Compact efficient cooler and power generation system

Abstract

The invention relates to the technical field of heat exchange equipment, and provides a compact and efficient cooler and a power generation system. The compact and efficient cooler comprises a device shell provided with a cooling water inlet, a liquid outlet, a steam inlet and an exhaust port, the cooling water inlet is formed in the top face of the device shell, the liquid outlet is formed in the bottom face of the device shell, the steam inlet is formed in the top face of the device shell, and the exhaust port is formed in the side face of the device shell; the flow guide plate is arranged in the device shell, and cooling water enters the device shell through the cooling water inlet, flows down along the flow guide plate, forms a liquid film on the surface of the flow guide plate and is discharged from the liquid outlet; the flow guide plates are spirally arranged, so that spiral heat exchange channels for steam to flow are formed between adjacent spiral rings of the flow guide plates; an inlet of the heat exchange channel communicates with the steam inlet, and an outlet of the heat exchange channel communicates with the exhaust port. And steam advances in the heat exchange channel.

Description

Technical Field

[0001] The present application relates to the technical field of heat exchange equipment, and in particular to a compact and efficient cooler and power generation system. Background Art

[0002] Direct-mix heat exchangers achieve heat exchange through direct contact between the cooling medium (liquid) and the cooled medium (vapor). Due to their high heat transfer coefficient, compact structure, no risk of heat exchange tube corrosion or blockage, and low maintenance costs, they are widely used in the power and chemical industries, such as direct-mix condensers. Large-scale direct-mix heat exchangers often use a liquid film condensation solution: cooling water is sprayed onto baffles through cooling tower nozzles, where it impacts and forms a liquid film, which then condenses directly with the steam.

[0003] However, the equipment space utilization rate in the existing solutions is not high, such as Figure 1 As shown in the figure, the liquid film is mainly concentrated in the middle and lower part of the condensation zone, and the upper space near the steam inlet is not fully utilized; and the nozzles are discretely distributed at a large distance in the condensation space, resulting in low utilization of the direct contact heat exchange space. Summary of the Invention

[0004] The present application provides a compact and efficient cooler to solve the problem of low utilization of internal heat exchange space of direct-mixing heat exchange equipment in the prior art and to improve the heat exchange efficiency of the heat exchange equipment.

[0005] The present application also provides a power generation system.

[0006] According to an embodiment of the first aspect of the present application, a compact and efficient cooler comprises: a device housing, provided with a cooling water inlet, a drain port, a steam inlet, and an exhaust port, wherein the cooling water inlet is provided on the top surface of the device housing, the drain port is provided on the bottom surface of the device housing, the steam inlet is provided on the top surface of the device housing, and the exhaust port is provided on the side surface of the device housing; a guide plate disposed within the device housing, wherein cooling water enters the device housing through the cooling water inlet, flows down the guide plate, and forms a liquid film on the surface of the guide plate before being discharged from the drain port; the guide plate is arranged in a spiral shape, so that a spiral heat exchange channel for steam flow is formed between adjacent spiral turns of the guide plate; The inlet of the heat exchange channel is communicated with the steam inlet, and the outlet of the heat exchange channel is communicated with the exhaust port; the steam advances in the heat exchange channel.

[0007] According to one embodiment of the present application, the device housing is a cylindrical housing; The steam inlet is located at the center of the top surface of the device shell, and the cooling water inlet is located between the center and the edge of the top surface of the device shell.

[0008] According to one embodiment of the present application, an upper header is further provided in the device housing, the upper portion of the upper header is communicated with the cooling water inlet, and a water outlet is provided at the bottom of the upper header; The bottom of the upper header is provided with a lowest water collection point, and the bottom area of ​​the upper header is inclined toward the lowest water collection point; Along the radial direction of the device shell, the lowest point of the water collection is arranged close to the center of the circle.

[0009] According to one embodiment of the present application, the upper header is an annular box; The steam inlet is provided with an air intake pipe, one end of which extends out of the top surface of the device shell, and the other end passes through the central area of ​​the upper header and extends to the upper part of the starting end of the guide plate.

[0010] According to one embodiment of the present application, a lower header is further provided in the device housing, the bottom of the lower header is connected to the drain port, and the upper opening of the lower header is provided to collect water flowing down from the guide plate.

[0011] According to one embodiment of the present application, a guide trough assembly is further provided in the device housing, one end of the guide trough assembly extends to the upper position of the upper collecting tank, and the other end extends to the upper opening of the lower collecting tank.

[0012] According to one embodiment of the present application, an air cooling zone is further provided in the device housing, and the air cooling zone is located between the guide plate and the inner wall of the device housing; The steam discharged from the outlet of the heat exchange channel is cooled in the air cooling zone and then discharged from the exhaust port.

[0013] According to one embodiment of the present application, the guide plate is a corrugated plate, or the guide plate is provided with a concave groove.

[0014] According to one embodiment of the present application, the guide plate is provided with a concave groove: The depth direction of the concave groove is perpendicular to the steam flow direction, and / or the concave groove is a U-shaped groove, a V-shaped groove, a rectangular groove, a trapezoidal groove or a corrugated groove.

[0015] According to one embodiment of the present application, a hydrophilic coating is provided on the surface of the guide plate.

[0016] According to a second aspect of the present application, a power generation system includes: steam generator; a steam turbine generator set, receiving the steam generated by the steam generator to generate power; The cooler adopts the aforementioned compact and efficient cooler, which receives the steam used by the steam turbine generator set and enters the cooler through the steam inlet; the condensed water formed after cooling enters the steam generator through the drain port, and the other part enters the cooling tower; The cooling tower further cools the received condensed water to form cooling water, and transports the cooling water to the cooling water inlet of the cooler.

