CN218510856U - Decompression-adjusted steam-gas co-production high-parameter industrial steam supply system - Google Patents
Decompression-adjusted steam-gas co-production high-parameter industrial steam supply system Download PDFInfo
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- CN218510856U CN218510856U CN202222367570.7U CN202222367570U CN218510856U CN 218510856 U CN218510856 U CN 218510856U CN 202222367570 U CN202222367570 U CN 202222367570U CN 218510856 U CN218510856 U CN 218510856U
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Abstract
The utility model discloses a vapour-gas coproduction high parameter industry steam supply system that decompression was adjusted. The utility model discloses at first draw forth high temperature feedwater all the way from the boiler feedwater, reduce pressure to the wet steam or the high temperature feedwater of required pressure through the relief pressure valve, then main steam becomes required high pressure saturated steam with wet steam or high temperature feedwater heating, utilizes high temperature reheat steam to heat the saturated steam for required high pressure superheated steam supplies as high pressure steam for the high pressure to go out at last. The reheated steam after the cooling drives the back pressure steam turbine again and drives the air compressor machine and prepare compressed air, satisfies the daily compressed air of power plant and uses, reduces air compressor machine power consumption. The utility model discloses promoted cogeneration unit high parameter industry by a wide margin and supplied vapour ability, can prepare compressed air simultaneously, reduced the station service power rate, realized the cogeneration of heat and electricity poly-generation, further improved cogeneration economic benefits.
Description
Technical Field
The utility model relates to an industry supplies vapour technical field, especially relates to a vapour-gas coproduction high parameter industry that decompression was adjusted supplies vapour system.
Background
The high-temperature high-pressure steam is one of raw materials required by production processes in various industries, and particularly the high-parameter steam with the pressure of more than 4MPa is required in the industries such as chemical industry, petroleum industry and the like. The conventional proposal is that a small-scale steam boiler is built by a steam enterprise for production. At present, related policies of China and places require accelerating the development of cogeneration and centralized heat supply, the existing cogeneration units, the pure condensing generator sets and the low-grade waste heat around cities and industrial parks are utilized to implement heat supply transformation, coal-fired boilers in the heat supply and steam supply range are eliminated, self-built boilers of enterprises are greatly limited by the policies, and a large number of steam-using enterprises change from self-production steam supply to steam supply of large cogeneration units.
However, at present, a relatively mature scheme for high-parameter industrial steam supply with the pressure of more than 4MPa does not exist, and the scheme of main steam supply, steam supply through a steam supplementing valve and the like is adopted conventionally, but the problem of relatively small steam extraction amount exists due to the limitation of the overtemperature of a boiler reheater. For a thermal power plant, a large amount of meters and equipment exist in the production process, and the meters and the equipment can be driven by high-pressure compressed air to normally operate. The conventional air compressor is driven by a motor, and a power supply is taken from a station service power system. Because the compressed air consumption of the whole plant is huge, the power consumption load of the air compressor is high, a large amount of precious electric energy needs to be consumed, the power consumption of the on-line power is reduced, the power consumption of the plant is increased, and the operational income is reduced.
SUMMERY OF THE UTILITY MODEL
The present invention aims at solving at least one of the technical problems in the related art to a certain extent.
Therefore, the embodiment of the utility model provides a vapour-gas coproduction high parameter industry steam supply system that decompression was adjusted.
The utility model provides a vapour-gas coproduction high parameter industry steam supply system that decompression was adjusted, include:
the heat exchanger comprises a first-stage heat exchanger, a first heat exchanger and a second heat exchanger, wherein a cold side inlet of the first-stage heat exchanger is connected with an outlet of a high-pressure heater, a pipeline between the high-pressure heater and the cold side inlet of the first-stage heat exchanger is provided with a pressure reducing valve, a hot side inlet of the first-stage heat exchanger is connected with a main steam extraction pipeline of a boiler, and a hot side outlet of the first-stage heat exchanger is connected with an inlet of a deaerator;
the secondary heat exchanger is arranged at the downstream of the first-stage heat exchanger, a cold side inlet of the secondary heat exchanger is connected with a cold side outlet of the first-stage heat exchanger, a cold side outlet of the secondary heat exchanger is connected with a high-pressure industrial steam supply system, a hot side inlet of the secondary heat exchanger is connected with a reheat steam extraction pipeline of the boiler, and a hot side outlet of the secondary heat exchanger is connected with a steam inlet of a backpressure steam turbine;
the steam outlet of the back pressure steam turbine is connected with the inlet of the low pressure cylinder, the output shaft end of the back pressure steam turbine is connected with the gear box coupler, the output shaft end of the gear box coupler is connected with the overrunning clutch, the output shaft end of the overrunning clutch is connected with the motor, and the output shaft end of the motor is connected with the air compressor.
