A dual shaft resonance sinusoidal helical line rotor centrifugal rotation steam generation device and method

Abstract

This invention discloses a biaxial resonant sinusoidal spiral rotor centrifugal steam generation device and method, comprising a shell, a rotating shaft, a rotor, and a rotary actuator. The shell has end caps at both ends, an inner cavity is formed inside the shell, a water inlet is opened on the outer periphery of the shell, and a steam outlet is opened on the outer side of the end caps. The rotating shaft is rotatably mounted in the inner cavity and driven to rotate by the rotary actuator. The rotor is located in the inner cavity and fixedly mounted on the rotating shaft. This invention utilizes electro-driven mechanical energy to directly convert into the internal energy of water, directly vaporizing liquid water without heat loss from the heat exchange surface, thus improving effective thermal efficiency. The centrifugal acceleration generated by the high-speed rotation of the rotor forms an ultra-thin, uniform water film within the water film gaps, significantly increasing the heat exchange area and shear efficiency. Frictional and shear heat are directly converted into latent heat of vaporization, achieving direct vaporization without pipe wall heat exchange.

Description

Technical Field

[0001] This invention relates to heat generators, and more specifically, to a steam generator using a biaxial resonant sinusoidal spiral rotor centrifugal rotation, and also to a method for generating steam using a biaxial resonant sinusoidal spiral rotor centrifugal rotation. Background Technology

[0002] Currently, steam generation technologies on the market are mainly divided into four categories: fuel-based, traditional electric heating, new clean energy, and industrial waste heat. Each type of technology has unresolved industry pain points and technical shortcomings, becoming the main bottleneck for industry upgrading.

[0003] Among them, fuel-based steam generation equipment (coal, gas, and oil boilers) has high energy consumption. Taking natural gas boilers as an example, it takes 85 cubic meters of natural gas to produce 1 ton of steam. At the same time, the fuel storage and transportation costs are high, and the combustion process is prone to safety accidents such as explosions and fires. It also produces pollutants such as NOx, SOx, and dust, resulting in high environmental compliance costs. Traditional electric heating steam generation equipment (resistance and electric heating tube heating) suffers from rapid aging of electric heating tubes and low thermal efficiency. It takes 720-750 kWh of electricity to produce 1 ton of steam, resulting in high operating costs. It also suffers from problems such as continuous decline in thermal efficiency due to scaling on the heat exchange surface and damage from dry burning. Clean energy steam generation equipment (solar, biomass, and geothermal) is severely limited by natural conditions and geographical location, resulting in poor energy supply stability. Biomass steam generation still involves a combustion process, which produces ash and a small amount of exhaust gas. The raw materials are prone to moisture, affecting operational stability. Industrial waste heat steam generation equipment has a strong coupling between waste heat output and production process, resulting in unstable energy supply and an inability to independently and stably supply steam.

[0004] The aforementioned existing technologies all share core common problems: they heavily rely on heat exchange surfaces for heat transfer, resulting in irreversible heat loss due to temperature differences during heat exchange. They also suffer from unstable energy supply, poor steam quality, high operation and maintenance costs, and stringent safety and environmental compliance requirements. The market urgently needs a clean steam generation technology that eliminates the need for heat exchange surfaces, provides independent energy supply, boasts high power efficiency, and delivers stable steam quality, while also addressing the comprehensive needs of low carbon emissions, environmental friendliness, safety control, and reasonable initial investment.

[0005] Therefore, a new solution is needed to address the aforementioned technical problems. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of the prior art and provide a device and method for generating steam by centrifugal rotation of a biaxial resonant sinusoidal spiral rotor.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A dual-axis resonant sinusoidal spiral rotor centrifugal steam generator includes a shell, a rotating shaft, a rotor, and a rotary actuator. The shell has end caps at both ends, an inner cavity is formed inside the shell, a water inlet is provided on the outer periphery of the shell, and a steam outlet is provided on the outer side of the end caps. The rotating shaft is rotatably mounted in the inner cavity and driven to rotate by the rotary actuator. The rotor is located inside the inner cavity and fixedly mounted on the rotating shaft. The rotating shaft, rotor, and inner cavity are coaxially arranged. A spiral protrusion is integrally formed on the outer peripheral wall of the rotor, and a water film gap is formed between the spiral protrusion and the inner peripheral wall of the inner cavity.

[0009] Furthermore, the helical protrusion has a root near the rotor and a top away from the rotor; along the axial direction of the rotor, the width W1 of the root is greater than the width W2 of the top.

[0010] Furthermore, along the radial direction of the rotor, the width between the outer peripheral wall of the rotor and the inner peripheral wall of the inner cavity is H1, the protrusion height of the spiral protrusion is H2, and the width of the water film gap is H3, where H3 = H1 - H2, and 1.0 mm ≤ H3 ≤ 4.0 mm.

[0011] Furthermore, the width H3 of the water film gap is 3 mm.