[0017] The above one or more technical solutions in the embodiments of the present application have at least one of the following technical effects: The compact and efficient cooler in this application adopts a structure different from that of existing large-scale direct-mixing heat exchange equipment. By providing a guide plate as the basis for the formation of a liquid film for cooling water, the cooling water flows from top to bottom to form a stable liquid film in the vertical direction. In this application, there is no need to use the existing nozzle spraying method to form a liquid film, and the steam flow will not be blocked in the horizontal direction. The liquid film is stably formed on the entire vertical surface of the guide plate, so that the upper and lower spaces of the heat exchange area (i.e., the area where the guide plate is located) can both achieve heat exchange between cooling water and steam, thereby improving the space utilization rate of the heat exchange area. In addition, the guide plate is configured as a spiral structure, so that heat exchange channels for heat exchange can be formed between adjacent spiral turns of the guide plate, further improving the overall space utilization rate within the device shell and reducing the volume of the cooler.

[0018] Additional aspects and advantages of the present application will be given in part in the description below, and in part will become obvious from the description below, or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the embodiments of the present application or related technologies, the following briefly introduces the drawings required for use in the embodiments or related technical descriptions. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0020] Figure 1 It is a structural diagram of a large direct-mixing heat exchange device in the prior art.

[0021] Figure 2 This is a schematic diagram of the structure of the compact and efficient cooler provided by this application Figure 1 (Front view).

[0022] Figure 3 for Figure 2 Medium AA section view (top view).

[0023] Figure 4 for Figure 3 Enlarged view of the structure of the middle C section.

[0024] Figure 5 for Figure 2 Middle BB cross-sectional view (top view).

[0025] Figure 6 This is a schematic diagram comparing the steam flow pattern on the guide plate surface in this application with the steam flow pattern on the surface of an ordinary flat plate.

[0026] Figure 7 This is a schematic diagram illustrating the volume reduction of the compact and efficient cooler in this application compared with traditional direct-mixing heat exchange equipment.

[0027] Figure 8 This is a schematic diagram of the structure of the power generation system in this application.

[0028] Reference numerals: 1. Device shell; 11. Cooling water inlet; 12. Drain port; 13. Steam inlet; 131. Air inlet pipe; 14. Exhaust port; 2. Guide plate; 21. Heat exchange channel; 3. Steam distribution area; 41. Upper header; 411. Lowest point of water collection; 42. Lower header; 43. Guide trough assembly; 44. Air cooling area; 51. Steam generator; 52. Steam turbine generator set; 53. Cooler; 54. Cooling tower; 55. Condensate pump; 56. Feed water pump; 61. Steam inlet in the prior art; 62. Cooling tower in the prior art; 63. Nozzle in the prior art; 64. Liquid film in the prior art; 65. Cooling water inlet in the prior art; 66. Drain port in the prior art. DETAILED DESCRIPTION

[0029] The following embodiments of the present invention are described in further detail with reference to the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0030] In the description of the embodiments of the present application, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the embodiments of the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as limiting the embodiments of the present application. In addition, the terms "first", "second", and "third" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0031] In the description of the embodiments of this application, it should be noted that, unless otherwise specified or limited, the terms "connected" and "connection" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art will understand the specific meanings of the above terms in the embodiments of this application based on the specific circumstances.

[0032] In the embodiments of the present application, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. Furthermore, a first feature being "above," "above," and "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0033] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the embodiments of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and the features of different embodiments or examples, unless they are contradictory.

[0034] The structure of existing large-scale direct mixing heat exchange equipment is as follows: Figure 1 As shown, it includes a steam inlet 61, a cooling tower 62, a nozzle 63 provided on the cooling tower 62, a liquid film 64 formed by the cooling water sprayed from the nozzle 63, a cooling water inlet 65, and a drain port 66. In addition to the aforementioned problem of low equipment space utilization, existing large-scale direct-mixing heat exchange equipment also has the following disadvantages during actual engineering use: 1. Poor liquid film stability. Under variable operating conditions, the pressure of the nozzle 63 on the cooling tower 62 deviates from the rated design operating conditions, and the heat transfer area cannot be maintained stably; especially under extremely low load conditions, the cooling water pump head and flow rate are low, and a stable liquid film 64 may not be formed. The steam cannot fully contact the cooling water, resulting in a sudden drop in heat exchange capacity and a risk of cooling function failure; 2. Low heat transfer area and efficiency. Direct contact heat exchange equipment is a free liquid film. The heat transfer liquid film 64 is formed freely after the nozzle 63 jets and impacts the baffle. It cannot be artificially designed and regulated, and the relative speed between the liquid film 64 and the steam develops freely, and disturbance enhancement cannot be performed on the heat transfer path; 3. Large vibration and noise. Under normal operating conditions, when the cooling water passes through the nozzle 63 jet and impacts the baffle to form the liquid film 64, obvious structural vibration and noise will be generated due to the jet impacting the baffle and the liquid film 64 hitting the shell.

[0035] Traditional direct contact heat exchange equipment (i.e., the aforementioned large direct mixing heat exchange equipment) has corresponding deficiencies in liquid film stability, heat transfer enhancement, device miniaturization, vibration and noise, etc., which limits the application of such heat exchange equipment in scenarios with variable operating conditions (especially when there are serious deviations from the design operating conditions), limited space, and high requirements for acoustic and vibration performance.

