CN115009487B - Rotor blade S-shaped anti-cavitation profile structure, application and design method thereof - Google Patents
Rotor blade S-shaped anti-cavitation profile structure, application and design method thereof Download PDFInfo
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- CN115009487B CN115009487B CN202210823544.2A CN202210823544A CN115009487B CN 115009487 B CN115009487 B CN 115009487B CN 202210823544 A CN202210823544 A CN 202210823544A CN 115009487 B CN115009487 B CN 115009487B
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- 238000004364 calculation method Methods 0.000 claims description 12
- 238000005457 optimization Methods 0.000 claims description 8
- 238000005259 measurement Methods 0.000 claims description 5
- 230000007423 decrease Effects 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 claims description 3
- 229910000881 Cu alloy Inorganic materials 0.000 claims description 2
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- 230000003247 decreasing effect Effects 0.000 claims description 2
- 230000005855 radiation Effects 0.000 abstract description 5
- 230000002829 reductive effect Effects 0.000 abstract description 4
- 230000002441 reversible effect Effects 0.000 abstract description 4
- 238000002679 ablation Methods 0.000 abstract description 3
- 238000004088 simulation Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
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- 230000009286 beneficial effect Effects 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H1/00—Propulsive elements directly acting on water
- B63H1/02—Propulsive elements directly acting on water of rotary type
- B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
- B63H1/14—Propellers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING
- B63B71/00—Designing vessels; Predicting their performance
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H1/00—Propulsive elements directly acting on water
- B63H1/02—Propulsive elements directly acting on water of rotary type
- B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
- B63H1/14—Propellers
- B63H1/18—Propellers with means for diminishing cavitation, e.g. supercavitation
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H1/00—Propulsive elements directly acting on water
- B63H1/02—Propulsive elements directly acting on water of rotary type
- B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
- B63H1/14—Propellers
- B63H1/26—Blades
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T70/00—Maritime or waterways transport
- Y02T70/10—Measures concerning design or construction of watercraft hulls
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- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The application belongs to the technical field of rotor structure design methods of underwater vehicles, and particularly relates to an S-shaped anti-cavitation profile structure of a rotor blade, and an application and a design method thereof. The rotor blade of the present application adopts an S-shaped profile design, and the S-shaped profile is centrosymmetric about a 0.5-time chord length point, so that the rotor in the present embodiment has substantially the same hydrodynamic performance whether it is rotating in a forward direction or a reverse direction. Compared with a conventional symmetrical profile rotor, the S-shaped profile rotor has positive camber at the chord length section of 0.5 times from the leading edge, so that the pressure value of a low-pressure area close to the suction surface of the leading edge during forward rotation or reverse rotation is greatly improved, cavitation is restrained, the rotor blade is prevented from cavitation and ablation, the anti-cavitation performance of the rotor blade of the channel side thruster is improved, and radiation noise and structural vibration noise caused by cavitation of the rotor blade are reduced.
Description
Technical Field
The application belongs to the technical field of rotor structure design methods of underwater vehicles, and particularly relates to an S-shaped anti-cavitation profile structure of a rotor blade, and an application and a design method thereof.
Background
In the process of gradually reducing the ship inlet ship speed, the steering force and the ship turning moment generated by steering are gradually reduced, and the capability of controlling the heading is gradually deteriorated. To solve this problem, another method of generating a turning moment, i.e., a side thruster, has been developed. As shown in fig. 1, in the rotation process of a rotor of a conventional channel side thruster, the pressure value of a rotor blade surface is large, the pressure value of a rotor blade back is low, and a pressure difference exists between the rotor blade surface and the blade back, so that the thrust is continuously provided for the channel side thruster.
