JP5683321B2 - Steam turbine system and its warm-up method - Google Patents

Description

  The present invention relates to a steam turbine system in which steam is supplied from a boiler to a turbine, and a warm-up method thereof.

  For ships using steam turbines as marine main engines, it is necessary to warm up the turbines even when they are anchored so that they can immediately leave the ship in response to an earthquake or tsunami warning issued when the terminal is anchored. . By warming up the turbine, it is possible to sail at full speed without going through the warm-up process by stepwise operation.

  Patent Document 1 discloses a technique for solving a problem when shifting from a warm-up operation during anchoring in a steam turbine ship to a normal operation when leaving a port.

Japanese Patent No. 41844949

  The steam for warming up the turbine is a main steam pipe connected from the boiler to a high-pressure turbine used during ship forward operation, and a branch pipe branched from the main steam pipe (hereinafter also referred to as a warm-up steam pipe). ) And a supply port provided in the turbine. The warm-up steam pipe is provided with a pressure adjustment valve that adjusts the steam pressure while being controlled by the control unit. Hereinafter, all turbines in the case of a steam turbine system including a plurality of turbines such as a high-pressure turbine, an intermediate-pressure turbine, and a low-pressure turbine are collectively referred to simply as “turbine”.

  In the related art, the amount of warm-up steam flowing into the turbine has been adjusted to a uniquely determined steam pressure. That is, it is not set to a value other than one preset steam pressure, and whether or not appropriate warm-up steam is supplied.

  The steam supplied from the boiler changes the steam temperature, that is, the energy of the steam, according to the boiler load. For this reason, when the amount of warm-up steam is controlled so as to achieve a uniquely determined steam pressure, the turbine cannot be warmed up in a state where the turbine can always be expected. In other words, the relationship between the steam pressure in the warm-up steam pipe and the turbine casing temperature can be confirmed by a preliminary test, but in actual operation, the steam temperature varies depending on the boiler load, so the steam pressure must be unique. In the method of adjusting to a predetermined value, the turbine cannot always be warmed up properly.

  Also, when adjusting the turbine so that steam with a uniquely determined pressure is supplied, if the temperature of the steam supplied from the boiler decreases and the temperature of the warm-up steam decreases, the relationship between the specific volume and The flow rate of steam flowing into the turbine increases. Therefore, there is a problem that excessive steam flows through the low-pressure turbine, which overheats the low-pressure turbine, and the low-pressure turbine is overheated.

  The present invention has been made in view of such circumstances, and is a steam turbine capable of stably maintaining the turbine casing temperature regardless of the steam energy from the boiler that changes according to the boiler load. It is an object of the present invention to provide a system and its warm-up method.

In order to solve the above problems, the steam turbine system and the warm-up method thereof according to the present invention employ the following means.
That is, a steam turbine system according to the present invention includes a supply port for supplying steam that changes in temperature conditions discharged from a boiler from a branched steam pipe branched from a main steam pipe into a first turbine casing, and a first turbine. A first temperature measurement unit that measures the temperature inside and outside the vehicle interior of the vehicle interior, and a pressure that is provided in the branch steam pipe and that adjusts the pressure of the steam supplied to the first turbine vehicle interior based on the measured vehicle interior / exterior temperature And a control unit.

  According to this invention, after the steam is discharged from the boiler and passes through the main steam pipe, the steam passes through the branch steam pipe branched from the main steam pipe and is supplied into the first turbine casing. Further, the temperature inside and outside the first turbine casing is measured, and the pressure of the steam supplied to the first turbine casing is adjusted based on the measured outside temperature inside the casing. Therefore, the pressure of the steam supplied to the first turbine casing is not constant and changes according to the temperature outside the casing of the first turbine casing.

  On the other hand, as related technology, when the pressure of the steam supplied to the first turbine casing is uniquely determined, the flow rate of steam supplied to the first turbine casing depending on the temperature condition of the steam discharged from the boiler Changes. Therefore, the first turbine cannot be properly warmed up due to the temperature condition of the steam discharged from the boiler. In the present invention, since the flow rate of the steam supplied to the first turbine casing is controlled according to the measured temperature inside and outside the vehicle interior, the first turbine is appropriately set regardless of the temperature condition of the steam discharged from the boiler. Can warm up.