[0012] Furthermore, the width W2 of the top is: 0.8H3≤W2≤1.1H3; the pitch of the spiral protrusion is P; and the width W1 of the root is: 0.8P≤W1≤1.1P.

[0013] Furthermore, the spiral protrusion has a multi-headed spiral structure, with 1 to 4 heads; the spiral angle of the spiral protrusion is 10° to 18°.

[0014] Furthermore, the outer diameter of the cross-section of the helical protrusion... It is a sine curve. for:

[0015]

[0016] in, This represents the rotation angle of the rotor; The outer diameter of the rotor's outer peripheral wall is 41. For amplitude, ; The number of spiral protrusions.

[0017] Furthermore, the outer diameter of the outer peripheral wall of the rotor is 300mm~500mm; the protrusion height of the spiral protrusion H2 is 20mm~60mm; and the axial length of the rotor is 280mm~500mm.

[0018] Furthermore, the spiral protrusion has several through holes, which sequentially penetrate each turn of the spiral protrusion along the axial direction, and the through holes are evenly distributed in a ring.

[0019] The present invention also proposes a method for generating steam by centrifugal rotation of a biaxial resonant sinusoidal spiral rotor, which employs the above-described biaxial resonant sinusoidal spiral rotor centrifugal rotation steam generating device.

[0020] During operation, water is introduced into the inner cavity of the shell through the inlet;

[0021] The rotary actuator rotates the drive shaft, which in turn drives the rotor to rotate within the housing cavity; the pressure within the cavity is controlled to be no more than 20 bar, and the rotor speed is controlled to be 3500~5000 r / min.

[0022] The centrifugal force generated by the rotation of the spiral protrusions on the outside of the rotor presses the water medium onto the rotor surface. A water film is formed between the spiral protrusions and the inner wall of the inner cavity. The spiral protrusions do work on the water film, and the water film heats up to the boiling point to form steam. The steam is output from the steam outlet of the shell.

[0023] In summary, the present invention has the following beneficial effects:

[0024] This scheme directly converts electric mechanical energy into the internal energy of water, directly vaporizing liquid water without heat loss from the heat exchange surface, thus improving effective thermal efficiency. The centrifugal acceleration generated by the high-speed rotation of the rotor forms an ultra-thin, uniform water film within the water film gaps, significantly increasing the heat exchange area and shear efficiency. Frictional and shear heat are directly converted into latent heat of vaporization, achieving direct vaporization without tube walls.

[0025] In this design, the outer periphery of the rotor has spiral protrusions with a sinusoidal spiral structure, which can generate periodic shear force on the water medium during high-speed rotation, promote uniform distribution of the water film and form turbulent disturbances, and increase the contact area and contact time between the water and the rotor surface. At the same time, the guiding effect of the sinusoidal spiral guides the water film to flow in an orderly manner along the axial direction, avoiding local drying or liquid accumulation. Combined with the top width design that matches the thickness of the water film, it can ensure that the medium has sufficient contact with the spiral protrusions, avoiding efficiency loss caused by idling or insufficient contact. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the structure of a biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to this embodiment;

[0027] Figure 2 This is a cross-sectional view of a biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to this embodiment;

[0028] Figure 3 for Figure 2 Enlarged view of point A in the middle;

[0029] Figure 4 This is a front view of the first type of rotor in this embodiment;

[0030] Figure 5 This is a schematic diagram of the end of the first type of rotor in this embodiment;

[0031] Figure 6 This is a cross-sectional view of the first type of rotor in this embodiment;

[0032] Figure 7 for Figure 6 Enlarged view of point A in the middle;

[0033] Figure 8 This is a perspective view of the second type of rotor in this embodiment;

[0034] Figure 9 This is a front view of the second type of rotor in this embodiment;

[0035] Figure 10 This is a schematic diagram of the end of the second type of rotor in this embodiment;

[0036] Figure 11 This is a schematic diagram of the structure of the dual-axis resonant sinusoidal spiral rotor centrifugal steam generator in this embodiment, coupled with a single rotary actuator;

[0037] Figure 12 This is a schematic diagram of the structure of the dual-axis resonant sinusoidal spiral rotor centrifugal steam generator in this embodiment, coupled with a dual-rotation actuator;

[0038] Figure 13 This is a schematic diagram of the impeller structure on the first side of the rotor in this embodiment;

[0039] Figure 14 This is a schematic diagram of the impeller structure on the second side of the rotor in this embodiment.

[0040] Reference numerals: 1. Housing; 10. Inner cavity; 101. Inner peripheral wall; 11. Inlet; 2. End cap; 21. Steam outlet; 22. Bearing seat; 221. Bearing assembly; 222. Rotary seal assembly; 3. Shaft; 31. Shaft end; 4. Rotor; 41. Outer peripheral wall; 42. Spiral protrusion; 421. Root; 422. Top; 43. Through hole; 44. Impeller; 440. Blade; 441. Inner end; 442. Outer end; 443. Blade flow channel; 5. Coupling; 6. Water film gap; 7. Rotary actuator; 71. Drive shaft. Detailed Implementation

[0041] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0042] Example 1

[0043] This embodiment discloses a biaxial resonant sinusoidal spiral rotor centrifugal steam generator, referring to... Figures 1-12 As shown, it includes a housing 1, a rotating shaft 3, a rotor 4, and a rotary drive 7.

