JP2015098787A - Compressor with air intake spray cooler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor including an air intake spray cooler, capable of making a clearance amount between rotor blades and a casing of the compressor close to a target value without restricting a quantity of sprayed water for air intake spray cooling.SOLUTION: A clearance amount δ between a casing 112 and each rotor blade 105 measured or estimated by a measuring instrument 115 is input to a clearance control device 120. If the input clearance amount δ is greater than a target clearance error εref and difference between the clearance amount δ and a target clearance amount δref is greater than the target clearance amount error εref, the clearance control device 120 calculates casing target temperature Tref and a casing-heat-exchanger target heat transfer quantity Qref so that the clearance amount δ is closer to the target value δref. The clearance control device 120 controls a casing heat exchanger 114 to operate on the basis of the calculated values.

Description

  The present invention relates to a compressor having an intake spray cooler used in a gas turbine or the like.

  The compressor is a device that sucks in gas, compresses it, and discharges it. Among them, turbo compressors are a class of large capacity, and are widely used as combustion air compressors for gas turbines. The turbo compressor is roughly classified into an axial flow compressor and a centrifugal compressor. Here, these turbo compressors are referred to as compressors without distinction.

  Since the compressor is efficient when operated in a state where the gap between the rotor blade attached to the rotating shaft and the casing on the outer periphery of the compressor is small, the design is made with a reduced gap. On the other hand, this gap amount changes from moment to moment during operation due to temperature changes of the compressor components and elongation due to centrifugal force. If the gap amount is excessively reduced, a phenomenon called rubbing where the moving blade and the casing come into contact with each other occurs, and the reliability is impaired.

  Another characteristic of the compressor is a characteristic with respect to the temperature of the gas to be sucked. The gas expands and the density decreases as the temperature increases. For this reason, the efficiency of the compressor decreases as the temperature of the sucked gas increases, and the mass flow rate that can be sucked also decreases. Along with this, the temperature of the compressed gas discharged increases as the temperature of the sucked gas increases.

  The above-described characteristics are particularly significant in the field related to gas turbines. Since the compressors that make up the gas turbines suck in and compress the atmosphere, the difference in the atmospheric temperature depending on the weather, season, and installation area directly affects the performance of the compressor. Since the compressor power reaches about half of the turbine output, this characteristic has a great influence on the gas turbine performance.

  Moreover, the combustion temperature of a gas turbine has an upper limit according to each model from the reliability of an apparatus. The combustion temperature depends on the mass flow rate and temperature of the compressed air discharged from the compressor. When the atmospheric temperature rises, the combustion temperature also rises due to a decrease in the mass flow rate of the sucked air and an increase in the compressor discharge air temperature. Therefore, in order to prevent the upper limit of the combustion temperature from being exceeded, if the atmospheric temperature rises, even if it is during rated operation, the amount of fuel input must be reduced to lower the combustion temperature. Leads to a decrease in output.

  Various techniques for cooling the intake air of the compressor have been proposed as a method for recovering the output decrease in response to the output decrease of the gas turbine. One type is intake spray cooling in which water is sprayed into the intake air and the air temperature is lowered by the latent heat of vaporization of the spray droplets.

  Regarding a technique for effectively performing intake air spray cooling, Patent Document 1 proposes a method of atomizing water sprayed on compressor suction air. The technique described in Patent Document 1 has a configuration in which water injection holes are provided in the guide vane portion of the diffuser, and water is injected at a substantially right angle to the gas flow. With the technique described in Patent Document 1, it is possible to effectively promote atomization of water and lower the suction air temperature even when sprayed with water alone without mixing with high-pressure air.

JP 2003-129997 A

  When the intake spray cooling is performed by the compressor constituting the gas turbine, it is general that the water spray amount is about 1% of the intake air flow rate by the mass flow rate ratio and the entire amount is immediately evaporated.

  When the water spray amount is increased to about 2% or more, the spray droplets flow into the compressor. Air is compressed inside the compressor, and when the temperature rises, the spray droplets evaporate and take latent heat of evaporation from the air. For this reason, when the spray droplets flow into the compressor, not only the output recovery effect by the intake air cooling but also the compression power reduction effect equivalent to the internal cooling can be obtained, and further efficiency improvement of the compressor can be expected.

  However, as the water spray volume of the intake spray cooler increases, some spray droplets adhere to the compressor casing before evaporation. When spray droplets adhere to the casing, the casing is cooled and the temperature decreases. When the amount of thermal expansion of the casing is reduced due to a temperature drop, the amount of gap between the moving blade of the compressor and the casing is reduced, and in some cases, rubbing is caused.

  The method disclosed in Patent Document 1 is a technique related to atomization of water sprayed into the compressor suction air, and there is no particular mention regarding the intake air cooling technique including the control of the gap between the moving blade of the compressor and the casing, thereby avoiding rubbing. There is no description about the technology.

  As one method of preventing rubbing that occurs when the spray droplets of the intake spray cooler adhere to the casing of the compressor, the water spray amount of the intake spray cooler is taken into account by taking into account the measured value or estimated value of the gap amount. There is a method of giving a constraint to. In this method, when the water spray amount of the intake spray cooler is small, spray droplets do not adhere to the casing of the compressor and the gap amount increases. For this reason, it will drive | operate in the state which the gap | interval amount expanded excessively, and the efficiency of a compressor falls. A reduction in compressor efficiency is undesirable because it leads to a reduction in fuel efficiency of the gas turbine itself.

  The main purpose of air-intake spray cooling for the gas turbine compressor is to recover the output drop due to the rise in the temperature of the intake air. Get. Regarding the output of gas turbines, in recent years, renewable energy has been introduced from the viewpoint of environmental considerations. Especially in the field of thermal power generation, cooperation that offsets fluctuations in the amount of power generated by renewable energy power generation with a highly responsive gas turbine. Driving is expected.

  For this reason, it is desirable to operate in a state where the water spray amount of the intake spray cooler, which is an adjustment parameter for the gas turbine output, can be freely changed as much as possible with respect to the atmospheric temperature, which is an external factor.

  An object of the present invention is to provide a compressor having an intake spray cooler that can bring the gap between the rotor blade and casing of the compressor close to a target value without restricting the water spray amount of the intake spray cooling. Is to realize.

  In order to achieve the above object, the present invention is configured as follows.

  The compressor having the intake spray cooler of the present invention includes a moving blade that is driven to rotate by a rotating shaft, a casing that surrounds the moving blade, and an intake spray cooling that sprays and cools the gas sucked into the casing. , A casing heat exchanger for exchanging heat with the casing, a gap between the rotor blade and the casing, a temperature of the casing, a temperature of the compressed gas discharged from the casing, and a rotational speed of the rotating shaft A measuring instrument for measuring at least one of the above and a gap controller.

  The gap control unit calculates a difference between the gap dimension between the moving blade and the casing obtained based on the measurement signal output from the measuring instrument and a predetermined gap dimension target value, and based on the calculated difference. And the operation of the casing heat exchanger is controlled.

  However, the example mentioned above does not limit the means for solving the problems of the present invention.

  A compressor having an intake spray cooler that can bring the gap between the moving blade of the compressor and the casing close to the target value without restricting the water spray amount of the intake spray cooling can be realized.

