Steam supply system

Abstract

The invention provides a steam supply system which comprises a compressor, an expansion machine, a circulation channel and a driving device, the compressor and the expansion machine are arranged on the circulation channel, a first heat exchanger and a second heat exchanger are arranged on the circulation channel, and the first heat exchanger is located between the inlet end of the compressor and the outlet end of the expansion machine; the second heat exchanger is located between the discharge port end of the compressor and the inlet end of the expansion machine, the first heat exchanger is connected with a waste heat steam pipeline, the second heat exchanger is connected with a gas supply pipeline, the driving device is connected with the compressor, a clutch is arranged between the driving device and the expansion machine, and the compressor is electrically connected with the coal power unit. Waste heat resources of a power plant can be utilized, heat exchange is conducted between fluid in the waste heat steam pipeline and fluid in the circulation channel, and the energy utilization rate is increased.

Description

Technical Field

[0001] This application belongs to the technical field of steam supply, and particularly relates to a steam supply system. Background Art

[0002] In the industrial field, high-temperature and high-pressure industrial steam is widely used, covering many industries such as chemical industry, petroleum, light textile, printing and dyeing, papermaking, food, as well as places such as restaurants, hospitals, and schools, and also plays a key role in the power and energy fields. Among them, the steam demand in the refining and aromatics integration industrial chain of the petrochemical industry shows the characteristics of "high safety, high stability, high flow rate, and high parameters", and currently generally relies on a self-provided thermal center with multiple boilers in parallel to meet the demand.

[0003] However, with the increasing emphasis on environmental protection, traditional heating methods are facing challenges, and supplying high-temperature and high-pressure steam to industrial users by large-scale generator sets is gradually becoming the mainstream trend in the future heating market.

[0004] The existing steam supply system lacks the utilization of the waste heat resources of power plants, resulting in insufficient energy utilization. Summary of the Invention

[0005] Therefore, the technical problem to be solved by this application is to provide a steam supply system that can utilize the waste heat resources of power plants for steam supply and improve energy utilization efficiency.

[0006] To solve the above problems, this application provides a steam supply system, including a compressor, an expander, a circulation channel, and a driving device. The compressor and the expander are arranged on the circulation channel. A first heat exchanger and a second heat exchanger are arranged on the circulation channel. The first heat exchanger is located between the inlet end of the compressor and the discharge port end of the expander, and the second heat exchanger is located between the discharge port end of the compressor and the inlet end of the expander. The first heat exchanger is connected to a waste heat steam pipeline, and the second heat exchanger is connected to a steam supply pipeline. The driving device is connected to the compressor, and a clutch is arranged between the driving device and the expander. The compressor is electrically connected to a coal-fired power generation unit.

[0007] Optionally, a first heat exchange channel and a second heat exchange channel are arranged in the first heat exchanger. The first heat exchange channel is communicated with the circulation channel, and the second heat exchange channel is communicated with the waste heat steam pipeline, so that the fluid in the waste heat steam pipeline exchanges heat with the fluid in the circulation channel in the first heat exchanger;

[0008] The steam in the waste heat steam pipeline is the medium-pressure exhaust steam or exhaust steam of a power plant.

[0009] Optionally, a third heat exchange channel and a fourth heat exchange channel are arranged in the second heat exchanger. The third heat exchange channel is communicated with the circulation channel, and the fourth heat exchange channel is communicated with the gas supply pipeline, so that the fluid in the circulation channel exchanges heat with the fluid in the gas supply pipeline in the second heat exchanger.

[0010] Optionally, the electrical energy source of the compressor includes power generation during the isolated network operation of the coal-fired power unit in the deep load regulation state or power generation during the start-stop of the coal-fired power unit.

[0011] Optionally, one end of the clutch is connected to the expander, and the other end is connected to the driving device. The clutch includes an engaged state and a disengaged state. When the clutch is in the engaged state, the expander drives the driving device to operate through the clutch. When the clutch is in the disengaged state, the expander is disengaged from the driving device.

[0012] Optionally, the clutch is an overrunning clutch. When the output speed of the expander is greater than or equal to a preset speed, the clutch enters the engaged state. When the output speed of the expander is less than the preset speed, the clutch enters the disengaged state.