[0036] A compact and efficient cooler according to the first embodiment of the present application, such as Figure 2 and Figure 3 As shown, the compact and efficient cooler includes: a device housing 1, provided with a cooling water inlet 11, a drain port 12, a steam inlet 13, and an exhaust port 14. The cooling water inlet 11 is located on the top surface of the device housing 1, the drain port 12 is located on the bottom surface of the device housing 1, the steam inlet 13 is located on the top surface of the device housing 1, and the exhaust port 14 is located on the side of the device housing 1; a guide plate 2 is disposed within the device housing 1, and cooling water enters the device housing 1 through the cooling water inlet 11, flows down the guide plate 2, and forms a liquid film on the surface of the guide plate 2 before being discharged from the drain port 12; the guide plate 2 is arranged in a spiral shape, so that a spiral heat exchange channel 21 for steam flow is formed between adjacent spiral turns of the guide plate 2; the inlet of the heat exchange channel 21 is connected to the steam inlet 13, and the outlet of the heat exchange channel 21 is connected to the exhaust port 14; steam advances within the heat exchange channel 21. The exhaust port 14 is positioned opposite the outlet at the end of the spiral guide plate 2, increasing the distance between them.

[0037] It should be noted that the purpose of the compact and efficient cooler is to condense the steam entering the steam inlet 13 into liquid water. There is no special requirement for the temperature of the water after condensation, that is, the temperature of the water after condensation is not required to be low.

[0038] The compact and efficient cooler in the embodiment of the present application sets a guide plate 2 as a carrier for the cooling water to form a liquid film, so that after the cooling water enters the device housing 1 from the cooling water inlet 11 on the top surface of the housing, it can flow smoothly down along the guide plate 2 and form a stable liquid film on the surface of the guide plate 2, and finally be discharged from the drain port 12. This design abandons the method of relying on nozzle injection to form a liquid film in the prior art, avoids the obstruction of the steam flow caused by the nozzle in the horizontal direction, and allows the liquid film to stably cover the entire vertical surface of the guide plate 2, so that the upper space and the lower space of the heat exchange area can fully participate in the heat exchange process between cooling water and steam, effectively improving the space utilization rate of the heat exchange area and the heat exchange capacity per unit volume. The liquid film can remain stable in the vertical direction. Even when the working conditions change, the flow state of the cooling water is relatively stable, and the liquid film is not easy to break or disappear, thereby ensuring the stability of the liquid film and providing a reliable foundation for continuous and efficient heat exchange. At the same time, the guide plate 2 is arranged in a spiral shape, so that a heat exchange channel 21 for steam flow and heat exchange can be formed between adjacent spiral circles of the guide plate 2. This design allows the space in the device shell 1 to be more fully utilized. While ensuring sufficient heat exchange area, the overall volume of the cooler is significantly reduced, thereby achieving a compact design of the equipment while realizing efficient heat exchange, meeting the demand for the use of miniaturized heat exchange equipment.

[0039] In terms of heat transfer, the spiral arrangement of the guide plate 2 allows heat exchange channels 21 to be formed between adjacent spiral turns, significantly increasing the area covered by the liquid film. As steam flows through the heat exchange channels 21, it fully contacts the liquid film on the surface of the guide plate 2, increasing the heat transfer area. Furthermore, the relative motion between the steam and the liquid film is stable during flow, ensuring more complete heat transfer and improving heat exchange efficiency.

[0040] Furthermore, since the cooling water does not need to be sprayed from nozzles, the impact and vibration generated by the nozzle spraying process are avoided, and the noise caused by the spraying is also reduced. As the cooling water flows along the guide plate 2, the flow state is smooth and the interaction with the guide plate 2 is relatively mild, further reducing the generation of vibration and noise, and improving the environmental impact of the equipment during operation.

[0041] According to one embodiment of the present application, Figure 2 and Figure 3 As shown, the device housing 1 is a cylindrical housing, the steam inlet 13 is located at the center of the top surface of the device housing 1, and the cooling water inlet 11 is located between the center and the edge of the top surface of the device housing 1. The exhaust port 14 is provided on the outer circumference of the device housing 1.

[0042] The compact and efficient cooler adopts a cylindrical shell design, and the specific position setting of the steam inlet 13 and the cooling water inlet 11 further improves the heat exchange efficiency and the rationality of space utilization. The cylindrical shell itself has the characteristics of structural symmetry, which can make the internal fluid flow more uniform and reduce local vortices or flow dead corners caused by the irregular shape of the shell. The steam inlet 13 is located at the center of the top surface of the device shell 1, and the starting end of the heat exchange channel 21 corresponds to the center of the guide plate 2, so that the steam directly reaches the starting end of the heat exchange channel 21 after entering the device shell 1, and then flows along the entire spiral heat exchange channel 21, so that the steam is in full contact with the cooling water film on the surface of the guide plate 2, thereby improving the uniformity of heat exchange. It should be understood that the starting end of the heat exchange channel 21 is also the starting end of the guide plate 2.

[0043] The cooling water inlet 11 is located between the center and edge of the top surface of the device housing 1 and can provide water flow to the guide plate 2 .

[0044] In some cases, the device housing 1 may also be a polygonal prism with a cross section close to a circle, for example, the device housing 1 may be a prism with a regular polygonal cross section.

[0045] According to one embodiment of the present application, Figure 2 As shown, an upper collecting tank 41 is further provided in the device shell 1, the upper part of the upper collecting tank 41 is connected to the cooling water inlet 11, and a water outlet is provided at the bottom of the upper collecting tank 41; a lowest water collection point 411 is provided at the bottom of the upper collecting tank 41, and the bottom area of ​​the upper collecting tank 41 is inclined toward the lowest water collection point 411; along the radial direction of the device shell 1, the lowest water collection point 411 is arranged close to the center of the circle.

[0046] The upper header 41, located within the device housing 1, communicates with the cooling water inlet 11 through its upper portion. It receives, temporarily stores, and distributes the cooling water entering the device housing 1. Multiple, evenly distributed outlets are located at the bottom of the upper header 41, guiding the cooling water evenly to the guide plates 2 below. This ensures a relatively balanced flow of water across all locations on the guide plates 2, preventing uneven cooling water distribution from causing thin or missing liquid films on portions of the guide plates 2. This ensures stable heat exchange within each heat exchange channel 21.

