A negative pressure steam inlet condensing steam turbine based on flash evaporation technology

Abstract

This invention provides a negative pressure steam inlet condensing steam turbine based on flash evaporation technology, relating to the field of steam turbines. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology includes: an inlet cylinder having an inlet port for introducing negative pressure steam; an exhaust cylinder connected to the inlet cylinder to form a connecting end, the exhaust cylinder having an exhaust port for connecting to a condenser, the exhaust port of the exhaust cylinder being connected to the inlet port of the condenser via a horizontally arranged pipe; and a power-operating assembly disposed within the space connecting the inlet cylinder and the exhaust cylinder. According to the present invention, the negative pressure steam inlet condensing steam turbine based on flash evaporation technology, by arranging the exhaust channel horizontally and axially with the condenser, reduces energy loss caused by the flow of negative pressure steam and improves the utilization rate of exhaust steam residual velocity.

Description

Technical Field

[0001] This application relates to the field of steam turbines, and in particular to a negative pressure steam inlet condensing steam turbine based on flash evaporation technology. Background Technology

[0002] Large-scale oil refining units generate a large amount of hot water during processes such as cracking and fractionation of petroleum. If this hot water is flash-evaporated into negative pressure steam and then passed into a steam turbine, the thermal energy contained in the negative pressure steam can be converted into mechanical energy. This allows for the secondary utilization of energy and reduces the impact on the environment.

[0003] Existing steam turbines are all configured with inlet steam pressures higher than atmospheric pressure, and the turbine and condenser are arranged in a tiered configuration. In this configuration, the exhaust steam generated by the turbine is discharged horizontally and then vertically downwards into the condenser. Overcoming the flow resistance during reversal causes energy loss, typically within 10 kJ / kg. For turbines with normal inlet steam parameters (i.e., inlet steam pressure higher than atmospheric pressure), a 10 kJ / kg energy loss is acceptable. However, for a negative-pressure inlet turbine with an adiabatic enthalpy drop of only 225.7 kJ / kg from inlet to outlet, a 10 kJ / kg outlet loss is clearly unacceptable. Furthermore, when a turbine uses negative-pressure inlet steam, the inlet and outlet pressure difference is extremely small, with a maximum of only 40 kPa. If existing turbine quick-closing valves and inlet regulating valves are used to regulate the inlet steam pressure, the pressure loss is relatively large, resulting in poor regulation performance. Summary of the Invention

[0004] In view of this, the purpose of this application is to provide a negative pressure steam inlet condensing steam turbine based on flash evaporation technology to solve the problem that existing steam turbines are not suitable for negative pressure steam inlet.

[0005] To achieve the above objectives, the present invention provides a negative pressure steam inlet condensing steam turbine based on flash evaporation technology, wherein the negative pressure steam inlet condensing steam turbine based on flash evaporation technology comprises:

[0006] The steam inlet cylinder has a steam inlet to introduce negative pressure steam.

[0007] An exhaust cylinder, which is connected to the inlet cylinder to form a communication end, has an exhaust port for connecting to a condenser, and the exhaust port of the exhaust cylinder is connected to the inlet of the condenser via a horizontally arranged pipe; and

[0008] The power-operating component is located in the space connecting the intake cylinder and the exhaust cylinder.

[0009] Preferably, the steam inlet of the steam inlet cylinder forms a steam inlet channel facing the connecting end; the connecting end forms a steam exhaust channel facing the steam exhaust port of the steam exhaust cylinder, and the steam exhaust channel is horizontally arranged.

[0010] Preferably, the steam inlet of the steam inlet cylinder is connected to a steam inlet flange, and the center of the steam inlet flange coincides with the center of the steam inlet; the steam outlet of the steam exhaust cylinder is connected to a steam exhaust flange, and the center of the steam exhaust flange coincides with the center of the steam outlet.

[0011] Preferably, both the inlet cylinder and the exhaust cylinder are integral structures formed by welding.

[0012] Preferably, the exhaust port is connected to multiple regulating valves, each of which can be controlled independently.

[0013] Preferably, the power-operating component includes a rotor, the rotor having a drive end extending out of the inlet cylinder, the drive end being provided with a front bearing; the rotor having a rear bearing at the end near the exhaust cylinder; the front bearing being a radial thrust integrated bearing.