[0044] Reference Figure 1 , Figure 2 As shown, the shell 1 is a horizontal cylindrical structure with end caps 2 fixedly connected to both ends by flanges. The shell 1 and the end caps 2 at both ends enclose a sealed inner cavity 10, which is a cylindrical cavity with an annular inner circumferential wall 101 on its inner wall. A water inlet 11 is provided on the outer circumference of the shell 1, which is connected to an external water supply pump and can pump water into the inner cavity 10 to provide a water source for steam generation. Moreover, in this embodiment, the water inlet 11 is arranged along the tangential direction of the inner circumferential wall 101, and several water inlets 11 are arranged along the axial direction to form multiple water inlets.

[0045] Steam outlets 21 are provided on both ends of the end caps 2. The steam outlets 21 are connected to the external steam pipeline network, and the steam generated in the inner cavity 10 can be output from the steam outlets 21.

[0046] Bearing seats 22 are fixedly formed on the two end caps 2. The two ends of the rotating shaft 3 are rotatably mounted on the bearing seats 22 of the end caps 2 at both ends via bearing assemblies 221. The main body of the rotating shaft 3 is located in the inner cavity 10, and the shaft end 31 of the rotating shaft 3 extends out of the bearing seat 22 and is connected to the drive shaft 71 of the rotary drive 7 via a coupling 5.

[0047] A rotary sealing assembly 222 is installed between the bearing housing 22 and the rotating shaft 3, which can maintain a good sealing effect while ensuring that both can rotate freely. In this embodiment, the housing 1 is heated to form a high-pressure steam environment. The rotary sealing assembly 222 can maintain an effective sealing effect in the inner cavity 10, and maintain a high-pressure, high-temperature rotary sealing state.

[0048] The rotor 4 is located inside the inner cavity 10 and is fixedly installed in the middle of the rotating shaft 3 by a thermocouple interference fit, so that the rotor 4 and the rotating shaft 3 can be fixed to each other. It can also be locked by other fasteners. The rotating shaft 3, rotor 4 and inner cavity 10 are coaxially arranged to ensure dynamic balance during high-speed rotation and avoid eccentric vibration.

[0049] Reference Figures 4-7 As shown, a spiral protrusion 42 is integrally formed on the cylindrical outer peripheral wall 41 of the rotor 4. The spiral protrusion 42 extends continuously along the axial direction of the rotor 4, and the spiral protrusion 42 basically covers the outer peripheral wall 41 of the rotor 4 along the axial direction of the rotor 4, forming protrusions and grooves distributed at intervals on the outer peripheral wall 41.

[0050] Reference Figure 2 , Figure 3 As shown, an annular water film gap 6 is formed between the outermost end of the spiral protrusion 42 and the inner peripheral wall 101 of the inner cavity 10, which is used to accommodate the water film formed by high-speed rotation and provide space for frictional shear heat generation.

[0051] Along the radial direction of rotor 4, the total width between the outer peripheral wall 41 of rotor 4 and the inner peripheral wall 101 of inner cavity 10 is H1, the protrusion height of helical protrusion 42 is H2, and the width of water film gap 6 is H3. The width H3 of water film gap 6 is: H3 = H1 - H2.

[0052] In this embodiment, the width H3 of the water film gap 6 ranges from 1.0mm ≤ H3 ≤ 4.0mm. For example, the total width H1 between the outer peripheral wall 41 of the rotor 4 and the inner peripheral wall 101 of the inner cavity 10 is 30mm, the protrusion height H2 of the spiral protrusion 42 is 27mm, and the width H3 of the water film gap 6 is H1 - H2 = 3mm. The water film gap 6 matches the water film thickness to ensure sufficient contact between the medium and the spiral protrusion 42. The water in the water film gap 6 can act as a lubricant for the water film medium and also serve as a source of water for generating steam. Moreover, after the water in the water film gap 6 absorbs heat and generates steam, the water vapor cannot adhere to the outside of the spiral protrusion 42 of the rotor 4, effectively throwing the water vapor off and separating it.

[0053] Reference Figure 3 As shown, along the axial direction of the rotor 4, the helical protrusion 42 has a root 421 close to the outer peripheral wall 41 of the rotor 4 and a top 422 away from the outer peripheral wall 41 of the rotor 4. The width W1 of the root 421 is greater than the width W2 of the top 422, forming a trapezoidal cross-section structure that is narrow at the top and wide at the bottom, which improves the structural strength of the helical protrusion 42 and is suitable for high-speed rotation conditions.

[0054] In this embodiment, the width W2 of the top 422 of the spiral protrusion 42 is related to the width H3 of the water film gap 6; the value range of the width W2 of the top 422 can be: 0.8H3≤W2≤1.1H3.