In some embodiments, the first path of condensed water on the cold side of the first-stage heat exchanger is heated to be saturated steam through the first path of main steam, the saturated steam is introduced into the second-stage heat exchanger and then heated to be superheated steam with a certain temperature through the first path of reheat steam, the condensed water after the heat exchange of the first path of main steam returns to the inlet of the deaerator through a pipeline, and the first path of reheated steam enters the back pressure turbine to do work to drive the air compressor to operate so as to produce compressed air after the heat exchange of the first path of reheat steam.
In some embodiments, the motor is electrically connected to an auxiliary power system, and when the back pressure turbine has a surplus power, the motor converts the surplus power output by the back pressure turbine into electric energy to supply to the auxiliary power system; when the output of the back pressure turbine is insufficient, the motor gets power from the service power system, and the back pressure turbine and the motor drive the air compressor together.
In some embodiments, a first valve is arranged on a pipeline between the pressure reducing valve and the outlet of the high-pressure heater, a second valve is arranged on a pipeline between the hot side outlet of the first-stage heat exchanger and the inlet of the deaerator, a third valve is arranged on a pipeline between the cold side outlet of the second-stage heat exchanger and the high-pressure industrial steam supply system, a fourth valve and a first valve group are arranged on a pipeline between the hot side outlet of the second-stage heat exchanger and the inlet of the back pressure turbine, the first valve group is arranged close to the back pressure turbine, and a fifth valve is arranged on a pipeline between the outlet of the back pressure turbine and the inlet of the low pressure cylinder.
In some embodiments, a second valve set is arranged on a pipeline between the hot side inlet of the first-stage heat exchanger and the main steam extraction pipeline, and a third valve set is arranged on a pipeline between the hot side inlet of the second-stage heat exchanger and the reheat steam extraction pipeline.
In some embodiments, the low-pressure cylinder exhaust steam enters a condenser to be condensed into condensed water, the condensed water is divided into two paths after passing through a condensed water pump, a low-pressure heater, the deaerator, a water supply pump and the high-pressure heater in sequence, the first path of condensed water enters a cold-side inlet of the first-stage heat exchanger after passing through the first valve and the pressure reducing valve, and the second path of condensed water enters the boiler to be heated into main steam.
In some embodiments, the main steam at the outlet of the boiler is divided into two paths, the first path of main steam enters the first-stage heat exchanger through the hot-side inlet of the first-stage heat exchanger, and the second path of main steam enters the high-pressure cylinder to do work.
In some embodiments, the exhaust steam of the high-pressure cylinder enters the boiler again for secondary heating, the reheat steam at the outlet of the boiler is divided into two paths, the first path of reheat steam enters the second-stage heat exchanger through the hot-side inlet of the second-stage heat exchanger, and the second path of reheat steam enters the intermediate-pressure cylinder for doing work.
In some embodiments, the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder to do work, and a butterfly valve is arranged on a pipeline between the outlet of the intermediate pressure cylinder and the inlet of the low pressure cylinder.
In some embodiments, the first path of condensed water is decompressed into wet steam or high-temperature feed water with a certain pressure through the pressure reducing valve.
Compared with the prior art, the beneficial effects of the utility model are that:
the utility model discloses an through the two-stage heat transfer, utilize main steam and reheat steam to heat the boiler feed water after the decompression in proper order respectively, through using boiler outlet steam as the heat source, solved because of the boiler reheater overtemperature limit, the problem of the high parameter industry steam supply ability of the limited influence of superheated steam extraction volume.
