CN211058872U - Large-scale steam turbine high-pressure cylinder concurrent flow heating system - Google Patents
Large-scale steam turbine high-pressure cylinder concurrent flow heating system Download PDFInfo
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- CN211058872U CN211058872U CN201921829478.XU CN201921829478U CN211058872U CN 211058872 U CN211058872 U CN 211058872U CN 201921829478 U CN201921829478 U CN 201921829478U CN 211058872 U CN211058872 U CN 211058872U
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Abstract
The utility model discloses a large-scale steam turbine high pressure cylinder following current heating system, including penetrating gas ejector, oil water separator, catch water, air heater and hot-air header, the pipeline between the high pressure cylinder governing valve of hot-air header and steam turbine main steam valve links to each other, and the suction port of penetrating the gas ejector links to each other with the blast pipe of the high pressure cylinder of steam turbine. The utility model is characterized in that the cylinder wall of the steam turbine of the large steam turbine generator unit and the thick temperature rise of the rotor material are slow, the rotor is not easy to rush and rotate, the cold start adopts the downstream heating mode, the temperature field downstream formed after the high temperature heating air flows through the high pressure cylinder is reduced in the mode, the direction of the steam flow is the same as that of the steam flow when the steam turbine rushes and rotates, the formed temperature field is consistent with the rushing and rotating process of the steam turbine, and the thermal shock to the high pressure cylinder in the rushing and rotating process of the steam turbine can be effectively reduced; the temperature of the high-pressure cylinder of the steam turbine can be quickly increased, the cost is saved, and the loss is reduced.
Description
Technical Field
The utility model relates to a steam turbine technical field especially relates to a large-scale steam turbine high pressure cylinder following current heating system.
Background
The steam that needs to adjust through the cylinder at turbo generator set cold starting in-process heats through the governing valve, because the power generation turbine cylinder wall thickness, it is longer to need the heating time, considers simultaneously that the turbine rotor is heated the inflation with the cylinder and is asynchronous, can take place the sound and rub at the unit start high-speed rotatory in-process, therefore the steam turbine admission can not be too big, needs low flow to heat slowly. This makes the unit start-up time overlength, and the boiler that supplies steam for the steam turbine runs for a long time low-load, and the boiler combustion of low-load operation is very unstable, needs to throw oil or throw plasma operation, causes the unit cold starting cost to be high. The large-scale steam turbine generator unit has the characteristics of low temperature rise due to thick materials of a steam turbine cylinder wall and a rotor, difficulty in impact rotation of the rotor and the like, and is more difficult to heat.
SUMMERY OF THE UTILITY MODEL
To above not enough, the utility model provides a large-scale steam turbine high-pressure cylinder following current heating system can help large-scale steam turbine high-pressure cylinder to heat.
In order to achieve the above purpose, the utility model adopts the following technical scheme:
the jet orifice of the jet air extractor is sequentially connected with the oil-water separator, the steam-water separator, the air heater and the hot air header, the hot air header is connected with a pipeline between a high-pressure cylinder regulating valve of the steam turbine and a main steam valve of the steam turbine, a high-pressure cylinder hot air inlet regulating valve is arranged on a pipeline connected with the steam turbine, a suction port of the jet air extractor is connected with an exhaust pipe of the high-pressure cylinder of the steam turbine, and a return air regulating valve is arranged on a pipeline connected with the steam turbine.
Furthermore, the number of the air heaters is more than two, and the two air heaters are operated in series or in parallel.
Furthermore, the oil-water separator is connected with the steam-water separator in series, an oil-water separator front stop valve is arranged between the oil-water separator and the air injection air extractor, and a steam-water separator rear stop valve is arranged between the steam-water separator and the air heater.
Furthermore, the oil-water separator front stop valve, the oil-water separator, the steam-water separator and the steam-water separator rear stop valve which are connected in sequence form an oil-steam-water separation mechanism, and the oil-steam-water separation mechanism is multiple and is connected in parallel between the air injection air extractor and the air heater.
Furthermore, a safety valve, an exhaust valve, a pressure measuring device, a temperature measuring device and a hot air header blow-off door are arranged on the hot air header.
Furthermore, a drain tank and an air exhaust valve are arranged between the air return regulating valve and the high-pressure cylinder on a pipeline connected with the air jet air ejector and the steam turbine, and an air return pollution discharge door is arranged on the drain tank.
