Steam generating equipment

Abstract

Disclosed is a steam generating apparatus comprising: a burner; a first flue gas flow channel and a main heat exchange flow channel are defined in the steam generation body; water in the main heat exchange runner exchanges heat with flue gas formed by combustion of the combustor and is heated to form primary steam; the drain heat recovery mechanism comprises a tubular cyclone throttling steam-water separator which is used for carrying out steam-water separation on the primary steam output by the steam generation body to form target steam and drain water, and the tubular cyclone throttling steam-water separator is provided with a steam output end, a drain water output end and an input pipe; the input pipe is communicated with the downstream of the main heat exchange runner so as to input the primary steam; the geometric volume of the tubular cyclone throttling steam-water separator is less than 5L; furthermore, the geometric volume of the tubular cyclone throttling steam-water separator is less than 3L; and the waste heat recovery heat exchanger is provided with a first flow channel and a second flow channel.

Description

Technical Field

[0001] This invention relates to the field of steam generation technology, and more particularly to a steam generation device. Background Technology

[0002] Under the national call for energy conservation and emission reduction, steam generating equipment is accelerating its development towards highly efficient, low-emission, fully premixed condensing steam generators. In particular, the inspection-free / report-free once-through gas-fired steam generators, compared to traditional steam boilers, produce steam faster, are more energy-efficient and environmentally friendly, and do not require installation, inspection, or annual boiler audits. They are widely favored by the market and are extensively used in national production and daily life, such as in hotels, restaurants, food processing, textiles, chemicals, and feed processing industries.

[0003] However, most of the existing inspection-exempt once-through gas-fired steam generators on the market have excessive actual water volume. Especially after the promulgation and implementation of the 2020 version of the boiler code, the calculation method for water volume was clarified, namely, the total geometric volume inside the steam-water system inlet and outlet, which includes the entire pressurized space from the feedwater pump outlet to the equipment's steam outlet. Based on this calculation method, the water volume of most once-through gas-fired steam generators on the market far exceeds 30 liters. This not only fails to meet the boiler code's inspection-exempt standard, but also poses a significant safety hazard because the condenser installed inside the equipment, as a pressure-bearing component, has high pressure requirements.

[0004] To address the aforementioned issues and reduce the water volume of the steam generator, Rejing Energy Saving Technology has filed an invention patent application (publication number CN114508745A) for a novel once-through steam generator or steam boiler and its heat exchange unit. This patent employs a single-ring riser structure in conjunction with a burner to achieve a small-volume steam generator structure. Furthermore, Rejing Energy Saving Technology has filed an invention patent application (publication number CN115614722A) for a steam generating device and its operating method. This invention patent also employs a dual-pump operating system in conjunction with a buffer to solve the cavitation problem.

[0005] Although the small-volume steam generator disclosed in the above patent can solve the technical problem of producing steam under small volume conditions, in actual use, the steam dryness of small water volume boilers is limited by the small steam-water space inside the furnace body, making it difficult to guarantee the steam dryness at the boiler outlet. Summary of the Invention

[0006] Before describing the specific structure of this invention, it is necessary to explain the steam-water separation technology in existing steam generation systems. In traditional industrial boilers or steam generator applications, especially for small-volume equipment, to improve steam dryness, a steam-water separator is usually installed at the boiler steam outlet to separate the output fluid into steam and water, thereby separating the steam with increased dryness and condensate. Traditional steam-water separators require a certain amount of space for steam-water separation to ensure the separation mechanism is effective. Currently, most methods use gravity separation or centrifugal separation for steam-water separation, and the overall volume of the steam-water separator is difficult to reduce.

[0007] In addition, there are currently two main recovery paths for the hydrophobic residues generated after gas-liquid separation, both of which have significant technical drawbacks: Path 1: Direct return to the pure water tank. The high-temperature condensate is directly piped back to the pure water tank.

[0008] Disadvantage 1 (Severe heat loss): Although the hydrophobic condensate carries high-grade heat energy (such as sensible heat above 100℃), when it is directly injected into the room temperature pure water tank, the heat is instantly diluted by a large amount of cold water. Moreover, the pure water tank is usually a non-insulated container, and the heat is lost through the surface of the tank. This part of the high-grade heat energy cannot be effectively used to preheat the boiler feedwater, resulting in low overall thermal efficiency of the system.

[0009] Disadvantage 2 (Risk of Increased TDS): Although the condensate from the steam-water separation is theoretically distilled water, in actual operation, it easily dissolves metal ions or carries rust impurities from the pipes as it flows through metal pipes, valves, and separators. Furthermore, if steam-water eutectic occurs in the boiler, a large amount of boiler water salt will concentrate in the condensate. Directly recirculating this "dirty water" back to the pure water tank will cause the total dissolved solids (TDS) level in the tank to gradually increase. High-TDS feedwater re-entering the boiler will accelerate scale formation in the boiler shell, severely impacting boiler lifespan and safety.

[0010] Pathway 2: Return to the front end of water treatment equipment (RO / filtration). To solve the TDS problem, some technologies attempt to guide the condensate back to the front end of reverse osmosis or ion exchange equipment for further treatment.

[0011] Disadvantages (total heat loss): Precision water treatment components such as reverse osmosis membranes have strict limitations on inlet water temperature (usually below 45°C). Therefore, the high-temperature hydrophobic material must be forcibly cooled before entering the filtration system. This means that the valuable heat energy carried by the hydrophobic material must be completely discharged as waste heat, resulting in a huge waste of energy.

[0012] In view of at least one of the above-mentioned technical problems, one object of this application is to provide a steam generating device that can improve the quality of steam.

[0013] To achieve at least one of the above objectives, the present invention adopts the following technical solution: A steam generating device, comprising: Burner; The steam generating body is defined by a first flue gas flow channel and a main heat exchange flow channel; the water in the main heat exchange flow channel exchanges heat with the flue gas generated by the combustion of the burner to form primary steam. Hydrophobic heat recovery mechanisms include: A tubular cyclone throttling steam-water separator is used to separate the primary steam output from the steam generator into target steam and condensate. It has a steam output end, a condensate output end, and an input pipe. The input pipe is connected downstream of the main heat exchange channel to input the primary steam. The geometric volume of the tubular cyclone throttling steam-water separator is less than 5L; further, the geometric volume of the tubular cyclone throttling steam-water separator is less than 3L. A waste heat recovery heat exchanger having a first flow channel and a second flow channel; the first flow channel having a first inlet end and a first outlet end; the second flow channel having a second inlet end and a second outlet end; wherein, the first inlet end is connected to the condensate outlet end; the second inlet end is connected to the inlet pump, and the second outlet end is connected upstream of the main heat exchange flow channel; the condensate input into the first flow channel is used to heat the water in the second flow channel.