It is a schematic block diagram of the compressor to which Example 1 of the present invention was applied. 3 is an operation control flowchart of the gap control device according to the first embodiment. It is a schematic diagram regarding the gap | interval amount in the compressor of Example 1, and the thermal elongation of a casing. It is the schematic of the driving | running characteristic of the compressor of Example 1. FIG. It is a schematic block diagram of the compressor to which Example 3 was applied. 6 is a control flowchart of the valve control device according to the third embodiment. FIG. 6 is a schematic configuration diagram of a main part of a compressor according to a fourth embodiment. FIG. 6 is a schematic configuration diagram of a main part of a compressor according to a fifth embodiment. FIG. 10 is a schematic configuration diagram of a main part of a compressor according to a sixth embodiment.

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

Example 1
First, the outline | summary about the compressor of this invention is demonstrated.

  The compressor of the present invention also has a gap control device, and the gap control device inputs the gap amount between the moving blade and the casing obtained from the measurement signal or the estimated gap value and the casing temperature value as a target for the gap amount. The amount of heat exchange of the casing heat exchanger necessary to approximate the value is calculated.

  The gap control device controls the refrigerant flow rate, temperature, and pressure of the casing heat exchanger according to the calculation result of the heat exchange amount. As a result, the casing temperature of the compressor is changed and the amount of thermal expansion of the casing is changed to bring the gap amount closer to a desired value. The target value of the gap amount is about 1 mm although it depends on the type of the compressor.

  In the compressor of the present invention, the gap amount between the moving blade and the casing is expanded until it can maintain a state larger than 0 even when the water spray amount of the intake spray cooler is maximized. In the rated operation that does not perform intake spray cooling, the cooling amount of the casing heat exchanger is increased to suppress the casing thermal expansion amount and bring the gap amount close to the target value.

  On the other hand, when the amount of water spray in the intake spray cooler is increased and adhesion of spray droplets to the casing of the compressor starts, the casing is cooled by the adhesion. The amount of cooling of the casing heat exchanger is reduced so that the amount of gap approaches the target value so that the amount of thermal expansion of the casing is not reduced more than necessary due to excessive cooling.

  In order to calculate the gap amount between the rotor blade and the casing of the compressor, it is effective to use the following expressions (1) and (2), for example.

ΔL = L0 × α × (TL−T0) + mb × (N × c) ² / (Ag × E × Lg) (1)
ΔR = R0 × α × (TR−T0) (2)

  Here, ΔL and ΔR are the amount of elongation of the moving blade and the casing, respectively. L0 and R0 are the blade height and casing radius at room temperature T0. Α represents the linear expansion coefficient of the members constituting the compressor, and TL and TR represent the temperatures of the moving blades and the casing, respectively.

  Mb is the mass of the moving blade, N is the rotational speed of the compressor rotating shaft, Ag is the radial cross-sectional area at the center of gravity of the moving blade, E is the Young's modulus of the moving blade constituent member, Lg is the height of the center of gravity of the moving blade, c is a unit conversion factor from the angular velocity to the rotational speed. In the above two formulas (1) and (2), the first term on the right side represents thermal elongation, and the second term on the right side represents elongation due to centrifugal force.

  When the initial gap amount at room temperature and when the rotating shaft is stopped is set to δ0, the gap amount δ can be expressed as the following equation (3).

  δ = δ0−ΔL + ΔR (3)

  Note that the method described here is merely an example in which the elements are simply simulated, and the gap amount between the moving blade and the casing of the compressor may be obtained by other means depending on the model and shape of the compressor.

  Examples of signals to be measured when estimating the gap amount between the rotor blade and the casing of the compressor include, for example, the compressor rotation speed, the compressor casing inner wall surface temperature, the compressor bleed gas temperature, and the compressor bleed gas pressure. The water spray amount of the intake spray cooler and the spray water temperature of the intake spray cooler. The compressor rotation speed is effective in estimating the amount of elongation due to the centrifugal force of the moving blade. The gas temperature is effective for estimating the amount of thermal elongation of the member.

  The gas pressure and water spray amount can be combined with the temperature and used to estimate the amount of spray droplets adhering to the compressor casing. In the present invention, the estimation calculation is executed from these values, but in addition to this, parameters representing the characteristics of the compressor such as the temperature, pressure and shaft torque of the discharge air of the compressor are measured, and data created in advance by experiments The gap amount may be estimated by interpolation or the calculation result may be corrected by comparing with the map.

  FIG. 1 is a schematic configuration diagram of a compressor to which the present invention is applied. The example shown in FIG. 1 assumes an axial-flow compressor having a multistage structure. The intake spray cooler 107, the casing 112, and the moving blade 105 supported in the casing 112 and driven to rotate by the rotating shaft 104. And. The moving blade 105 is surrounded by a casing. The gap between the moving blade 105 and the casing 112 is expanded until it can maintain a state larger than 0 even when the water spray amount of the intake spray cooler 107 is maximized, and a casing temperature measuring device and a casing heat exchanger 114 are provided. The compressor is characterized by that. The rotating shaft 104 is connected to the turbine 123.

  In FIG. 1, the suction gas 101 passes through the intake duct 102 and is guided to the inside of the compressor 103. The compressor 103 is driven by a rotating shaft 104, and a moving blade 105 is attached to the rotating shaft 104. The suction gas 101 compressed by the compressor 103 is compressed and discharged as a compressed gas 106 every time it passes through the moving blade 105. An intake spray cooler 107 is attached to the intake duct 102, and high-pressure spray water is supplied from a regulating valve 109 through a pipe 108. The water spray amount can be adjusted by the adjusting valve 109. A rotation speed measuring device 110 is attached to the rotation shaft 104, and the rotation speed of the compressor can be measured. A thermometer 111 is attached to the flow path of the compressed gas 106 so that the temperature of the compressed gas 106 can be measured.

  On the other hand, a thermometer 113 is attached to the casing 112 of the compressor 103, and the temperature of the casing 112 can be measured from the outside of the compressor 103. As shown in the figure, it is desirable to set a plurality of thermometers 113 in the axial direction of the compressor, but the number of thermometers is not limited. In addition, a casing heat exchanger 114 is attached to the casing 112 so that the casing 112 can be cooled or heated by heat exchange with the casing 112.

  Further, the compressor 103 is provided with a measuring instrument 115 for measuring information necessary for directly measuring the gap amount or performing an estimation calculation. The measuring instrument 115 may be, for example, a gap sensor that directly measures the gap amount, or a plurality of pieces of information such as the number of rotations of the rotating shaft 104 and the temperature and pressure of the compressed gas 106 necessary for the calculation of the gap amount. A measuring instrument may be used instead.

  The measurement signal 116 of the measuring instrument 115, the measurement signal 117 of the rotation speed measuring instrument 110, the measurement signal 118 of the thermometer 111, and the measurement signal 119 of the thermometer 113 are connected to a gap control device (gap control unit) 120.

  The gap control device 120 calculates the heat exchange amount of the casing heat exchanger 114 for making the gap amount close to the target value from the received signal, and controls the control actuator 122 of the casing heat exchanger 114 to bring the heat exchange amount close to this value. A heat exchange amount command 121 is issued so as to change the flow rate, pressure, and temperature of the refrigerant. The equipment configuration of the casing heat exchanger 114 is not particularly limited. A model that can be used safely in the operating range of the compressor 103 may be selected as appropriate. It is desirable that the model has good responsiveness.

  FIG. 2 is an operation control flowchart of the gap control device 118 according to the first embodiment of the present invention. In FIG. 2A, when the gap control device 118 receives a measurement signal, it performs signal processing as follows. First, measurement signals 116, 117, 118, and 119 are input to the gap control device 120 (step S1). Next, when the measurement signal is input, the gap control device 120 determines whether or not the gap amount between the moving blade 105 of the compressor 103 and the casing 112 is directly measured (step S2). If the measuring instrument 115 is configured to directly measure the gap amount, the gap amount (gap size) δ is determined here, and the process proceeds to step S4.

