KR100874046B1 - Turbine for free flowing water - Google Patents

Abstract

It can be rotated unidirectionally under a switchable fluid flow with a winged blade blade with a bladed spiral blade that flows in the axial direction and converts some of the energy from the fluid into rotational energy to increase the efficiency of the turbine. Improved recoil turbine. Converting axial flow into rotational energy allows the spiral blades of the turbine to have a larger twist angle and the turbine itself to have a ratio of length to smaller diameter, making the turbine smaller without compromising efficiency.

Description

TURBINE FOR FREE FLOWING WATER}

The present invention relates generally to turbines, in particular turbines capable of unidirectional rotation under multidirectional fluid flows for use in pneumatic, hydro, wind or wave power systems.

Unidirectional turbines are turbines that can provide unidirectional rotation from bidirectional or reversible fluid flow or changing wind direction, such as at the tail of a tidal wave. In general, five basic types are known: the Wells turbine, the McCormick turbine, the Darrieus turbine, Goldberg turbine, and the Gorlov turbine. )to be.

The wells turbine is a propeller-type turbine having a series of airfoil-shaped blades arranged to extend concentrically from the rotating shaft. In general, turbines are installed in channels that direct fluid flow in a straight line along a rotating shaft axis. The blade extends radially from the rotating shaft and is mounted to rotate in a plane perpendicular to the fluid flow direction. Regardless of the direction in which the fluid flows, the blades rotate in the direction of the leading edge of the vane.

Wells turbines can rotate at high speeds. The outer ends of these blades move fast enough than flowing air, producing significant noise. The efficiency of the wells turbine is reduced because the effective surface area of the blade is limited to the outer tip. Such blades cannot obtain a sufficient amount of available energy in the fluid flowing close to the shaft.

McCormick turbines use a series of V-shaped rotor blades mounted concentrically between two sets of stator blades. The rotor blades are installed for rotation in a plane perpendicular to the fluid flow direction. The fixed blade directs fluid flow to the rotor blades. The outer fixed blade is open to the fluid flowing from one direction to achieve unidirectional rotation with bidirectional fluid flow, while the inner fixed blade is open to the fluid flowing from the opposite direction.

McCormick turbines are quieter than wells turbines. But too slow for the direct operation of the generator. McCormick turbines are complex and expensive to manufacture.

Darius turbines are reaction turbines with straight blade-shaped blades oriented transverse to the fluid stream and parallel to the axis of rotation. The blade may be attached to the shaft with circumferential end plates, struts or other known structures. In some variations, the blade is bent and attached to the end of the shaft. A Darius reactionary turbine with a series of right angle blades, mounted either perpendicularly or horizontally in a rectangular channel, is placed directly in the flowing body of water for exploitation of hydropower. Darius turbines rotate with strong pulsations due to the acceleration of the blades through the high pressure zones of the fluid. This powerful pulsation reduces the efficiency of the Darius turbine.

Goldberg turbines described in US Pat. No. 5,405,246, referenced in the description and drawings, and Goldberg turbines described in US Pat. No. 5,642,894, referenced in the description and drawings, use twisted blades or helical blades. The torque in the orientation of the blades used in such a turbine can be generated from water or air that impacts the blade in the transverse direction (perpendicular to the axis of rotation of the turbine).

Some of the water or air impacting the helical blade in the transverse direction is deflected in the axial direction. This axial flow stresses turbines, especially turbine bearings, and must be replaced after a short period of time. Although Goldberg and Golov turbines are an improvement over previous designs, neither of these turbines effectively utilize axially deflected flow.

The present invention is a fluid that is generally switchable using an annular radial blade together with an annular spiral blade or other twisted blade that converts a portion of the fluid flow energy into rotational energy in the axial direction to increase the efficiency of the turbine. Provided is an improved turbine capable of rotating in one direction under flow. Converting the deflected axial flow into rotational energy results in a larger torsional angle of the helical blade of the turbine and smaller than the ratio of the length to the diameter of the turbine, allowing the turbine to become smaller without compromising efficiency.