[0014] As one aspect of the present invention, the steam generating device further includes: a condensing heat exchanger defining a second flue gas flow channel and a preheating flow channel; the second flue gas flow channel is connected downstream of the first flue gas flow channel in the flue gas flow direction; the preheating flow channel is connected upstream of the main heat exchange channel in the water flow direction; the water in the preheating flow channel exchanges heat with the flue gas in the first flue gas flow channel to preheat it; wherein, the second water outlet is connected to the preheating water inlet of the preheating flow channel.

[0015] As one aspect of the present invention, the tubular cyclone throttling steam-water separator includes: The outer tube shell extends longitudinally; the upper end of the outer tube shell is provided with a steam output end, and the lower end is provided with a condensate output end; A central tube is fixedly installed inside the outer shell and extends together with the outer shell; the upper end of the central tube has an outlet and the lower end has an inlet; a spiral separation channel extending spirally from top to bottom around the central tube and an empty annulus connected to the bottom of the spiral separation channel are provided between the central tube and the outer shell; the upper end of the spiral separation channel is blocked. The input pipe is fixedly connected to the outer shell, with one end connected to the spiral separation channel and the other end connected to the steam generator body to input primary steam.

[0016] As one aspect of the present invention, at least one perforated plate or wire mesh is provided at the lower inlet or upper outlet of the central tube or inside the central tube; the perforated plate is provided with a plurality of through holes.

[0017] As one aspect of the present invention, one of the input pipe and the steam output end is provided with a throttling section, which has a throttling orifice; optionally, the throttling section is a throttling plate disposed at the port of the input pipe or the port of the steam output end.

[0018] As one aspect of the present invention, the outer shell and the central tube are coaxially arranged; a spiral guide vane forming the spiral separation channel is provided between the outer shell and the central tube; no spiral guide vane is provided in the empty annulus; optionally, the length of the empty annulus is 0.5-0.8 times the outer diameter of the outer shell; the outer diameter of the central tube is 0.3 to 0.7 times the outer diameter of the outer shell, preferably, the outer diameter of the central tube is 0.5 times the outer diameter of the outer shell.

[0019] As one aspect of the present invention, the spiral guide vane is spirally fixedly connected to the outer wall of the central tube; a first flow gap is provided between the spiral guide vane and the inner wall of the outer tube shell, specifically, the width of the first flow gap is >0.1mm.

[0020] As one aspect of the present invention, the input tube is perpendicularly connected to the outer shell; the central axis of the input tube is offset from the central axis of the outer shell; along the axial direction of the input tube, the outer wall of the central tube is located within the annular projection of the input tube 51; further, the outer diameter of the input tube is 0.5 times the outer diameter of the outer shell.

[0021] The beneficial effects of this invention are as follows: The tubular cyclone throttling steam-water separator of the present invention achieves comprehensive capture of large, medium and small-diameter water droplets in a compact space through a multi-stage combination of tangential centrifugation, spiral flow guidance, vacant annular flow stabilization and inertial collision of bottom baffles. The dryness of the separated steam can reach more than 99%, and it can adapt to a wide range of steam velocity changes.

[0022] The steam generator of the present invention integrates a condensate heat recovery system, which exchanges heat between the high-temperature condensate discharged from the tubular cyclone throttling steam-water separator and the system feedwater. This not only increases the feedwater temperature but also reduces the temperature of the discharged water to below 40°C, significantly reducing heat loss and thermal pollution.

[0023] Features described and / or illustrated for one embodiment may be used in the same or similar manner in one or more other embodiments, combined with features in other embodiments, or substituted for features in other embodiments.

[0024] It should be emphasized that the term "including / comprises" as used herein refers to the presence of a feature, whole, step, or component, but does not exclude the presence or addition of one or more other features, wholes, steps, or components. Attached Figure Description

[0025] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0026] Figure 1 This is a three-dimensional structural diagram of a hydrophobic heat recovery system provided in one embodiment of the present invention; Figure 2 yes Figure 1 Another view; Figure 3 yes Figure 1 Perspective view of a waste heat recovery heat exchanger; Figure 4 yes Figure 1 3D structural diagram of a tubular cyclone throttling steam-water separator; Figure 5 yes Figure 4 Internal view; Figure 6 yes Figure 4 A sectional view; Figure 7 yes Figure 4 Exploded view; Figure 8 yes Figure 4 Three-dimensional structural diagram of the central tube; Figure 9 yes Figure 8 A schematic diagram of the installation angle of the air deflector; Figure 10 yes Figure 4 A schematic diagram of the helix angle of the spiral guide vane; Figure 11 yes Figure 5 AA cross-section view; Figure 12 yes Figure 5 BB cross-section; Figure 13 This is a schematic diagram of the wire mesh installation at the lower outlet of the central tube of a tubular cyclone throttling steam-water separator provided in one embodiment of the present invention; Figure 14 This is a schematic diagram of a steam generating device provided in one embodiment of the present invention.

[0027] Explanation of reference numerals in the attached diagram: 5. Tubular cyclone throttling steam-water separator; 50. Outer shell; 501. Baffle plate; 502. Spiral guide vane; 505. Spiral separation channel; 506. Empty annulus; 507. Steam output end; 508. Drain output end; 521. Upper flange; 522. Upper connecting pipe; 523. Upper hemispherical cap; 531. Lower flange; 532. Lower connecting pipe; 533. Lower hemispherical cap; 51. Input pipe; 511. Input flange; 54. Baffle plate; 541. Connecting rib; 542. Second flow gap; 60. Central pipe; 601. Sealing ring; 521. Upper flange; 6. Drainage connecting pipe; 600. Drainage valve; 7. Waste heat recovery heat exchanger; 701. Outer shell; 702. Heat recovery spiral tube; 71. Water inlet connecting pipe; 72. Valves (electric ball valves); 73. Drainage pipe; 74. Water inlet pipe; 741. Inlet pump. Detailed Implementation

[0028] To enable those skilled in the art to better understand the technical solutions of this invention, the technical solutions of the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this invention, and not all embodiments. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of this invention.