The utility model discloses at first draw forth high temperature feedwater all the way from the boiler feedwater, reduce pressure to the wet steam or the high temperature feedwater of required pressure through the relief pressure valve, then main steam becomes required high pressure saturated steam with wet steam or high temperature feedwater heating, utilizes high temperature reheat steam to heat the saturated steam for required high pressure superheated steam supplies as high pressure steam for the high pressure to go out at last. The reheated steam after the cooling drives the back pressure steam turbine again and drives the air compressor machine and prepare compressed air, satisfies the daily compressed air of power plant and uses, reduces air compressor machine power consumption. The utility model discloses promoted cogeneration unit high parameter industry by a wide margin and supplied vapour ability, can prepare compressed air simultaneously, reduced the station service power rate, realized the cogeneration of heat and electricity poly-generation, further improved cogeneration economic benefits.
The utility model discloses can reduce the air compressor machine power consumption rate of whole factory, the power system can be supplied with to the multiple electric quantity, increases the electric quantity of surfing the net, improves unit operation economy.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 is a schematic view of a pressure-reducing regulated steam-gas co-production high-parameter industrial steam supply system of the present invention;
description of reference numerals:
1. a boiler; 2. a high pressure cylinder; 3. an intermediate pressure cylinder; 4. a low pressure cylinder; 5. a high pressure heater; 6. a deaerator; 7. a feed pump; 8. a low-pressure heater; 9. a condensate pump; 10. a condenser; 11. a butterfly valve; 12. a first valve; 13. a second valve group; 14. a second valve; 15. a third valve group; 16. a fifth valve; 17. a pressure reducing valve; 18. a first stage heat exchanger; 19. a second stage heat exchanger; 20. a back pressure turbine; 21. a gearbox coupling; 22. an overrunning clutch; 23. an electric motor; 24. an air compressor; 25. a fourth valve; 26. a third valve; 27. a first valve group; 28. a high pressure industrial steam supply system; 29. a main steam extraction pipeline; 30. a reheat steam extraction line; 31. and a service power system.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention.
The pressure-reducing regulated steam-gas cogeneration high-parameter industrial steam supply system according to an embodiment of the present invention is described below with reference to the accompanying drawings.
As shown in fig. 1, the utility model discloses a vapour-gas cogeneration high parameter industry steam supply system that decompression was adjusted, including first order heat exchanger 18, second level heat exchanger 19, backpressure steam turbine 20, boiler 1 and low pressure cylinder 4.
The discharged steam of the low-pressure cylinder 4 enters a condenser 10 to be condensed into condensed water, the condensed water is divided into two paths after sequentially passing through a condensed water pump 9, a low-pressure heater 8, a deaerator 6, a water feeding pump 7 and a high-pressure heater 5, the first path of condensed water enters a cold side inlet of a first-stage heat exchanger 18 after passing through a first valve 12 and a pressure reducing valve 17, and the second path of condensed water enters a boiler 1 to be heated into high-temperature main steam.
Specifically, the discharged steam of a low-pressure cylinder 4 enters a condenser 10 through a steam discharge pipeline, the discharged steam of the low-pressure cylinder 4 is condensed into condensed water in the condenser 10, the outlet end of the condenser 10 is connected with a condensate pump 9, the condensed water enters a low-pressure heater 8 under the action of the condensate pump 9, the outlet end of the low-pressure heater 8 is connected with a deaerator 6, the condensed water is heated in the low-pressure heater 8 and then enters the deaerator 6, the deaerator 6 is used for removing oxygen in the condensed water to ensure the quality of the condensed water, the outlet end of the deaerator 6 is connected with a water feed pump 7, the outlet end of the water feed pump 7 is connected with a high-pressure heater 5, the condensed water enters the high-pressure heater 5 after being pressurized by the water feed pump 7, the condensed water flows out of the high-pressure heater 5 and then is divided into two paths, the first path of condensed water is depressurized to a required pressure under the action of a pressure reducing valve 17 after passing through a first valve 12, and the depressurized first path of condensed water enters a first-stage heat exchanger 18 from a cold-side inlet of the first-stage heat exchanger 18; the second path of condensed water enters the boiler 1 for heating, and the second path of condensed water is heated into high-temperature main steam in the boiler 1. Wherein, the exit end of the feed pump 7 is connected with the high pressure heater 5, the exit end of the high pressure heater 5 is connected with the boiler 1, and the first valve 12 is arranged on the pipeline between the pressure reducing valve 17 and the exit of the high pressure heater 5, it can be understood that the flow of the first path of condensed water can be adjusted by adjusting the first valve 12.