Furthermore, a compressed air joint of the air injection air ejector is connected with a compressed air main pipe, and a compressed air main pipe air supply adjusting valve is arranged on the compressed air main pipe.
Compared with the prior art, the beneficial effects of the utility model are that:
1. aiming at the characteristics that the temperature rise of the steam turbine cylinder wall and the rotor material of a large steam turbine generator unit is slow, the rotor is not easy to rush and rotate and the like, the patent adopts a downstream heating mode, the downstream of a temperature field formed by high-temperature heating air flowing through a high-pressure cylinder in the mode is reduced, the direction of the temperature field is the same as the steam flow direction of steam during the rush and rotation of the steam turbine, the formed temperature field is consistent with the rush and rotation process of the steam turbine, and the thermal shock to the high-pressure cylinder during the rush and rotation process of the;
2. the utility model adopts the air ejector, and the low-pressure high-temperature air is sucked by the high-pressure compressed air, so that on one hand, the consumption of the high-pressure compressed air is reduced, on the other hand, the temperature of the high-pressure compressed air entering the air ejector is improved because the high-pressure compressed air is sucked, the temperature of the air in the air heater is also improved, the power consumption of the air heater is reduced, and the starting and operating cost of the unit is reduced;
3. because the heating medium adopted by the high-pressure cylinder of the steam turbine is air which is non-condensable gas, the hidden troubles that the water content of the steam turbine oil exceeds the standard, metal parts are rusted and the like because water is condensed into water by heating steam are overcome;
4. the utility model discloses improve the unit from the cold state to temperature attitude, hot attitude, make the turbine rush to rise the speed and can rise the load fast after being incorporated into the power networks, reduced the cold start of turbine and promoted the warm jar time of turbine high pressure cylinder, promote the quick response performance of generator group to the electric wire netting by a wide margin, avoid long-time low-load warm jar will cause the boiler to throw the oil mass to increase by a wide margin, or throw plasma and cause the loss of negative and positive pole life-span and the consumption of electric quantity by a wide margin;
5. the utility model provides a large-scale steam turbine high-pressure cylinder following current heating system has generating set cold starting practices thrift cost, heating fast, reduces the loss, satisfies characteristics such as electric wire netting power regulation requirement fast.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly described below.
Fig. 1 is a schematic structural view of the present invention;
fig. 2 is a schematic diagram of the present invention.
Detailed Description
The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the embodiments described are only some embodiments of the invention, and not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
Referring to fig. 1 and 2, a preferred embodiment of the present invention provides a cold state turbine high pressure cylinder downstream heating system, which comprises an air injection air extractor 3, an oil-water separator, a steam-water separator, an air heater and a hot air header 25, wherein a jet orifice of the air injection air extractor 3 is sequentially connected to the oil-water separator, the steam-water separator, the air heater and the hot air header 25, the hot air header 25 is connected to a pipeline between a high pressure cylinder regulating valve 38 of a turbine and a main steam valve 40 of the turbine, a high pressure cylinder hot air inlet regulating valve 39 is arranged on a pipeline connecting the hot air header 25 and the turbine, the air injection air extractor 3 is connected to an exhaust pipe of a high pressure cylinder 47 of the turbine, a specific connection position is between the exhaust pipe high pressure cylinder 47 and a high pressure cylinder exhaust check valve, and a return air regulating valve 52 is arranged on a pipeline connecting the air injection air extractor 3 and the turbine.
In operation, the heated air flow enters the high pressure cylinder 47 from the conduit between the turbine high pressure cylinder regulator valve 38 and the turbine main steam valve 40, and is therefore a concurrent heating mode.
