KR890002952B1 - Apparatus for producing force of moving fluid - Google Patents

Abstract

An elongated body has a rounded and symmetrical profile. The profile defines a rounded and elongated leading portion (110a) whose thickness increases from the front to the rear and a rounded trailing portion (110b) whose thickness decreases. The maximum thickness of the profile is between 50 and 100% of its length in the direction defined by its axis of symmetry. The trailing portion has a section formed by a circular arc smaller than a halfcircle. The remainder of the profile has a shape smoothly joined to the circular arc. The system sucks the fluid into the body in an area located on a first side of the profile toward which the force is to be produced.

Description

A device that generates a force in a fluid

The device located in FIG. 1 or at a point M and moving in an arbitrary angle α with respect to the wind direction generates a lateral driving force P and a direction force R under the wind speed V, thereby generating a driving force T accordingly. Vector diagram showing having.

2a is a flow diagram around a circular body to illustrate the principles of the present invention.

2B and 2C are schematic cross-sectional views of hollow bodies showing various ways of separating oil into an outer surface (downstream of the wind) and an inner surface (upstream of the wind).

3 is a cross-sectional view of an embodiment of a prior application of the present invention.

4a to 4d show various modifications of the suction device used in various embodiments of the present invention.

5a-5c show various variations of a deflector flap arrangement in an embodiment of the invention.

6 is a cross-sectional view of another embodiment of the sexual application having a device for reversing driving force.

7 is a cross-sectional view showing the shape of a profile that has been improved for use in accordance with the prior invention.

8 is a cross-sectional view showing the shape of a further improved profile for use in the present invention.

9 is a graph obtained from a boat test or a wind tunnel test showing efficiency factors for various profile shapes.

The present invention relates to a novel apparatus for generating an effective force from a flowing fluid. In particular, the present invention relates to an active device which is located in a flowing fluid (eg air or water) to effectively generate maximum propulsion for the required energy consumption.

The present invention, in a preferred embodiment in the marine field, serves to achieve conservation of energy resources by generating propulsion of the ship by wind, assisting or replacing other energy consumption propulsion devices of the ship. However, the present invention may also be used in other fields and applications, such as in land or ice vehicles, windmills, turbines or hydro or wind generators.

The present invention is an improvement of the invention of Korean Patent Application No. 4742/1981, filed on November 30, 1981, entitled "A device for generating lift in a fluid." For clarity of understanding, the present invention further describes the principles and structures of the foregoing prior applications.

Conventionally known sails (passive devices) for propelling ships are limited in practical use because the force generated by the wind requires the use of large area sails in which the sails are proportional to the area. Although many efforts have been attempted to make active devices such as continuous rotating cylinders practical, using the Magnus effect as described in US Pat. In addition to the high energy consumption of the device, the mechanism has to be complicated because the cylinder must be continuously rotated at several hundred rpm per minute to generate the desired propulsion force. In addition, such a device must stop and reverse the cylinder when changing the direction, and is subject to operational limitations.

In particular, the present invention and the preceding Korean patent application are an improvement of the "wind power motor" described in US Patent No. 2,713,392, which was granted to von Carman et al. On July 19, 1955, and greatly improved the effective output. In addition, it significantly increased the energy efficiency with respect to the energy consumed to obtain its useful output.

In general, the present invention and the preceding invention use a tubular column or a hollow but variable directional changeable shape of the cylinder, in which a particular cross-sectional shape (ie, profile) is desired. The hollow body has a specially shaped fluid permeable zone (eg a hole) through which the fluid is aspirated by a suitable fan or suction device. Adjustable control vanes or flaps provide additional parameters that greatly improve the output ratio to input energy and provide flexibility in the operation of the device.

To better understand the present invention, the basic principles are described below with reference to the accompanying Figure 1, which illustrates certain principles upon which the present invention is based.

The accompanying FIG. 1 shows that a device, such as a sail on a ship, is located at a point M in a fluid (such as air) flowing at a relative speed V with respect thereto and subjected to a force F. FIG. This force F can be decomposed into a driving force P perpendicular to the fluid velocity vector V and a directivity R in the same direction as the velocity vector V. FIG. At this point, when the device moves in the direction of forming an angle α with respect to the velocity vector V at the point A, the device receives a driving force T corresponding to the projection of the driving force F in the direction A. do. Therefore, when the angle of incidence α between the wind direction and the ship route is smaller than 90 ° C., the driving force T increases as the driving force P increases and the direction force R decreases.

In general, the driving force and the drag force are represented by dimensionless coefficients Cz and Cx as shown in the following equation.

