End-mounted spiral rotor

专利摘要:
SUMMARYThe present invention relates to a turbine which recovers the energy from the velocity of a flowing fluid such as wind, steam, water currents and water waves.The invented turbine is arranged with the axis of rotation arranged mainly forperpendicular orientation towards the fluid direction in question and of a kind whichcomprises a self-supporting rotationally symmetrical blade body integrally built up of rotor blades connected in pairs and crosswise, the fluid passing through the turbine with less vortex turbulence than in other types of turbines with independent rotor blades.The invention relates to a method of controlling the speed of the turbine solely with the aid ofthe fluid velocity by automatically and simultaneously changing the length of the leaf body anddiameter.The invention relates to the use of the turbine for generating electrical or mechanical or visual power in a ground-based or floating power unit, especially in turbine parks comprising several turbines where maximum power is required on a limitedarea.
公开号:SE1330093A1
申请号:SE1330093
申请日:2013-07-23
公开日:2015-01-24
发明作者:Thomas Kullander
申请人:Thomas Kullander；
IPC主号:

专利说明:

SUSPENSION SPIRAL ROTOR TECHNICAL FIELDThe present invention relates to a turbine arranged for recovering energy from a flowing fluid by rotating a rotor about a line of rotation at substantiallyperpendicular orientation of the same towards the fluid direction, i.e. a cross-sectionturbine, the rotor being provided with helical rotor blades located between the ram spirits of the rotor and suspended in the turbine in at least one of said spirits.
The invention also relates to a method of controlling the speed of the turbine by controlling the size of the rotor, the rotor in combination with the suspension of the rotor in the turbineenables automatic control when changing the size of the fluid velocity.
The invention also relates to a use of the turbine and an implementation of the control method in a ground-based or floating power unit which converts the recovered energy into electrical or mechanical or visual effect, or into a combination of two or three of said effects.
BACKGROUND OF THE INVENTIONTurbines that are arranged to extract energy from a flowing fluid - such as air currents, angstroms, water currents or water waves - are usually designed to extract maximum energy from the flow at a certain fluid velocity, i.e. have a construction operating point. Basics of the turbineeffective function is the existence of a fluid velocity that provides sufficient lifting force pathe rotor blades to overcome the total resistance of the rotor blades and turbine. The turbine shaft is thus rotated by the lifting force, which arises as a result of pressure differences during the passage of the wing profile of the rotor blades, has a force component directed in the direction of rotation which - when multiplied by the distance tothe line of rotation - gives rise to a moment of force which creates the named spirituallyrotation. The above grids for saval conventional so-called quick-openers (wind turbines), ang turbines and water turbines where the turbine shaft is directed substantially parallel to the fluid direction; as for more unconventional transverse turbines where the turbine shaft is directed vertically and perpendicular to the fluid direction, e.g. wind turbines of the type s.k. H-rotors(SE564997C2), or where the turbine shaft is directed perpendicularly but horizontally to thethe fluid direction, e.g. US2011 / 110779A1.
HH-112Two-dimensional turbines have as edge an axis of rotation with a rotor rotating about said axis of rotation, and four significant passages of the fluid through the rotor: upstream, co-current, downstream and counter-current; thereby obtaining a pulsating lifting force on the rotor blades during the rotational revolution which is cosine distributed to the amount andto the size maximum upstream and downstream, and minimum co-current andcountercurrent. It is known that the rotation of the rotor is transmitted to the turbine in one or more joints, each of which has a suspension point to a rotor blade. Thus, the rotor and the rotor blades can be connected to the turbine at a plurality of suspension points. Suspension at two symmetrically inclined points in or around the central plane of the rotor,s.k. central suspension rotor, there is a challenge has i.a. named H-rotors. Suspension inthe ram spirits of the rotor blades are a challenge for e.g. Darrieus wind turbine (NL19181). Also suspension in one end of the rotor blades, so-called and suspended rotor, is the bachelor and challenger of a wind turbine with straight blades united in a central turbine hub located at ground level and spreading obliquely upwards. It is also an edge that center-mounted turbines are equipped witha bar plant comprising support arms, turbine hub and turbine shaft as large fluid flowthrough the blade body, so that the lifting force on the rotor blade decreases, especially in the downstream passage, and the efficiency of the turbine is thereby lowered. This disadvantage i.a. a. means that transverse turbines have a lower efficiency than conventional quick-loops at the same solidity, i.e. that the ratio between the tip speed of the rotor bladesand the actual fluid velocity is lower. When investing in wind turbines is preferredddrfor often snapblopare. As may be appreciated from the foregoing, there is a need to avoid a rotor that is center-suspended in order to achieve a higher efficiency of the turbine.
Transverse turbines preferably have as an edge three straight rotor blades, i.e. withthe nose (leading edge) parallel to the line of rotation, as for example in H-rotors. TheIt is further known that a centrifugal force arises as a result of the rotation of the turbine about the line of rotation and acting on the mass of the turbine, directed perpendicularly and outwards from the line of rotation. The centrifugal force is thereby added vectorially to the lifting force on the rotor blades, so that the resulting force on the rotor blade increases at the passageco-current, downstream and countercurrent; while it instead decreases upstream. TheThe resulting pulsating force on the rotor blades thus has its maximum downstream and minimum upstream, an oblique distribution which gives rise to the risk of material fatigue, undesired vibrations, natural oscillations and noise of the turbine. Rotors equipped with straight rotor blades present the above challengesHH-113the construction of the rotor blades and attachments thereof. It is known technology that transverse turbines having three straight rotor blades do not start the rotor automatically at low fluid velocities, but the turbine must be started with the generator; however, helical rotor blades have the property of being able to start the rotor more easily. Spiral shapedrotor blades are known from technology including CA 2674997 which describes a wind turbinearranged with helical vertical rotor blades, most of which are directly and firmly connected to the turbine's nay on the turbine shaft; and in WO2120153813 (A1) which describes a water turbine arranged analogously to a multi-bladed so-called Darrieus wind turbine (NL19181); and in WO2120152869 (A1) which describes a water turbine with collapsiblespiral-shaped leaves. As may be appreciated from the above, a rotor is provided withspiral-shaped leaves benefit which can be further developed and produced.
As an edge, transverse turbines preferably have rotor blades in the wind design provided at a wing profile with a constant angle of attack against the direction of rotation, which lack the property of being able to brake the turbine aerodynamically at wind speeds.exceeding the construction operating point as above. In fast walkers, for example, canthe turbine blade is mechanically rotated about its own longitudinal axis in order to - at a sufficiently high wind speed - adjust the angle of attack (a) of the turbine blades and thereby obtain a constant speed, sa. that - if the wind speed exceeds a certain value - the turbine blades are completely turned out of the wind and the turbine is stalled. No effect is generated then, but when the wind decreases it is turnedthe blades back and the turbine delivers power again. Has H-rotors like, okarthe speed with the wind speed up to a certain upper limit where the turbine shaft must be equipped with a device or method for braking or controlling the turbine's speed, otherwise the turbine will fail due to for star load or by the generator overheating. In the absence of, or in combination with, methods of controlling the speed -such as a speed shaft - the turbine can be equipped with two generators intended for differentspeed ranges, which require a larger control system with the following control equipment. Instead, a single generator can be used - which simplifies electricity production - by the turbine being electrically braked by a permanently magnetized synchronous generator, which is described in WO2010 / 039075 and is stated to require a strong nate connection with anight voltage exceeding 10 kV to be effective. For turbines that are not connected toa strong night with a night voltage exceeding 10 kV, however, the above-mentioned solution is not possible to carry out, instead an aerodynamic braking is preferable for such autonomous free turbines. However, since the rotor blades have a constant angle of attack (a) as above, they cannot be turned out of wind so that the lifting force ceases and the rotorHH-114stops, as is possible for the rotor blades of quick-release openers as above. As may be appreciated from the foregoing, there is a need to be able to aerodynamically brake transverse turbines with a constant angle of attack (a) against the direction of rotation in order to reduce the speed at wind speeds greater than the nominal ground power, instead ofcompletely stop the turbine.
The above grids are generally for all the mentioned turbine types where these are placed individually, but gathered in groups, the effect of the influence is added from the proximity to each other. Especially for turbines that are pine grouped, the aforementioned shadow effect can be significant, which means that the group's actual recovery of energy is far belowthe sum of the ground power of the individual turbines. Economic, environmental orpractical shells are often behind such advanced construction of turbines; i.e. turbine parks, where energy recovery per unit area or volume is to be maximized. When the fluid passes through a turbine park, the overlap and the extension have the fluid shadow downstream of individual turbines decisive for the total turbine parkbe able to extract the energy from the fluid. This is determined i.a. of a minimum allowedhorizontally s.k. separation distance between the center points of the turbines; in addition, the turbines can have different inboard size and height. It is an edge that some floating turbine parks with quick loops are allowed to rotate around an anchorage point (eg WO2011 / 117903A2), whereby all the individual turbines can be oriented with theirhorizontal turbine shafts directed towards the fluid eye, so that the Iage of the fluid shadow thereby onlydepends on the geometry of the turbine park. The latter also applies to turbine parks that are equipped with only vertical-axis turbines.
When the fluid passes through a single turbine, the induced resistance is of particular interest, as it should determine the extent of the fluid shadow downstream ofturbines. The induced resistance arises through the pressure equalization that takes placebetween the upper and lower sides of the wing profile and tends to level out at the tip of the leaf. This phenomenon results especially in fast runners, in so-called tailwind, i.e. helical air vortices; which emanate from the blade tip with the helical axis coinciding with the line of rotation, and propagate downstream during dissipation untilthey are completely or partially dissolved at a distance from the turbine corresponding to about 7 moreturbine diameters. The tailwind acts as a brake on the turbine and interferes with other turbines downstream; especially for the rotor blades of quick-release openers that are attached to one duct to the rotor hub while the other duct (blade tip) is free. The size of itHH-11induced resistance depends on the lateral relationship of the rotor blade, so that a long and narrow blade with a short chord (large lateral relationship) has a higher induced resistance than a short and wide blade with a long chord (small lateral relationship). Quick rotors have a typical lateral relationship for the rotor blades between 8 and 12, while straight rotor blades have a typicallateral ratio between 20 and 40 in the wind version. It also applies that it inducedthe air resistance increases squarely with the apparent angle of attack of the fluid against the wing profile.
Parameters relating to the overlap and extension of the fluid shadow can be considered asparameters regarding the ability to efficiently extract energy per unit area of a turbine park in a limited area. Thus, in the construction and building of aturbine park which is arranged to extract energy from a flowing fluid, it is generallyIt is interesting to note that the actual efficiency of the turbine park corresponds to the assumed efficiency required for the turbines to extract the energy from the fluid on the prescribed salt, e.g. to be able to deliver agreed ground power. In the operational phase of a wind turbine fleet of fast-openers, it has occurred that the originally assumedthe efficiency has had to be adjusted downwards due to new information from feeds ofthe efficiency of other turbine parks with similar horizontal separation distances, turbine diameters or fluid ratios. During the construction and / or construction phase of new wind turbines with high-speed openers, prior art suggests that the turbines be placed more sparingly (separation distance increased to 7 turbine diameters) so as not to shadeeach other; which has to WO that the number of turbines and energy recovery per unit areareduces. As may be seen from the above, there is a need to increase the efficiency of energy recovery per unit area of turbine parks in a limited area by e.g. use turbines that can be placed tatter without oiling significant power reduction.
HH-116SUMMARY OF THE INVENTIONA first object of the present invention is to provide a turbine for recovering energy from flowing fluids at a substantially perpendicular orientation of the line of rotation towards the fluid direction, the invention introducing a new type of rotor for the purpose ofto achieve higher efficiency, the turbine has a comparison with the corresponding transverseturbines with vertical shaft or horizontal shaft rotors.
A second object of the present invention is to provide a method of preventing overload having the generator by regulating the speed of the turbine, the invention enabling automatic control of the size of the rotor when changing the fluid velocitysize.
