CN110030149B - Elastic movement steering system with counterweight device - Google Patents
Elastic movement steering system with counterweight device Download PDFInfo
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- CN110030149B CN110030149B CN201811170555.5A CN201811170555A CN110030149B CN 110030149 B CN110030149 B CN 110030149B CN 201811170555 A CN201811170555 A CN 201811170555A CN 110030149 B CN110030149 B CN 110030149B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor
- F03D1/06—Rotors
- F03D1/065—Rotors characterised by their construction elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D7/00—Controlling wind motors
- F03D7/02—Controlling wind motors the wind motors having rotation axis substantially parallel to the air flow entering the rotor
- F03D7/022—Adjusting aerodynamic properties of the blades
- F03D7/0224—Adjusting blade pitch
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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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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Abstract
The invention discloses an elastic movement steering system with a counterweight device, which comprises a main shaft and a plurality of blades distributed around the axis of the main shaft, and is characterized by further comprising: the blade cavity shell is arranged on the main shaft and used for installing the blade; an elastic movement steering mechanism for guiding the deflection of the blade when the blade moves relative to the blade cavity shell and for applying an elastic force to the blade; and the blade counterweight assembly is used for counteracting the component force influence of the gravity of the blade in the direction of the center line of the blade during the rotation of the blade. The system can automatically obtain the optimal combination of pitch angle and rotation speed in different types of turbomachinery, and the pure mechanical structure is not affected by power failure, inaccuracy of an anemometer or errors of users, so that the reliability, the rigor and the control efficiency of the system are enhanced, and the extremely complex and expensive defects of the existing active control system are overcome. In addition, the set of resiliently movable steering systems also overcomes the periodic effects of gravity as the blades rotate.
Description
Technical Field
The invention relates to the blade technology, in particular to an elastic movement steering system with a counterweight device.
Background
Currently, devices for achieving power input or power output using rotating blades are widely used, for example: the device is widely used in wind driven generators, water turbines, screw propellers, turbines, rotary wheel machines and other equipment. In which it is often necessary to adjust the pitch angle of the blades for different flow rates, as the blades are affected by the speed of the fluid (gas or liquid) during rotation. In the prior art, the pitch angle of the blades is typically adjusted by electronically controlling, and the wind speed is detected by using a computer system to adjust the pitch angle of the blades. However, the above-mentioned rely on several subsystems, such as computers, software, anemometers, thermometers, etc., which are susceptible to errors and faults, resulting in an overall system that is very complex, less reliable and more costly to manufacture and maintain. How to design an elastic mobile steering system with high reliability and low cost is the technical problem to be solved by the invention.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: the elastic mobile steering system solves the defects of low reliability and high cost of an automatic pitch system in the prior art, improves the reliability of the automatic pitch system, and reduces the manufacturing cost and the maintenance cost of the automatic pitch system.
The technical scheme provided by the invention is that the elastic movement steering system comprises a main shaft, a plurality of blades distributed around the axis of the main shaft, and further comprises:
a blade housing disposed on the spindle for mounting the blade, the blade being movable on the blade housing along a longitudinal axis of the blade when rotation of the blade causes a change in centripetal force of the blade;
an elastic movement steering mechanism for guiding the blade to rotate around its own center line to change a pitch angle when the blade moves longitudinally with respect to the blade cavity shell, and for applying an elastic force to the blade;
and the blade counterweight assembly is used for counteracting the component force influence of the gravity of the blade in the direction of the center line of the blade during the rotation of the blade.
Further, the blade counterweight assembly comprises a ring-shaped guide rail and a gravity roller, wherein the center of the ring-shaped guide rail is positioned above the axis of the main shaft, each blade is provided with the gravity roller, the elastic member is connected between the gravity roller and the blade, and the gravity roller is arranged in the ring-shaped guide rail in a rolling or sliding manner.
Further, the movement steering mechanism comprises a chute and a guide member arranged in the chute.