The air ejector 3 adopts a common air ejector structure and mainly comprises a compressed air joint, a jet orifice and a suction port. Compressed air enters from the compressed air joint, return air enters from the suction port and flows out from the jet port together. The air ejector 3 is provided with two air paths, wherein one air path is connected with a compressed air main pipe through a compressed air joint of the air ejector 3, the other end of the compressed air main pipe is connected with a compressed air storage tank (not shown in the figure), the compressed air main pipe is provided with a compressed air main pipe air supply regulating valve 1, the compressed air main pipe air supply regulating valve 1 can be used for regulating the ventilation volume so as to regulate the pressure in the system and the like, and the air path is a main source of compressed air and has high pressure; the other path is connected with an exhaust pipe of the high-pressure cylinder 47 through a suction port of the air injection air extractor 3, and the pressure is lower for a return air path after the high-pressure cylinder 47 of the steam turbine is heated. The air ejector 3 sucks return air with lower pressure after flowing through the high-pressure cylinder 47 by using compressed air with high pressure, and the return air flows out from the jet orifice along with the compressed air, so that on one hand, the consumption of the high-pressure compressed air is reduced, on the other hand, because the sucked air is low-pressure high-temperature air, the temperature of the high-pressure compressed air entering from a compressed air joint of the air ejector 3 is improved, namely, the temperature of the air heater can be improved, the power consumption of the air heater is reduced, and the starting and operating cost of a unit is reduced. The compressed air main pipe is provided with a blowoff valve 2 on a pipeline between the compressed air main pipe air supply regulating valve 1 and the air jet air extractor 3.
An air exhaust valve 51 and a drain tank 49 are arranged on a pipeline between the air return regulating valve 52 and the exhaust pipe of the high-pressure cylinder 47, and an air return blow-down valve 50 is arranged on the drain tank 49.
The oil-water separator and the steam-water separator are connected in series for operation, an oil-water separator front stop valve is arranged between the oil-water separator and the air injection air extractor 3, and a steam-water separator rear stop valve is arranged between the steam-water separator and the air heater. In the preferred embodiment, there are two oil-water separators, namely, the first oil-water separator 6 and the second oil-water separator 11; the number of the steam-water separators is two, the two steam-water separators are respectively a first steam-water separator 8 and a second steam-water separator 13, and the first steam-water separator 8 and the second steam-water separator 13 are both provided with a drier. A first oil-water separator front stop valve 4 is arranged between the first oil-water separator 6 and the gas injection air ejector 3, and a second oil-water separator front stop valve 10 is arranged between the second oil-water separator 11 and the gas injection air ejector 3; a first steam-water separator rear stop valve 9 is arranged between the first steam-water separator 8 and the air heater, and a second steam-water separator rear stop valve 15 is arranged between the second steam-water separator 13 and the air heater. The first oil-water separator front stop valve 4, the first oil-water separator 6, the first steam-water separator 8 and the first steam-water separator rear stop valve 9 form an oil-steam-water separation mechanism, the second oil-water separator front stop valve 10, the second oil-water separator 11, the second steam-water separator 13 and the second steam-water separator rear stop valve 15 form an oil-steam-water separation mechanism, and the two oil-steam-water separation mechanisms are connected in parallel. Each oil-steam-water separation mechanism independently forms a group, and two groups of oil-steam-water separation mechanisms can be used for one by one and can also be used simultaneously, so that the switching or the maintenance in operation is convenient. The first oil-water separator 6 is provided with a first oil-water separator sewage discharging door 5, the second oil-water separator 11 is provided with a second oil-water separator sewage discharging door 12, the first steam-water separator 8 is provided with a first steam-water separator sewage discharging door 7, the second steam-water separator 13 is provided with a second steam-water separator sewage discharging door 14, and the above sewage discharging doors are convenient for discharging impurities, oil and steam water inside the second steam-water separator.
The air heater is divided into two air heaters, namely a first air heater 16 and a second air heater 19, the first air heater 16 and the second air heater 19 can be operated in parallel or in series, specifically, a first air heater rear stop valve 20 is arranged on a pipeline between the first air heater 16 and a hot air header 25, a second air heater front stop valve 17 is arranged on a pipeline between the second air heater 19 and a steam-water separator, and a heater switching stop valve 18 is arranged on a pipeline between the first air heater 16 and the second air heater 19. In practice, according to the requirement of air temperature adjustment, the first air heater 16 and the second air heater 19 are connected in parallel in the low temperature stage, and can be connected in series in the high temperature stage to improve the air temperature adaptability.
The hot air header 25 joins the hot air from the first air heater 16 and the second air heater 19, and the hot air header 25 is provided with an exhaust valve 22, a pressure measuring device 23, a temperature measuring device 24 and a hot air header blowdown door 53. Wherein, pressure measurement device 23 adopts E type thermocouple, tests hot-air header 25 air pressure, and temperature measurement device 24 adopts EJA series pressure transmitter, tests hot-air header 25 interior air temperature, installs relief valve 21 on the hot-air header 25, and relief valve 21 is the one protection of taking precautions against hot-air header 25 pressure and exceeding standard and damaging. The exhaust valve 22 can exhaust air in the hot air header 25, and the hot air header blowdown gate 53 is used to exhaust impurities, oil, and steam water in the hot air header 25.
