System and method for stabilizing pressure and recycling waste heat of generator set

Abstract

The invention discloses a generator set pressure stabilizing and waste heat recycling system and method. Medium-pressure bled steam of a steam turbine communicates with a first steam heat accumulator through a pipeline, and low-pressure bled steam of the steam turbine communicates with a second steam heat accumulator through a pipeline; wherein the first steam heat accumulator supplies heat to a first steam user, and a working medium subjected to heat supply enters the condensate water recovery system; wherein the second steam heat accumulator supplies heat to a second steam user, and a working medium subjected to heat exchange also enters the condensate water recovery system; condensate water in the condensate water recovery system enters the flue gas heat exchanger through a pipeline for heat exchange, and after the heated condensate water is desalted, the condensate water is supplemented into a water system of the boiler through a pipeline. According to the system, fluctuation of steam pressure of the steam turbine and the boiler is reduced, the adaptive capacity of the back extraction steam turbine to the steam pressure is enhanced, meanwhile, waste heat utilization of boiler flue gas and steam user condensate water is achieved, and the utilization rate of heat energy is increased.

Description

Technical Field

[0001] The present invention relates to the technical field of waste heat utilization of power generation systems, and in particular to a system and method for stabilizing pressure and recovering waste heat of a power generation unit. Background Art

[0002] An extraction back-pressure steam turbine is one that extracts part of the steam from the middle stage of the turbine to supply heat users that require a higher pressure level, while maintaining a certain back pressure to exhaust steam for heat users that require a lower pressure level. This type of unit has the characteristics of simple structure, large heat supply, and good design operating economy, and is widely used in steel and chemical companies.

[0003] Because the pumped-back steam turbine has no condenser, the unit has poor adaptability to load changes and is easily affected by the steam user's usage during operation, causing large fluctuations in the unit's steam pressure and power generation load, which in turn leads to problems such as increased unit vibration and power reduction, affecting the safe operation and unit performance of the pumped-back steam turbine. Since there is no condenser, the steam condensate cannot be recovered. After the steam is sent out for use by steam users, the condensate is generally used as industrial water, and the heat utilization rate of the condensate is low, resulting in a low waste heat recovery rate in the system. Summary of the invention

[0004] The purpose of the present invention is to provide a system and method for stabilizing the pressure of a generator set and recovering waste heat, so as to solve the problem of how to improve the operating stability of a back-drawn steam turbine and the recovery rate of waste heat.

[0005] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0006] The present invention provides a generator set pressure stabilization and waste heat recovery system, including a boiler, a steam turbine, and a generator;

[0007] A flue gas heat exchanger is provided on the flue gas exhaust pipeline of the boiler;

[0008] The medium-pressure spent steam of the steam turbine is connected to the first steam accumulator through a pipeline, and the low-pressure spent steam of the steam turbine is connected to the second steam accumulator through a pipeline;

[0009] The first steam accumulator supplies heat to the first steam user, and the working medium after heat supply enters the condensate recovery system; the second steam accumulator supplies heat to the second steam user, and the working medium after heat exchange also enters the condensate recovery system;

[0010] The condensed water in the condensed water recovery system enters the flue gas heat exchanger through a pipeline for heat exchange, and the heated condensed water is desalinated and then replenished into the water system of the boiler through a pipeline.

[0011] Furthermore, the main steam in the boiler is directly connected to the first steam accumulator via a bypass pipeline, and a first temperature and pressure reducer is provided on the bypass pipeline.

[0012] Furthermore, the low-pressure steam discharged from the first steam accumulator enters the second steam accumulator after passing through a second temperature and pressure reducing device.

[0013] Furthermore, the second steam accumulator also transports steam to the seawater desalination component through pipes, and the desalted water produced by the seawater desalination component is replenished into the water system of the boiler.

[0014] Furthermore, the condensed water in the condensed water recovery system is transported to the flash evaporation assembly through pipes, and the steam produced by the flash evaporation assembly is transported to the seawater desalination assembly, wherein the cooling water after heat exchange in the seawater desalination assembly is transported to the flue gas heat exchanger for heat exchange;

[0015] The condensed water in the condensed water recovery system is also transported to the heating station through pipes.

[0016] Furthermore, the condensed water recovery system supplies heat to the heating station, and the working fluid of the heating station after heat exchange is also connected to the water inlet end of the flue gas heat exchanger through a pipe with a valve.

