperature of the turbine housing 48 in order to convert the detected temperature into the distance. The distance measuring device 101 can measure the distance between the second row of rotor blades 44a and the turbine housing 48.In addition, the distance measuring device 101 can measure the distance between the first rotor blade row 44a and the turbine housing 48 and the distance between the second rotor blade row 44 and the turbine housing 48.

[0061] As in Fig. As shown in Figure 4, the control device 100 according to the present embodiment includes several distance measuring devices 101. One distance measuring device 101 is arranged in an upper section of the turbine housing 48. Another distance measuring device 101 is arranged in a lower section of the turbine housing 48. A further distance measuring device 101 is arranged in an approximate central section in an upward / downward direction of the turbine housing 48 and in a right-hand lateral section from the axis Ar. A further distance measuring device 101 is arranged in an approximate central section in the upward / downward direction of the turbine housing 48 and in a left-hand lateral section from the axis Ar.

[0062] As in Fig. As shown in Figure 5, the control device body 110 functionally comprises a distance signal processing unit 111, a power output rate adjustment unit 120, a speed rate adjustment unit 140, a fuel operating quantity delivery unit 160, a cooling operating quantity adjustment unit 170, a cooling operating quantity delivery unit 179, a supply air operating quantity adjustment unit 180 and a supply air operating quantity delivery unit 189.

[0063] The distance signal processing unit 111 receives a signal emitted by the multiple distance measuring devices 101 and outputs the minimum distance amount CL from the distance amounts CL measured by the multiple distance measuring devices 101.

[0064] The power output rate change setting unit 120 comprises a base power output rate change calculation unit 121, a change value calculation unit 124, and a change unit 130. The base power output rate change calculation unit 121 receives a base power output rate change ΔPWb based on a deviation between a target power PWt determined in accordance with a charging command or an actuation command and a power output PW measured by the power output meter 103. The change value calculation unit 124 receives a change value to modify the base power output rate change ΔPWb in accordance with the distance amount CL output by the distance signal processing unit 111. The change unit 130 modifies the base power output rate change ΔPWb using the change value. The rate of change of a power output PW is the amount of change in the power output PW per unit of time.

[0065] The speed rate of change setting unit 140 comprises a base speed rate of change calculation unit 141, a change value calculation unit 144, and a change unit 150. The base speed rate of change calculation unit 141 receives a base speed rate of change ΔRPMb based on a deviation between a target speed RPMt, determined in accordance with the charging command or the actuation command, and the speed RPM measured by the tachometer 102. The change value calculation unit 144 receives a change value to modify the base speed rate of change ΔRPMb in accordance with the distance value CL, output by the distance signal processing unit 111. The change unit 150 modifies the base speed rate of change ΔRPMb using the change value. The speed rate of change RPM is the amount of change in speed RPM per unit of time.

[0066] The fuel delivery unit 160 comprises a power output rate conversion unit 162, a speed rate conversion unit 164, and a selection unit 169. The power output rate conversion unit 162 converts a power output rate PW, set by the power output rate adjustment unit 120, into an operating quantity of the fuel control valve 36, which is an operating terminal. The speed rate conversion unit 164 converts a speed rate ΔRPM set by the speed rate adjustment unit 140 into an operating quantity of the fuel control valve 36, which is an operating terminal. The selection unit 169 only supplies the operating quantity received from the power output rate change conversion unit 162 and an operating quantity from the operating quantities received from the speed rate change conversion unit 164 to the fuel control valve 36.

[0067] The cooling quantity setting unit 170 has a cooling quantity generation unit 171 and a modification unit 172. For example, the cooling quantity generation unit 171 generates a cooling quantity that is an operating quantity of the cooling controller 64. Here, the cooling quantity generation unit 171 generates the operating quantity of the fuel control valve 36, which is delivered by the fuel quantity delivery unit 160; that is, the cooling quantity, which increases with increasing fuel flow rate. The modification unit 172 changes the cooling quantity in accordance with the distance value CL, which is delivered by the distance signal processing unit 111. The cooling quantity delivery unit 179 delivers the modified cooling quantity to the cooling controller 64.

[0068] The intake air operating quantity setting unit 180 has an IGV opening degree generation unit 181 and a modification unit 182. The IGV opening degree generation unit 181 generates an IGV opening degree, which is an opening degree of the IGV 21. Here, the IGV opening degree generation unit 181 generates the actuation quantity of the fuel control valve 36, which is delivered by the fuel operating quantity delivery unit 160; in other words, the IGV opening degree, which increases as the fuel flow rate increases. The modification unit 182 changes the IGV opening degree in accordance with the distance value CL, which is delivered by the distance signal processing unit 111. The supply air operating quantity delivery unit 189 transmits the changed IGV opening degree to the driver 23 of the IGV 21.

[0069] As in Fig. As shown in Figure 6, the basic power output rate of change calculation unit 121 comprises a setpoint power calculation unit 122 and a ΔPI calculation unit 123. The setpoint power calculation unit 122 receives a setpoint power PWt in accordance with the charging command or the actuation command. The ΔPI calculation unit 123 receives a deviation between the power output PW measured by the power output meter 103 and the setpoint power PWt and receives a basic power output rate of change ΔPWb, which is a proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.

[0070] The change value calculation unit 124 of the power output rate change setting unit 120 has an upper limit power output rate change calculation unit 125, a first change value calculation unit (first calculation unit) 126, and a second change value calculation unit (second calculation unit) 127. The upper limit power output rate change calculation unit 125 has a characteristic map 125m that shows a relationship between the actual power output PW and an upper limit power output rate change ΔPWL, which is an upper limit value of the power output rate change ΔPW. The upper limit power output rate change calculation unit 125 uses the characteristic map 125m to obtain the upper limit power output rate change ΔPWL, which corresponds to the power output PW measured by the power output meter 103.The first change value calculation unit 126 of the power output rate change setting unit 120 has a characteristic map 126m that specifies a relationship between the distance value CL and a first change value ΔPWc1 for changing the base power output rate change ΔPWb. The first change value calculation unit 126 uses the characteristic map 126m to obtain the first change value ΔPWc1, which corresponds to the distance value CL output by the distance signal processing unit 111. The relationship indicated by the characteristic map 126m is essentially one in which the first change value ΔPWc1 increases as the distance value CL increases. Therefore, the first change value PWc1 obtained by the first change value calculation unit 126 increases as the distance value CL increases.Furthermore, in characteristic map 126m, if the distance CL is greater than a permissible minimum distance CLmin, the first change value PWc1 indicates a positive value. If the distance CL is equal to or less than the permissible minimum distance CLmin, the first change value ΔPWc1 indicates a negative value. The permissible minimum distance CLmin is a permissible minimum value that relates to the distance. The second change value calculation unit 127 of the power output rate of change adjustment unit 120 has a permissible minimum value storage unit 128 and a ΔPI calculation unit 129. The permissible minimum value storage unit 128 stores the permissible minimum distance CLmin.The ΔPI calculation unit 129 receives a deviation between the permissible minimum distance CLmin and the distance CL output by the distance signal processing unit 111 and receives a second change value ΔPWc2, which is a proportional and integral controlled variable (PI controlled variable) corresponding to the deviation. Therefore, the second change value ΔPWc2, obtained by the second change value calculation unit 127, increases when the deviation between the permissible minimum distance CLmin and the distance CL increases.

[0071] The change unit 130 of the power output rate change setting unit 120 has a first adder 131, a second adder 132, and a minimum value selector 133. The first adder 131 adds the first change value ΔPWc1 received from the first change value calculation unit 126 and the second change value ΔPWc2 received from the second change value calculation unit 127. The second adder 132 adds the upper limit power output rate change PWL received from the upper limit power output rate change calculation unit 125 and the power output of the first adder 131. That is, the second adder 132 outputs a value obtained by adding the first change value PWc1, the second change value PWc2, and the upper limit power output rate change PWL.The minimum value selector 133 selects a smaller value from the basic power output rate of change PWb obtained from the basic power output rate of change calculation unit 121 and the power value from the second adder 132, and outputs the smaller value as the power output rate of change PW. The power output rate of change PW output by the minimum value selector 133 is input into the power output rate of change conversion unit 162 of the fuel delivery unit 160 described above.

[0072] As in Fig. As shown in Figure 7, the basic speed-rate of change calculation unit 141 has a target speed calculation unit 142 and a PI calculation unit 143.

[0073] The target speed calculation unit 142 receives a target speed RPMt in accordance with the charging command or the actuation command. The PI calculation unit 143 receives a deviation between the speed RPM measured by the tachometer 102 and the target speed RPMt and receives a base speed change rate RPMb, which is a proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.

[0074] The change value calculation unit 144 of the speed-rate-of-change setting unit 140 has an upper limit speed-rate-of-change calculation unit 145, a first change value calculation unit 146, and a second change value calculation unit 147. The upper limit speed-rate-of-change calculation unit 145 has a characteristic map 145m that specifies a relationship between the actual speed RPM and the upper limit speed-rate-of-change ΔRPML, which is an upper limit of the speed-rate-of-change ΔRPM. The upper limit speed-rate-of-change calculation unit 145 uses the characteristic map 145m to obtain the upper limit speed-rate-of-change ΔRPML, which corresponds to the speed RPM measured by the tachometer 102.The first change-value calculation unit 146 of the speed-rate-of-change setting unit 140 has a characteristic map 146m that shows a relationship between the distance amount CL and a first change value ΔRPMc1 for changing the base speed-rate-of-change ΔRPMb. The first change-value calculation unit 146 uses the characteristic map 146m to obtain the first change value ΔRPMc1, which corresponds to the distance amount CL output by the distance signal processing unit 111. The relationship shown by the characteristic map 146m is essentially one in which the first change value ΔRPMc1 increases with increasing distance amount CL. Therefore, the first change value ΔRPMc1 obtained by the first change-value calculation unit 146 increases as the distance amount CL increases.Furthermore, in the characteristic map 146m, if the distance CL is greater than the permissible minimum distance CLmin, the first change value ΔRPMc1 displays a positive value. If the distance CL is equal to or less than the permissible minimum distance CLmin, the first change value ΔRPMc1 displays a negative value. The second change value calculation unit 147 of the speed-rate-of-change adjustment unit 140 has a permissible minimum value storage unit 148 and a ΔPI calculation unit 149. The storage unit 148 for permissible minimum values ​​stores the permissible minimum distance CLmin.The ΔPI calculation unit 149 receives a deviation between the permissible minimum distance CLmin and the distance CL output by the distance signal processing unit 111 and receives a second change value ΔRPMc2, which is a proportional and integral controlled variable (PI controlled variable) corresponding to the deviation. Therefore, the second change value ΔRPMc2, obtained by the second change value calculation unit 147, increases when the deviation between the permissible minimum distance CLmin and the distance CL increases.

[0075] The change unit 150 of the speed-rate-of-change setting unit 140 has a first adder 151, a second adder 152, and a minimum value selector 153. The first adder 151 adds the first change value ΔRPMc1 received from the first change value calculation unit 146 and the second change value ΔRPMc2 received from the second change value calculation unit 147. The second adder 152 adds the upper limit speed-rate-of-change ΔRPML, which is obtained by the upper limit speed-rate-of-change calculation unit 145 and the power output of the first adder 151. That is, the second adder 152 outputs a value obtained by adding the first change value ΔRPMc1, the second change value ΔRPMc2, and the upper limit speed-rate-of-change ΔRPML.The minimum value selector 153 selects a smaller value from the base speed change rate ΔRPMb, which is obtained by the base speed change rate calculation unit 141 and the power value of the second adder 152, and outputs the smaller value as the speed change rate ΔRPM. The speed change rate ΔRPM output by the minimum value selector 153 is input into the speed change rate conversion unit 164 of the fuel delivery unit 160 described above.