1 is a front left perspective view of one embodiment of the present invention;                 

2 is a front left perspective view of one embodiment of a turbine of the present invention showing a generally axially deflected transverse fluid flow;

3A is a cross-sectional perspective view of one embodiment of the present invention showing twisted blades and radial blades.

3B is a top view of one embodiment of the present invention showing deflected fluid flow in twisted and radial blades.

3C is a front view of one embodiment of the present invention showing deflected fluid flow in twisted and radial blades.

4 shows an embodiment of the invention showing twisted and radial blades and involving shearing and rotation.

FIG. 5 is a side view of one embodiment of the present invention showing an O-surface and angle of attack with respect to the placement of the twisted blades. FIG.

FIG. 6 is a perspective view of one embodiment of the present invention showing the design of a twisted blade and with turbine contour by O-curve, B-curve and O-surface. FIG.

FIG. 7 is a side view of one embodiment showing the curvature orientation of a turbine caused by rotation of an O-curve about an axis of rotation. FIG.

8 is a perspective view of one embodiment of a turbine of the present invention having a barrel shaped outline.

9 is a side view of one embodiment of the present invention in which a radial blade is used as the blade support member.

* Code Description *

10 turbine 12 rotating member

14 rotation axis 16 blade support member

18: twisted turbine blade 20: radial turbine blade

20L: leading edge 20T: trailing edge

20A: wing cross section 34,40: O-surface

36: O-curve 38: B-curve

44 barrel turbine 46 cylinder turbine

50: transverse fluid flow 65: axial flow

The present invention is a reaction turbine capable of unidirectional rotation under switchable fluid flow. Some preferred embodiments are shown in the drawings. Other embodiments consistent with the claims can be seen by the present invention.

In one embodiment, the turbine 10 extracts rotational energy from the kinetic energy of the incoming transverse fluid flow 50, which is generally a transversal flow deflected in the axial direction 60 and generally the axial flow 65. Use the features of the combination. Referring to FIG. 1, the recoil turbine 10 consists of a rotating member 12, a blade support member 16, a twist turbine blade 18 and a radial turbine blade 20.

Rotating member 12 can engage engagement member 12A to form a rotating shaft 14 that turbine 10 rotates in a unidirectional manner. The support member 12A may also be any structure capable of fixing the position of the rotation member 12 while allowing free rotation about the rotation axis 14. The rotating member may be any device that can rotate smoothly. For example, it is also possible to use a rotating hub having a bearing (not shown) that allows smooth rotation.

Generally attached at right angles to the rotating member 12 is one or more blade support members 16 that rotate in a plane perpendicular to the rotating member 12 together with the rotating member. Rotating member 12 is a shaft of a generator (not shown) that converts rotational energy of the turbine into electrical energy by means of a gearbox or other torque generating device, or other power available by the present invention. It is preferred to be coupled to the device.

Although not necessary to rotate around the axis of rotation 14, a twist turbine blade 18 having a wing section 18A is preferably attached to the blade support member 16. In some embodiments, a single blade support member 16 may be used. The twisted blade 18 has a leading edge 18L and a trailing edge 18T at its cross section. The cross section of the twisted blades is oriented such that the airfoil profile of the twisted blades 18 is in a plane parallel to the transverse fluid flow 50 component of the fluid flow. With the varying orientation of the twisted blades, the twisted blades can provide different faces to the transverse fluid at any given time in rotation. The twist blades 18 are designed to generate a constant torque from the turbine 10 in the unidirectional orientation 70 when the turbine is in transverse fluid flow regardless of the angular position of the turbine 10 relative to the fluid flow.
6 and 7, by rotating a planar curve, such as O-curve 36, about an axis of rotation 14 in the same plane, an axially symmetrical O-surface 34 can be obtained. The O-surface 34 defines the overall shape and dimensions of the turbine 10. The design of the present invention provides several shapes and dimensions of the turbine 10. For example, a small O-curve curvature allows the barrel turbine 44 to be made, a straight line parallel to the axis of rotation results in a cylindrical turbine 46, and an O-curve that intersects the axis of rotation 14 is elliptical or spherical. Create a turbine 48.