High-pressure compressed air enters through a compressed air main pipe through the air injection air extractor 3, enters an air heater after being purified by the oil-water separator and the steam-water separator, is heated into dry hot air (called hot air), and then is collected in the hot air header 25, the hot air header 25 is used for storage, temperature mixing and air distribution, and then is guided into the high-pressure cylinder 47 through a pipeline between the high-pressure cylinder regulating valve 38 of the steam turbine and the main steam valve 40 of the steam turbine, so that the aim of rapidly heating and warming the high-pressure cylinder 47 is fulfilled.
The flow part of the high-pressure cylinder 47 is heated to rise temperature, hot air enters the flow part of the high-pressure cylinder 47 in a flow mode in the same direction as the flow, namely a forward flow heating mode, the hot air enters the high-pressure cylinder 47 by utilizing a pipeline between the high-pressure cylinder regulating valve 38 and the main steam valve 40 of the steam turbine, rotors and corresponding stator part sleeves are respectively heated by forward flow, part of the hot air is discharged to the atmosphere from an exhaust pipe of the high-pressure cylinder 47 as heating air while flowing through a moving part and a static part, the hot air is recycled after conditions are met, and part of the hot air enters the air ejector 3 again through the pipeline so as to realize recycling.
To better illustrate the present invention, a 300MW steam turbine generator set is taken as an example to detail the downstream heating process. The steam turbine is a subcritical, single-shaft, three-cylinder, two-steam-exhaust, once-intermediate-reheat condensing steam turbine, please refer to fig. 2, the steam turbine mainly comprises a high-pressure cylinder 47, an intermediate-pressure cylinder 36, a low-pressure cylinder I34, a low-pressure cylinder II33, a condenser 30, a condensate pump 31, corresponding connecting pipelines, and a deaerating water level regulating valve 26, a condenser vacuum breaking door 31, a low-pressure cylinder desuperheating water first regulating valve 27, a low-pressure cylinder desuperheating water second regulating valve 29, a high-pressure cylinder regulating valve 38, a turbine main valve 40, a turbine bypass valve 41, a first high-pressure cylinder steam-exhaust check valve 42, a second high-pressure cylinder steam-exhaust check valve 46, a low-pressure cylinder desuperheating water first regulating valve 27, a low-pressure cylinder desuperheating water second regulating valve 29, a high-pressure cylinder inner cylinder regulating level metal temperature measuring device 43, a shaft eccentricity measuring device 44, a high-pressure turbine high-pressure differential expansion measuring device 45 and a high-pressure cylinder upper and lower, the low-pressure cylinder I34 is provided with a first low-pressure cylinder steam exhaust measuring device 35, and the low-pressure cylinder II33 is provided with a second low-pressure cylinder steam exhaust measuring device 32. The first high-pressure cylinder steam exhaust check valve 42 and the second high-pressure cylinder steam exhaust check valve 46 are respectively installed on the exhaust pipes of the high-pressure cylinder 47 (two exhaust pipes of the high-pressure cylinder 47), the hot air header 25 is connected with the pipeline between the high-pressure cylinder regulating valve 38 of the steam turbine and the main steam valve 40 of the steam turbine, and the high-pressure cylinder hot air inlet regulating valve 39 is arranged on the pipeline connecting the hot air header 25 and the steam turbine. The air injection air ejector 3 is communicated with two exhaust pipes through a pipeline, and the connection position is between the high-pressure cylinder 47 and the first high-pressure cylinder steam exhaust check valve 41 and the second high-pressure cylinder steam exhaust check valve 45.
Before heating, the turbine is in a cold state, i.e. the temperature measured by the high-pressure cylinder inner cylinder regulating stage metal temperature measuring device 43 is less than a certain value, such as < 150 ℃ in the preferred embodiment.
The turbine is turning continuously normally and the measured value of the shaft eccentricity measuring device 44 is less than a certain value, such as < 76um in the preferred embodiment.