A third object of the present invention is to provide a use of the turbine and an embodiment of the control method in a turbine park comprising a plurality of turbines placed in a limited area, the invention allowing minimal separation distances between the turbines without significantly reducing the turbine parkefficiency.
A fourth object of the present invention is to overcome or improve at least one of the disadvantages of prior art or to provide a useful alternative.
At least one of the above objects is achieved with a turbine according to claims 1-20. As used,the term "axial" refers to a direction parallel to the line of rotation and "radial" perpendicular to the line of rotation;the term "cross-sectional section" refers to the planar figure which arises when intersecting a structural element at right angles to its longitudinal axis;-refers to the term "center line" a normal line to the plane containing saidcross-sectional section with foot point located on the line of symmetry or skeletal line of the cross-section or in its center of gravity. The term "center line" is also used on the long axis of the structural element is not straight, that is to say that the "center line" has the property of being able to be curved. The term "skeletal line" (Q) refers to the line thatconnects the midpoints of the circles which can be inscribed in a wing profile, thatHH-117viii legend that the skeletal line lies midway between the upper and lower wing surface of a wing profile;the term is intended to be "connected with", "in connection with" or "enclosed by" another part, that the part may be either directly connected to or directly enclosedof the second part or intermediate parts may also be present.
On the other hand, when a part is referred to as being "directly connected" with or "directly enclosed" by another part, then there is no intermediate part present;the term "fixed bandage" or "fixed bandage" means that rotation and translation between integral parts of the bandage is not possible, while the term "bearing" indicates thatrotation and translation between end parts ram is possible; whereby "plain bearing"indicates that axial translation but not rotation is possible, and "roller bearing" that rotation but not axial translation is possible;the terms "first", "second" and "third" refer to the need to distinguish singularity of a plurality of completely permutable elements, but not to numberphysically; the viii saga, which as heist of the elements can thereby be termed asthe "first", "second" or "third".
Thus, the present invention relates to a turbine arranged for the production of usable energy from the motion having a flowing fluid at a substantially perpendicular orientation of the line of rotation of the turbine towards the direction of fluid (W),comprising a turbine roller bearing provided with a rotatable bearing housing and a non-rotatable onebearing housing, and having a center point and a center line passing through said center point, and at least one support hub arranged in fixed connection with the rotatable bearing housing and a support structure arranged in fixed connection with the non-rotatable bearing housing, and a blade body fully or partially coated in the fluid and arranged in bandageswith the rotatable bearing housing, the movement of the fluid dialing rotation of the blade bodyaround the line of rotation which coincides with the center line at a point identical to the center point, and comprises a plurality of rotor blades each of which is continuously extending axially and radially in a space spiral curve with helical axis in the line of rotation and having a twisting direction about the line of rotation and in the normal plane tothe space spiral curve provided with a cross-sectional section provided with a center line andhaving a wing profile with two duck portions, the first duck portion having a rounded nose (N) directed in the direction of rotation (V) of the leaf body and the second duck portionHH-118has a tip (S) in the opposite direction, the blade body having onediameter (D) and a center point (PM) at the intersection point between the line of rotation and the center normal plane (M).
The invention is particularly distinguished by the fact that the rotor blades have different twisting directions aroundthe line of rotation and that two rotor blades with different twist directions are connectedeach other in at least one blade joint.
As may be understood from the above (see requirement 1):it is the movement of a flowing fluid which gives rise to the rotation of the leaf body, i.e. that the leaf body can be either completely in the flowingthe fluid or partially in a portion of the fluid that is not flowing. Thus canthe leaf body does not rotate if it is completely in the part of the fluid which is not flowing, i.e. where the fluid is stillast.ende;the fluid can in principle consist of any matter which is raised in a liquid or gaseous aggregation state. For example, the fluid may consist of one or moregaseous elements, such as air; or in liquid form, such as water; or amixture of gas and liquid forms, as occurs in condensing form. Thus, the fluid may be composed of two or more different substances, for example air and water, the flow of these fluids may have different strength and direction;-describes the expression "twisting direction" whether the space spiral curve is right-turnedor vanstervviden. A rotor blade can thus have one of two torsional directions, i.e. right-handed or left-handed; wherein two rotor blades can have twisted directions which are either equal, i.e. ram right-handed or left-handed; or different, i.e. a right-handed first rotor blade and oneleft-handed other rotor blades. Thus, according to the present inventiona first right-hand rotor blade is connected to all left-handed rotor blades, a second right-hand rotor blade is connected to all left-hand rotor blades, and so on. until all the right-handed rotor blades are connected. In the practice of the present invention, it may be noted that this is not a necessary conditionthat the leaf body is rotationally symmetrical, i.e. that rotor blades exhibiting differenttwists and turns are equal in number; or that rotor blades having equalHH-119twist directions also have equal spiral angles or are equidistant, or are separate and not connected to each other;there is a blade joint in the habit of crossing between a right-handed and left-handed rotor blade, the blade joint connecting the ram crossing the rotor blades.
Thus, each right-handed rotor blade is connected to all the left-hand rotor bladesrotor blades in one or more blade joints, and likewise, the habit-rotating rotor blade is connected to all right-rotating rotor blades in the same blade joints. The number of blade connections depends on the number of rotor blades and spiral angles (y). For example, 21 blade joints are required to connect a blade body consisting of 3 right-turned and 3left-handed rotor blades that rotate 1 spiral turn (i.e. have the pitch 1) onleaf body length (L), denoted (3 + 3) xl. The spiral angle (y) of the rotor blade is the angle between the center line of the rotor blade and the projection of the rotation line on the rotor blade.the term "blade body" refers to the rotationally symmetrical space-space whichlimited in part by the ram and normal planes (M1, M2), which constitute the normal planto the line of rotation and each contains at least one point tangentially to the rotor blades; and partly by the inner and outer concentric rotational surfaces which are generated radially by the envelope of the rotor blades when the spiral rotor rotates, the radius from the line of rotation to the inner rotating surface being smaller than the radius fromthe line of rotation to the outer surface of rotation in the usual normal plane coated between thebagge namnda andnormalplanen. The center normal plane (M) of the leaf body refers to the plane of symmetry of the ram and normal planes (M1, M2) and the length of the leaf body (L) refers to the distance between the ram and normal planes (M1, M2);the blade body is part of the turbine but does not form a solid body but oneinhomogeneous space provided with openings in both normal and flat surfaces.
The blade body thus extends continuously and circumferentially the line of rotation in an integrated grid of intersecting rotor blades, where the blade joints form the knots and the meshes are bounded by the rotor blades, the rotor blades being connected to each other only in the blade joints. Since habit leaf dressings connect two leaves withopposite twisting direction means that the habit of right-handed rotor blade is connected witha left-handed rotor blade. The return torque of a right-turned and left-handed rotor blade, respectively, is counterclockwise and thus takes out each other in the blade joint if the spiral angles are equal, which in practice gives aHH-11torque-free blade body in unloaded condition; i.e. without significant built-in natural voltages such as can result in the disadvantage of unwanted deformations;the blade body forms a self-rigid and thus self-supporting structure, since the rotor blades support each other in the blade joints; wherein the bending and torsional rigidity ofthe leaf body depends on i.a. the number of rotor blades, the number of blade connections, the length andthe diameter of the leaf body. The leaf body can thus be bent out in the fluid direction due to the load from the fluid on the leaf body, which has the consequence that the line of rotation can deviate markedly from the center line of the leaf body. The leaf body can thus rotate around a curved line of rotation, said. tocertain parts of the blade body during rotation are not perpendicular to the fluid direction;For example, the rotor blades can be constructed with shorter span lengths and thus smaller dimensions than what is usual with other turbine types with independent rotor blades - such as quick-release and H-rotors - because the number of storage points increases as the rotor blades support each other. In addition, canthe rotor blades are constructed with a rounder cross-section, i.e. with thickerwing profile than is otherwise usual with the above-mentioned turbine types with independent rotor blades; and thereby obtain increased bending and torsional resistance with an attenuating reduction of the stresses in and between the bearing points, as well as a stiffer blade body. Thus, it may be realized that because the rotor blades arehelical, becomes the angle between the center lines of the rotor blades and the line of rotationcoinciding with the spiral angle (y); and since the fluid direction is substantially perpendicular to the line of rotation, the angle of inflow (13) between the center line of the rotor blade and a normal to the projection of the line of rotation on the rotor blade thereby becomes equal to 90 minus (y) degrees.
It may also be appreciated that the effective chord of the wing profile in the fluid directionrequired by a factor equal to the inverse of the sine of (y), equal to the actual width of the rotor blade; and since the ratio of the blade profile between thickness to chord can be assumed to be determined at the given turbine size, the rotor blade must therefore be constructed with an actual MO which is correspondinglylarger thereby obtaining a rounder cross-section;the said shorter span lengths of the rotor blades may allow a considerably higher lateral ratio calculated on the free rear length between two blade joints than is usual with other turbine types with independent rotor blades.
HH-1111The lateral ratio of rotor blades according to the present invention is typically a number between 100 and 150, which gives rise to a laid induced resistance which i.a. The present invention is a suitable candidate for turbine parks in a limited area (see claim 20). The high side ratio Or even thatthe fluid flow may occur completely or partially laminated over the wing profile, i.e.exhibit a set Reynolds number at high fluid velocities which reduces the resistance of the rotor blade to the fluid and thereby increases the efficiency of the turbine;the continuous helical rotor blade of the blade body gives the advantageous property of being positioned somewhere on the angle of rotation for aoptimal angle of attack against the fluid flow, so that the blade body can thus beable to start the rotation. The rotation angle (0) of the blade body refers to the angle in the normal plane of the line of rotation with the point in the line of rotation. The angle of attack (a) of the rotor blade means the angle between the chord of the rotor blade and the apparent wind direction in question;-the continuous and integrated helical rotor blade of the blade bodyadvantageous property of absorbing and distributing the fluid load more evenly than straight rotor blades can Ora, by spreading the moment of force of the rotation over at least parts of the angle of rotation, whereby the said cosine-distributed pulsating load is distributed more evenly over the rotational speed. Thereby decreasingthe risk of material fatigue, unwanted vibrations and self-oscillations inleaf bodies; as well as that the noise from the turbine in wind performance can be avoided, as well as with quick-release blowers with straight turbine blades that generate a pulsating and whistling noise every time they pass the wind power mast.
In accordance with a preferred embodiment, the present invention hasthe turbine has a point of intersection (PN) between the line of rotation and another normal linethe line of rotation, and the blade joint has a point of intersection (PB1) between the center line of the first rotor blade and said normal line and a point of intersection (PB2) between the center line of the second rotor blade and said normal line, the points of intersection (PN, PB1, PB2) being connected by a common line tothe line of rotation, which normal line dr is provided with an endpoint in (PN), whereby the distancePN-PB1 is equal to the distance PN-PB2 and equal to the diameter of the leaf body (D).
HH-1112As may be seen from the above (see claim 2), two rotor blades are connected to each other in the same normal to the line of rotation and at one and the same radial distance to the line of rotation, i.e. the center lines of the rear rotor blades have a common point of intersection in the common normal line. and that they thus crosseach other in the same plane. An advantage of the above is that the blade joints can be given onesimple design as a continuous nut-sealed bolt in the common intersection of the ram rotor blades. A disadvantage of the above is that the rotor blades are coated at the same radius to the line of rotation and thus increases the risk that they shade each other during rotation.
In accordance with a preferred embodiment of the present invention,the turbine has a point of intersection (PN) between the line of rotation and a normal line to the line of rotation, and the blade joint has a point of intersection (PB1) between the center line of the first rotor blade and said normal line and a point of intersection (PB2) between the center line of the second rotor blade and said normal line.the intersection points (PN, PB1, PB2) are connected by a common normal line tothe line of rotation, which normal line is provided with an endpoint i (PN), the distance PN-PB1 not being equal to the distance PN-PB2.