[0017] Furthermore, the water that has undergone heat exchange in the flue gas heat exchanger flows back to the condensed water recovery system.

[0018] The present embodiment discloses a method for stabilizing the pressure and recovering waste heat of a generator set. When the steam consumption of a steam user increases or decreases suddenly, causing a large fluctuation in the steam pressure, the internal water levels of the first steam accumulator and the second steam accumulator are adjusted. The steam accumulator has a pressure buffering function, which is used to reduce the fluctuation of the steam pressure, so as to avoid the problem of increased vibration and power reduction of the steam turbine caused by the large fluctuation of the steam pressure, thereby ensuring the safe and stable operation of the back-type steam turbine.

[0019] Furthermore, when heating is needed, the working fluid outlet of the condensate recovery system is connected to the hot water inlet of the heating station to provide heat for the heating station; the working fluid discharged from the heating station is transported to the flue gas heat exchanger through a pipeline for heat exchange, and flows back to the condensate recovery system; wherein the condensate recovery system also continuously receives condensate generated after the first steam user and the second steam user use steam; thereby preheating the waste heat of the steam used by the first steam user and the second steam user and the flue gas obtained by the flue gas heat exchanger to continuously provide heating for the heating station.

[0020] Furthermore, when seawater desalination is required, the steam from the second steam accumulator and the steam produced by the flash assembly are used to heat the seawater desalination assembly, wherein the smoke-free water produced by the seawater desalination assembly is supplemented to the water system of the boiler;

[0021] The working fluid of the flash evaporation component comes from the condensate recovery system; the steam generated by the flash evaporation component is transported to the seawater desalination component for heating, and after condensation, the steam is transported to the flue gas heat exchanger for heat exchange and finally flows back to the condensate recovery system.

[0022] Compared with the prior art, the beneficial technical effects of the present invention are:

[0023] In the present invention, after the boiler flue gas passes through the flue gas heat exchanger, the heat of the boiler flue gas can be transferred to the cooling medium. Since the cooling medium outlet of the flue gas heat exchanger is connected to the hot water inlet of the heating station, the heated cooling medium can be used as a heat source for the heating station, so that the heating station can provide heating to users, thereby realizing the utilization of the thermal energy of the boiler flue gas.

[0024] The steam accumulator has a pressure buffering function. When the steam users suddenly increase or decrease their steam usage, causing a large fluctuation in steam pressure, the steam accumulator can adjust the amount of steam entering or outgoing through the steam stored internally to avoid problems such as increased turbine vibration and power reduction caused by large fluctuations in steam pressure, thereby ensuring the safe and stable operation of the back-drawn steam turbine.

[0025] The condensed water formed after the steam from the first steam user and the second steam user is cooled and the hot water at the first cooling water outlet of the flue gas heat exchanger enters the condensed water recovery system. The mixed hot water enters the flash evaporation system to transfer the heat of the hot water to the steam. The steam enters the seawater desalination component and is used as a heat source for seawater desalination, realizing the thermal energy utilization of the mixed hot water. The cooled hot water enters the flue gas heat exchanger to absorb heat again.

[0026] In addition, by adopting the generator set pressure stabilization and waste heat recovery system provided by the present invention, the steam pressure fluctuation range of the back-drawn steam turbine can be narrowed by 80%, the thermal energy utilization rate of the boiler flue gas waste heat within the available range is 90%, the utilization rate of the condensed water heat of the steam user is 90%, and the comprehensive utilization rate of the system waste heat is more than 90%.

[0027] Therefore, the system provided by the present invention reduces the fluctuation of steam pressure of the steam turbine and boiler, enhances the adaptability of the back-drawn steam turbine to steam pressure, and at the same time realizes the waste heat utilization of boiler flue gas and condensed water of steam users, thereby improving the utilization rate of thermal energy. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The present invention will be further described below in conjunction with the accompanying drawings.

[0029] Figure 1 This is a schematic diagram of the structure of a generator set pressure stabilization and waste heat recovery system of this embodiment.