[0076] The control device body 110 is a computer, as shown in Fig. Figure 8 shows that the control device body 110 includes a CPU 191 that performs various calculations, a memory 192 that serves as the working area of ​​the CPU 191, an auxiliary storage device 193, such as a hard disk drive device, a manual input device 195a, such as a keyboard and a mouse, a display device 195b, an input and output interface 195 for the manual input device 195a and the display device 195b, a device input interface 196 into which signals from various sensors installed in the gas turbine 1 are input, a device power interface 197 for delivering the operating quantity to various operating terminals of the gas turbine 1, a communication interface 198 for communicating with external devices via a network N, and a storage / playback device 194 for performing data storage and playback operations on a disk-type storage medium D.

[0077] The auxiliary storage device 193 stores gas turbine eigenvalue data 193a, a control program 193b, and an operating system (OS) program 193c in advance. Examples of the gas turbine eigenvalue data 193a include various characteristic maps 125m, 126m, 145m, and 146m, which were described above, and the permissible minimum clearance CLmin. The control program 193b is a program for controlling the gas turbine 1, which serves as the rotating machine. Various data and programs stored in the auxiliary storage device 193 are, for example, loaded into the auxiliary storage device 193 from the disk-type storage medium D via the storage / playback device 194. Various data and programs can be loaded into the auxiliary storage device 193 from an external device via the communication interface 198.Various data and programs can be integrated into the built-in auxiliary storage device 193 from the manual input device 195a via the input and output interface 195.

[0078] The CPU 191 develops the control program 193b, which is stored in the auxiliary storage device 193 in the memory 192, and executes the control program 193b, thereby realizing each functional configuration of the control device body 110.

[0079] Next, the operation of the gas turbine power plant according to the present embodiment will be described.

[0080] First, a basic operating procedure of the gas turbine 1 is described. The compressor 10 of the gas turbine 1 compresses air A to produce compressed air. The compressed air is supplied to the combustion chamber 30. The fuel F is also supplied to the combustion chamber 30. The fuel injector 32 of the combustion chamber 30 injects the fuel F and the compressed air into the combustion cylinder 31. Inside the combustion cylinder 31, the fuel F is combusted in the compressed air, producing the high-temperature and high-pressure combustion gas G. The combustion gas G is fed from the combustion cylinder 31 into the combustion gas flow path 49 within the turbine 40, thereby rotating the turbine rotor 41. The generator 9, connected to the turbine rotor 41, generates energy by rotating the turbine rotor 41.

[0081] Next, the operation of the control device 100 will be described.

[0082] First, the operation of the control device 100 is described in one actuation step. The actuation step is the step taken until the generator 9 is connected to a power grid, after the speed of the gas turbine 1 has reached a rated speed (for example, 3,600 rpm) in a state in which the fuel F is not being supplied to the gas turbine 1.

[0083] In the actuation step, the gas turbine rotor 2 is rotated by the generator 9 acting as a motor. In a case where a separate actuator is provided, the gas turbine rotor 2 is rotated by the actuator.

[0084] In the activation step, a flowchart is used. Fig. Step 9, as shown, is executed repeatedly. First, the tachometer 102 measures the rotational speed RPM of the gas turbine 1 (S11: parameter measurement step). In addition, the multiple distance sensors 101 measure the distance CL (S12: distance measurement step). The speed rate adjustment unit 140 of the control device body 110 receives the rotational speed RPM from the tachometer 102 (S21: parameter reception step). Furthermore, the distance signal processing unit 111 of the control device body 110 receives signals from the multiple distance sensors 101 and outputs the smallest distance CL from the distances CL measured by the multiple distance sensors 101 (S22: distance reception step).

[0085] The speed-rate-of-change setting unit 140 then determines the speed-rate-of-change ΔRPM of gas turbine 1 (S30: parameter-rate-of-change setting step). In the parameter-rate-of-change setting step (S30), a base rate-of-change calculation step (S31), an upper limit rate-of-change calculation step (S32), a first change value calculation step (S33), a second change value calculation step (S34), and a change step (S35) are performed.

[0086] In the basic rate of change calculation step (S31), the target speed calculation unit 142 first receives the target speed RPMt in accordance with the actuation command. The ΔPI calculation unit 143 of the basic speed rate of change calculation unit 141 receives a deviation between the speed RPM measured by the tachometer 102 and the target speed RPMt and receives a basic speed rate of change RPMb, which is a proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.

[0087] In the upper limit rate of change calculation step (S32), the upper limit speed rate of change calculation unit 145 uses the value with reference to Fig. 7 described map 145m to obtain the upper limit speed change rate ΔRPML which corresponds to the speed measured with the tachometer 102.

[0088] In the first change value calculation step (S33), the first change value calculation unit 146 of the speed change rate setting unit 140 uses the value with reference to Fig. The characteristic curve 146m described in section 7 is used to obtain the first change value ΔRPMc1, which corresponds to the distance value CL output by the distance signal processing unit 111. As described above, the first change value ΔRPMc1 increases as the distance value CL increases.

[0089] The second change value calculation step (S34) is performed by the second change value calculation unit 147 of the speed-rate-of-change setting unit 140. The PI calculation unit 149 of the second change value calculation unit 147 receives a deviation between the permissible minimum distance CLmin stored in the permissible minimum value storage unit 148 and the distance CL output by the distance signal processing unit 111, and receives the second change value ΔRPMc2, which is a proportional and integral controlled variable (PI controlled variable) corresponding to the deviation. As described above, the second change value ΔRPMc2 increases with increasing deviation between the permissible minimum distance CLmin and the distance CL.

[0090] In the modification step (S35), the modification unit 150 of the speed rate adjustment unit 140 modifies the base speed rate of change RPMb. The first adder 151 of the modification unit 150 adds the first modification value ΔRPMc1 and the second modification value ΔRPMc2. The second adder 152 of the modification unit 150 adds the upper limit speed rate of change ΔRPML, which is obtained by the upper limit speed rate of change calculation unit 145 and the power output of the first adder 151. The minimum value selector 153 of the change unit 150 selects a smaller value from the base speed change rate ΔRPMb and the power value of the second adder 152 and outputs the smaller value as the speed change rate ΔRPM to the speed change rate conversion unit 164 of the fuel operating quantity delivery unit 160.

[0091] According to the procedure described above, the parameter change rate setting step is complete (S30).

[0092] The fuel delivery unit 160 then supplies the operating quantity to the fuel control valve 36 (S36: operating quantity power step). The speed-rate conversion unit 164 of the fuel delivery unit 160 converts the speed-rate of change RPM set by the speed-rate of change setting unit 140 into the operating quantity of the fuel control valve 36. The operating quantity is supplied to the fuel control valve 36 via the selection unit 169. As a result, the fuel F is supplied to the combustion chamber 30 at a fuel flow rate that can maintain the speed-rate of change RPM set in the parameter change rate setting step (S30).

[0093] As described above, the rotational speed (RPM) of the gas turbine rotor 2 gradually increases as a result of the repeated execution of the step described above. When the rotational speed (RPM) of the gas turbine 1 reaches a rated speed (e.g., 3,600 rpm) and the generator 9 is connected to a power grid, the actuation step is complete.

[0094] Once the actuation step is complete, a charging step is performed. Within the charging step itself, a step similar to the actuation step is repeated.

[0095] The charging process step includes a step that is represented by a flowchart in Fig. The process shown in Figure 9 is repeated. First, the power output meter 103 measures the power output PW of the gas turbine 1 (S11a: parameter measurement step). In addition, the multiple distance measuring devices 101 measure the distance CL (S12a: distance measurement step).

[0096] The power output rate adjustment unit 120 of the control device body 110 receives the power output PW from the power output meter 103 (S21a: parameter reception step). Furthermore, the distance signal processing unit 111 of the control device body 110 receives signals from the multiple distance measuring devices 101 and outputs the smallest distance value CL from the distance values ​​CL measured by the multiple distance measuring devices 101 (S22a: distance reception step).

[0097] Next, the power output rate of change setting unit 120 determines the power output rate of change ΔPW of gas turbine 1 (S30a: parameter rate of change setting step). In the parameter rate of change setting step (S30a), a base rate of change calculation step (S31a), an upper limit rate of change calculation step (S32a), a first change value calculation step (S33a), a second change value calculation step (S34a), and a change step (S35a) are performed.

[0098] In the basic rate of change calculation step (S31a), the target power calculation unit 122 first receives the target power PWt in accordance with the charging command. The ΔPI calculation unit 123 of the basic power output rate of change calculation unit 121 receives a deviation between the power output PW measured by the power output meter 103 and the target power PWt and receives the basic power output rate of change ΔPWb, which is the proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.

[0099] In the upper limit rate of change calculation step (S32a), the upper limit power output rate of change calculation unit 125 uses the value with reference to Fig. 6 described characteristic map 125m to obtain the upper limit power output change rate ΔPWL which corresponds to the power output PW measured by the power output meter 103.

[0100] In the first change value calculation step (S33a), the first change value calculation unit 126 of the power output change rate setting unit 120 uses the value with reference to Fig. The characteristic curve 126m described in section 6 is used to obtain the first change value ΔPWc1, which corresponds to the distance value CL output by the distance signal processing unit 111. As described above, the first change value ΔPWc1 increases when the distance value CL increases.

[0101] The second change value calculation step (S34a) is performed by the second change value calculation unit 127 of the power output rate of change setting unit 120. The ΔPI calculation unit 129 of the second change value calculation unit 127 receives a deviation between the permissible minimum distance CLmin stored in the permissible minimum value storage unit 128 and the distance CLmin output by the distance signal processing unit 111, and receives the second change value ΔPWc2, which is the proportional and integral controlled variable (PI controlled variable) corresponding to the deviation. As described above, the second change value ΔPWc2 increases with increasing deviation between the permissible minimum distance CLmin and the distance CL.

[0102] In the modification step (S35a), the modification unit 130 of the power output rate change setting unit 120 modifies the basic power output rate change ΔPWb. The first adder 131 of the modification unit 130 adds the first change value ΔPWc1 and the second change value ΔPWc2. The second adder 132 of the modification unit 130 adds the upper limit power output rate change ΔPWL, which is obtained by the upper limit power output rate change calculation unit 125 and the power output of the first adder 131. The minimum value selector 133 of the change unit 130 selects the smaller value from the basic power output change rate ΔPWb and the power value of the second adder 132 and outputs the smaller value as power output change rate ΔPW to the power output change rate conversion unit 162 of the fuel operating quantity delivery unit 160.

[0103] According to the procedure described above, the parameter change rate setting step (S30a) is complete.

[0104] The fuel delivery unit 160 then supplies the operating quantity to the fuel control valve 36 (S36a: operating quantity power step). The power output rate conversion unit 162 of the fuel delivery unit 160 converts the power output rate change ΔPW set by the power output rate change setting unit 120 into the operating quantity of the fuel control valve 36. The operating quantity is supplied to the fuel control valve 36 via the selection unit 169. This supplies the fuel F to the combustion chamber 30 at the fuel flow rate that can be maintained by the power output rate change ΔPW set in the parameter change rate setting step (S30a).

[0105] When the control unit 110 receives a new charging command, the step described above is repeated until the power output PW measured by the power output meter 103 reaches a required power output indicated by the new charging command. When the control unit 110 receives the charging command indicating the required power output "0", the power output PW gradually decreases. When the power output PW reaches the specified power output PW, the generator 9 is electrically disconnected from the power grid. The fuel flow rate to the combustion chamber 30 then becomes "0".