  The measuring instrument 115 does not directly measure the gap amount, and when the estimation calculation is being performed, the process proceeds to the gap amount δ estimation calculation process (step S3). The processing of the gap amount δ estimation calculation is shown in FIG.

  2B, in the first embodiment, the temperature TG of the compressed gas 106, the rotation speed N of the rotating shaft 104, and the temperature TR of the casing 112 are obtained as signals instead of the temperature of the moving blade 105. The function f1 in step S3a gives an equation for calculating the gap amount δ by estimating and calculating the extension amount of the moving blade 105 and the extension amount of the casing 112. The function f1 uses the above formulas (1), (2), and (3) and uses the temperatures TG and TR and the rotation speed N as inputs, but other inputs may be added.

  When the gap amount δ is determined, the process proceeds from step S3b to step S4 in FIG. 2A to set a gap amount allowable error (gap size allowable error) εref.

  The gap amount allowable error εref may be a fixed value set in advance, or may be a function having a measurement signal of the measuring instrument 115 attached to the compressor 103 as an input. There are two main purposes for determining the gap amount allowable error εref. One is to prevent a hunting state in which the control signal is increased or decreased repeatedly until the gap amount δ exactly matches the target value. Is the purpose of ensuring a margin for heat exchange delay of the casing heat exchanger 114.

  The shorter the control cycle of the gap control device 120 and the higher the responsiveness of the casing heat exchanger 114, the smaller the gap amount allowable error εref can be set. Although it is desirable to set an appropriate value in consideration of the configuration of the device, the effect of the first embodiment can be obtained even if 0 is set.

  When the setting of the gap amount allowable error εref is completed in step S4, the process proceeds to step S5, and the size comparison between the gap amount δ and the gap amount allowable error εref is performed. If the gap amount δ is larger than the gap amount allowable error εref, the process proceeds to step S6, and the gap amount error defined by the absolute value of the difference between the preset gap amount target value (gap dimension target value) δref and the gap amount δ. Calculate ε. Next, in step S8, it is determined whether or not the gap amount error (gap size error) ε is larger than the gap amount allowable error εref. If the gap amount error ε is larger than the gap amount allowable error εref, the gap amount δ is set to the gap amount. In order to approach the quantity target value δref, Tref and Qref calculation processing for calculating the casing target temperature Tref and the casing heat exchanger target heat transfer quantity Qref by calculation is performed in step S9. As shown in step S9a of FIG. 2C, the calculation process of step S9 is a substitute for the gap amount target value δref and the temperature of the moving blade 105 in the calculation process of Tref and Qref in the first embodiment. Then, the casing target temperature Tref is calculated by back-calculating the thermal expansion amount of the casing 112 by the function f2 using the temperature TG of the compressed gas 106 and the rotation speed N of the rotating shaft 104 as inputs.

  Moreover, the casing heat exchanger target heat transfer amount Qref necessary for setting the temperature of the casing 112 to the casing target temperature Tref is calculated from the function f3 using the temperature TR of the casing 112 and the casing target temperature Tref measured by the thermometer 113 as inputs. To do. In step S9b, the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref are output, and the process proceeds to step S12. In step S12, the gap control device 120 controls the casing heat exchanger 114 so that the gap amount becomes the target value δref based on the calculated target temperature Tref and the casing heat exchanger target heat transfer amount Qref.

  In the first embodiment, the temperatures TG, TR, the rotation speed N, and the gap amount target value δref are used to calculate the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref, but other inputs are added. It doesn't matter. The functions f2 and f3 may be arbitrary, and the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref may be determined by interpolation reference of table data obtained through experiments. Further, in the first embodiment, the case where the casing 112 is cooled by the casing heat exchanger 114 is assumed. However, a heating medium may be circulated instead of the age medium, and the gap amount may be brought close to a desired value by heating. The method shown here does not limit these arithmetic processes.

  On the other hand, when the gap amount δ is equal to or smaller than the gap amount allowable error εref in step S5, it means that the gap amount between the moving blade 105 and the casing 112 is close to 0 due to some unexpected situation. For this reason, it progresses to step S7 and the instruction | command is generated so that the casing heat exchanger 114 may be stopped immediately as a protection function, and control which enlarges gap | interval amount (delta) may be implemented. In step S11, the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref, which are preset heat exchange amount commands, are invalidated, and the refrigerant flow in the casing heat exchanger 114 is stopped in step S12. A heat exchange amount command 121 is output from the gap control device 120.

  In step S8, when the gap amount error ε is equal to or smaller than the gap amount allowable error εref, the process proceeds to step S10, and the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref, which are set heat exchange amount commands, are held. Proceed to step S12.

  In the first embodiment, the control flow for calculating the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref for making the gap amount δ close to the gap amount target value δref is configured. However, the control method is limited to this. is not. For example, PID control for increasing / decreasing the refrigerant flow rate of the casing heat exchanger 114 so as to converge the gap amount error ε to 0 may be configured, or various state quantities that well represent the operating characteristics of the compressor 103 may be measured. You may control the heat exchange amount of the casing heat exchanger 114 by comprising the neural network which inputs a measurement signal.

  FIG. 3 is a schematic diagram regarding the gap amount δ of the compressor 103 and the thermal elongation of the casing 112 according to the first embodiment. Each of (a) to (d) in FIG. 3 shows an enlarged gap between the moving blade 105 and the casing 112 during operation of the compressor 103, and (a) in FIG. 3 (b), the water spray amount of the intake spray cooler 107 increases, and when the droplets adhere to the casing 112, FIG. 3 (c) shows the intake spray cooler. When the water spray amount 107 is increased to the maximum, (d) of FIG. 3 is a case where there is no droplet adhesion to the casing 112 and the casing heat exchanger 114 is stopped. FIG. 3D is shown for comparison, but is not executed in the operation of the first embodiment.

  3 (a), 3 (b), and 3 (c), the gap amount δ is operated within the range where the difference from the gap amount target value δref is within the gap amount target error εref (not shown in FIG. 3). Here, ΔRc in FIG. 3 represents the amount of shrinkage due to cooling of the casing heat exchanger 114, and ΔRw represents the amount of shrinkage due to adhesion of droplets to the casing 112 with respect to the thermal expansion of the casing 112. In the operation in FIG. 3 (a), since no droplets adhere to the casing 112, the shrinkage amount ΔRc is increased by increasing the heat exchange amount of the casing heat exchanger 114, and the gap amount δ is set to the gap amount target value. Approach δref.

  On the other hand, in (b) of FIG. 3, the droplet 301 adheres to the casing 112, and the temperature of the casing 112 falls. As a result, the casing 112 contracts by the contraction amount ΔRw. The gap control device 120 shown in FIG. 1 calculates a temperature and a heat transfer amount necessary to bring the gap amount δ closer to the gap amount target value δref from various measurement signals, and sends a heat exchange amount command 121 to the casing heat exchanger 114. give. The heat exchange amount of the casing heat exchanger 114 is lower in the case shown in FIG. 3B than in the case shown in FIG. 3A, and the gap amount is reduced by reducing the shrinkage amount ΔRc. δ is brought close to the gap amount target value δref.

  When the water spray amount of the intake spray cooler 107 is increased to the maximum, it becomes as shown in FIG. The state shown in FIG. 3C is a state where the number of droplets 301 attached to the casing 112 is further increased from the state shown in FIG. Since the amount of shrinkage ΔRw increases as the number of droplets 301 adhering to the casing 112 increases, the amount of shrinkage ΔRc is reduced by reducing the heat exchange amount of the casing heat exchanger 114 in order to compensate for this.