[0030] Explanation of the reference numerals: 1- boiler; 2- flue gas heat exchanger; 3- chimney; 4- steam turbine; 5- generator; 6- first steam accumulator; 7- second steam accumulator; 8- first steam user; 9- second steam user; 10- seawater desalination component; 11- first temperature reducing and pressure reducing device; 12- second temperature reducing and pressure reducing device; 13- flash evaporation component; 14- condensate recovery system; 15- heating station. DETAILED DESCRIPTION

[0031] Example 1

[0032] like Figure 1 As shown, this embodiment provides a system for stabilizing pressure and recovering waste heat of a power generation unit, which includes a flue gas heat exchanger 2 installed on the flue gas channel between the boiler 1 and the chimney 3, a first steam accumulator 6 for receiving steam from the boiler 1 that has been cooled and decompressed and medium-pressure spent steam from the turbine 4, a second steam accumulator 7 for receiving low-pressure spent steam from the turbine 4, and a condensate recovery system 14 for condensing waste heat steam generated at the user end.

[0033] The flue gas inlet of the flue gas heat exchanger 2 is connected to the flue gas duct of the boiler 1, the flue gas outlet of the flue gas heat exchanger 2 is connected to the outside or the chimney 3, and the cooling medium inlet of the flue gas heat exchanger 2 is connected to the external cooling water source.

[0034] The inlet of the first steam accumulator 6 is connected to the steam extraction port of the steam turbine 4, and the outlet of the first steam accumulator 6 is connected to the inlet of the first steam user 8; the inlet of the second steam accumulator 7 is connected to the exhaust port of the steam turbine 4, and the outlet of the second steam accumulator 7 is respectively connected to the inlet of the second steam user 9 and the second steam port of the seawater desalination component 10.

[0035] The exhausted steam outlet of the first steam user 8, the condensed water outlet of the second steam user 9, and the hot water outlet of the flue gas heat exchanger 2 are all connected to the inlet of the condensed water recovery system 14, so that the steam condensed water or exhausted steam of the first steam user 8, the steam condensed water of the second steam user 9, and the hot water at the first cooling water outlet of the flue gas heat exchanger 2 all enter the condensed water recovery system 14; the outlet of the condensed water recovery system 14 is respectively connected to the hot water inlet of the flash component 13 and the hot water inlet of the heating station 15.

[0036] In this embodiment, after the flue gas of the boiler 1 passes through the flue gas heat exchanger 2, the heat of the flue gas of the boiler 1 can be transferred to the cooling medium flowing through the flue gas heat exchanger 2; since the cooling medium outlet of the flue gas heat exchanger 2 is connected to the hot water inlet of the heating station 15, the heated cooling medium can be used as a heat source for the heating station 15, so that the heating station 15 can provide heating to users, thereby realizing the thermal energy utilization of the flue gas of the boiler 1, and the cooled flue gas is discharged into the atmosphere.

[0037] The medium-pressure steam of the steam turbine 4 is extracted and stored in the first steam accumulator 6, and then transported to the first steam user 8 by the first steam accumulator 6; the low-pressure steam exhaust of the steam turbine 4 is stored in the second steam accumulator 7, and then transported to the second steam user 9 by the second steam accumulator 7. The extraction and exhaust of the steam turbine 4 are connected to the steam user through the steam accumulator. The steam accumulator has a pressure buffering function. When the steam user suddenly increases or decreases the use of steam, causing a large fluctuation in steam pressure, the first steam accumulator 6 and the second steam accumulator 7 can adjust the amount of steam entering or sent out through the steam stored inside to avoid problems such as increased vibration and power reduction of the steam turbine 4 caused by large fluctuations in steam pressure, thereby ensuring the safe and stable operation of the extraction steam turbine 4.

[0038] During the heating season, the outlet of the condensed water recovery system 14 is connected to the hot water inlet of the heating station 15 and can be used as a heat source for the heating station 15 .

[0039] In the non-heating season, the hot water in the condensate recovery system 14 enters the flash evaporation component 13 after mixing, and the heat of the hot water is transferred to the steam. The steam is then transported into the seawater desalination component 10 and used as a heat source to desalinate seawater, thereby realizing the thermal energy utilization of the mixed hot water. The cooled hot water enters the flue gas heat exchanger 2 to absorb heat again. Therefore, the system provided in this embodiment reduces the fluctuation of the steam pressure of the steam turbine 4, enhances the adaptability of the back-type steam turbine 4 to the steam pressure, and realizes the waste heat utilization of the flue gas of the boiler 1 and the condensed water of the steam user, thereby improving the utilization rate of thermal energy.