[0029] It should be noted that when an element is referred to as being "set on" another element, it can be directly on the other element or may be interposed with another element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or may be interposed with another element. The terms "vertical," "horizontal," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementations.

[0030] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0031] like Figures 1 to 14 As shown, a steam generating device provided in one embodiment of this application is applicable to, but not limited to, inspection-exempt steam generators or steam boilers. Preferably, the water volume of the entire steam generating device (especially the pressurized part) can be controlled below 50L, and more specifically, below 30L, to meet the relevant safety regulations for small steam equipment and achieve safety exemption from inspection.

[0032] Please see Figures 1 to 14 This application provides a steam generating device, including a steam generating body. A burner is fixedly installed on one side of the steam generating body. The burner utilizes low-NOx fully premixed high-efficiency combustion technology to fully mix fuel (such as natural gas) with air before combustion, producing high-temperature flue gas. The burner can burn towards or extend into the steam generating body. For example, the burner can be a planar burner. Compared to traditional cylindrical or gun-type burners, the flame of a planar burner typically advances forward in a relatively uniform plane or area, laying the foundation for subsequent uniform heat exchange.

[0033] Of course, the steam generator body can also be a cross-flow steam generator body like CN114508745A or CN115614722A, and this application does not impose any restrictions.

[0034] The steam generator body internally defines a first flue gas flow path and a main heat exchange flow path. The first flue gas flow path is the path for the high-temperature flue gas. The high-temperature flue gas generated by combustion flows within this path, transferring heat to the water through convection and radiation heat transfer. The main heat exchange flow path is where the water is heated and vaporized. The water absorbs the heat released by the flue gas within the main heat exchange flow path, gradually increasing its temperature to the saturation temperature and boiling, forming a gas-liquid mixture, i.e., primary steam. Due to the characteristics of small-capacity boilers, this primary steam typically contains a high proportion of liquid water (high humidity), which, if used directly, would severely impact the efficiency and lifespan of downstream equipment.

[0035] To process the aforementioned primary steam and recover energy, this embodiment includes a hydrophobic heat recovery mechanism. This mechanism mainly consists of two core components: a tubular cyclone throttling steam-water separator 5 and a waste heat recovery heat exchanger 7. Specifically, the tubular cyclone throttling steam-water separator 5 is used to separate the primary steam output from the steam generator into gas and liquid components. For example... Figure 1 As shown, the tubular cyclone throttling steam-water separator 5 has a steam output end 507 located at the top, a condensate output end 508 located at the bottom, and an input pipe 51 located on the side. The steam output end 507 is provided with an upper flange 521.

[0036] The tubular cyclone throttling steam-water separator of the present invention occupies a small volume, with a geometric volume of less than 5L; furthermore, the geometric volume of the tubular cyclone throttling steam-water separator is less than 3L, for example, around 2.5L. This allows the tubular cyclone throttling steam-water separator to achieve comprehensive capture of large, medium, and small-sized water droplets within a compact space, with the separated steam dryness reaching over 99%. The input pipe 51 is connected downstream of the main heat exchange channel of the steam generator (boiler body) via a pipeline; specifically, it can be connected to the upper flange 521 via a pipeline. Thus, the high-temperature, high-pressure wet steam from the boiler body directly enters the tubular cyclone throttling steam-water separator 5 tangentially for processing. The processed high-dryness steam (target steam, dryness > 99%) is discharged from the steam output end to supply the steam consumption point; while the separated saturated water (condensate) flows out from the condensate output end.

[0037] To recover heat from the condensate, the steam generator in this embodiment is equipped with a waste heat recovery heat exchanger 7 having a first flow channel and a second flow channel. In this embodiment, as... Figure 3 As shown, the waste heat recovery heat exchanger 7 preferably adopts a shell-and-tube heat exchanger structure, specifically including a cylindrical shell 701 and a spiral heat exchange tube 702 located inside the cylindrical shell.

[0038] The first flow channel, serving as the heat source, is mainly formed by the cavity of the spiral heat exchange tube 702. The first flow channel has a first inlet and a first outlet. The first inlet is connected to the condensate outlet 508 of the tubular cyclone throttling steam-water separator 5 via a condensate drain pipe 6. To control the timing and flow rate of condensate discharge, a condensate drain valve 600 is installed on the condensate drain pipe 6 between the condensate outlet 508 and the first inlet. When the water level in the tubular cyclone throttling steam-water separator reaches a certain height or according to preset logic, the condensate drain valve 600 opens, allowing high-temperature condensate (approximately 100℃-180℃, depending on the working pressure) to flow into the spiral heat exchange tube 702. The first outlet is connected to a drain pipe 73, through which the water, cooled by heat exchange (temperature reduced to below 40℃), is discharged from the equipment.

[0039] The second flow channel, serving as the heated object (located on the cold side), is primarily formed by the space between the cylindrical shell 701 and the spiral heat exchange tube 702. The second flow channel has a second inlet and a second outlet. The second inlet is connected to an external inlet pump 741 (which also functions as a circulation pump) via an inlet pipe 74. The second outlet is ultimately connected upstream of the main heat exchange flow channel via an inlet connecting pipe 71.

[0040] In the waste heat recovery heat exchanger 7, the condensate entering through the first flow channel is used to heat the water in the second flow channel, and the two exchange heat using a counter-current or cross-flow heat exchange method. Low-temperature makeup water (e.g., 20°C) enters the shell 701, surrounding the spiral tube 702 containing high-temperature condensate. Heat is transferred from the condensate inside the spiral tube to the makeup water outside the tube. In this way, the condensate is cooled (sensible heat is recovered, and thermal contamination is avoided), and the makeup water is preheated (reducing the fuel consumption of the boiler body).

[0041] To further recover waste heat from the flue gas, the steam generator also includes a condensing heat exchanger. The medium-temperature flue gas (e.g., 200°C) discharged from the steam generator enters the condensing heat exchanger to continue releasing heat. The condensing heat exchanger defines a second flue gas flow path and a preheating flow path. The second flue gas flow path is connected downstream of the first flue gas flow path of the steam generator in the flue gas flow direction. Water is pumped into the preheating flow path (or pre-treated before pumping) by a water inlet pump 741, which is connected upstream of the main heat exchange flow path (i.e., the input end of the first heat exchange component 2) in the water flow direction. In the preheating flow path, the water exchanges heat with the flue gas from the second heat exchange component 3 (at which point the flue gas temperature is further reduced) to preheat its temperature; for example, the water temperature can be preheated to above 60°C, increasing the water temperature entering the first heat exchange component 2, thereby improving the overall thermal efficiency. Finally, the flue gas, cooled by the condensing heat exchanger, is discharged through the flue gas outlet 50.