The main steam at the outlet of the boiler 1 is divided into two paths, the first path of main steam enters the first-stage heat exchanger 18 through the hot side inlet of the first-stage heat exchanger 18, and the second path of main steam enters the high-pressure cylinder 2 to do work.
Specifically, a second valve group 13 is arranged on a pipeline between a hot side inlet of the first-stage heat exchanger 18 and the main steam extraction pipeline 29, the first path of main steam serving as a heat source enters the hot side inlet of the first-stage heat exchanger 18 after passing through the second valve group 13, the first path of main steam after heat exchange is condensed and then returns to the deaerator 6 through a second valve 14, and the second valve 14 is arranged on the pipeline between the hot side outlet of the first-stage heat exchanger 18 and the inlet of the deaerator 6, so that the flow of the first path of main steam can be adjusted by adjusting the second valve group 13; and the second path of main steam enters the high-pressure cylinder 2 from the inlet end of the high-pressure cylinder 2 to do work.
The exhausted steam of the high-pressure cylinder 2 enters the boiler 1 again for secondary heating, the reheat steam at the outlet of the boiler 1 is divided into two paths, the first path of reheat steam enters the second-stage heat exchanger 19 through the hot side inlet of the second-stage heat exchanger 19, and the second path of reheat steam enters the intermediate-pressure cylinder 3 for doing work.
Specifically, the second path of main steam enters the high pressure cylinder 2 to do work, then is exhaust steam of the high pressure cylinder 2 and is exhausted from the outlet end of the high pressure cylinder 2, the exhaust steam of the high pressure cylinder 2 enters the boiler 1 again to be heated for the second time, the exhaust steam of the high pressure cylinder 2 is heated to become reheat steam and is exhausted from the outlet of the boiler 1, the reheat steam at the outlet of the boiler 1 is divided into two paths, wherein the first path of reheat steam is used as a heat source and enters the second-stage heat exchanger 19 through the hot side inlet of the second-stage heat exchanger 19, and the first path of reheat steam after heat exchange enters the backpressure steam turbine 20 to do work; the second path of reheated steam enters the intermediate pressure cylinder 3 to do work, and the exhaust steam of the intermediate pressure cylinder 3 enters the low pressure cylinder 4 to do work through the butterfly valve 11. Wherein, a third valve group 15 is arranged on a pipeline between a hot side inlet of the second-stage heat exchanger 19 and the hot re-extraction pipeline, a fourth valve 25 and a first valve group 27 are arranged on a pipeline between a hot side outlet of the second-stage heat exchanger 19 and an inlet of the backpressure steam turbine 20, the first valve group 27 is arranged close to the backpressure steam turbine 20, and the butterfly valve 11 is arranged on a pipeline between an outlet of the intermediate pressure cylinder 3 and an inlet of the low pressure cylinder 4.
A cold side inlet of the first-stage heat exchanger 18 is connected with an outlet of the deaerator 6, a pressure reducing valve 17 is arranged on a pipeline between the high-pressure heater 5 and the cold side inlet of the first-stage heat exchanger 18, a hot side inlet of the first-stage heat exchanger 18 is connected with a main steam extraction pipeline 29 of the boiler 1, and a hot side outlet of the first-stage heat exchanger 18 is connected with an inlet of the deaerator 6.
Specifically, the first path of condensed water at the outlet of the high-pressure heater 5 is decompressed by a decompression valve 17 and then enters the first-stage heat exchanger 18 from the cold side inlet of the first-stage heat exchanger 18, the first path of main steam enters the first-stage heat exchanger 18 from the hot side of the first-stage heat exchanger 18, the first path of main steam serves as a heat source to heat the first path of condensed water, the first path of condensed water at the cold side of the first-stage heat exchanger 18 is heated by the first path of main steam to be saturated steam, and the first path of condensed water after heat exchange of the main steam is condensed to be condensed water and then flows out from the hot side outlet of the first-stage heat exchanger 18 and then enters the deaerator 6. The first path of condensed water is decompressed into wet steam or high-temperature feed water with certain pressure through a pressure reducing valve 17.
