A centrifugal pneumatic fluid flash evaporation seawater desalination device and method

Abstract

This invention discloses a centrifugal pneumatic fluid flash seawater desalination device and method, including a rotary driver and a desalination module. The desalination module includes a shell, a rotating shaft, a rotor, a positive pressure impeller, and a negative pressure impeller. The rotor is rotatably mounted inside the shell via the rotating shaft, and a phase change gap is formed between the outer periphery of the rotor and the inner wall of the shell. The positive pressure impeller and the negative pressure impeller are located in the positive pressure chamber and the negative pressure chamber, respectively. The shell is provided with an inlet and an outlet corresponding to the outer periphery of the positive pressure chamber and the negative pressure chamber, respectively. The rotating shaft drives the positive pressure impeller, the rotor, and the negative pressure impeller to rotate. The positive pressure impeller can send seawater from the positive pressure chamber into the phase change gap, the rotor can heat the seawater in the phase change gap, and the negative pressure impeller can create a negative pressure in the negative pressure chamber. After passing through the phase change gap, the heated seawater can boil and evaporate in the negative pressure chamber. The steam-water mixture formed in the negative pressure chamber is thrown out from the outlet, and fresh water is obtained after steam-water separation.

Description

Technical Field

[0001] This invention relates to seawater desalination equipment, and more specifically, to a centrifugal pneumatic fluid flash seawater desalination device, and also to a centrifugal pneumatic fluid flash seawater desalination method using the device. Background Technology

[0002] The global freshwater shortage is becoming increasingly severe, and seawater desalination is a core technological means to solve the water shortage problem in coastal, island, and offshore environments. Current mainstream seawater desalination technologies mainly include multi-stage flash distillation (MSF), low-temperature multi-effect distillation (MED), and reverse osmosis (RO), but their application scenarios and limitations differ significantly.

[0003] Existing technology application areas and environments: 1. Multi-stage flash distillation and low-temperature multi-effect distillation: mostly used in areas with abundant fossil energy / industrial waste heat, such as the Middle East coast and large coastal industrial parks. They are suitable for large-scale fixed desalination plants, but rely on high-temperature heat sources and supporting boilers and waste heat systems. The equipment is bulky and the infrastructure cost is high. They cannot be adapted to mobile / miniaturized scenarios without centralized heat sources, such as ships, islands, and offshore platforms. 2. Reverse osmosis membrane method: Although it can be miniaturized, it has strict requirements for seawater pretreatment. It is susceptible to membrane blockage and damage due to seawater impurities and salt corrosion. The operation and maintenance cost is high. It is not stable enough in high-salt and high-impurity seawater environments and cannot be adapted to remote scenarios with extreme low temperatures and no external high-voltage power supply.

[0004] The core shortcomings of existing technologies are: traditional flash evaporation technology requires an external high-temperature heat source to drive it, the negative pressure construction is disconnected from the phase change heat transfer, and the phase change efficiency is low; conventional miniaturized desalination devices either have high energy consumption or insufficient freshwater purity and water production stability, making it difficult to meet the three core requirements of portability, low energy consumption, and high freshwater purity. Especially in scenarios with limited space and no centralized heat source, such as island garrisoning, ocean-going vessels, and marine scientific research, the applicability of existing equipment is extremely poor. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a centrifugal pneumatic fluid flash seawater desalination device and method.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] A centrifugal pneumatic fluid flash seawater desalination device includes a rotary driver and a desalination module. The desalination module includes a shell, a rotating shaft, a rotor, a positive pressure impeller, and a negative pressure impeller. The shell has a cylindrical inner cavity.

[0008] The rotor is rotatably mounted inside the housing via a rotating shaft, and a phase change gap is formed between the outer periphery of the rotor and the inner wall of the housing, the radial width of the phase change gap being 1mm-4mm.

[0009] The outer casing contains a positive pressure chamber and a negative pressure chamber corresponding to the two ends of the rotor. The positive pressure impeller and the negative pressure impeller are coaxially fixedly connected to the two ends of the rotor and are located in the positive pressure chamber and the negative pressure chamber, respectively.

[0010] The outer shell is provided with an inlet and an outlet on the outer periphery of the positive pressure chamber and the negative pressure chamber, respectively.

[0011] The rotating shaft drives the positive pressure impeller, rotor and negative pressure impeller to rotate. The positive pressure impeller can send the seawater in the positive pressure chamber into the phase change gap. The rotor can heat the seawater in the phase change gap. The negative pressure impeller can throw the seawater in the negative pressure chamber out of the outlet and form a negative pressure in the negative pressure chamber.