[0055] The width W1 of the root 421 of the spiral protrusion 42 is related to the pitch P of the spiral protrusion 42; the range of the width W1 of the root 421 can be: 0.8P≤W1≤1.1P.

[0056] In this embodiment, the spiral protrusion 42 has a sinusoidal spiral structure, specifically a single-start or multi-start thread structure; the number of starts n of the spiral protrusion 42 is 1 to 4, and the helix angle α of the spiral protrusion 42 is 10° to 18°. For example, the spiral protrusion 42 can adopt a double-start sinusoidal spiral structure, with the number of starts n=2 and the helix angle α being 15°.

[0057] For example, the pitch of the spiral protrusion 42 is equal to the width W1 of the root 421, satisfying the requirement of 0.8P≤W1≤1.1P. The width W2 of the top 422 is 3mm, which is equal to the width H3 of the water film gap 6, satisfying the requirement of 0.8H3≤W2≤1.1H3. This forms a basic structure with equal pitch and equal root width, which is beneficial to the stability of the medium flow and reduces turbulence loss.

[0058] Specifically, to quantify the influence of the helical structure on water film shear, the key geometric parameters of the helical protrusions in this embodiment are calculated and explained as follows:

[0059] The pitch P is:

[0060]

[0061] in, The rotor diameter is α is the helix angle. This embodiment uses... Let α = 15° be used for explanation.

[0062] The lead L is:

[0063]

[0064] Where n is the number of spiral heads. This embodiment uses n=2 for illustration.

[0065] The number of spiral turns N is:

[0066]

[0067] This embodiment is illustrated with a total helical segment length of 350 mm and a pitch P of 41.4 mm.

[0068] The projected area S of a single helical protrusion (approximately trapezoidal in shape) is:

[0069]

[0070] Wherein, W1 is the width of the root 421; W2 is the width of the top 422; and H2 is the protrusion height of the spiral protrusion 42.

[0071] In this embodiment, since the spiral protrusion 42 has a spiral structure, and there is a certain width difference between the root 421 and the top 422 of the spiral protrusion 42, the outer diameter of the cross-section of the spiral protrusion 42 is... Satisfaction and The relevant sine curve.

[0072] The outer diameter of the cross section of the spiral protrusion 42 The sine curve, for:

[0073]

[0074] in, This represents the rotation angle of rotor 4; The outer diameter of the outer peripheral wall 41 of rotor 4; For amplitude, ; This refers to the number of spiral protrusions (42). This sinusoidal structure generates periodic shear forces on the water medium during rotation, promoting uniform water film distribution and creating turbulent disturbances, thus improving heat generation efficiency. The amplitude... The number of heads determines the magnitude of the periodic vibration. The target period frequency is determined. For example, in this embodiment, , , During the rotation of rotor 4, the outer circumference of rotor 4 will form sinusoidal periodic vibrations on both sides for each rotation.

[0075] Reference Figures 4-5 , Figures 8-10 As shown, in this embodiment, the axial length and outer diameter of rotor 4 can be designed with different parameters according to the work requirements. If the outer diameter of rotor 4 is larger, then according to the formula for linear velocity, at the same rotational speed, the outer peripheral wall 41 of rotor 4 has a greater linear velocity, which means that it generates greater friction, impact and other thermal effects on the water medium at the water film gap 6, and the torque required for rotation at the same rotational speed will also be greater; if the outer diameter of rotor 4 is slightly smaller, the torque required for rotation of rotor 4 at the same rotational speed will also be smaller, and the work and heat generation effect of rotor 4 on the water medium can be improved by adjusting the rotational speed.

[0076] In this embodiment, the radial and axial dimensions of the rotor 4 are defined. The outer diameter of the outer peripheral wall 41 of the rotor 4 is 300mm~500mm; the protrusion height H2 of the helical protrusion 42 is 20mm~60mm; and the axial length of the rotor 4 is 280mm~500mm.

[0077] Furthermore, referring to Figure 3 , Figures 8-10 As shown, a number of through holes 43 are provided on the spiral protrusion 42. The through holes 43 pass through each turn of the spiral protrusion 42 in sequence along the axial direction, and the through holes 43 are evenly distributed in a ring.

[0078] Specifically, the rotor 4 has an axial length of 350 mm, and the spiral protrusions 42 are continuously arranged along the entire axial length of the rotor 4. Each spiral protrusion 42 has four axially extending through holes 43, which are evenly distributed in a ring along the circumference of the rotor 4. Each through hole 43 sequentially penetrates each turn of the spiral protrusion 42 along the axial direction. The through holes 43 connect the spiral grooves between the turns of the spiral protrusion 42, enabling communication between the two ends of the rotor 4, balancing the pressure on both sides of the rotor 4, promoting the axial flow of the water medium, and preventing localized liquid accumulation.