As may be appreciated from the foregoing (see claim 3), the present invention allows:-two rotor blades are connected to each other with different radial distances to the line of rotation,that is to say, they are level. This reduces the risk that the fluid flow from the front rotor blade to the rear during rotation;different cross-sectional sections can be used for rotor blades with different radial distances to the line of rotation in order to best utilize the energy of the higher blade speed ofthe larger radial distance, or the lower blade speed on the smaller oneradial distance to the line of rotation;Unnecessary distortion and skew of the cross-sectional section of the blades, and thus secondary torque in the blade overhang and loss of power of the turbine, can be avoided by the resultant of the lifting force on the wing profiles of the rams.the rotor blades attack in a common normal line to the line of rotation; which canis allowed, since the aerodynamic center of the wing profiles in a leaf band ramHH-1113can be assumed to have the same distance to the nose (N) relative to the length of the respective chord;The spiral curves of the rotor blades can be generated so that the inner and outer rotational surfaces of the blade body separately describe a cylindrical, straight conical, double conical(hourglass conical) or biconical truncated space; whereby the volume of the leaf bodyis limited by the space between the outer and inner rotating surfaces, which means that the blade body can assume the most shape-specific shape of the turbine in question among 16 (4x4) different and possible formations.
In accordance with a preferred embodiment of the present invention,a first blade joint has the distance PN-PB1 which is greater than the distance PN-PB2and a second blade joint the distance PN-PB1 which is smaller than the distance PN-PB2, no blade joint being coated between the first and second blade joints.
As may be appreciated from the foregoing (see claim 4), this embodiment means that the rotor blade having the smallest radius of the line of rotation in a blade joint willto exhibit the largest radius in an immediately adjacent blade joint. This replacement ofplacement of the rotor blade in two adjacent blade joints, so that the rotor blade alternately belongs to the outer and inner rotating surfaces of the blade body, respectively; which meant that the space spiral curve of the rotor blade has the property of undulating as a sine curve with the largest amplitude in the blade joints and zero amplitude between two blade joints. The sine curvefor an undulating rotor blade which has a right-angled twist direction is offset bya factor (Tr) relative to the sine curve of a left-handed rotor blade, i.e. with 180 degrees; but exhibits the same amplitude, i.e. is opposite. The blade body thus gives the impression - for a viewer - that all rotor blades are "floated" around each other. Thus, the space spiral curve of the rotor blade around the line of rotation is superimposed in the axial and radial directions.of a sine curve as above. It should be noted that the definition of a (not superimposed)cylindrical or conical space spiral curve requires that the amplitude must be equal to zero for the tangent angle of the rotor blades to the line of rotation to be constant, which is thus not fulfilled for said superimposed space spiral curve. An advantage of the above undulated blade body is that the risk of the rotor blades large below each other is reducedthe rotation, and that all blade joints are exposed to compressive forces which strain to holdtogether habit individual leaf dressing.
HH-1114According to a further preferred embodiment of the present invention, a first blade joint has a first sum of said distance PNPB1 and PN-PB2, while a second blade joint has a second sum of said distance PN-PB1 and PN-PB2, the first the sum is equal to the other andequal to the diameter (D) of the said leaf body.
As may be appreciated from the above (see claim 5), this embodiment meant that the diameter (D) of the leaf body was set equal to its average diameter by definition, it means that (D) is shaved in the middle of the "rock thickness" and that the leaf body thus has a common diameter (D ) along its entire length (L). A significant benefit ofThe above is that all rotor blades have the same rear length, so that two rotor bladesthus boarding can be distorted without having to be displaced in the blade joint, which is a prerequisite for the control method according to claim 18.
In accordance with a preferred embodiment of the present invention, the blade joint comprises two blade sheaths each of which is provided with across-sectional section with a center line parallel to the center line of the rotor blade, whereinthe cross-section section completely or partially encloses the wing profile of the rotor blade.
As may be appreciated from the foregoing (see claim 6), the advantage of enclosing blade blades is that the rotor blades are reinforced on the outside where the highest bend stresses of the cross section occur, and that they can be relocated continuously without splicing in the blade joints (except in the case ofnon-planar crossings according to claim 2) and without limping for the leaf attacks, whichreduces the risk of fatigue of the rotor blades. Furthermore, the blade blades can advantageously be provided with a cross-sectional section at the wing profile with a nose (N) in the direction of rotation (V) of the blade body and comprise a slot in the rear edge (S) of the blade profile, the elastic construction of the blade blades allowing the rotor bladesopening which is then closed, for example by a friction joint or bolted joint(not shown). This device allows the rotor blades to adjust freely one after the other and thereby avoids unnecessary intrinsic stresses in the blade body when mounting the blade body.
According to a preferred embodiment of the present invention, comprisesthe blade joint a rod joint which connects the two blade joints with each other andis provided with a rod having a cross-sectional section with a center line, the center line coinciding with the common normal line of the blade joint.
HH-11As may be appreciated from the foregoing (see claim 7), the rod joint serves the primary purpose of connecting two intersecting rotor blades to each other which lie at different radii and is particularly preferred for absorbing compressive forces occurring in undulated blade bodies.
In accordance with a preferred embodiment, the present invention has includedthe bar joint at least one bar roller bearing provided with a center linecoinciding with the center line of the strut, the roller bearing allowing inward rotation of the center lines of the rotor blades about the common normal line to the blade joint.
As may be appreciated from the above (see claim 8), the roller bearing allows the spiral angle (y)may be other in the rotor blades in the blade joint; and, since the leaf body is integrated,if the change becomes equal to all the rotor blades in the blade body; i.e. that the length (L) and diameter (D) of the leaf body can change at the same time. For example, in leisure use, the spiral angle can be reduced to near zero or increased to near 90 degrees, and the blade joints are thus transported flat with the blade body in a rolled-up condition.
In accordance with a preferred embodiment of the present invention,the rotor blades made of polyolefin plastics such as polyethylene and polypropylene, or of polystyrene or of polyvinyl chloride or of metal such as aluminum, or in combination of two or more of said materials.
As may be appreciated from the foregoing (see claim 9), the rotor blades may be manufactured inthermoplastic material that enables a high degree of adaptation of the material of the rotor blades tothe surrounding million (E) and of the shape of the rotor blades to different operating conditions.
In accordance with a preferred embodiment of the present invention, the rotor blades are manufactured in a manufacturing process by extrusion or co-extrusion.
As may be appreciated from the foregoing (see claim 10), the rotor blades can be mass producedmechanically by extrusion of a plastic material, or co-extrusion of two or moreplastic materials with different material properties; i.e. is pressed with high pressure through a press die intended for the wing profile of the rotor blade, which thereby obtains the desired shape and the rotor blade obtains the desired length. The manufacturing methods for extrusion and co-extrusion give - individually or together - rotor blades which i.a. are:-continuous, which Or them producible in full lengths for the turbine, wherebyjoining short lengths by welding can be avoided;HH-1116slata, which Or them suitable in wing profiles designed for full or partial laminar flow, whereby grinding of the surface can be avoided;rough, which Or they suitable in wing profiles designed for full or partial turbulent flow, whereby application of coarse texture can be avoided;strong, with a tensile strength between about 20 - 50 MPa depending on the choice ofplastic material, whereby unnecessary weight of the rotor blades can be avoided;weldable, which makes them easy to repair and supplement on site if necessary, whereby disassembly of the rotor blades can be avoided;liquid, as the density of many plastics falls below that of water, thereby floating offthe rotor blades are possible and transport of, for example, a towing boat;wadded, by co-extruding with a UV-resistant material if necessary, whereby different material properties can be obtained in different parts of the blade cross section;durable, by choosing material properties adapted to temperature and load, whereby the creep deformation of the rotor blades is kept under control throughoutits longevity;The above grids for both homogeneous and inhomogeneous cross-sectional sections.
In accordance with a preferred embodiment of the present invention, the wing profile of the rotor blade is limited by a closed contour curve (KV) located in the normal planeto the center line of the rotor blade and enclosing a surface provided with at least twosection halls, each of which is bounded by a closed halrand curve (KS), whereinthe haland curves do not have an intersection point with the contour curve or with each other.
As may be appreciated from the above (see claim 11), the cross-sectional section has at least two separate sectional halls separated by a continuous and tat inner wall and a continuous and tat outer wall against the contour curve of the wing profile. Thus requirements are stated ongoods but not the thickness of the wing profile's inner cradle and outer cradle. The cross-section becomesthus inhomogeneous and the wing profile has the property of being persistent. These sectional halls thus form at least two separate and separately separated channels in the cross-sectional section. A tight inner cradle can advantageously be placed perpendicular to the chord at a distance corresponding to approximately 25% of the chord length from the nose, in order to reduceHH-1117the rotation of the cross-sectional section of the rotor blade which may arise about its center line tofollowing the point of attack of the crater in the aerodynamic center of the wing profile (see requirement 3).
The manufacturing methods for extrusion and co-extrusion of wing profiles with section halls produce - individually or together - rotor blades which, among other things, are:weight effective, i.e. exhibits the highest possible bending stiffness, torsional rigidity and cutting area inrelative to the mass, all inefficient area of the cross-section being removed;ihaliga, which allows the mentioned channels i.a. can be used for laying and laying cables and pipes; for example, for the purpose of feeding fluid velocities and collecting environmental data; monitor and control the turbine's function and performance; feedtension, pressure and temperature in the rotor blades; check density andmaterial resistance of the rotor blades; regulating mass flow through the rotor blades and lighting the turbine; assemble electronic systems for identification and positioning; and provide traffic systems for data communication and telephony. The channels can also be reinforced internally, for example withreinforcement element (see requirement 12);Ulla, i.e. with small mass of the rotor blades; which makes the turbine easy to start, since it squeezes a smaller lifting force to start and rotate a blade body with lower mass than a larger one; gives lower bearing forces, since the leaf body has lower mass; and makes the turbine easier to transport, assemble and repair;flexible, which makes the rotor blades possible to twist into spirals; for example, twoshorter rotor blades less than about 10 meters rear length, with craftsmanship simplicity are assembled together with opposite twists and turns to a blade joint in the usual spirit, so the rotor blades form the said space spiral curves. The rotor blades can be rewound on the drum for transport to the installation site, or stored.on roll for smaller turbines;simple and quick to manufacture, since the wing profile is one and the same along the entire length of the rotor blade, whereby a damaged rotor blade can, if necessary, be newly manufactured in an extruder factory in the vicinity;cheap, thanks to mass production, reducing the cost per producedkWh and the turbine will be attractive for investments.
HH-1118Extruded hollow plastic profiles are known technology that i.a. used for spacer profiles in electric shock cables, as well as co-extruded plastic profiles, but not for use as rotor blades. Furthermore, wing profiles are produced in extruded aluminum known technology for straight rotor blades for H-rotors, but not for helical rotor blades according to the invention.In accordance with a preferred embodiment of the present invention, isat least one reinforcing element located in at least one of the section halls in the cross-sectional section of the rotor blade, which reinforcing element is provided with a cross-sectional section and a center line which is parallel to the center line of the rotor blade.
As may be appreciated from the foregoing (see claim 12), reinforcing elements are referred to ascomplementary structural elements for blade attack in order to more evenly distribute the loads onthe rotor blades at the connection to the blade attacks and thereby reduce the stresses with consequent reduced risk of material fatigue in these exposed positions. The cross-sectional section of the reinforcing member may, for example, have a buoyancy between 30 to 150 percentage points, preferably 100 percentage points, of the turbine blade.bOj resistance excluding reinforcement element. The two-rivet section can, for exampleis designed as an I-beam, which allows free passage through the opening in the cross section between the 1-beam upper and lower flange. The extent of the reinforcing element along the rotor blade need not correspond to that of the blade cover.In accordance with a preferred embodiment of the present invention,the rotor blades have a first portion provided with a first end and a second portionprovided with a second end, the rotor blade and the ram ends together forming a body with a closed blade surface which delimits the body towards the surrounding million (E).