On the other hand, because the distance between the pressure surface and the suction surface is small, a large pressure gradient is formed between the rotor blade surface and the blade back at the corresponding position, so that fluid can turn over from the pressure surface to the blade tip end surface and then turn over from the blade tip end surface to the suction surface, and cavitation is easy to generate at the rotor blade back of the channel side thruster due to the flow characteristic, and cavitation noise is generated. Meanwhile, the blade backs and the blade faces of the rotor blade sections of the conventional channel side thrusters are axisymmetric about the chord line, the camber is 0, and the pressure of the section shape near the front edge of the blade backs is very low, so that the cavitation of the blade backs is aggravated, the pulsating pressure of the rotor blade and the inner wall of the nearby channel is obviously increased, the rotor blade is broken, and serious engineering accidents are caused. The cavitation noise is generated by cavitation damage caused by cavitation erosion of the rotor blade due to huge pressure impact generated during cavitation collapse, so that the radiation noise of the channel side pusher is increased sharply. The influence of the factors finally causes that the conventional ship side thruster is easy to generate cavitation near the back of the rotor blade in the working process, enhances the fatigue damage of the rotor blade, reduces the service life of the rotor, obviously increases the noise, and greatly limits the efficiency of the ship side thruster and the stealth performance of a ship or an underwater vehicle.
Disclosure of Invention
The present application is directed to solving the above-mentioned problems, and an object of the present application is to provide a rotor blade cross-sectional structure having anti-cavitation capability, an application thereof, and a design method thereof, which optimally design a cross-sectional shape of a rotor blade, and design a rotor blade having an S-shaped cross-sectional shape. Compared with the rotor section of the traditional channel side thruster, the rotor section of the novel channel side thruster can effectively reduce the pressure drop of the rotor blade back at the position near the leading edge, prevent cavitation of the blade, avoid cavitation and ablation, reduce the excitation force of the blade, improve the propulsion efficiency of the channel side thruster and reduce the radiation noise of the side thruster.
In order to achieve the above purpose, the present application adopts the following technical scheme.
An S-shaped anti-cavitation profile structure for a rotor blade, the rotor blade having an S-shaped profile structure that is centrosymmetric with respect to a 0.5-chord point of the rotor blade.
The S-shaped cavitation-resistant section structure of the rotor blade according to claim 1, wherein the camber is positive at the position of the front edge to 0.5 times of the chord length, and the camber is gradually reduced to 0 at the position of 0.5 times of the chord length after the camber is increased to the maximum along the chord line direction; the S-shaped section structure is arranged at the position of 0.5 times chord length to the rear edge, the camber is negative, the absolute value of the camber is firstly increased along the chord line direction and gradually decreased after reaching the maximum value, and the camber is contracted to 0 at the rear edge.
The anti-cavitation rotor is characterized in that the main body of the anti-cavitation rotor is made of copper alloy materials, a plurality of blades are connected with the periphery of the rotor hub, the blades have an S-shaped cross-section structure, and the blades are radially arranged with the central shaft of the rotor hub as the center.
The shaft-driven channel side pusher with the S-shaped anti-cavitation section structure comprises a rotor, a prime motor and a shaft system;
The blades of the rotor have an S-shaped section structure;
the prime mover is arranged at the central shaft in the channel or outside the channel, and when the prime mover is positioned at the central shaft in the channel, the prime mover drives a shafting, and the shafting drives the anti-cavitation rotor to rotate;
When the prime mover is positioned outside the channel, the prime mover drives a shafting through the Z-shaped transmission device, and the shafting drives the anti-cavitation rotor to rotate.
The rim driving type channel side pusher with the S-shaped anti-cavitation section structure comprises a rim motor, a magnetic pole ring rotor, a rotor and a bearing
The blades of the rotor have an S-shaped section structure;
The rim motor is arranged in the ship body, a motor stator of the rim motor is connected with the magnetic pole ring rotor through a bearing, and the magnetic pole ring rotor is fixedly connected with the anti-cavitation rotor; when the rim motor works, the magnetic pole ring rotor drives the anti-cavitation rotor to rotate relative to the motor stator.