[0079] Reference Figure 1 , Figure 11 As shown, in this embodiment, the rotary drive 7 can be a permanent magnet synchronous motor, and the drive shaft 71 of the rotary drive 7 is connected to the shaft end 31 of the rotating shaft 3 by a coupling 5 to achieve transmission. Specifically, the coupling 5 can be a JM plate coupling.

[0080] Alternatively, to increase the rotational driving force on rotor 4, rotary drivers 7 can be installed on both ends 31 of shaft 3, meaning shaft 3 is simultaneously driven by two permanent magnet synchronous motors, as shown in the reference. Figure 12 As shown. Two motors are respectively installed at both ends of the housing 1. The drive shafts 71 of the two motors are respectively connected to both ends of the rotating shaft 3 through JM couplings, forming a dual-shaft coaxial drive structure. The two motors can be independently speed-adjusted and can achieve synchronous rotation in the same or opposite directions. By frequency matching, the system operates at the resonance point, realizing force field superposition and enhancing energy input. The two motors adopt encoder full closed-loop control, and together with the vector frequency converter, achieve a position synchronization accuracy of ±0.1° and a speed synchronization accuracy of ±0.1%, with an operating vibration amplitude ≤8.2mm / s².

[0081] To verify the heat generation capacity of this device, its heat generation performance was estimated:

[0082] Frictional heat generation power :

[0083]

[0084] Where η is the energy conversion efficiency. The value range is 0.6 to 0.85; The power is for the rotary driver 7. For example, in this embodiment, The value is 0.75; specifically, a rotary actuator 7 can be used for driving, with a single unit power of If it is 110kW, then .

[0085] The theoretical steam production m is:

[0086]

[0087] in, For the system thermal efficiency, this embodiment can be taken as 0.9, where hfg is the latent heat of vaporization of water, approximately 2260 kJ / kg;

[0088] but, This yields an estimated gas production figure.

[0089] In this embodiment, to enhance the collision and impact between the water input from the inlet 11 and the rotor 4, and to improve the efficiency of heat generation from the water, a Venturi structure is designed inside the inlet 11 of the housing 1. That is, the inner diameter of the inlet 11 forms a constricted structure towards the inner cavity 10 of the housing 1. By increasing the speed through the constricted diameter and negative pressure ejection, the vortex velocity of the incoming water is increased a second time, strengthening the fusion of the incoming water and the vortex within the cavity, reducing the energy loss of the incoming water, and simultaneously enhancing the heat generation from the vapor-liquid turbulence.

[0090] This embodiment also includes a PLC control system, which integrates real-time monitoring of multiple parameters such as speed, pressure, temperature, and steam production. It supports automatic adjustment of motor speed and water pump flow. The specific control method can adopt existing control technology, which will not be elaborated in this embodiment.

[0091] In this embodiment, the material selection for each component is as follows:

[0092] The shell 1 can adopt a multi-layer composite structure. The outer layer of the shell 1 is made of carbon steel Q235, the inner layer is lined with 304 stainless steel, and the middle layer is set with a 50mm thick aluminum silicate cotton insulation layer to reduce heat loss.

[0093] Rotor 4 is made of TC4 titanium alloy, which has wear resistance, high temperature resistance and pressure resistance, and is suitable for high-speed rotation conditions; the material can also be selected according to the working load: 304 / 316 stainless steel for low load conditions, 42CrMo low alloy steel for medium load conditions, and Inconel 718 nickel-based alloy for high load conditions.

[0094] The shaft 3 is made of 42CrMo low alloy steel, heat treated and tempered to HRC30-40, and the sealing position is coated with ceramic to improve wear resistance and corrosion resistance.

[0095] The sealing structure adopts carbon ring seal or dry gas seal to meet the high-speed rotation sealing requirements and ensure that the inner cavity 10 can withstand a working pressure of up to 30 bar.

[0096] The surface of the spiral protrusions 42 of rotor 4 can be coated with tungsten carbide to improve wear resistance and extend service life.

[0097] This embodiment also discloses a method for generating steam using a biaxial resonant sinusoidal spiral rotor centrifugal rotation, employing the biaxial resonant sinusoidal spiral rotor centrifugal rotation steam generating device as described in the above embodiment. During operation, water is introduced into the inner cavity 10 of the housing 1 through the inlet 11; the rotary actuator 7 drives the rotating shaft 3, causing the rotor 4 to rotate within the inner cavity 10 of the housing 1; the pressure in the inner cavity 10 is controlled to be no greater than 20 bar, and the rotational speed of the rotor 4 is controlled to be 3500~5000 r / min; the centrifugal force generated by the rotation of the spiral protrusions 42 on the outside of the rotor 4 presses the water medium onto the surface of the rotor 4, forming a water film between the spiral protrusions 42 and the inner peripheral wall 101 of the inner cavity 10. The spiral protrusions 42 perform work on the water film, causing the water film to heat up to its boiling point and form steam; the steam is output from the steam outlet 21 of the housing 1.