[0012] The present invention is further configured such that the axial length of the rotor is 300mm-400mm, the outer diameter of the rotor is 450mm-500mm, and the rotational speed of the rotor is 3500r / min-5500r / min.

[0013] The present invention is further configured such that a phase change structure is formed on the outer periphery of the rotor, and the axial distribution length of the phase change structure on the outer periphery of the rotor is 90%-95% of the axial length of the rotor; the phase change structure includes a plurality of phase change holes.

[0014] The present invention is further configured such that the phase change holes are divided into several groups, and each group is distributed in a ring array; in each group of phase change holes, each phase change hole is evenly arranged along the axis of rotation.

[0015] The present invention is further configured such that the phase change holes are provided in 50-60 groups, each group having 10-20 phase change holes, and the diameter of the phase change holes being 15mm-20mm.

[0016] The present invention is further configured such that the axial direction of the phase change hole is inclined to the radial direction of the rotor and inclined towards the rotation direction of the rotor, with an inclination angle of α, the range of the inclination angle α being 5°-45°.

[0017] The present invention is further configured such that the blades of the positive pressure impeller and the negative pressure impeller are arranged in opposite directions;

[0018] The present invention is further configured such that the two ends of the outer shell are respectively closed by end cap one and end cap two, and the inner cavities of end cap one and end cap two are both eccentric volute structures, and the eccentricity is in opposite directions;

[0019] The present invention is further configured such that bearing seats are fixedly installed on the outer sides of both end cap one and end cap two, and the two ends of the rotating shaft pass through end cap one and end cap two respectively, and are rotatably installed on the bearing seats through bearing assemblies; a sealing assembly is installed between the bearing seats and the rotating shaft.

[0020] The present invention is further configured such that slag discharge holes are provided at the lower parts of both the positive pressure chamber and the negative pressure chamber of the outer shell.

[0021] The present invention is further configured such that the rotary driver has two drive shafts, and the dilution module is provided in two sets, with the rotating shafts of the two sets of dilution modules respectively connected to the two drive shafts via couplings.

[0022] The present invention also provides a centrifugal pneumatic fluid flash seawater desalination method, which uses the centrifugal pneumatic fluid flash seawater desalination device described above.

[0023] During the seawater desalination process, seawater is pumped into the input port of the desalination module; the rotary drive drives the shaft to rotate, which in turn drives the positive pressure impeller, rotor and negative pressure impeller to rotate.

[0024] The positive pressure impeller can send the seawater in the positive pressure chamber into the phase change gap, and the rotor can heat the seawater in the phase change gap. The negative pressure impeller can throw the seawater in the negative pressure chamber out of the outlet and create a negative pressure environment in the negative pressure chamber.

[0025] Seawater passes through a phase change gap, and the heated seawater boils and evaporates in the negative pressure chamber. The steam-water mixture formed in the negative pressure chamber is thrown out from the outlet, and fresh water is obtained after steam-water separation.

[0026] In summary, the present invention has the following beneficial effects:

[0027] This solution utilizes centrifugal pneumatic fluid and negative pressure phase change principles to achieve seawater flash desalination. The device housing has a cylindrical inner cavity with a rotor arranged correspondingly around its inner circumference. A phase change structure is located on the outer circumference of the rotor. The phase change structure on the inner wall of the housing and the outer circumference of the rotor interact to form a phase change gap, suitable for a design range of 1mm-4mm. As water flows through this gap, a uniform water film forms between the rotor and the inner wall of the housing. The high-speed rotation of the rotor causes the seawater to collide, rub, and shear, generating heat and directly converting pneumatic kinetic energy into phase change heat energy. This achieves an autonomous phase change from liquid to gaseous state. The entire process requires no external boiler, steam, or other heat sources, significantly reducing energy consumption. It is suitable for applications in remote coastal areas, open ocean locations, and isolated islands without centralized heating.