The design method for the S-shaped anti-cavitation profile structure of the rotor blade comprises the following steps:
(1) Analyzing and selecting geometric parameters of the channel side pusher according to design conditions and design requirements of the underwater vehicle, and determining preliminary geometric shapes of the channel, the stator and the rotor;
(2) Optimizing the shape of the channel in the step (1) in view of three aspects of channel inner wall pressure, channel inlet pressure and hull surface pressure, and taking the lowest pressure of the channel inner wall, channel inlet and hull surface as a design target; calculating the flow field of the channel by a numerical calculation method, and if the solved channel hydrodynamic performance parameters meet the design requirements, determining the geometric shape of the final channel and entering the next step; otherwise, carrying out re-optimization design on the geometric shape of the channel until the design requirement is met;
(3) The stator shape in the step (1) is optimally designed in terms of hydrodynamic performance and strength of the stator, and the strength and the lowest pressure of the stator are improved as design targets; calculating a flow field of the stator by a numerical calculation method, and if the solved hydrodynamic performance parameter and strength of the stator meet the design requirement, determining the geometric shape of the final stator and entering the next step; otherwise, carrying out re-optimization design on the geometric shape of the stator until the set requirement is met;
(4) The rotor shape of the channel side pusher in the step (1) is optimally designed, and the optimal design steps are as follows:
4a) The method comprises the steps of optimally designing cross section dimension parameters of each radial position of a rotor of a channel side thruster by taking an original symmetrical wing-shaped cross section as a basic cross section, and taking thrust, propulsion efficiency and minimum pressure of the rotor as design targets, wherein the dimension parameters comprise chord length distribution, thickness distribution and pitch distribution;
4b) Designing the shape of each radial position profile at the leading edge to 0.5 chord length based on each radial position profile designed in step (a); firstly, primarily designing the maximum camber of each radial position section of a rotor to improve the pressure drop of the blade back near the front edge as a design target, then primarily designing the camber of the section in the chord direction distribution form from the front edge to a section with 0.5 times of chord length to improve the pressure value of a low-pressure area of a suction surface as a design target, thus obtaining the shape of each radial position section from the front edge to a section with 0.5 times of chord length, and carrying out center symmetry on the section shape of the section with 0.5 times of chord length point as a symmetry center to obtain the shape of the whole section at each radial position;
4c) Three-dimensional modeling is carried out on the S-shaped section rotor based on the parameters of the sections of the radial positions of the rotor in the step (b); taking rotor thrust, received power, propulsion efficiency and minimum pressure as measurement references, solving a three-dimensional flow field of the S-shaped section rotor by adopting a CFD method, and determining the geometric shape of the rotor section of the final channel side thruster if the solved rotor thrust, received power, propulsion efficiency and minimum pressure meet design requirements; otherwise, continuing to optimally design the shape of the cross section of each radial position of the rotor until the design requirement is met.
The beneficial effects are that:
the rotor blade of the present invention adopts an S-shaped profile design, and the S-shaped profile is centrosymmetric about a 0.5-time chord length point, so that the rotor in the present embodiment has substantially the same hydrodynamic performance whether it is rotating in a forward direction or a reverse direction. Compared with a conventional symmetrical profile rotor, the S-shaped profile rotor has positive camber at the chord length section of 0.5 times from the leading edge, so that the pressure value of a low-pressure area close to the suction surface of the leading edge during forward rotation or reverse rotation is greatly improved, cavitation is restrained, the rotor blade is prevented from cavitation and ablation, the anti-cavitation performance of the rotor blade of the channel side thruster is improved, and radiation noise and structural vibration noise caused by cavitation of the rotor blade are reduced.
Drawings
FIG. 1 is a schematic cross-sectional view of a conventional channel side pusher rotor blade;
FIG. 2 is a schematic illustration of a cross-sectional structure of a rotor blade with anti-cavitation capability;
FIG. 3 is a cloud of channel side pusher rotor blade back pressure distribution for the original structure;
FIG. 4 is a cloud of back pressure distribution of a channel side pusher rotor blade based on the construction of the present application;
FIG. 5 is a cloud of original channel side pusher rotor blade face pressure distribution;
FIG. 6 is a cloud of channel side pusher rotor blade face pressure distribution based on the construction of the present application;
FIG. 7 is a cloud of low pressure zone position pressure distribution for the original structure;
fig. 8 is a cloud of low pressure zone location pressure distribution based on the inventive structure.