  Finally, the casing heat exchanger 114 stops the heat exchange, and the shrinkage amount ΔRc becomes zero. From the viewpoint of the equipment capacity of the casing heat exchanger 114, it is preferable that ΔRc can be set to 0 at the point where the amount of droplets 301 adhering to the casing 112 becomes maximum during the operation of the compressor 103. That is, the casing 112 liquid in the operating state of FIG. 3 (c) is within the range of the shrinkage amount of the casing 112 necessary to make the error ε between the gap amount δ and the gap amount target value δref within the gap amount target error εref. It is desirable to design to a gap size in which the amount of shrinkage ΔRw due to droplet adhesion is accommodated.

  FIG. 3D is an operation that is not executed in the control flow shown in FIG. 2 of the first embodiment, but is shown for comparison. In a state where there is no droplet 301 adhering to the casing 112, the amount of contraction ΔRc is increased by increasing the heat exchange amount of the casing heat exchanger 114, and the gap amount δ is brought close to the gap amount target value δref. Therefore, when the casing heat exchanger 114 is stopped in this state, the gap amount δ increases as shown in FIG.

  The operation of the compressor 103 according to the first embodiment will be described with reference to FIG. FIG. 4 is a schematic diagram of operating characteristics of the compressor 103 according to the first embodiment. The graph shown in FIG. 4A shows a schematic change in the gap amount δ in the start-up operation when the intake spray cooler 107 is not used. In the graph shown in FIG. 4A, the horizontal axis represents the elapsed time from the start of the operation of the compressor 103, and the vertical axis represents the radial length from the axial center of the rotating shaft 104 of the compressor 103. And the length to the front-end | tip position of the moving blade 105 is shown with a broken line, the length to the casing position in a prior art is shown with a dashed-dotted line, and the length to the position of the casing 112 of Example 1 is shown with the thick continuous line. . The thin solid line is the length to the position of the casing 112 of the first embodiment when cooling is stopped.

  A value obtained by subtracting the length from the length to the position of the casing 112 to the tip position of the moving blade 105 at an arbitrary time becomes the gap amount between the moving blade 105 of the compressor 103 and the casing 112.

  At time t0, operation of the stopped compressor 103 is started. As the time elapses, the rotational speed and power are increased. At time t1, the compressor 103 is operated at rated power, and from time t1, it is assumed that the rated power is maintained. In this graph, it is possible to confirm the change in the gap amount at the start-up from the stop to the rated power.

  Here, although it depends on the model of the compressor, in general, when the casing and the rotating shaft are compared, the heat capacity of the rotating shaft is larger. Further, the elongation due to centrifugal force increases on the rotating shaft side until the rotational speed reaches the rated rotational speed.

  For the above reasons, in a general compressor, the casing position converges faster than the moving blade tip position during startup. This relationship is also shown in FIG.

  When attention is paid to a region a1 in FIG. 4A, the length to the position of the casing 112 of the first embodiment at time t0 is larger than the length to the conventional casing position. However, when the operation is started, the casing 112 in the first embodiment is operated while being cooled by the casing heat exchanger 114 so that the gap amount approaches the gap amount target value δref, so that the gap amount immediately reaches the gap amount target value δref. Converge. The first embodiment of the present invention can be operated with the gap amount close to the gap amount target value δref even during startup, unlike the prior art.

  Further, attention is focused on a region a2 when the rated power is maintained after time t1. Since the time has elapsed while the operation state is kept constant, the temperature changes of the moving blade 105 and the casing 112 converge. As the temperature change converges, changes in the thermal expansion amount of the rotor blade 105 and the casing 112 also converge, and as a result, the gap amount also converges. In the conventional casing position, the gap amount converged with a slightly larger value than the gap amount target value δref due to an assembly error. However, the gap amount of the first embodiment is the gap amount and the gap amount target due to the effect of the casing heat exchanger 114. The difference from the value δref can be made close to the target gap amount error εref or less.

  Further, in the graph shown in FIG. 4A, as described above, the length to the casing position when the compressor of the first embodiment is operated with the thin solid line as a reference value while the casing heat exchanger is stopped is also shown. Posted.

  In this case, the effect of Example 1 is not obtained, but is shown for comparative explanation. The difference between the length to the casing position indicated by the thin solid line and the length to the casing 112 position of the first embodiment indicated by the thick solid line is to be cooled by the casing heat exchanger 114 in order to bring the gap amount close to the gap amount target value δref. This corresponds to the amount of shrinkage ΔRc of the casing 112 reduced in step (b).

  Next, the graph of FIG. 4B will be described. The graph of (b) of FIG. 4 is a start-up operation case when the intake spray cooler 107 is used. From the graph in FIG. 4A, the time change of the water spray amount of the intake spray cooler 107 is indicated by a two-dot chain line except for the casing position when the casing heat exchanger 114 is stopped. At time t0, operation of the stopped compressor 103 is started. As the time elapses, the rotational speed and power are increased. At time t1, the compressor 103 is operated at rated power, and from time t1, it is assumed that the rated power is maintained. Here, the water spray is started from the intake spray cooler 107 at the time t0w in the middle of activation. The amount of water spray is assumed to be 2% or more of the flow rate of the suction gas 101 at which droplets adhere to the casing 112. Furthermore, the compressor 103 is operated at the rated power from time t1 in the graph, and the rated power is maintained from time t1, but the water spray amount of the intake spray cooler 107 is further increased from time t1w.

  The behavior up to time t0w is the same as the graph of FIG. Attention is paid to the region b1 immediately after the time t0w. By starting water spraying from the intake spray cooler 107 at time t0w, the temperature of the suction gas 101 decreases, and the amount of thermal expansion of the moving blade 105 decreases, so the length to the moving blade tip position also decreases. The casing 112 generates a cooling effect due to droplet adhesion in addition to a decrease in the temperature of the suction gas 101.

  The length to the conventional casing position is larger than the length to the rotor blade tip position by the amount of shrinkage due to the cooling effect of droplet adhesion, and there is a region where the gap amount is transiently less than zero. It has occurred. For this reason, conventionally, during startup, it has been necessary to temporarily reduce the amount of water spray to an amount that can ensure the gap amount.

  On the other hand, the length to the casing 112 position of the first embodiment shown by the solid line can be controlled so that excessive shrinkage of the casing 112 does not occur by suppressing the heat transfer amount of the casing heat exchanger 114.

  For this reason, it is possible to operate with the gap amount close to the gap amount target value δref, and there is no need to restrict the water spray amount.

  Next, attention is paid to a region b2 after the water spray amount is further increased at time t1w. The amount of water spray reaches a level at which droplets adhere to the casing 112 at time t0w, and the amount of droplet adhesion further increases. The relationship between the blade tip position and the conventional casing position maintains the gap amount larger than 0, but the gap amount becomes less than 0 again. The reduction of the gap amount by water spray at time t0w was transient because it was being started, and was resolved as the rated power was approached. However, since the operating state is maintained after time t1, the gap amount is steadily increased. Less than 0.

  Therefore, from the viewpoint of preventing rubbing, the water spray amount has reached the upper limit, and an increase in water spray starting from time t1w is not possible.

  On the other hand, in Example 1, as long as it is in the operation range in which the amount of heat elongation is reduced by heat exchange of the casing heat exchanger 114, the amount of gap can be brought close to the target value by controlling the heat transfer amount of the casing heat exchanger 114. Is possible. Therefore, the upper limit of the water spray amount of the intake spray cooler 107 can be increased as compared with the conventional case, and the operational freedom of the compressor 103 can be expanded.