[0047] The design of the lowest water collection point 411 at the bottom of the upper collecting tank 41, combined with the structure of the bottom area tilted toward the lowest point, can collect the cooling water in the upper collecting tank 41 to the lowest water collection point 411 under low-load conditions with less cooling water flow, so that the limited cooling water is concentrated and flows out from the water outlet near the lowest water collection point 411.

[0048] The lowest water collection point 411 allows a smaller amount of cooling water to be collected, and the concentrated cooling water can flow precisely to the starting end of the guide plate 2 near the center of the circle, that is, to ensure that a stable liquid film is formed on the wall surface at the starting end of the guide plate 2. At this time, the steam entering the heat exchange channel 21 through the steam inlet 13 can fully contact the stable liquid film, effectively solving the problem of liquid film instability caused by insufficient water under low-load conditions and ensuring the cooling effect. Of course, the lowest water collection point 411 at the bottom of the upper header 41 can also be set at other locations, such as: the lowest water collection point 411 can be set close to the outermost spiral circle of the guide plate 2.

[0049] At the same time, under conditions of high cooling water flow, the evenly distributed water outlets can fully function, allowing the cooling water to be evenly distributed through the multiple outlets to all spiral turns of the guide plate 2, meeting the liquid film formation requirements throughout the heat exchange channel 21 and adapting to the heat exchange needs of high-load conditions. This structural design not only achieves uniform cooling water distribution, but also adapts to low-load scenarios through the concentrated effect of the lowest water collection point 411, improving the equipment's adaptability to different operating conditions.

[0050] According to one embodiment of the present application, Figure 2 As shown, the upper header 41 is an annular box body; the steam inlet 13 is provided with an air intake pipe 131, one end of the air intake pipe 131 extends out of the top surface of the device shell 1, and the other end passes through the central area of ​​the upper header 41 and extends to the upper part of the starting end of the guide plate 2.

[0051] In some cases, a water inlet pipe may be provided at the cooling water inlet 11 on the device housing 1, a water outlet pipe may be provided at the drain port 12, and an exhaust pipe may be provided at the exhaust port 14 and used in conjunction with an exhaust assembly.

[0052] The annular upper header 41, combined with the aforementioned lowest water confluence point 411, forms a concave tank design with a "low center and high periphery," where the water level gradually decreases from the center outward. The steam distribution area 3 (the distribution region before steam enters the heat exchange channel, located in the center of the spiral guide plate 2), which communicates with the steam inlet 13, is located below the center of the upper header 41. This design serves two purposes: First, because the steam temperature and pressure at the starting point of the heat exchange channel 21 near the steam distribution area 3 are relatively high, it is a critical area that affects the heat transfer efficiency of the cooler. Positioning the steam distribution area 3 below the center of the upper header 41 shortens the liquid film flow distance, increases the liquid film descent rate within the cooling zone (i.e., the area where the guide plate 2 is located) near the center of the steam distribution area 3, and enhances convection between the cooling water and the relatively high-temperature steam near the steam distribution area 3, thereby further improving the overall heat transfer efficiency of the cooler. Secondly, when the demand for cooling water decreases during low-load operation of the heat exchanger and the liquid level in the upper header 41 drops, the cooling water can still form an effective heat exchange liquid film on the surface of the guide plate 2 in the central ring area near the steam distribution area 3, thereby improving the cooling capacity of the heat exchanger under low-load conditions.

[0053] In addition, the upper collecting box 41 of the annular box body can better adapt to the internal space of the device shell 1, and its annular structure can provide a more uniform basis for the distribution of cooling water in the circumferential direction, so that the cooling water can flow more smoothly toward the guide plate 2 after entering from the cooling water inlet 11, which helps to form a more stable liquid film on the surface of the guide plate 2.

[0054] The air inlet pipe 131 passes through the center of the upper header 41 and extends above the starting end of the guide plate 2, allowing steam to be delivered directly to the starting point of the heat exchange channel 21. This reduces flow losses and path deviation before the steam enters the heat exchange channel 21. After exiting the air inlet pipe 131, the steam quickly enters the heat exchange channel 21 formed by the adjacent spiral turns of the spiral guide plate 2. This prevents irregular steam diffusion in the upper space of the device housing 1 and ensures that the steam flows along the pre-defined heat exchange channel 21, thereby fully contacting the cooling water film on the surface of the guide plate 2, thereby improving the effectiveness of heat exchange.

[0055] At the same time, the arrangement of the air intake pipe 131 passing through the center area of ​​the upper header 41 does not interfere with the normal function of the annular upper header 41. The annular space of the upper header 41 and the central passage of the air intake pipe 131 form a reasonable spatial layout, which fully utilizes the space at the top of the device housing 1, avoids spatial conflicts between components, further reduces the overall volume of the cooler, and enhances the compactness of the device. This structure continues the characteristic of not requiring nozzle injection to form a liquid film, does not block the flow of steam in the horizontal direction, and allows the upper and lower spaces of the heat exchange area to achieve effective heat exchange. Combined with the structure of the spiral guide plate 2, it further improves the space utilization and heat exchange efficiency within the device housing 1.

[0056] According to one embodiment of the present application, Figure 2 As shown, a lower header 42 is further provided in the device housing 1. The bottom of the lower header 42 is connected to the drain port 12. The upper portion of the lower header 42 is opened to collect water flowing down from the guide plate 2. The shape of the lower header 42 can correspond to the shape of the device housing 1, for example, the lower header 42 can be a cylindrical box.