  For example, when the temperature inside and outside the first turbine casing is lower than a predetermined lower temperature limit, the pressure of steam supplied to the first turbine casing is increased to increase the energy flowing into the first turbine. , Eliminate the lack of warm-up. Conversely, when the temperature inside and outside the first turbine casing is higher than a predetermined upper temperature limit, the pressure of the steam supplied to the first turbine casing is reduced to reduce the energy flowing into the first turbine. To prevent overheating.

  In the present invention, after the first turbine casing is supplied to the second turbine casing, it further includes a second temperature measuring section that measures the exhaust temperature of the steam discharged from the second turbine casing, and the pressure control section The pressure of the steam supplied into the first turbine casing may be adjusted based on the measured outside temperature and exhaust temperature.

  According to the present invention, the steam discharged from the boiler passes through the first turbine casing, is supplied from the first turbine casing to the second turbine casing, and then passes through the second turbine casing. , Exhausted from the second turbine casing. Then, the exhaust temperature of the steam discharged from the second turbine casing is measured, and the pressure of the steam supplied into the first turbine casing is adjusted based on the measured outside temperature and exhaust temperature. Therefore, the pressure of the steam supplied to the first turbine casing changes according to not only the temperature outside the casing of the first turbine casing but also the exhaust temperature of the steam discharged from the second turbine casing. Therefore, the exhaust temperature of the steam discharged from the second turbine casing serves as an index, and not only the first turbine but also the second turbine can be appropriately warmed up.

  For example, when the exhaust temperature of the steam discharged from the second turbine casing is higher than a predetermined temperature upper limit, the energy flowing into the first turbine by reducing the pressure of the steam supplied to the first turbine casing To prevent overwarming.

  In the present invention, the pressure control unit further includes a reheat steam pipe that supplies steam from the first turbine casing to the reheater, and a warm pipe steam pipe that supplies steam from the branch steam pipe into the reheat steam pipe. The pressure of the steam supplied into the warm pipe steam pipe may be adjusted based on the measured temperature inside and outside the vehicle or the exhaust temperature.

  According to the present invention, in a steam turbine system having a reheat cycle in which a reheater is provided and steam is supplied from the first turbine casing to the reheater, steam is supplied from the branch steam pipe into the reheat steam pipe. Is done. And the pressure of the steam supplied into the first turbine casing and the reheat steam pipe is adjusted based on the measured temperature outside the vehicle interior or exhaust temperature. Therefore, not only the pressure of the steam supplied to the first turbine casing but also the pressure of the steam supplied to the reheat steam pipe changes. Therefore, not only the first turbine and the second turbine but also the reheat steam pipe can be appropriately warmed up.

Further, the method for warming up the steam turbine system according to the present invention includes a step of supplying steam having a changed temperature condition discharged from the boiler from the branch steam pipe branched from the main steam pipe into the first turbine casing; Measuring the temperature inside and outside the first turbine casing, and adjusting the pressure of steam supplied to the first turbine casing based on the measured outside temperature in the branch steam pipe Prepare.

  According to the present invention, since the flow rate of the steam supplied to the first turbine casing is adjusted according to the measured temperature inside and outside the vehicle interior, the first turbine is irrespective of the temperature condition of the steam discharged from the boiler. Can be warmed up properly.

  Regardless of the steam energy from the boiler that changes according to the boiler load, the turbine casing temperature can be stably maintained.

It is a lineblock diagram showing the steam turbine system concerning one embodiment of the present invention. It is an end view which shows the lower half compartment of a high intermediate pressure turbine compartment. It is a flowchart which shows operation | movement of the steam turbine system which concerns on one Embodiment of this invention. It is a lineblock diagram showing the steam turbine system concerning the modification of one embodiment of the present invention.