[0106] As described above, in the charging process step, if the charging command indicating the required power output is greater than the current power output PW, the power output PW gradually increases until it reaches the required power output. Conversely, if the charging command indicating the required power output is less than the current power output PW, the power output PW gradually decreases until it reaches the desired power output.

[0107] Next, with reference to Fig. 10 describes a change in rotational speed RPM, power output PW and distance amount CL when the parameter change rate is not controlled based on the distance amount CL described above.

[0108] When the control device 100 receives the actuation command at time t0, the rotational speed RPM gradually increases from time t0.

[0109] At the start of the actuation step, there is an extremely large deviation between the actual rotational speed RPM and the target rotational speed RPMt of gas turbine 1. Consequently, the base speed change rate RPMb, obtained by the base speed change rate calculation unit 141, has an extremely high value. Therefore, at the start of the actuation step, the power value of the second adder 152 in the base speed change rate ΔRPMb and the power value of the second adder 152 are lower. Therefore, the minimum value selector 153 of the change unit 150 selects the power value from the second adder 152 and outputs the power value as the rotational speed change rate ΔRPM to the rotational speed change rate conversion unit 164 of the fuel delivery unit 160.

[0110] Furthermore, at the end of the actuation step, the deviation between the actual rotational speed RPM and the target rotational speed RPMt of gas turbine 1 is smaller. Accordingly, the base speed change rate ΔRPMb, obtained by the base speed change rate calculation unit 141, is smaller than an initial value in the actuation step. Therefore, at the end of the actuation step, the difference between the base speed change rate ΔRPMb and the power value of the second adder 152 is smaller than the initial value in the actuation step. Therefore, the minimum value selector 153 of the change unit 150 can select the power value from the second adder 152 and, in some cases, can output the power value as the rotational speed change rate ΔRPM. Alternatively, the minimum value selector 153 of the change unit 150 can select the base speed change rate ΔRPMb and in some cases output the base speed change rate ΔRPMb as the speed change rate ΔRPM.

[0111] For the sake of simplicity, the following description assumes that the power value of the second adder 152 is smaller than the base speed change rate ΔRPMb in the actuation step. In this case, the minimum value selector 153 of the change unit 150 selects the power value from the second adder 152 and outputs the power value as a speed change rate ΔRPM to the speed change rate conversion unit 164 of the fuel delivery unit 160.

[0112] If the rate of change is not controlled, the speed rate of change setting unit 140 of the change unit 150 does not add the first change value ΔRPMc1 and the second change value ΔRPMc2, which are related to the speed rate of change ΔRPM, to the upper limit speed rate of change ΔRPML. Therefore, the minimum value selector switch 153 of the change unit 150 selects the upper limit speed rate of change ΔRPML as the power output of the second adder 152 and outputs the upper limit speed rate of change ΔRPML as the speed rate of change ΔRPM to the speed rate of change conversion unit 164 of the fuel delivery unit 160. The upper limit speed rate of change RPML is nearly constant. Therefore, the rotational speed RPM increases linearly from the time the actuation command is received (t0) until the rotational speed RPM reaches the rated speed.

[0113] If the rotational speed RPM reaches the rated speed at time t2, the rotational speed RPM is maintained at the rated speed after time t2. At time t3 after time t2, the generator 9 is electrically connected to the power grid. Consequently, the generator produces the power output PW from time t3 onwards. Thereafter, the power output PW increases or decreases according to the required power output specified by the charging command.

[0114] During the charging process, the deviation between the actual power output PW of gas turbine 1 and the required power output indicated by the charging command is large at the beginning of the charging command reception. Accordingly, the base power output rate of change ΔPWb, obtained by the base power output rate of change calculation unit 121, has a large value. Therefore, at the beginning of the charging command reception, the power value of the second adder 132 is lower in terms of both the base power output rate of change ΔPWb and the power value of the second adder 132. Consequently, the minimum value selector 133 of the change unit 130 selects the power value from the second adder 132 and outputs the power value as the speed rate of change ΔRPM to the speed rate of change conversion unit 162 of the fuel delivery unit 160.

[0115] Furthermore, after a predetermined time has elapsed following receipt of the charging command, the deviation between the actual power output PW of gas turbine 1 and the required power output indicated by the charging command decreases. Accordingly, the baseline power output rate of change ΔPWb, obtained by the baseline power output rate of change calculation unit 121, has a smaller value than the initial value when the charging command is received. Therefore, when the predetermined time has elapsed after the charging command was received, the difference between the baseline power output rate of change ΔPW and the power value from the second adder 132 is smaller than the initial value when the charging command is received. Consequently, the minimum value selector 133 of the change unit 130 can select the power value from the second adder 132 and, in some cases, output the power value as the power output rate of change ΔPW.Alternatively, the minimum value selector 133 of the change unit 130 can select the basic power output rate of change ΔPWb and in some cases output the basic power output rate of change ΔPWb as the power output rate of change ΔPW.

[0116] For the sake of simplicity, it is assumed here that the power value from the second adder 132 is less than the base power output rate of change ΔPWb in the charging step. In this case, the minimum value selector 133 of the change unit 130 selects the power value from the second adder 132 and outputs the power value as the power output rate of change ΔPW to the power output rate of change conversion unit 162 of the fuel operating quantity unit 160.

[0117] If the rate of change is not controlled, the change unit 130 of the power output rate of change setting unit 120 does not add the first change value ΔPWc1 and the second change value ΔPWc2, which relate to the power output rate of change ΔPW, to the upper limit power output rate of change ΔPWL. Therefore, the minimum value selector 133 of the change unit 130 selects the upper limit power output rate of change ΔPWL as the power output of the second adder 132 and outputs the upper limit power output rate of change ΔPWL as the power output rate of change ΔPWL to the power output rate of change conversion unit 162 of the fuel operating quantity unit 160. The upper limit power output rate of change PWL is nearly constant. Therefore, the power output PW increases or decreases linearly from the time the charging command is received until the power output PW reaches the required power output specified by the charging command.

[0118] When the gas turbine rotor 2 begins to rotate (t0), a centrifugal force acts on the rotor blade 44, and the rotor blade 44 extends towards the radial outer side Dro. Therefore, when the gas turbine 1 begins to rotate (t0), the distance CL decreases.

[0119] The turbine casing 48 has a greater heat capacity than the rotor blade 44. Therefore, the thermal expansion per unit time of the turbine casing 48 is smaller than the thermal expansion per unit time of the rotor blade 44. Fuel is then supplied to the gas turbine 1, and the high-temperature combustion gas flows into the combustion gas flow path 49 of the turbine 40. Even if the turbine casing 48 and the rotor blade 44 are heated similarly by the combustion gas, the distance CL decreases. While the distance CL decreases to some extent, it also gradually increases. During this process, the distance CL is minimized. A point of minimized distance CL is called the clamping point.

[0120] From a point at which the power output PW begins to increase (t3), the amount of fuel supplied to the gas turbine 1 increases. The temperature of the combustion gas flowing in the combustion gas flow path 49 increases, and the combustion gas flow rate also increases. Therefore, when the power output PW begins to increase (t3), the distance CL decreases again. After the power output PW reaches the required power output (t5), if the power output PW remains unchanged, the difference in thermal expansion between the turbine casing 48 and the rotor blade 44 decreases. Accordingly, the distance CL gradually increases. During this process, the distance CL is minimized. A point of minimized distance CL is called the clamping point.If the power output remains constant for a predetermined time or longer, the distance CL is maintained at a constant value.

[0121] When the amount of fuel supplied to the gas turbine 1 decreases, the rotor blade 44 shrinks in a shorter time than the turbine casing 48. Accordingly, the distance CL temporarily increases.

[0122] This means that in a case where the required power output indicated by the charging command is less than the current power output PW, the distance CL temporarily increases.

[0123] Next, with reference to Fig. 11 describes a change in the speed RPM and the distance CL when the rate of change is controlled based on the distance CL described above. For the sake of simplicity, the following description assumes that the power value from the second adder 152 of the speed-rate-of-change setting unit 140 is less than the base speed-rate-of-change ΔRPMb. In this case, the minimum value selector 153 of the change unit 150 selects the power value from the second adder 152 and outputs the power value as the speed-rate-of-change ΔRPM to the speed-rate-of-change conversion unit 164 of the fuel delivery unit 160.

[0124] If the rotational speed RPM of the turbine rotor 41 gradually increases from time t0 and reaches the rated speed, the rated speed is maintained. The clearance CL at time t0 is much larger than the clearance CL and the permissible minimum clearance CLmin at the clamping point.

[0125] The first change value ΔRPMc1 and the second change value ΔRPMc2, which relate to the speed change rate ΔRPM, increase with increasing distance CL. Furthermore, if the distance CL is greater than the permissible minimum distance CLmin, the first change value ΔRPMc1 and the second change value ΔRPMc2 are positive values. Therefore, the power output of the second adder 152 at time t0 is a value obtained by adding the positive values ​​of the first change value ΔRPMc1 and the second change value ΔRPMc2 to the upper limit speed change rate ΔRPML. As described above, the power output from the second adder 152 is the speed change rate ΔRPM determined by the speed change rate adjustment unit 140.Therefore, at time t0, the speed change rate ΔRPM, which is determined by the speed change rate setting unit 140, has a larger value than the upper limit speed change rate ΔRPML.

[0126] During the actuation step, the distance CL gradually decreases over time. Therefore, the first change value ΔRPMc1 and the second change value ΔRPMc2, which relate to the speed change rate ΔRPM, also gradually decrease over time during the actuation step. However, if the distance CL is greater than the permissible minimum distance CLmin, the first change value ΔRPMc1 and the second change value ΔRPMc2 are positive values. Accordingly, even after time t0, if the distance CL is greater than the permissible minimum distance CLmin, the speed change rate ΔRPM determined by the speed change rate setting unit 140 is greater than the upper speed change rate limit ΔRPML during the actuation step.

[0127] If the rate of change is not controlled, the speed rate of change ΔRPM determined by the setting unit 140 for the speed rate of change is the upper limit speed rate of change ΔRPML, as described above. Therefore, if the rate of change is controlled until the distance value CL has a small value close to the permissible minimum distance value CLmin from time t0, the speed rate of change ΔRPM is greater than that when the rate of change is not controlled.

[0128] Therefore, according to the present embodiment, if the rate of change is not controlled, the rotational speed RPM is the rated speed at time t1 before time t2, at which the rotational speed RPM is the rated speed. That is, according to the present embodiment, the time from the start of operation of gas turbine 1 (t0) until the rotational speed RPM of gas turbine 1 is the rated speed can be shortened.

[0129] In this way, according to the present embodiment, the time from the start of operation of gas turbine 1 (t0) until the rotational speed RPM of gas turbine 1 reaches its rated speed is reduced. Accordingly, in the operating step, the time until the distance CL reaches the clamping point is also reduced compared to the time during which the rate of change is not controlled.

[0130] The first change value ΔRPMc1, which relates to the speed change rate ΔRPM, has a negative value when the distance CL is close to the permissible minimum distance CLmin, and also when the distance CL is less than the permissible minimum distance CLmin. Furthermore, the second change value ΔRPMc2, also related to the speed change rate ΔRPM, has a negative value when the distance CL is less than the permissible minimum distance CLmin. Therefore, when the distance CL is close to the permissible minimum distance CLmin, and when the distance CL is less than the permissible minimum distance CLmin, the speed change rate ΔRPM determined by the speed change rate setting unit 140 is smaller than the upper limit speed change rate ΔRPML.

[0131] Therefore, according to the present embodiment, the rotational speed change rate ΔRPM is smaller than the rotational speed change rate ΔRPM when the change rate is not controlled, when the distance CL is close to the clamping point. Therefore, according to the present embodiment, it can be prevented that the distance CL at the clamping point is smaller than the change rate when the change rate is not controlled.