Detailed Description
The present application will be described in detail with reference to specific examples.
Based on the current situation and the problems, the invention provides a rotor blade profile structure with anti-cavitation capability, and provides an application and a design method thereof, theoretical analysis and selection are carried out on geometric parameters of a rotor blade through design conditions and design requirements of an underwater vehicle, and an optimized and improved scheme of the rotor blade is determined, so that the aims of inhibiting cavitation of a rotor blade of a conventional channel side thruster, improving the cavitation starting rotating speed of the side thruster, preventing cavitation and cavitation erosion of the rotor blade, reducing radiation noise of the channel side thruster and improving the anti-cavitation performance of the rotor of the channel side thruster are fulfilled.
The rotor blade section structure with the cavitation resistance is characterized in that the section of the rotor blade adopts an S-shaped section structure, and the S-shaped section structure is centrally symmetrical about a 0.5-time chord length point of the rotor blade.
Specifically, as shown in fig. 2, in the S-shaped cross-section structure, the camber is positive at the position from the leading edge to 0.5 times of the chord length, and increases along the chord line direction, gradually decreases after reaching the maximum value, and decreases to 0 at the position 0.5 times of the chord length; the camber is negative from the 0.5 chord length position to the trailing edge, the absolute value of the camber increases along the chord line direction, and gradually decreases after the camber reaches the maximum value, and the camber contracts to 0 at the trailing edge. The S-shaped section is centrally symmetrical about a 0.5 times chord length point. Compared with a conventional symmetrical section rotor, the S-shaped section rotor has camber in sections at different radial positions, when the S-shaped section rotor rotates positively, the alpha surface is a leaf surface, the beta surface is a leaf back, and the lowest pressure value of a low-pressure area of the beta surface is greatly improved; because the S-shaped section is centrally symmetrical about the 0.5-time chord length point, the hydrodynamic performance of the side thruster rotor is basically the same when the side thruster rotor rotates positively and reversely, and when the S-shaped section rotor rotates reversely, the beta surface is a leaf surface and the alpha surface is a leaf back, and the lowest pressure value of a low pressure area of the alpha surface is also greatly improved.
For ease of description of the features of the foregoing rotor blade cross-sectional structure, the following embodiments are described in connection with specific design optimization procedures and simulation test results. The application relates to a design method of a rotor blade section structure with anti-cavitation capability, which specifically comprises the following steps:
(1) Analyzing and selecting geometric parameters of the channel side pusher according to design conditions and design requirements of the underwater vehicle, and determining preliminary geometric shapes of the channel, the stator and the rotor;
(2) Optimizing the shape of the channel in the step (1) in view of three aspects of channel inner wall pressure, channel inlet pressure and hull surface pressure, and taking the lowest pressure of the channel inner wall, channel inlet and hull surface as a design target; calculating the flow field of the channel by a numerical calculation method, and if the solved channel hydrodynamic performance parameters meet the design requirements, determining the geometric shape of the final channel and entering the next step; otherwise, carrying out re-optimization design on the geometric shape of the channel until the design requirement is met;
(3) The stator shape in the step (1) is optimally designed in terms of hydrodynamic performance and strength of the stator, and the strength and the lowest pressure of the stator are improved as design targets; calculating a flow field of the stator by a numerical calculation method, and if the solved hydrodynamic performance parameter and strength of the stator meet the design requirement, determining the geometric shape of the final stator and entering the next step; otherwise, carrying out re-optimization design on the geometric shape of the stator until the set requirement is met;
(4) The rotor shape of the channel side pusher in the step (1) is optimally designed, and the optimal design steps are as follows:
4a) The method comprises the steps of optimally designing cross section dimension parameters of each radial position of a rotor of a channel side thruster by taking an original symmetrical wing-shaped cross section as a basic cross section, and taking thrust, propulsion efficiency and minimum pressure of the rotor as design targets, wherein the dimension parameters comprise chord length distribution, thickness distribution and pitch distribution;