Further, the sliding chute is arranged in the blade cavity shell, and the guide piece is arranged on the blade; alternatively, the chute is provided on the vane and the guide is provided on the vane chamber housing.
Further, the guide piece is a guide post or a sliding block or a shaft collar which is arranged on the sliding groove in a sliding manner.
Further, the guide member is a guide roller capable of rolling in the chute.
Further, two or more than two blade cavity shells are distributed in the circumferential direction of the main shaft, each blade cavity shell is provided with a mounting hole, and the root of each blade is mounted in each mounting hole.
Further, a fixing ring is further arranged on the blade cavity shell, and the fixing ring is sleeved on the blade and is fixed on the blade cavity shell; or the blade is also provided with a fixing ring, and the fixing ring is sleeved on the blade cavity shell and is fixed on the blade.
Further, the rotating shaft is connected with a generator, a motor or an engine.
Further, the elastic member is a member that generates a restoring force against tensile, compressive, rotational, torsional deformation when subjected to such deformation, and includes a spring.
Further, the outer diameter of the blade cavity shell is smaller than the inner diameter of the blade root of the blade, and the blade root can slide on the outer surface of the blade cavity shell; alternatively, the inner diameter of the blade cavity shell is larger than the outer diameter of the blade root of the blade, the blade root being slidable in the blade cavity shell.
Further, the blade cavity shells are wholly or partly accommodated inside the central hub, but may also be wholly outside the central hub.
Further, a linear bearing or ball bearing array is used on the blade root or blade cavity shell.
Compared with the prior art, the invention has the advantages and positive effects that: according to the elastic movement steering system provided by the invention, the elastic force is applied to the blades by the elastic member, the centrifugal force generated by the blades is changed in the process of changing the rotating speed of the blades, so that the elastic force applied by the elastic member to the blades is different, the blades move along the direction vertical to the axis of the main shaft relative to the cavity shells of the blades under the condition of different rotating speeds, at the moment, the blades are guided by the movable steering mechanism, so that the blades rotate while moving, the pitch angle is automatically adjusted, the optimal pitch angle is automatically configured for each blade rotating speed, the automatic adjustment of the pitch angle of the blades is realized by the elastic member and the movable steering mechanism in a mechanical mode, a complex electronic control system is not required to be configured, the operation reliability is better, and the whole system has a simple structure, and low manufacturing cost and maintenance cost.
In summary, compared with the prior art, the invention has the following advantages:
1) Relatively simple.
2) Is not affected by user errors.
3) Is not affected by the loss of power.
4) Is not affected by computer failure or malfunction.
5) Is not affected by electronic subsystem failures or errors (such as anemometers).
6) The durability and the service life are extremely high.
7) Low maintenance.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions of the prior art, the following description will briefly explain the drawings used in the embodiments or the description of the prior art, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of an embodiment of an elastically mobile steering system in accordance with the present invention;
FIG. 2 is a partial cross-sectional view of an embodiment of the resiliently mobile steering system of the present invention;
FIG. 3 is a partial exploded view of an embodiment of the resiliently mobile steering system of the present invention;
FIG. 4 is an assembly view of a toroidal guide, a gravity roller and a spring of an embodiment of the resiliently movable steering system of the present invention;
FIG. 5 is an assembly view of the annular rail and spindle of an embodiment of the resiliently movable steering system of the present invention;
FIG. 6 is an assembled view of a toroidal guide and gravity roller in accordance with an embodiment of the resiliently movable steering system of the present invention;
FIG. 7 is a second view of an assembly of a toroidal guide and a gravity roller of an embodiment of the resiliently movable steering system of the present invention;
FIG. 8 is a third view of an assembly of a toroidal guide and a gravity roller of an embodiment of the resiliently movable steering system of the present invention;
FIG. 9 is a schematic view of a toroidal guide rail of an embodiment of a resiliently movable steering system according to the present invention;
FIG. 10 is a schematic diagram of a second embodiment of a toroidal guide rail of an elastically mobile steering system in accordance with the present invention;
FIG. 11 is a schematic view of a third embodiment of a toroidal guide rail of an elastically mobile steering system in accordance with the present invention;
FIG. 12 is a schematic view of a toroidal guide rail of an embodiment of a resiliently movable steering system in accordance with the present invention;
FIG. 13 is a schematic view of a toroidal guide rail of an embodiment of an elastically mobile steering system in accordance with the present invention;
FIG. 14 is a schematic view of a gravity roller structure according to an embodiment of the elastic displacement steering system of the present invention;
FIG. 15 is a schematic diagram of a gravity roller according to an embodiment of the present invention;
FIG. 16 is a schematic diagram III of a gravity roller configuration of an embodiment of the resilient mobile diversion system of the present invention;
FIG. 17 is an assembled view of a blade hub and a blade cavity shell;
FIG. 18 is a graph of a coordinate analysis of a blade;
FIG. 19 is a force analysis diagram of a blade;
FIG. 20 is a coordinate analysis of a blade cavity shell.