  As described above, according to the first embodiment of the present invention, the measured or estimated gap amount δ between the casing 112 and the moving blade 105 is larger than the target gap error εref, and the measured or estimated gap amount δ and the gap When the difference from the amount δref is larger than the target gap amount εref, the casing target temperature Tref and the casing heat exchanger target heat transfer amount Qref for calculating the gap amount between the casing 112 and the moving blade 105 close to the target value δref are calculated. The operation of the casing heat exchanger 114 is controlled based on the calculated value.

  That is, when the gap amount δ is smaller than the target gap error εref, the operation of the casing heat exchanger 114 is stopped, and when the gap amount δ is larger than the target gap error εref, the gap amount δ is the target value δref plus. If it is a predetermined range with the target gap error εref as the upper limit and the target value δref minus the target gap error εref as the lower limit, the current state is maintained, and when the gap amount δ is outside the predetermined range, it approaches the target value δref. Therefore, the target temperature Tref and the target heat transfer amount Qref are calculated, and the operation of the casing heat exchanger 114 is controlled based on the calculated values.

  Therefore, it is possible to realize a compressor having an intake spray cooler that can bring the gap between the moving blade and casing of the compressor close to a target value without restricting the amount of water spray for intake spray cooling. it can.

(Example 2)
Next, a second embodiment of the present invention will be described.

  Since the basic configuration of the second embodiment is the same as that of FIGS. 1, 2, 3, and 4, description thereof is omitted. In the second embodiment, the gap δ between the moving blade 105 of the compressor 103 and the casing 112 is larger than 0 even if the temperature drop ΔT occurs in the casing 112 due to the droplet 301 adhering to the casing 112 in the configuration of the first embodiment. The initial gap amount (initial gap dimension) δ0 to be in the state is set. A method for determining the initial gap amount δ0 will be described below.

  In the second embodiment, for the sake of explanation, the gas that becomes the suction gas 101 and the compressed gas 106 is considered as air.

  Since the moving blade 105 and the casing 112 are exposed to the air passing through the internal gas flow path of the compressor 103, it can be approximated to be the same as the air temperature TG passing through the temperatures TL and TR of the moving blade 105 and the casing 112. On the other hand, when the water spray amount of the intake spray cooler 107 increases, the casing 112 of the compressor 103 is cooled by the adhering droplets 301 as shown in FIG. For this reason, in the operation in which the droplet 301 adheres to the casing 112, the temperature of the casing 112 can be approximated to be the same as the temperature of the droplet 301 that adheres.

  Here, when the droplet 301 is generated, it is assumed that the air passing through the internal gas flow path of the compressor 103 has reached a saturated vapor amount. According to this assumption, the temperature of the droplet 301 can be given as a wet bulb temperature where the air temperature passing through the internal gas flow path of the compressor 103 is the dry bulb temperature and the relative humidity is 100%. The relationship between dry bulb temperature and wet bulb temperature can be obtained from various wet air diagrams, approximate polynomials via saturated vapor pressure, or derived equations derived from the above wet air diagrams and approximate polynomials via saturated vapor pressure. At least one of them may be used.

  If this relationship is expressed as a function f4, the temperature drop ΔT of the casing 112 can be expressed by the following equations (4), (5), and (6).

Twet = f4 (Tdry) (4)
Tdry = TG (5)
ΔT = Tdry−Twet = Tdry−f4 (Tdry) = TG−f4 (TG) (6)

  Here, Twet is a wet bulb temperature with a relative humidity of 100%, and in Example 2, the temperature of the droplet 301. Tdry is the dry bulb temperature. The function f4 is defined as a dry / wet conversion function.

  In addition, the initial gap amount δ0 when the rotating shaft 104 is stopped at normal temperature can be expressed using, for example, the above-described equations (1), (2), and (3). Furthermore, by applying the operating characteristic map, the thermal equilibrium diagram, the theoretical calculation formula, and the experimental formula of the compressor 103, the rotational speed N of the rotating shaft 104 is set as a function f5 of the temperature TG of the compressed gas (air) 106, and the following formula (7 ).

  N = f5 (TG) (7)

  Since the temperature TL of the moving blade 105 is approximated to the temperature TG of the compressed gas (air) 106 and the temperature TR of the casing 112 is approximated to TG−ΔT, the equations (1), (2), (3), (6), From (7), the difference between the gap amount δ and the initial gap amount δ0 can be expressed by the function f6 of the compressed gas (air) 106 temperature TG as follows:

  δ = δ0−f6 (TG) (8)

  Here, the condition that the gap amount δ is larger than 0 is applied to Expression (8) to obtain Expression (9).

  δ0> f6 (TG) (9)

  By designing the initial gap amount δ0 so that Equation (9) is established for the temperature TG of the compressed gas (air) 106 within the operating range of the compressor 103, the droplets 301 adhering to the casing 112 cause the casing to Even when the temperature drop ΔT occurs in 112, the initial gap amount δ 0 that satisfies the state where the gap amount δ between the moving blade 105 of the compressor 103 and the casing 112 is larger than 0 is satisfied. The function f6 (TG) is an expression obtained by substituting the temperature TL into the temperature TG and the temperature TR as TG−ΔT into the above formulas (1), (2), and (3). It is a function corresponding to ΔL−ΔR. The function f6 is defined as a gap amount change function, and a value obtained by the function f6 is defined as a change gap amount.

  Note that the calculation shown here is merely an example, and if necessary, the calculation formula may be expanded or correction based on actual machine characteristics may be added.

  According to the second embodiment of the present invention, the same effects as those of the first embodiment can be obtained, and the following effects can be obtained.

  That is, since it is possible to design to minimize the initial gap amount when the rotor blade 105 and the casing 112 are stopped, it is easy to change the design from the conventional compressor to the compressor 103 of the second embodiment. it can. Further, if the amount of expansion of the initial gap amount is small, the necessary heat transfer capacity of the casing heat exchanger 114 can be kept low.

  Therefore, the structure of the casing heat exchanger 114 can be made compact compared to the case where the gap is expanded without any index, and the responsiveness can be expected to be improved because the heat exchange amount is reduced. Since the operating temperature range is narrowed, there are fewer restrictions imposed on the refrigerant and heat exchanger models.

(Example 3)
Next, Embodiment 3 of the present invention will be described.

  The configuration of the third embodiment will be described with reference to FIGS. FIG. 5 is a schematic configuration diagram of a compressor according to the third embodiment. A description of the same parts as those in the first embodiment will be omitted. In the third embodiment, in the configuration of the compressor shown in the first embodiment, an antisurge valve 501 is provided in the intermediate stage of the compressor 103, and the temperature of the casing 112 measured by the thermometer 113 is used as the measurement signal 119. The valve control device (valve control unit) 502 receives the valve control device 502, and the valve control device 502 controls opening / closing of the anti-surge valve 501 according to the temperature increase rate of the casing 112.

  Further, although not essential, in the third embodiment, in order to measure the water spray amount of the intake spray cooler 107, the flow meter 503 is measured on the pipe 108 and the pressure of the compressed gas 106 of the compressor 103 is measured. A pressure gauge 504 and a measuring instrument 505 for measuring the flow rate of the suction gas 101 are installed in the intake duct 102, measurement signals 506, 507, 508 of the flow meter 503, the pressure gauge 504, and the measuring instrument 505, and the number of revolutions The measurement signal 117 of the measuring instrument 110 is supplied to the valve control device 502.