[0040] Example 2

[0041] In this embodiment, the cooling medium in the flue gas heat exchanger 2 can be water, and correspondingly, the heating medium of the heating station 15 is also water. The flue gas heat exchanger 2 belongs to the prior art and can transfer the heat energy in the flue gas to the cooling medium, such as cooling water. The flue gas heat exchanger 2 can also be flexibly selected according to actual needs, and no specific limitation is made here. The first steam accumulator 6 and the second steam accumulator 7 are also a prior art, which is a steam container with water as the heat storage medium. Technical personnel in the field can flexibly select according to needs without specific limitation here.

[0042] In this embodiment, in order to realize the recycling of cooling water in the system and reduce water consumption, the cold water outlet of the heating station 15 can be connected to the cooling medium inlet of the flue gas heat exchanger 2. The water with a temperature of 40°C generated after the heating station 15 supplies heat to the user for heating can be used as the cooling medium in the flue gas heat exchanger 2 and as a carrier to absorb the thermal energy of the flue gas.

[0043] Example 3

[0044] In this embodiment, since the back-drawn steam turbine has no condenser, its ability to adjust steam pressure changes is poor. When the steam consumption of the steam user fluctuates greatly, it is easy to cause the turbine to experience increased vibration, power reduction and other problems, resulting in a decrease in turbine efficiency.

[0045] In order to overcome the above technical problems, in this embodiment, the steam extracted from the steam turbine 4 is stored in the first steam accumulator 6, the steam pressure of the first steam accumulator 6 has an operating range of 3.0-3.8 MPa and a temperature of 250-350°C, and then the steam is transported from the first steam accumulator 6 to the first steam user 8. The exhaust steam from the steam turbine 4 is stored in the second steam accumulator 7, the operating range of the second steam accumulator 7 is 0.5-1.0 MPa and the temperature is 160-200°C, and then the steam is transported from the second steam accumulator 7 to the second steam user 9.

[0046] The steam extraction and exhaust of the steam turbine 4 are connected to the steam user through the steam accumulator. The steam accumulator has a pressure buffering function. When the steam consumption of the steam user increases or decreases suddenly and causes a large fluctuation in steam pressure, the first steam accumulator 6 and the second steam accumulator 7 can alleviate and reduce the fluctuation of steam pressure by adjusting the internal water level, thereby avoiding problems such as increased vibration and power reduction of the steam turbine 4 caused by large fluctuations in steam pressure, thereby ensuring the safe and stable operation of the extraction-back steam turbine 4.

[0047] Example 4

[0048] In this embodiment, in order to further improve the stability of the system, the system includes a steam turbine 4, a generator 5, a first desuperheater 11 and a second desuperheater 12, the steam outlet of the boiler 1 is connected to the steam inlet of the steam turbine 4 and the steam inlet of the first desuperheater 11 through pipelines, the steam outlet of the first desuperheater 11 is connected to the steam inlet of the first heat accumulator 6, the steam inlet of the second desuperheater 12 is connected to the steam outlet of the first heat accumulator 6, the steam outlet of the second desuperheater 12 is connected to the steam inlet of the second heat accumulator 7, and the steam turbine 4 is driven and coordinated with the generator 5. When the steam turbine 4 and the generator 5 are overhauled, the first desuperheater 11 and the second desuperheater 12 can be started to desuperheat and reduce the steam, and transport it to the first heat accumulator 6 and the second heat accumulator 7, so as to meet the use of the first steam user 8 and the second steam user 9, wherein the first desuperheater 11 and the second desuperheater 12 are respectively provided to meet the needs of different users for different steam pressures, which is convenient for arrangement and prevents the centralized arrangement of two desuperheaters on the boiler side.

[0049] In this embodiment, the second steam inlet of the seawater desalination component 10 is connected to the steam outlet of the second heat accumulator 7 for use by the seawater desalination component 10; the specific operation of the steam turbine 4 and the generator 5 and the operation of the first temperature reducing and pressure reducing device 11, the second temperature reducing and pressure reducing device 12 and the seawater desalination component 10 can be flexibly selected according to actual conditions, and are not specifically limited here. The steam turbine 4 and the generator 5 are both prior art, wherein the steam turbine 4 can convert the steam heat energy generated by the boiler 1 into mechanical work. After the steam from the boiler 1 enters the steam turbine 4, it passes through a series of annularly configured nozzles and moving blades in sequence, converting the heat energy of the steam into mechanical energy for the rotation of the turbine rotor.