  Hereinafter, the structure of the steam turbine system 1 which concerns on one Embodiment of this invention is demonstrated using FIG. FIG. 1 is a configuration diagram showing a steam turbine system 1 according to the present embodiment.

  The steam turbine system 1 includes a high-pressure turbine 2H, an intermediate-pressure turbine 2M, a low-pressure turbine 2L, a main boiler 4H, a reheater 4R, and the like. The high-pressure turbine 2H and the intermediate-pressure turbine 2M are housed inside the high-medium-pressure turbine casing 3, and the low-pressure turbine 2L is housed inside the low-pressure turbine casing 5. Hereinafter, the high-pressure turbine 2H, the intermediate-pressure turbine 2M, and the low-pressure turbine 2L are collectively referred to simply as “turbine”.

  The steam turbine system 1 applies a reheat cycle in which the steam discharged from the high pressure turbine 2H is reheated by the reheater 4R, and the reheated steam is supplied to the intermediate pressure turbine 2M to be expanded.

  The main steam supplied from the main boiler 4H to the high-pressure turbine 2H during ship forward operation passes through the main steam pipes L1-1 and L1-2 shown in FIG. 1 and is supplied to the high-pressure turbine 2H.

  The steam turbine system 1 has a turbine warm-up system. The turbine warm-up system holds the steam turbine system 1 in a warm-up state by warming the high-pressure turbine 2H, the intermediate-pressure turbine 2M, and the high-medium-pressure turbine casing 3 with steam supplied from the main boiler 4H.

  Steam for warming up the high-pressure turbine 2H, the intermediate-pressure turbine 2M, and the high- and intermediate-pressure turbine casing 3 is supplied from the main steam pipe L1-1 connected to the high-pressure turbine 2H from the main boiler 4H and the main steam pipe L1-1. It is supplied to the high and medium pressure turbine casing 3 through a turbine warming system comprising a branching branch warming steam pipe L2, a pressure control valve 7, a shutoff valve 8, a supply port 9, and the like. As described above, the turbine warm-up system is provided in front of the high-pressure turbine 2H, and supplies the steam discharged from the boiler 4H into the high / medium-pressure turbine casing 3. The pressure control valve 7 provided in the warm-up steam pipe L2 is adjusted by the control unit 6 so as to allow energy suitable for the turbine warm-up state to flow into the high / medium-pressure turbine casing 3, and controls the steam pressure.

  The control unit 6 variably adjusts the pressure control valve 7 based on the temperatures measured by the temperature measurement units 12, 13, and 14. The pressure control valve 7 changes the steam flowing through the warm-up steam pipe L2 to various pressures. The temperature measuring units 12 and 13 are an example of a first temperature measuring unit. The temperature measuring unit 12 measures the temperature inside and outside the high and medium pressure turbine casing 3 in the high-pressure turbine 2H, and the temperature measuring unit 13 The inside / outside temperature of the high / intermediate pressure turbine casing 3 in the pressure turbine 2M is measured. The temperature measurement unit 14 is an example of a second temperature measurement unit, and measures the exhaust temperature of the steam discharged from the low-pressure turbine 2L.

  Further, the warm-up steam pipe L2 is provided with a shut-off valve 8 that shuts off the steam so that the steam does not flow into the high and medium pressure turbine casing 3 from the supply port 9 except during the warm-up.

  The turbine warm-up system warms up the turbine during berthing so that the ship can be immediately taken off in response to an earthquake or tsunami warning issued when the terminal is berthed. The turbine warm-up is not performed while the turbine is being driven in a state such as when the ship is operating, but is performed when the turbine is stopped in a state such as a cargo handling operation at the terminal or in the standby mode.