[0013] Optionally, the driving device includes an asynchronous motor and a speed reducer. The asynchronous motor is connected to the clutch, the asynchronous motor is electrically connected to the coal-fired power unit, and the asynchronous motor is connected to the compressor through the speed reducer.

[0014] Optionally, the compressor is a multi-stage compressor, and the exhaust temperature of the compressor is 435°C to 445°C.

[0015] Optionally, the fluid in the circulation channel exchanges heat with the fluid in the gas supply pipeline in the second heat exchanger to heat the fluid in the gas supply pipeline to 425°C to 435°C.

[0016] Optionally, the fluid temperature at the inlet end of the expander is 290°C to 300°C, the temperature at the outlet end of the expander is 70°C to 90°C, and the temperature of the fluid flowing into the first heat exchanger through the waste heat steam pipeline is 290°C to 320°C, so as to heat the fluid entering the first heat exchanger through the circulation channel to 150°C to 190°C.

[0017] Beneficial effects

[0018] In an embodiment of the present invention, a steam supply system is provided. By arranging a first heat exchanger connected to the waste heat steam pipeline on the circulation channel, the waste heat resources of the power plant can be utilized, enabling the fluid in the waste heat steam pipeline to exchange heat with the fluid in the circulation channel. The waste heat that might otherwise be wasted is used for system operation, thereby improving the energy utilization rate and reducing energy consumption. By arranging a compressor and an expander on the circulation channel, and arranging a first heat exchanger and a second heat exchanger on the circulation channel, a circulation system is formed. The compressor compresses and heats up the fluid, and the fluid in the supply gas pipeline is heated by the second heat exchanger to generate medium and high parameter steam for external supply. The expander realizes energy conversion in the steam supply system, and cooperates with the power supplied by the coal-fired power unit to drive the compressor to operate, and then continuously and stably provides steam that meets the needs for industrial users. Description of the Drawings

[0019] Figure 1 It is a schematic diagram of the steam supply system according to the embodiment of the present application.

[0020] The reference numerals are shown as:

[0021] 1. Compressor; 2. Expander; 3. First heat exchanger; 4. Second heat exchanger; 5. Clutch; 6. Asynchronous motor; 7. Reducer; 8. Pump assembly. Detailed Embodiments

[0022] In the description of the present application, it should be understood that the orientation or positional relationship indicated by terms such as "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0023] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, "a plurality" means two or more, unless otherwise specifically defined.

[0024] In this application, unless otherwise clearly defined and limited, terms such as "installation", "connection", "linkage", "fixation" shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be a direct connection or an indirect connection through an intermediate medium, and it may be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0025] The preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are only for the purpose of illustrating and explaining the present invention, and are not used to limit the present invention.

[0026] Combined with the reference to Figure 1 As shown, according to an embodiment of the present application, a steam supply system is provided, including a compressor 1, an expander 2, a circulation channel and a driving device. The compressor 1 and the expander 2 are arranged on the circulation channel. A first heat exchanger 3 and a second heat exchanger 4 are arranged on the circulation channel. The first heat exchanger 3 is located between the inlet end of the compressor 1 and the discharge port end of the expander 2. The second heat exchanger 4 is located between the discharge port end of the compressor 1 and the inlet end of the expander 2. The first heat exchanger 3 is connected to the waste heat steam pipeline, and the second heat exchanger 4 is connected to the steam supply pipeline. The driving device is connected to the compressor 1, a clutch 5 is arranged between the driving device and the expander 2, and the compressor 1 is electrically connected to the coal-fired power unit.

[0027] By arranging the first heat exchanger 3 connected to the waste heat steam pipeline on the circulation channel, the waste heat resources of the power plant can be utilized, so that the fluid in the waste heat steam pipeline exchanges heat with the fluid in the circulation channel, and the waste heat that might have been wasted is used for system operation, thereby improving the energy utilization rate and reducing energy consumption.

[0028] By arranging the compressor 1 and the expander 2 on the circulation channel, and arranging the first heat exchanger 3 and the second heat exchanger 4 on the circulation channel, a circulation system is formed. The compressor 1 compresses and heats up the fluid, and the fluid in the steam supply pipeline is heated by the second heat exchanger 4 to generate medium and high parameter steam for external supply. The expander 2 realizes energy conversion in the steam supply system, and drives the compressor 1 to operate in cooperation with the power supplied by the coal-fired power unit, so as to continuously and stably provide steam that meets the requirements for industrial users.