As may be appreciated from the above (see claim 13), vane gavel forms one essentiallyperpendicular normal plane to the center line of the rotor blade. Said gable may be the beldgen intwo arbitrary different portions of the rotor blade, for example in its ram spirits. The ends can thus be placed anywhere at the length of the rotor blade in order to divide the rotor blade into piecewise partitions. For example, two tight partitions can be formed by welding an end end into the ram spirits of the rotor blade, the rotor blade is cut in the central normal plane (M)and a gable is welded to the first part and the rotor blade is assembled by it amenthe other part is welded to the gable. Thus, the rotor blade can thus have the property of permanently enclosing a mass - such as a partial gas (for wind power units) orHH-1119air (for hydropower units) in order to minimize the mass of the enclosed volume in said body and thereby obtain a further lighter leaf body with consequent lower bearing forces. It should be obvious to a person skilled in the art that the said blade surface can be provided with one or more halves, each of which can be provided with a lid arranged toclosing and opening of the blade surface towards the surrounding million (not shown). Thus canthe rotor blade thus has the property that, if necessary, masses can be supplied via said hall and / or enclose masses with the aid of said lid and / or empty masses through said hall, for example a gas or liquid for tightness or pressure testing of the rotor blades. The lids may also comprise one or more bushings provided with tatclosure.
In accordance with a preferred embodiment of the present invention, at least one blade cover or reinforcing member made of composite material containing fibers of glass, carbon or Kevlar is enclosed in synthetic polymeric material.
As may be appreciated from the foregoing (see claim 14), reinforcing elements andblade attack Mgt pakanda structural element that can be molded to advantage, for examplein an autoclave; whereby prefabrication is possible and casting on site can be avoided.
According to a preferred embodiment of the present invention, the connection of the blade body to the support hub comprises at least one bar arm which comprises a blade cover connected to the bar arm and is rotatable about a straight center line passingby at least two arm roller bearings each provided with a bearing housing fixedly connected tothe center hub, the centerline of the arm roller bearings being parallel to the centerline of the turbine roller bearing and the usual blade bearing being fixedly connected to a duct portion of a rotor blade.
As may be appreciated from the foregoing (see claim 15), a helical rotor suspended in one of the two normal body planes of the leaf body (M1, M2) is described, wherein a bare arm is required for fastening ina blade attack of a duck portion of a rotor blade. It should be obvious to oneskilled in the art that a blade body according to the invention can also be suspended in the ram and the normal plane at the same time and was made to form a double-suspended rotor, for example several water turbines challenge with a common horizontal line of rotation located in a row across an elf. In the practice of the present invention, it may be noted that it does notis a necessary condition that the center line of the turbine bearing is vertical, but it canexhibit an arbitrary angle in a plane perpendicular to the fluid direction; i.e. the center line can also be horizontal or oblique. OneHH-11essential advantage of a duct-suspended or double-suspended spiral rotor is that a central turbine shaft can be avoided in the fluid so that the fluid flow through the turbine is not disturbed, whereby several advantageous properties can thereby be achieved:the efficiency of the turbine increases, as described in the background of the invention, which goesthat the cost per unit of power produced can be reduced;disturbing noise can be avoided because there is no non-rotating body upstream which creates a stationary pressure change downstream, for example as in fast runners where a hissing noise is heard every time a turbine blade passes the wind power mast. This advantage Or the invented turbine is possible to place inurban miljo.
In accordance with a preferred embodiment of the present invention, the center line (27) of the arm roller bearings has a point of intersection with the center line (6) of the turbine bearing.
As may be understood from the above (see claim 16), in the particular case meant thatthe center line of the turbine bearing is vertical, that the center line of the arm roller bearings forms oneangle to the vertical line. In the case that the point of intersection between the center lines is coated vertically above the center point (6), said angle becomes pointed upwards which meant that the blade overhang connection to the bar arm will pivot upwards then this rapids in radial direction out from the line of rotation. This upward shift ofthe bar arm strains to lift the attachment of the rotor blades to said blade attack and thusOka layer energy has leaf bodies, i.e. consume energy from any centrifugal force and a gravitational force on the turbine (see requirement 18). These forces force the ram to increase the helical angle of the rotor blades with the result that the blade body collapses in a stable equilibrium stroke, i.e. length (L)decreases and the diameter (D) increases; which the leaf body ingests at a decrease or completelyabsent centrifugal force. An effect of the vertical and horizontal movement of the bar arm is that the blade overhang must be connected at a pivot point to the bar arm to accommodate the change of the spiral angle with the diameter of the blade body.
In accordance with a preferred embodiment, the present invention hasthe turbine comprises a generator for converting the turbine's kinetic energy into electricalenergy, wherein the non-rotatable bearing housing or the support structure constitutes a stator and the rotatable bearing housing or the said support hub constitutes a rotor.
HH-1121As may be appreciated from the above (see claim 17), the desired diameter of the rotor may be given to achieve the required speed difference relative to the stator; which is a prior art, but does not challenge in the present invention.
From a second aspect of the present invention there is provided a method of:adjust the size of a leaf body to the device above using onedisplacement means comprising a rod connection arranged for rotating the center lines of the rotor blades about a common normal line to the line of rotation and a bar arm arranged for rotation about a center line passing through at least two arm roller bearings connected to a stand hub, said displacement means being arranged simultaneouslyincreasing the length (L) and decreasing the diameter (D) of the leaf body, or viceversa, said method comprising the steps of:provide an angular velocity of the turbine;causing said bar arm to be arranged in a first position, said first position corresponding to a first helical angle (y1) of the blade body;bringing said bar arm to be arranged in a second position, said secondposition corresponds to a second helical angle (y2) of the blade body, where (y2) is not equal to (y1).
As may be appreciated from the above (see claim 18), the size of the blade body can be changed by allowing the rotor blades to rotate relative to each other in the blade joints so that the angletowards the line of rotation, that is to say the spiral angle, changes. This is made possible byall blade attacks rotate at the same angle around their respective normal lines to the line of rotation (see requirement 9) in said rod bearings. According to the embodiment with undulated rotor blades (see claim 4) and common diameter (D) (see claim 6), a second helical angle means that the rotor blades only rotate towards each other in the blade joints, whileother embodiments mean that the ram rotor blades in a blade joint also receivedifferent inboard displacement in the direction of the line of rotation (Z). The change in the size of the leaf body takes place with the aid of the displacing means which affects the leaf body with a force resultant, which component attacks in the attachment of the leaf attack to the bar arm and is directed in the circumferential joint of the leaf body. The size of the power resultant is determined by the equilibriumbetween the turbine and the surrounding system, which equilibrium enters at salvagestationary as a rotating turbine.
HH-1122The dynamic equilibrium includes the effect of the flow of fluid on the turbine, which primarily results in a lifting force and a resistance on the rotor blades, but also gives rise to a centrifugal force and a moment of movement of the turbine. An increasing centrifugal force strives to displace both the mass of the leaf body and the mass of the bare armsperpendicular to the outside of the line of rotation. The blade joints allow, as above, the rotor bladesis rotated and the diameter of the blade body is increased, which is made possible by the fact that the bar arms are suspended in the support hub for rotation out of the rotational line; thereby saras - in circumferential direction - the attachment points of the rotor blades to the blade attacks; whereby the spiral angle increases and the length of the leaf body decreases. This increases the cord length of the wing profile (see requirements1) and the profile risks being exceeded to the extent that the ratio of the lifting force divided byresistance decreases. At an otherwise increasing spiral angle exceeding 45 degrees, the solidity of the turbine also increases. At very high fluid velocities, in combination with the overshoot above, this meant that the fluid resistance eventually becomes so great that the angular velocity of the turbine decreases; to in the extreme case further decrease because the lifting forcedisappears when the diameter increases so that the leaf body almost appears as an obstaclefor the fluid to pass. A decreasing centrifugal force has an opposite effect on the leaf body and the bar arms, so that a "closed" leaf body with high solidity automatically "opens" as the high fluid velocity decreases; thereby allowing the turbine to return to the construction operating point. As may also be realized, collarsdynamic equilibrium at an accelerating or decelerating fluid velocity to that of the turbinerorelsemangmmoment is conserved, i.e. that the product of the turbine's rotational moment of torque and angular velocity momentarily remains unchanged. In the present invention, this meant that the diameter and angular velocity of the ram body could be changed, simultaneously and instantaneously, before a new equilibrium enters at the newthe fluid velocity. Only at the new equilibrium is the new moment of movement taken.
Thus, the displacement means allows the angular velocity of the turbine to be changed automatically according to the fluid velocity without forced displacement, so that e.g. the turbine speed can be regulated and the turbine brakes aerodynamically at high fluid velocities.
From a third aspect, the present invention relates to the use of the turbine andexecution of the regulation in a power unit arranged in solid ground or floating in awater mass for generating electrical or mechanical or visual power or a combination of two or more of said effects, said support structure being arranged in fixed connection to said foundation.
HH-1123As is apparent from the above (see requirement 19), the turbine is used in a power unit whichconverts the energy of the turbine into power. Ground-based power plant units also refer to bottom-fixed ditto placed at sea. Furthermore, it may be realized thatthe power unit can be arranged vertically, horizontally or inclined and in different waysdistance in relation to the power center mass center. Thus canthe length of the power unit exceeds the length of the blade body, for example said power unit may constitute a wind power mast to said turbine;the power unit can be arranged in different media - such as air or water. Thus, the flowing fluid may include wind in one part andwater currents or water waves, individually or in combination with each other, in itthe second part; wherein the fluid direction may be unidirectional in different media (see claim 1);the electrical power can be transported in a cable (K) from said power supply to consumers on land and / or at sea, which is known technology and not further explained;-the mechanical effect can, for example, be constituted by a turbine shaft for directmechanical operation of a propeller or pump, which completely eliminates the need to generate electrical power for the operation of the pump;the visual effect can be achieved by illumination of the rotor blades. These can, for example, be made of milky white polyethylene with high density (HDPE), which, among other thingsOr they are permeable to light from a light source placed inside the rotor blades, orclear polymethyl methacrylate (PMMA) which makes them fully or partially transparent to light even from a light source placed outside the rotor blades. Transparent rotor blades can also tame vultures (see claim 13) and be filled with gas, for example neon gas, whereby the rotor blades can obtain a colored light according to prior art. The gas can be ignitedusing the electric current produced by the power supply anddistributed in the power cables located in the section tail (see requirement 11) in the rotor blades. The turbine can thus constitute a rotating illumination for use as an advertising space, lighthouse, floating sea mark, flare for night fishing or other vantage point.
As may also be appreciated (see claim 19), the invention is adapted to use formobile leisure use in that the rotor blades can advantageously be carried in rolled-up condition andthe blade joints and any power supplies can be packaged in a barbaric package. MountingHH-1124of the blade body takes place in place by the rotor blades being pushed into the blade joints, which are turned up and buttoned; lay the rotor blades barely in the blade rafters on the stand hub, after which the turbine shaft is stored in the power unit, which is suggested to be fixed with ropes to the ground or the float. The turbine shaft can be placed in a portable generator and the power unit salundagenerate electric current and just as easily disassemble after use.
In accordance with a preferred embodiment of the present invention, the turbine is used in a turbine park comprising at least two power units each provided with a turbine having a vertical centerline and having a horizontal separation distance (A) between the center points of the turbine roller bearings of afirst and second turbines at the projection on a common horizontal plane, whereinthe minimum separation distance of the turbine park exceeds the length of half the average value and is less than the length of four times the average value of the blade body diameter (D) of said first and second turbines.