The design of the twisted blades 18 is made to create a B-curve 38 on the O-surface 34. The B-curve is defined as the angle (Ω) 32 which is unchanged and exists between the two tangents. The first tangent abuts the B-curve itself and the second tangent abuts the O-curve 36 at the intersection. Angle (Ω) 32 is constant or varies with the length of B-curve 38. The B-curve forms the long axis of each twist blade 18, and a constant angle Ω provides the cylindrical turbine 10. The centers of weight or pressure of the twisted blade vane section 18A are shown as B-curves. The cross-sections are oriented such that the long axis is in tangential to the circumference of the intersection of the O-surface 40 and in a plane perpendicular to the turbine axis of rotation 14.

The present invention allows a small angle of attack (alpha) between the long axis of the wing section 18A and the tangent to the circumference. Thus, each portion of the twisted blade 18 has different shear and rotational forces as compared to straight blades (not shown) having the same cross section, as shown in FIGS. 4, 5, 8.

6, 7 and 8, the turbine 10 of the present invention comprises n blades that are uniformly distributed such that the turbine 10 has axial symmetry of the nth order, the number being equal to two. Or more (n≥2). If the O-surface 34 forms a cylinder 48, the geometry and angle Ω of the twisted blade vanes is preferably constant along the length of the twisted blade 18. In this embodiment, the length to radial ratio is such that the 2π / n rotation of the turbine arranges the cross section imprint from one end to the other end of the twisted blade 18 of the cross section imprint, and the torque is the turbine. It is constant regardless of each position of (10). In this embodiment, the constant angle Ω is chosen to provide such symmetry or to minimize the asymmetry. If other O-surface or spheroid 46 or barrel 44 shapes are used, the constant torque state will change the vane-shaped cross section 18A and the angle Ω 32 of the twisted blade 18. You can get close.

In addition to generating torque from the sectional fluid flow 50, the twisted blades 18 are partially sectional fluid flows that are generally axially deflected as shown in FIGS. 2, 3A, 3B, 3C, 4 and 9. Produce 50. The present invention may utilize a generally axial 60 flow or any axial flow deflected to increase the rotational energy and overall efficiency of the turbine 10. This consists of a generally radial blade 20 attached to the twisted blade 18. This cross section of the radial blade 20 is preferably substantially perpendicular to the axis of rotation 14 of the turbine and is generally coaxial in flows 60, 65, whether or not deflected by the rotational energy by the twisted blade 18. The partial kinetic energy of the flowing fluid can be diverted.

2 and 3, the radial blade 20 of the present invention has a wing having a leading edge 20L and a trailing edge 20T that generate greater rotational energy than when the radial blade 20 is flat. It has a cross section 20A. The wing cross section 20A of the radial blade 20 may be symmetrical (teardrop shaped) or asymmetrical in the major axis. In one embodiment of the invention, the leading edge 20L of the radial blades is directed in the same direction as the leading edge 18L of the twisted blades 18. The radial blades 20 may or may not protrude from one or both of the inner and outer surfaces 90 and 80 of the twisted blades 18, and may be evenly or unevenly distributed along the twisted blades 18. have. The preferred distribution of the radial blades 20 is subject to the twist angle and the relative size of the twist blades 18 as will be described below.

The deflected flow in the axial direction 60 created by the twisted blades 18 also causes a first axial force in the first direction to act on the rotating member 12. The radial blade 20 may be designed with an asymmetrical cross section such that a second axial force is generated in the second opposite direction. This feature of the invention is useful for sustaining the elasticity of turbine bearings (not shown) when the rotating member 12 used is a hub having bearings.