[0042] In an optional or enhanced water system, a dual-pump relay water supply can be used, with a water storage buffer tank to handle the gas released from the preheated water. For example, an inlet pump 741 (e.g., a fixed-frequency pump with a head of 5-9m) can be installed upstream of the condenser heat exchanger (energy saver), with the pump's head set to be greater than the water flow resistance of the condenser heat exchanger. In this case, the condenser heat exchanger can operate at a lower pressure or at atmospheric pressure. A booster pump (e.g., a multi-stage centrifugal variable-frequency pump with a head greater than 80m) is connected in series between the downstream of the condenser heat exchanger and the upstream of the steam generator's inlet. To prevent the gas released from the preheated water (e.g., reaching 70-80°C) from entering the booster pump 40 and causing cavitation or reduced pump efficiency, a water storage buffer tank with an internal water-holding space can be connected between the downstream of the condenser heat exchanger and the upstream of the booster pump 40, with a volume of 1L-500L, preferably 20-50L.

[0043] In this embodiment, the preheating channel is connected upstream of the main heat exchange channel in the water flow direction. Specifically, in this embodiment, the second outlet of the waste heat recovery heat exchanger 7 (i.e., the water that has been preheated once by condensate) is connected to the preheating inlet of the preheating channel of the condensing heat exchanger. A valve 72 is provided on the connecting pipe 71 between the second outlet and the preheating inlet. This valve 72 is an electric ball valve, mainly used to control the water supply and to regulate the flow rate in conjunction with the control system.

[0044] During steam generation, pure water first enters the waste heat recovery heat exchanger 7 via the inlet pump 741, absorbing the sensible heat from the condensate and raising its temperature from 20°C to, for example, 35°C. It then enters the condensation heat exchanger, absorbing the latent and sensible heat of the flue gas, further raising its temperature to, for example, 60°C-80°C. Finally, it enters the main heat exchange channel of the steam generator. This multi-stage gradient heating method maximizes the utilization of the system's internal waste heat, allowing the exhaust gas temperature to drop below 60°C and the drainage temperature to drop below 40°C, significantly improving the system's thermal efficiency.

[0045] High-temperature condensate (approximately 160℃-180℃) enters the interior of the spiral tube 702. Simultaneously, low-temperature fresh pure water (approximately 20℃) enters the shell side of the spiral tube. The two exchange heat in countercurrent flow, with the condensate transferring heat to the pure water. The pure water is preheated to a relatively high temperature (e.g., 40-50℃) before entering the boiler, which directly reduces the fuel consumption required for the boiler to boil the water. The heat is not lost to the environment or diluted in the pure water tank; instead, it returns directly to the feedwater circuit on the high-pressure side, achieving near 100% heat recovery.

[0046] Furthermore, the condensate and feedwater are physically isolated within the waste heat recovery heat exchanger 7 (flowing through the tube side and shell side respectively). After heat exchange, the condensate temperature drops below 40°C and is then discharged through drain pipe 73. Because the condensate does not flow back to the pure water tank, any metal ions, rust residue, or concentrated salts that may be carried in the condensate are completely removed from the system, ensuring that the pure water tank and boiler feedwater always maintain a low TDS (pure) state, greatly protecting the boiler body and extending the service life of the steam boiler.

[0047] In this embodiment, as Figures 4 to 13 As shown, the tubular cyclone throttling steam-water separator 5 is a structure that integrates multiple separation mechanisms, including inertial separation, tangential centrifugal separation, spiral flow guidance, spatial flow stabilization, and gravity separation, within a small volume. The tubular cyclone throttling steam-water separator 5 includes a longitudinally extending outer tube shell 50. The outer tube shell 50 is a vertically extending tube shell. The outer tube shell 50 is the pressure-bearing body and is mainly made of stainless steel (such as 304) to withstand the corrosion of high-temperature and high-pressure steam. A steam output end 507 is provided at the upper end of the outer tube shell 50.

[0048] In terms of specific structure, such as Figure 4 and Figure 7As shown, an upper hemispherical cap 523 is welded to the top of the outer shell 50, an upper connecting pipe 522 is connected above the upper hemispherical cap, and an upper flange 521 is connected at the very top. The hemispherical cap structure at the upper end of the outer shell 50 helps to disperse stress and improve pressure resistance. The lower end of the outer shell 50 is provided with a condensate drain end 508, which mainly includes a lower hemispherical cap 533, a lower connecting pipe 532, and a lower flange 531. The lower hemispherical cap 533 is fixedly connected to the upper end of the outer shell 50, and the lower hemispherical cap 533 and the lower flange 531 are connected by the lower connecting pipe 532. The outer diameter of the lower connecting pipe 532 is smaller than the outer diameter of the upper connecting pipe 522. The lower hemispherical cap 533 facilitates the collection of hydrophobic liquid and avoids liquid accumulation in dead corners.

[0049] A central tube 60 is fixedly installed inside the outer shell 50. The central tube 60 is a hollow circular tube, which is coaxially arranged with the outer shell 50 and extends vertically together. The upper end of the central tube 60 has an outlet, and the lower end has an open inlet. All dry steam (target steam) ultimately passes through the interior of the central tube 60 upwards and is discharged through its outlet.

[0050] In this embodiment, the upper end of the central tube 60 is sealed to the outer tube shell by a sealing ring 601, forcing the primary steam flow to enter the central tube only from below. Figure 5 , Figure 8 As shown, in order to force the primary steam flow, the upper end of the central tube 60 is provided with a sealing ring 601 that completely seals the space between it and the inner wall of the outer tube shell 50. Thus, the rising airflow in the annular space between the outer tube shell 50 and the central tube 60 cannot directly reach the top outlet and must first run downwards for subsequent spiral separation.