And a cold side inlet of the second-stage heat exchanger 19 is connected with a cold side outlet of the first-stage heat exchanger 18, a cold side outlet of the second-stage heat exchanger 19 is connected with a high-pressure industrial steam supply system 28, a hot side inlet of the second-stage heat exchanger 19 is connected with a reheated steam extraction pipeline 30 of the boiler 1, and a hot side outlet of the second-stage heat exchanger 19 is connected with a steam inlet of the backpressure steam turbine 20.
Specifically, the second-stage heat exchanger 19 is arranged at the downstream of the first-stage heat exchanger 18, a cold-side inlet of the second-stage heat exchanger 19 is connected with a cold-side outlet of the first-stage heat exchanger 18, saturated steam flows out from the cold-side outlet of the first-stage heat exchanger 18 and then enters the second-stage heat exchanger 19 from the cold-side inlet of the second-stage heat exchanger 19, the first path of reheat steam enters the second-stage heat exchanger 19 from a hot-side inlet of the second-stage heat exchanger 19 through the third valve group 15 to heat the saturated steam, the saturated steam is heated to superheated steam with a certain temperature in the second-stage heat exchanger 19, the superheated steam flows out from the cold-side outlet of the second-stage heat exchanger 19 and is supplied to the high-pressure industrial steam supply system 28 through the third valve 26, the first path of reheat steam after heat exchange sequentially passes through the fourth valve 25 and the first valve group 27 to enter the back pressure steam turbine 20 to do work, and the back pressure steam turbine 20 drives the air compressor 24 to operate to prepare compressed air.
The steam outlet of the backpressure steam turbine 20 is connected with the inlet of the low pressure cylinder 4, the output shaft end of the backpressure steam turbine 20 is connected with a gear box coupler 21, the output shaft end of the gear box coupler 21 is connected with an overrunning clutch 22, the output shaft end of the overrunning clutch 22 is connected with a motor 23, and the output shaft end of the motor 23 is connected with an air compressor 24.
Specifically, a fifth valve 16 is arranged on a pipeline between an outlet of the back pressure turbine 20 and an inlet of the low pressure cylinder 4, after steam discharged from the back pressure turbine 20 passes through the fifth valve 16, the steam finally enters the low pressure cylinder 4 through a butterfly valve 11 to do work, an output shaft end of the back pressure turbine 20 is connected with a gear box coupler 21, an output shaft end of a wheel box and a coupler is connected with an overrunning clutch 22, an output shaft end of the overrunning clutch 22 is connected with a motor 23, an output shaft end of the motor 23 is connected with an air compressor 24, so that the back pressure turbine 20 can drive the air compressor 24 to operate, and the air compressor 24 can be driven by steam and electricity.
The motor 23 is electrically connected with the service system 31, and when the back pressure turbine 20 has excess power, the motor 23 converts the excess power output by the back pressure turbine 20 into electric energy to supply to the service system 31; when the output of the back pressure turbine 20 is insufficient, the motor 23 takes power from the service power system 31, and the back pressure turbine 20 and the motor 23 drive the air compressor 24 together.
Specifically, a steam source of the back pressure steam turbine 20 is the first path of reheated steam after the temperature of the second-stage heat exchanger 19 of the unit is reduced, the back pressure steam turbine 20 simultaneously drives the motor 23 and the air compressor 24 to operate, and the back pressure steam turbine 20 bears the power consumption of the motor 23, so that the power consumption of the air compressor 24 system is reduced. When the back pressure turbine 20 is in a power-generating state, the motor 23 automatically changes the power output by the back pressure turbine 20 into electric energy to supply the electric energy to the plant power system 31. When the output of the back pressure turbine 20 is not enough to meet the working requirement of the air compressor 24, the back pressure turbine 20 and the motor 23 jointly drag the air compressor 24 to work, the motor 23 becomes in a power consumption state, the power is taken from the service power system 31, and the rest of the power consumption of the air compressor 24 is shared, so that the power consumption of the air compressor 24 is reduced. When the back pressure turbine 20 is in failure, the operation is disconnected and quitted, and the air compressor 24 is driven to operate by the motor 23 completely.
The utility model discloses a vapour-gas coproduction high parameter industry of decompression regulation supplies vapour system's operational mode specifically as follows.