In one embodiment of the invention, the blade support member 16 is an extended radial blade 20. In the present invention, by using the extended radial blade 20 for coupling the twisting blade 18 to the rotating member 12, the radial blade is distributed along both ends of the turbine 10. This radial member supports the twist blade 18 and also converts a portion of the kinetic energy of the fluid flowing in the coaxial direction 60, 65, whether or not deflected by the rotational energy by the twist blade 18. Can increase the efficiency.

In one embodiment of the present invention, the rotation is constant by being provided with a variable size of twisted blade cross-section 18A. The cross section of the twist blades adjacent to the axis of rotation of the turbine can be increased. The thickness of the cross-sections of the twisted blades 18 proximate to the axis of rotation 14 may be wider. Thus, the pulling force of the twisted blades 18 increases because the cross-sectional area increases, compensating for low linear speeds and axial spacings and generally leading to small torques. This embodiment of the present invention provides the generated torque separately from each position of the turbine 10. This innovation is useful for the turbine 10 in which the twist blade 18 of the turbine 10 is bent, in particular the twist blade 18 causing the turbine to be barrel-oriented.

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With the turbine 10 of the invention, which is transverse 50 and generally uses axial flows 60, 65, the overall efficiency of the turbine 10 is greater than the turbine which does not have the advantages of the invention. The larger the angle Ω or twist angle 32 is, the greater the deflection of the transverse flow. Thus, the turbine 10 of the present invention has a large angle (Ω) 32 that fits the twisted blade 18 due to the ability of the radial blade 20 to use a transverse flow deflected in the axial direction 60. For example, in one embodiment, this angle (Ω) 32 is greater than the optimum angle (about 32 °) for the helical blade of the golov turbine described above. In addition, the turbine with the radial blade of the present invention can be smaller than a conventional golov turbine while applying the same rotational energy. The present invention provides the same efficiency as a golov turbine but with a shorter ratio of length to diameter.

With reference to FIG. 9, a ring shaped region of transverse flow deflected in axial direction 60 is shown. This deflected axial flow is caused by the angle Ω at which the twisted blades draw the cross flow 50.

The radial blades are preferably spaced sufficiently apart from each other in the twisted blades so as not to interfere with each other's fluid flow. Depending on the size and shape of the radial blades and the twisting of the twisted blades, an optimal number of blades are optimally arranged and spaced apart on each twisted blade. The optimal spacing and arrangement of the radial blades requires knowledge of the direction and type of fluid flow that the turbine is expected to experience.

If the curve of the radial blades in contact with the actual fluid flow is appropriate, then normal axial fluid flow, and also axial fluid flow parallel to the axis of rotation of the axial turbine, may generate rotational energy from interaction with the radial blades. The original transversely moving fluid, which is deflected by the twisted blades and moves "down" in the inclined plane of the twisted blades, contains both axial and transverse forces. The radial blades are placed and sized in the twisted blades to convert some of the transverse components into rotational energy. Radial blades are thus more efficient at converting transverse fluid flow into rotational energy through the turbine and more efficiently at other angles through the turbine.

Radial blades have a geometric structure and spacing that are aligned from a fish such as a radial blade about 1 centimeter high and a large radial blade and about 1 centimeter apart from the given twisted blade by as little as two radial blades. It is arranged to allow the axial 60 flow energy to be converted into rotational energy with which the radial blades are sized. It is not necessary for each twisted blade to have a radial blade, or since there is no long rotational imbalance, it is not necessary to place or align the radial blades of each twisted blade to be the same on all twisted blades of the turbine. However, it is desirable that the number of blades of each twisted blade is two or more and the turbine is uniformly distributed such that it has n-axis symmetry. For balance the radial blades must be secured to at least one twisted blade.

Detailed embodiments of the invention are disclosed herein as required; However, it is to be understood that the disclosed embodiments are merely illustrative of the invention, which may be embodied in various alternative forms. The drawings are not necessarily to scale, some drawings being exaggerated or minimized to show details of particular components. Accordingly, the specific structural and functional details disclosed herein are not to be understood as limiting, but merely as a basis for claiming and as a basis for teaching those skilled in the various uses of the invention.