[0132] Next, with reference to Fig. 12 describes a change in the power output PW and the distance amount CL when the rate of change is controlled based on the distance amount CL described above. For the sake of simplicity, the following description assumes that the power value of the second adder 132 of the power output rate of change setting unit 120 is less than the power output rate of change ΔPWb. In this case, the minimum value selector 133 of the change unit 130 selects the power value from the second adder 132 and outputs the power value as the power output rate of change ΔPW to the power output rate of change conversion unit 162 of the fuel operating quantity unit 160.

[0133] The power output PW of gas turbine 1 gradually increases from time t3, as described above, and when the power output PW reaches the required level, it is maintained. The distance CL at time t3 is greater than the distance CL at the clamping point.

[0134] The first change value ΔPWc1 and the second change value ΔPWc2, which relate to the power output rate of change ΔPW, increase with increasing distance CL. Furthermore, if the distance CL is greater than the allowable minimum distance CLmin, the first change value ΔPWc1 and the second change value ΔPWc2 are positive values. Therefore, the power output of the second adder 132 at time t3 is a value obtained by adding the positive values ​​of the first change value ΔPWc1 and the second change value ΔPWc2 to the upper limit power output rate of change ΔPWL. As described above, the power output of the second adder 132 is the power output rate of change ΔPW determined by the power output rate of change setting unit 120.Therefore, at time t3, the power output rate of change PW determined by the power output rate of change setting unit 120 has a larger value than the upper limit power output rate of change PWL.

[0135] In the case of an increase in power output PW, the offset CL gradually decreases over time. Therefore, the first change value ΔPWc1 and the second change value ΔPWc2, which relate to the power output rate of change ΔPW, also gradually decrease as time passes during the increase in power output PW. However, in a case where the offset CL is greater than the minimum allowable offset CLmin, the first change value ΔPWc1 and the second change value ΔPWc2 are positive values. Accordingly, when increasing power output PW, in a case where the offset CL is greater than the minimum allowable offset CLmin, the power output rate of change ΔPW determined by the power output rate of change setting unit 120 has a larger value than the upper limit power output rate of change ΔPWL.

[0136] If the rate of change is not controlled, the power output rate of change ΔPW, determined by the power output rate of change setting unit 120, is the upper limit power output rate of change ΔPWL, as described above. Therefore, if the rate of change is controlled, the power output PW at time t4 will reach the required power output before time t5, just as the power output PW from time t3 onwards will reach the required power output. That is, according to the present embodiment, it is possible to shorten the time from time t3 until the power output PW of the gas turbine 1 reaches the required power output.

[0137] In this way, according to the present embodiment, the time from time t3 until the required power output PW of the gas turbine 1 is reduced. Accordingly, in the actuation step, the time until the distance CL is the clamping point is also reduced compared to the time during which the rate of change is not controlled.

[0138] The offset CL has a negative value in a case where the first change value ΔPWc1, relative to the power output rate of change ΔPW, is close to the permissible minimum offset CLmin, and in a case where the offset CL is less than the permissible minimum offset CLmin. The second change value ΔPWc2, relative to the power output rate of change ΔPW, has a negative value in a case where the offset CL is less than the permissible minimum offset CLmin. Therefore, in a case where the offset CL is close to the permissible minimum offset CLmin, and in a case where the offset CL is less than the permissible minimum offset CLmin, the power output rate of change ΔPW determined by the power output rate of change setting unit 120 has a smaller value than the upper limit speed rate of change ΔRPML.

[0139] Therefore, according to the present embodiment, the power output rate of change PW is smaller than the power output rate of change PW when the distance CL is close to the clamping point during the power output increase process if the rate of change is not controlled. Therefore, according to the present embodiment, when increasing the power output PW, it is possible to prevent the distance CL at the clamping point from being smaller than that measured when the rate of change is not controlled.

[0140] As described above, the distance CL temporarily decreases when the power output increases. Conversely, the distance CL temporarily increases when the power output decreases. Therefore, according to the present embodiment, even in the case of receiving a charging command whose required power output is less than the current power output PW—that is, even in the case of receiving a charging command indicating a decrease in power output—when the rate of change is controlled, the power output PW will reach the required power output in a shorter time than if the rate of change is not controlled.

[0141] The modification unit 182 of the intake air operating rate adjustment unit 180 changes the IGV opening degree (operating rate of the inlet guide vane) in accordance with the distance value CL measured by the distance measuring device 101. The intake air operating rate delivery unit 189 delivers the changed IGV opening degree to the driver 23 of the IGV 21. As a result, the IGV opening degree becomes the modified IGV opening degree. If the intake air flow rate increases without changing the fuel flow rate, the temperature of the combustion gas flowing in the combustion gas flow path 49 decreases, and the distance value CL changes. As described above, according to the present embodiment, the IGV opening degree is changed in accordance with the distance value CL. This prevents the distance value CL from becoming extremely small.

[0142] The compressed air vented from the intermediate housing 18b is cooled by the cooler 62 to become the cooling air Am. The cooling air Am is guided via the vent line 61 to the first rotor blade row 44a. Subsequently, the cooling air Am is discharged into the combustion gas flow path 49 through the cooling channel 44c formed in the first rotor blade row 44a. The cooling air Am exchanges heat with the first rotor blade row 44a as it passes through the cooling channel 44c formed in the first rotor blade row 44a, thereby cooling the first rotor blade row 44a. When the cooling air Am is discharged from the first rotor blade row 44a, a portion of the cooling air Am also acts as film cooling air for the rotor blade row 44a. Therefore, according to the present embodiment, thermal damage to the first rotor blade row 44a from the heat of the combustion gas can be prevented.

[0143] Furthermore, as the rotor blade 44 cools, its thermal expansion decreases and the distance CL increases. According to the present embodiment, the modification unit 172 of the cooling quantity setting unit 170 causes the cooling control 64 to change the flow rate of the cooling medium flowing in the cooler 62 in accordance with the distance CL measured by the distance measuring device 101. As a result, the temperature of the cooling air Am is changed, and the cooling quantity of the first rotor blade row 44a cooled by the cooling air Am is changed. Therefore, according to the present embodiment, the cooling quantity of the first rotor blade row 44a is changed in accordance with the distance CL. Accordingly, it is possible to prevent the distance CL from being extremely small.

[0144] As described above, according to the present embodiment, the rate of change of the rotational speed ΔRPM is modified in accordance with the distance value CL. Therefore, the actuation time until the rotational speed RPM reaches the rated speed can be reduced. Furthermore, according to the present embodiment, the rate of change of the power output ΔPW is modified in accordance with the distance value CL. Therefore, the time until the power output PW reaches the required power output can be reduced. In this way, according to the present embodiment, both the time until the rotational speed RPM reaches the rated speed and the time until the power output PW reaches the required power output can be reduced. Moreover, the rate of change of the rotational speed ΔRPM and the rate of change of the power output ΔPW are modified in accordance with the distance value CL. This prevents the distance value CL from being extremely small.

[0145] Furthermore, according to the present embodiment, the opening degree of the IGV21 and the cooling quantity of the compressed air are changed in accordance with the distance CL. From this perspective, this prevents the distance CL from being extremely small.

[0146] Therefore, according to the present embodiment, the power output PW and the rotational speed of the gas turbine 1 can reach a setpoint in a short time, while preventing damage to the gas turbine 1.

[0147] In gas turbine 1, as described above, if the rotational speed or power output PW increases, the distance CL temporarily decreases. If the rotational speed or power output PW decreases, the distance CL temporarily increases. Therefore, the rate of change of the rotational speed or power output PW can only be controlled based on the distance CL if the rotational speed or power output PW increases. If the rotational speed RPM or power output PW decreases, the rate of change of the rotational speed RPM or power output PW can be set to a fixed value. [Second embodiment]

[0148] A second embodiment of a rotating machine equipment according to the present invention is described below with regard to the Fig. Described in sections 13 to 14.

[0149] The rotating machinery equipment according to the present embodiment is a steam turbine power plant, as described in Fig. Figure 13 shows the steam turbine power plant system, which includes a steam turbine 70, a generator 9a that generates energy by driving the steam turbine 70, and a control device 100a.

[0150] The steam turbine 70 has a steam turbine rotor 71 rotating about the axis Ar, a steam turbine casing 78 covering the steam turbine rotor 71, and several stator blade rows 75. The steam turbine rotor 71 has a rotor shaft 72 extending in the axial direction Da about the axis Ar, and several rotor blade rows 73 attached to the rotor shaft 72. The several rotor blade rows 73 are aligned with each other in the axial direction Da. Each rotor blade row 73 is configured to contain several rotor blades 74 aligned with each other in the circumferential direction Dc. A stator blade row 75 is located on each axial upstream side Dau of the several rotor blade rows 73. The respective stator blade rows 75 are arranged in the turbine casing 78.The respective stator blade rows 75 are all configured to contain several stator blades 76 aligned with each other in the circumferential direction Dc. A space between the outer circumferential side of the rotor shaft 72 and the inner circumferential side of the steam turbine casing 78, that is, an annular space in a region where the stator blade row 75 and the rotor blade row 73 are located in the axial direction Da, forms a main steam flow path 79 in which the steam flows. In the following description, of the several rotor blade rows 73, the rotor blade row 73 furthest upstream on the axial side Dau is referred to as a first rotor blade row, and the rotor blade rows 73 towards the axial downstream side Dad are referred to as a second rotor blade row, a third rotor blade row, and so on.

[0151] According to the present embodiment, the steam turbine 70, together with the steam turbine rotor 71 and the steam turbine casing 78, forms a rotary machine of the axial flow type. A rotor of the generator 9a is connected to the steam turbine rotor 71.

[0152] In the steam turbine casing 78, a steam inlet 78i is formed in a section on its own axial upstream side Dau and a steam outlet 78o in a section on its own axial downstream side Dad. A main steam line 91 is connected to the steam inlet 78i. The main steam line 91 has a steam control valve 92 for controlling the flow rate of the steam flowing into the steam turbine casing 78.

[0153] The control device 100a comprises the steam control valve 92, a distance measuring device 101, a tachometer 102, a power output meter 103, and a control device body 110a. The distance measuring device 101 measures the distance CL between the steam turbine casing 78 and the steam turbine rotor 71. The tachometer 102 measures the rotational speed RPM of the steam turbine rotor 71. The power output meter 103 measures the power output PW of the steam turbine 70, that is, the amount of energy generated by the generator 9a. Both the tachometer 102 and the power output meter 103 are examples of parameter counters.

[0154] A gap exists between the rotor blade 74 of the steam turbine rotor 71, which rotates about the axis Ar, and the steam turbine casing 78, which covers the steam turbine rotor 71. The distance measuring device 101 according to the present embodiment measures the distance CL between the first row of rotor blades 74a and the steam turbine casing 78. The control device 100a according to the present embodiment includes the multiple distance measuring devices 101, as in the control device 100a according to the first embodiment. The distance measuring device 101 can measure the distance between the second row of rotor blades 74 and the steam turbine casing 78. Furthermore, the distance measuring device 101 can measure the distance between the first row of rotor blades 74a and the steam turbine casing 78, and the distance between the second row of rotor blades 74 and the steam turbine casing 78.

[0155] As in Fig. As shown in Figure 14, the control device body 110a comprises a distance signal processing unit 111, a power output rate adjustment unit 120a, a speed rate adjustment unit 140a, and a steam output quantity delivery unit 160a. The control device body 110a is also a computer, as in the control device body 110 according to the first embodiment. Each functional configuration of the control device body 110a is implemented by the computer's CPU, which executes a control program stored in the computer.

[0156] The distance signal processing unit 111 processes signals emitted by the multiple distance measuring devices 101 and outputs the minimum distance amount CL from the distance amounts CL measured by the multiple distance measuring devices 101.