[0050] Example 5

[0051] In order to further improve the stability of the back-drawn steam turbine, in this embodiment, the exhaust port of the steam turbine 4 is connected to the steam inlet of the second heat accumulator 7. The steam pressure of the exhaust port of the steam turbine 4 is 0.8-1.0MPa, and the steam extraction port of the steam turbine 4 can also be connected to the steam inlet of the first heat accumulator 6, with a steam extraction pressure of 4.0MPa. The steam pressure of the first heat accumulator 6 operates in the range of 3.0-3.8MPa and the temperature is 250-350℃, and the steam pressure of the second heat accumulator 7 operates in the range of 0.5-1.0MPa and the temperature is 160-200℃. The second steam inlet of the seawater desalination component 10 is connected to the steam outlet of the second heat accumulator 7. Since the seawater desalination component 11 adopts the low-pressure steam mode, the steam pressure is required to be 0.5-1.0MPa. The steam pressure operating range of the second heat accumulator 7 is 0.5-1.0MPa, which can meet its normal use. At the same time, when the steam consumption of the second steam user 9 fluctuates greatly, the steam consumption of the seawater desalination component 11 can be adjusted to further reduce the steam pressure fluctuation and improve the stability of the back-type steam turbine.

[0052] The seawater desalination component 10 is a prior art, and specifically may be a vacuum hand-evaporation seawater desalination device, or may be any other seawater desalination component that can realize the function of the present invention, which is not specifically limited herein.

[0053] Example 6

[0054] In this embodiment, the system may further include a flash assembly 13, and the outlet condensed water of the condensed water recovery system 14 is respectively connected to the inlet of the flash assembly 13 and the hot water inlet of the heating station 15; the steam outlet of the flash assembly 13 is connected to the first steam inlet of the seawater desalination assembly 10. The condensed water recovery system 14 is responsible for recovering the hot water of 80-90°C after the heat exchange of the flue gas heat exchanger 2 and the condensed water of 80-90°C generated after the first steam user 8 and the second steam user 9 use the steam. The flash assembly 13 can convert the water with a temperature of 80-90°C recovered by the condensed water recovery system into steam under a negative pressure of 0.035MPa, further improving the utilization rate of waste heat. Since the steam pressure generated by the flash assembly 13 is unstable, in actual operation, the steam provided by the second heat accumulator 7 should be used in conjunction with the steam provided by the flash assembly 13. Specifically, the steam generated by the flash assembly 13 is used as the main component. When the steam pressure is lower than 0.031 MPa, the steam provided by the second heat accumulator 7 is added for mixing to ensure that the steam pressure after mixing is higher than 0.035 MPa.

[0055] Example 7

[0056] In this embodiment, the flash assembly 13 may include a flash tank and a steam ejector. The inlet of the flash tank is respectively connected to the outlet of the condensate recovery system 14 and the hot water inlet of the heating station 15. The steam outlet of the flash tank is connected to the steam inlet of the steam ejector. The steam ejector can further reduce the pressure of the saturated steam at the steam outlet of the flash tank.

[0057] In this embodiment, the flue gas outlet of the flue gas heat exchanger 2 can be discharged into the atmosphere through the chimney 3. In addition, the condensate outlet of the flash evaporation component 13 and the condensate outlet of the seawater desalination component 10 can be connected to the cooling medium inlet of the flue gas heat exchanger 2 to achieve the recycling of cooling water.

[0058] Example 8

[0059] In this embodiment, the cold water generated after the above-mentioned heating can also absorb the heat of the boiler flue gas, thereby realizing the recycling of water.