[0029] Wherein, the circulation channel is formed by pipelines connected into a ring, and the compressor 1, the expander 2, the first heat exchanger 3 and the second heat exchanger 4 are all arranged on the ring-shaped pipeline.

[0030] Wherein, the coal-fired power unit can supply power to the driving device to drive the compressor 1 to operate. The driving device can also be driven by the expander 2 to drive the compressor 1 to operate.

[0031] As an implementation manner, the electric power supplied to the driving device can also come from renewable energy sources, such as wind energy, solar energy, geothermal energy, etc.

[0032] A first heat exchange channel and a second heat exchange channel are arranged in the first heat exchanger 3. The first heat exchange channel is communicated with the circulation channel, and the second heat exchange channel is communicated with the waste heat steam pipeline, so that the fluid in the waste heat steam pipeline exchanges heat with the fluid in the circulation channel in the first heat exchanger 3. The steam in the waste heat steam pipeline is the medium-pressure exhaust steam or the exhausted steam of the power plant.

[0033] By arranging the first heat exchange channel and the second heat exchange channel, good heat exchange efficiency and effect between the fluid in the waste heat steam pipeline and the fluid in the circulation channel are ensured. By using the medium-pressure exhaust steam or the exhausted steam of the power plant as the heat exchange fluid of the waste heat steam pipeline, the steam supply system can make full use of the common waste heat resources of different power plants. Whether it is medium-pressure exhaust steam or exhausted steam, effective heat recovery can be carried out through the special structure of the first heat exchanger 3, expanding the applicability of the steam supply system in different power plant environments and improving the versatility and flexibility of the system.

[0034] Among them, the medium-pressure exhaust steam refers to the exhaust steam of the medium-pressure cylinder of the steam turbine.

[0035] Among them, the exhausted steam refers to the exhaust steam of the medium-low pressure cylinders of the steam turbine.

[0036] A third heat exchange channel and a fourth heat exchange channel are arranged in the second heat exchanger 4. The third heat exchange channel is communicated with the circulation channel, and the fourth heat exchange channel is communicated with the steam supply pipeline, so that the fluid in the circulation channel exchanges heat with the fluid in the steam supply pipeline in the second heat exchanger 4.

[0037] By arranging the third heat exchange channel and the fourth heat exchange channel, good heat exchange efficiency and effect between the fluid in the circulation channel and the fluid in the steam supply pipeline are ensured.

[0038] Among them, a pump assembly 8 can be arranged in the steam supply pipeline to increase the steam supply pressure.

[0039] The electric energy source of the compressor 1 includes power generation during the isolated network operation of the coal-fired power unit in the deep load regulation state or power generation during the start-stop process of the coal-fired power unit.

[0040] During the isolated network operation or start-stop process of the coal-fired power unit in the deep load regulation state, electric energy that might otherwise be wasted will be generated. By driving the compressor 1 to operate, energy can be fully utilized, energy waste can be avoided, and the demand for purchasing electricity from the external power grid can also be reduced, thereby lowering the electricity cost of the enterprise.

[0041] Among them, the isolated network operation power generation of the coal-fired power unit refers to that the coal-fired generating unit is separated from the large power grid and independently supplies power to the local power grid.

[0042] Among them, the deep regulation state refers to the state where the unit operates for a long time or frequently in a low load range far below the rated power.

[0043] That is to say, the off-grid operation and power generation of coal-fired power units in the deep regulation state means that coal-fired power generation units operate independently from the large power grid in the deep peak shaving state to provide power for local power grids such as industrial parks, remote areas, and emergency scenarios.

[0044] Among them, the start-stop power generation of coal-fired power units refers to the power generation strategy of starting and stopping coal-fired power generation units to adjust power output to adapt to the power grid load changes or cooperate with the fluctuations of renewable energy.

[0045] One end of the clutch 5 is connected to the expander 2, and the other end is connected to the driving device. The clutch 5 includes an engaged state and a disengaged state. When the clutch 5 is in the engaged state, the expander 2 drives the driving device to operate through the clutch 5. When the clutch 5 is in the disengaged state, the expander 2 is disengaged from the driving device.