[0157] As in the power output rate change setting unit 120 according to the first embodiment, the power output rate change setting unit 120a has a basic power output rate change calculation unit 121a, a change value calculation unit 124a and a change unit 130a.

[0158] The basic power output rate of change calculation unit 121a has essentially the same configuration as the basic power output rate of change calculation unit 121 according to the first embodiment and obtains the basic power output rate of change ΔPWb based on a deviation between the target power PWt determined in accordance with the charging command or the actuation command and the power output PW measured by the power output meter 103.

[0159] The change value calculation unit 124a has essentially the same configuration as the change value calculation unit 124 according to the first embodiment. Therefore, although not shown, the change value calculation unit 124a includes, as in the change value calculation unit 124a, the upper limit power output rate of change calculation unit, the first change value calculation unit, and the second change value calculation unit. The upper limit power output rate of change calculation unit uses the characteristic map that shows the relationship between the actual power output PW and the upper limit power output rate of change ΔPW, which is the upper limit power output rate of change ΔPW, to obtain the upper limit power output rate of change ΔPWL, which corresponds to the power output PW measured by the power output meter 103.The first change-value calculation unit of the change-value calculation unit 124a uses the characteristic map, which specifies the relationship between the distance amount CL and the first change value ΔPWc1, to modify the basic power output rate of change ΔPWb in order to obtain the first change value ΔPWc1, which corresponds to the distance amount CL output by the distance signal processing unit 111. As in the characteristic map 126m belonging to the first change-value calculation unit 126 according to the first embodiment, the relationship indicated by the characteristic map is essentially one in which the first change value ΔPWc1 increases as the distance amount CL increases. Furthermore, in this characteristic map, in a case where the distance CL is greater than the permissible minimum distance amount CLmin, the first change value ΔPWc1 indicates a positive value.In a case where the distance value CL is less than the permissible minimum distance value CLmin, the first change value ΔPWc1 indicates a negative value. Although not shown, as in the second change value calculation unit 127 according to the first embodiment, the second change value calculation unit of the change value calculation unit 124a includes the permissible minimum value storage unit and the calculation unit ΔPI. The permissible minimum value storage unit stores the permissible minimum distance value CLmin. The ΔPI calculation unit receives the deviation between the permissible minimum distance value CLmin and the distance value CL output by the distance signal processing unit 111 and receives the second change value ΔPWc2, which is the proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.Therefore, the second change value ΔPWc2, obtained by the second change value calculation unit, increases when the deviation between the allowable minimum distance amount CLmin and the distance amount CL increases.

[0160] The modification unit 130a has essentially the same configuration as the modification units 130, 150, 172, and 182 according to the first embodiment. Although not shown as in the modification unit 130 according to the first embodiment, the modification unit 130a therefore includes the first adder, the second adder, and the minimum value selector. The first adder is operated similarly to the first adder 131 according to the first embodiment. The second adder is operated similarly to the second adder 132 according to the first embodiment. The minimum value selector is operated similarly to the minimum value selector 133 according to the first embodiment.

[0161] The steam output delivery unit 160a comprises a power output rate conversion unit 162a, a speed rate conversion unit 164a, and a selection unit 169a. The power output rate conversion unit 162a converts the power output rate ΔPW set by the power output rate setting unit 120a into the operating output of the steam control valve 92, which is the operating terminal. The speed rate conversion unit 164a converts the speed rate ΔRPM set by the speed rate setting unit 140a into the operating output of the steam control valve 92, which is the operating terminal. The selection unit 169a outputs only one operating quantity from the operating quantity obtained by the power output rate change conversion unit 162a and the operating quantity obtained by the speed rate change conversion unit 164a to the steam control valve 92.

[0162] As in the speed-rate-of-change setting unit 140 according to the first embodiment, the speed-rate-of-change setting unit 140a has a base speed-rate-of-change calculation unit 141a, a change value calculation unit 144a and a change unit 150a.

[0163] The base speed rate of change calculation unit 141a has essentially the same configuration as the base speed rate of change calculation unit 141 according to the first embodiment and obtains the base speed rate of change ΔRPMb based on the deviation between the target speed RPMt determined in accordance with the actuation command and the speed measured by the tachometer 102.

[0164] The change value calculation unit 144a has essentially the same configuration as the change value calculation unit 144 according to the first embodiment. Therefore, although not shown, the change value calculation unit 144a also includes the upper limit speed change rate calculation unit, the first change value calculation unit, and the second change value calculation unit, as in the change value calculation unit 144 according to the first embodiment. The upper limit speed change rate calculation unit uses the map that specifies the relationship between the actual speed RPM and the upper limit speed change rate RPML, which is the upper limit speed change rate RPM, to obtain the upper limit speed change rate RPML corresponding to the speed RPM measured by the tachometer 102.The first change value calculation unit of the change value calculation unit 144a uses the map showing the relationship between the distance amount CL and the first change value ΔRPMc1 for changing the base speed change rate ΔRPMb to obtain the first change value ΔRPMc1, which corresponds to the distance amount CL output by the distance signal processing unit 111. As in the map 146m belonging to the first change value calculation unit 146 according to the first embodiment, the relationship shown by the map is essentially one in which the first change value ΔRPMc1 increases as the distance amount CL increases. Furthermore, in the map, in a case where the distance amount CL is greater than the permissible minimum distance amount CLmin, the first change value ΔRPMc1 shows a positive value.In a case where the distance value CL is less than the permissible minimum distance value CLmin, the first change value ΔRPMc1 indicates a negative value. Although not shown, as in the second change value calculation unit 147 according to the first embodiment, the second change value calculation unit 144a of the change value calculation unit 144a has the permissible minimum value storage unit and the calculation unit ΔPI. The permissible minimum value storage unit stores the permissible minimum distance value CLmin. The ΔPI calculation unit receives the deviation between the permissible minimum distance value CLmin and the distance value CL output by the distance signal processing unit 111 and receives the second change value ΔRPMc2, which is the proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.Therefore, the second change value ΔRPMc2, obtained by the second change value calculation unit, increases when the deviation between the allowable minimum distance amount CLmin and the distance amount CL increases.

[0165] The modification unit 150a has essentially the same configuration as the modification unit 150 according to the first embodiment. Although not shown as in the modification unit 150 according to the first embodiment, the modification unit 150a therefore includes the first adder, the second adder, and the minimum value selector. The first adder is operated similarly to the first adder 151 according to the first embodiment. The second adder is operated similarly to the second adder 152 according to the first embodiment. The minimum value selector is operated similarly to the minimum value selector 153 according to the first embodiment.

[0166] According to the gas turbine 1 described in the first embodiment, the distance CL temporarily decreases when the rotational speed RPM or the power output PW increases, and temporarily increases when the rotational speed RPM or the power output PW decreases. On the other hand, according to the steam turbine 70, due to the relationship between the heat capacity of the steam turbine casing 78 and the heat capacity of the rotor blade 74, the distance CL temporarily increases when the rotational speed RPM or the power output PW increases, and temporarily decreases when the rotational speed RPM or the power output PW decreases. That is, the tendencies of change in the distance CL with respect to an increase or decrease in the rotational speed RPM or the power output PW are opposite between the gas turbine 1 and the steam turbine 70.

[0167] However, according to the present embodiment, as in the first embodiment, the rate of change of speed ΔRPM and the rate of change of power output ΔPW decrease when the distance CL decreases, and when the distance CL increases, the rate of change of speed ΔRPM and the rate of change of power output ΔPW increase. Therefore, according to the present embodiment, as in the first embodiment, the operating time until the speed RPM reaches the rated speed can be reduced. Furthermore, according to the present embodiment, the time until the power output PW reaches the required power output can be reduced. In addition, it can be prevented that the distance CL is extremely small.

[0168] According to the steam turbine 70, as described above, if the rotational speed RPM or power output PW decreases, the distance CL temporarily decreases. If the rotational speed RPM or power output PW increases, the distance CL temporarily increases. Therefore, the rate of change of the rotational speed RPM or power output PW can only be controlled based on the distance CL if the rotational speed RPM or power output PW decreases. If the rotational speed RPM or power output PW increases, the rate of change of the rotational speed RPM or power output PW can be set to a fixed value. [Third embodiment]

[0169] A third embodiment of a rotating machine equipment according to the present invention is described below with regard to the Fig. described in sections 15 to 16.

[0170] The rotating machine equipment according to the present embodiment is a gas compression system, as described in Fig. Figure 15 shows the gas compression system, which includes a compressor 80, a motor 9b that drives the compressor 80, and a control device 100b.

[0171] The compressor 80 comprises a compressor rotor 81 rotating about the axis Ar, a compressor housing 88 covering the compressor rotor 81, and several stator blade rows 85. The compressor 81 has a rotor shaft 82 extending axially Da around the axis Ar, and several rotor blade rows 83 attached to the rotor shaft 82. The several rotor blade rows 83 are aligned with each other axially Da. Each rotor blade row 83 is configured to include several rotor blades 84 aligned circumferentially Dc. The stator blade row 85 is located on each axial downstream side Dad of the several rotor blade rows 83. The respective stator blade rows 85 are arranged within the compressor housing 88.The respective stator blade rows 85 are all configured to include several stator blades 86 aligned with each other in the circumferential direction Dc. A space between the outer circumferential side of the rotor shaft 82 and the inner circumferential side of the compressor housing 88, that is, an annular space in a region where the stator blade row 85 and the rotor blade row 83 are arranged in the axial direction Da, forms a gas compression flow path 89 in which flowing gas is compressed. That is, the compressor 80 is a multi-stage axial flow compressor. In the following description, of the several rotor blade rows 83, the rotor blade row 83 furthest upstream on the axial side Dau is referred to as a first rotor blade row, and the rotor blade rows 83 towards the axial downstream side Dad are referred to as a second rotor blade row, a third rotor blade row, and so on.The rotor blade row 83 furthest upstream on the axial side Dad is referred to as a last rotor blade row.

[0172] According to the present embodiment, the compressor 80, together with the compressor rotor 81 and the compressor housing 88, forms a rotating machine. A rotor of the motor 9b, which rotates the compressor rotor 81, is connected to the compressor rotor 81. A current circuit 94, which changes the rotational speed (RPM) of the rotor of the motor 9b by changing the supply state of the current supplied to the motor 9b, is connected to the motor 9b.

[0173] In the compressor housing 88, a gas inlet 88i is formed in a section on its own axial upstream side Dau, and a gas outlet 88o is formed in a section on its own axial downstream side. A pressurized gas line 93 is connected to the gas outlet 88o. The pressurized gas line 93 has a flow meter 104 for measuring a flow rate Q of the gas discharged by the compressor 80.

[0174] The control device 100b comprises a current circuit 94, a distance measuring device 101, a tachometer 102, a flow meter 104, and a control device body 110b. The distance measuring device 101 measures the distance CL between the compressor housing 88 and the compressor rotor 81. The tachometer 102 measures the rotational speed RPM of the compressor rotor 81.

[0175] The flow meter 104 measures a discharge flow rate as the power output of the compressor 80. Both the speed meter 102 and the flow meter 104 are examples of the parameter meter.

[0176] A distance exists between the rotor blade 84 of the compressor rotor 81, which rotates about the axis Ar, and the compressor housing 88, which covers the compressor rotor 81. The distance measuring device 101 according to the present embodiment measures the distance CL between a rotor blade 84a of the last row and the compressor housing 88. The control device 100b according to the present embodiment includes the multiple distance measuring devices 101, as in the control devices 100 and 100a according to the first and second embodiments. The distance measuring device 101 can measure the distance CL between the rotor blade 84, which is arranged in a preceding row on the axial upstream side Aru of the last row, and the compressor housing 88.In addition, the distance measuring device 101 can measure the distance CL between the rotor blade 84a of the last row and the compressor housing 88 and the distance CL between the rotor blade 84, which is located in a preceding row on the axial upstream side Aru of the last row, and the compressor housing 88.