The elements may also be specified "in combination"; Such predicates may be other components that are spaced apart between certain elements and are considered to be elements that are connected so that highly detailed elements can be connected in a fixed or movable relationship with one another. The term "in combination" should be contrasted with the use of "direct" linkage, which is a predicate indicating a fixed or movable relationship or combination with respect to each other that do not have other components located apart from each other. Certain structural relationships or orientations may also be indicated by the word "virtually." In such cases, the relationship or orientation is described within variations that do not affect the described component or cooperation of components.

Although the present invention has been described with reference to specific embodiments, the description is not to be taken in a limiting sense. On the contrary, those skilled in the art may make various modifications to the disclosed embodiments with reference to the detailed description of the present invention. Accordingly, the appended claims are intended to cover such modifications, alternatives and equivalents within the spirit and scope of the invention.

Claims (9)

A recoil turbine for mounting to a support member that can rotate unidirectionally under a reversible fluid flow, A rotating member defining a rotating shaft for the turbine and being able to engage with the support member; A plurality of blade support members attached at right angles to the rotating member for rotating together in a plane perpendicular to the rotating member; A plurality of twisted turbine blades attached to the blade support member to rotate about a rotational axis of the turbine, The plurality of twisted blades have a wing-shaped cross section consisting of a leading edge and a trailing edge, wherein the blade-shaped shape is located in a plane parallel to the transverse fluid flow component of the fluid flow; And a plurality of radial turbine blades attached to the plurality of twisted blades, each having a wing-shaped cross section, the cross section of the radial blade being perpendicular to the axis of rotation. And converting a part of the kinetic energy of the fluid flowing in the axial direction from the rotating member to the rotating energy. The turbine according to claim 1, wherein the blade-shaped cross section of the radial blade is symmetrical with its long axis. 2. The turbine of claim 1 wherein the plurality of radial blades have a leading edge and a trailing edge, wherein the leading edge faces the same direction as the leading edge of the twisted blade. The turbine according to claim 1, wherein the blade support member has a wing-shaped cross section, and the blade-shaped blade support member connects the twist blade to the rotating member. 2. The turbine of claim 1 wherein the thickness of some cross sections of the twisted blades proximate to the axis of rotation of the turbine can be increased. delete delete The turbine of claim 1, wherein the plurality of radial turbine blades are uniformly distributed and attached along the plurality of twisted turbine blades to achieve axial symmetry to the turbine. A recoil turbine for mounting on a support member capable of unidirectional rotation under a switchable fluid stream, A rotating member which forms a rotating shaft of the turbine and can be engaged with the support member; A plurality of blade support members attached in a direction perpendicular to the rotating member for rotating together in a plane perpendicular to the rotating member; It comprises a plurality of twisted turbine blades attached to the blade support member for rotating around the axis of rotation of the turbine, The plurality of twisted blades have a wing-shaped cross section consisting of a leading edge and a trailing edge, wherein the blade-shaped shape is located in a plane parallel to the transverse fluid flow component of the fluid flow; The twist blade has a larger twist angle than the golov turbine, and the turbine has a ratio of length to diameter smaller than a turbine without a radial blade; Each radial blade of twisted blade has a wing-shaped cross section, A number of radial turbine blades are attached to each of the twisted turbine blades, Many radial blades have a leading edge and a trailing edge, the leading edge of the radial blades facing the same direction as the leading edge of the twisted blades, The radial blades convert a portion of the kinetic energy of the fluid flowing in the axial direction from the rotating member to rotational energy, Radial blades are used as some blade support members, which radial blades connect the twisted blades to the rotating member and also support the twisted blades, thereby converting energy from the fluid flow into the rotating energy in the rotating member. A recoil turbine, characterized in that for switching.

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