[0014] Preferably, the rotor is provided with a sealing part, the sealing part including a front steam seal and a rear steam seal; the front steam seal is located at the position where the rotor is connected to the inlet cylinder, and the rear steam seal is located at the connecting end.

[0015] Preferably, the cylinder is further provided with a guide vane holder and a blade assembly, the blade assembly including multiple stationary blades connected to the guide vane holder and multiple moving blades distributed circumferentially along the rotor.

[0016] Preferably, the rotor is a forged rotor.

[0017] Preferably, the drive end of the rotor is connected to a turning device.

[0018] According to the present invention, the negative pressure steam turbine based on flash evaporation technology is introduced into the main body through the steam inlet of the steam inlet cylinder, and then flows to the steam outlet through the interconnected steam inlet cylinder and steam outlet cylinder. It is then introduced into the condenser for condensation and recovery by a horizontally arranged pipe. In this way, the steam outlet cylinder and the condenser are arranged in the same layer, which effectively avoids the energy loss of the negative pressure steam due to overcoming the flow resistance of the reversing direction. Moreover, the thermal energy in the negative pressure steam can be converted into mechanical energy through the power components. That is, the turbine of the present invention is suitable for negative pressure steam after flash evaporation.

[0019] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0020] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a cross-sectional view of a negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to an embodiment of the present invention;

[0022] Figure 2 This is a partial schematic diagram of a negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to an embodiment of the present invention.

[0023] Icons: 1-Main body; 2-Inlet cylinder; 20-Inlet port; 21-Inlet flange; 22-Drain port; 23-First interface; 3-Exhaust cylinder; 30-Exhaust port; 31-Exhaust flange; 32-Second interface; 4-Rotor; 50-Front steam seal; 51-Rear steam seal; 60-Front bearing; 61-Rear bearing; 62-Bearing housing; 7-Turning wheel device; 80-Guide vane holder; 81-Moving blade; 82-Stationary blade; 9-Support column. Detailed Implementation

[0024] The following detailed embodiments are provided to help the reader gain a comprehensive understanding of the methods, apparatus, and / or systems described herein. However, various changes, modifications, and equivalents of the methods, apparatus, and / or systems described herein will be apparent after understanding the disclosure of this application. For example, the order of operations described herein is merely illustrative and is not limited to the order set forth herein; changes that will be apparent after understanding the disclosure of this application are possible, except for operations that must occur in a specific order. Furthermore, for clarity and brevity, descriptions of features known in the art may be omitted.

[0025] The features described herein may be implemented in different forms and should not be construed as being limited to the examples described herein. Rather, the examples described herein have been provided merely to illustrate some of the many feasible ways of implementing the methods, apparatus, and / or systems described herein that will be apparent upon understanding the disclosure of this application.

[0026] Throughout the specification, when an element (such as a layer, region, or substrate) is described as being "on" another element, "connected to" another element, "bonded to" another element, "on" another element, or "covering" another element, it may be directly "on" another element, "connected to" another element, "bonded to" another element, "on" another element, or "covering" another element, or there may be one or more other elements in between. In contrast, when an element is described as being "directly on" another element, "directly connected to" another element, "directly bonded to" another element, "directly on" another element, or "directly covering" another element, there may be no other elements in between.

[0027] As used herein, the term “and / or” includes any one of the relevant items listed and any combination of any two or more items.

[0028] Although terms such as “first,” “second,” and “third” may be used herein to describe individual components, assemblies, regions, layers, or parts, these components, assemblies, regions, layers, or parts are not limited by these terms. Rather, these terms are used only to distinguish one component, assembly, region, layer, or part from another. Therefore, without departing from the teachings of the examples described herein, the first component, assembly, region, layer, or part referred to as the second component, assembly, region, layer, or part may also be referred to as the second component, assembly, region, layer, or part.

[0029] For ease of description, spatial relation terms such as “above,” “upper,” “below,” and “lower” are used herein to describe the relationship between one element and another, as shown in the accompanying drawings. Such spatial relation terms are intended to include not only the orientation depicted in the drawings but also different orientations of the device during use or operation. For example, if the device in the drawings is flipped, an element described as being “above” or “upper” relative to another element will subsequently be “below” or “lower” relative to that other element. Therefore, the term “above” includes both “above” and “below” orientations depending on the spatial orientation of the device. The device may also be positioned in other ways (e.g., rotated 90 degrees or in other orientations), and the spatial relation terms used herein will be interpreted accordingly.