Where P is the driving force (equivalent to the aerodynamic lift), R is the drag, P is the density of the fluid, V is the velocity of the fluid, and S is the area of the device projected on a plane perpendicular to the direction of fluid movement (V). Cz and Cx are known lift coefficients (C _L ) and drag coefficients (C _D ) in air foils.

From the above equation, it can be seen that the driving force (T) can be expressed by the following equation.

This equation indicates that the larger the enemy of S and C _Z with respect to the predetermined fluid velocity V and the predetermined direction α of the driving force T, the larger the driving force.

When these results are applied to conventional devices (e.g. wings of airplanes, sails of ships, wings of windmills) that can generate driving forces without supplying energy from the outside, the coefficient Cz is always lower than 1.7. For a wing with a flap, it is 2.2, and for a hypersustaination device it is 2.7. As can be seen from this, in order to generate a large propulsion force T, a surface that is too large and difficult to handle in actual use is required.

It is known to generate a very high driving force P or a drag coefficient Cz by using an externally energized active device. That is, as described in the above-described flattener patent, when rotating a circular cylinder located in a flowing fluid around its own axis, a so-called Magnus effect causes a deflection of the fluid flow, whereby the speed of the cylinder A large force in a predetermined direction along the and directions can be generated in the cylinder. Rotation of the cylinder also delays and reduces the separation of fluid flow from the cylinder surface, and hence the occurrence of turbulence.

However, although it is possible to generate a high value coefficient Cz by the Magnus effect, a fairly complex mechanical structure and large power are required to obtain the circumferential rotational speed of the cylinder required for it to be possible. In order to be sufficient for the propulsion of relatively small vessels (i.e. 30 m length of the ship), it is necessary to recall that the dimensions of the cylinders should be, for example, 3 meters in diameter and 15 meters in height. This mechanical complexity is especially related to vibrations, gyroscopic effects, etc., caused by the rotation of the cylinder, which can reach up to 400 r · p.m at high wind speeds. In addition, when applying this configuration to the propulsion of the boat or ship, it is necessary to reverse the direction of rotation of the cylinder, in order to reverse the direction of the propulsion force, which can be seen that it takes a long time due to the large inertia of the cylinder. .

In order to remedy some of these drawbacks, in 1955 von Carman, U.S. Patent No. 2,713,392, a propulsion stationary vertical circular cylinder provided on a ship was allowed to penetrate the air, by sucking air into the cylinder. It keeps the air flowing around the cylinder surface. Separate air flows around the cylinders have different lengths of paths by means of short deflectors, thus causing lateral forces on the cylinders. However, this structure failed to obtain a coefficient Cz value of about 2.4 or more in wind tunnel tests in France about 20 years ago, making it impractical. A similar principle was theoretically proposed in British Patent No. 222,845 to N. V. Institue Bour Aero-en-Hydrodynamic, dated May 7, 1925, but failed to become a practical structure.

The object of the invention and the invention of the Republic of Korea patent application is considerably without the drawbacks of prior art devices such as rotating circular cylinders using the Magnus effect, while having a coefficient (Cz) value of 5 to 8 with minimum energy supply from the outside. It is to provide an active device that generates a large driving force.

Needless to say, the device according to the invention can be used in a variety of applications, such as the propulsion of an automatic body, such as a ship, or the production of useful mechanical energy from the flow of a fluid, for example, which can be converted into electrical energy by a generator. have. With the present invention, it is possible to benefit from the present invention not only from wind energy, but also from any fluid induction, such as the flow of fluid in streams, currents, tides or turbines. Although applicable to other fluids besides such air, the present invention is particularly described with respect to the flow of air (wind) in which the driving force corresponds to the lift force of the afoil.

The present invention does not use the basic physical principles that correspond to some of the principles contained in the aerodynamics of airplane airfoils (ie, airplane wings or helicopter wings), but in the present invention, the conditions under which the principles are used are Is quite different. The present invention is particularly used for low flow rates of 50 knots or less, while airplane airfoils are used at higher speeds. Also in airfoils it is primarily a matter of maximum lift and the problem of energy saving is essentially ignored. In contrast, in the case of the present invention, energy saving is a major concern, generating the maximum driving force for the consumed energy. In addition, the design of the airfoil is related to the factor of the force, and many efforts have been made to optimize the ratio of the force coefficient (C _L or Cz) to the force coefficient (C _D or Cx). In contrast, in the present invention, in particular when applied to ships, the heading is not so important because the resistance to the hull passing through the water far exceeds the heading of the fluid on the propulsion system.