Reference numerals illustrate: 1-blade, 2-blade cavity shell, 3-elastic member, 4-guide, 5-chute, 6-fixed ring, 7-blade root, 8-hub, 9-gravity roller, 10-annular guide rail, 11-motor/generator, 12-spindle, 13-casing, 14-rotating cover.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
As shown in fig. 18, the centrifugal force acting on all the rotating blades is proportional to the square of the hub rotational speed. The higher the rotational speed, the greater the centrifugal force pulling the blades off the hub. This centrifugal force is countered by a linear spring that lengthens as the rotational speed increases. When the spring is stretched, the blade will rotate in its axial direction under the action of the rollers and the guide rail. The guide rail may be designed to increase the blade pitch angle strictly (e.g. for a propeller) as the rotational speed increases, or to increase the blade pitch angle in a safe rotational speed range (e.g. for a turbine), and then decrease the blade pitch angle and/or to zero when the rotational speed increases too high.
A simple model of an in-plane vertical hub constant speed rotation system can be derived for typical wind turbines, various axial fans, propellers in horizontal straight line flight, etc. The model can be used to analyze its dynamics and its behavior in order to make a more suitable design for various applications.
One useful method is to define a ground-fixed coordinate system and a hub-fixed coordinate system, both having the same origin. XYZ represents the coordinate system fixed to the ground, and XYZ represents the coordinate system fixed to the hub.
The centers of both coordinate systems are located at the intersection of the blade cavity shell centerlines. The X axis is vertical, the Y axis is out of the page, and the Z axis is horizontal. The Y and Y axes are always co-linear, but when the hub rotates, the x and z axes change their direction, denoted as beta, and the z axis is always directed towards the centre line of one blade cavity shell.
As shown in fig. 19, a free body diagram.
It is necessary to take into account the forces and moments exerted on the blades to simulate and understand their movement, including their response to disturbances. These forces come from aerodynamic forces, gravity forces, interaction forces of rollers and rails, centrifugal forces, springs, and interaction forces of the blade cavity shells. The free body force diagram helps to understand these forces and moments.
There are four key points, A, C, R and G. A is the aerodynamic center of the blade, which is the point of action of aerodynamic force and moment, C is the center of mass of the blade, which is the point of application of centrifugal force and gravity. R is the point of action of the reaction force/moment and G is the center of the circular cross section of the blade roll plane. It is assumed here that the aerodynamic forces in the z-direction are negligible, as are the aerodynamic moments acting in the x-axis and y-axis directions.
In addition, F represents a force, and M represents a moment. The subscript a denotes "aerodynamic", c denotes "centrifugal", g denotes "grooved", r denotes "reaction", s denotes "spring", x denotes "in x-direction", y denotes "in y-direction", and z denotes "in z-direction", in relation to the force or moment acting on the rail or groove.