[0030] The terminology used herein is for the purpose of describing various examples only and is not intended to limit this disclosure. Unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. The terms “comprising,” “including,” and “having” enumerate the stated features, quantities, operations, components, elements, and / or combinations thereof, but do not exclude the presence or addition of one or more other features, quantities, operations, components, elements, and / or combinations thereof.

[0031] Variations in the shapes shown in the accompanying drawings may occur due to manufacturing techniques and / or tolerances. Therefore, the examples described herein are not limited to the specific shapes shown in the accompanying drawings, but include changes in shape that may occur during manufacturing.

[0032] The features of the examples described herein can be combined in various ways that will be apparent upon understanding the disclosure of this application. Furthermore, although the examples described herein have a wide variety of constructions, other constructions are possible, as will be apparent upon understanding the disclosure of this application.

[0033] like Figures 1 to 2 As shown, the negative pressure steam inlet condensing turbine based on flash evaporation technology in this embodiment may include components such as an inlet cylinder 2 and an exhaust cylinder 3 connected to each other. The specific structure of the above-mentioned components of the negative pressure steam inlet condensing turbine based on flash evaporation technology according to the present invention will be described in detail below.

[0034] like Figures 1 to 2 As shown, in this embodiment, the inlet cylinder 2 and the exhaust cylinder 3 are connected to each other to form the main body 1 of the steam turbine. The main body 1 is formed into a cylindrical structure, but its size, i.e. the size of the inlet cylinder 2 and the exhaust cylinder 3, is not specifically limited and should be determined according to the actual situation, such as the displacement of the steam turbine.

[0035] In this embodiment, as Figures 1 to 2 As shown, the steam inlet cylinder 2 is configured as an L-shape, meaning it forms an L-shaped steam inlet channel. Its vertical portion is used for steam intake, and its horizontal portion is used to connect with the exhaust cylinder 3. Specifically, a steam inlet 20 is formed at the top of its vertical portion, and a steam inlet flange 21 is provided at this inlet 20. Through the steam inlet flange 21, negative pressure steam from the flash tank can be introduced into the steam inlet cylinder 2 via the steam inlet pipe and the steam inlet 20. The shape of the steam inlet flange 21 is adapted to the steam inlet 20, and the center of the steam inlet flange 21 coincides with the center of the steam inlet 20, thus further ensuring the stability of the steam inlet pipe connection. However, the size of the steam inlet flange 21 should be determined based on actual conditions such as inlet volumetric flow rate and inlet velocity. For example, when the inlet volumetric flow rate is large or the inlet velocity is small, the area of ​​the steam inlet flange 21 should be set slightly larger. In addition, a drain outlet 22 is provided on the side of the horizontal part of the cylinder 2 away from the steam inlet 20 to facilitate the outflow of condensate inside the cylinder during the start-up phase.

[0036] It should be noted that, to avoid unnecessary energy loss of the negative pressure steam itself, the steam inlet 20 cannot be located at the bottom of the steam inlet cylinder 2. Furthermore, due to the large volumetric flow rate of the negative pressure steam, opening a large steam inlet 20 on the side of the steam inlet cylinder 2 (i.e., tangential steam intake) would be inconvenient for the installation of other components on the main body 1. Therefore, placing the steam inlet 20 at the top of the steam inlet cylinder 2, allowing the negative pressure steam to enter the cylinder from top to bottom, is the optimal choice. The size of the steam inlet 20 needs to be determined based on the actual steam intake volume, which is determined by the flash pressure and the input volume of high-pressure saturated water from the flash tank.

[0037] Furthermore, a first interface 23 for introducing negative pressure steam into the exhaust cylinder 3 is formed at the end of the horizontal portion of the inlet cylinder 2 away from the vertical portion. This first interface 23 is connected to the exhaust cylinder 3 via a flange, thereby achieving communication between the inlet cylinder 2 and the exhaust cylinder 3. The shape and size of the first interface 23 are not specifically limited, as long as the efficiency of the turbine's energy conversion is guaranteed. Furthermore, the size and shape of the flange at the location of the first interface 23 are only required to ensure a stable connection between the inlet cylinder 2 and the exhaust cylinder 3, forming a complete passage from the flash tank to the condenser described below.