  Note that the description here does not limit the measurement signal, and may be added or replaced as appropriate. For example, if the measurement signal 508 of the measuring instrument 505 is a compressor having an inlet variable vane (IGV), it is estimated and calculated from the inlet variable vane opening, the rotational speed of the rotating shaft 104, and the temperature of the suction gas 101. It is also possible. In this case, a device for measuring the inlet variable blade opening required for the estimation calculation and a device for measuring the temperature of the suction gas 101 may be added.

  The anti-surge valve 501 is an ON / OFF valve that can output only a fully open or fully closed control command, and is closed during normal operation. When the anti-surge valve 501 receives the protection signal 509 from the valve control device 502, the anti-surge valve 501 is fully opened, discharges a part of the suction gas 101 from the middle stage of the compressor 103, and reduces the flow rate of the compressor 103. When the protection signal 509 from the valve control device 502 stops, it is fully closed again.

  Next, the operation of the third embodiment will be described with reference to FIGS. FIG. 6 is a control flowchart of the valve control device 502.

  5 and 6, when the valve control device 502 receives the measurement signal, it performs signal processing as follows. First, in step S100 of FIG. 6A, the valve control device 502 inputs a measurement signal. Next, for the casing temperature TR received as the measurement signal, the casing temperature TR (i) of the current i-th signal processing and the casing temperature TR (i-1) of the past (i-1) -th processing. And a change rate dTR corresponding to the rate of temperature rise of the casing 112 is obtained (step S101).

  Next, the upper limit value dTRlim of the change rate dTR is set (step S102). The upper limit value dTRlim may be a predetermined constant or may be a function of a measurement signal representing the characteristics of the compressor 103. In the third embodiment, the correction calculation process is performed on the change rate upper limit dTRlim.

  In the correction calculation of the change rate upper limit dTRlim (step S103), as shown in step S103a of FIG. 6B, the correction amounts X1 and X2 are calculated by the functions f7 and f8, and the correction amount X1 is calculated from the change rate upper limit dTRlim. , X2 is subtracted to correct. The function f7 receives the temperature TG of the compressed gas 106, the pressure PG of the compressed gas 106, the rotation speed N, and the flow rate Gi of the suction gas 101, and outputs a larger value as the surging margin of the compressor 103 at the time of measurement is smaller. To do. Accordingly, the correction amount X1 increases as the compressor 103 is operated closer to the surging region, and the change rate upper limit dTRlim is corrected to be smaller. The function f8 receives the water spray amount Gw of the intake spray cooler 107, and the output increases as the water spray amount Gw increases. Therefore, the correction amount X2 increases as the water spray amount Gw increases, and the change rate upper limit dTRlim is corrected to be small. In step S103b, the change rate upper limit dTRlim is corrected to the change rate upper limit dTRlim, and the process proceeds to step S104. Note that the correction amount calculation method shown in the third embodiment does not limit the correction method.

  In step S104, the change rate dTR is compared with the change rate upper limit dTRlim after the correction calculation. When the change rate dTR is larger than the change rate upper limit dTRlim, the protection signal ON process is performed (step S105), and the valve control device 502 outputs the protection signal to the anti-surge valve 501 (step S107). In step S104, when the change rate dTR is equal to or less than the change rate upper limit dTRlim, a protection signal OFF process is performed (step S106). As a result, the valve control device 502 stops outputting the protection signal to the anti-surge valve 501.

  The effects of the third embodiment of the present invention configured as described above will be described below.

  In the third embodiment, as in the first and second embodiments, the casing 112 is cooled by the casing heat exchanger 114. When a large amount of droplets adheres to the casing 112 and the heat transfer amount of the casing heat exchanger 114 rapidly decreases due to some reason, for example, a failure, the droplets adhering to the casing 112 may start to evaporate. Here, as described above, when the inflow of liquid droplets occurs, the compression power reduction effect equivalent to the internal cooling can be expected. On the other hand, the gas flow rate of the compressor 103 increases from the stage where the droplets have evaporated.

  For this reason, it is not desirable from the viewpoint of reliability with respect to surging that the droplets flowing into the inside evaporate rapidly. In the third embodiment, the droplets adhering to the casing 112 suddenly start to evaporate due to an unexpected situation, and when the operating state of the compressor 103 approaches the surging phenomenon, the anti-surge valve 501 is activated by a protection signal from the valve controller 502. It can be fully opened and surging can be avoided. Therefore, the reliability of the compressor 103 can be improved even in an operation state where the water spray amount of the intake spray cooler 107 is high. In the third embodiment, the anti-surge valve 501 is an ON / OFF valve. However, an adjustment valve may be selected so that the opening degree can be indicated more finely.

  That is, the third embodiment of the present invention can obtain the same effects as those of the first embodiment and the above-described effects.

Example 4
Next, a fourth embodiment of the present invention will be described with reference to FIG.

  A description of the same components as those in the first embodiment will be omitted. As shown in FIG. 7, the difference from the first embodiment is that thermometers 113a, 113b, 113c, and 113d are set at four locations on the casing 112, the temperature of the casing 112 is measured, and the corresponding four locations are separately provided. As a system, casing heat exchangers 114a, 114b, 114c, and 114d are provided.

  In the fourth embodiment, four measurement points and casing heat exchangers are used for explanation, but the number is not limited, and the method of the fourth embodiment is effective if there are two or more systems. Although not shown, the measurement signals 119a, 119b, 119c, and 119d of the thermometers 113a, 113b, 113c, and 113d are transmitted to the gap control devices 120a, 120b, 120c, and 120d, respectively. Arithmetic processing, control commands, and the like executed in the gap control devices 120a, 120b, 120c, and 120d are the same as those in the flowchart shown in FIG. Here, the heat exchange amount commands 121a, 121b, 121c, and 121d from the respective control devices 120a, 120b, 120c, and 120d to the casing heat exchangers 114a, 114b, 114c, and 114d are controlled by the control actuators 122 (each casing heat exchanger 114a, 114b). , 114c, 114d are output to four control actuators (not shown in FIG. 7), and the casing heat exchanger 114 is controlled.

  In the fourth embodiment, the internal calculations of the gap control devices 120a, 120b, 120c, and 120d are performed independently of each other. However, the correction calculation may be performed by transmitting and receiving signals. For example, you may perform the correction | amendment which makes the casing target temperature close | similar between adjacent site | parts.

  In addition, the correspondence between the thermometer and the casing heat exchanger 114 is not necessarily 1: 1. For example, in FIG. 7, when there is no thermometer 113c, the casing heat exchanger 114c may be controlled with the value of the thermometer 113a as an input, assuming that there is no temperature deviation in the circumferential direction of the compressor 103. . Alternatively, if there is no thermometer 113b, a function for calculating the estimated temperature at the part where the thermometer 113b was installed from the temperature measured by the thermometer 113a and the temperature gradient obtained from the past experimental data is substituted. It is also possible to do.

  The effects of Example 4 will be described below.

  According to the fourth embodiment, the temperature distribution is generated in the casing 112, and even when the uniform temperature control causes a portion where the gap amount δ is small and a portion where the gap amount δ is large, the target temperature is set to each part of the casing 112. As a result, the plurality of casing heat exchangers 114a, 114b, 114c, and 114d perform heat exchange separately, whereby the gap amount δ can be made close to the gap amount target value δref over the entire casing 112.

  Further, it is possible to correct the gap amount δ against the distortion of the casing 112 caused by external factors related to operation such as ventilation in the room in which the compressor 103 is installed and temperature distribution due to equipment arrangement.

  That is, the fourth embodiment of the present invention can obtain the same effects as those of the first embodiment and the above-described effects.