[0057] The upper opening allows lower header 42 to fully collect water flowing from all parts of deflector plate 2. Regardless of the distribution of deflector plate 2 within the device housing 1, water flowing down the surface of deflector plate 2 can smoothly enter lower header 42, preventing the accumulation or leakage of cooling water at the bottom of the device housing 1 and ensuring sufficient cooling water recovery. Water flowing from deflector plate 2 is concentrated in lower header 42 and then discharged in an orderly manner through drain port 12, avoiding interference caused by the random flow of water within the device housing 1 and helping to maintain a stable operating environment for the device's internal structure.

[0058] After the collected water is discharged through the drain port 12 at the bottom of the lower collecting tank 42, it can be introduced into the device shell 1 again through the cooling water inlet 11 after cooling treatment, forming a cooling water recycling process, reducing the continuous input demand for new cooling water, reducing water resource consumption, and also reducing operating costs related to water resources.

[0059] In some cases, a diversion assembly can be installed inside the lower header 42. The diversion assembly is inclined from the edge of the lower header 42 toward the drain outlet 12 at the bottom. This allows water entering the lower header 42 to converge toward the drain outlet 12 more quickly, reducing the time the water stays inside the lower header 42 and the risk of sediment accumulation that may occur due to prolonged retention. Furthermore, an anti-corrosion coating can be provided on the inner wall of the lower header 42 to enhance its resistance to corrosive substances that may be contained in the water and extend its service life.

[0060] In actual applications, a filter can also be installed at the drain port 12 to intercept impurities that may be carried in the water and prevent them from entering the subsequent cooling treatment system, thereby ensuring the cleanliness of the circulating cooling water, avoiding impurities from clogging or wearing the cooling equipment, and further improving the stability and reliability of the cooling water circulation system.

[0061] According to one embodiment of the present application, Figure 2 As shown, a guide trough assembly 43 is further provided in the device housing 1 , one end of the guide trough assembly 43 extends to the upper position of the upper header 41 , and the other end extends to the upper opening of the lower header 42 .

[0062] The guide trough assembly 43 provided in the device shell 1 extends at one end to the upper position of the upper header 41 and at the other end to the upper opening of the lower header 42. When the water volume in the upper header 41 exceeds the maximum capacity, the excess cooling water can be promptly drained to the lower header 42 through the guide trough assembly 43 to avoid leakage of the excess cooling water, thereby ensuring that the upper header 41 always supplies water downward in a stable state, thereby providing continuous support for the formation of a uniform liquid film on the surface of the guide plate 2.

[0063] The multi-porous structure of the guide trough assembly 43 disperses the cooling water into multiple small streams as it flows through it, reducing the impact and vibration generated by the water flowing within the guide trough assembly 43, thereby effectively reducing noise. Furthermore, the dispersed water flow enters the lower header 42 more smoothly, avoiding the splashing and increased noise caused by a large amount of water directly impacting the inner wall of the lower header 42, thus contributing to a quieter equipment operating environment.

[0064] The guide trough assembly 43 may be arranged outside the guide plate 2 , and the upper and lower ends are respectively connected to the upper header 41 and the lower header 42 , that is, the guide trough assembly 43 may be a component with a ring-shaped cross section.

[0065] According to one embodiment of the present application, Figure 2 and Figure 3 As shown, an air cooling zone 44 is further provided in the device shell 1 , and the air cooling zone 44 is located between the guide plate 2 and the inner wall of the device shell 1 ; the steam discharged from the outlet of the heat exchange channel 21 is cooled in the air cooling zone 44 and then discharged from the exhaust port 14 .

[0066] The compact and efficient cooler is provided with an air cooling zone 44 in the device shell 1, and the air cooling zone 44 is located between the guide plate 2 and the inner wall of the device shell 1, so that the steam discharged from the outlet of the heat exchange channel 21 can be further cooled in the air cooling zone 44 before being discharged from the exhaust port 14, thereby improving the condensation efficiency of the steam and making full use of the idle space in the device shell 1.

[0067] After the steam exchanges heat with the cooling water film on the surface of the guide plate 2 in the heat exchange channel 21, some uncondensed steam may still be discharged from the outlet of the heat exchange channel 21. The provision of the air-cooling zone 44 provides additional cooling space for this uncondensed steam, allowing the steam to exchange heat with the inner wall of the device housing 1 and the air in the air-cooling zone 44 as it flows toward the exhaust port 14, thereby achieving further condensation, reducing the amount of uncondensed steam discharged from the exhaust port 14, and improving the overall condensation effect.

[0068] Air-cooling zone 44, located between guide plate 2 and the inner wall of device housing 1, provides secondary cooling for the steam, ensuring improved condensation efficiency while maintaining the cooler's compactness. This design also creates a progressive cooling path for the steam, with primary condensation occurring within heat exchange channel 21 through contact with the cooling water film, followed by subsequent condensation within air-cooling zone 44 through heat exchange with the surrounding environment. These two cooling methods work together to further optimize the condensation effect.

[0069] The existence of the air-cooling zone 44 will not interfere with the steam flow and the formation of the cooling water film in the heat exchange channel 21, because it is located outside the guide plate 2 and is relatively independent of the area where the heat exchange channel 21 is located, ensuring efficient heat exchange in the heat exchange channel 21. The subsequent air-cooling process also improves the overall condensation efficiency, making the performance of the entire cooler more stable and reliable.