[0038] In this embodiment, as Figure 1 As shown, the exhaust cylinder 3 is a horizontally arranged cylindrical structure with a horizontal exhaust channel. One end of the exhaust cylinder 3 has a second interface 32 corresponding to the first interface 23, i.e., this end is the connection end; and an exhaust port 30 is formed on the end of the exhaust cylinder 3 opposite to the connection end, which is used to connect to the condenser to condense the discharged negative pressure steam. In this embodiment, the steam inlet of the condenser and the exhaust port 30 are connected through an exhaust flange 31 and a horizontally arranged connecting pipe, and the center of the exhaust flange 31 coincides with the center of the exhaust port 30 of the exhaust cylinder 3, thereby avoiding unnecessary energy loss. It should be noted that when the center of the exhaust flange 31 coincides with the center of the exhaust port 30, the shape and size of the exhaust flange 31 only need to be adapted to the exhaust port 30 to facilitate the discharge of negative pressure steam.

[0039] Furthermore, the turbine exhaust port 30 is connected to multiple regulating valves. These regulating valves can be located at the condenser inlet or on a connecting pipe that connects the exhaust port 30 to the condenser inlet. These regulating valves control the exhaust pressure at the turbine exhaust port 30 by controlling the condenser vacuum, thereby controlling the rotational speed of the turbine rotor 4. Specifically, when the regulating valve opening decreases, the pressure at the exhaust port 30 decreases, reducing the flow resistance of steam inside the turbine. This, in turn, reduces the pressure at the inlet 20 of the inlet cylinder 2, leading to a decrease in resistance to the negative pressure steam generated by, for example, the flash tank, entering the turbine. This means more negative pressure steam can enter the turbine, increasing the turbine's work output. Conversely, when the regulating valve opening increases, the pressure at the exhaust port 30 increases, increasing the pressure at the inlet 20 of the inlet cylinder 2. This increases the resistance to the negative pressure steam entering the inlet cylinder 2, reducing the steam intake and consequently decreasing the turbine's work output.

[0040] The aforementioned functions of this regulating valve are based on the unique characteristic of negative-pressure steam turbines, where the steam inlet flow rate is significantly affected by back pressure (i.e., exhaust pressure), unlike existing pressure steam turbines. Furthermore, this regulating valve can replace the shut-off and control valves located at the steam inlet in existing steam turbines, eliminating the need for these valves to control the steam flow and on / off. In other words, the negative-pressure steam generated by the flash tank can be directly introduced into the turbine without obstruction, thus improving turbine efficiency. Moreover, based on these functions, the applicability of this regulating valve is also broader; for example, the same effect can be achieved with a very small diameter regulating valve.

[0041] It should be noted that in this embodiment, the aforementioned multiple regulating valves adopt a split-range control method. That is, the exhaust pressure range of the exhaust port 30 is divided into several pressure intervals, and each pressure interval is individually controlled by a corresponding regulating valve. This control method allows for precise control of the valve opening degree, thereby precisely controlling the torque of the rotor 4, i.e., the turbine's output power. The number of regulating valves and the specifications of each regulating valve should be determined based on actual conditions such as exhaust pressure and inlet steam flow. For example, two regulating valves, DN50 and DN80, can be installed at the exhaust port 30, and their opening degree can be controlled by a DCS control device. When the inlet steam pressure is between 11 kPa and 20 kPa, the DCS control device controls the opening degree of the DN50 regulating valve, thereby regulating the exhaust pressure of the exhaust port 30; when the inlet steam pressure is between 21 kPa and 40 kPa, the DCS control device controls the opening degree of the DN80 regulating valve, thereby regulating the exhaust pressure of the exhaust port 30. In this way, by adjusting the steam inlet pressure and thus the turbine power through the multiple regulating valves set at the exhaust port 30, the pressure loss of the steam inlet is effectively reduced, and the adjustment is more flexible.

[0042] Furthermore, when the pressure of the steam entering the turbine is greater than atmospheric pressure, both the inlet cylinder 2 and the exhaust cylinder 3 are manufactured using a casting process to ensure the turbine's operating efficiency. To guarantee cylinder strength, the wall thickness of both cylinders is set relatively large. However, in this embodiment, since the steam is under negative pressure, the pressure difference between the inner and outer walls of the inlet cylinder 2 and the exhaust cylinder 3 is small. Therefore, it is unnecessary to set their wall thickness excessively. Thus, in this embodiment, both the inlet cylinder 2 and the exhaust cylinder 3 are designed as a welded, integrated structure. This ensures that the heat from the negative pressure steam is fully converted while also saving on manufacturing costs and meeting the environmental protection requirements for waste heat utilization in oil refining units.