4b) Designing the shape of each radial position profile at the leading edge to 0.5 chord length based on each radial position profile designed in step (a); firstly, primarily designing the maximum camber of each radial position section of a rotor to improve the pressure drop of the blade back near the front edge as a design target, then primarily designing the camber of the section in the chord direction distribution form from the front edge to a section with 0.5 times of chord length to improve the pressure value of a low-pressure area of a suction surface as a design target, thus obtaining the shape of each radial position section from the front edge to a section with 0.5 times of chord length, and carrying out center symmetry on the section shape of the section with 0.5 times of chord length point as a symmetry center to obtain the shape of the whole section at each radial position;
4c) Three-dimensional modeling is carried out on the S-shaped section rotor based on the parameters of the sections of the radial positions of the rotor in the step (b); taking rotor thrust, received power, propulsion efficiency and minimum pressure as measurement references, solving a three-dimensional flow field of the S-shaped section rotor by adopting a CFD method, and determining the geometric shape of the rotor section of the final channel side thruster if the solved rotor thrust, received power, propulsion efficiency and minimum pressure meet design requirements; otherwise, continuing to optimally design the shape of the cross section of each radial position of the rotor until the design requirement is met.
The rotor blade profile is optimally designed based on the channel side thruster basic structure of a certain type of equipment, wherein # 1 is applied to a rotor blade with a conventional symmetrical profile structure, and # 2 is applied to a rotor blade with an S-shaped profile structure used in the application. Taking total thrust of the side thruster, received power of the rotor and minimum absolute pressure (1 meter water depth) of the rotor as measurement standards, carrying out numerical simulation on the model through CFD numerical calculation software, carrying out unsteady hydrodynamic calculation on the channel thruster by adopting an unstructured grid, and respectively calculating different schemes of No. 1 and No. 2 rotors, wherein the calculation results are shown in Table 1.
Table 1 channel propulsion hydrodynamic calculations for different rotor schemes
The distribution cloud patterns of the rotor blade back pressure, the blade surface pressure and the low-pressure area position pressure of the two schemes are obtained through simulation and are shown in figures 3 to 8; as can be seen from the figure, the rotors with two different section shapes can meet the thrust and power requirements of ships, and meanwhile, the section shape of the rotor adopting the 2# scheme designed in the application enables the pressure distribution characteristics of a low-pressure area of the rotor to be better than that of the traditional 1# scheme, wherein the lowest absolute pressure (1 meter water depth) of the rotor of the side thruster is 29496pa, the pressure value is far higher than the critical cavitation pressure of water (cavitation phenomenon can be generated when the pressure is lower than the critical cavitation pressure), cavitation can be effectively avoided, and the S-shaped section rotor blade is better than the conventional symmetrical section rotor in the aspect of cavitation resistance.
On the basis of the above, the shape of the S-shaped section rotor blade is optimally designed, and three rotor blades with different section shapes are obtained according to different design indexes and requirements. The thrust of the side thruster and the received power of the rotor are used as measurement standards, the model is subjected to numerical simulation through CFD numerical calculation software, the channel thruster is subjected to steady hydrodynamic calculation by adopting an unstructured grid, different schemes of rotors No. 3, no. 4 and No. 5 are calculated respectively, and the calculation results are shown in Table 2.
Table 2 channel propulsion hydrodynamic calculations for different rotor schemes
Through simulation, the rotor blades with different section shapes obtained based on the scheme, the design scheme and the optimization method can be determined to meet the thrust and power requirements of ships. The total thrust of the side pusher is 25879.54N when the section shape I of the rotor is adopted, the received power of the rotor is 106.84kW, and the performance parameters of each structure are far superior to those of the existing equipment, so that the scheme and the design method are integrated to obtain various design results meeting different design requirements and targets, and the design results far exceeding the existing design scheme in different design indexes are obtained, and the design method has wide application prospects.