  The temperature of the moving blade and the temperature of the casing can be approximated to be the same as the discharge gas temperature of the compressor, and the shaft rotational speed of the compressor can be expressed as a function of the discharge gas temperature of the compressor. Therefore, it is also possible to calculate only the gas temperature of the compressor, calculate the shaft rotational speed of the compressor from the detected gas temperature, and calculate the gap amount δ. In addition, only the temperature of the rotor blade or the casing is detected, and the shaft rotational speed of the compressor is calculated by a function similar to the function of the compressor discharge gas temperature described above, and the gap amount δ is calculated. It is also possible to do. Furthermore, it is also possible to detect only the shaft rotational speed of the compressor, and calculate the gap amount δ by calculating back the gas temperature of the compressor from the detected shaft rotational speed.

  As described above, according to the present invention described with Examples 1 to 4 as an example, the operation of the compressor blades and the casing that change from moment to moment during operation due to temperature changes of the compressor constituent members and elongation due to centrifugal force. It is possible to operate with the gap amount close to the target value. In particular, when a compressor that is stopped is started, the elongation due to temperature change and centrifugal force changes greatly.

  According to the present invention, the amount of heat exchange between the casing heat exchanger and the casing is controlled in accordance with the change in the gap amount between the rotor blades and the casing of the compressor. Therefore, it is possible to operate with the gap amount between the moving blades of the compressor and the casing close to the target value throughout the entire operation including when the compressor is started.

  The present invention controls the compressor blades and casing by controlling the heat transfer amount of the casing heat exchanger even when the water spray amount of the intake spray cooler is increased and the casing is cooled by the adhesion of the spray droplets to the casing. The gap amount can be brought close to the target value.

  For this reason, in the present invention, in a compressor not provided with a casing heat exchanger, even in a situation where the water spray amount of the intake spray cooler must be restricted to prevent rubbing, the heat transfer amount of the casing heat exchanger is reduced. It can respond by controlling.

  As described above, the degree of freedom of operation of the water spray amount of the intake spray cooler is increased. For example, in the case of a compressor for a gas turbine, it is easy to recover the output decrease due to the temperature increase and the target output is easily obtained.

  Further, as described above, the present invention provides a casing heat exchanger as a compensation measure against the case where the water spray amount of the intake spray cooler increases and the casing is cooled due to the spray droplets adhering to the casing.

  Therefore, in this invention, the restriction | limiting regarding the rubbing which arises when the water spray amount of an intake spray cooler is increased can be eliminated, and it is easy to increase the water spray amount. For this reason, it becomes easy to aim at reduction of compression power equivalent to internal cooling by making spray droplets flow into the compressor.

  As a further advantage, the gap amount can be adjusted after the compressor assembly is completed. In recent years, from the viewpoint of improving the performance of compressors, the gap amount is a very small planned value relative to the equipment dimensions. However, there is a limit to precision manufacturing, and the number of parts of the compressor including the casing is large. Therefore, when the assembly is completed, the gap amount has a planned value and an error.

  Since the present invention is configured such that the casing is constantly cooled by the casing heat exchanger during rated operation without performing the intake spray cooling, the casing thermal expansion adjustment after completion of the compressor assembly is controlled by controlling the casing cooling amount. Is possible.

  Therefore, it is an advantage that the operation can be performed close to the planned value by offsetting the error between the planned value of the gap amount between the moving blade of the compressor and the casing, which has occurred in the manufacture and assembly of the compressor.

  In addition, the compressor of this invention is connected with a gas turbine, and can be comprised so that the combustion air of a gas turbine may be compressed.

(Example 5)
Next, a fifth embodiment of the present invention will be described with reference to FIG.

  A description of the same components as those in the first embodiment will be omitted. As shown in FIG. 8, the part different from the first embodiment is that water is supplied from a water supply tank 801 to a pressure pump 802 through a water supply pipe, and high-pressure water flows into a flow rate adjustment valve 803. The high-pressure water whose flow rate has been adjusted by the flow rate adjustment valve 803 flows into the casing heat exchanger 114, and after heat exchange, becomes high-temperature water and is stored in the storage tank 804. The gap control device 120 outputs a heat exchange amount command 121 to the water supply tank 801 and the flow rate adjustment valve 803, and the pressurization pump 802 and the flow rate adjustment valve 803 flow into the casing heat exchanger 114 in accordance with the heat exchange amount command 121. Change the pressure and flow rate of high-pressure water.

  In Example 5, although the storage tank 804 was provided, you may supply high temperature water directly to a demand source. Since the temperature of the high-temperature water obtained from the casing heat exchanger 114 depends on the control state of the gap amount, it is desirable to provide a storage tank 804 for the purpose of having a high-temperature water temperature and flow rate buffer function.

  The effects of Example 5 will be described below.

  According to the fifth embodiment, the high-temperature water after cooling the casing 112 can be stored in the storage tank 804. Although the compressor 103 depends on the model, for example, if the pressure ratio of the compressor 103 is 15 or more, the temperature of the compressed gas 106 reaches 300 ° C., and the temperature of the casing 112 rises accordingly, so the storage tank 804 Can be expected to store hot water at 100 ° C. or higher.

  If the application destination of the compressor 103 of Example 5 is a gas turbine, for example, a cogeneration system will be comprised and it will become effective utilization of an installation.

  Moreover, if the application destination of the compressor 103 of Example 5 is a high-humidity utilization gas turbine system that constitutes a regeneration cycle in which moisture is added, the high-temperature water supply destination can be a humidification tower. In a high-humidity gas turbine system, adding moisture to the compressed gas 106 in a humidification tower is the key to improving system efficiency. In order for the humidification tower to efficiently add moisture to the compressed gas 106, it is recommended that hot water flow down.

  In order to obtain high temperature water, an economizer is provided to recover heat from the gas turbine exhaust gas. According to the fifth embodiment, by using the high temperature water from the casing heat exchanger 114, the heat transfer area of the economizer can be reduced. If the heat transfer area of the economizer is reduced, the efficiency can be improved by downsizing and exhaust pressure loss.

  Or application to a solar heat assist gas turbine is considered. An intake spray cooler of a solar-assisted gas turbine uses atomized water at high temperature of 100 ° C. or higher to atomize spray droplets. The high temperature water is obtained from solar heat, and the amount of high temperature water obtained is reduced depending on the weather. Therefore, a configuration in which high temperature water is stored in a heat storage tank is desirable. If the structure of Example 5 is applied to a solar heat assist gas turbine, since high temperature water can be supplied also from the casing heat exchanger 114, further stabilization of the amount of high temperature water stored in the heat storage tank can be achieved.

  That is, the fifth embodiment of the present invention can obtain the same effects as the first embodiment and the above-described effects.

(Example 6)
Next, Embodiment 6 of the present invention will be described with reference to FIG.

  A description of the same components as those in the first embodiment will be omitted. As shown in FIG. 9, the part different from the first embodiment is that an actuator 901 is attached to the spray nozzle of the intake spray cooler 107, and the spray direction of the spray nozzle can be changed. The actuator 901 receives a direction command 902 from the gap control device 120 and corrects the direction of the spray nozzle.

  The gap control device 120 measures temperatures at a plurality of positions of the casing 112. The measurement positions are preferably distributed in the circumferential direction with respect to the rotation shaft 104. The gap control device 120 selects a point having a high temperature from the measurement signal 119 and generates a direction command 902 so that the amount of water spray in that direction can be increased. In generating the direction command 902 from the measurement signal 119, a conversion table may be given in advance or may be given as a function. Other measurement information may be used in the conversion process.