In the case of an airfoil, the lift coefficient during normal operation is in the range of 0.2 to 0.3, which increases to 0.2 to 0.3 when the flap is unfolded during landing. The coefficient of gravity Cx is about 0.1, and the ratio of Cz is moderately high.

In contrast, the present invention and the invention of the prior application provide Cz values of 5 to 8 as an indication of the driving force achieved. The effect on the energy consumed in converting the fluid flow into driving force is measured and expressed as an energy factor (CA). This is not important for airfoils on airplanes.

In the present invention, the CA for rational consumption of energy should be less than 0.2. As described below, in the effective range of CA of 0.1 to 0.2, the present invention generates Cz values of 5 to 8 (and thus corresponding driving forces) which are much higher than the above values obtained by airfoils for airplanes.

The present invention relates to an apparatus located in a fluid moving in a first direction to generate a driving force in a second (drive) direction transverse to a first (fluid) direction, wherein the device is angled relative to the first direction. A device having an elongated hollow body (such as a tube or cylinder or conical column) having a special in-plane cross section (ie, profile) that is symmetrical and round about an axis that forms a shape. The symmetrical construction of the profile and all associated devices (such as the flaps or holes described below) is due to the necessity of exploiting wind from both sides of the ship. The profile preferably has an extended leading edge whose width increases from the front to the rear and a trailing edge whose width decreases from the front to the rear. The profile is thick, i.e. it is preferred that the maximum width of the profile is from 50 to 100% of the length in the symmetry axis direction.

In particular, the trailing edge of the profile is formed as an arc whose portion is smaller than a semicircle, and the remaining portion has a shape that smoothly joins the arc. The apparatus also generates a substantially low pressure or vacuum at the body surface in at least a portion of the trailing edge of the body profile located on the side to which the lateral drive force is directed (ie downstream of the wind) (eg For example, by sucking fluid through the fluid permeation zone of the profile surface). In addition, an additional device is provided for separating the two fluid classifications generated on both sides of the outer surface of the body, which device is on the side facing the direction from which the fluid flows (ie upstream of the wind). Located.

These features of the present invention allow the construction of a propulsion device that is easy to implement and capable of generating large and effective driving forces, in particular with low energy consumption.

This advantage is due in part to the formation of a thick symmetric body profile and the elongated specific shape of the profile leading edge, which makes it possible to limit the intake fluid permeation zone to a very small area of the profile, which is also necessary for the device. Energy consumption can be significantly reduced. Therefore, it is necessary to generate suction only when the velocity of the fluid boundary layer on the outer surface of the body (i.e., upstream of the wind) is such that the air separation leaves the surface and causes turbulence, that is, when the pressure gradient is positive. However, the elongated specific shape of the profile (especially the leading edge of the profile) significantly delays such a state, thus limiting the outer surface area in which the intake port is formed to a relatively small area, and also the intake flow rate and the body surface. The degree of vacuum can be reduced.

A particularly good function of the device of the present invention is to combine a significantly thicker profile with the suction device to obtain a large vibration or pressure reduction by sucking the fluid into the body from the permeation zone. The shape of the profile also has the advantage that the internal pressure is easily lowered by making the suction chamber large, so that the loss due to air flow is reduced, thereby reducing the energy consumption of the device.

In addition, the outer surface (downstream of the wind) and the inner surface (upstream of the wind) around the hollow body, which are done by a vane or flap with special placement and dimensions (i.e., without any other energy consumption). By separating the fluid in the phase, it is possible to prevent the generation of harmful vortices or turbulent flows with a small driving force for a predetermined energy pressure level.

Thus, a significant effective effect can be obtained by combining various features of the device according to the invention. As an example, when the projection surface area of the main body is 150 square meters, the angle α of the ship's traveling direction with respect to the wind direction is preferably about 60 ° C., and at a wind speed of 12 meters (24 knots) per second, Up to 14 knots of thrust can be achieved by generating a low suction pressure with the motor. In comparison, to achieve the same results, the sails should have a surface area of about 1,000 square meters, and the ship's overall dimensions and the number of people and systems for operating it should be significantly increased.

In view of the energy economy obtained by the device according to the invention, an engine of about 1,200 horsepower is required in order to obtain the above-mentioned results by the device according to the invention in a ship equipped with a conventional propulsion device.

In addition, the device of the present invention is substantially floating relative to the ship, so there is no mechanical problem with the rotating cylinder device utilizing the Magnus effect.

According to another feature of the invention, there is provided an apparatus for automatically directing the axis of symmetry of the profile of the main body at an appropriate angle of attack with respect to the fluid direction.

Indeed, according to one embodiment of the present invention, the elongated main body profile has a circular arc shape whose trailing edge is smaller than a semicircle, and the remaining portions have a substantially elliptic shape larger than a semi-ellipse that smoothly joins the circular arc.