[0051] The central tube 60 has a perforated plate or wire mesh 608 at its lower inlet or upper outlet. The perforated plate has multiple through holes. For example... Figure 13 As shown, in this embodiment, the lower inlet of the central tube 60 is provided with a wire mesh 608. Both the perforated plate and the wire mesh 608 allow steam flow and utilize adsorption to absorb and filter the tiny droplets attached to the passing steam, thereby improving the steam dryness. In other feasible embodiments, the perforated plate or wire mesh 608 can also be disposed inside the central tube 60. The outer diameter of the central tube 60 is 0.3 to 0.7 times the outer diameter of the outer tube shell 50. Preferably, the outer diameter of the central tube 60 is 0.5 times the outer diameter of the outer tube shell 50. Through the perforated plate or wire mesh 608, the tiny droplets inside the steam can be adsorbed onto the surface of the perforated plate or wire mesh 608 as it passes through, eventually dripping down and separating from the steam.

[0052] In this embodiment, the input pipe 51 is fixedly connected to the upper part of the outer shell 50 and communicates with the internal space. Specifically, the input pipe 51 communicates with the lower part of the sealing ring 601. This confines the incoming steam within the annular space below the sealing ring 601. The input pipe 51 is tangentially connected to the outer shell and located below the sealing ring 601. Figure 11 As shown, the centerline of the input pipe 51 does not intersect with the axis of the outer shell, causing the steam to enter tangentially and form a swirling flow.

[0053] like Figure 11 As shown, the input pipe 51 is perpendicularly connected to the outer shell 50 and enters the spiral separation channel 505 tangentially along the outer shell 50. Specifically, the central axis of the input pipe 51 is offset from the central axis of the outer shell 50 and also from the central axis of the central pipe, and they do not intersect. To ensure the airflow velocity and tangential effect, the outer diameter of the input pipe 51 is preferably set to about 0.5 times the outer diameter of the outer shell 50. The outer and inner diameters of the input pipe 51 can be the same as those of the central pipe 60 or the upper connecting pipe 522. The perpendicular distance between the central axis of the input pipe 51 and the central axis of the outer shell is about 1 / 4 of the outer diameter of the outer shell or about 1 / 2 of the outer diameter of the input pipe. Along the axial direction of the input pipe 51, the outer wall of the central pipe is located within the annular projection of the input pipe 51, so that when the primary steam enters through the input pipe 51, it impacts the wall of the central pipe, achieving inertial separation. Furthermore, the tangential entry method allows the steam-water mixture to obtain extremely high tangential velocity the moment it enters the separator, generating initial rotational centrifugal force. Subsequently, the spiral flow of the spiral guide vanes achieves the centrifugal separation effect.

[0054] To further improve the dryness of the output steam, one of the input pipe and the steam output end is provided with a throttling section, which has a throttling orifice. The throttling section is a throttling plate disposed at the port of the input pipe or the port of the steam output end. Specifically, the throttling plate can be installed on the input flange 511 of the input pipe 51, and fixedly clamped between the input flange 511 and the pipe end flange connected thereto. Similarly, the throttling plate can be installed on the upper flange 521, and fixedly clamped between the upper flange 521 and the pipe end flange connected thereto. By setting the throttling section to throttle the steam, the dryness of the downstream steam can be improved. The orifice area of ​​the throttling orifice is smaller than the flow area of ​​the input pipe 51. Of course, at the steam output end, the orifice area of ​​the throttling orifice is smaller than the flow area of ​​the upper connecting pipe 522.

[0055] A spiral guide vane 502 is provided between the central tube 60 and the outer shell 50, forming a spiral separation channel 505. The spiral guide vane 502 is spirally fixed to the outer wall of the central tube 60. Specifically, the spiral guide vane 502 can be fixed to the central tube 60 by continuous welding. The spiral guide vane 502 can force the airflow to maintain high-speed rotation and descent within the annular space. During this process, denser droplets are thrown towards the inner wall of the outer shell 50 by centrifugal force, forming a liquid film and flowing downwards. The airflow rotates and descends at high speed within this channel, using centrifugal force to throw large droplets towards the wall surface.

[0056] To reduce impact turbulence during air intake, such as Figure 8 and Figure 9 As shown, a guide plate 501 is provided at the upper end of the spiral channel to block this end. The guide plate 501 is essentially a "ceiling" of the spiral channel. Considering the turbulent flow field inside traditional tangential inlet separators, the uneven connection between the inlet and the internal vortex blades, resulting in large energy losses and low initial separation efficiency, a special design was made for the installation angle α of the guide plate 501 in this embodiment. The plane containing the outer edge of the guide plate 501 and the central axis of the outer shell 50 is taken as the reference plane, and the angle between the guide plate and this reference plane is the installation angle α.

[0057] like Figure 9 , Figure 10 As shown, the installation angle α and the spiral helix angle θ (lead angle θ) of the spiral guide vane 502 differ by less than 20 degrees. Preferably, the installation angle α and the spiral helix angle θ of the spiral guide vane 502 are equal. In this way, the airflow entering from the inlet pipe 51 smoothly slides into the spiral track along the inclined direction of the guide vane 501, minimizing kinetic energy loss and turbulence, achieving a smooth and impact-free transition of steam from the tangential inlet to the internal spiral flow channel, maximizing the conversion of the steam's kinetic energy into centrifugal force of rotational motion, significantly reducing energy loss (pressure drop) and noise in the inlet section, and improving the initial separation efficiency of the centrifugal separation section, ensuring the overall efficiency of the entire tubular cyclone throttling steam-water separator.

[0058] In this embodiment, a gap with a width > 0.1 mm is left between the spiral guide vane 502 and the inner wall of the outer tube shell. This allows the liquid film on the wall to flow smoothly downwards, preventing it from being sheared by the high-speed airflow and re-entered into mixing with the steam. The installation angle of the guide plate 501 at the top of the spiral channel matches the spiral lift angle (lead angle) of the spiral guide vane (difference < 20 degrees). This reduces inlet air impact disturbance and maintains a stable flow field.

[0059] Specifically, such as Figure 11As shown, the outer edge of the spiral guide vane 502 is not completely sealed to the inner wall of the outer shell 50, but is provided with a first flow gap. The width of this first flow gap is greater than 0.1 mm (e.g., 0.5 mm-2 mm). If the spiral guide vane 502 is in close contact with the inner wall, the high-speed rotating airflow will scrape up the liquid film on the inner wall like a scraper and re-entrain it into the airflow (secondary entrainment). However, by setting the first flow gap, the liquid film flowing along the wall can be smoothly slid down the wall without being directly sheared by the spiral guide vane 502, greatly improving the separation efficiency.