As may be appreciated from the foregoing (see claim 20), a turbine park may comprise two orseveral power supplies, i.e. two or more vertical transverse turbines, the firstthe turbine may be located in the fluid direction so that it overlaps and thereby shadows the other turbine downstream. Hdrav may realize that:transversely divided turbines with a vertical center line preferably have rotor blades inthe wind formation provided at the wing profile with a constant angle of attack towardsthe direction of rotation, which have the advantage that they do not need to be provided with acomplicated device for changing the angle of attack during the rotational revolution, but the disadvantage of giving a lower efficiency has the turbine. Thus, in the countercurrent passage as above, the wing profile has the angle of attack (a) towards both the direction of rotation and the direction of fluid; whilethe wing profile in the co - current passage shows the angle of attack (a) towardsthe direction of rotation and the angle of attack (a + 180 degrees) towards the fluid direction in question. In the not uncommon case that the mentioned constant angle of attack (a) is equal to zero, the lifting force in the countercurrent passage as well as in the cocurrent passage also becomes equal to zero; and only the shape resistance of the wing profile,The so-called. zero resistance, remains. Thus, savdli countercurrent passage as inwith the cocurrent passage, the fluid is not accelerated and no disturbance of the fluid flow occurs beyond that which is operable to the zero resistance;HH-11and thus the blade bodies of two turbines can be allowed to overlap each other downstream without the nominal ground effects of the turbines being significantly reduced;Transverse turbines having a vertical centerline are always perpendicular to the fluid direction in question. This is especially beneficial then. turbinesthus becoming independent of any device that sets the turbine shaft againstfluidogat - as is the case for fast-trackers. Another advantage of the vertical turbine shaft is that equipment for energy conversion - such as generator, gear unit and transformer - can be placed with a low center of gravity, for example in a protected space in a power unit located under the turbine. As may be realized by itabove, there are advantages to using vertical shaft transverse turbinesin floating power units which can thus be anchored firmly in the hay or seabed to the geographical north and not floating with the direction of fluid in question, as in the case of a changing wind or current direction;the blade body of the present invention has rotor blades having onelarge lateral and probe parts fluid in many small vortices that dissipatein short distances, while the blade body of fast-trackers has rotor blades that have a small lateral relationship and generate few but large vortices that dissipate over long distances, typically 7 - 10 turbine diameters. Turbines according to the present invention can therefore be placed closer than is the case with high-speed openers.i.e. may exhibit smaller horizontal separation distances, which is an essential oneadvantage when the area for placing turbines in a turbine park is limited but the effect thereof must be maximized;turbine parks equipped with several power units, can have different horizontal separation distances depending on. the location in the turbine park and what length anddiameter of the leaf body. The smallest of the separation distance is usuallymost interesting for turbine parks located in a limited area. Thus, the mean value of the leaf body diameter (D) is the basis for the determination, so that the smallest separation distance corresponds to the hypothetical case that two leaf bodies touch each other's diameters, while the largest separation distance corresponds to4 x (D). Preferably, the smallest separation distance is with itthe present invention between 1.5 and 2.5 x (D);HH-1126BRIEF DESCRIPTION OF THE DRAWINGSThe present invention will be described below more fully with reference to figures of non-limiting examples of various embodiments. It should be understood, however, that the embodiments have been introduced to explain the principlesthe invention and not to limit the scope of the invention, which is determined bythe appended claims. It should be noted that the figures have not been drawn up to scale and that the dimensions of certain pitcher features have been exaggerated for the sake of clarity. In particular, the leaf body has a three-dimensional shape which in reality may deviate from the sketchy models presented according to the figures.
Figure 1. is a perspective view of the rotor blades in the blade body according to the firstaspect of the present invention.
Figure 2. is a schematic side view of the turbine mounted on the hay or seabed inin accordance with the third aspect of the present invention.
Figure 3. is a view showing the extent of a cylindrical blade body with 3left-handed and 3 right-handed undulated rotor blades with pitch 1vary per leaf body length L.
Figure 4 is a view showing the extent of a cylindrical blade body of 4left-handed and 4 right-handed non-undulated rotor blades with a pitch of 0.5 vary per blade body Idngd L.
Figure is a view showing different sections of the leaf body in Fig. 3.
Figure 6 is a perspective view of a blade joint with a normal linethe line of rotation.
Figure 7 is a schematic view of the blade body with undulated rotor blades.
Figure 8 is a schematic view of the blade body with non-undulated rotor blades.
Figure 9 is a view showing two blade attacks to the blade joint in Fig. 6.
Figure is a view showing leaf joints in two sections of the undulatedthe leaf body according to Fig. 3.
Figure 11 is a view showing the wing profile of the rotor blade at different helix angles.
HH-1127Figure 12 is a schematic view of the cross-sectional section of the rotor blade withreinforcement element.
Figure 13 is a perspective view of a rotor blade provided with ends in the spirits.
Figure 14 is a view of the turbine according to the second aspect of the invention atno or low angular velocity ddr bdrams are positioned in infdlltIdge.
Figure is a view of the turbine in Fig. 4 fixed at a higher angular velocity ddrthe carrier arms are positioned in the extended position.
Figure 16 is a schematic view of a location of a generator in Figure 1.
Figure 17 is a side view of the turbine placed in a floating power unit.
Figure 18 is a view from a helicopter perspective and a section of a turbine parkseparation distance and different turbine heights of power units with blade body in infdllt layer.
Figure 19 is a view of the turbine park according to Fig. 18 but with the blade body in complete Idge.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTSFig. 1 shows a perspective view of a blade body (9) according to the invention and a line of rotation (3) around which the blade body is intended to rotate. The blade body is placed in a flowing fluid (2) with the velocity vector (W) directed perpendicular to the line of rotation and attacks the blade body in fluid holes at the angle of rotation (6) equal to 0. The blade bodyextension in the direction of the line of rotation. i.e. in the axial joint, bounded by the two.the normal plane (M1) and (M2) which are perpendicular to the line of rotation; and in the radial direction, of the outer and inner concentric mantle surface generated by the envelope of the outer and inner rotor blades, respectively, when the blade body rotates with the radius (r). The leaf body according to Fig. 1 thus has a double-conical (hourglass conical) inner and a cylindrical outermantle surface as ram is truncated in the normal plane of the duck, so that the leaf body is the largestdistance between the mantle surfaces is shown in the central normal plane (M). It should be noted that Fig. 1 is primarily intended to obscure the geometric construction of the blade body of rotor blades and not how these are attached to each other or to the turbine (1). Thus, Fig.1 indicates. only one blade joint (13) despite the present invention being characterized in thathabit pairs of intersecting rotor blades are connected by a blade joint between them.
HH-1128Fig. 1 shows the blade body made up of 6 rotor blades in space spiral curve, of which three are twisted with right rotation (10-H1, 10-H2, 10-H3) and three pieces are twisted with left rotation (10-V1, 10-V2, 10 -V3). The rotor blades are made of injection-molded plastic profiles that allow them to be rotated to a suitable radius (s). Fig. 1 shows the rotor bladestwisted one vary per leaf body length, i.e. the slope is equal to 1. Eachright-turned rotor blade is thus connected to a left-handed ditto in the spirits: thus 10-H1 is connected to 10-V1 in a blade joint (13) in (M2) and a blade joint (not shown) in (M1), 10-H2 connected to 10 -V2 in a blade joint (not shown) in both (M1) and (M2), and 10-H3 connected to 10-V3 in a blade joint (not shown) in both (M1) and (M2); i.e. 6leaf bandage. In addition, the vane right-handed rotor blade is connected in a bath dressing (noshown) in (M), i.e. 3 leaf dressings. Since no right-handed rotor blade crosses anything else right-turned and no left-handed one crosses any other left-handed rotor blade, habitual right-handed rotor blade in Fig. 1 intersects the other two left-hand rotor blades in an area between (M1) and (M), i.e. 6 blade joints; and in a range between (M2) and (M), i.e.another 6 blade joints. This gives a total of 21 blade joints for the blade body in Fig. 1.
Fig.1. indicates that all rotor blades are provided with a wing profile with a round nose in the direction of rotation of the blade body (V) and a pointed trailing edge (S) in the opposite direction. All rotor blades thus have a wing profile against the direction of rotation which makes them suitable for generating the lifting force required to rotate the turbine.
From the above, it should be clear to a person skilled in the art that Fig. 1 shows only one of a numberembodiments of the present invention. Thus, the pitch, number, back length and undulation ("flattening") of the rotor blades can be varied by one and the same combination of the length and diameter of the blade body. In addition, the height of the blade joints can be varied so that the blade body can assume one of 16 different combinations of outer and innermantle surfaces: cylindrical, conical, double conical (hourglass conical) and biconical. Finally canthe combination of the length and diameter of the leaf body is varied according to an embodiment of the invention.
Fig. 2 shows a turbine (1) arranged to recover energy from a tightening fluid (2) has onebody of water (F2) with a seabed (F1). For simplicity, the term is used"seabed" regardless of whether the body of water is an area in an ocean, a hay, a lake ora river. The turbine (1) comprises a blade body (9) connected to a support hub (7) fixedly connected to a rotating bearing housing (4) in a turbine roller bearing, the turbine roller bearing having a non-rotating bearing housing (5) being fixedly connected to a support structure ( 8) fastHH-1129connected to a power supply (28). Fig. 2 shows the turbine completely submerged in the body of water, but alternatively the turbine can be partially submerged as, for example, in shallow tidal bays. Fig. 2 further shows the power unit equipped with a power cable (K) laid on the seabed. For simplicity, anyands term "power cable" regardlessthe medium enclosed in the power cable includes electric current, liquid, gas orinformation and regardless of the direction in which the medium is transported. As may be appreciated, the power cable can be used to transmit energy to consumers, for example located on land; but alternatively be non-existent when all the energy produced by the turbine goes to consumption for operation of equipment located on the power unit, for example pumps forcirculation of oxygen-rich seawater. In addition to the leaf body, the above can be consideredas a graduate technician.
The turbine (1) in Fig. 2 is oriented with a vertical center line (6) through the rotating bearing housing (4) of the turbine roller bearing, the blade line (3) of rotation of the blade body coinciding with said center line at a center point of the turbine roller bearing. Sasomshown in Fig. 2, the line of rotation bends out the distance (Uh) in the direction of the fluid velocity (W), whichmeant that the turbine rotates around a curved line of rotation. A further feature of the present invention is that the line of rotation will also bend out to the side a distance (not shown), alternately at Niger and at left and thus describing a oscillating motion perpendicular to (W). The aforementioned turbine roller bearing is intended to accommodatethe buoyancy corresponding to the above-mentioned deflections has the turbine and at the same time allowthe second rotation of the turbine.
Fig. 3 relates to ash-like a blade body (9) of length L and diameter D which is cut longitudinally with a section parallel to the line of rotation (3) through the blade joints (13 ', 13 ", 13", 13 ") and viewed in the direction of the line of rotation from aplace outside the leaf body. Fig. 3 shows the cut leaf body spread out in a plane,wherein the width is thus equal to H multiplied by D; having 21 blade joints (13) connecting 3 right-angled (10-H1, 10-H2, 10-H3) and 3 left-handed (10-V1, V2, 10-V3) undulated rotor blades, which have the pitch 1 vary in length L and the helical angle (y).
The present invention neither limits the rear length of the rotor blades (10) norrequires blade joints (13) located in the second normal plane (M1, M2). This is shown in Fig. 1 as the length (L) of the leaf body comprising a partial length (dL), the partial length corresponding to a distance between one of the second normal planes (M1, M2) and a blade joint.HH-11(13); i.e. that the rotor blade is provided with a duct portion which is not laid in a blade joint and can thus obtain a free displacement. As may be appreciated, such a free end portion of a rotor blade offers the possibility of providing a lifting force on said free end portion which counteracts and partially reduces the bending moment in the rotor blade.caused by the lifting force on the non-free portion of the rotor blade between two blade joints.
Fig. 4 relates to ash-like a blade body (9) of length L and diameter D which is cut longitudinally with a section parallel to the line of rotation (3) through the blade joints (13 ', 13 ", 13") and viewed in the direction of the line of rotation from a place outside the leaf body. Fig. 4 shows the cut-out blade body spread out in a plane, whereinthe width is thus equal to H multiplied by D; having 20 blade joints (13)connecting 4 right-handed and 4 left-handed non-undulated rotor blades (10), which have the pitch 0.5 vary in length L and the helical angle (y).
As mentioned above, the embodiments shown in Figs. 3 and 4 are two examples among a myriad of other examples of the possible configuration of a leaf body.