[0043] Furthermore, in this embodiment, such as Figures 1 to 2 As shown, the power-operating assembly is located within the space connecting the inlet cylinder 2 and the exhaust cylinder 3, i.e., inside the main body 1. Specifically, the power-operating assembly includes a rotor 4 horizontally positioned in the center of the exhaust passage, with the axis of rotor 4 coinciding with the axis of exhaust cylinder 3. This concentric arrangement of rotor 4 and exhaust cylinder 3 improves the uniform distribution of negative pressure steam outside rotor 4, thereby ensuring the energy conversion efficiency of the negative pressure steam. The front end of rotor 4, near the inlet cylinder 2, extends from the vertical portion of inlet cylinder 2 and is fixed by a front bearing 60; the rear end of rotor 4 extends into the interior of exhaust cylinder 3 and is fixed to the inner wall of exhaust cylinder 3 by a rear bearing 61. This arrangement ensures that the negative pressure steam interacts fully with rotor 4 throughout its entire flow within the turbine, thus guaranteeing the energy conversion rate of the negative pressure steam.

[0044] It should be noted that, as Figure 2 As shown, multiple support columns 9 are evenly arranged around the outer wall of the rear bearing 61. Each support column 9 has its two ends connected to both the outer wall of the rear bearing 61 and the inner wall of the exhaust cylinder 3, thus stably mounting the rear bearing 61 at the center of the exhaust cylinder 3. It should be further noted that the support columns 9 can be arranged at equal intervals or staggered. The term "evenly arranged" refers to the uniform distribution of force points on the rear bearing 61 to provide stable support for the power-generating components. Furthermore, there are no specific limitations on the size or number of the support columns 9, as long as the smooth operation of the turbine is ensured.

[0045] Furthermore, the aforementioned front bearing 60 is configured as a radial thrust integrated bearing, which allows it to not only support the rotor 4 but also withstand the thrust generated by steam, preventing axial movement of the rotor 4 during rotation. Moreover, there are no specific restrictions on the connection method between the front bearing 60 and the rear bearing 61 and the main body 1; for example, both can be fixed to the main body 1 via bearing housings 62. Furthermore, the rotor 4 is a single-forged rotor, which has a compact structure and high strength and rigidity, thus avoiding the problem of loosening of the blade assembly at high temperatures.

[0046] In addition, such as Figures 1 to 2 As shown, since the steam in this embodiment is negative pressure steam, in order to ensure the sealing of the inlet cylinder 2 and the outlet cylinder 3 and prevent the inflow of external gas, a sealing part is also provided on the rotor 4. The sealing part includes a front steam seal 50 and a rear steam seal 51 sleeved on the rotor 4. Specifically, the front steam seal 50 is located at the position where the rotor 4 connects to the inlet cylinder 2, and the rear steam seal 51 is located at the end where the outlet cylinder 3 communicates with the inlet cylinder 2. This ensures the stability of the steam pressure inside the inlet cylinder 2 and the outlet cylinder 3.

[0047] Furthermore, in this embodiment, such as Figure 1 As shown, a guide vane holder 80 is also provided inside the inlet cylinder 2. This guide vane holder 80 and a multi-stage blade assembly, each stage of which includes multiple moving blades 81 distributed circumferentially along the rotor 4 and multiple stationary blades 82 mounted on the guide vane holder 80. The negative pressure steam expands in the stationary blades 82, causing a decrease in its temperature and pressure, which in turn increases its velocity. That is, the thermal energy in the negative pressure steam is converted into the kinetic energy of the airflow. Then, the high-speed airflow formed by the negative pressure steam changes its speed and direction of motion in the moving blades 81, converting the kinetic energy of the airflow into the mechanical energy of the rotor 4. This achieves the conversion of the thermal energy of the negative pressure steam into mechanical energy. It should be noted that there are no specific restrictions on the specific shape and size of each blade in the blade assembly, as long as it can ensure good aerodynamic performance and strong tensile, bending, and torsional resistance during rotation to meet the requirements of the above-mentioned actions. Furthermore, there are no specific restrictions on the number of stages in the blade assembly; it should be determined based on actual conditions, such as the pressure of the negative pressure steam or the turbine speed.