  The effects of Example 6 will be described below.

  According to the sixth embodiment, droplets attached to the casing 112 when the intake spray cooler 107 is increased can be concentrated on a specific portion of the casing 112. Therefore, a specific part of the casing 112 can be concentrated and cooled. During the operation of the casing 112, the thermal stress of the casing 112 also increases as the temperature deviation in the circumferential direction increases. At this time, by increasing the amount of water spray toward the high temperature portion by the actuator 901, the high temperature portion of the casing 112 can be cooled by the spray droplets, the temperature distribution of the casing 112 can be smoothed, and the thermal stress can be relaxed. .

  That is, the sixth embodiment of the present invention can obtain the same effects as those of the first embodiment and the above-described effects.

  DESCRIPTION OF SYMBOLS 101 ... Suction gas, 102 ... Intake duct, 103 ... Compressor, 104 ... Rotating shaft, 105 ... Rotor blade, 106 ... Compressed gas, 107 ... Intake spray cooler , 108 ... piping, 109 ... regulating valve, 110 ... rotation speed measuring instrument, 111 ... thermometer, 112 ... casing, 113 ... thermometer, 114 ... casing heat exchange 115, measuring instrument, 116, 117, 118, 119 ... measurement signal, 120 ... gap controller, 121 ... heat exchange amount command, δ ... gap amount, δref ... Gap amount target value, ε ... gap amount error, εref ... gap amount tolerance, f1, f2, f3 ... function, N ... rotation speed, Qref ... casing heat exchanger target heat transfer amount TG ... compressed gas temperature, TR ... casing temperature, ref: casing target temperature, 301: droplet, ΔRc: casing shrinkage due to cooling of casing heat exchanger, ΔRw: casing shrinkage due to casing droplet adhesion, t0: compressor operation Start time, t0w: Water spray start time of intake spray cooler, t1 ... Compressor rated power arrival time, t1w ... Water spray increase start time of intake spray cooler, δ0 ... Initial gap amount , ΔT ... casing temperature drop, f4, f5, f6 ... function, Tdry ... dry bulb temperature, Twe ... wet bulb temperature, 501 ... anti-surge valve, 502 ... valve control device 503 ... Flow meter, 504 ... Pressure gauge, 505 ... Measuring instrument, 506, 507, 508 ... Measurement signal, 509 ... Protection signal, dTR ... Change rate, dTRlim ... Change rate upper limit, Gw ... water fountain Quantity, i ... number of steps, PG ... compressed gas pressure, 113a, 113b, 113c, 113d ... thermometer, 114, 114a, 114b, 114c, 114d ... casing heat exchanger, 119a, 119b, 119c, 119d ... Measurement signal, 120a, 120b, 120c, 120d ... Gap control device, 121a, 121b, 121c, 121d ... Heat exchange command, 122 ... Control actuator, 123 ... Turbine, 801 ..Water tank, 802 ... Pressure pump, 803 ... Flow control valve, 804 ... Storage tank, 901 ... Actuator, 902 ... Direction command

Claims (12)

A rotor blade driven to rotate by a rotating shaft;
A casing surrounding the blade,
An intake air spray cooler that sprays and cools the gas sucked into the casing;
A casing heat exchanger for cooling or heating the casing;
A measuring instrument for measuring at least one of a gap size between the moving blade and the casing, a temperature of the casing, a temperature of the compressed gas discharged from the casing, and a rotational speed of the rotating shaft;
A difference between a gap dimension between the moving blade and the casing obtained based on a measurement signal output from the measuring instrument and a predetermined gap dimension target value is calculated, and the casing heat is calculated based on the calculated difference. A gap controller for controlling the operation of the exchanger;
A compressor having an intake spray cooler. In the compressor which has an intake spray cooler according to claim 1.
The gap controller is
When the gap dimension between the obtained moving blade and the casing is not more than a predetermined gap dimension tolerance, the operation of the casing heat exchanger is stopped,
When the gap dimension is larger than the predetermined gap dimension tolerance, and the difference between the gap dimension and the predetermined gap dimension target value is larger than the gap dimension tolerance, the gap dimension and the predetermined gap A compressor having an intake spray cooler which controls the operation of the casing heat exchanger according to a difference from a gap dimension target value. A compressor having an intake spray cooler according to claim 2,
The difference between the temperature of the compressed gas within the operating range of the compressor and the wet bulb temperature obtained by converting the compressed gas temperature by a predetermined dry / humidity conversion function is defined as the casing temperature decrease ΔT, and the casing temperature decrease ΔT and the above When the value obtained by substituting the temperature of the compressed gas into the predetermined gap amount change function is the change gap amount, the initial value of the gap dimension between the casing and the rotor blade is larger than the change gap amount. A compressor having an intake spray cooler characterized in that it is set. In the compressor which has an intake spray cooler according to claim 3.
The gas compressed by the compressor is air, and the predetermined dry-humidity conversion function used to calculate the casing temperature drop ΔT is a relational expression of a wet air diagram, a relational expression of a saturated vapor pressure curve, or the above two relational expressions A compressor having an intake spray cooler including at least one of derivative formulas derived from A compressor having an intake spray cooler according to claim 2,
The compressor is a multi-stage type, and an anti-surge valve in the middle stage,
The gap control unit includes a valve control unit that compares and calculates a rate of temperature increase of the casing and a predetermined threshold value, and controls the opening and closing of the anti-surge valve according to the calculation result. Compressor with spray cooler. A compressor having an intake spray cooler according to claim 2,
The measuring instrument is a temperature measuring instrument that measures or estimates at least two casing temperatures, and the gap control unit uses the casing temperature distribution information obtained from the temperature measuring instrument as a correction input value to determine the casing. A compressor having an intake spray cooler that calculates a target heat transfer amount of a heat exchanger and / or a target temperature of the casing. A compressor having an intake spray cooler according to claim 6.
The casing heat exchanger is at least two of a plurality of casing heat exchangers, and cools at least two different portions of the casing, and the gap control unit is provided for each of the plurality of casing heat exchangers. A compressor having an intake air spray cooler that separately calculates a region target heat transfer amount or a region target temperature of the casing, or both, and controls the operation of the casing heat exchanger. In the compressor which has an intake spray cooler according to claim 1.
A compressor having an intake spray cooler, wherein the compressor is connected to a gas turbine and compresses combustion air of the gas turbine. In the compressor which has an intake spray cooler according to claim 1.
The refrigerant of the casing heat exchanger is high-pressure water, and the high-pressure water that is heated by heat exchange of the casing heat exchanger and becomes hot water is used in another system different from the casing heat exchanger. A compressor having an intake spray cooler. A compressor having an intake spray cooler according to claim 9,
The compressor is a combustion air compressor of the high-humidity air-utilizing gas turbine system, which is a part of the high-humidity air-utilizing gas turbine system, and the other system using the hot water is A compressor having an intake spray cooler which is a humidification tower of an air-utilizing gas turbine system. A compressor having an intake spray cooler according to claim 9,
The compressor is a combustion air compressor of the solar assisted gas turbine system, which is a part of the solar assisted gas turbine system, and the other system using the warm water is the intake spray of the solar assisted gas turbine system. A compressor having an intake spray cooler, wherein the compressor is a cooler. In the compressor which has an intake spray cooler according to claim 1.
An estimator for measuring or estimating the power of the compressor; the spray nozzle of the intake spray cooler is movable and the spray direction is changed by a nozzle control device; the nozzle control device outputs an output signal of the gap control unit and A compressor having an intake spray cooler, wherein the nozzle spray direction is controlled by using power information of the compressor as an input.

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