The test value of the turbine high pressure differential expansion measuring device 45 is preferably-1.2 mm-6.6 mm.
Accumulated water in each heating pipeline is drained; the turbine body and the extraction pipe are drained and then all the drain valves of the high pressure cylinder 47 of the turbine are closed.
The operation of a compressed air system is ensured, the air source is normally supplied, and the blowoff valve 2 on the compressed air main pipe is opened to drain impurities such as oil, steam and water in the pipe.
The condenser 30 is evacuated to zero and the shaft seal steam is stopped. The condenser 30 of steam turbine leads to the circulating water, and condenser vacuum destroys door 31 and opens, and all other valves are all closed.
Before heating, concurrent flow heating system discharge and heating pipe operation are carried out.
Before the heating system is put into use, a first oil-water separator blowdown door 5, a second oil-water separator blowdown door 12, a first steam-water separator blowdown door 7, a second steam-water separator blowdown door 14, a hot air header blowdown door 53 and a return air blowdown door 50 are opened, and impurities, oil, steam and water are exhausted;
keeping a first oil-water separator blowdown door 5, a second oil-water separator blowdown door 12, a first steam-water separator blowdown door 7, a second steam-water separator blowdown door 14, a hot air header blowdown door 53 and a return air blowdown door 50 open, opening a first oil-water separator front stop valve 4 and a second oil-water separator front stop valve 10, opening a compressed air main pipe air supply regulating valve 1 with the opening degree of 5-30%, and purging a heating system pipeline;
opening a first steam-water separator rear stop valve 9, a second steam-water separator rear stop valve 15, a heater switching stop valve 18 and a hot air header blowdown door 53 for purging; after purging is completed, the pair of air exhaust valves 51 are opened, and the heater switching stop valve 18 is closed; and then closing the first oil-water separator blowdown door 5, the second oil-water separator blowdown door 12, the first steam-water separator blowdown door 7, the second steam-water separator blowdown door 14, the hot air header blowdown door 53 and the return air blowdown door 50, automatically opening and closing according to the liquid level.
After the above work is completed, the heating operation is started.
The first oil-water separator front stop valve 4 and the first steam-water separator rear stop valve 9 are closed, the second oil-water separator front stop valve 10 and the second steam-water separator rear stop valve 15 are opened, and the second oil-water separator 11 and the second steam-water separator 13 are put into operation. Of course, the first oil-water separator front stop valve 4 and the first steam-water separator rear stop valve 9 can be opened according to the maintenance or repair requirement, the second oil-water separator front stop valve 10 and the second steam-water separator rear stop valve 15 are closed, the second oil-water separator 11 and the second steam-water separator 13 are cut off, and the first oil-water separator 6 and the first steam-water separator 8 are put into operation;
keeping the opening degree of an air supply regulating valve 1 of a compressed air main pipe at 5-20%, supplying power to a first air heater 16 and a second air heater 19, adjusting the temperature to a zero position, and closing a matched air switch of the control cabinet;
and (3) opening an exhaust valve 22, adjusting the heating air temperature set values of the first air heater 16 and the second air heater 19, increasing the air temperature, opening an air exhaust valve 51, opening a high-pressure cylinder regulating valve 38, closing the exhaust valve 22 and gradually opening a high-pressure cylinder hot air inlet regulating valve 39 when the test value of the hot air header temperature measuring device 23 reaches a required value and is stable, and allowing hot air to enter the high-pressure cylinder 47 from a pipeline between the high-pressure cylinder regulating valve 38 and a main steam valve 40 of the steam turbine through the high-pressure cylinder regulating valve 38, namely heating the high-pressure cylinder 47 by supplying hot air to the high-pressure cylinder 47 in a downstream mode, so that the cylinder temperature of the high-pressure cylinder 47 is increased.
When the steam trap 49 is empty, the air return adjusting valve 52 is opened, the air return blow-down valve 50 and the opposite air exhaust valve 51 are closed, the hot air enters the air jet ejector 3 from the exhaust pipe of the high-pressure cylinder 47, and the return air flowing through the high-pressure cylinder 47 is sucked, recovered and reused by the air jet ejector 3.
The measured value of the hot air header pressure measuring device 24 in heating operation is kept between 0.2 MPa and 0.6MPa, and the pressure can be cooperatively adjusted through the air supply adjusting valve 1 of the compressed air main pipe, the matching of the air exhaust valve 51 and the suction effect of the air ejector 3 on the return air of the high-pressure cylinder 47 according to the cylinder temperature lifting effect.