When the unit starts to supply heat and extract steam, the first valve 12 and the pressure reducing valve 17 are opened, the pressure reducing valve 17 is utilized to reduce the pressure of the first path of condensed water at the outlet of the high-pressure heater 5 to wet steam or high-temperature feed water with required pressure, and the reduced first path of condensed water enters the cold side of the first-stage heat exchanger 18. The first path of main steam enters a first-stage heat exchanger 18 to exchange heat with wet steam or high-temperature feed water obtained after the pressure of the first path of condensed water is reduced, the wet steam or the high-temperature feed water at the outlet end of a pressure reducing valve 17 is heated into saturated steam, the first path of main steam is condensed into condensed water and returns to the inlet of a deaerator 6, and the saturated steam at the outlet of the first-stage heat exchanger 18 enters the cold side of a second-stage heat exchanger 19.
And the second path of main steam enters the high-pressure cylinder 2 from the inlet end of the high-pressure cylinder 2 to do work. The exhausted steam of the high-pressure cylinder 2 enters the boiler 1 again for secondary heating, the reheated steam at the outlet of the boiler 1 is divided into two paths, the first path of reheated steam enters the second-stage heat exchanger 19 to exchange heat with the saturated steam at the outlet of the first-stage heat exchanger 18, the saturated steam at the outlet of the first-stage heat exchanger 18 is heated to the superheated steam with the required temperature and then enters the high-pressure industrial steam supply system 28, and the first path of reheated steam in the second-stage heat exchanger 19 is cooled and then enters the backpressure steam turbine 20 to drive the backpressure steam turbine to do work. The second path of reheated steam enters the intermediate pressure cylinder 3 to do work, and the exhaust steam of the intermediate pressure cylinder 3 enters the low pressure cylinder 4 to do work through the butterfly valve 11.
The back pressure turbine 20 is connected with the motor 23 through the gear box coupler 21 and the overrunning clutch 22, the motor 23 is driven to operate together, the electric output end of the motor 23 is connected to the auxiliary power system 31, when the back pressure turbine 20 has output force which is surplus except for driving the air compressor 24 to operate, the motor 23 automatically becomes a power generation state at the moment, surplus power output by the back pressure turbine 20 is converted into electric energy, and the electric energy is supplied to the auxiliary power system 31 of the unit and is used for supplying to auxiliary machines in a plant; when the output force of the back pressure turbine 20 is insufficient, the motor 23 automatically becomes a power consumption state at the moment, power is supplied from the service power system 31 to supplement the residual power consumption required by the air compressor 24, the air compressor 24 is driven to operate together with the back pressure turbine 20, and the exhaust steam which is finished by the back pressure turbine 20 enters the low pressure cylinder 4; when the back pressure turbine 20 breaks down, the back pressure turbine 20 is disconnected from the system, the motor 23 of the air compressor 24 automatically becomes in a power consumption state, power is supplied from the auxiliary power system 31, and the air compressor 24 is driven to operate independently.
Compared with the conventional scheme, the utility model greatly improves the steam supply capacity of the high-parameter industry of the unit by more than 4MPa by more than one time, and enlarges the cogeneration capacity; the utility model utilizes the residual pressure power-applying capacity of heat supply steam extraction, realizes the steam step utilization, and improves the energy utilization efficiency; the utility model discloses can reduce whole factory's air compressor machine power consumption, the power system of station service can be supplied with to the multiple electric quantity, increases the online electric quantity, improves unit operation economy.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms may be directed to different embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or to implicitly indicate the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.
While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (10)
1. A pressure-reducing regulated steam-gas co-production high-parameter industrial steam supply system is characterized by comprising:
the heat exchanger comprises a first-stage heat exchanger, a first heat exchanger and a second heat exchanger, wherein a cold side inlet of the first-stage heat exchanger is connected with an outlet of a high-pressure heater, a pipeline between the high-pressure heater and the cold side inlet of the first-stage heat exchanger is provided with a pressure reducing valve, a hot side inlet of the first-stage heat exchanger is connected with a main steam extraction pipeline of a boiler, and a hot side outlet of the first-stage heat exchanger is connected with an inlet of a deaerator;
the cold side inlet of the second-stage heat exchanger is connected with the cold side outlet of the first-stage heat exchanger, the cold side outlet of the second-stage heat exchanger is connected with a high-pressure industrial steam supply system, the hot side inlet of the second-stage heat exchanger is connected with a reheat steam extraction pipeline of the boiler, and the hot side outlet of the second-stage heat exchanger is connected with a steam inlet of a backpressure steam turbine;
the steam outlet of the back pressure steam turbine is connected with the inlet of the low pressure cylinder, the output shaft end of the back pressure steam turbine is connected with the gear box coupler, the output shaft end of the gear box coupler is connected with the overrunning clutch, the output shaft end of the overrunning clutch is connected with the motor, and the output shaft end of the motor is connected with the air compressor.