As the blades rotate, the weight of the blades will act in different directions in the hub fixed coordinate system. Unfortunately, gravity is primarily applied in the xz plane and affects the force in the z direction, creating a periodically varying blade tension, thereby affecting the pitch angle of the blade. As the pitch angle of each blade changes periodically, all forces and moments will also change periodically with the rotational frequency of the blade. The center rail and center roller design is designed to correct for this periodic action, pushing upward when the blade is at the top of the periodic rotation and pulling upward when the blade is at the bottom of the periodic rotation. As a result of this correction, the z-coordinate position of the blade will not depend on its angular position, β, but only on the rotational speed of the hub. Mathematically we can change the free length, z, of the spring s0 The influence of the central track and the rollers is moldedIs intended as a function of angular position, beta. An important consideration is the added cost and complexity of the center roll and rail assembly that can be avoided. The weight of the blade is constant and the centrifugal force is proportional to the square of the hub speed. The centrifugal force is dominant with respect to the weight when the rotational speed is large. Furthermore, by designing the material with a higher density near the blade tip, the effect of centrifugal force with respect to gravity can be further increased. To avoid resonance, the system should be designed such that its natural frequency is outside the rotational speed domain. Damping systems may also be used and adjusted. We can consider a simple point mass rotating in a vertical plane and connected to its centre of rotation with a rope. When the point mass is in the lowest position, the centrifugal force and gravity are acting in the same direction, in which case the tension on the rope is:l is the length of the rope, m is the mass, g is the gravitational acceleration, the upper point represents the time derivative,is the rotational angular velocity of the blade around the hub. The propeller radius of a small unmanned aerial vehicle is about 0.1m, and the corresponding rope length is about 0.035m. The rotating speed of the propeller can reach 78.5-130.9rad/s when the small unmanned aerial vehicle flies; these frequencies should be as high as possible to avoid the natural frequencies of the system. When the drone is simplified to point mass and rope, gravity is 1.6% to 4.5% of centrifugal force over the entire rotational speed range of the hub. In this case, the pitch angle fluctuation is slight, and it is possible to omit the center roller and center rail assembly. All systems that rotate in a horizontal plane, or that operate without gravity, can omit the center rail and roller assembly and work well. As another example, consider a typical large wind turbine rotating at a speed of 1.05rad/s in a vertical plane, with blades 40 meters in length and 5500 kg in mass. In this case, the gravity is 67% of the centrifugal force, and thus the center rail and the roller assembly cannot be omitted.
The R point is plotted at the outer edge of the blade shell and at the center of the circular cross-section. The position of R is somewhat optional, since for any assumed point of application an exact value of a reaction force-moment system can be determined. The reaction moment and force are small enough to be negligible in the z direction (good lubrication, no friction). The spring force is also a result of the geometric analysis of point R.
The last key point is G, which is the center of the circular cross section in the plane of the blade roll. The force exerted on the blade roller can be reduced to one force and the corresponding moment exerted on point G. The blade rail depth is assumed to be sufficient to prevent the end of the blade roller from touching the bottom of the blade rail so that no force is applied to the blade roller in the direction of the sub-normal of the blade rail. Further, the friction is neglected so that no force is exerted on the blade roller in the tangential direction of the guide rail. Therefore, the force which the guide rail can exert can be simplified to be only force along the normal direction of the guide railThe subscript n represents "normal", the upper arrow represents a vector, and a represents a unit vector. Assuming a completely rigid blade, the equation of motion can be derived.
Equation of motion
(1)F ax +F rx +F gx +W x ＝0
(2)F ay +F ry +F gy ＝0
(4)-F ay ·(z A -z R )+F gy ·(z R -z G )+M rx ＝0
(5)F ax ·(z A -z R )-F gx ·(z R -z G )+W x ·(z C -z R )+M ry ＝0
There are eight unknowns to the six equations of motion: f (F) gx ，F gy ，F gz ，M gz ，F rx ，F ry ，M rx ，M ry The method comprises the steps of carrying out a first treatment on the surface of the However, more equations can be obtained through rail-roller interactions.