Fig. 5 shows cross-sections of the blade body at the direction of rotation (V) according to Fig. 3,i.e. that habits for the viewer. View a - a shows a section in the middle normal plane (M) of the leaf body, which is parallel to (V); through 3 blade joints (13) and 6 rotor blades (10), the nose (N) of the wing profile of all rotor blades being directed in the direction of rotation (V). The aisle position between the center lines of the rotor blades in the center normal plane (M) is indicated by the distancewith the length (h0). Thus, in sections a - a, all left-handed rotor blades (10-Vi, 10-V2, 10-V3) a common radius (r) of the line of rotation (3) exceeding the common radius of all right-turned rotor blades (10-H1, 10-H2, 10-H3).
As can be seen from Fig. 3, views b - b show a section in the direction of rotation (V) of the blade body coated midway between two. blade joints (13), where all rotor blades have onecommon radius (s) to the line of rotation due to the undulation. As may be appreciated by FIG., this is a WO in that the distance is equal between the center lines of the rotor blades in the central normal plane (h0) and in the blade joint closest to the respective normal plane (h1, h2). In another example (not shown), views b - b are not coated between two blade joints, but only somewhere between two blade joints; all leaf joints having onecommon radius (r) to the line of rotation, but different distances (h0) and (h1) and (h2).
Fig. 5 shows in views c - c a section in the longitudinal joint of the blade body through 4 blade joints and 8 rotor blades, the nose of the wing profile to one half of the rotor blades being directed inHH-1131the direction of rotation (V) and to the other half are opposite, which is a consequence of the section being taken perpendicular to the direction of rotation (V). In the section, there are no rotor blades located in the central normal plane (M) and the distance (h0) can thus not be specified. The distances (h1) and (h2) are equal in this example, but may be different in other examples that havedescribed above.
As can be seen from Fig. 3, views d - d show a section in a rotor blade (10-V3), i.e. in the angle of inclination (13) of the rotor blade towards the fluid direction (W) in question. Since the helix angle (y) is shown to be about 45 degrees in Fig. 3, the center lines of all right-handed rotor blades become almost perpendicular to the center line of the rotor blade.(10-V3) in section; i.e. the cross-sectional sections of all wing profiles are closestmaximum round, which corresponds to the width (x0) in Fig. 11.
The undulation shown is intended to ash a sinusoidal shape. As can be seen from Fig. 3, (13 ') and (13 ") denote different blade connections; and (10i) and (10ii) different part lengths of the rotor blade (10-V3), which can thus have different lengths. The distance (h1 ) and (h2) areequal in this example, but may be different in other examples described above.
Fig. 6 shows a perspective view of a blade joint (13) comprising two rotor blades (10) each provided with a center line (11) and wing profile (12). A normal line (14) of the line of rotation (3) has a point of intersection (PN) with the line of rotation, said normal line also having a point of intersection (PB1) with the center line of the rotor bladewhich exhibits the smaller distance, i.e. radius, to (PN); and an intersection point(PB2) with the center line showing the greater distance to (PN). As shown in Fig. 5, PB1 and PB2 are connected by a structure further described in Fig. 7. The distance between PB1 and PB2 can be zero, giving one and the same radius of the ram rotor blades; or be different, giving different radii of the ram rotor blades.
Fig. 7 is intended to locate a first (15) and second blade joints (16) and shows a viewof an undulated leaf body viewed in the direction of the line of rotation from a location outside the leaf body. As can be seen from Fig. 7, no blade joint is located between said first (15) and second blade joints (16); i.e. the leaf joints are the closest neighbors.
Fig. 8 has the same purpose as Fig. 7, but for a non-undulated leaf body. Fig. 8 shows thatno blade joint is located between said first (15) and second blade joints (16); i.e. the leaf joints are the closest neighbors.
HH-1132Fig. 9 shows the blade joint (13) and the rotor blades (10) in Fig. 6 (dotted line) comprising two blade struts (17, solid line) which partially enclose the respective wing profile (12) and leave an opening in the trailing edge. When mounting a blade cover (17) with a rotor blade (10), the rotor blade can be allowed to be pressed into the blade cover with the nose first throughsaid opening with the aid of an applied external force and utilization of the blade attackflexibility in construction and materials. As may be appreciated from Fig. 9, the blade cover is connected in contact with the wing profile except in said opening; which is an advantage in the uptake and distribution of the forces on the rotor blades to the blade joint.
In another embodiment of a blade attack (not shown), the blade attack comprises onerotor blade two parts, for example shaped after the upper and lower side of the wing profile, whichconnect with screw, bolt or glue joints. The blade sheaths (17) are connected by a rod joint (18) shown in Fig. 9, the center line (19) of the rod joint coinciding with the normal line (14) of the blade joint.
Fig. 10 shows a view of a blade joint (13) in section e - e according to Fig. 3 comprising twoblade cover (17) connected by a bar joint (18) provided with bar roller bearing (T).
The rotor blades (10) may be allowed to rotate about the centerline (19) of the rod joint so that the helical angle (y) is different. Fig. 10 shows the rotor blades with the cross-sectional section drawn for the purpose of clarifying the appearance and orientation of the wing profile, i.e. that the direction of rotation points perpendicular to the viewer. Section f - f in Fig. 10 shows the blade joint atthe direction of rotation pointing to the left.
Fig. 11 shows in section g - g a view of a rotor blade (1) seen perpendicular to the plane containing the cord of the wing profile, showing the spiral angle (Vi) and the angle of inclination (pi), whereby (Vi) Plus (131) is equal to 90 degrees; and the cord length (xi) in the flow direction (13i). After a rotation of the rotor blade (1) aroundthe center line (19) of the bar joint (18), to a new approach angle (132) intrader,the rotor blade (102) receives a new chord length (x2), where (32) is smaller than (131) and (x2) is larger than (x1). The physical cord length of the rotor blade is equal to (xo), which is less than both (xi) and (x2) as shown in Fig.11. It is also shown that the thickness (y) of the wing profile is unchanged, and since the cord lengths (xo, x1, x2) are different with the spiral angles (Vi, y2)this meant that the angles of attack (al, 02) also affected others. Thus meant a largerspiral angle (y2) also a larger chord length (x2) and a smaller angle of attack (02), i.e. when the leaf body collapses due to a higher rotational speed, the angle of attack becomes smaller and the risk of exceeding the wing profile decreases.
HH-1133Fig. 12 shows a view of a cross-sectional section of a rotor blade (10) with a center line (11), which is a line of symmetry (Q) of the wing profile (12) provided with a nose (N) in the direction of rotation (V) and a tip (S) in the opposite direction. The wing profile is bounded by a closed contour curve (KV), and Fig. 12 shows the cross-sectioncomprising two section halls (20) each delimited by a closed onehalrand curve (KS). The cross-section shown is thus inhomogeneous, a reinforcing element (21) being shown to be located in one of the section halls. Fig. 12 shows only one example among a number of embodiments of the mold and the contents of a cross-sectional section of a rotor blade according to the present invention. Anotherembodiment (not shown) is provided with a curved line of symmetry (Q) and four section hallsseparated by straight cradles with a wall thickness corresponding to 2% of the cord length, which cradles are placed at right angles to (Q), a reinforcing element in the form of a 1-beam being located in two of the section hall. Yet another embodiment (not shown) is provided with a homogeneous cross section, i.e. without section hall or reinforcement element.
Fig. 13 is a perspective view of a rotor blade (10) having two duck portions (B1, B2)each of which is provided with an end (22, 23), the rotor blade forming a closed body between said ends so that it is completely delimited towards the surrounding million (E). Another embodiment (not shown) is provided with a duct portion (B1) and a middle portion (B2), the duct end (22) and the middle end (23) dividing the closed body onthe middle part of the rotor blade, i.e. pa halften; wherein the surrounding million (E) is in contactwith (23) via the sectional tail in the half of the rotor blade which does not include the end cap (22), i.e. one half of the rotor blade forms a closed body while the other half is open.
Fig. 14 shows in section h - h a turbine with (3 + 3) rotor blades viewed in the direction of the line of rotation (3) (Z) and direction of rotation of hooks with the blade body (9) in infant position (01). Fig. 14shows the blade body (9) with a vertical center line (6) and rotor blades (10) connected tothe blade struts (17) in a pivot point (m), the blade struts being articulated to the support arms (24) in a center line (25) through two arm roller bearings (26) on the stand hub (7). The blade body has the helical angle (Vi) and the blade connections (13), a filled circle indicating that the blade connection is located in front of the line of rotation (3) and an unfilled circle indicatinglocation behind (3) .1the figure is indicated by the angle (c) the slope of the risercenter line (25) to the center line (6) of the turbine, whereby (c) is a value between 1 - 15 degrees, typically 5 degrees or sufficient start to automatically raise the blade body as the fluid velocity decreases. Fig. 14 shows in section h - h the stud hub (7) designed as a circular typeHH-1134central hub with star-shaped support arms, which form a rigid and torsionally rigid supporting structure for the support arms with little fluid resistance during rotation. The stud arms can advantageously be designed with a wing-profiled cross-section (not shown).
Fig. 15 shows the turbine according to Fig. 14 in embodiment Idge (02). Vy k - k shows the position ofthe leaf attack (n) and describes its path from the infdlIda team shown in view h - h.
Thus, the support arms (24) are rotated in the center lines (25) of the arm roller bearings (26) until they reach the maximum distance from the line of rotation, which is limited by the length of the support arms (24) in the extended position. P.g.a. the rigidity of the integrated blade body, see claim 1, the carrier arms are prevented from shifting inboard without the helical angle of the blade bodyalso others. Fig. 14 shows that the pivot point (m) of the blade attack has been displaced outwardsat the second angle of rotation 60 degrees, whereby the lower and normal plane of the blade body has been displaced upwards while the upper and normal plane of the blade has been displaced downwards (not shown) so that the length of the blade body has decreased and diameter increased.
Fig. 16 shows a partial view of Fig. 2 and an enlargement of the generator is shown in views q - qhaving an existing gap (G) between the stator, which is constituted by the non-rotatable bearing housing (5) provided with copper winding (G1); and the rotor, which is constituted by the rotatable bearing housing (4) coated with permanent magnets (G2); said gap being small enough to be effective in generating electrical energy and saidpower cable (K) has sufficient rigid capacity to transmit electrical power. Fig. 16 showsin view p - p a principle sketch of a cross-section of the generator. The gap (G) is preferably smaller than 0.2% of the stator diameter.
Fig. 17 shows the invented turbine (1) with the carrier arms in the infant Idge (01) dal 'the structure (8) is fixedly connected to a power unit (28) designed as acylindrical rudder standing upright in a body of water (F2) in a hay, in a lake or an elf.
By way of example only, the rudder diameter may be 7 meters and its length below the water surface be 80 meters, with the blade body distance being 25 meters above the still water surface (marked with a triangle) and its MO 85 meters and width 42 meters. The power unit is firmly anchored with anchor lines (F3) in anchors (F4) on the seabed (F1) suspended at one point(F5) beldgen below the still water surface, and is provided with a power cable (K) suspended in apoint on the turbine or power unit above the still water line. The turbine (1) in Fig. 17 is thus always directed towards the fluid direction in question. The power unit is equipped with a solid ballast mass (MF) and a liquid ballast mass (MW) which providesHH-11required stability, and said cylindrical rudder is provided with a duct plate extending up the frail baseline (BL) and innumerable frail rotation line (3) in order to limit the vertical movements of the floating body resulting from waves and wind.
Fig. 18 shows the invented turbine in a turbine park (29) floating in a body of water (F2) ina hay, in a lake or an elf pa and limited to the area of the size of the floating body, firmly anchored with anchor lines (F3) in anchors (F4) on the seabed (F1) suspended at a point (F5) covered below the still water surface and provided with a power cable (K) suspended at a point on the turbine park (not shown in detail). The turbine park includes four turbines (30, 31)with a minimum separation distance (A), a first turbine (30) having a firstdistance (A1) and a second turbine (31) a second distance (A2) to the still water surface. For example, A can be equal to 100 meters, A1 can be equal to 30 meters and A2 equal to 50 meters. The power units are connected to each other via a pontoon (Si) immersed in the body of water provided with a baseline (BL) which is substantially parallel tothe still water surface, whereby each power unit has a duck part in common with twopontoons and two pontoons are connected to each other by an oblique pontoon (S2). Fig. 18 shows all four turbines (30, 31) comprising a blade body configured(3 + 3) xl with the bar arms in the recessed position (01) where the fluid direction (W) in question is pointing from the left. Section t - t shows a helicopter view of the turbine park withthe harmless horizontal spread (Yh ') of the wind shadow for the turbine located upstreamis dotted. Section s - s shows the corresponding vertical distribution (Yv ') of the wind shadow.
Fig. 19 shows the turbine park according to Fig. 18 with the turbine's bar arms in the outgoing position. As shown in Fig. 18 and Fig. 19 for a single fluid direction (W), the distribution of the wind shadow changes with the length and diameter of the leaf body; said that the horizontal spread(Yh ") akar with the diameter of the leaf body while the vertical spread (Yv")reduces. It should be obvious to a person skilled in the art that the shadow propagation (Yh) and (Yv) depends on the distance A, A1 and A2, the size and configuration of the blade body and the fluid direction, and that the efficiency of the turbine park can be optimized m.a.p. these quantities.