[0098] Installation and coaxiality adjustment: The rotor 4 is fixedly installed on the shaft 3 using a heat-shrinking process, and the dynamic balance of the rotor assembly is verified. The shaft 3 is installed on the end caps 2 at both ends through bearing assemblies, and then the end caps 2 are connected to the flanges of the housing 1 to complete the cavity assembly. The rotary drives 7 at both ends are connected to the two ends of the shaft 3 through couplings. Through mechanical leveling and coaxiality alignment, the coaxiality of the motor, coupling, shaft, and rotor is ensured, and the coaxiality deviation is controlled to be ≤0.02mm. The water inlet and steam outlet pipelines are connected to the electrical control system to complete the overall assembly.

[0099] No-load commissioning: By setting the inverter parameters, the control mode is vector control, the rated frequency is 50Hz, the rated speed is 1500r / min, and overload protection is enabled; jog the rotary drive 7, with a single start time ≤5s, and observe whether the rotation direction of rotor 4 is correct. After confirming there is no jamming or abnormal noise, proceed to graded speed-increase no-load operation, gradually increasing the speed to the rated speed, for example, 4000r / min, and run stably for 30 minutes. Monitor the operating vibration amplitude ≤8.2mm / s², and the motor current ≤90% of the rated current. The no-load commissioning is considered successful.

[0100] Pre-filling with water and load testing: Softened water is pumped from the inlet 11 into the inner cavity 10 of the housing 1 through the water supply pump until the water level in the inner cavity 10 reaches the rated water level, and the cavity is sealed; repeat the step-by-step speed increase process, gradually increasing the rotor speed 4 to 3500 r / min. If it runs stably for 2 hours, and the heat generation power fluctuation is ≤ ±2%, the vibration amplitude is ≤ 8.2 mm / s², and the motor current is ≤ 90% of the rated current, then the load testing is qualified.

[0101] Continuous steam production operation: During operation, the rotor 4 is kept rotating continuously, and softened water is continuously supplied from the water inlet 11 to the inner cavity 10 through the water supply pump. The working pressure of the inner cavity 10 is controlled to be 0.8MPa (corresponding to a saturation temperature of 172℃) by the PLC control system, and the rotation speed of the rotor 4 is controlled to be 3500r / min.

[0102] The rotor 4 rotates at high speed with the shaft 3. The centrifugal force generated by the rotation of the spiral protrusion 42 presses the water medium onto the surface of the outer peripheral wall 41 of the rotor 4. The water medium forms an ultra-thin uniform water film with a thickness of 50-200μm in the water film gap 6 between the spiral protrusion 42 and the inner peripheral wall 101 of the inner cavity 10. The high-speed rotation of the spiral protrusion 42 generates continuous friction, shearing and collision work on the water film, directly converting the mechanical energy output by the motor into the internal energy of the water, causing the water film to heat up rapidly to the saturation temperature of 172℃, and instantly vaporize to form saturated steam.

[0103] The generated saturated steam flows towards the end caps 2 at both ends under the action of centrifugal force and pressure difference, and is output from the steam outlet 21 and directly connected to the steam pipeline network. In this embodiment, when the rotor speed 4 is 3500 r / min, the saturated steam output can reach 780 kg / h, the steam dryness is ≥98%, the system thermal efficiency is ≥92%, and the energy consumption for producing 1 ton of steam is ≤108 kWh.

[0104] Using the device described above in the embodiment, different steam production effects can be achieved by adjusting the rotational speed of rotor 4 and the working pressure of inner cavity 10. Specific parameters are explained below:

[0105] Low load conditions: control rotor speed 4 2500r / min, internal cavity working pressure 0.8MPa, saturated steam output 530kg / h, steam dryness ≥95%, system thermal efficiency ≥90%;

[0106] Medium load conditions: control rotor speed 4 3000 r / min, internal cavity working pressure 0.8 MPa, saturated steam output 680 kg / h, steam dryness ≥ 97%, system thermal efficiency ≥ 91%;

[0107] High-load conditions: control rotor speed 4000r / min, internal cavity working pressure 1.0MPa, saturated steam output 920kg / h, steam dryness ≥98%, system thermal efficiency ≥90%;

[0108] High pressure condition: control rotor speed 4500r / min, internal cavity working pressure 20bar, saturated steam output 850kg / h, steam dryness ≥96%, system thermal efficiency ≥88%.

[0109] In this embodiment, the steam output and steam parameters can be flexibly adjusted by regulating the rotor speed and internal cavity pressure to adapt to different steam demand, maintaining high thermal efficiency and stable steam production performance over a wide range of operating conditions.

[0110] 1. Housing; 10. Inner cavity; 101. Inner peripheral wall; 11. Inlet; 2. End cap; 21. Steam outlet; 22. Bearing seat; 221. Bearing assembly; 222. Rotary seal assembly; 3. Shaft; 31. Shaft end; 4. Rotor; 41. Outer peripheral wall; 42. Spiral protrusion; 421. Root; 422. Top; 43. Through hole; 44. Impeller; 440. Blade; 441. Inner end; 442. Outer end; 443. Blade flow channel; 5. Coupling; 6. Water film gap; 7. Rotary actuator; 71. Drive shaft;

[0111] Example 2

[0112] This embodiment discloses a biaxial resonant sinusoidal spiral rotor centrifugal steam generator, based on Embodiment 1, and further referring to... Figure 13 Please provide a detailed explanation.