[0028] The device employs a design combining a compact shell with an eccentric spiral volute structure. The end caps at both ends of the shell are equipped with volute structures in opposite eccentric directions, which effectively increases the positive pressure and negative pressure during impeller rotation. It adopts a symmetrical structure with water entering at one end of the rotor and exiting at the other. The positive pressure impeller at one end of the rotor efficiently draws in seawater using the principle of pneumatic fluid, while the negative pressure impeller at the other end centrifugally ejects the steam-water mixture at high speed, completing the flash evaporation process. At the same time, the negative pressure impeller at one end of the rotor creates a stable negative pressure environment, which lowers the boiling point of seawater, completely eliminating the dependence on high-temperature heat sources. With the subsequent addition of a steam-water separation module, it can achieve rapid and efficient separation of steam and concentrated seawater, ultimately obtaining fresh water. Attached Figure Description

[0029] Figure 1 This is a cross-sectional structural diagram of this embodiment;

[0030] Figure 2 for Figure 1 Enlarged view of point A in the middle;

[0031] Figure 3 This is a top view of the structure in this embodiment;

[0032] Figure 4 This is a three-dimensional structural diagram of this embodiment;

[0033] Figure 5 This is a first-view perspective perspective view of the rotor, positive pressure impeller, and negative pressure impeller in this embodiment.

[0034] Figure 6 This is a second-view perspective perspective view of the rotor, positive pressure impeller, and negative pressure impeller in this embodiment;

[0035] Figure 7 This is a schematic cross-sectional view of the rotor in this embodiment;

[0036] Figure 8 This is a schematic diagram of the dual fade module in this embodiment.

[0037] Reference numerals: Rotary driver 1; Drive shaft 101; Coupling 102; Desalination module 2; Housing 3; Positive pressure chamber 301; Negative pressure chamber 302; End cover 1 4; Inlet 401; End cover 2 5; Output port 501; Rotating shaft 6; Rotor 7; Phase change structure 701; Phase change hole 702; Positive pressure impeller 8; Negative pressure impeller 9; Bearing housing 10; Bearing assembly 1001; Sealing assembly 1002. Detailed Implementation

[0038] 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.

[0039] This embodiment provides a centrifugal pneumatic fluid flash seawater desalination device, which relies on the principle of centrifugal pneumatic fluid and negative pressure phase change to achieve seawater flash desalination. The device has a compact structure and low energy consumption, effectively solving the pain points of existing technologies such as reliance on high-temperature heat sources, large equipment size, and complex operation and maintenance.

[0040] Reference Figures 1-8 As shown, the centrifugal pneumatic fluid flash seawater desalination device in this embodiment mainly includes a rotary drive 1 and a desalination module 2. The desalination module 2 is the core working unit, which is specifically composed of components such as a shell 3, end cover 1 4, end cover 2 5, rotating shaft 6, rotor 7, positive pressure impeller 8, negative pressure impeller 9, and bearing seat 10.

[0041] The outer shell 3 has a cylindrical inner cavity with an integrated molding structure. Its two ends are closed by end cap 4 and end cap 5, respectively. The inner cavities of end cap 4 and end cap 5 are both designed as eccentric volute structures, and their eccentricity is in opposite directions. This eccentric volute structure design, combined with Bernoulli's equation, can effectively improve the positive pressure and negative pressure during impeller rotation, realize the conversion of fluid from "high speed and low pressure" to "low speed and high pressure", and ensure the stability of fluid transportation and negative pressure construction.

[0042] The machined surface of the outer casing 3 is free of scratches, burrs, and oxide layers, ensuring the smoothness of the flow channel and reducing fluid resistance. An inlet 401 is provided on the outer periphery of the positive pressure chamber 301, which can be located on the outer side of end cap 4. An outlet 501 is provided on the outer periphery of the negative pressure chamber 302, which can be located on the outer side of end cap 5.

[0043] In addition, slag discharge holes are provided at the lower part of both the positive pressure chamber 301 and the negative pressure chamber 302. Slag discharge holes can also be provided on the lower side of the middle section of the outer shell 3. Impurities and concentrated salt slag generated during the seawater treatment process can be discharged in a timely manner through the slag discharge holes to avoid clogging the equipment flow channel, affecting the water film formation and phase change efficiency, and extending the service life of the device.

[0044] The rotor 7 is rotatably mounted in the cylindrical inner cavity of the outer casing 3 via the rotating shaft 6. The outer periphery of the rotor 7 is provided with a phase change structure 701, which consists of a number of evenly distributed phase change holes 702 with independently sealed channels. The axial direction of the phase change holes 702 is inclined to the radial direction of the rotor 7 and is inclined towards the rotation direction of the rotor 7. The inclination angle α between the phase change holes 702 and the radial direction of the rotor can be adjusted according to the actual working conditions. The recommended range is 5°-45°.