[0060] The spiral guide vane 502 does not extend to the very bottom of the central tube 60. For example... Figure 5 and Figure 6 As shown, the spiral guide vane 502 extends to the lower part of the central tube and then stops, that is, the spiral guide vane extends to the upper end of the empty annulus and stops. Thus, an empty annulus 506 is formed below the spiral separation channel 505 between the central tube 60 and the outer shell 50. No spiral guide vanes are provided within the empty annulus 506. Figure 6 As shown, the length L of the vacant annulus 506 is preferably 0.5 to 0.8 times the diameter of the outer shell 50. The vacant annulus 506 region allows the rotating airflow to recover from a turbulent state and become ordered, preparing for the next stage of separation, and achieving stabilization of the vortex and deliquescence.

[0061] After undergoing intense spiral centrifugal motion in the upper part, the airflow, although separating most of the water, remains in a highly turbulent state. The empty annulus 506 provides a relatively open space, allowing the rotating airflow to be rectified and stabilized in this region, known as the "vortex stabilization zone." In this region, some medium-sized water droplets that were not ejected continue to drift outwards due to inertia and adhere to the wall surface, while the axial velocity component of the airflow tends to be uniform, preparing for the next stage of deflection and separation.

[0062] After passing through the empty annulus 506, the airflow needs to enter the central tube 60 and exit upwards. This involves a large 180-degree turn in the flow direction. To utilize this turning process to capture tiny droplets, the outer tube shell 50 is also equipped with a baffle 54 below the central tube 60. Figure 12 As shown, the baffle 54 is fixed to the inner wall of the outer shell via connecting ribs 541. The axial projection of the baffle 54 is circular, and it is coaxially arranged inside the outer shell. The baffle 54 can be a circular plate as a whole, with a diameter of 0.6 to 0.75 times the inner diameter of the outer shell. Converted to area, its projected area accounts for 0.5 to 0.9 times the cross-sectional area of ​​the outer shell.

[0063] like Figure 5 , Figure 7As shown, the baffle 54 is not a flat plate, but an upwardly convex plate (similar to an umbrella or spherical shape). This convex structure has two advantages: first, it guides water droplets impacting the plate to slide off in all directions, preventing water accumulation; second, it complements the airflow streamline, reducing unnecessary drag loss.

[0064] Furthermore, the baffle 54 and the lower inlet of the central tube 60 are not adjacent, but rather separated by a significant blank space 555 (L2 segment). The length L2 of this blank space 555 is set to 1.2 to 1.5 times the outer diameter of the outer tube shell 50. This distance was determined through extensive fluid dynamics simulations and experiments. If the blank space 555 is too close, the airflow turns too sharply, resulting in excessively high velocity and a strong suction effect, drawing the water collected on the baffle back into the central tube. If the blank space 555 is too far, the airflow turning radius is too large, weakening the inertial separation effect. At a distance of 1.2 to 1.5 times the diameter, the airflow can smoothly complete a 180-degree turn, but small water droplets with greater inertia cannot follow the turn and instead collide with the baffle 54 in a straight line and are captured.

[0065] A baffle 54 is provided below the central tube 60. A clearance space 555 of 1.2-1.5 times the outer diameter of the central tube 60 is maintained between the baffle 54 and the inlet of the central tube 60. The baffle 54 is an upwardly convex umbrella shape, with a projected area occupying 0.5-0.9 times the cross-section. The airflow makes a sharp 180-degree turn at this point before entering the central tube, and tiny droplets are captured by impacting the baffle due to inertia. A second flow gap 542 of 5mm-60mm is left between the edge of the baffle and the inner wall for liquid dripping.

[0066] A second flow gap 542 is provided between the outer edge of the baffle 54 and the inner wall of the outer casing 50. The width of this gap is 5mm-60mm. This wider annular channel is a spare channel for airflow, and also allows the liquid film flowing down from the upper wall to pass smoothly through this gap and fall to the bottom without accumulating above the baffle 54. The distance between the baffle 54 and the bottom (lower hemispherical cap) of the outer casing 50 is 10mm-200mm (L3 section). This area is the final gravity settling and water collection area. The separated water finally collects here and is discharged through the drain end 508.

[0067] Based on the above description of the tubular cyclone throttling steam-water separator of this embodiment, it can be seen that the tubular cyclone throttling steam-water separator is divided into several functionally defined parts: Impact separation zone: mainly composed of an eccentrically arranged inlet pipe 51 and a central pipe 60. When steam enters, it impacts the wall of the central pipe 60, achieving inertial separation. Centrifugal separation zone: mainly composed of the area corresponding to the spiral guide vane 502, to achieve the centrifugal separation effect of spiral flow; Swirl flow stabilization and desliming zone: defined as the space between the end of the spiral guide vane 502 and the lower inlet of the central tube 60 (empty annular space 506), its height (L1) can be set to 0.5-0.8 times the outer tube diameter (D); the steam and water after spiral separation are stabilized in this zone, and the centrifugal separation is gradually converted to gravity separation to further ensure the separation effect of steam and water; Inertial deflection and deceleration zone: defined as the space between the baffle plate 54 and the bottom inlet of the central tube 60 (blank interval space 555), the height (L2) of which is set to 1.2-1.5 times the diameter (D) of the outer tube shell; steam returns through the baffle and flows upward through the central tube, while water moves downward under the action of gravity and gradually accumulates, achieving gravity separation from water; Adsorption separation zone: A perforated plate or wire mesh 608 is provided at the upper outlet or lower inlet of the central tube 60 to achieve adsorption separation; Throttling zone: Throttling plates are installed at the input pipe or steam output end to throttle the steam output and further improve the steam dryness.

[0068] The working process of this tubular cyclone throttling steam-water separator is as follows: Tangential impact vortex: Wet steam (primary steam) enters tangentially at high speed, impacts the outer wall of the central tube to achieve impact separation, and forms a strong vortex below the sealing ring 601.

[0069] First-stage centrifugation: Guided by the spiral guide vane 502, the airflow spirals downward at high speed. Large water droplets are thrown towards the wall by centrifugal force and flow downward through the first flow gap. The matching angle of the guide vane 501 ensures stable inflow.

[0070] Flow stabilization and rectification: When the airflow enters the bladeless empty annulus 506, the flow pattern tends to stabilize, maintaining rotational inertia, preventing turbulence from breaking water droplets and further separating and deliquerating them.

[0071] Secondary inertia: When the airflow reaches the bottom of the central tube 60, it impacts the baffle 54 and is forced to turn 180 degrees upward. Tiny droplets are captured by the inertial impact on the baffle 54, and the blanking space 555 prevents secondary entrainment.