[0177] As in Fig. As shown in Figure 16, the control device body 110b comprises a distance signal processing unit 111, a flow rate change rate setting unit 120b, and a flow rate operating quantity delivery unit 160b. The control device body 110b is also a computer, as in the control device body 110 according to the first embodiment. Each functional configuration of the control device body 110b is implemented by the computer's CPU, which executes a control program stored in the computer.

[0178] The distance signal processing unit 111 processes signals emitted by the multiple distance measuring devices 101 and outputs the minimum distance amount CL from the distance amounts CL measured by the multiple distance measuring devices 101.

[0179] The flow rate-rate of change setting unit 120b includes a base flow rate-rate of change calculation unit 121b, a change value calculation unit 124b, and a change unit 130.

[0180] The basic flow rate-rate of change calculation unit 121b has a ΔPI calculation unit 123b. The ΔPI calculation unit 123b receives a basic flow rate-rate of change ΔQb, which is the proportional and integral controlled variable (PI-controlled variable) corresponding to the deviation between a required gas flow rate indicated by an external gas flow rate command and a delivery flow rate Q measured by the flow meter.

[0181] The change value calculation unit 124b has essentially the same configuration as the change value calculation unit 124 according to the first embodiment. Therefore, the change value calculation unit 124b, like the change value calculation unit 124 of the first embodiment, has an upper limit flow rate change rate calculation unit 125b, a first change value calculation unit 126b, and a second change value calculation unit 127b. The upper limit flow rate change rate calculation unit 125b has a characteristic map 125mb that shows a relationship between the actual upper discharge flow rate Q and an upper limit flow rate change rate ΔQL, which is the upper limit value of the flow rate change rate.The upper limit flow rate change rate calculation unit 125b uses the characteristic map 125mb to obtain the upper limit flow rate change rate ΔQL, which corresponds to the delivery flow rate Q measured by the flow meter 104. The first change value calculation unit 126b has a characteristic map 126mb that shows a relationship between the distance value CL and a first change value ΔQc1 for changing a base flow rate change rate ΔQb. The first change value calculation unit 126b uses the characteristic map 126mb to obtain the first change value ΔQc1, which corresponds to the distance value CL delivered by the distance signal processing unit 111. As in the characteristic map 126m, which belongs to the first change value calculation unit 126 according to the first embodiment, the relationship shown by the characteristic map 126mb is essentially a relationship in which the first change value ΔQc1 increases when the distance amount CL increases.Furthermore, in characteristic map 126m, if the distance CL is greater than the permissible minimum distance CLmin, the first change value ΔQc1 displays a positive value. If the distance CL is less than the permissible minimum distance CLmin, the first change value ΔQc1 displays a negative value. The second change value calculation unit 127b has a storage unit 128b for a permissible minimum value and a ΔPI calculation unit 129b. The storage unit 128b for the permissible minimum value stores the permissible minimum distance CLmin. The ΔPI calculation unit 129b receives the deviation between the permissible minimum distance CLmin and the distance CL output by the distance signal processing unit 111 and receives a second change value ΔQc2, which is the proportional and integral controlled variable (PI controlled variable) corresponding to the deviation.Therefore, the second change value ΔQc2, obtained by the second change value calculation units 127 and 147, increases when the deviation between the allowable minimum distance amount CLmin and the distance amount CL increases.

[0182] The modification unit 130 has essentially the same configuration as the modification unit 130 according to the first embodiment. Therefore, the modification unit 130, like the modification unit 130 according to the first embodiment, includes the first adder 131, the second adder 132, and the minimum value selector 133. The first adder 131 is operated similarly to the first adder 131 according to the first embodiment. The second adder 132 is operated similarly to the second adder 132 according to the first embodiment. The minimum value selector 133 is operated similarly to the minimum value selector 133 according to the first embodiment.

[0183] The flow rate operating quantity delivery unit 160b converts the flow rate change rate ΔQ, set by the flow rate change rate adjustment unit 120b, into the operating quantity of the power circuit 94, which is the operating terminal. The flow rate operating quantity delivery unit 160b then delivers the operating quantity to the power circuit 94. As a result, the rotational speed (RPM) of the motor rotor changes. The rotational speed (RPM) of the compressor rotor 81 changes along with the change in the rotational speed (RPM) of the motor rotor, and the delivery flow rate Q reaches the required gas flow rate indicated by the gas flow rate command.

[0184] According to the gas turbine 1 described in the first embodiment, the distance CL temporarily decreases when the rotational speed RPM or the power output PW increases, and temporarily increases when the rotational speed RPM or the power output PW decreases. On the other hand, according to the compressor 80, generally due to the relationship between the heat capacity of the compressor housing 88 and the heat capacity of the rotor blade 84, as in the steam turbine 70, the distance CL temporarily increases when the discharge flow rate Q or the rotational speed RPM increases, and temporarily decreases when the discharge flow rate Q or the rotational speed RPM decreases.This means that the tendencies of change in the distance with respect to an increase or a decrease in the delivery flow rate Q or the rotational speed RPM are opposite to each other between the gas turbine 1 and the compressor 80 and are the same between the steam turbine 70 and the compressor 80.

[0185] However, according to the present embodiment, as in the first embodiment, the rate of change of the flow rate ΔQ decreases when the distance CL decreases, and when the distance CL increases, the rate of change of the flow rate ΔQ increases. Therefore, according to the present embodiment, the time until the actual delivery flow rate Q reaches the required flow rate can be reduced, and it can be prevented that the distance CL becomes extremely small.

[0186] In the description above, the discharge flow rate Q is treated as the power output of compressor 80 and is considered a parameter of compressor 80. Alternatively, the discharge pressure can be treated as the power output of compressor 80 and is considered a parameter of compressor 80. In this case, the base pressure rate of change is obtained, which is the proportional and integral controlled variable (PI control variable) corresponding to the deviation between the required gas pressure indicated by the external gas pressure command and a discharge pressure measured by a pressure gauge. The base pressure rate of change is then modified using the first and second change values ​​based on the upper limit pressure rate of change and the distance CL. Additionally, the rotational speed RPM of compressor 80 can be treated as a parameter of compressor 80.In this case, the base speed rate of change is obtained, which is the proportional and integral controlled variable (PI controlled variable) corresponding to the deviation between the required speed indicated by the external speed command and the speed measured by the tachometer 102. The base speed rate of change is then modified using the first and second change values ​​based on the upper limit speed rate of change and the distance value.

[0187] According to the compressor 80, as described above, if the delivery flow rate Q or the rotational speed RPM decreases, the distance CL temporarily decreases. If the delivery flow rate Q or the rotational speed RPM increases, the distance CL temporarily increases. Therefore, the rate of change of the delivery flow rate Q or the rotational speed RPM can only be controlled based on the distance CL if the delivery flow rate Q or the rotational speed RPM decreases. If the delivery flow rate Q or the rotational speed RPM increases, the rate of change of the delivery flow rate Q or the rotational speed RPM can be set to a fixed value.

[0188] Additionally, as described in the first, second and third embodiments, the rate of change is determined as long as the rotating machine has the rotating rotor and the housing covering the outer circumferential side of the rotor, even if the other rotating machine is used to control the rotational speed or the output flow rate, as the power output can be controlled so that it is changed on the basis of the clearance in the same way as those according to the embodiments described above. [Fourth embodiment]

[0189] A fourth embodiment of a rotating machine apparatus according to the present invention is described below with regard to the Fig. Described in sections 17 to 18.

[0190] The rotating machine equipment according to the present embodiment is a so-called combined power plant, as in Fig. Figure 17 shows the combined power plant including the gas turbine 1, the steam turbine 70, a generator 9c, a heat recovery system 95, a main steam line 91c, a condenser 96, a water supply line 97, a water supply pump 98 and a control device 100c.

[0191] The gas turbine 1 is the gas turbine 1 with the same configuration as the gas turbine 1 according to the first embodiment. Therefore, the gas turbine 1 includes the compressor 10, which compresses the air A, the combustion chamber 30, which generates the combustion gas by burning the fuel F in the air compressed by the compressor 10, and the turbine 40, which is driven using the combustion gas. The fuel line 35, through which the fuel F flows, is connected to the combustion chamber 30. The fuel control valve 36 includes the fuel line 35. The turbine casing 48 includes a gas turbine distance measuring device 101a for measuring a distance CLg between the turbine casing 48 and the rotor blade 44a of the first row.

[0192] The steam turbine 70 is a steam turbine with the same configuration as the steam turbine 70 according to the second embodiment. The steam turbine casing 78 has a steam turbine distance measuring device 101b for measuring a distance CLs between the steam turbine casing 78 and the rotor blade of the first row.

[0193] Generator 9c generates power by driving gas turbine 1 and steam turbine 70. The gas turbine rotor 2, the steam turbine rotor 71, and the rotor of generator 9c are interconnected and rotate integrally about the same axis Ar. Therefore, the combined power plant according to the present embodiment is a single-axis combined power plant.

[0194] The heat recovery system 95 uses the heat from the exhaust gas emitted by the gas turbine 1 to convert the water into steam. The main steam line 91c carries the steam generated by the heat recovery system 95 to the steam turbine 70. The main steam line 91c is equipped with the steam control valve 92 to control the flow rate of the steam flowing into the steam turbine 70. The condenser 96 cools the steam delivered by the steam turbine 70 to return the steam to the water. The water supply line 97 carries the water within the condenser 96 to the heat recovery system 95. The water supply pump 98 delivers the water in the water supply line 97 to the condenser 96.

[0195] The control device 100c comprises the fuel control valve 36, the steam control valve 92, the gas turbine distance measuring device 101a, the steam turbine distance measuring device 101b, a tachometer 102, a power output meter 103, and a control device body 110c. The tachometer 102 measures the rotational speed (RPM) of each gas turbine rotor 2, the steam turbine rotor 71, and the rotor of the generator 9c. The power output meter 103 detects the amount of energy produced by the generator 9c. According to the present embodiment, the rotational speed (RPM) measured by the tachometer 102 is the parameter relating to the gas turbine 1 and is also the parameter relating to the steam turbine 71. The power output PW measured by the power output meter 103 is the parameter that relates to the gas turbine 1 and is also the parameter that relates to the steam turbine 70.

[0196] As in Fig.As shown in Figure 17, the control device body 110c comprises a first distance signal processing unit 111a, a second distance signal processing unit 111b, a distance selection output unit 112, a gas turbine power output rate change adjustment unit 120 and a gas turbine speed rate change adjustment unit 140, a fuel operating quantity output unit 160, a steam turbine power output rate change adjustment unit 120a, a steam turbine speed rate change adjustment unit 140a and a steam operating quantity output unit 160a. The control device body 110c is also a computer, as in the control device body 110 according to the first embodiment.

[0197] Each functional configuration of the control device body 110c is realized by the computer's CPU, which executes a control program stored in the computer.

[0198] The first distance signal processing unit 111a processes signals output by the multiple gas turbine distance measuring devices 101a and outputs a minimum distance value CLg from the distance values ​​CLg measured by the multiple gas turbine distance measuring devices 101a. Hereinafter, the distance value CLg output by the first distance signal processing unit 111a is referred to as the gas turbine distance value CLg. The second distance signal processing unit 111b processes signals output by the multiple steam turbine distance measuring devices 101b and outputs a minimum distance value CLs from the distance values ​​CLs measured by the multiple steam turbine distance measuring devices 101b. The distance value CLs output by the first distance signal processing unit 111a is referred to below as the steam turbine distance value CLs.