In a practical structure, the extended leading edge is composed of a fairing having an elliptical shape in cross section. To ensure that the device does not break when placed in a flow fluid that is significantly faster than normal, increase the strength of the device, or provide at least one retractable portion on the extended leading edge of the device to reduce the overall surface area of the body. Can be reduced.

With other features of the present invention, various structures for the retractable portion can be provided. Thus, if the elongated body has a rigid cylindrical container that forms a trailing edge, it may be moved by a flexible, expandable container having a single or double wall, or radially relative to the cylindrical container and cylindrical by a flexible bulkhead. By means of movable ferrules connected to the vessel or by flexible beak-shaped projections disposed between two supports, such as masts or lines, which are substantially parallel to the axis of the cylindrical pot and produce a gap effect, or radially relative to the vessel. The low edge can be generated by the rigid beak-shaped protrusion. Finally, the elongated body assembly is flexible and has a plurality of rigid portions having one or more portions of flexible material so that they can be arbitrarily shortened in length.

These features can improve the performance of the device even under unfavorable high fluid velocity operating conditions, since the extended leading edge can be similarly shrunk to reduce the effective cross-sectional area of the body disposed in the flow fluid. .

Suitably, the device for performing boundary layer control of the surface downstream of the wind separately separates a device such as a fan and / or a device for discharging the fluid almost tangentially to the body in the direction of the outer surface oil flow to suck the fluid into the body. It also has in combination.

Further, the apparatus for separating the outer side oil and the inner side oil has a flap or vane projecting outward from the main body, or an apparatus for blowing fluid out of the main body disposed in the outer side oil inclined in the flow direction thereof. The flap may be straight or inwardly curved, and the discharge device may be in a radial, inclined or tangential direction, or may be combined with the flap to accelerate the outer surface oil around the flap.

In order to reverse the direction of the driving force, two various members are made two by one, and symmetrically provided with respect to the symmetry axis of the main body, and only the other one can be used in a state in which one is contracted or unused. Alternatively, the end member may be moved to both sides of the symmetry axis of the main body.

According to another feature of the invention, end plates or equivalent structures may be provided at each end of the body to limit the effects of undesirable surrounding vortices or turbulence. In order to further increase the efficiency of the device, each end plate may be provided with a suction device or a discharge device that is tangential, perpendicular or inclined with respect to the surface of the circular or end plate rotating in the outer surface oil direction.

According to the economical combination of these various features, the vacuum is generated on the surface of the elongated body by using the suction device disposed in the body, and the inner surface oil and the outer surface by the vanes or flaps provided in the radial direction with respect to the elongated body. The flow path can be separated, and the end plates are provided at both ends of the extended body.

According to one embodiment of the invention, the suction device has at least one fan having an axis parallel to the longitudinal axis of the elongated body. The single or plural fans are installed inside each end of the body to suck the fluid into the interior of the body over the entire distance between the two ends and to discharge the fluid out through each disk end. This configuration is particularly suitable when the stretched body is elastic. However, this configuration can also be used in combination with all other variations of the streamline. Discharge is preferably performed radially on the circumference of the circumference of each disk end on the trailing edge side. In addition, the discharge cross section is made large enough to limit the pressure drop that increases energy consumption to the maximum possible.

According to another embodiment of the present invention, the partition walls extend in the longitudinal direction in the elongated body so as to form two compartments communicating with each other by the circular opening. Fans are provided in these openings to suck fluid into one compartment having an intake zone, and to discharge the fluid into the other compartment having a discharge zone located in the fluid fraction around the flip. The axis of the fan is preferably perpendicular to the axis of symmetry of the profile in which the partition is installed. Two suction zones and two discharge zones provided symmetrically with respect to the axis of symmetry of the profile are provided so that the direction of the driving force can be reversed, and a means for blocking the fluid permeable zone which does not correspond to the desired driving force direction is provided. The permeable zone has a panel with segments formed on the surface of the body and open toward the inside of the body, and the discharge device has a panel with segments formed on the surface of the body and open toward the outside of the body. In this configuration, the suction and discharge panels are alternately opened and closed by overpressure, low pressure, or mechanical or means generated on either side of the partition by the operation of the fan.

Hereinafter, non-limiting embodiments of the present invention will be described with reference to the accompanying drawings.