[0046] By enabling the clutch 5 to have two states of engagement and disengagement, when in the engaged state, the expander 2 can drive the driving device to operate through the clutch 5, and the power of the expander 2 is used to assist the compressor 1 to work. When the clutch 5 is disengaged, the expander 2 is disengaged from the driving device, and the driving device can operate independently. This enables the system to dynamically adjust the power output mode according to different working conditions and operation requirements. For example, when the expander 2 is working normally and has sufficient power, the clutch 5 is engaged to achieve combined drive. When the expander 2 fails or has insufficient power during the start-up phase, the clutch 5 is disengaged, and the driving device drives the compressor 1 alone to maintain the operation of the system, greatly improving the flexibility of the system operation.

[0047] By setting the clutch 5, redundant protection is provided for the system. When the expander 2 fails and cannot work normally, the clutch 5 is disengaged, and the driving device can still ensure the normal operation of the compressor 1, avoiding the shutdown of the steam supply system due to the failure of the expander 2 and ensuring the continuous supply of steam. During the start-up process, if the expander 2 starts slowly or the rotational speed does not reach the expected value, the driving device can work first, and then cooperate through the clutch 5 after the expander 2 reaches the appropriate rotational speed, enhancing the reliability of the system in different operation stages.

[0048] Through the state switching of the clutch 5, the steam supply system can reasonably allocate power resources according to the actual operation conditions of the expander 2 and the driving device. When the power output of the expander 2 is greater than the demand of the driving device, the clutch 5 is engaged to transfer the excess power to the driving device, reducing energy waste. When the power of the expander 2 is insufficient, the driving device timely supplements the power to maintain the stable operation of the system, improving the energy utilization efficiency of the entire system and reducing the energy consumption cost.

[0049] Specifically, the clutch 5 is an overrunning clutch. When the output speed of the expander 2 is greater than or equal to the preset speed, the clutch 5 enters the engaged state. When the output speed of the expander 2 is less than the preset speed, the clutch 5 enters the disengaged state.

[0050] By setting the clutch 5 as an overrunning clutch, the engagement and disengagement can be automatically controlled according to the speed of the expander 2. When the speed of the expander 2 is greater than or equal to the preset speed, it enters the engaged state, and the expander 2 can drive the drive device to operate, providing additional power for the compressor 1. When the speed is less than the preset speed, the clutch 5 disengages, and the drive device independently drives the compressor 1, enabling the steam supply system to automatically adjust power transmission according to the actual operating state of the expander 2, ensuring the stable operation of the compressor 1 under different working conditions, ensuring the continuous and stable supply of steam, and meeting the industrial users' requirements for steam with "high safety, high stability, high flow rate, and high parameters".

[0051] By automatically adjusting power transmission, the overrunning clutch can make full use of the energy of the expander 2. When the output power of the expander 2 is sufficient, the excess mechanical energy is transmitted to the drive device to drive the compressor 1, avoiding energy waste. When the power of the expander 2 is insufficient, the drive device timely supplements power to ensure the normal operation of the system, thereby improving the energy utilization efficiency of the entire steam supply system and reducing energy consumption and operating costs.

[0052] Among them, the preset speed is flexibly set according to the specific parameters and models of the drive device, and the setting method is a conventional technology in this field, which will not be elaborated here.

[0053] The drive device includes an asynchronous motor 6 and a speed reducer 7. The asynchronous motor 6 is connected to the clutch 5, the asynchronous motor 6 is electrically connected to the coal-fired power unit, and the asynchronous motor 6 is connected to the compressor 1 through the speed reducer 7.

[0054] The drive device includes an asynchronous motor 6 and a speed reducer 7. The asynchronous motor 6 is connected to the clutch 5, can flexibly receive the power of the expander 2 or independently drive the compressor 1, and is electrically connected to the coal-fired power unit to obtain stable electric energy. The setting of the speed reducer 7 can accurately adjust the speed, match the working requirements of the compressor 1, optimize power transmission, improve the working efficiency of the compressor 1, stably generate medium and high parameter steam, and meet the requirements of industrial users.