[0199] The distance selection output unit 112 outputs the gas turbine distance amount CLg, which is output by the first distance signal processing unit 111a when the power output PW increases, and outputs the steam turbine distance amount CLs, which is output by the second distance signal processing unit 111b when the power output PW decreases.

[0200] The gas turbine power output rate change adjustment unit 120 is the same as the power output rate change adjustment unit 120 according to the first embodiment. Therefore, as in the power output rate change adjustment unit 120 according to the first embodiment, the gas turbine power output rate change adjustment unit 120 according to the present embodiment also includes the basic power output rate change calculation unit 121, the change value calculation unit 124, and the change unit 130. The gas turbine speed rate change adjustment unit 140 is the same as the speed rate change adjustment unit 140 according to the first embodiment.Therefore, as in the speed-rate-of-change control unit 140 according to the first embodiment, the gas turbine speed-rate-of-change control unit 140 according to the present embodiment also includes the base speed-rate-of-change calculation unit 141, the change value calculation unit 144, and the change unit 150. The fuel operating quantity delivery unit 160 is the same as the fuel operating quantity delivery unit 160 according to the first embodiment. Therefore, as in the fuel operating quantity delivery unit 160 according to the first embodiment, the fuel operating quantity delivery unit 160 according to the present embodiment also includes the power output rate-of-change conversion unit 162, the speed-rate-of-change conversion unit 164, and the selection unit 169.

[0201] The steam turbine power output rate change adjustment unit 120a is the same as the power output rate change adjustment unit 120a according to the second embodiment. Therefore, as in the power output rate change adjustment unit 120a according to the second embodiment, the steam turbine power output rate change adjustment unit 120a according to the present embodiment also includes the basic power output rate change calculation unit 121a, the change value calculation unit 124a, and the change unit 130a. The steam turbine speed rate change adjustment unit 140a is the same as the speed rate change adjustment unit 140a according to the second embodiment.Therefore, as in the speed-rate-of-change control unit 140a according to the second embodiment, the steam turbine speed-rate-of-change control unit 140a according to the present embodiment also includes the base speed-rate-of-change calculation unit 141a, the change value calculation unit 144a, and the change unit 150a. The steam output delivery unit 160a is the same as the steam output delivery unit 160a according to the second embodiment. Therefore, as in the steam output delivery unit 160a according to the second embodiment, the steam output delivery unit 160a according to the present embodiment also includes the power output rate-of-change conversion unit 162, the speed-rate-of-change conversion unit 164, and the selection unit 169.

[0202] In the combined power plant, if the rotational speed RPM or power output PW of gas turbine 1 increases, the rotational speed RPM or power output PW of steam turbine 70 increases in response. Furthermore, as described above, according to the gas turbine 1, if the rotational speed RPM or power output PW increases, the gas turbine spacing CLg temporarily decreases. If the rotational speed or power output PW decreases, the gas turbine spacing CLg temporarily increases. As described above, according to the steam turbine 70, if the rotational speed RPM or power output PW increases, the steam spacing CLs temporarily increases. If the rotational speed or power output PW decreases, the steam spacing CLs temporarily decreases.

[0203] Therefore, according to the present embodiment, in a case where the rotational speed RPM and the power output PW (power output PW in the entire combined power plant) of generator 9c increase, the power output rate of change △PW and the rotational speed rate of change ΔRPM of gas turbine 1 are determined based on the gas turbine distance CLg, which temporarily decreases. Furthermore, according to the present embodiment, in a case where the rotational speed RPM and the power output PW of the generator 9c decrease, the power output rate of change ΔPW and the rotational speed rate of change ΔRPM of the gas turbine 1 are determined based on the steam turbine distance CLs, which temporarily decreases, and the power output rate of change ΔPW and the rotational speed rate of change ΔRPM of the steam turbine 70 are determined.

[0204] Therefore, according to the present embodiment, if the steam turbine clearance CLs is large, resulting in a smaller increase in rotational speed RPM or power output PW, the rate of change of rotational speed ΔRPM and the rate of change of power output ΔPW of both gas turbine 1 and steam turbine 70 increase due to the gas turbine clearance CLg and the steam turbine clearance CLs. Conversely, if the gas turbine clearance CLg is large, resulting in a greater decrease in rotational speed RPM or power output PW, the rate of change of rotational speed ΔRPM and the rate of change of power output ΔPW of both gas turbine 1 and steam turbine 70 increase due to the gas turbine clearance CLg and the steam turbine clearance CLs.Furthermore, according to the present embodiment, if the steam turbine distance CLs is small, resulting in a smaller increase in rotational speed RPM or power output PW, the rate of change of rotational speed ΔRPM and the rate of change of power output ΔPW of both gas turbine 1 and steam turbine 70 decrease as a result of the gas turbine distance CLg and the steam turbine distance CLs. Conversely, if the gas turbine distance CLg is small, resulting in a larger decrease in rotational speed RPM or power output PW, the rate of change of rotational speed ΔRPM and the rate of change of power output ΔPW of both gas turbine 1 and steam turbine 70 decrease as a result of the gas turbine distance CLg and the steam turbine distance CLs.

[0205] Therefore, according to the present embodiment, as in the first embodiment, the actuation time can be shortened until the rotational speed RPM reaches the rated speed.

[0206] Furthermore, according to the present embodiment, the time until the power output PW reaches the required power output can be shortened. Moreover, according to the present embodiment, it can be prevented that both the gas turbine clearance CLg and the steam turbine clearance CLs are extremely small.

[0207] In addition to the combined power plant of the single-axis type as in the present embodiment, the combined power plant includes a combined power plant of the multi-axis type. In the combined power plant of the multi-axis type, the gas turbine rotor 2 and the steam turbine rotor 71 are not mechanically connected to each other, and the rotor of the individual generator is connected to both the gas turbine rotor 2 and the steam turbine rotor 71. In the combined power plant of the multi-axis type, as in the combined power plant of the single-axis type described above, when the rotational speed RPM and the power output PW of the gas turbine 1 increase, the rotational speed RPM and the power output PW of the steam turbine 71 increase in response. Therefore, the combined power plant of the multi-axis type can also be controlled similarly to the present embodiment. Industrial applicability

[0208] According to one aspect of the present invention, the rotational speed or power output of a rotating machine can reach a target value in a short time, while preventing damage to the rotating machine. Reference symbol list 1 Gas turbine (rotating machine) 2 gas turbine rotor 5 gas turbine casings 9, 9a, 9c Generator 9b Motor 10.80 Compressor 11, 81 Compressor rotor 12, 82 Rotor shaft 13, 83 Rotor blade row 14.85 Stator blade row 18, 88 Compressor housing 18a Compressor body housing 18b Intermediate housing 19 Air compression flow path 21 IGV (Inlet guide vane) 22 movable shovels 23 drivers 30 combustion chamber 31 combustion cylinders (or rear cylinders) 32 Fuel injector 35 Fuel line 36 Fuel control valve (operating terminal) 40 Turbine 41 Turbine rotor 42 Rotor shaft 42a first step wave section 42c cooling channel 43 rotor blade rows 44 Rotor blade 44a Rotor blade of the first row 44c cooling channel 48 turbine housings 49 Combustion gas flow path 53 Stator blade row 54 Stator blade 60 Cooling device 61 Vent line 62 coolers 63 Medium line 64 Cooling control 70 Steam turbine (rotating machine) 71 Steam turbine rotor 72 Rotor shaft 73 rotor blade row 74 Rotor blade 75 stator blade row 76 Stator blade 78 steam turbine housings 78i steam inlet 78° Steam outlet 79 Main steam flow path 84 Rotor blade 84a Rotor blade of the last row 86 Stator blade 88i Gas Intake 88° Gas outlet 89 Gas compression flow path 91, 91c Main steam line 92 Steam control valve (operating terminal) 93 Compressed gas line 94 Power circuit (operating terminal) 95 Heat recovery system 96 Capacitor 97 Water supply line 98 Water supply pump 100, 100a, 100b, 100c Control device 101 Distance measuring device 101a Gas turbine distance measuring device 101b Steam turbine distance measuring device 102 Tachometer (parameter meter) 103 Power output meter (parameter meter) 104 Flow meters (parameter meters) 110, 110a, 110b, 110c Control device body 111 Distance signal processing unit 111a first distance signal processing unit 111b second distance signal processing unit 112 Distance Selection Dispensing Unit 120 Power output rate of change setting unit 120 Power Output Rate of Change Adjustment Unit (Steam Turbine Power Output Rate of Change Adjustment Unit) (Gas Turbine Power Output Rate of Change Adjustment Unit) 120b Flow Rate-Rate Change Adjustment Unit 121, 121a Basic service delivery rate of change unit of calculation 122 Target power calculation unit 123, 129, 129b, 143, 149 ΔPI calculation unit 124, 124a, 124b, 144, 144a Change value calculation unit 125 Upper limits-power output-rate of change-calculation unit 125b Upper limit flow rate rate of change unit of calculation 126, 126b, 146 first change value calculation unit (first calculation unit) 127, 127b, 147 second change value calculation unit (second calculation unit) 128, 128b, 148 Storage unit for a permissible minimum value 130, 130a, 150, 150a, 172, 182 Unit of change 131, 151 first adder 132, 152 second adder 133, 153 Minimum value selector 140 Speed-rate-change-adjustment unit (gas turbine speed-rate-change-adjustment unit) 140a Speed-rate-change-adjustment unit (steam turbine speed-rate-change-adjustment unit) 141, 141a Basic speed-rate of change calculation unit 142 Target speed calculation unit 145 Upper limit speed-rate of change calculation unit 160 Fuel operating quantity delivery unit 160a Steam operating quantity delivery unit 160b Flow rate-Operating quantities-Delivery unit 162, 162a Power output rate of change conversion unit 164, 164a Speed-rate-change conversion unit 169, 169a Selection unit 170 Cooling operating quantity setting unit 171 Cooling operating volume generation unit 179 Cooling operating quantity delivery unit 180 Supply air operating volume setting unit 181 IGV opening degree generation unit 189 Supply air operating volume delivery unit 191 CPU 192 storage locations 193 Auxiliary storage device 193a Gas turbine eigenvalue data 193b Tax Program 193c operating system program 194 Storage / Playback Device 195 Input and output interface 195a manual input device 195b Display device 196 Device input interface 197 Device output interface 198 Communication interface Ar axis Since axial direction Dau axial upstream side Dad axial downstream side DC circumferential direction Dr. Radial direction Dri radial inside Dro radial outer side