[0060] The embodiment of the present invention provides a system and method for stabilizing pressure and recovering waste heat of a back-type steam turbine. The back-type steam turbine 4 extracts steam and stores it in a first steam accumulator 6. The steam pressure of the first accumulator operates in a range of 3.0-3.8 MPa and a temperature of 250-350°C. The steam is then transported to a first steam user 8 by the first steam accumulator 6. The exhaust steam of the steam turbine 4 is stored in a second steam accumulator 7. The second accumulator operates in a range of 0.5-1.0 MPa and a temperature of 160-200°C. The exhaust steam is then transported to a second steam user 9 by the second steam accumulator 7. The steam extraction and exhaust steam of the steam turbine 4 are both connected to the steam user through the steam accumulator. The steam accumulator has a pressure buffering function. When the steam consumption of the steam user increases or decreases suddenly, causing a large fluctuation in steam pressure, the first steam accumulator 6 and the second steam accumulator 7 can reduce the fluctuation in steam pressure by changes in the internal water level, thereby avoiding problems such as increased vibration and power reduction of the steam turbine 4 caused by large fluctuations in steam pressure, thereby ensuring safe and stable operation of the back-type steam turbine 4.

[0061] The second steam inlet of the seawater desalination component 10 is connected to the steam outlet of the second heat accumulator 7. Since the seawater desalination component 10 adopts the low-pressure steam mode, the steam pressure is required to be 0.5-1.0MPa. The steam pressure operating range of the second heat accumulator 7 is 0.5-1.0MPa, which can meet its normal use. At the same time, when the steam consumption of the second steam user 9 fluctuates greatly, the steam consumption of the seawater desalination component 11 can be adjusted to further reduce the steam pressure fluctuation and improve the stability of the back-type steam turbine. The flue gas generated by the boiler enters the flue gas heat exchanger 2 and exchanges heat with the cooling water in the flue gas heat exchanger 2. The flue gas temperature is reduced to 100°C and discharged into the atmosphere through the chimney 3. The temperature of the cooling water heated in the flue gas heat exchanger 2 reaches 80-90°C. The condensed water generated after the first steam user 8 and the second steam user 9 use the steam can also reach 80-90°C. These two parts of water are combined into the condensed water recovery system. This part of the heated cooling water is divided into two paths. One path can enter the heating station 15 to provide users with winter heating, and the other path can enter the flash evaporation component 13 to become negative pressure steam with a pressure of 0.035MPa and a temperature of 80-90°C and enter the seawater desalination component 10 as a heat source for seawater desalination, thereby realizing the effective utilization of the thermal energy of the boiler flue gas and the condensed water of the steam users.

[0062] Through the generator set pressure stabilization and waste heat recovery system provided by the present invention, the steam pressure of the pumped-back steam turbine is stabilized when the steam user consumption fluctuates greatly. At the same time, it can meet the heating needs of factory users in the heating season, and reduce the steam consumption of the seawater desalination system in the non-heating season, realizing the full-season application of flue gas and steam condensate waste heat, which can greatly reduce the steam consumption of factory heating and seawater desalination systems, thereby achieving the technical effect of maximizing the use of flue gas and steam condensate waste heat, and also realizing the recycling of cooling water. The heating station is only put into operation in winter, and is shut down in the non-heating season, and the seawater desalination device operates throughout the year; it should be noted that in order to realize the circulation and disconnection of the above-mentioned cooling water, steam, hot water, etc., valves can be set on the connected pipes according to actual needs, and no specific restrictions are made here.

[0063] By adopting the generator set pressure stabilization and waste heat recovery system provided by the present invention, the steam pressure fluctuation range of the back-drawn steam turbine can be narrowed by 80%, the thermal energy utilization rate of the boiler flue gas waste heat within the available range is 90%, the utilization rate of the condensed water heat of the steam user is 90%, and the comprehensive utilization rate of the system waste heat is more than 90%.

[0064] The above embodiments are only descriptions of the preferred methods of the invention, and are not intended to limit the scope of the invention. Without departing from the design spirit of the invention, various modifications and improvements made to the technical solutions of the invention by ordinary technicians in this field should fall within the protection scope of the claims of the invention.

Claims

1. A system for stabilizing pressure and recovering waste heat of a generator set, characterized in that: It comprises a boiler (1), a steam turbine (4), and a generator (5); A flue gas heat exchanger (2) is provided on the flue gas exhaust pipeline of the boiler (1); The medium-pressure spent steam of the steam turbine (4) is connected to the first steam accumulator (6) through a pipeline, and the low-pressure spent steam of the steam turbine (4) is connected to the second steam accumulator (7) through a pipeline; The first steam accumulator (6) supplies heat to a first steam user (8), wherein the working fluid after heat supply enters a condensate recovery system (14); the second steam accumulator (7) supplies heat to a second steam user (9), wherein the working fluid after heat exchange also enters the condensate recovery system (14); The condensed water in the condensed water recovery system (14) enters the flue gas heat exchanger (2) through a pipeline for heat exchange, and after the heated condensed water is desalinated, it is replenished into the water system of the boiler (1) through a pipeline.