In particular, the present invention can be applied to both shaft-driven channel side pushers and rim-driven channel side pushers.
The main structure of the axial-driven channel side thruster comprises rotor blades, a prime motor and a shafting, wherein the prime motor can be arranged outside a ship body or inside the ship body. When the prime mover is positioned at a central shaft (outside the ship body) in the channel, the prime mover drives the shaft to rotate, and the rotor blades are connected with the shaft and then driven by the shaft to rotate; when the prime mover is positioned in the ship body, the prime mover drives the shaft to rotate through the Z-shaped transmission device, and the shaft drives the rotor to rotate.
When the wheel rim driving type channel side thruster is applied, the main structure is composed of a wheel rim motor, a magnetic pole ring rotor, rotor blades, a bearing and other parts, the wheel rim motor is arranged inside a ship body, a motor stator of the wheel rim motor is connected with the magnetic pole ring rotor through the bearing, the magnetic pole ring rotor is fixedly connected with the rotor blades, and when the wheel rim motor works, the magnetic pole ring rotor drives the rotor blades to rotate relative to the motor stator. When the channel side pusher is operated in fluid, the fluid enters the channel from one side and exits the channel from the other side due to the rotor suction effect, creating a side thrust.
Finally, it should be noted that the above embodiments are only for illustrating the technical solution of the present application, and not for limiting the scope of the present application, and although the present application has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions can be made to the technical solution of the present application without departing from the spirit and scope of the technical solution of the present application.
Claims (5)
1. An S-shaped anti-cavitation profile structure of a rotor blade, characterized in that the rotor blade has an S-shaped profile structure which is centrosymmetric with respect to a 0.5-time chord length point of the rotor blade profile, the S-shaped anti-cavitation profile structure of the rotor blade being obtained based on the steps of:
(1) Analyzing and selecting geometric parameters of the channel side pusher according to design conditions and design requirements of the underwater vehicle, and determining preliminary geometric shapes of the channel, the stator and the rotor;
(2) Optimizing the shape of the channel in the step (1) in view of three aspects of channel inner wall pressure, channel inlet pressure and hull surface pressure, and taking the lowest pressure of the channel inner wall, channel inlet and hull surface as a design target; calculating the flow field of the channel by a numerical calculation method, and if the solved channel hydrodynamic performance parameters meet the design requirements, determining the geometric shape of the final channel and entering the next step; otherwise, carrying out re-optimization design on the geometric shape of the channel until the design requirement is met;
(3) The stator shape in the step (1) is optimally designed in terms of hydrodynamic performance and strength of the stator, and the strength and the lowest pressure of the stator are improved as design targets; calculating a flow field of the stator by a numerical calculation method, and if the solved hydrodynamic performance parameter and strength of the stator meet the design requirement, determining the geometric shape of the final stator and entering the next step; otherwise, carrying out re-optimization design on the geometric shape of the stator until the design requirement is met;
(4) The rotor shape of the channel side pusher in the step (1) is optimally designed, and the optimal design steps are as follows:
4a) The method comprises the steps of optimally designing cross section dimension parameters of each radial position of a rotor of a channel side thruster by taking an original symmetrical wing-shaped cross section as a basic cross section, and taking thrust, propulsion efficiency and minimum pressure of the rotor as design targets, wherein the dimension parameters comprise chord length distribution, thickness distribution and pitch distribution;
4b) Designing the shape of each radial position profile at the leading edge to 0.5 chord length section based on each radial position profile designed in step 4 a); firstly, primarily designing the maximum camber of each radial position section of a rotor to improve the pressure drop of the blade back near the front edge as a design target, then primarily designing the camber of the section in the chord direction distribution form from the front edge to a section with 0.5 times of chord length to improve the pressure value of a low-pressure area of a suction surface as a design target, thus obtaining the shape of each radial position section from the front edge to a section with 0.5 times of chord length, and carrying out center symmetry on the section shape of the section with 0.5 times of chord length point as a symmetry center to obtain the shape of the whole section at each radial position;
4c) Three-dimensional modeling is carried out on the S-shaped section rotor based on the parameters of the sections of the radial positions of the rotor in the step 4 b); taking rotor thrust, received power, propulsion efficiency and minimum pressure as measurement references, solving a three-dimensional flow field of the S-shaped section rotor by adopting a CFD method, and determining the geometric shape of the rotor section of the final channel side thruster if the solved rotor thrust, received power, propulsion efficiency and minimum pressure meet design requirements; otherwise, continuing to optimally design the shape of the cross section of each radial position of the rotor until the design requirement is met.