The first air heater 16 and the second air heater 19 are connected in parallel in the low temperature stage, and can be connected in series in the high temperature stage to improve the air temperature adaptability.
In the gradual rising process of the cylinder temperature, the metal temperature rise rate of the cylinder monitored by the high-pressure cylinder and the medium-pressure cylinder in the rapid heating process is controlled to be less than or equal to 10 ℃/h, and the instant is not more than 18 ℃/h.
The set value of the air outlet temperature of the heating system is adjusted in time along with the rise of the temperature of the cylinder after the heating is put into operation, and the set value is always kept to be higher than the temperature of the cylinder by a certain value. The principle is shown in table 1 below.
TABLE 1 relationship table of heated air temperature and high pressure cylinder in-cylinder temperature
| Temperature of heated air | Temperature difference between inner cylinder adjusting metal of high-pressure cylinder and heated air |
| ＞300℃ | ＜50℃ |
| ＞200℃ | ＜80℃ |
| ＞150℃ | ＜100℃ |
In the process of rapidly heating the steam turbine, the testing values of the first low-pressure cylinder steam exhaust temperature measuring device 35 and the first low-pressure cylinder steam exhaust measuring device 35 are kept at a certain value, if the value is more than or equal to 80 ℃ in the preferred embodiment, a condensate system is put into use, and the low-pressure cylinder steam exhaust water spray temperature reduction is started.
The temperature difference measuring device 48 for the upper cylinder and the lower cylinder of the high-pressure cylinder of the steam turbine is kept to be smaller than a certain value, the test value is less than 56 ℃ in the preferred embodiment, and the temperature difference measuring device can be adjusted by opening a drain valve (54) of the high-pressure cylinder.
The continuous turning of the turbine is kept normal, and the testing value of the shaft eccentricity measuring device 44 is smaller than a certain value, and the testing value is smaller than 76um in the preferred embodiment. The high pressure differential expansion measuring device 45 of the steam turbine has a test value of-1.2 mm to 6.6 mm.
The high pressure cylinder hot air intake adjusting valve 39 is automatically closed when the first and second air heaters 16 and 19 are suddenly de-energized, and the impact of the cold air on the high pressure cylinder 47 is prevented.
In order to ensure safety, in the rapid heating process, the pressure of the hot air header 25 is set to a certain ratio, when the pressure is greater than 0.9, the safety valve 21 is automatically opened to release the pressure, and the hot air header is reset after normal operation; when the testing value of the heating air pressure measuring device 23 is less than 0.05MPa, the switches of the first air heater 16 and the second air heater 19 are automatically closed, and the power supply is cut off.
Heating the steam turbine from a cold state to a warm state or a hot state according to starting requirements, wherein the warm state or the hot state is divided according to the metal temperature of an inner cylinder adjusting stage of a starting cylinder of the steam turbine:
and (3) cold state: the temperature of the adjusting metal is less than 150 ℃.
Temperature state: the temperature of the adjusting metal is higher than 150 ℃ and lower than 280 ℃.
Thermal state: the temperature of the regulating grade metal is more than 280 ℃ and less than 380 ℃.
When the heating is finished, the high-pressure cylinder hot air inlet adjusting valve 39 is closed, and the exhaust valve 22 on the hot air header 25 is opened; deactivating the first air heater 16 and the second air heater 19; the return air adjustment valve 52 is closed.
After the heating is stopped, the steam turbine has the steam inlet rush rotation starting condition at the same time.
And after the test value of the temperature measuring device 24 of the hot air header 25 is reduced to the ambient temperature, the heating system completely quits the operation.