[0045] A phase change gap is formed between the outer periphery of the rotor 7 and the inner wall of the outer casing 3. The radial width of this phase change gap is controlled between 1mm and 4mm. In this embodiment, it is preferably 3mm. This width design ensures that a uniform water film is formed when water flows through, which not only guarantees the contact area between the seawater and the wall surface and improves the efficiency of friction and shear heat generation, but also avoids the problem of dry burning caused by an excessively thin water film, thus achieving a stable and controllable phase change process.

[0046] In this embodiment, the operating speed of the rotor 7 can be adjusted according to actual desalination needs, with a recommended range of 3500 r / min to 5500 r / min. The aperture of the phase change hole 702 is preferably 15 mm to 20 mm. The axial distribution length of the phase change structure 701 on the outer periphery of the rotor 7 is 90% to 95% of the axial length of the rotor 7. Its length-to-width ratio can be reasonably designed according to the dimensions of the outer shell 3 and the rotor 7 to ensure seawater heating efficiency and flash evaporation effect.

[0047] Specifically, rotor 7 can adopt various size parameters and operate at different speeds;

[0048] For example: the rotational speed n of rotor 7 is controlled to be 3500 r / min; the phase change holes 702 outside rotor 7 are arranged in 60 groups of annular arrays, with 15 holes in each group, a hole diameter of φ20mm, and a total of 900 holes; the inclination angle α of phase change holes 702 is 10°; the outer diameter D of rotor 7 is 480mm.

[0049] According to the formula for linear velocity V: V = π × D × n / 60; the calculated linear velocity V ≈ 87.96 m / s;

[0050] In operation, seawater forms a uniform water film in the phase change gap. After being cut, rubbed, and sheared through the oblique hole, it generates heat and enters the negative pressure chamber, where it can flash evaporate in a low-temperature environment of 40-50℃.

[0051] For example: the rotational speed n of rotor 7 is controlled to be 4500 r / min; the phase change holes 702 outside rotor 7 are arranged in 60 groups of annular arrays, with 20 holes in each group, and the hole diameter is φ15mm, for a total of 1200 holes; the inclination angle α of phase change holes 702 is 10°; the outer diameter D of rotor 7 is 480mm.

[0052] According to the formula for linear velocity V: V=π×D×n / 60; the calculated linear velocity V≈113.10m / s; the heat generation at the same rotational speed is 1.33 times that of a φ20mm hole; the relative heat generation ratio at 3500r / min is approximately 1.65.

[0053] In operation, the water film is cut more finely and has a larger specific surface area, resulting in stronger heat generation and significantly improved vaporization speed. The water production efficiency is higher than that of Example 1, making it suitable for medium-sized water production needs.

[0054] For example: the rotational speed n of rotor 7 is controlled to be 5000 r / min; the phase change holes 702 outside rotor 7 are arranged in 60 groups of annular arrays, with 20 holes in each group, and the hole diameter is φ15mm, for a total of 1200 holes; the inclination angle α of phase change holes 702 is 15°; the outer diameter D of rotor 7 is 480mm.

[0055] According to the formula for linear velocity V: V=π×D×n / 60; the calculated linear velocity V≈125.66m / s; the heating ratio is further increased relative to 3500r / min, and the heat generation is nearly doubled.

[0056] When in operation, it has the strongest high-speed shearing power, reaches the peak negative pressure flash evaporation rate, and has the largest water production, making it suitable for emergency water supply and high-yield freshwater demand scenarios.

[0057] For example: the rotational speed n of rotor 7 is controlled to be 4000 r / min; the phase change holes 702 outside rotor 7 are arranged in 55 annular arrays, with 18 holes in each group and a hole diameter of φ18mm; the inclination angle α of phase change holes 702 is 30°; the outer diameter D of rotor 7 is 480mm.

[0058] According to the formula for linear velocity V: V=π×D×n / 60; the calculated linear velocity V≈100.48m / s.

[0059] The large tilt angle during operation makes the water flow collision stronger and the local friction and shearing more intense, resulting in high single-point heating intensity. It is suitable for desalination after pretreatment of high-salinity and high-impurity seawater.