The three new equations obtained contain four new unknowns: f (F) g ，But is provided withWill be determined during the rail design process. Then F gx ，F gy And F gz Will become an unknown function F g We have nine equations for nine unknowns, which is a solvable system with unique solutions.
As shown in fig. 20, the guide rail design is normal to the direction.
For this particular invention, the rail design is novel. For convenience, a coordinate system with g subscript is defined herein and starts from the inner edge of the rail such that z=z g +z g0 Then:
each rail has a constant radial distance from the blade cavity shell centerline, so it is more convenient to use cylindrical coordinates.
Can be expressed as a variable z g Wherein the function θ g (z g ) Determining when the blade has been pulled to a particular z g Pitch angle at position. For a particular blade design operating on a particular domain, several optimal rotation rate/pitch angle combinations may be calculated. Curve fitting can be applied to the optimal rotation rate/pitch angle in the domain to obtain θ g (z g ). The following useful description of the guide rail is obtained by converting back to a Cartesian coordinate system fixed to the hub:
next, we determine the curve length "s" of the rail, described as a function of z (the sign "-" indicates the integral variable z, so as to distinguish from the integral limit z)
Introduction ofEqual, symbol' denotes the differentiation with respect to z, we determine the unit normal vector as:
acting force and moment
Aerodynamic force
For a propeller or turbine, it is typically possible to design around the central value () of the flow rate, pitch angle, rotational speed etc. to meet its efficient operation. Its aerodynamics is then characterized and modeled, including variations in the different parameters and dimensionless coefficients of the application domain. These models are synthesized into the equations of motion of the passive pitch control system.
Centrifugal force is described by the following formula:
where m is the mass of the blade,is the rotational speed of the hub, z c Is the position of the center of mass of the blade and is +.>Is a function of (2).
Weight:
if the hub rotates in a vertical plane, its weight will have no y-component. In this case, the weight induced forces in the hub fixed coordinate system will depend on the angle of rotation of the blade, as follows:
W x ＝-W·sin(β)
W z ＝-W·cos(β)
and (3) a spring:
if the spring is linear over its working range, then its force on the blade is modeled as:
where k is the linear spring constant, z s0 Is the z-position of the blade roll corresponding to zero spring compression or extension. z s0 Is a known function of the hub rotation angle beta designed to counteract the weight W of the blade in the z-direction z . The pitch change of the blade will cause the spring to twist and elongate. If the moment is sufficientLarge, coupling is ignored and torque due to torsion is assumed to be linear, then:
wherein τ s Is the torsion spring constant, theta s0 Is the pitch angle corresponding to zero spring torsion.
Roller and reaction force/torque:
using the previously derived equations of motion, the net reaction force and moment applied to the blade can be determined.
As shown in fig. 1 to 17, the specific structure of the elastic-motion steering system of the present embodiment will be described with reference to the accompanying drawings:
the elastic movement steering system of the embodiment comprises a blade 1, a hub 8 and a main shaft 12, wherein the hub 8 is fixed on the main shaft 12, and the elastic movement steering system further comprises:
a blade housing 2 arranged on said hub 8 for mounting said blade 1, said blade 1 being movable on said blade housing 2 along a longitudinal axis of said blade 1 when a rotation of said blade 1 causes a change of a centripetal force of said blade 1; the method comprises the steps of carrying out a first treatment on the surface of the
An elastic member 3 provided in the blade housing 2 for applying an elastic force to the blade 1;
a movement steering mechanism for guiding the blade 1 to rotate about its own center line to change the pitch angle when the blade 1 is longitudinally moved relative to the blade cavity casing 2;
a blade weight assembly for counteracting the influence of the component force of gravity of the blade 1 in the direction of the center line of the blade 1 during the rotation of the blade 1.