The utility model discloses in, to large-scale turbo generator set steam turbine jar wall and the thick temperature rise of rotor material slow, the rotor is heavy be difficult for dashing characteristics such as commentaries on classics, adopt following current heating methods, the temperature field following current that forms under this mode high temperature heated air stream flows through behind the high pressure cylinder reduces, and steam stream direction is the same when dashing the commentaries on classics with the steam turbine, and the temperature field of formation just also dashes the process with the steam turbine unanimously, can effectively reduce the steam turbine and dash the thermal shock of commentaries on classics in-process to high pressure cylinder. The utility model discloses an penetrate gas aspirator 3, through the mode of high-pressure compressed air suction low pressure high temperature air, reduce high-pressure compressed air consumption on the one hand, on the other hand is low pressure high temperature air because of the suction, and the high-pressure compressed air temperature that gets into in penetrating gas aspirator 3 has obtained the promotion, has also improved the temperature of the air in the air heater, has reduced air heater power consumption, reduces the unit start-up running cost. Because the heating medium adopted for the high-pressure turbine cylinder 47 is air which is non-condensable gas, the hidden troubles that the water content of the steam turbine oil exceeds the standard and metal parts are rusted and the like because the steam is heated and condensed into water are overcome. The utility model discloses improve temperature attitude, thermal state with the unit from the cold state, make the steam turbine rush to rotate the speed of rise and can rise the load fast after being incorporated into the power networks, reduced the cold state start of steam turbine and promoted the warm jar time of steam turbine high pressure cylinder, avoid long-time low-load warm jar to cause the boiler to throw the oil mass and increase by a wide margin, or throw plasma and cause the consumption by a wide margin of negative and positive pole life-loss and electric quantity. The utility model provides a pair of large-scale steam turbine high pressure cylinder following current heating method has generating set cold starting cost-saving, heats characteristics such as quick, reduction loss, quick adaptation electric wire netting power regulation dispatch.
The above description is only for the specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention should be covered by the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (7)
1. The utility model provides a large-scale steam turbine high pressure cylinder cocurrent heating system which characterized in that: the jet nozzle of the jet air exhauster is sequentially connected with the oil-water separator, the steam-water separator, the air heater and the hot air header, the hot air header is connected with a pipeline between a high-pressure cylinder regulating valve of a steam turbine and a main steam valve of the steam turbine, a high-pressure cylinder hot air inlet regulating valve is arranged on the pipeline connected with the steam turbine, a suction opening of the jet air exhauster is connected with an exhaust pipe of a high-pressure cylinder of the steam turbine, and a return air regulating valve is arranged on the pipeline connected with the steam turbine.
2. The large steam turbine high pressure cylinder concurrent heating system according to claim 1, wherein: the number of the air heaters is more than two, and the air heaters are operated in series or in parallel.
3. The large steam turbine high pressure cylinder concurrent heating system according to claim 1, wherein: the oil-water separator is connected with the steam-water separator in series, an oil-water separator front stop valve is arranged between the oil-water separator and the air injection air extractor, and a steam-water separator rear stop valve is arranged between the steam-water separator and the air heater.
4. The large steam turbine high pressure cylinder concurrent heating system according to claim 3, wherein: the oil-water separator front stop valve, the oil-water separator, the steam-water separator and the steam-water separator rear stop valve which are connected in sequence form an oil-steam-water separation mechanism, and the oil-steam-water separation mechanism is multiple and connected in parallel between the air injection air extractor and the air heater.
5. The large steam turbine high pressure cylinder concurrent heating system according to claim 1, wherein: and the hot air header is provided with a safety valve, an exhaust valve, a pressure measuring device, a temperature measuring device and a blow-down door of the hot air header.
6. The large steam turbine high pressure cylinder concurrent heating system according to claim 1, wherein: and a drain tank and an air exhaust valve are arranged between the air return regulating valve and the high-pressure cylinder on a pipeline connecting the air jet air ejector and the steam turbine, and an air return pollution discharge door is arranged on the drain tank.
7. The large steam turbine high pressure cylinder concurrent heating system according to claim 1, wherein: and a compressed air joint of the air jet ejector is connected with a compressed air main pipe, and the compressed air main pipe is provided with a compressed air main pipe air supply regulating valve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201921829478.XU CN211058872U (en) | 2019-10-29 | 2019-10-29 | Large-scale steam turbine high-pressure cylinder concurrent flow heating system |
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|---|---|---|---|
| CN201921829478.XU CN211058872U (en) | 2019-10-29 | 2019-10-29 | Large-scale steam turbine high-pressure cylinder concurrent flow heating system |
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| CN211058872U true CN211058872U (en) | 2020-07-21 |
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| CN201921829478.XU Active CN211058872U (en) | 2019-10-29 | 2019-10-29 | Large-scale steam turbine high-pressure cylinder concurrent flow heating system |
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