[0048] In addition, such as Figure 1As shown, in this embodiment, the portion of the rotor 4 extending into the cylinder 2 is also connected to a turning device 7. This device is mounted on the bearing seat 62 and connected to the main body 1. This device allows the rotor 4 to be turned before or after the turbine starts up, ensuring that the rotor 4 rotates at a low speed for a certain period before or after the turbine starts up. This helps determine if there is friction between the moving and stationary parts of the turbine and whether the lubrication system is functioning properly, thus ensuring the safe operation of the turbine. Furthermore, the turning device 7 also prevents the rotor 4 from undergoing thermal bending deformation due to uneven heating.

[0049] According to the present invention, the negative pressure steam inlet condensing turbine based on flash evaporation technology, as described above, reduces energy loss caused by the flow of negative pressure steam and improves the utilization rate of exhaust steam residual velocity by arranging the exhaust passage horizontally and axially with the condenser. Furthermore, by setting the inlet cylinder 2 and the exhaust cylinder 3 as a welded integral structure, manufacturing costs and manufacturing cycle are saved for the enterprise.

[0050] Finally, it should be noted that the above-described embodiments are merely specific implementations of this application, used to illustrate the technical solutions of this application, and not to limit them. The protection scope of this application is not limited thereto. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that any person skilled in the art can still modify or easily conceive of changes to the technical solutions described in the foregoing embodiments, or make equivalent substitutions for some of the technical features, within the technical scope disclosed in this application. Such modifications, changes, or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application, and should all be covered within the protection scope of this application. Therefore, the protection scope of this application should be defined by the protection scope of the claims.

Claims

1. A negative pressure steam inlet condensing steam turbine based on flash evaporation technology, characterized in that, The negative pressure steam inlet condensing steam turbine based on flash evaporation technology includes: The steam inlet cylinder has a steam inlet to introduce negative pressure steam. An exhaust cylinder is connected to the inlet cylinder to form a communication end. The exhaust cylinder has an exhaust port for connecting to a condenser. The exhaust port of the exhaust cylinder is connected to the inlet of the condenser via a horizontally arranged pipe. The exhaust port is connected to multiple regulating valves, each of which can be independently controlled. These multiple regulating valves employ a split-range control method, and each regulating valve controls the exhaust pressure of the exhaust port by controlling the vacuum level of the condenser. The power-operating component is located in the space connecting the intake cylinder and the exhaust cylinder.

2. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 1, characterized in that, The steam inlet of the steam inlet cylinder forms a steam inlet channel facing the connecting end; the connecting end forms a steam exhaust channel facing the steam exhaust port of the steam exhaust cylinder, and the steam exhaust channel is horizontally arranged.

3. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 2, characterized in that, The steam inlet of the steam inlet cylinder is connected to a steam inlet flange, and the center of the steam inlet flange coincides with the center of the steam inlet; the steam outlet of the steam exhaust cylinder is connected to a steam exhaust flange, and the center of the steam exhaust flange coincides with the center of the steam outlet.

4. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 1, characterized in that, Both the intake cylinder and the exhaust cylinder are integral structures formed by welding.

5. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 1, characterized in that, The power-operating component includes a rotor, which has a drive end extending out of the intake cylinder, and the drive end is provided with a front bearing; a rear bearing is provided at the end of the rotor near the exhaust cylinder; the front bearing is a radial thrust integrated bearing.

6. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 5, characterized in that, The rotor is provided with a sealing part, which includes a front steam seal and a rear steam seal; the front steam seal is located at the position where the rotor is connected to the inlet cylinder, and the rear steam seal is located at the connecting end.

7. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 6, characterized in that, The intake cylinder is also provided with a guide vane holder ring and a blade assembly. The blade assembly includes multiple stationary blades connected to the guide vane holder ring and multiple moving blades distributed circumferentially along the rotor.

8. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 5, characterized in that, The rotor is a solid forged rotor.

9. The negative pressure steam inlet condensing steam turbine based on flash evaporation technology according to claim 5, characterized in that, The rotor is connected to a turning device at its drive end.

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