[0060] In this embodiment, the rotor 7, positive pressure impeller 8, and negative pressure impeller 9 are made of titanium alloy Ti-6Al-4V, which possesses excellent strength and corrosion resistance, good fatigue resistance, excellent heat and low temperature resistance, good biocompatibility, and is non-magnetic and does not interfere with magnetic fields, making it suitable for harsh marine environments with high humidity and high salinity. The shaft 6 is made of 42CrMo material and has undergone quenching and tempering treatment, achieving a hardness of 57-62HRC, ensuring the shaft's fatigue strength and rotational stability. The shaft surface is partially chrome-plated, with a single-sided chrome plating thickness of 0.10mm, resulting in an outer diameter of 55mm after chrome plating, improving the shaft's corrosion resistance and sealing performance. Simultaneously, a threaded structure is machined on the shaft 6, which, together with a steel plate locking nut, achieves coaxial locking and fixation of the rotor 7, negative pressure impeller 9, positive pressure impeller 8, and shaft 6, preventing loosening of components during rotation.

[0061] The positive pressure impeller 8 and the negative pressure impeller 9 are coaxially fixedly connected to both ends of the rotor 7, and are respectively located in the positive pressure chamber 301 and the negative pressure chamber 302 formed in the outer casing 3. The blades of the positive pressure impeller 8 and the negative pressure impeller 9 rotate in opposite directions. With the volute structure with opposite eccentric directions at both ends, the efficient intake of seawater and the high-speed ejection of the air-water mixture can be achieved respectively.

[0062] Bearing seats 10 are fixedly installed on the outer sides of both end cap 4 and end cap 5. The two ends of the rotating shaft 6 pass through end cap 4 and end cap 5 respectively, and are rotatably installed in the bearing seats 10 via bearing assemblies 1001. The bearing assemblies 1001 are arranged in left and right sets to achieve stable support for the rotating shaft 6. A sealing assembly 1002 is installed between the bearing seat 10 and the rotating shaft 6, which can effectively prevent fluid leakage and external air entry into the device, ensure the stability of the negative pressure environment, and provide the necessary conditions for low-temperature phase change of seawater.

[0063] The rotary drive 1 includes a water-cooled motor, a coupling 102, and a motor mounting channel steel. The coupling 102 enables the desalination module 2 to be driven.

[0064] Furthermore, referring to Figure 8 As shown, the desalination module 2 can be driven by two sets of drives, and the rotary actuator 1 adopts a dual-shaft structure. The rotary actuator 1 has two drive shafts 101, which can be dual-head motors. The desalination module 2 is set with two sets of drives, and the rotating shafts 6 of the two sets of desalination modules 2 are connected to the two drive shafts 101 through couplings 102, which can realize the synchronous operation of the two modules and improve the seawater desalination efficiency. Among them, the coupling 102 has good buffering and vibration reduction performance to ensure the coaxiality of the transmission; the motor fixing channel steel fixes the drive motor, improving the stability of the motor operation, and the shock-absorbing pad is set between the outer shell 3 and the device support base to reduce vibration and noise during the operation of the device.

[0065] This embodiment also discloses a centrifugal pneumatic fluid flash evaporation seawater desalination method. Based on the implementation of the device in the above embodiment, relying on the principle of centrifugal pneumatic fluid and negative pressure phase change, the specific implementation steps are as follows:

[0066] The first step is equipment debugging and startup: check the connection and sealing of each component of the device, the lubrication of the bearing assembly 1001, the unobstructedness of the slag discharge hole, and the sealing performance of the sealing assembly 1002. After ensuring that the equipment is fault-free and leak-free, start the water-cooled motor of the rotary drive 1. Through the coupling 102, drive the rotating shafts 6 of the two sets of desalination modules 2 to rotate synchronously, thereby driving the positive pressure impeller 8, rotor 7 and negative pressure impeller 9 to rotate synchronously at high speed.

[0067] The second step is negative pressure water absorption and seawater input: During rotation, the negative pressure impeller 9 at one end of the rotor 7 rotates at high speed, forming a stable negative pressure environment in the negative pressure chamber 302. Relying on the continuity equation, mass conservation, and Bernoulli equation of fluid mechanics, energy is efficiently converted, reducing the boiling point of seawater from 100℃ to 40-50℃, providing conditions for low-temperature phase change of seawater. At the same time, seawater is continuously pumped to the input port 401 of the desalination module 2 through the delivery pump. The seawater enters the positive pressure chamber 301 of the outer shell 3 through the input port 401. At this time, the positive pressure impeller 8 generates positive pressure using the principle of pneumatic fluid during high-speed rotation, smoothly and efficiently pressing the seawater in the positive pressure chamber 301 into the phase change gap between the rotor 7 and the inner wall of the outer shell 3, realizing the synchronous absorption and transportation of seawater and improving the fluid absorption efficiency.