As described above, the present invention is an elongated nearly tubular shape having a thick circular profile symmetrical with respect to the flow direction of the fluid in the flow of a fluid flowing at a constant velocity (V), the leading edge of the profile being elongated and having a special shape. A sifted device. However, in order to simplify the explanation and description of the principle of the present invention, in Fig. 2a, the main body is shown to have a circular profile. That is, this profile is shown in the form of a circle for explanation, but it should be understood that it is preferable to have a shape similar to the eighth figure described later in accordance with one feature of the present invention.

As shown in FIG. 2A, the fluid flow (eg wind) at velocity V is induced along the axis X-X 'of the profile. The biaxial (X-X '), along with the transverse axis (Y-Y'), divides the profile into four quadrants (10a, 10b, 10c, 10d), where they are represented by first to fourth quadrants, respectively. The quadrants 10b and 10c form the leading edge of the profile where the fluid first strikes, and the quadrants 10a and 10d form the trailing edge of the profile. The flow fluid is divided into two flows, as shown in FIG. 2A, the outer surface (downstream of the wind) and the oil 11 and the inner surface (upstream of the wind). In order to generate the differential pressure, providing the elongated main body 10 in the transverse direction Y-Y 'in the form of lifting force P (FIG. 1), two main features are provided.

One is referred to in order to generate a vacuum or pressurization in the main body 10 at substantially the copy source 10a of the profile at the wind downstream side (upper side in the drawing) of the trailing edge of the main body 10. It is a device schematically indicated by reference numeral 12. The device has a fluid permeable (eg perforated) zone 54 in the wall of the body 10 at a certain angle β, and also draws a fluid into the body 10 as described below. It is configured by having a suction device such as. The permeation zone 54 is provided at a position where the outer side oil 11 is normally separated from the body surface. The permeation zone 54 and the suction device have the function of holding the outer side oil 11 around the outer side of the profile so as not to cause turbulence as much as possible. In addition, a second fraction flows around the other (inside) surface of the profile.

In addition, a vane or deflector flap 14 type means for separating the outer surface oil 11 from the inner surface oil 13 on the outside of the main body 10 is provided. The vanes 14 are also installed at the trailing edge of the profile, but are installed inside the profile (upstream of the wind) (i.e. quadrant 10d) opposite the permeation zone.

As shown in FIG. 1, the above structure generates the driving force P in the transverse direction Y-Y 'with respect to the direction of the fluid flow V. As shown in FIG. Here, if the device M is an airfoil disposed in the wind classification V, the force P becomes the lifting force of the airfoil daily, and the force R becomes the drag force. With the features of the invention, it is possible to generate a lift coefficient Cz between 5 and 8 with minimal energy consumption.

The configuration of FIG. 2B differs from the configuration of FIG. 2A as follows. That is, the device 14 for separating the outer side oil and the inner side oil in addition to the peel wrap 14a has a radius approximately around the flap 14a around the wind downstream of the flap 14a which generates the outer side oil. The device is schematically indicated by an arrow 14b for discharging the fluid to the outside of the main body 10 in the direction.

In another variation, not shown, the flap 14a may be curved inward so that the outer surface of the fluid has a concave surface. The discharge device thus acts in the direction of the outer surface oil and in the direction tangential to the body 10.

In the configuration of FIG. 2C, besides the elements of the embodiment of FIG. 2A, a device 12 for generating a vacuum in the first quadrant 10a is generally also profiled between the flap 14a and the suction device 12a. Has a discharge device indicated by an arrow 12b acting in a tangential direction.

In another embodiment, not shown, the structural features of FIGS. 2B and 2C may be combined. Further, a plurality of tangential discharge devices such as the device 12b may be provided between the suction device 12a and the flap 14a.

In yet another configuration example, not shown, the vacuum acting on the fluid oil around the first quadrant 10a is generated by a discharge device such as the device 12b of FIG. 2C. Needless to say, in this modification, it is possible to combine with any configuration example of the device 14 for separating the outer side oil and the inner side oil.

Figure 2d shows yet another embodiment of the present invention, in which the device for separating the outer side oil and the inner side oil does not have a flap. Instead, in the fourth quadrant, only the discharging device 14c for discharging the fluid outward from the main body 10 in the substantially tangential direction with respect to the main body 10 in the inner surface oil is used.

Thus, any one of the devices as shown in FIGS. 2a to 2d, in particular the suction device 12a, can obtain a vacuum or low pressure which causes the outer surface oil to soften the profile.

3 illustrates a characteristic of the prevailing invention in which the Bonner body 110 has a thick, rounded profile that is symmetrical about the axis X-X '. More specifically, as shown in FIG. 3, the profile of the main body 110 includes an extended leading edge 110a whose thickness increases from the front to the rear, and a trailing edge whose thickness decreases from the front to the rear ( 110b).