2. The system of claim 1, wherein a first path of condensed water on the cold side of the first stage heat exchanger is heated into saturated steam through a first path of main steam, the saturated steam is heated into superheated steam with a certain temperature through a first path of reheat steam after being introduced into the second stage heat exchanger, the condensed water after heat exchange of the first path of main steam returns to an inlet of the deaerator through a pipeline, and the first path of reheat steam enters the backpressure steam turbine after heat exchange of the first path of reheat steam to do work to drive the air compressor to operate to produce compressed air.
3. The system of claim 1, wherein the motor is electrically connected to a utility power system, and when the back pressure turbine is outputting excess power, the motor converts the excess power output by the back pressure turbine into electrical energy to supply the utility power system; when the output of the back pressure turbine is insufficient, the motor gets power from the station service system, and the back pressure turbine and the motor drive the air compressor together.
4. The system of claim 2, wherein a first valve is disposed on a pipeline between the pressure reducing valve and the outlet of the high pressure heater, a second valve is disposed on a pipeline between the outlet of the hot side of the first stage heat exchanger and the inlet of the deaerator, a third valve is disposed on a pipeline between the outlet of the cold side of the second stage heat exchanger and the high pressure industrial steam supply system, a fourth valve and a first valve group are disposed on a pipeline between the outlet of the hot side of the second stage heat exchanger and the inlet of the back pressure turbine, the first valve group is disposed adjacent to the back pressure turbine, and a fifth valve is disposed on a pipeline between the outlet of the back pressure turbine and the inlet of the low pressure cylinder.
5. The system of claim 1, wherein a second set of valves is provided in a line between the hot side inlet of the first stage heat exchanger and the main steam extraction conduit, and a third set of valves is provided in a line between the hot side inlet of the second stage heat exchanger and the reheat steam extraction conduit.
6. The system of claim 4, wherein the low-pressure cylinder exhaust steam enters a condenser to be condensed into condensed water, the condensed water is divided into two paths after passing through a condensed water pump, a low-pressure heater, a deaerator, a water feeding pump and a high-pressure heater in sequence, the first path of condensed water enters a cold-side inlet of the first-stage heat exchanger after passing through the first valve and the pressure reducing valve, and the second path of condensed water enters the boiler to be heated into main steam.
7. The system of claim 6, wherein the main steam at the outlet of the boiler is divided into two paths, the first path of main steam enters the first-stage heat exchanger through the hot-side inlet of the first-stage heat exchanger, and the second path of main steam enters the high-pressure cylinder to do work.
8. The system of claim 7, wherein the exhaust steam of the high pressure cylinder enters the boiler again for secondary heating, the reheat steam at the outlet of the boiler is divided into two paths, the first path of reheat steam enters the second stage heat exchanger through the hot side inlet of the second stage heat exchanger, and the second path of reheat steam enters the intermediate pressure cylinder for doing work.
9. The system of claim 8, wherein the exhaust steam from the intermediate pressure cylinder enters the low pressure cylinder to perform work, and a butterfly valve is disposed in a line between the outlet of the intermediate pressure cylinder and the inlet of the low pressure cylinder.
10. The system of claim 6, wherein the first path of condensed water is decompressed into wet steam or high-temperature feed water with a certain pressure through the decompression valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222367570.7U CN218510856U (en) | 2022-09-06 | 2022-09-06 | Decompression-adjusted steam-gas co-production high-parameter industrial steam supply system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222367570.7U CN218510856U (en) | 2022-09-06 | 2022-09-06 | Decompression-adjusted steam-gas co-production high-parameter industrial steam supply system |
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