Specifically, in the present embodiment, the blade 1, the hub 8 and the spindle 12 of the elastic movement steering system rotate together, the root of the blade 1 is disposed in the blade cavity 2, the blade 1 can reciprocate relative to the blade cavity 2 along the axis direction perpendicular to the spindle 12 and can rotate around the center thereof, the elastic member 3 applies elastic force to the blade 1 to satisfy the condition of different rotation speeds, the blade 1 is in a state of balanced stress, the rotation speeds of the blade 1 are different, the centrifugal force generated by the blade 1 is different, the elastic force applied by the elastic member 3 to the blade 1 is different, the elastic member 3 stretches and contracts under the condition of different rotation speeds of the blade 1, so that the blade 1 moves in the blade cavity 2, and the movement steering mechanism can guide the blade 1 to perform corresponding rotation deflection in the process of moving the blade 1, so as to satisfy the ratio of the pitch angle to the rotation speed of the blade 1, so as to obtain higher efficiency. Compared with the prior art that an electric control system is adopted to adjust the pitch angle, the elastic mobile steering system of the embodiment realizes mechanical adjustment of the pitch angle through the cooperation of the elastic member 3 and the mobile steering mechanism, and in the actual use process, the reliability of pure mechanical adjustment is higher, and the whole structure is simple, and the manufacturing cost and the later maintenance cost are lower. The blade counterweight assembly may further include a fixed annular guide rail 10, a center of the annular guide rail 10 is located above an axis of the main shaft 12, each blade 1 is provided with a gravity roller 9, the elastic member 3 is connected between the gravity roller 9 and the blade 1, the gravity roller 9 is arranged in the annular guide rail 10 in a rolling manner, a plurality of blade cavity shells 2 are distributed in a circumferential direction of the hub 8, each blade cavity shell 2 is provided with a mounting hole, a blade root 7 of the blade 1 is mounted in the mounting hole, the corresponding elastic member 3 is connected with a root of the blade 1, and the elastic member 3 is also located in the mounting hole and connected with the gravity roller 9. Specifically, because the position of the blade 1 periodically changes in the rotation process of the blade 1, meanwhile, the influence of gravity of the blade 1 also periodically changes along with the direction of the centrifugal force, in order to reduce the influence of the gravity of the blade 1 on the pitch angle adjustment process, the eccentric annular guide rail 10 cooperates with the gravity roller 9 to reduce the influence of gravity, specifically, when the blade 1 rotates to the lowest end, the gravity of the blade 1 is the same as the direction of the centrifugal force, the acting force is superposed, and when the blade 1 rotates to the uppermost end, the gravity of the blade 1 is opposite to the direction of the centrifugal force, and the acting force is counteracted. When the blade 1 is located in the lower region, gravity is superimposed on centrifugal force, thereby increasing the force applied to the elastic member 3, increasing the tensile deformation of the elastic member 3 to move the blade 1 outwardly from the rotation center, and since the center of the annular guide rail 10 is offset from the axis of the rotation shaft 12 and located above the axis, the outward displacement of the blade 1 is canceled, thereby maintaining the absolute position of the blade 1 in the blade axial direction unchanged. Similarly, when the blade 1 is located in the upper region, the gravity and the centrifugal force weaken each other, the elastic member 3 is made to undergo compression deformation or the tensile deformation is made to decrease so as to move the blade 1 inward toward the rotation center, and since the center of the annular guide rail 10 is deviated from the axis of the rotation shaft 12 and is located above the axis, the inward displacement of the blade 1 is canceled, so that the absolute position of the blade 1 in the blade axial direction is maintained unchanged. Wherein, in order to improve reliability and structural strength, the annular guide rail 10 comprises a plurality of guide rail grooves arranged side by side, each blade 1 is provided with a plurality of gravity rollers 9 arranged side by side, and the gravity rollers 9 are arranged in the corresponding guide rail grooves 71 in a rolling manner. The annular guide rail 10 may have a closed loop structure such as a circle, an ellipse, or an approximate triangle. In addition, for example, the reliability is improved, the blade 1 is prevented from being separated from the mounting hole, the blade cavity shell 2 is further provided with a fixing ring 6, the fixing ring 6 is sleeved on the blade 1 and fixed on the blade cavity shell 2, and the fixing ring 6 can prevent the guide piece 4 from sliding out of the sliding groove 5 so as to prevent the blade 1 from falling off. The elastic member 3 is a member that generates a restoring force against tensile, compressive, rotational, and torsional deformations when subjected to these deformations. For example: the elastic member 3 may employ a spring or other component having an elastic expansion function. It is also possible to design an elastic mechanism that does not require moving the steering mechanism, but rather relies on its own coupling of torsion and tension to produce the desired pitch angle.