In a particular form, the trailing edge of the prior invention profile is essentially a semicircle whose diameter is equal to the maximum width of the profile. In addition, the leading edge may be a semi-ellipse, or other smooth curve may be used. If the maximum width of the profile here is e, its length or chord is 1, then their ratio (e / l) is slightly larger than 0.5 in this case but is generally between 0.50 and 1.00.

By using such a profile, the driving force can be increased by inclining the X-X 'of the profile by the angle of inclination (i) with respect to the fluid flow (ie wind) direction in the direction to give the driving force (P). . In addition, the elongated shape of the profile front retards separation of the fluid fraction from the body, thereby allowing to reduce the area of the permeable zone 54 and hence the required suction power, which can further enhance energy savings. .

As in the case of the apparatus of FIG. 3, FIG. 2a, it has a permeable zone 54 and a flap 14a. This configuration raises the ratio of the driving force P to the suction energy consumed. In addition, any of the various suction devices of the embodiment of FIGS. 2B-2D can be adapted to the non-circular profile of FIG. 3.

In FIG. 3, the apparatus for separating both side oils 11 and 13 is comprised with the flat rigid flap 14a provided radially in the outer side of the main body 110. As shown in FIG. Since the coefficient Cz increases with the length of the flap, the length of the flap 14a increases from at least R / 2 to the length R (where R is the radius of the semicircular trailing edge 110b of the body 110). . Beyond that, there is no substantial performance improvement. In other words, the flap 14a extends to the point below the lowest point of the profile of FIG. This configuration is particularly advantageous when the permeable zone 54 is located near the starting point of the trailing edge 110b of the outer side shown in FIG. 3, that is, the outer side oil separates from the main body. This position is between about 65 ° and 150 ° from the side OX (where 0 is the center of the cross-sectional circle of the container 110 and the angle is measured clockwise). In practice, the permeable zone can be made smaller. That is, as shown in FIG. 3, the angle β can be made small from about 60 degrees to about 45 degrees around the axis OX, so that the permeable zone is about 85 degrees on the axis OX. At about 130˚. In other words, the permeable zone 54 extends between 60% and 90% of the string as measured from the leading edge.

The fluid permeability (ie porosity) in zone 54 need not always be the same and may be adjusted as described below in some cases. It is preferably selected between 20% and 50%. In addition, the permeable zone 54 may be arranged to have two or more separate zones within the aforementioned angle range. This configuration is particularly advantageous when the suction flow rate is limited. In addition, the internal pressure generated in the body 10 or 110 must be at least less than the external pressure minus the pressure drop in the permeable zone 54 and other flow losses. However, in energy economy, the suction power is limited only to the power required for suction of the fluid boundary layer.

Moreover, it is preferable to incline a certain angle with respect to the axis OX 'in the axis | shaft on the opposite side of the permeable zone 54 with respect to the axis | shaft X-X' of the flap 14a. This inclination angle is between 30 ° and 45 ° to obtain a high coefficient (Cz), and 15 ° and 25 to increase the maximum value of the ratio between the lift coefficient (Cz) and the lift coefficient (Cx). It becomes ˚. Only one flap may be provided, and it may be comprised so that it may move from one side of the axis X-X '(described above) to the other side according to a desired drive force direction as mentioned later.

Needless to say, the above-described configuration of the suction device is not at all limited and can be used alone or in combination with the embodiment of FIG. As another example, FIGS. 4A-4D show various embodiments of a suction device used in the present invention. These suction devices generate a vacuum or low pressure in the first quadrant 10a or the fourth quadrant 10d substantially depending on the direction in which the driving force P is to be applied. These inhalation devices make it possible to limit turbulence by preventing thin outward (i.e., downstream of the wind) fluid fractionation or boundary side separation at the trailing edge of the body surface.

To do this, the body 10 shown in FIGS. 4A and 4B has a fluid permeable container 101 and a non-permeable container 102, and the non-permeable container has a permeation zone angle β on a portion of its circumference. It has a slot 16 having a width (see also FIG. 2A). In the embodiment of FIG. 4A, the permeable container 110 is provided outside the non-permeable container 102, but in the embodiment of FIG. 4B, it is reversed. The permeable container 101 is composed of a porous or perforated wall or system of meshes, gratings, slots, and the like. The permeable zone 54 is preferably located within the first quadrant, but may extend into the second quadrant up to about 25 degrees. Needless to say, the above conditions are reversed when trying to reverse the direction of the driving force, so that the permeable zone is in the fourth quadrant and may optionally extend to the third quadrant. Here, in order to move the slot 16 from the first quadrant to the fourth quadrant, the fluid non-transmissive container 102 may be configured to be oriented.