[0070] In some cases, a number of heat sinks can be installed on the inner wall of the device housing 1 corresponding to the air-cooling zone 44. The heat sinks can increase the contact area between the device housing 1 and the steam in the air-cooling zone 44, thereby enhancing the heat exchange effect of the air-cooling zone 44 and allowing the incompletely condensed steam to complete heat exchange more quickly in the air-cooling zone 44. At the same time, a heat dissipation fan can be installed outside the device housing 1 corresponding to the air-cooling zone 44. The fan drives the air flow around the air-cooling zone 44, accelerating the heat exchange rate between the steam in the air-cooling zone 44 and the external environment, further improving the cooling efficiency of the air-cooling zone 44.

[0071] According to one embodiment of the present application, the guide plate 2 is a corrugated plate, or the guide plate 2 is provided with a concave groove.

[0072] The following takes "the guide plate 2 is provided with a concave groove" as an example to specifically explain the role of the guide plate 2 in the heat exchange process between cooling water and steam: First, the concave grooves on guide plate 2 increase the vapor-liquid contact heat exchange area by changing the distribution of the liquid film. As cooling water flows along guide plate 2, the concave grooves guide the liquid film to spread into and around the grooves. This allows the liquid film to no longer be confined to the flat surface of guide plate 2, but instead fill the interior of the grooves and cover the sidewalls and bottom of the grooves, creating a wider coverage area on the surface of guide plate 2. This expanded liquid film distribution increases the contact area between the steam and the liquid film, providing a larger exchange interface for heat transfer and helping to improve overall heat exchange capacity.

[0073] Second, the concave grooves can disturb the steam flowing within heat exchange channel 21, thereby enhancing the energy and mass transfer between the steam and the liquid film. As the steam flows through heat exchange channel 21, it interacts with the contours of the concave grooves. The concave-convex structure formed by the groove sidewalls and bottom disrupts the laminar flow of the steam, causing the steam to form local eddies and turbulence near the grooves. This change in flow allows the steam to more fully contact the liquid film, reducing the thermal resistance between the steam and the liquid film, accelerating the heat transfer rate, and thus improving the heat and mass transfer coefficient.

[0074] Third, when the steam flows along the surface of the guide plate 2, the concave grooves on the surface of the guide plate 2 will destroy the smooth flow of the steam: Figure 6 As shown, at the place where the shape of the concave groove changes suddenly, the steam forms a circulating vortex due to the flow separation effect - secondary flow.

[0075] The concave groove profile allows the steam to convert kinetic energy and pressure energy during its "contraction-expansion" flow path, thereby inducing vortices. These vortices are not disordered turbulence, but rather structured secondary flows with stable rotational directions. On the one hand, the vortices continuously disturb the main steam stream, increasing the contact frequency and mixing between the steam and the liquid film on the surface of the guide plate 2. On the other hand, the vortex group fills the gaps in the groove, reducing the frictional resistance between the main steam stream and the groove wall, while maintaining steam flow stability and helping to increase the pressure and saturation temperature at the rear end (i.e., the end of the spiral heat exchange channel 21, or the outlet of the spiral heat exchange channel 21).

[0076] Through the synergistic effect of the heat flow in the above three aspects, the total volume of the cooler can be significantly reduced under the same heat exchange demand. Taking into account the heat transfer coefficient, area and temperature difference, the volume can be reduced to less than 90% of the traditional direct hybrid heat exchange equipment; and the higher the heat load of the heat exchange equipment, the more significant the volume reduction. For direct hybrid heat exchange equipment with a capacity of more than 100MW, the volume can be reduced by more than 40%. Figure 7 shown.

[0077] In some cases, denser and deeper grooves can be installed in the front section of heat exchange channel 21 to enhance the initial disturbance of the steam, while sparser and shallower grooves can be installed in the back section to maintain steam flow stability, so that the groove functions in different areas are more closely matched to the steam flow state. At the same time, tiny bumps can be added to the inner wall of the groove to further break up the boundary layer on the liquid film surface and enhance local heat and mass transfer processes.

[0078] According to one embodiment of the present application, the guide plate 2 is provided with a concave groove: the depth direction of the concave groove is perpendicular to the steam flow direction, and / or the concave groove is a U-shaped groove, a V-shaped groove, a rectangular groove, a trapezoidal groove or a corrugated groove.

[0079] The concave grooves on the surface of guide plate 2, with their depth perpendicular to the steam flow direction, guide the steam to generate secondary vortices near the groove contours. The grooves can be U-shaped, V-shaped, rectangular, trapezoidal, or corrugated, adapting to diverse flow field control needs through different profile characteristics. As steam flows along the surface of guide plate 2, the vertical distribution of the groove depth causes the steam flow to separate as it crosses the groove body. Combined with the geometric differences in the groove shape, this continuously disturbs the main steam flow.

[0080] On the one hand, the concave groove increases the spreading range of the liquid film on the guide plate 2 through the complex surface, thereby increasing the vapor-liquid contact heat exchange area; on the other hand, the secondary vortex induced by the concave groove can enhance the energy and mass exchange between the steam and the liquid film, fill the groove gap to reduce the steam flow resistance, help the steam maintain a higher pressure and saturation temperature in the later section, and optimize the heat transfer temperature difference.

[0081] According to one embodiment of the present application, a hydrophilic coating is provided on the surface of the guide plate 2 .

[0082] The hydrophilic coating provided on the surface of the guide plate 2, by virtue of its own hydrophilicity and viscosity, allows the cooling water to quickly infiltrate and evenly spread along the vertical wall surface during its descent, forming a continuous and stable liquid film. In a high-speed steam scouring environment, the viscosity of the hydrophilic coating can effectively inhibit the wrinkling and stacking of the liquid film, maintain the complete shape and effective heat exchange area of ​​the liquid film, and ensure the continuous stability of the vapor-liquid contact interface. At the same time, the dynamic bonding effect formed between the hydrophilic coating and the cooling water not only strengthens the bonding stability between the liquid film and the surface of the guide plate 2, but also forms a flexible buffer for the lateral flow of steam in the concave groove area. With the help of this dynamic interaction, the flow resistance of the steam when flowing through the groove surface is reduced, helping the steam to maintain a higher pressure and corresponding saturation temperature in the rear section of the heat exchange channel 21, optimizing the heat transfer temperature difference and improving the condensation efficiency.