[0113] In this embodiment, impellers 44 are fixedly connected to both end faces of rotor 4. Impellers 44 include a plurality of blades 440. Specifically, each blade 440 is a backward-curved arc-shaped blade, and the blades 440 are arranged in a circumferential array. Impellers 44 are located in the end gap 8, and can apply centrifugal rotational force to both ends of rotor 4.

[0114] The blade 440 includes an inner end 441 and an outer end 442, with the inner end 441 being narrower and the outer end 442 being thicker. A blade flow channel 443 is formed between adjacent blades 440, connecting the inner and outer circumferences of the impeller 44. The width of the blade flow channel 443 gradually increases towards the outer circumference and gradually decreases towards the inner circumference.

[0115] In this embodiment, steam outlets 21 are provided at both ends of the end caps 2 of the housing 1. Moreover, the impellers 44 at both ends of the rotor 4 rotate in the same direction.

[0116] Reference Figure 13 As shown, the bending direction of the blade 440 is opposite to the clockwise rotation direction of the rotor. During the rotation of the rotor 4, the blade 440 will generate centrifugal movement, causing the blade 440 to move outwards. After the gas-liquid mixture enters the end gap 8 on the output side, the blade 440 forms a radial centrifugal throw-out of the water. Moreover, since the density of liquid water in the gas-water mixture is greater, the liquid water can move towards the outer periphery during centrifugal action and can re-enter the outer periphery of the rotor 4. The gaseous steam has a relatively lower density and can be retained in the end gap 8 at the end of the rotor 4. The end gap 8 is close to the steam outlet 21, which facilitates the discharge of steam from the steam outlet 21.

[0117] Moreover, under the centrifugal action of the blades 440, centrifugal pressure can be applied to the outer periphery of the rotor 4, thereby increasing the internal pressure in the water film gap 6 on the outer periphery of the rotor 4, thereby improving the heat generation efficiency of the water film gap 6, strengthening the heat generation by shear friction and external impact, improving the heat generation efficiency, and thus increasing the steam generation rate.

[0118] Example 3

[0119] This embodiment discloses a direct-drive oblique-hole array type high-speed rotary steam generator, which is based on Embodiment 1 and further refers to... Figure 14 Please provide a detailed explanation.

[0120] In this embodiment, impellers 44 are fixedly connected to both end faces of rotor 4. Impellers 44 include a plurality of blades 440. Specifically, each blade 440 is a backward-curved arc-shaped blade, and the blades 440 are arranged in a circumferential array. Impellers 44 are located in the end gap 8, and can apply centrifugal rotational force to both ends of rotor 4.

[0121] The blade 440 includes an inner end 441 and an outer end 442, with the inner end 441 being narrower and the outer end 442 being thicker. A blade flow channel 443 is formed between adjacent blades 440, connecting the inner and outer circumferences of the impeller 44. The width of the blade flow channel 443 gradually increases towards the outer circumference and gradually decreases towards the inner circumference.

[0122] In this embodiment, a steam outlet 21 is provided only on the end cover 2 on one side (first side) of the housing 1, and no steam outlet 21 is provided on the end cover on the other side (second side). Moreover, the impellers 44 at both ends of the rotor 4 rotate in opposite directions.

[0123] In this embodiment, during the rotation of the rotor 4, the spiral protrusions 42 on the outer peripheral wall 41 will push the water spirally from the first side to the second side, thereby pushing the water toward the end cap on the side where the steam outlet 21 is not opened, so that the second side in the inner cavity 10 can achieve pressure accumulation.

[0124] Reference Figure 13As shown, on the first side (i.e. the steam output side), the bending direction of the blade 440 is opposite to the clockwise rotation direction of the rotor. During the rotation of the rotor 4, the blade 440 will generate centrifugal movement, causing the blade 440 to generate centrifugal movement towards the outer periphery. After the gas-liquid mixture enters the end gap 8 on the output side, the blade 440 forms a radial centrifugal throw-out of the water. Moreover, since the density of liquid water in the gas-water mixture is greater, during centrifugal action, the liquid water can move towards the outer periphery and can re-enter the outer periphery of the rotor 4. The gaseous steam has a relatively lower density and can be retained in the end gap 8 at the end of the rotor 4. The end gap 8 is close to the steam outlet 21, which facilitates the discharge of steam from the steam outlet 21.

[0125] Moreover, under the centrifugal action of the blades 440, centrifugal pressure can be applied to the outer periphery of the rotor 4, thereby increasing the internal pressure in the water film gap 6 on the outer periphery of the rotor 4, thereby improving the heat generation efficiency of the water film gap 6, strengthening the shear friction inside the hole and the impact heat generation outside the hole, improving the heat generation efficiency, and thus increasing the steam generation rate.