Further, in order to facilitate the deflection of the adjustment blade 1 by the mobile steering mechanism, the mobile steering mechanism comprises a chute 5 and a guide 4 arranged in said chute 5. Specifically, the guide member 4 moves along the chute 5, guides along the radian of the chute 5, and can control the deflection of the blade 1, wherein the chute 5 can be arranged in the blade cavity shell 2, and the corresponding guide member 4 is arranged on the blade 2; or, the chute 5 is disposed on the vane 1, the guide member 4 is disposed on the vane cavity shell 2, specifically, the chute 5 is disposed on the vane cavity shell 2, and the vane 1 is illustrated by taking the guide member 4 as an example: after the rotating speed of the blade 1 changes, the blade 1 moves in the mounting hole under the action of centrifugal force, and the blade 1 is guided by the guide piece 4 and the chute 5 in a matched manner in the moving process, so that the blade 1 rotates and deflects along the curve of the chute 5, and the required pitch angle requirement under the speed condition is automatically met. Wherein the guide 4 can be a guide post or a slide block which is slidably arranged in the chute 5; alternatively, the guide 4 is a guide roller which can roll in the chute 5. In general, the greater the speed at which the blade 1 rotates, the greater the pitch angle of the blade 1 needs to be, and then in the conventional design of the chute 5, the chute 5 may be designed such that the pitch angle of the blade 1 gradually increases during the outward movement of the blade 1 along the chute 5, whereas the pitch angle of the blade 1 gradually decreases during the inward movement of the blade 1 along the chute 5.
Wherein the outer diameter of the blade cavity shell 2 is smaller than the inner diameter of the blade root 7 of the blade 1, and the blade root 7 can move on the outer surface of the blade cavity shell 2; alternatively, the inner diameter of the blade cavity 2 is larger than the outer diameter of the blade root 7 of the blade 1, said blade root 7 being movable in the blade cavity 2. For the hub 8 in the system, the blade cavity shell 2 may be located outside the hub 8, or the size of the hub 8 may be increased, so that the hub 8 partially or completely wraps the blade cavity shell 2, and the blade cavity shell 2 does not protrude from the hub 8.
In addition, during actual use, the elastic mobile steering system of the present embodiment configures additional equipment for input power generation or for power output, for example: the main shaft 12 may be connected to a generator 11, a motor, an engine, or other related components.
The elastic movement steering system provided by the invention adopts a pure mechanical mechanism, is not affected by power failure, inaccuracy of an anemometer or errors of users, thereby enhancing the reliability, the rigor and the control efficiency of the system, and in the process of changing the rotating speed of the blades, the centrifugal force generated by the blades changes to change the spring force exerted by the springs on the blades, the blades move relative to the cavity shells of the blades, and the blades are guided by matching with the movement steering mechanism, so that the blades rotate to automatically adjust the pitch angle. Alternatively, an elastic mechanism may be designed that does not require mechanical movement of the steering mechanism, but rather relies on a coupling of torsion and tension of its own to produce the desired pitch angle. The system may be slightly adapted for use in many applications, for example, the system may provide anti-overspeed protection for a fluid driven turbine.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.