[0083] The hydrophilic coating can be made of a highly viscous hydrogel material or a hydrophilic polymer coating.

[0084] The compact and efficient cooler provided in the embodiment of the present application operates as follows: Steam and cooling water, two working media, enter the cooler through different inlets, fully contact and mix before heat exchange. Condensed water is discharged from the drain port 12, and non-condensable gases are discharged from the exhaust port 14. The flow paths of the two media are as follows: Steam enters the device shell 1 through steam inlet 13, passes through steam distribution area 3, and enters the cooling zone (i.e., the area where guide plate 2 is located). It flows along the spiral heat exchange channel 21. During this process, it evenly mixes with the cooling water film (i.e., liquid film) attached to the side wall of guide plate 2, is fully cooled to form condensate, and then injected into the lower header 42 and discharged through drain port 12. Non-condensable gases such as air finally gather in the air cooling zone 44 and are extracted by an exhauster connected to the exhaust port 14.

[0085] The cooling water enters the cooler through the cooling water inlet 11, passes through the upper header 41 and enters the spiral heat exchange channel 21 of the cooling zone; under the action of gravity, the cooling water flows downward along the wall of the guide plate 2 of the cooling zone and exchanges heat with the steam, and finally gathers into the lower header 42 and is discharged through the drain port 12.

[0086] The bottom interface of the upper header 41 is in the form of a concave water tank with "low in the middle and high around", and the water level gradually decreases from the center to the outside; the steam distribution area 3 connected to the steam inlet 13 is set below the central area of ​​the upper header 41.

[0087] On the one hand, since the steam temperature and pressure at the starting end of the spiral heat exchange channel 21 near the steam distribution area 3 is relatively high, it is a key area affecting the heat transfer effect of the cooler. Setting the steam distribution area 3 below the central area of ​​the upper header 41 can shorten the liquid film flow distance, increase the liquid film descent speed in the central ring area near the steam distribution area 3 in the cooling zone, and strengthen the convection between the cooling water and the relatively high-temperature steam near the steam distribution area 3, thereby further improving the overall heat transfer efficiency of the cooler.

[0088] On the other hand, when the heat exchanger operates at low load and the cooling water demand decreases and the liquid level in the upper header 41 drops, the cooling water can still form an effective heat exchange liquid film on the surface of the guide plate 2 in the central ring area near the steam distribution area 3, thereby improving the cooling capacity of the heat exchanger under low load conditions.

[0089] When the cooler is operating normally, cooling water is oversupplied, and the excess cooling water flows into the lower header 42 through the guide trough assembly 43, thereby maintaining a constant pressure differential between the upper header 41 and the lower header 42. The gravitational potential difference drives the cooling water downward, ensuring the stable maintenance of the liquid film state under different operating conditions and the constant consistency of the steam-water contact heat exchange effect, eliminating the operational control difficulties caused by inconsistent liquid film state and changes in heat transfer performance due to changes in cooling water flow. When cooling water is oversupplied, the guide trough assembly 43 directly guides the excess cooling water into the lower header 42, setting a reasonable upper limit for the water storage capacity of the upper header 41 and the cooling water flow rate. In addition, the installation of the guide trough assembly 43 can avoid vibration caused by splashing cooling water, thereby significantly reducing the noise of the cooler operation. The higher the cooling water flow rate, the greater the noise reduction compared to direct splashing of traditional direct-mix heat exchange equipment.

[0090] The compact and efficient cooler provided in the embodiments of this application effectively addresses issues such as unstable liquid film caused by inconsistent nozzle pressure, a sharp drop in heat transfer capacity under low-load conditions, an inability to expand the steam-water contact surface and enhance heat transfer, and high structural vibration and noise in conventional direct-mix heat exchange equipment. This enhances the cooler's and the cooling system's adaptability to variable operating conditions (especially extremely low operating conditions), while also improving equipment compactness and reducing vibration and noise.

[0091] According to a second aspect of the present application, a power generation system is provided. Figure 8 As shown, the power generation system includes: a steam generator 51; a steam turbine generator set 52, which receives steam generated by the steam generator 51 for generating power; a cooler 53, which adopts the aforementioned compact and efficient cooler, receives steam used by the steam turbine generator set 52 and enters the cooler 53 through the steam inlet 13; the condensed water formed after cooling enters the steam generator 51 through the drain port 12, and the other part enters the cooling tower 54; the cooling tower 54 further cools the received condensed water to form cooling water, and transports the cooling water to the cooling water inlet 11 of the cooler 53.

[0092] The steam generated by the steam generator 51 enters the steam turbine generator set 52 to generate power and is then discharged into the cooler 53. The condensed water is pressurized by the condensate pump 55 and then divided into two paths: one path enters the cooling tower 54, where it is cooled by the air and then discharged back to the cooler 53 as cooling water; the other path is sent to the feed water pump 56 for further pressurization and finally enters the steam generator 51 for heating and evaporation to produce steam, further participating in the power cycle. During actual installation, by lowering the installation height of the cooler 53, the cooling water from the cooling tower 54 can be delivered to the cooler 53 via gravity potential difference, thereby achieving natural circulation heat dissipation without the need for a cooling water pump, further improving the system's power generation efficiency.