2. The S-shaped cavitation-resistant cross-sectional structure of a rotor blade according to claim 1, wherein the camber is positive at the position of 0.5 times chord length from the leading edge, and increases gradually after reaching the maximum value along the chord line direction, and decreases to 0 at the position of 0.5 times chord length; the S-shaped section structure is arranged at the position of 0.5 times chord length to the rear edge, the camber is negative, the absolute value of the camber is firstly increased along the chord line direction and gradually decreased after reaching the maximum value, and the camber is contracted to 0 at the rear edge.
3. An anti-cavitation rotor having an S-shaped anti-cavitation sectional structure as claimed in claim 1 or 2, wherein the anti-cavitation rotor body is made of a copper alloy material, a plurality of blades are provided on the rotor and connected to the outer circumference of the rotor hub, the blades have an S-shaped sectional structure, and the blades are radially arranged centering on the central axis of the rotor hub.
4. A shaft-driven channel side pusher, which is characterized by comprising an anti-cavitation rotor, a prime mover and a shaft system with the S-shaped anti-cavitation profile structure as claimed in claim 3;
The blades of the rotor have an S-shaped section structure;
the prime mover is arranged at the central shaft in the channel or outside the channel, and when the prime mover is positioned at the central shaft in the channel, the prime mover drives a shafting, and the shafting drives the anti-cavitation rotor to rotate;
When the prime mover is positioned outside the channel, the prime mover drives a shafting through the Z-shaped transmission device, and the shafting drives the anti-cavitation rotor to rotate.
5. A rim-driven channel side pusher, comprising a rim motor, a magnetic pole ring rotor, an anti-cavitation rotor with the S-shaped anti-cavitation section structure of claim 3, and a bearing;
The blades of the rotor have an S-shaped section structure;
The rim motor is arranged in the ship body, a motor stator of the rim motor is connected with the magnetic pole ring rotor through a bearing, and the magnetic pole ring rotor is fixedly connected with the anti-cavitation rotor; when the rim motor works, the magnetic pole ring rotor drives the anti-cavitation rotor to rotate relative to the motor stator.
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| DD228506A1 (en) * | 1984-11-09 | 1985-10-16 | Rostock Dieselmotoren | PROPELLER FLOOR FOR CROSS-RAY INSTALLATION SYSTEMS WITH ADJUSTING PROPELLERS |
| US5290147A (en) * | 1991-12-02 | 1994-03-01 | Brunswick Corporation | Variable pitch marine propeller with shift biasing and synchronizing mechanism |
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| KR20000032070A (en) * | 1998-11-12 | 2000-06-05 | 이해규 | Propeller for ship, underwater blade for underwater ship and cross section profile of blade in air propeller |
| JP2001234843A (en) * | 2000-02-23 | 2001-08-31 | Hitachi Ltd | Water turbine moving blade |
| US7517263B1 (en) * | 2007-09-05 | 2009-04-14 | The United States Of America As Represented By The Secretary Of The Navy | Advanced blade sections for high speed propellers |
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| CN108733958A (en) * | 2018-06-05 | 2018-11-02 | 中国人民解放军海军工程大学 | A kind of 7 vane propeller hydraulic model of low noise and design method of delay cavitation inception |
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| CN115009487A (en) | 2022-09-06 |
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