[0068] The third step is high-speed phase change heat generation: When seawater flows through the phase change gap, driven by the high-speed rotation of rotor 7, it undergoes continuous and intense collisions, friction, and shearing with the porous phase change zone of the phase change structure 701 on the outer periphery of the rotor and the inner wall of the outer shell 3, forming a turbulent state. This directly converts aerodynamic kinetic energy into phase change heat energy, rapidly heating the seawater. This process does not require an external boiler, steam, or other additional heat source; it utilizes only the fluid's own energy to achieve phase change, significantly reducing energy consumption. Simultaneously, the 3mm width design of the phase change gap allows the seawater to form a water film with a uniform cross-section, further improving the efficiency of friction and shear heat generation and ensuring the fullness of the liquid-gas phase change.

[0069] The fourth step is positive pressure centrifugal flash evaporation: Rotor 7 continues to rotate at high speed. Seawater heated to 40-50℃ enters the negative pressure chamber 302 and rapidly boils and flashes under negative pressure, forming a steam-water mixture. Subsequently, the steam-water mixture is transported to the negative pressure end of rotor 7 under the action of centrifugal force. It is then propelled at high speed into the negative pressure chamber 302 region of the outer shell 3 by the centrifugal force of the negative pressure impeller 9. The centrifugal force field causes the gas phase vapor to move to the outside of the shell and the concentrated seawater to gather towards the center of the rotor, achieving preliminary gas-liquid separation of the steam-water mixture and completing the flash evaporation process. The centrifugal projection speed of the negative pressure impeller 9 is precisely matched with the rotational speed of rotor 7 to ensure flash evaporation efficiency and lay the foundation for subsequent deep steam-water separation.

[0070] The fifth step is steam-water separation: the steam-water mixture after flash evaporation is ejected through outlet 501 and enters the matching steam-water separation module. By utilizing the density difference between the gas and liquid phases, the steam and concentrated seawater are efficiently and deeply separated. The separated steam enters the condensation zone and is condensed to obtain pure fresh water, while the concentrated seawater is discharged through outlet 501. It can be desalinated or recycled to improve the utilization rate of seawater and ensure the purity of fresh water.

[0071] During the operation of the device, impurities in the seawater will accumulate in the phase change gap, flow channel and porous phase change zone. The impurities are periodically discharged through the slag discharge hole on the side cover of the outer shell 3 and the slag discharge hole on the rotor shell without stopping the machine for disassembly. This ensures the smooth flow of the flow channel inside the device and prevents changes in water film thickness and a decrease in phase change efficiency caused by flow channel blockage. After a period of operation, the machine is stopped to check the sealing performance of the sealing component 1002 and the wear of the bearing component 1001. Lubrication or replacement is performed in a timely manner. At the same time, the threaded connection of each component is checked to ensure the long-term stable operation of the device.

[0072] This solution, relying on structural innovation, principle innovation, process innovation, and scenario adaptation innovation, realizes low-temperature flash evaporation seawater desalination without an external high-temperature heat source, significantly reducing the energy consumption of seawater desalination. Moreover, the device has a compact structure, is easy to operate, and runs stably. The materials and processing precision of the components are adapted to the harsh marine environment, and it can be adapted to a variety of special scenarios without centralized heating and with limited space. It solves the pain point of poor applicability of existing technologies in mobile and miniaturized scenarios, and has good practicality, stability, and promotion value.

[0073] 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 centrifugal pneumatic fluid flash seawater desalination device, characterized in that, It includes a rotary driver (1) and a desalination module (2). The desalination module (2) includes a housing (3), a rotating shaft (6), a rotor (7), a positive pressure impeller (8), and a negative pressure impeller (9). The housing (3) has a cylindrical inner cavity. The rotor (7) is rotatably mounted inside the housing (3) via a rotating shaft (6). A phase change gap is formed between the outer periphery of the rotor (7) and the inner wall of the housing (3). The radial width of the phase change gap is 1mm-4mm. The outer casing (3) has a positive pressure chamber (301) and a negative pressure chamber (302) respectively formed at both ends of the rotor (7). The positive pressure impeller (8) and the negative pressure impeller (9) are coaxially fixedly connected to both ends of the rotor (7) and are located in the positive pressure chamber (301) and the negative pressure chamber (302) respectively. The outer shell (3) is provided with an inlet (401) and an outlet (501) on the outer periphery of the positive pressure chamber (301) and the negative pressure chamber (302), respectively; The rotating shaft (6) drives the positive pressure impeller (8), the rotor (7) and the negative pressure impeller (9) to rotate. The positive pressure impeller (8) can send the seawater in the positive pressure chamber (301) into the phase change gap. The rotor (7) can heat the seawater in the phase change gap. The negative pressure impeller (9) can throw the seawater in the negative pressure chamber (302) out from the outlet (501) and form a negative pressure in the negative pressure chamber (302).