In the configuration of FIG. 4C, the configurations of FIGS. 4A and 4B are improved, and the angle β can be adjusted during operation. For this purpose, the fluid impermeable container 102 actually consists of two containers 103 and 104, and at least one of them can be directed. Here, if the container 104 'is symmetrical about the axis XX', the width of the slot 16 is changed by the displacement of the container 103 indicated by reference numeral 116, and the slot is placed on the upper portion of the main body. It is possible to displace from the lower part of the main body (as seen in the figure) and vice versa.

In the modification of FIG. 4D, as described later, when attempting to change the direction of the driving force, the directing of the flap and the active transmission zone is simultaneously performed in a single operation. In this embodiment, the hollow body 10 is a fixed inner container 105 (non-permeable except for the permeable zones 54, 54 '), and a non-permeable container which acts outward as a cover or shutter ( 106, and the displacement of this container can cover either the permeable zone 54 or 54 '.

In the modified example which is not shown in figure, the permeable area | region may be made into the shape of the gate formed in the container of the main body 10, and opening to the inside of the main body.

When the direction of the driving force is reversed (when the direction of the fluid flow is changed), the quadrant of the flap 14 and the drilling zone 54 must be exchanged with each other. 5A and 5B show two embodiments of multiple flaps, which are applied to the embodiment of FIG. 3 (or another embodiment), inverting the flap 14 between the first and fourth quadrants. You can. As shown in Figure 5a, the apparatus of the present invention has two radially flat flaps 14a, 14b arranged symmetrically about an axis X-X '. As can be seen in the figure, the flaps 14a and 14b can be retracted into each of the radial slots 18a and 18b respectively formed in the body 10 to be fully retracted with respect to the body profile. More specifically, when one flap 14a or 14b is extended, the other flap is retracted. In this way, the direction reversal of the driving force P is possible.

FIG. 5B shows another configuration example, and two flaps 14a and 14b are arranged symmetrically with respect to the axis X-X 'as in the above-described embodiment. The flaps are each pivotally attached to the lead 20 of the body 10 and can thus rotate to abut on the body. These flaps may be flat or may be inwardly curved in close contact with the profile of the main body 10 so as not to impede the flow of fluid around the main body 10.

As in the modification of FIG. 5A, the flap 24a on the other side is brought into the arcuate position while abutting on the main body 10 of the one flap 24b according to the direction in which the driving force P is to be applied. .

FIG. 5C shows another variant with a single flat radial flap 14a mounted on the body 10. Here, the flap 34a may move around the axis of the main body 10 so that each position can be adjusted according to the direction to give the driving force, and is installed to move between the fourth quadrant and the first quadrant.

Needless to say, other flap configurations besides these are possible. For example, two flat flaps may be installed symmetrically about the axis X-X ', and the flaps may be alternately inflated with each other according to the direction of the driving force to be generated by the device.

The pseudo radial or radial discharge device 14b (FIG. 2B) acts like a fluid flap between the outer side oil and the inner side oil while accelerating the outer side oil. Pseudo tangential or tangential ejection devices 12b and 14c (FIGS. 2C and 2D) drive thin fluid fractions that lose energy by friction against the walls of the body 10, and induced effects To drive another fluid classification layer.

The variant of FIG. 5C can be used in conjunction with that of FIG. 4D and can be configured as shown in FIG. Here, it is preferable that the main body 10 has a leading edge portion 110a that is rounded like a third degree and a semicircular trailing edge portion 110b. The main body 10 is provided symmetrically with respect to the axis XX 'two transmissive zones 54, 54a in the positions and dimensions as described above. An arc-shaped outer container or shutter 106 (such as FIG. 4d) of a single part is installed to move out of the main body 10, and one transmissive zone 54 or 54a as shown in FIGS. 4c and 4d. The other permeable zone is closed at the same time as controlling the angle size. The flap 14a is mounted at the center of the arc of the shutter 106 and moves with it. In this way, the direction of the driving force can be changed by displacing the assemblies 106 and 14a from the fourth quadrant to the first quadrant.

7 shows another profile 210 for use in the configuration described above. In this case, the leading edge 210a is in the form of a semi-ellipse (see FIG. 6), and is smoothly connected to the semicircular trailing edge 210b. That is, the diameter of the semicircle of the trailing edge is equal to the minor diameter of the ellipse of the leading edge. In this embodiment, the ellipse has a width to length ratio of about 0.5, that is, the short diameter of the ellipse is about 0.5 times the long diameter. Therefore, the ratio of the width to the overall length of the profile is about 0.66.