  While the turbine is warming up, the turbine must not idle due to the energy of the steam flowing into the high and medium pressure turbine casing 3 and the low pressure turbine casing 5. Therefore, the steam pressure of the warm-up steam is controlled so that the steam flow or steam energy equivalent to the starting torque that enables the turbine to be driven from the stationary state of the turbine does not flow into the high / medium pressure turbine casing 3 or the low pressure turbine casing 5. Is done. In the present embodiment, the upper limit is set for the pressure of the steam flowing through the warm-up steam pipe L2, and the upper limit is set for the exhaust temperature of the steam discharged from the low-pressure turbine 2L, thereby adjusting the steam pressure of the warm-up steam. To do.

  In addition, as shown in FIG. 1, the vehicle interior / external temperature of the high / medium pressure turbine casing 3 may be measured at one location for each of the high pressure turbine 2H and the intermediate pressure turbine 2M, particularly on the main steam inlet side. As shown in FIG. 2, the measurement may be made at a plurality of locations in the turbine axial direction or the radial direction of the turbine. FIG. 2 is an end view showing the lower half casing of the high and medium pressure turbine casing 3.

  As shown in FIG. 2, the high and medium pressure turbine casing 3 has a space S in which the high pressure turbine 2H and the intermediate pressure turbine 2M are housed. The left end of the high and medium pressure turbine casing 3 in FIG. 2 is the exhaust side of the high pressure turbine 2H, and the right end of the high and medium pressure turbine casing 3 in FIG. 2 is the exhaust side of the intermediate pressure turbine 2M. And the intermediate part of the high and medium pressure turbine casing 3 in FIG. 2 is the steam inlet side for both the high pressure turbine 2H and the intermediate pressure turbine 2M.

  The high and medium pressure turbine casing 3 includes a vehicle interior temperature sensor 31H at the high pressure side entrance, a vehicle exterior temperature sensor 32H at the high pressure side entrance, a vehicle interior temperature sensor 31M at the medium pressure side entrance, and a vehicle exterior temperature sensor at the intermediate pressure side entrance. 32M is provided. The control in the control unit 6 mainly includes measurement of a vehicle interior temperature sensor 31H at the high pressure side inlet, a vehicle exterior temperature sensor 32H at the high pressure side entrance, a vehicle interior temperature sensor 31M at the intermediate pressure side entrance, and a vehicle exterior temperature sensor 32M at the intermediate pressure side entrance. This is done based on the signal.

  The vehicle interior temperature sensor 31H at the high-pressure side inlet and the vehicle exterior temperature sensor 32H at the high-pressure side entrance are regions where main steam flows into the high-pressure turbine 2H. The temperature of the inner wall surface (the temperature of the area adjacent to the space) and the outer wall surface of the passenger compartment 3 in the virtual cross section including the point where the distance between them is farthest is measured. Similarly, the vehicle interior temperature sensor 31M at the intermediate pressure side inlet and the vehicle exterior temperature sensor 32M at the intermediate pressure side inlet are regions where reheated steam flows into the intermediate pressure turbine 2M. The temperature of the inner wall surface and the outer wall surface of the vehicle interior 3 in the virtual cross section including the point where the distance between them is farthest is measured.

  The high- and medium-pressure turbine casing 3 includes a high-pressure-side outlet cabin temperature sensor 33H, a high-pressure-side outlet cabin temperature sensor 34H, a medium-pressure-side outlet cabin temperature sensor 33M, and a medium-pressure-side outlet cabin temperature. A sensor 34 </ b> M may be provided to measure the temperature of the high and medium pressure turbine casing 3 and used for control in the control unit 6. The measurement signals of the high-pressure-side outlet cabin temperature sensor 33H, the high-pressure-side outlet cabin temperature sensor 34H, the intermediate-pressure-side outlet cabin temperature sensor 33M, and the intermediate-pressure-side outlet cabin temperature sensor 34M are used as reference information.

  The vehicle interior temperature sensor 33H at the high pressure side outlet and the vehicle exterior temperature sensor 34H at the high pressure side exit measure the temperatures of the inner wall surface and the outer wall surface of the vehicle chamber 3 in a virtual section of the region where the main steam flows out from the high pressure turbine 2H. It is. Similarly, the vehicle interior temperature sensor 33M at the intermediate pressure side outlet and the vehicle interior outside temperature sensor 34M at the intermediate pressure side outlet have an inner wall surface and an outer wall surface of the vehicle cabin 3 in a virtual cross section of the region where the reheat steam flows out from the intermediate pressure turbine 2M. The temperature is measured.