[0055] The asynchronous motor 6 has a simple structure, lower cost compared with other motors, and is easy to maintain. Cooperating with the speed reducer 7, it forms a drive device with a compact structure and high cost-effectiveness, reducing the equipment cost of the steam supply system. Its simple structure reduces the failure points, lowers the maintenance difficulty and cost, and improves the overall reliability and economy of the system.

[0056] Among them, the preset rotational speed is flexibly set according to the specific parameters and models of the asynchronous motor 6, etc. The setting method is a conventional technology in this field and will not be elaborated here.

[0057] Specifically, the asynchronous motor 6 is connected to the power input end of the compressor 1 through a speed reducer 7, thereby driving the compressor 1 to operate.

[0058] The compressor 1 is a multi-stage compressor, and the exhaust temperature of the compressor 1 is 435°C to 445°C.

[0059] Among them, the compressor 1 compresses the fluid in the circulation channel into high-temperature compressed air with a pressure of 0.6 MPa to 0.8 MPa and a temperature of 435°C to 445°C.

[0060] The fluid in the circulation channel exchanges heat with the fluid in the supply gas pipeline in the second heat exchanger 4 to heat the fluid in the supply gas pipeline to 425°C to 435°C.

[0061] Among them, water can be introduced into the supply gas pipeline on the upstream side of the second heat exchanger 4. The high-temperature compressed air discharged by the compressor 1 is used through the second heat exchanger 4 to heat the water to medium-high parameter superheated steam at 425°C to 435°C, and then supplied externally.

[0062] The temperature of the fluid at the inlet end of the expander 2 is 290°C to 300°C, the temperature at the discharge end of the expander 2 is 70°C to 90°C, and the temperature of the fluid flowing into the first heat exchanger 3 through the waste heat steam pipeline is 290°C to 320°C, so as to heat the fluid entering the first heat exchanger 3 through the circulation channel to 150°C to 190°C.

[0063] Among them, the temperature of the fluid at the inlet end of the expander 2 is the temperature of the fluid in the circulation channel after heat exchange through the second heat exchanger 4. The fluid in the circulation channel after heat exchange through the second heat exchanger 4 cools down to 290°C to 300°C and then enters the expander 2 to do work.

[0064] Among them, after the fluid does work in the expander 2, the pressure of the fluid discharged from the discharge end of the expander 2 is 0.08 Mpa to 0.12 Mpa, and the temperature is 70°C to 90°C.

[0065] Among them, the fluid discharged from the expander 2 exchanges heat with the fluid flowing into the first heat exchanger 3 through the waste heat steam pipeline in the first heat exchanger 3. The pressure of the fluid discharged from the circulation channel after heat exchange through the first heat exchanger 3 is 0.08 MPa to 0.12 Mpa, and the temperature is 150°C to 190°C, and enters the compressor 1 for compression. The fluid in the waste heat steam pipeline condenses into water after heat exchange through the first heat exchanger 3, the temperature is 80°C to 95°C, and flows back to the condenser to recover the working medium and heat.

[0066] In one embodiment, the steam demand is high-temperature and high-pressure steam at 15.4 MPa and 430 °C. The medium-pressure exhaust steam of the power plant at 310 °C enters the gas supply system and enters the first heat exchanger 3. After exchanging heat with the low-temperature and low-pressure air at 0.1 MPa and 78 °C in the circulation pipe, the temperature drops to 88 °C and returns to the condenser. The low-temperature and low-pressure air in the circulation pipe is heated to 0.1 MPa and 170 °C and then enters the compressor 1, where it is compressed to 0.7 MPa and 440 °C. Then it enters the second heat exchanger 4 to release heat. After the temperature drops to 0.7 MPa and 295 °C, it enters the expander 2 to do work. When the unit is operating in deep regulation and islanding mode or the power plant is starting and stopping the unit for standby power generation, electric energy powers the asynchronous motor to drive the compressor 1 to operate. The expander 2 and the compressor 1 are connected by a clutch 5. When the output speed of the expander 2 is greater than or equal to the preset speed, the expander 2 drives the asynchronous motor to move, and then drives the compressor 1 to operate. The high-temperature compressed air at 0.7 MPa and 440 °C at the outlet of the compressor 1 heats the water in the gas supply pipeline to medium-high parameter superheated steam at 430 °C in the second heat exchanger 4 and supplies it externally to meet its steam demand.