2. The generator set pressure stabilization and waste heat recovery system according to claim 1, characterized in that: The main steam in the boiler (1) is directly connected to the first steam accumulator (6) via a bypass pipeline, and a first temperature and pressure reducing device (11) is provided on the bypass pipeline.

3. The generator set pressure stabilization and waste heat recovery system according to claim 2 is characterized in that: The low-pressure steam discharged from the first steam accumulator (6) passes through a second temperature and pressure reducing device (12) and then enters the second steam accumulator (7).

4. The generator set pressure stabilization and waste heat recovery system according to claim 3 is characterized in that: The second steam accumulator (7) also transports steam to the seawater desalination component (10) through pipes, and the desalted water produced by the seawater desalination component (10) is replenished into the water system of the boiler (1).

5. The generator set pressure stabilization and waste heat recovery system according to claim 4, characterized in that: The condensed water in the condensed water recovery system (14) is transported to the flash evaporation component (13) through a pipe, and the steam produced by the flash evaporation component (13) is transported to the seawater desalination component (10), wherein the cooling water in the seawater desalination component (10) that has undergone heat exchange is transported to the flue gas heat exchanger (2) for heat exchange; The condensed water in the condensed water recovery system (14) is also transported to the heating station (15) through pipes.

6. The generator set pressure stabilization and waste heat recovery system according to claim 5, characterized in that: The condensate recovery system (14) supplies heat to the heating station (15), and the working fluid after heat exchange in the heating station (15) is also connected to the water inlet end of the flue gas heat exchanger (2) through a pipe with a valve.

7. The system and method for stabilizing pressure and recovering waste heat of a generator set according to claim 6, characterized in that: The water that has undergone heat exchange in the flue gas heat exchanger (2) flows back to the condensed water recovery system (14).

8. A method for stabilizing pressure and recovering waste heat of a generator set, according to the system for stabilizing pressure and recovering waste heat of a generator set according to any one of claims 1 to 7, characterized in that: When the steam consumption of the steam user increases or decreases suddenly, causing the steam pressure to fluctuate greatly, the internal water levels of the first steam accumulator (6) and the second steam accumulator (7) are adjusted, wherein the steam accumulator has a pressure buffering function to reduce the fluctuation of the steam pressure, so as to avoid the problem of increased vibration and power reduction of the steam turbine (4) caused by the large fluctuation of the steam pressure, thereby ensuring the safe and stable operation of the pumped-back steam turbine (4).

9. The method for stabilizing pressure and recovering waste heat of a generator set according to claim 8, characterized in that: When heating is required, the working fluid outlet of the condensate recovery system (14) is connected to the hot water inlet of the heating station (15) to provide heat for the heating station (15); the working fluid discharged from the heating station (15) is transported to the flue gas heat exchanger (2) through a pipeline for heat exchange, and then flows back to the condensate recovery system (14); wherein the condensate recovery system (14) also continuously receives condensate generated from the use of steam by the first steam user (8) and the second steam user (9); thereby preheating the waste heat of the steam used by the first steam user (8) and the second steam user (9) and the flue gas obtained by using the flue gas heat exchanger (2), and continuously providing heat for the heating station (15).

10. The method for stabilizing pressure and recovering waste heat of a generator set according to claim 9, characterized in that: When seawater desalination is required, the steam from the second steam accumulator (7) and the flash component (13) are used to generate steam to supply heat to the seawater desalination component (10), wherein the smoke-free water generated by the seawater desalination component (10) is supplemented to the water system of the boiler (1); The working fluid of the flash evaporation component (13) comes from the condensate recovery system (14); the steam generated by the flash evaporation component (13) is transported to the seawater desalination component (10) for heat supply, and the steam is condensed and transported to the flue gas heat exchanger (2) for heat exchange, and finally flows back to the condensate recovery system (14).

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