  In addition, the high and medium pressure turbine casing 3 is provided with a high pressure side inlet bolt temperature sensor 35H, a medium pressure side inlet bolt temperature sensor 35M, a high pressure side outlet bolt temperature sensor 36H, and a medium pressure side outlet bolt temperature sensor 36M. The temperature of the bolt in the bolt hole 41 may be measured and used as a reference temperature for control in the control unit 6. The measurement signals of the high pressure side inlet bolt temperature sensor 35H, the intermediate pressure side inlet bolt temperature sensor 35M, the high pressure side outlet bolt temperature sensor 36H, and the intermediate pressure side outlet bolt temperature sensor 36M indicate that the corresponding bolt temperature is the adjacent high and medium pressure turbine casing. 3 is used to check whether the temperature changes in conjunction with the temperature inside and outside the vehicle.

  Next, operation | movement of the steam turbine system 1 which concerns on this embodiment is demonstrated using FIG. FIG. 3 is a flowchart showing the operation of the steam turbine system 1 according to the present embodiment.

  Turbine warm-up maintenance is achieved by a heat balance such as heat input into the turbine, heat dissipation / exhaust heat from the turbine, heat retention of the turbine, etc. In this embodiment, the turbine can maintain warm-up. The determination of whether or not is quantitatively performed using temperature.

  Specifically, the control unit 6 determines whether or not the temperature inside and outside the high and medium pressure turbine casing 3 that has once reached a steady state is appropriate as the warm-up state of the turbine. When the warm-up maintenance state is insufficient, the flow rate of steam flowing through the warm-up steam pipe L2 is increased to increase the amount of heat supplied to the inside of the high / medium pressure turbine casing 3, or when the warm-up maintenance state is excessive Restricts the amount of heat supplied to the inside of the high and medium pressure turbine casing 3 by restricting the flow rate of the steam flowing through the warm-up steam pipe L2.

  That is, the effect of the turbine warm-up system is quantitatively evaluated based on the temperature inside and outside the high- and medium-pressure turbine casing 3, and the flow rate of the steam flowing into the high and medium-pressure turbine casing 3 is controlled so that the warm-up state is appropriate for the turbine. To do.

  In the related art, the steam flowing through the warm-up steam pipe is fixed at a preset pressure P1. Therefore, even if the turbine casing temperature is measured, it is only measured as a result of changing according to the state of the steam flowing into the turbine casing.

  In the present embodiment, first, the steam source valve is opened so that the steam flows into the warm-up steam pipe L2, and at the same time, water accumulated in the warm-up steam pipe L2 is discharged by opening the drain valve (step). S1). Next, the shutoff valve 8 is opened so that the warm-up steam flows into the high and medium pressure turbine casing 3 (step S2). At this time, the actual pressure P0 of the warm-up steam after the pressure control valve 7 is first adjusted as the warm-up steam set pressure P1 (step S3). The state is maintained until the thermal saturation state is reached (step S4). Here, the saturated state is when the temperature change rate is smaller than 1 ° C./hr, for example.

  When the warm-up steam is supplied, the turbine exhaust temperature TE is TE <TEmax with respect to the turbine exhaust temperature upper limit TEmax (for example, 75 ° C.) that is a guideline for the overwarm condition, and the turbine casing wall actual The warm-up steam set pressure P1 is controlled such that the temperature T0 is TL <T0 <TH with respect to the target passenger compartment temperature lower limit TL (eg, 200 ° C.) and the target passenger compartment temperature upper limit TH (eg, 250 ° C.). As a result, the warm-up state is maintained at a pressure P1 that satisfies TE <TEmax and TL <T0 <TH.