[0067] It is easy for those skilled in the art to understand that, on the premise of no conflict, the above advantageous ways can be freely combined and superimposed.

[0068] The above are only the preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present application shall be included in the protection scope of the present application. The above is only the preferred implementation mode of the present application. It should be noted that for those of ordinary skill in the art in this technical field, several improvements and variations can be made without departing from the technical principle of the present application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A steam supply system, characterized in that, It includes a compressor (1), an expander (2), a circulation channel and a driving device. The compressor (1) and the expander (2) are arranged on the circulation channel. A first heat exchanger (3) and a second heat exchanger (4) are arranged on the circulation channel. The first heat exchanger (3) is located between the inlet end of the compressor (1) and the discharge port end of the expander (2). The second heat exchanger (4) is located between the discharge port end of the compressor (1) and the inlet end of the expander (2). The first heat exchanger (3) is connected to a waste heat steam pipeline. The second heat exchanger (4) is connected to a gas supply pipeline. The driving device is connected to the compressor (1). A clutch (5) is arranged between the driving device and the expander (2). The compressor (1) is electrically connected to a coal-fired power unit.

2. The steam supply system according to claim 1, characterized in that, A first heat exchange channel and a second heat exchange channel are arranged in the first heat exchanger (3). The first heat exchange channel is communicated with the circulation channel. The second heat exchange channel is communicated with the waste heat steam pipeline, so that the fluid in the waste heat steam pipeline exchanges heat with the fluid in the circulation channel in the first heat exchanger (3). The steam in the waste heat steam pipeline is medium-pressure exhaust steam or exhaust steam of a power plant.

3. The steam supply system according to claim 1, characterized in that, A third heat exchange channel and a fourth heat exchange channel are arranged in the second heat exchanger (4). The third heat exchange channel is communicated with the circulation channel. The fourth heat exchange channel is communicated with the gas supply pipeline, so that the fluid in the circulation channel exchanges heat with the fluid in the gas supply pipeline in the second heat exchanger (4).

4. The steam supply system according to claim 1, wherein, The power source of the compressor (1) includes power generation during the isolated network operation of the coal-fired power unit in the deep load regulation state or power generation during the start-up and shutdown of the coal-fired power unit.

5. The steam supply system according to claim 1, characterized in that, One end of the clutch (5) is connected to the expander (2), and the other end is connected to the driving device. The clutch (5) includes an engaged state and a disengaged state. When the clutch (5) is in the engaged state, the expander (2) drives the driving device to operate through the clutch (5). When the clutch (5) is in the disengaged state, the expander (2) is disengaged from the driving device.

6. The steam supply system according to claim 5, characterized in that, The clutch (5) is an overrunning clutch. When the output speed of the expander (2) is greater than or equal to a preset speed, the clutch (5) enters the engaged state. When the output speed of the expander (2) is less than the preset speed, the clutch (5) enters the disengaged state.

7. The steam supply system according to claim 1, characterized in that, The driving device includes an induction motor (6) and a speed reducer (7). The induction motor (6) is connected to the clutch (5). The induction motor (6) is electrically connected to the coal-fired power unit. The induction motor (6) is connected to the compressor (1) through the speed reducer (7).

8. The steam supply system according to claim 1, characterized in that The compressor (1) is a multi-stage compressor, and the exhaust temperature of the compressor (1) is 435°C to 445°C.

9. The steam supply system according to claim 1, characterized in that The fluid in the circulation channel exchanges heat with the fluid in the gas supply pipeline in the second heat exchanger (4) to heat the fluid in the gas supply pipeline to 425°C to 435°C.

10. The steam supply system according to claim 1, characterized in that, The fluid temperature at the inlet end of the expander (2) is 290°C to 300°C, the temperature at the discharge end of the expander (2) is 70°C to 90°C, and the temperature of the fluid flowing into the first heat exchanger (3) via the waste heat steam pipeline is 290°C to 320°C, so as to heat the fluid entering the first heat exchanger (3) via the circulation channel to 150°C to 190°C.

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