2. The centrifugal pneumatic fluid flash seawater desalination device according to claim 1, characterized in that, The rotor (7) has an axial length of 300mm-400mm and an outer diameter of 450mm-500mm; the rotor (7) has a rotational speed of 3500r / min-5500r / min.

3. The centrifugal pneumatic fluid flash seawater desalination device according to claim 1, characterized in that, A phase change structure (701) is formed on the outer periphery of the rotor (7), and the axial distribution length of the phase change structure (701) on the outer periphery of the rotor (7) is 90%-95% of the axial length of the rotor (7); the phase change structure (701) includes a plurality of phase change holes (702).

4. A centrifugal pneumatic fluid flash seawater desalination device according to claim 3, characterized in that, The phase change holes (702) are divided into several groups, and each group is arranged in a ring array. In each group of phase change holes (702), each phase change hole (702) is evenly arranged along the axis of rotation (6).

5. A centrifugal pneumatic fluid flash seawater desalination device according to claim 4, characterized in that, The phase change holes (702) are provided in 50-60 groups, with 10-20 phase change holes (702) in each group, and the diameter of the phase change holes (702) is 15mm-20mm.

6. A centrifugal pneumatic fluid flash seawater desalination device according to claim 3, characterized in that, The phase change hole (702) is inclined axially to the radial direction of the rotor (7) and inclined toward the rotation direction of the rotor (7) with an inclination angle of α, the range of which is 5°-45°.

7. A centrifugal pneumatic fluid flash seawater desalination device according to claim 1, characterized in that, The blades of the positive pressure impeller (8) and the negative pressure impeller (9) are arranged in opposite directions; The two ends of the outer shell (3) are respectively closed by end cap one (4) and end cap two (5). The inner cavities of end cap one (4) and end cap two (5) are both eccentric volute structures, and the eccentricity is in opposite directions. Bearing seats (10) are fixedly installed on the outer sides of the first end cover (4) and the second end cover (5). The two ends of the rotating shaft (6) pass through the first end cover (4) and the second end cover (5) respectively, and are rotatably installed on the bearing seat (10) through the bearing assembly (1001). A sealing assembly (1002) is installed between the bearing seat (10) and the rotating shaft (6).

8. A centrifugal pneumatic fluid flash seawater desalination device according to claim 1, characterized in that, The lower part of the positive pressure chamber (301) and negative pressure chamber (302) of the outer shell (3) are provided with slag discharge holes.

9. A centrifugal pneumatic fluid flash seawater desalination device according to claim 1, characterized in that, The rotary driver (1) has two drive shafts (101), and the desalination module (2) is provided in two sets. The rotating shafts (6) of the two sets of desalination modules (2) are respectively connected to the two drive shafts (101) through couplings (102).

10. A centrifugal pneumatic fluid flash evaporation method for seawater desalination, characterized in that, The centrifugal pneumatic fluid flash seawater desalination device as described in any one of claims 1-9 is used; During the seawater desalination process, seawater is pumped into the input port (401) of the desalination module (2); the rotary drive (1) drives the rotating shaft (6) to rotate, and drives the positive pressure impeller (8), rotor (7) and negative pressure impeller (9) to rotate; The positive pressure impeller (8) can send the seawater in the positive pressure chamber (301) into the phase change gap, the rotor (7) can heat the seawater in the phase change gap, and the negative pressure impeller (9) can throw the seawater in the negative pressure chamber (302) out of the outlet (501) and form a negative pressure environment in the negative pressure chamber (302). Seawater passes through a phase change gap, and the heated seawater can boil and evaporate in a negative pressure chamber (302). The steam-water mixture formed in the negative pressure chamber (302) is thrown out from the outlet (501) and fresh water is obtained after steam-water separation.

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