  Here, the turbine exhaust temperature TE is the temperature of the steam exhausted from the low-pressure turbine 2 </ b> L, that is, the temperature measured by the temperature measuring unit 14. The turbine casing wall actual temperature T0 is, for example, the vehicle interior temperature sensor 31H at the high pressure side inlet, the vehicle exterior temperature sensor 32H at the high pressure side entrance, the vehicle interior temperature sensor 31M at the intermediate pressure side entrance, and the vehicle at the intermediate pressure side entrance shown in FIG. It is a measured temperature based on the outdoor temperature sensor 32M, and is an average temperature obtained from these sensors or a temperature at any one point.

  In step S5, it is determined whether or not TE <Tmax for the turbine exhaust temperature TE. If TE ≧ TEmax, it is determined that the engine is overheated, and the set pressure P1 is set with respect to the current warmup steam set pressure P1. The pressure width β for reducing the pressure is decreased to P1 = P1−β (step S11). Thereby, the energy which flows into the high intermediate pressure turbine casing 3 is reduced, and overheating is prevented.

  In step S6, it is determined whether or not T0> TL for the turbine casing wall actual temperature T0. If T0 ≦ TL, it is determined that the warm-up is insufficient, and the current warm-up steam set pressure P1 is set. On the other hand, the pressure width α for increasing the set pressure P1 is increased to P1 = P1 + α (step S8). Thereby, the energy which flows into the high intermediate pressure turbine casing 3 is raised, and the warm-up shortage is solved. At this time, it is determined whether or not the set pressure P1 satisfies P1 <Pmax with respect to the warm-up steam pressure upper limit Pmax (step S9). The set pressure P1 is controlled within the range of P1 <Pmax. However, even if the set pressure P1 reaches P1 = Pmax and reaches the warm-up steam pressure upper limit Pmax, the turbine casing wall actual temperature T0 is the target casing temperature lower limit. When TL is not reached and T0> TL is not satisfied, the target passenger compartment temperature cannot be achieved with the current steam temperature (steam energy). Therefore, the operator is cautioned to improve the steam state, for example, increase the boiler load to raise the steam temperature.

  Further, in step S7, it is determined whether or not T0 <TH for the turbine casing wall actual temperature T0. If T0 ≧ TH, it is also determined that the engine is overwarming, and the current warming steam set pressure P1 is set. P1 = P1−β is set (step S11). Thereby, the energy which flows into the high intermediate pressure turbine casing 3 is reduced, and overheating is prevented.

  Next, a modification of one embodiment of the present invention will be described with reference to FIG. FIG. 4 is a configuration diagram showing a steam turbine system 11 according to a modification of the embodiment of the present invention.

  In the steam turbine system 11 of this modification, not only the high and medium pressure turbine casing 3 but also the reheat steam pipe are targeted for control in the turbine warm-up system. The reheat steam pipe is a pipe from the high pressure turbine 2H to the intermediate pressure turbine 2M through the reheater 4R. This modification is different from the steam turbine system of FIG. 1 in that a warm pipe steam pipe L3 is provided.

  The steam for warming the reheat steam pipe is a main steam pipe L1-1 connected from the main boiler 4H to the high-pressure turbine 2H, and a warming steam that is a branch pipe branched from the main steam pipe L1-1. It passes through the pipe L2 and the warm pipe steam pipe L3 branched from the warm-up steam pipe L2, and is supplied to the reheat steam pipe. The warm pipe steam pipe L3 is provided with a shutoff valve 15 for shutting off steam so that steam does not flow into the reheat steam pipe except during warm-up.

  According to this modification, the pressure of the steam supplied into the reheat steam pipe is adjusted based on the measured turbine casing wall actual temperature T0 or the exhaust temperature. Therefore, not only the pressure of the steam supplied to the high and medium pressure turbine casing 3 but also the pressure of the steam supplied to the reheat steam pipe changes. Therefore, not only the high pressure turbine 2H and the intermediate pressure turbine 2M but also the reheat steam pipe can be appropriately warmed up. Therefore, even when the steam turbine system is driven suddenly, the reheat steam pipe is not rapidly heated, and the thermal stress on the reheat steam pipe can be reduced.