[0072] Discharge: Steam is output upward along the inside of the central tube 60. Tiny droplets inside are captured by the perforated plate or wire mesh 608, further improving the dryness of the steam. All captured liquid water drips down the wall or from the edge of the baffle plate 54 and collects at the bottom for discharge.

[0073] Tests have shown that the tubular cyclone throttling steam-water separator with this structure performs excellently over a very wide range of operating conditions: the steam dryness reaches 99.50% under high load (930 kg / h, 8 bar) and the steam dryness still remains at 99.50% under low load (300 kg / h, 8 bar).

[0074] To verify the effectiveness of the tubular cyclone throttling steam-water separator in this embodiment, the inventors conducted multiple sets of comparative tests. The table below shows the performance test data of the tubular cyclone throttling steam-water separator: Fan speed liquid level Set pressure bar Steam flow rate (kg / h) Steam conductivity (ppm) Water conductivity (ppm) Steam dryness % 5400 58 8 930 2 400 99.50% 4500 52 8 780 2 400 99.50% 4500 52 6 780 3 400 99.25% 3200 48 8 580 1 300 99.67% 3200 48 4 580 2 300 99.33% 1800 48 8 300 2 400 99.50% 1800 48 4 300 3 400 99.25% Under high-load conditions, with a fan speed of 5400 rpm and a steam flow rate as high as 930 kg / h, the system pressure is 8 bar. At such high flow rates, traditional baffle separators are prone to water entrainment. However, using the structure of this embodiment, the steam dryness reaches 99.50%. This demonstrates that the spiral centrifugal separator with an empty annulus structure can effectively handle high flow rates, and the "first flow gap" effectively prevents shearing and entrainment of the liquid film by the high-speed airflow.

[0075] Under medium load conditions, when the steam flow rate is 780 kg / h and the pressure is 8 bar, the steam dryness is maintained at 99.50%. Even when the pressure is reduced to 6 bar (due to increased gas specific volume and further increase in flow rate), the dryness remains at 99.25%. This demonstrates the equipment's adaptability to pressure fluctuations.

[0076] Under low-load conditions, when the fan speed drops to 1800 rpm and the steam flow rate is only 300 kg / h (approximately one-third of full load), the centrifugal force is significantly reduced. Normally, separators relying solely on centrifugal force experience a sharp drop in efficiency at low flow rates. However, in this embodiment, the dryness still reaches 99.50%. This is mainly attributed to the inertial separation effect of the baffle 54 and the gravitational settling effect. At low flow rates, gravity separation and baffle collision become the dominant mechanisms, compensating for the inadequacy of centrifugal force.

[0077] Regarding conductivity, test data showed that the steam conductivity remained consistently between 1-3 ppm, while the feed water conductivity was 300-400 ppm. The extremely low steam conductivity directly proves that the droplets (carrying dissolved salts) were separated very thoroughly.

[0078] The data in the table above fully demonstrates that the limitations on the empty annular length (0.5-0.8D), blank interval space (1.2-1.5D), and baffle area ratio (0.5-0.9) in this embodiment enable the tubular cyclone throttling steam-water separator to maintain a high efficiency of over 99% within a wide flow velocity range of 1:10.

[0079] This invention, through the implementation of a tubular cyclone throttling steam-water separator with the aforementioned structure and a system flow for hydrophobic heat recovery, achieves high efficiency and energy saving in steam generation equipment. The tubular cyclone throttling steam-water separator utilizes multiple functions—inertial separation, spiral centrifugal separation, annular flow stabilization, gravity separation, adsorption separation, and throttling and dehydration—to achieve excellent steam-water separation efficiency (steam dryness greater than 99%) within a smaller volume (e.g., less than 3 liters).

[0080] Meanwhile, the supporting hydrophobic heat recovery mechanism uses the countercurrent heat exchange principle to "transfer" the originally discarded high-temperature hydrophobic heat back to the feedwater system. In conjunction with the condensing heat exchanger, it achieves the deep energy-saving target of flue gas temperature less than 60℃ and drainage temperature less than 40℃, which can effectively improve the energy efficiency and service life of small water volume boilers.

[0081] Any numerical values ​​cited herein include all values ​​ranging from a lower limit to an upper limit, increasing by one unit, with at least two units between any lower and any higher value. For example, if the quantity of a component or process variable (e.g., temperature, pressure, time, etc.) is described as ranging from 1 to 90, preferably from 20 to 80, more preferably from 30 to 70, the purpose is to illustrate that values ​​such as 15 to 85, 22 to 68, 43 to 51, 30, etc., are also explicitly listed in this specification. For values ​​less than 1, a unit is appropriately considered to be 0.0001, 0.001, 0.01, 0.1, etc. These are merely examples intended for explicit expression, and it can be assumed that all possible combinations of numerical values ​​listed between the minimum and maximum values ​​are explicitly described in this specification in a similar manner.

[0082] Unless otherwise stated, all ranges include the endpoints and all numbers between them. The terms "approximately" or "about" used with ranges apply to both endpoints of the range. Thus, "approximately 20 to 30" is intended to cover "approximately 20 to approximately 30," including at least the specified endpoints.

[0083] All articles and references disclosed herein, including patent applications and publications, are incorporated herein by reference for various purposes. The term “substantially constitutes…” used to describe a combination should include the identified elements, components, parts, or steps, as well as other elements, components, parts, or steps that do not substantially affect the essential novelty of the combination. The use of the terms “comprising” or “including” to describe combinations of elements, components, parts, or steps herein also contemplates embodiments substantially constituted by such elements, components, parts, or steps. The use of the term “may” herein is intended to indicate that any described attribute included by “may” is optional.

[0084] Multiple elements, components, parts, or steps can be provided by a single integrated element, component, part, or step. Alternatively, a single integrated element, component, part, or step can be divided into multiple separate elements, components, parts, or steps. The use of the word "a" or "an" to describe an element, component, part, or step does not imply the exclusion of other elements, components, parts, or steps.

[0085] It should be understood that the above description is for illustrative purposes and not for limitation. Many embodiments and applications beyond the provided examples will be apparent to those skilled in the art upon reading the above description. Therefore, the scope of this teaching should not be determined by reference to the above description, but rather by reference to the appended claims and the full scope of their equivalents. For purposes of completeness, all articles and references, including patent applications and publications, are incorporated herein by reference. The omission of any aspect of the subject matter disclosed herein in the preceding claims is not intended as a waiver of that subject matter, nor should it be construed as an indication that the inventors have not considered that subject matter as part of the disclosed inventive subject matter.