Claims (11)
1. An elastic mobile steering system with counterweight device, comprising a main shaft and a plurality of blades distributed around the axis of the main shaft, characterized in that it further comprises:
a blade housing disposed on the spindle for mounting the blade, the blade being movable on the blade housing along a longitudinal axis of the blade when rotation of the blade causes a change in centripetal force of the blade;
an elastic-movement-steering mechanism for guiding the blade to rotate about its own center line to change a pitch angle when the blade moves longitudinally with respect to the blade housing, and for applying an elastic force to the blade; comprises an elastic member arranged in the blade cavity shell for applying an elastic force to the blade;
a blade weight assembly for counteracting the effects of the force component of the blade gravity in the direction of the blade centerline during rotation of the blade; the blade counterweight assembly comprises an annular guide rail and a gravity roller, wherein the gravity roller is arranged in the annular guide rail in a sliding or rolling manner, and the center of the annular guide rail is positioned above the axis of the main shaft; each blade is provided with the gravity roller; the elastic member is connected between the gravity roller and the blade.
2. The elastic displacement steering system according to claim 1, wherein two or more of the blade shells are distributed in a circumferential direction of the main shaft, each of the blade shells having a mounting hole provided therein, and the root portion of the blade is mounted in the mounting hole.
3. The resiliently mobile steering system of claim 1, wherein the blade chamber housing is wholly or partially housed within the central hub, and may be wholly external to the central hub.
4. The resilient mobile steering system of claim 1, wherein the outer diameter of the blade housing is less than the inner diameter of a blade root of the blade, the blade root being slidable on an outer surface of the blade housing; alternatively, the inner diameter of the blade cavity shell is larger than the outer diameter of the blade root of the blade, the blade root being slidable in the blade cavity shell.
5. The resilient mobile steering system of claim 4, wherein the vane housing further comprises a retaining ring, the retaining ring being positioned over the vane and secured to the vane housing; or the blade is also provided with a fixing ring, and the fixing ring is sleeved on the blade cavity shell and is fixed on the blade.
6. The resilient mobile steering system of claim 1, wherein a linear bearing or an array of ball bearings is used on the blade root or blade cavity shell.
7. The resilient mobile steering system of claim 1, wherein the mobile steering mechanism comprises a chute and a guide disposed in the chute.
8. The resilient mobile steering system of claim 7, wherein the chute is disposed in the vane chamber housing and the guide is disposed on the vane; alternatively, the chute is provided on the vane and the guide is provided on the vane chamber housing.
9. The resiliently movable steering system of claim 7, wherein the guide is a guide post or a slider or a collar slidably disposed on the chute; alternatively, the guide is a guide roller that can roll in the chute.
10. The resiliently movable steering system according to any of claims 1-7, characterized in that said resilient member is a member that generates a restoring force against tensile, compressive, rotational, torsional deformations when subjected to such deformations, including springs.
11. The resiliently mobile steering system of any of claims 1-8, wherein the main shaft is connected to a generator, or a motor, or an engine.
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| CN2017109175804 | 2017-09-25 | ||
| CN201710917580 | 2017-09-25 |
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| FR2926535B1 (en) * | 2008-01-23 | 2011-08-12 | Eurocopter France | DEVICE AND METHOD FOR DYNAMICALLY BALANCING A BLADE |
| US8540485B2 (en) * | 2008-03-04 | 2013-09-24 | Philip Bogrash | Cycloidal rotor with non-circular blade orbit |
| CN102155355A (en) * | 2010-02-12 | 2011-08-17 | 大银微系统股份有限公司 | Vane pitch automatic adjusting device for wind driven generator |
| CN105089945B (en) * | 2015-09-10 | 2017-08-25 | 沈阳华创风能有限公司 | Wind generator unit wheel hub |
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| CN101787958A (en) * | 2009-01-22 | 2010-07-28 | 风技绿能科技股份有限公司 | Improved wind power generation device structure |
| KR20120035408A (en) * | 2010-10-05 | 2012-04-16 | 김병만 | Wind power system having rotation structure using eccentricity of gravity |
| WO2012111913A2 (en) * | 2011-02-16 | 2012-08-23 | Lee Seung Geun | Rotary body for a wind power generating apparatus |
| CN103174586A (en) * | 2011-12-22 | 2013-06-26 | 大银微系统股份有限公司 | Blade pitch angle control mechanism of wind driven generator |
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