[0126] Reference Figure 14 As shown, on the second side (i.e. the side where steam is not output), the bending direction of the blade 440 is the same as the clockwise rotation direction of the rotor. During the rotation of the rotor 4, the opening of the outer periphery of the blade flow channel 443 can face the water-vapor mixture, thereby increasing the internal pressure of the gap 8 at the end of that side. The pressure can be transmitted from the gap to the water film gap 6 and other spaces, thereby increasing the overall pressure in the entire shell 1, further improving the heat generation efficiency of the water film gap 6, strengthening the heat generation efficiency of shear friction and external impact, and thus increasing the steam generation rate.

[0127] The above description is merely a preferred embodiment of the present invention. The scope of protection of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the present invention's concept are within the scope of protection of the present invention. It should be noted that for those skilled in the art, any improvements and modifications made without departing from the principles of the present invention should also be considered within the scope of protection of the present invention.

Claims

1. A dual-axis resonant sinusoidal helical rotor centrifugal steam generator, characterized in that, The device includes a housing (1), a rotating shaft (3), a rotor (4), and a rotary actuator (7). The housing (1) has end caps (2) at both ends. The housing (1) has an inner cavity (10) inside. The housing (1) has a water inlet (11) on its outer periphery and a steam outlet (21) on the outer side of the end caps (2). The rotating shaft (3) is rotatably mounted in the inner cavity (10) and driven to rotate by the rotary actuator (7). The rotor (4) is located in the inner cavity (10) and is fixedly mounted on the rotating shaft (3). The rotating shaft (3), the rotor (4), and the inner cavity (10) are coaxially arranged. The outer peripheral wall (41) of the rotor (4) is integrally formed with a spiral protrusion (42), and a water film gap (6) is formed between the spiral protrusion (42) and the inner peripheral wall (101) of the inner cavity (10).

2. The biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 1, characterized in that, The spiral protrusion (42) has a root (421) near the rotor (4) and a top (422) away from the rotor (4); along the axial direction of the rotor (4), the width W1 of the root (421) is greater than the width W2 of the top (422).

3. The biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 2, characterized in that, Along the radial direction of the rotor (4), the width between the outer peripheral wall (41) of the rotor (4) and the inner peripheral wall (101) of the inner cavity (10) is H1, the protrusion height of the spiral protrusion (42) is H2, the width of the water film gap (6) is H3, H3=H1-H2, and 1.0mm≤H3≤4.0mm.

4. A biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 3, characterized in that, The width H3 of the water film gap (6) is 3 mm.

5. A biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 3, characterized in that, The width W2 of the top (422) is: 0.8H3≤W2≤1.1H3; the pitch of the spiral protrusion (42) is P; and the width W1 of the root (421) is: 0.8P≤W1≤1.1P.

6. A biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 2, characterized in that, The spiral protrusion (42) is a multi-headed spiral structure, with 1 to 4 heads; the spiral angle of the spiral protrusion (42) is 10° to 18°.

7. A biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 2, characterized in that, The outer diameter of the cross section of the helical protrusion (42) It is a sine curve. for: in, The rotation angle of the rotor (4); The outer diameter of the outer peripheral wall 41 of the rotor (4); For amplitude, ; The number of heads of the spiral protrusion (42).

8. A biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 3, characterized in that, The outer diameter of the outer peripheral wall (41) of the rotor (4) is 300mm~500mm; the protrusion height of the spiral protrusion (42) is H2, which is 20mm~60mm; the axial length of the rotor (4) is 280mm~500mm.

9. A biaxial resonant sinusoidal spiral rotor centrifugal steam generator according to claim 1, characterized in that, The spiral protrusion (42) has several through holes (43), which pass through each turn of the spiral protrusion (42) in sequence along the axial direction, and the through holes (43) are evenly distributed in a ring.

10. A method for generating steam by centrifugal rotation of a biaxial resonant sinusoidal helical rotor, characterized in that, The device for generating steam using a biaxial resonant sinusoidal spiral rotor as described in any one of claims 1-9 is employed. During operation, water is introduced into the inner cavity (10) of the shell (1) through the inlet (11); The rotary drive (7) rotates the drive shaft (3) and drives the rotor (4) to rotate in the inner cavity (10) of the housing (1); the pressure in the inner cavity (10) is controlled to be no more than 20 bar, and the rotation speed of the rotor (4) is controlled to be 3500~5000 r / min; The centrifugal force generated by the rotation of the spiral protrusion (42) outside the rotor (4) presses the water medium onto the surface of the rotor (4). The water medium forms a water film between the spiral protrusion (42) and the inner peripheral wall (101) of the inner cavity (10). The spiral protrusion (42) does work on the water film, and the water film heats up to the boiling point to form steam. The steam is output from the steam outlet (21) of the shell (1).

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