Claims

1. A steam generating device, characterized in that, include: Burner; The steam generating body is defined by a first flue gas flow channel and a main heat exchange flow channel; the water in the main heat exchange flow channel exchanges heat with the flue gas generated by the combustion of the burner to form primary steam. Hydrophobic heat recovery mechanisms include: A tubular cyclone throttling steam-water separator is used to separate the primary steam output from the steam generator into target steam and condensate. It has a steam output end, a condensate output end, and an input pipe. The input pipe is connected downstream of the main heat exchange channel to input the primary steam. The geometric volume of the tubular cyclone throttling steam-water separator is less than 5L; further, the geometric volume of the tubular cyclone throttling steam-water separator is less than 3L. A waste heat recovery heat exchanger having a first flow channel and a second flow channel; the first flow channel having a first inlet end and a first outlet end; the second flow channel having a second inlet end and a second outlet end; wherein, the first inlet end is connected to the condensate outlet end; the second inlet end is connected to the inlet pump, and the second outlet end is connected upstream of the main heat exchange flow channel; the condensate input into the first flow channel is used to heat the water in the second flow channel.

2. The steam generating equipment as described in claim 1, wherein, The steam generating equipment further includes: a condensing heat exchanger defining a second flue gas flow channel and a preheating flow channel; the second flue gas flow channel is connected downstream of the first flue gas flow channel in the flue gas flow direction; the preheating flow channel is connected upstream of the main heat exchange flow channel in the water flow direction; the water in the preheating flow channel exchanges heat with the flue gas in the first flue gas flow channel to preheat it; wherein, the second water outlet is connected to the preheating water inlet of the preheating flow channel.

3. The steam generating equipment as described in claim 1, wherein, The tubular cyclone throttling steam-water separator includes: The outer tube shell extends longitudinally; the upper end of the outer tube shell is provided with a steam output end, and the lower end is provided with a condensate output end; A central tube is fixedly installed inside the outer shell and extends together with the outer shell; the upper end of the central tube has an outlet and the lower end has an inlet; a spiral separation channel extending spirally from top to bottom around the central tube and an empty annulus connected to the bottom of the spiral separation channel are provided between the central tube and the outer shell; the upper end of the spiral separation channel is blocked. The input pipe is fixedly connected to the outer shell, with one end connected to the spiral separation channel and the other end connected to the steam generator body to input primary steam.

4. The steam generating equipment as described in claim 1, wherein, At least one perforated plate or wire mesh is provided at the lower inlet or upper outlet of the central tube or inside the central tube; the perforated plate is provided with multiple through holes.

5. The steam generating equipment as described in claim 1, wherein, One of the input pipe and the steam output end is provided with a throttling section, which has a throttling orifice; optionally, the throttling section is a throttling plate provided at the port of the input pipe or the port of the steam output end.

6. The steam generating equipment as described in claim 1, wherein, The outer shell and the central tube are coaxially arranged; a spiral guide vane is provided between the outer shell and the central tube to form the spiral separation channel; no spiral guide vane is provided in the empty annulus; optionally, the length of the empty annulus is 0.5-0.8 times the outer diameter of the outer shell; the outer diameter of the central tube is 0.3 to 0.7 times the outer diameter of the outer shell, preferably, the outer diameter of the central tube is 0.5 times the outer diameter of the outer shell.

7. The steam generator as claimed in claim 1, wherein, The spiral guide vane is spirally fixed to the outer wall of the central tube; a first flow gap is provided between the spiral guide vane and the inner wall of the outer tube shell, specifically, the width of the first flow gap is >0.1mm.

8. The steam generator as claimed in claim 1, wherein, The input tube is perpendicularly connected to the outer shell; the central axis of the input tube is offset from the central axis of the outer shell; along the axial direction of the input tube, the outer wall of the central tube is located within the annular projection of the input tube 51; further, the outer diameter of the input tube is 0.5 times the outer diameter of the outer shell.

9. The steam generator as claimed in claim 1, wherein, The upper end of the central tube is provided with a sealing ring to seal the gap between it and the inner wall of the outer tube shell; the spiral separation channel extends spirally below the sealing ring.

10. The steam generator as claimed in claim 1, wherein, The outer shell is further provided with a baffle plate below the central tube; the projected area of ​​the baffle plate along the axial direction accounts for 0.5 to 0.9 times the cross-sectional area of ​​the outer shell.

11. The steam generator as claimed in claim 7, wherein, A blank space is provided between the baffle plate and the central tube; the length of the blank space is 1.2-1.5 times the outer diameter of the outer tube shell; a second flow gap is provided between the baffle plate and the inner wall of the outer tube shell; the width of the second flow gap is 5mm-60mm.

12. The steam generator as claimed in claim 1, wherein, The baffle plate is an upwardly convex plate with a convex height; preferably, the axial projection of the baffle plate is circular, and its diameter is 0.6 to 0.75 times the inner diameter of the outer tube shell when it is coaxially arranged on the outer tube shell; the distance between the baffle plate and the bottom of the outer tube shell is 10 mm to 200 mm.

13. The steam generator as claimed in claim 1, wherein, The upper end of the spiral channel is provided with a guide plate that seals that end; the installation angle of the guide plate and the spiral helix angle of the spiral guide vane are within 20 degrees, and further, the installation angle of the guide plate and the spiral helix angle of the spiral guide vane are equal; wherein, taking the plane where the outer side of the guide plate and the central axis of the outer shell are located as the reference plane, the angle between the guide plate and the reference plane is the installation angle of the guide plate.

14. The steam generating apparatus as claimed in claim 1, wherein, The preheating and recovery heat exchanger includes a cylindrical shell and a spiral heat exchange tube located inside the cylindrical shell; the lumen of the spiral heat exchange tube forms the first flow channel; the space between the cylindrical shell and the spiral heat exchange tube forms the second flow channel.

15. The steam generating apparatus as claimed in claim 1, wherein, The preheating recovery heat exchanger includes a shell-and-tube heat exchanger with countercurrent heat exchange; a drain valve is provided on the connecting pipe between the drain outlet and the first inlet; an electric ball valve is provided on the connecting pipe between the second outlet and the preheating inlet; and a drain pipe is connected to the first outlet.

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