权利要求:
Claims (20)
[1]
HH-11 1 REQUIREMENT 1. A turbine (1) arranged for the production of usable energy from the motion of a flowing fluid (2) at a substantially perpendicular orientation of the rotation line (3) of the turbine towards the fluid direction (W) in question, comprising: a turbine roller bearing comprising a rotatable bearing housing (4) and a non-rotatable bearing housing (5), and having a center point and a center line which (6) passes through said center point, and at least one stand hub (7) arranged in fixed connection with the rotatable bearing housing, and a support structure (8) arranged in fixed connection with the non-rotatable bearing housing, and a blade body (9) completely or partially coated in the fluid and arranged in connection with the support hub, the movement of the fluid allowing rotation of the blade body about the line of rotation which (3) coincides with the center line (6) at a point identical to said center point, and comprises a plurality of rotor blades which (10) are each continuously extending axially and radially in a space spiral curve with helical axis in the line of rotation and having a twisting direction around the line of rotation and in the normal plane to the space spiral curve provided with a cross-section section provided with a center line (11) and having a wing profile (12) with two end portions, the first end portion having a rounded nose (N) the direction of rotation of the blade body (V) and the second end portion has a tip (S) in the opposite direction, the blade body having a diameter (D) and a center point (PM) at the point of intersection between the line of rotation and the center normal plane (M), characterized in that said rotor blade (10) have different twist directions around the line of rotation (3) and two named rotor blades (10) with different twist directions are connected to each other in at least one blade joint (13).
[2]
The turbine according to claim 1, characterized in that the turbine (1) has a point of intersection (PN) between the line of rotation (3) and a normal line to the line of rotation, and the blade joint (13) has a point of intersection (PB1) between the center line (11) in the first rotor blade (10) and said normal line and an HH-11 2 intersection point (PB2) between the center line (11) of the second rotor blade (10) and said normal line, the intersection points (PN, PB1, PB2) being connected by a common normal line ( 14) to the line of rotation and (14) are provided with an end point in (PN), the distance PN-PB1 being equal to the distance PN-PB2 and equal to the diameter (D) of the blade body (9).
[3]
The turbine according to claim 1, characterized in that the turbine (1) has a point of intersection (PN) between the line of rotation (3) and a normal line to the line of rotation, and the blade joint (13) has a point of intersection (PB1) between the center line (11) in the the first rotor blade (10) and said normal line and an intersection point (PB2) between the center line (11) of the second rotor blade (10) and said normal line, the intersection points (PN, PB1, PB2) being connected by a common normal line (14) to the rotation line and (14) is provided with an endpoint in (PN), the distance PN-PB1 is not equal to the distance PN-PB2.
[4]
The turbine according to claim 3, characterized in that a first blade joint (15) has a distance PN-PB1 which is greater than the distance PN-PB2 and that a second blade joint (16) has a distance PN-PB1 which is smaller than the distance PNPB2, wherein no blade joint (13) is coated between said first and second blade joints.
[5]
The turbine according to claim 4, characterized in that said first blade joint (15) has a first sum of the distance PN-PB1 and PN-PB2, and that said second blade joint (16) has a second sum of the distance PN-PB1 and PN-PB2, the first sum being equal to the second sum and equal to the diameter (D) of the leaf body (9).
[6]
The turbine according to claims 1-5, characterized in that the blade joint (13) comprises two blade struts which (17) are each provided with a cross-sectional section with a center line parallel to the center line (11) of the rotor blade, the cross-section section completely or partially enclosing the rotor blade. wing profile (12).
[7]
The turbine according to claim 6, characterized in that the blade joint comprises a rod joint which (18) connects two blade joints (17) in a blade joint (13) HH-11 3 to each other and is provided with a rod with a cross-sectional section with a center line (19), the center line (19) coinciding with the common normal line (14) of the blade joint (13).
[8]
The turbine according to claim 7, characterized in that the rod joint (18) comprises at least one rod roller bearing (T) provided with a center line coinciding with the center line (19) of the rod, the rod roller bearing allowing inboard rotation of the center lines (11) of the rotor blades about the common normal line (14) to the blade joint (13).
[9]
The turbine according to any one of the preceding claims, characterized in that said rotor blades (10) are made of polyolefin plastics such as polyethylene and polypropylene, or of polystyrene or of polyvinyl chloride or of metal such as aluminum, or in combination of two or more of said material.
[10]
The turbine according to claim 9, characterized in that said rotor blades (10) are produced in a manufacturing process by extrusion or co-extrusion.
[11]
The turbine according to claim 10, characterized in that the wing profile (12) of the rotor blade is bounded by a closed contour curve (KV) located in the normal plane to the center line (11) of the rotor blade and enclosing a surface provided with at least two section halls each (20) of a closed hdlrand curve (KS), the halrand curves (KS) not having an intersection point with the contour curve (KV) or each other.
[12]
The turbine according to claim 11, characterized in that the rotor blade (10) comprises at least one reinforcing element which (21) is provided with a cross-sectional section with a center line, the reinforcing element being located in at least one of the section members (20) and the center line of the reinforcing element being parallel to the center line of the rotor blade (11).
[13]
The turbine according to claim 11, characterized in that the rotor blade (11) has a first portion (B1) provided with a first end (22) and a second portion (B2) provided with a second end (23), wherein the rotor blade and the ram the ends together HH-11 4 forms a body with a closed blade surface which delimits the body towards the surrounding mil * (E).
[14]
The turbine according to claims 6 and 12, characterized in that at least one blade overhang (17) or reinforcing element (21) therefrom made of composite material containing fibers of glass, carbon or Kevlar enclosed in synthetic polymeric material.
[15]
The turbine according to any of the preceding claims, characterized in that the connection of the blade body to the support hub (7) comprises at least one bar arm which (24) comprises a blade cover (17) connected to the bar arm and is rotatable about a straight center line (25) passing through at least two arm roller bearings (26) each provided with a bearing housing fixedly connected to the support hub (7), the center line (25) being parallel to the center line (6) of the turbine roller bearing and the vane blade cover (17) being fixedly connected to a duct portion of a rotor blade (10) .
[16]
The turbine according to claim 15, characterized in that the center line (25) of the arm roller bearings has an intersection point with the center line (6) of the turbine bearing.
[17]
The turbine according to claim 1, characterized in that the turbine comprises a generator (27) for converting the kinetic energy of the turbine (1) into electrical energy, the non-rotatable bearing housing (5) or the support structure (8) constituting the stator and the rotatable bearing housing ( 4) or the stud hub (7) forms the rotor.
[18]
A method of controlling the size of a blade body (9) of the device according to claims 1 - 17 by means of a displacing means comprising a rod joint (18) arranged to rotate the center lines (11) of the rotor blades about a common normal line (14) to the line of rotation ( 3) and a bar arm (24) arranged for rotation about a center line (25) by at least two arm roller bearings (26) connected to a stand hub (7), said displacement means being arranged to simultaneously increase the length (L) and reduce the diameter ( D) of the blade body (9), or vice versa, said method comprising the steps of: providing an angular velocity of the turbine (1); HH-11 causing said support arm (24) to be arranged in a first position (01), said first position corresponding to a first helical angle (y1) of the blade body (9); causing said support arm (24) to be arranged in a second position (02), said second position corresponding to a second helical angle (y2) of the blade body (9), wherein (y2) is not equal to (y1).
[19]
Use of the device according to claims 1 - 17 and execution of the control according to claim 18 in a power unit which (28) is arranged solid in ground (F1) or floating in a body of water (F2) for generating electrical or mechanical or visual power or a combination of two or more of said effects, wherein a support structure (8) is arranged in fixed connection to said power unit.
[20]
The use and design according to claim 20 in a turbine park (29) comprising at least two power units (28) each of which is provided with a turbine (1) with a vertical center line (6) and having a horizontal separation distance (A) between the center points to the roller bearings of a first (30) and second (31) turbine at the projection network of a common horizontal plane, the minimum separation distance of the turbine park exceeding the length of half the mean and being less than four times the mean of the blade body diameter (D) of said first and second turbines. HH-111/1 10-H2 M2 13 -H3 -V3 2 --- ------- / -V2 -V1 / ,, e. , / 7, i'N '"' ../A / ..- 1 ..- ---., / ..... i. ------ ..4. '- -`, = - 77.., - „:. ----- '-' ,. v - ,, i, ..- ,,, / /,, ... -..... i , '. .- = .. --- 7 —---- e - 4 • - 4- -H1