Claims

[1] A control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) including a rotating rotor (2, 71) and a casing (5, 48, 78) for covering an outer peripheral side of the rotor (2, 71), the control device (100, 100a, 100b, 100c) comprising: an operation terminal (36, 92) that changes a parameter that is a speed or an output of the rotating machine (2, 71); a distance measuring device (101) that measures a distance between the rotor (2, 71) and the housing (5, 48, 78); a parameter change rate setting unit (120, 140, 140a) that determines a change rate of the parameter in accordance with the distance amount to change the change rate of the parameter; and an operating quantity output unit (160, 160a) that determines an operating quantity of the operating terminal (36, 92) in accordance with the rate of change of the parameter and outputs the operating quantity to the operating terminal (36, 92), wherein the parameter change rate setting unit (120, 140, 140a) determines the change rate of the parameter such that the change rate of the parameter in a case of obtaining a second distance amount that is larger than a first distance amount is higher than the change rate of the parameter in a case of obtaining the first distance amount. [2] A control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) including a rotating rotor (2, 71) and a casing (5, 48, 78) for covering an outer peripheral side of the rotor (2, 71), the control device (100, 100a, 100b, 100c) comprising: an operation terminal (36, 92) that changes a parameter that is a speed or an output of the rotating machine (2, 71); a distance measuring device (101) that measures a distance between the rotor (2, 71) and the housing (5, 48, 78); a parameter change rate setting unit (120, 140, 140a) that determines a change rate of the parameter in accordance with the distance amount to change the change rate of the parameter; and an operating quantity output unit (160, 160a) that determines an operating quantity of the operating terminal (36, 92) in accordance with the rate of change of the parameter and outputs the operating quantity to the operating terminal (36, 92), wherein the parameter change rate setting unit (120, 140, 140a) comprises: a basic change rate calculation unit (121, 121a, 141, 141a) that obtains a basic change rate of the parameter in accordance with a deviation between a target value of the parameter and a detection value of the parameter, a change value calculation unit (126, 126b, 146, 127, 127b, 147) which receives a change value for changing the basic change rate in accordance with the distance amount, and a rate of change changing unit (130, 130a, 150, 150a, 172, 182) that changes the base rate of change using the change value. [3] Control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) according to claim 2, wherein the change value calculation unit (126, 126b, 146) comprises a first calculation unit (126, 126b, 146) which uses a relationship between the distance amount and a first change value for changing the base change rate to obtain the first change value corresponding to the distance amount, and wherein the change rate changing unit (130, 130a) uses the first change value to change the base change rate. [4] Control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) according to claim 3, wherein the change value calculation unit (127, 127b, 147) has a second calculation unit (127, 127b, 147) which obtains a second change value for changing the basic change rate in accordance with a deviation between the distance amount and a predetermined allowable minimum distance amount, and wherein the change rate changing unit (150, 150a) uses the first change value and the second change value to change the base change rate. [5] A control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) according to claim 3 or 4, wherein the relationship is a relationship in which the first change value increases with increasing distance amount. [6] Rotating machine equipment, comprising: the control device (100, 100a, 100b, 100c) of the rotating machine (1, 70) according to one of claims 1 to 5; and the rotating machine (1, 70). [7] Rotating machine equipment according to claim 6, wherein the rotating machine (1) is a gas turbine (1) including a compressor (10, 80) that generates compressed air by compressing air, a combustion chamber (30) that generates combustion gas by burning a fuel in the compressed air, and a turbine (40) driven using the combustion gas, wherein the compressor (10, 80) comprises a rotating compressor rotor (11, 81) and a compressor housing (18, 88) covering the compressor rotor (11, 81), wherein the turbine (40) comprises a rotating turbine rotor (41) and a turbine casing (48) covering the turbine rotor (41), wherein the compressor rotor (11, 81) and the turbine rotor (41) are mechanically connected to each other to form a gas turbine rotor (2), wherein the operating terminal (36) is a fuel control valve (36) that controls a flow rate of the fuel to be supplied to the combustion chamber (30), wherein the distance measuring device (101) measures a gas turbine distance amount between the turbine rotor (41) and the turbine housing (48), and wherein the parameter change rate setting unit (120, 140, 140a) determines the change rate of the parameter so that the change rate of the parameter is changed in accordance with the gas turbine clearance amount at least when the parameter increases, when the parameter increases, and when the parameter decreases. [8] Rotating machine equipment according to claim 7, wherein the compressor (10, 80) is arranged in the compressor housing (18, 88) and has an inlet guide vane (21) which controls the flow rate of the air flowing into the compressor housing (18, 88), wherein the control device (100, 100a, 100b, 100c) comprises: an intake air operating amount setting unit (180) that determines an operating amount of the inlet guide vane (21) in accordance with the gas turbine clearance amount, and an inlet air operating quantity output unit (189) which outputs the operating quantity of the inlet guide vane (21) to the inlet guide vane (21). [9] Rotating machine equipment according to claim 7 or 8, wherein the gas turbine (1) includes: a vent line (61) which vents the air compressed by the compressor (10, 80) so that the vented air is directed to a rotor blade (44, 74, 84) of the turbine rotor (41), a cooler (62) which cools the air flowing in the vent line (61), and a cooling control (64) which controls a cooling amount of the air cooled by the cooler (62), and wherein the control device (100, 100a, 100b, 100c) comprises: a cooling operation amount setting unit (170) that determines an operation amount of the cooling control (64) in accordance with the gas turbine clearance amount, and a cooling operating quantity output unit (179) that outputs the operating quantity of the cooling controller (64) to the cooling controller (64). [10] Rotating machine equipment according to claim 6, wherein the rotating machine (70) is a steam turbine (70) driven using steam, wherein the steam turbine (70) comprises a rotating steam turbine rotor (71) and a steam turbine casing (78) covering the steam turbine rotor (71), wherein the operating terminal (92) is a steam control valve (92) that controls a flow rate of the steam to be supplied to the steam turbine (70), wherein the distance measuring device (101) measures a steam turbine distance amount between the steam turbine rotor (71) and the steam turbine housing (78), and wherein the parameter change rate setting unit (120, 140, 140a) determines the change rate of the parameter in accordance with the steam turbine clearance amount so that the change rate of the parameter is changed at least when the parameter increases, when the parameter increases, and when the parameter decreases. [11] Rotating machine equipment comprising: a control device (100, 100a, 100b, 100c) of a rotating machine (1, 70) including a rotating rotor (2, 71) and a housing (5, 48, 78) for covering an outer peripheral side of the rotor (2, 71), the control device (100, 100a, 100b, 100c) comprising: an operation terminal (36, 92) that changes a parameter that is a speed or an output of the rotating machine (2, 71); a distance measuring device (101) that measures a distance between the rotor (2, 71) and the housing (5, 48, 78); a parameter change rate setting unit (120, 140, 140a) that determines a change rate of the parameter in accordance with the distance amount to change the change rate of the parameter; and an operating amount output unit (160, 160a) that determines an operating amount of the operating terminal (36, 92) in accordance with the rate of change of the parameter and outputs the operating amount to the operating terminal (36, 92); and the rotating machine (1, 70), wherein a first rotating machine (1) and a second rotating machine (70) are provided as the rotating machine (1, 70), wherein the first rotating machine (1) is a gas turbine (1), wherein the second rotating machine (70) is a steam turbine (70), wherein the rotating machine equipment comprises a heat recovery system (95) which generates steam using exhaust gas from the gas turbine (1) and which supplies the steam to the steam turbine (70), wherein the gas turbine (1) comprises a compressor (10, 80) which generates compressed air by compressing air, a combustion chamber (30) which generates combustion gas by burning a fuel in the compressed air, and a turbine (40) which is driven using the combustion gas, wherein the compressor (10, 80) comprises a rotating compressor rotor (11, 81) and a compressor housing (18, 88) covering the compressor rotor (11, 81), wherein the turbine (40) comprises a rotating turbine rotor (41) and a turbine casing (48) covering the turbine rotor (41), wherein the compressor rotor (11, 81) and the turbine rotor (41) are mechanically connected to each other to form a gas turbine rotor (2), wherein the operating terminal (36) of the gas turbine (1) is a fuel control valve (36) which controls a flow rate of the fuel to be supplied to the combustion chamber (30), wherein the distance measuring device (101) of the gas turbine (1) is a gas turbine distance measuring device (101a) which measures a gas turbine distance amount between the turbine rotor (41) and the turbine housing (48), wherein the steam turbine (70) comprises a rotating steam turbine rotor (71) and a steam turbine casing (78) covering the steam turbine rotor (71), wherein the operating terminal (92) of the steam turbine (70) is a steam control valve (92) which controls a flow rate of the steam to be supplied to the steam turbine (70) from the heat recovery system (95), wherein the distance measuring device (101) of the steam turbine (70) is a steam turbine distance measuring device (101b) which measures a steam turbine distance amount between the steam turbine rotor (71) and the steam turbine casing (78), wherein the parameter change rate setting unit (120, 140) of the gas turbine (1) determines the change rate of a gas turbine parameter, which is the parameter related to the gas turbine (1), such that the change rate of the gas turbine parameter is changed in accordance with the gas turbine spacing amount when the gas turbine parameter increases, and determines the change rate of the gas turbine parameter such that the change rate of the gas turbine parameter is changed in accordance with the steam turbine spacing amount when the gas turbine parameter decreases, wherein the operating quantity output unit (160) of the gas turbine (1) determines an operating quantity of the fuel control valve (36) in accordance with the change rate of the gas turbine parameter determined by the parameter change rate setting unit (120, 140) of the gas turbine (1), and outputs the operating quantity of the fuel control valve (36) to the fuel control valve (36), wherein the parameter change rate setting unit (120, 140a) of the steam turbine (70) determines a change rate of a steam turbine parameter, which is the parameter related to the steam turbine (70), such that the change rate of the steam turbine parameter is changed in accordance with the gas turbine distance amount when the steam turbine parameter increases, and determines the change rate of the steam turbine parameter such that the change rate of the steam turbine parameter is changed in accordance with the steam turbine distance amount when the steam turbine parameter decreases, and wherein the operating amount output unit (160a) of the steam turbine (70) determines an operating amount of the steam control valve (92) in accordance with the change rate of the steam turbine parameter determined by the parameter change rate setting unit (120, 140a) of the steam turbine (70), and outputs the operating amount of the steam control valve (92) to the steam control valve (92). [12] A control method of a rotating machine (1, 70) including a rotating rotor (2, 71) and a casing (5, 48, 78) for covering an outer peripheral side of the rotor (2, 71), the control method comprising: a step of receiving a clearance amount between the rotor (2, 71) and the housing (5, 48, 78); a step of determining a rate of change of a parameter which is a rotational speed or an output of the rotating machine (1, 70) so that the rate of change of the parameter is changed in accordance with the distance amount; and a step of determining an operation amount of an operation terminal (36, 92) for changing the parameter in accordance with the rate of change of the parameter and outputting the operation amount to the operation terminal (36, 92), wherein in the step of determining the rate of change of the parameter, the rate of change of the parameter is determined such that the rate of change of the parameter in a case of obtaining a second distance amount that is greater than a first distance amount is higher than the rate of change of the parameter in a case of obtaining the first distance amount. [13] A control method of a rotating machine (1, 70) including a rotating rotor (2, 71) and a casing (5, 48, 78) for covering an outer peripheral side of the rotor (2, 71), the control method comprising: a step of receiving a clearance amount between the rotor (2, 71) and the housing (5, 48, 78); a step of determining a rate of change of a parameter which is a rotational speed or an output of the rotating machine (2, 71) so that the rate of change of the parameter is changed in accordance with the distance amount; and a step of determining an operation amount of an operation terminal (36, 92) for changing the parameter in accordance with the rate of change of the parameter and outputting the operation amount to the operation terminal (36, 92), wherein the step of determining the rate of change of the parameter a step of obtaining a basic change rate of the parameter in accordance with a deviation between a target value of the parameter and a detection value of the parameter, a step of obtaining a change value for changing the base rate of change, and includes a step of changing the base rate of change using the change value. [14] Control method of a rotating machine (1, 70) according to claim 13, wherein the step of obtaining the change value includes a step of using a relationship between the distance amount and a first change value to change the base change rate to obtain the first change value corresponding to the distance amount, and wherein in the step of changing the base rate of change, the first change value is used to change the base rate of change. [15] Control method of a rotating machine (1, 70) according to claim 14, wherein the step of obtaining the change value includes a step of obtaining a second change value for changing the base change rate in accordance with a deviation between the distance amount and a predetermined allowable minimum distance amount, and wherein in the step of changing the base rate of change, the first change value and the second change value are used to change the base rate of change. [16] A control method of a rotating machine (1, 70) according to claim 14 or 15, wherein the relationship is a relationship in which the first change value increases with increasing distance amount.

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