  When warming the reheat steam pipe, the amount of heat applied to the high / medium pressure turbine casing 3 is reduced by the amount used for the warm pipe, so the warm-up steam set pressure P1 to be adjusted is set in the above-described embodiment. It becomes larger than the pressure P1.

  As described above, according to the embodiment and the modification of the present invention, the steam pressure is controlled so that the expected turbine warm-up state is maintained, and the inflow steam energy is actively adjusted regardless of the steam temperature condition. And the warm-up state is properly maintained. As a result, it is possible to leave the ship immediately in response to a tsunami warning issued when the terminal is anchored. Further, since the inflow energy due to the steam can be controlled so as to approach the target values of the turbine vehicle interior / outside temperature and the turbine exhaust temperature regardless of the boiler load, it is possible to prevent the turbine from being overheated or insufficiently warmed up.

  In addition, when the temperature of the steam supplied from the boiler decreases and the temperature of the warm-up steam decreases, the related technology adjusts so that steam with a uniquely determined pressure is supplied to the turbine. The steam flow rate flowing into the turbine increases due to the specific volume. Therefore, there is a problem that excessive steam flows through the low-pressure turbine, which overheats the low-pressure turbine, and the low-pressure turbine is overheated. On the other hand, in this embodiment and the modification, the steam pressure is controlled using the turbine exhaust temperature TE, which is the temperature of the steam exhausted from the low-pressure turbine 2L, as an index. Therefore, overheating of the low pressure turbine 2L can be prevented.

  In addition, in the said description, although the case where the steam turbine system 1 applied a reheat cycle was demonstrated, this invention is not limited to this example. For example, even in a steam turbine system to which a Rankine cycle without a reheater 4R or a reheat steam pipe is applied, the turbine warm-up system of the present invention can be installed, and the turbine can be warmed up appropriately.

1,11 Steam turbine system 2H High pressure turbine 2M Medium pressure turbine 2L Low pressure turbine 3 High and medium pressure turbine casing (first turbine casing)
4H main boiler (boiler)
4R Reheater 5 Low pressure turbine casing (second turbine casing)
6 Control unit 7 Pressure control valve (pressure control unit)
8, 15 Shut-off valve 9 Supply port 12, 13 Temperature measuring part (first temperature measuring part)
14 Temperature measurement unit (second temperature measurement unit)
L1 Main steam pipe L2 Warm-up steam pipe (branch steam pipe)
L3 Steam pipe for warm pipe

Claims (4)

To branch a steam pipe or we first turbine wheel chamber branched from the main steam pipe, a supply port for supplying the steam temperature condition, which is discharged from the boiler is changed,
A first temperature measuring unit for measuring a temperature inside and outside the first turbine casing;
A pressure control unit that is provided in the branch steam pipe and adjusts the pressure of the steam supplied to the first turbine casing based on the measured temperature outside the casing;
A steam turbine system comprising: A second temperature measuring unit for measuring an exhaust temperature of the steam discharged from the second turbine casing after being supplied from the first turbine casing to the second turbine casing;
2. The steam turbine system according to claim 1, wherein the pressure control unit adjusts a pressure of the steam supplied into the first turbine casing based on the measured temperature outside the cabin and the exhaust temperature. A reheat steam pipe for supplying steam from the first turbine casing to the reheater;
A warm pipe steam pipe for supplying steam from the branch steam pipe into the reheat steam pipe;
Further comprising
3. The steam turbine system according to claim 2, wherein the pressure control unit adjusts the pressure of the steam supplied into the warm pipe steam pipe based on the measured temperature inside and outside the vehicle or the exhaust temperature. Supplying steam from the branch steam pipe branched from the main steam pipe into the first turbine casing to change the temperature condition discharged from the boiler;
Measuring the temperature inside and outside the first turbine casing;
Adjusting the pressure of the steam supplied into the first turbine casing based on the measured temperature outside the casing in the branch steam pipe;
A method for warming up a steam turbine system comprising:

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