类似技术:

---

公开号 | 公开日 | 专利标题

---

SE1330093A1|2015-01-24|End-mounted spiral rotor

---

US8497594B2|2013-07-30|Horizontal-axis hydrokinetic water turbine system

---

US8525363B2|2013-09-03|Horizontal-axis hydrokinetic water turbine system

---

JP5466649B2|2014-04-09|Turbine engine with cross-flow hydro turbine to reduce total lift

---

CN104520579A|2015-04-15|Spiral screw fluid turbine having axial void

---

US20110027084A1|2011-02-03|Novel turbine and blades

---

ES2771523T3|2020-07-06|Floating wind turbine with twin vertical axis turbines with improved performance

---

US20070048137A1|2007-03-01|Wind turbine and energy distribution system

---

ES2626450T5|2021-03-29|Coupled blade wind turbine rotor

---

RU2461731C2|2012-09-20|Hydraulic turbine

---

ES2748702T3|2020-03-17|Rotor blade for wind turbine

---

Bøckmann et al.2014|Experiments with actively pitch-controlled and spring-loaded oscillating foils

---

US9777709B2|2017-10-03|Translating foil system for harvesting kinetic energy from wind and flowing water

---

EA023602B1|2016-06-30|Wind/water turbine with rotational resistance reduced due to wind vane blades

---

US20150337794A1|2015-11-26|Turbine with helical blades

---

EP3514372A1|2019-07-24|Shielding blade supporting piece type vertical axis wind turbine

---

US10151294B2|2018-12-11|Buoyant housing device enabling large-scale power extraction from fluid current

---

CN203175763U|2013-09-04|Sail-type wind driven generator for land and water

---

EP2937557A1|2015-10-28|Wind wheel |

---

CN106489024A|2017-03-08|Wave energy converter

---

US20120134823A1|2012-05-31|Wind Turbine

---

CN202273812U|2012-06-13|Device used for wind power or hydraulic power generation

---

WO2014174327A2|2014-10-30|Turbine with moving-self adjusting blades for conversion of the kinetic energy of fluids to mechanical-rotational and electric

---

SE0950727A1|2011-04-03|Wind turbine with turbine blade

---

US20110070083A1|2011-03-24|Streamlined Wind Turbine Optimized for Laminar Layer

同族专利:

---

公开号 | 公开日

---

US20160160650A1|2016-06-09|

---

US9957803B2|2018-05-01|

---

EP3025055A4|2017-08-16|

---

EP3025055B1|2019-08-28|

---

EP3025055A1|2016-06-01|

---

WO2015012752A9|2015-10-08|

---

WO2015012752A1|2015-01-29|

---

SE539772C2|2017-11-28|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US1851680A|1930-06-23|1932-03-29|Robert H Morris|Hydraulic water motor|

---

FR2424470A1|1978-04-26|1979-11-23|Amf Inc|Stiff structures moulded with tubular and cellular cores - for skis, wings etc. of high specific stiffness|

---

SU1150395A1|1983-01-17|1985-04-15|Научно-Исследовательский Сектор Всесоюзного Ордена Ленина Проектно-Изыскательского И Научно-Исследовательского Института "Гидропроект" Им.С.Я.Жука|Vertical axle wind wheel|

---

JPS6357874A|1986-08-29|1988-03-12|Kusuo Matsuo|Structure and use for spiral windmill and spiral water turbine|

---

KR100874046B1|1999-12-29|2008-12-12|쥐씨케이 테크놀로지, 인코포레이티드|Turbine for free flowing water|

---

RU2330791C2|2006-03-28|2008-08-10|Закрытое акционерное общество "Авиастроительная корпорация " Русич"|Shpadi propeller and development of its blades|

---

KR100774309B1|2006-11-28|2007-11-08|한국해양연구원|Power genaration system using helical turbine|

---

DE202008005724U1|2007-04-27|2008-09-18|Wasser- und Elektrizitätswerk der Gemeinde Buchs|Axial flowed through wind turbine|

---

US7741729B2|2008-10-15|2010-06-22|Victor Lyatkher|Non-vibrating units for conversion of fluid stream energy|

---

US8061993B2|2009-05-04|2011-11-22|Seab Energy Ltd.|Vertical axis turbine|

---

US20110027084A1|2009-07-31|2011-02-03|Andrew Rekret|Novel turbine and blades|

---

US20120128500A1|2010-04-14|2012-05-24|Arcjet Holdings Llc|Turbines|

---

EP2823181B1|2012-03-06|2016-10-26|Axis Energy Group Pty Ltd|Cross flow turbine with straight vertical and helical slanted blades|CA2932373A1|2013-12-18|2015-06-25|Altin PUPULEKU|Crossflow axes rotary mechanical devices with dynamic increased swept area|

---

US10167847B2|2016-03-24|2019-01-01|Per Mellin|Vertical axle or axis helically swept blade wind turbine|

---

CN106368897A|2016-10-11|2017-02-01|西华大学|Wind power generation device and wind wheel thereof|

---

US10605227B2|2017-04-12|2020-03-31|General Electric Company|Segmented wind turbine rotor blade with welded joint|

---

US10844835B2|2017-06-30|2020-11-24|National Research Council Of Canada|Offset perpendicular axis turbine|

---

GB2583204A|2017-10-25|2020-10-21|10X Tech Llc|Rigid polymeric blade for a wind turbine and method and apparatus to manufacture same|

---

GB2585061B|2019-06-27|2021-10-06|Samuel Ogden James|A hydropower energy generating device|

法律状态:

优先权:

---

申请号 | 申请日 | 专利标题

---

SE1330093A|SE539772C2|2013-07-23|2013-07-23|End-mounted spiral rotor|SE1330093A| SE539772C2|2013-07-23|2013-07-23|End-mounted spiral rotor|

---

US14/907,527| US9957803B2|2013-07-23|2014-07-21|End supported helical turbine|

---

PCT/SE2014/000101| WO2015012752A1|2013-07-23|2014-07-21|End supported helical turbine|

---

EP14829963.9A| EP3025055B1|2013-07-23|2014-07-21|End supported helical turbine|