[0093] The power generation system forms a complete steam cycle and cooling cycle through the coordinated operation of the steam generator 51, the steam turbine generator set 52, the cooler 53 (i.e., the compact and efficient cooler mentioned above) and the cooling tower 54: the steam generated by the steam generator 51 enters the steam turbine generator set 52 to generate power, and the used steam enters the cooler 53 through the steam inlet 13 of the compact and efficient cooler.

[0094] Cooler 53 efficiently condenses used steam, rapidly converting it into condensed water. After being discharged through drain port 12, part of the steam flows back to steam generator 51 to resume steam generation, while the remaining part enters cooling tower 54 for cooling, thus recycling water resources and reducing the system's reliance on external water sources. Cooling tower 54 further cools the condensed water, ensuring that the cooling water delivered to cooler 53 remains at a relatively low temperature. This enhances the heat exchange temperature difference within cooler 53, improves condensation efficiency, and thus maintains the stability of the exhaust pressure of steam turbine generator set 52, ensuring the economic operation of the unit.

[0095] The compact structure and efficient heat exchange characteristics of the compact and efficient cooler make the entire power generation system layout more compact, reducing the floor space, and are particularly suitable for installation scenarios with limited space. At the same time, the closed-loop design of the cooling and steam circulation reduces energy and water waste, improving the system's environmental performance and operational stability.

[0096] Finally, it should be noted that the above embodiments are intended only to illustrate the present application and are not intended to limit the present application. Although the present application has been described in detail with reference to the embodiments, those skilled in the art will appreciate that various combinations, modifications, or equivalent substitutions of the technical solutions of the present application do not depart from the spirit and scope of the technical solutions of the present application and are intended to be encompassed by the claims of the present application.

Claims

1. A compact and efficient cooler, characterized in that: include: The device housing (1) is provided with a cooling water inlet (11), a liquid discharge port (12), a steam inlet (13) and an exhaust port (14), wherein the cooling water inlet (11) is provided on the top surface of the device housing (1), the liquid discharge port (12) is provided on the bottom surface of the device housing (1), the steam inlet (13) is provided on the top surface of the device housing (1), and the exhaust port (14) is provided on the side surface of the device housing (1); The guide plate (2) is arranged in the device housing (1), and cooling water enters the device housing (1) through the cooling water inlet (11), flows down along the guide plate (2), forms a liquid film on the surface of the guide plate (2), and is discharged from the drain port (12); the guide plate (2) is arranged in a spiral shape, so that a spiral heat exchange channel (21) for steam flow is formed between adjacent spiral turns of the guide plate (2); The inlet of the heat exchange channel (21) is in communication with the steam inlet (13), and the outlet of the heat exchange channel (21) is in communication with the exhaust port (14); the steam advances in the heat exchange channel (21).

2. The compact and efficient cooler according to claim 1, characterized in that The device housing (1) is a cylindrical housing; The steam inlet (13) is located at the center of the top surface of the device shell (1), and the cooling water inlet (11) is located between the center of the top surface and the edge of the top surface of the device shell (1).

3. The compact and efficient cooler according to claim 2, characterized in that An upper header (41) is further provided in the device housing (1), the upper portion of the upper header (41) is in communication with the cooling water inlet (11), and a water outlet is provided at the bottom of the upper header (41); The bottom of the upper header (41) is provided with a lowest water collection point (411), and the bottom area of ​​the upper header (41) is inclined toward the lowest water collection point (411); Along the radial direction of the device housing (1), the lowest water collection point (411) is located close to the center of the circle.

4. The compact and efficient cooler according to claim 3, characterized in that The upper header (41) is an annular box; The steam inlet (13) is provided with an air intake pipe (131), one end of which extends out of the top surface of the device housing (1), and the other end of which passes through the central area of ​​the upper header (41) and extends to the upper part of the starting end of the guide plate (2).

5. The compact and efficient cooler according to claim 3, characterized in that A lower header (42) is also provided in the device housing (1), the bottom of the lower header (42) is in communication with the drain port (12), and an upper opening of the lower header (42) is provided to collect water flowing down from the guide plate (2).

6. The compact and efficient cooler according to claim 5, characterized in that A guide trough assembly (43) is also provided in the device housing (1), one end of the guide trough assembly (43) extending to the upper position of the upper header (41), and the other end extending to the upper opening of the lower header (42).

7. The compact and efficient cooler according to any one of claims 1 to 6, characterized in that An air cooling zone (44) is further provided in the device housing (1), and the air cooling zone (44) is located between the guide plate (2) and the inner wall of the device housing (1); The steam discharged from the outlet of the heat exchange channel (21) is cooled in the air cooling zone (44) and then discharged from the exhaust port (14).

8. The compact and efficient cooler according to any one of claims 1 to 6, characterized in that The guide plate (2) is a corrugated plate, or the guide plate (2) is provided with a concave groove.

9. The compact and efficient cooler according to claim 8, characterized in that Based on the fact that the guide plate (2) is provided with a concave groove: The depth direction of the concave groove is perpendicular to the steam flow direction, and / or the concave groove is a U-shaped groove, a V-shaped groove, a rectangular groove, a trapezoidal groove or a corrugated groove.

10. The compact and efficient cooler according to any one of claims 1 to 6, characterized in that The surface of the guide plate (2) is provided with a hydrophilic coating.

11. A power generation system, characterized in that: include: Steam generator (51); A steam turbine generator set (52) receives steam generated by the steam generator (51) to generate power; The cooler (53) adopts the compact and efficient cooler as claimed in any one of claims 1 to 10, receives the steam used by the steam turbine generator set (52) and enters the cooler (53) through the steam inlet (13); the condensed water formed after cooling enters the steam generator (51) through the drain port (12), and the other part enters the cooling tower (54); The cooling tower (54) further cools the received condensed water to form cooling water, and transports the cooling water to the cooling water inlet (11) of the cooler (53).

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