As in the case of FIG. 6, two symmetrically installed permeable zones 54, 54a are provided. In one form, these zones stretch between about 85 and 130 degrees from the axis XO and have a porosity between about 20% and 50%, preferably between 30% and 40%. The flap 14a is on the arc-shaped shutter 206, which selects the quadrant of the flap 14a and sets its inclination angle, converts the utilization permeability zone from 54 to 54a and vice versa. Adjust to close the unused area.

8 shows an improved profile 310 of the present invention, which can be seen that the effective driving force for energy consumption is increased by about 20% from the shape of FIG. The profile 310 of this form is also symmetrical about the axis X-X ', and part of the trailing edge 310b thereof is formed by an arc AB. It is preferable that the remaining part of the trailing edge portion 310b and the entire leading edge portion 310a have a partial ellipse shape (larger than a semi-ellipse) that smoothly joins the arc AB. In a particular preferred form, the arc AB is symmetrical about the axis OX 'and 90 degrees about its center (0). The center (0) is about 74% of the total profile length from the tip of the leading edge 310a, and the radius of this arc is about 26% of the profile length. This profile is an ellipse in which the ratio of the shorter diameter to the longer diameter of the 90 ° circular arc at the elliptic end is about 0.66. Flap 14a is located about 35 degrees from axis OX '. The shutter 306 is arcuate as before, and a suitable suitable seal is provided between the main body 310 and the shutter as necessary, whereas the shutter 306 is provided in the profile portion where it overlaps. It is good also as an elliptical arc shape instead of the shape to match, ie, arc shape. Other shutter designs may also be used.

The arrangement of FIG. 8 also has the advantage of making the permeable zone small. At a porosity of about 45%, the permeable zone (such as projected on the axis (X-X ')) extends from about 75% of the profile length to about 91% of the profile length from the leading edge. In contrast, in the form of FIG. 7 the permeable zone extends from the tip to about 63% to 88% of the length of the profile. If the permeable zone is made smaller than this, the energy saving of the device can be improved by further reducing the power required by the suction device to achieve the required pressure drop in the body.

Advantages of the present invention will be more readily apparent from FIG. 9, which shows the curve of C _A at Cz of a number of propulsion generating devices. The results shown in FIG. 9 are all obtained for an apparatus in which the ratio of the length to the string of the main body is about six. As can be seen from the figure, the steeper the slope of the curve, the greater the benefit of the increase in Cz over the increase in power consumed. In practice, it has been determined that the energy factor C _A does not exceed 0.2 in order to ensure that the power consumed in the fan providing the pressure drop for suction is not too large. In addition, a Cz value of 5 or less is hardly a practical value for the invested expense and the profits that can be obtained. Thus, the effective area of C _A will be between about 0.1 and 0.2.

Curve 1 in FIG. 9 shows the test results for the operation of the Magnus effect rotor device (no end plate). As can be seen from this, within the effective area of energy consumption the lift coefficient (Cz) of the device is between 4 and about 5.1.

Curve 2 shows the results for the suction circular cylinder for comparison, where the value of Cz is greater than the Magnus effect device in the zone where the value of C _A is greater, but is less effective than the Magnus effect device in the effective zone, and Cz The value of is limited to between about 2 and 4. In such a configuration shown in FIG. 7, the result shown by curve 3 is obtained, and as can be seen, a larger effective Cz (from about 4.5 to about 6) is provided for the same allowable energy consumption.

Comparing curves 2 and 3, it can be seen that the elongated leading edge of the profile can make the suction energy consumption required to generate the driving force smaller than the circular profile. That is, in the case of wind propulsion, if the angle of incidence i formed between the symmetry axis XX 'of the profile of the main body 10 and the wind direction is close to 30 degrees to 35 degrees, a rigid cylindrical container for obtaining Cz = 5 ( The energy consumption required for suction in the transmission zone 54 of 50 can be reduced by about half as compared to a body having a relatively circular cross section with the same projected surface area.

The performance of the embodiment as shown in FIG. 8 of the present invention is shown by curve 4 in FIG. 9, where a higher Cz is obtained for a given C _A or vice versa compared to other configurations. For Cz, the energy required for the fan is lower than it actually is. According to this, when the same driving force is obtained, energy saving of 20% is possible compared with that of FIG.

Various configurations of FIGS. 2-5 may be used with the profile form of FIG. 8. 2a to 2d, 3a to 3d, 4a, 5a to 5b, 6a to 6a, 8a to 8e of the above-mentioned prior US patent application As described in the application with respect to FIGS. 9A to 9E and 10 to 15, the apparatus of FIGS. 3, 6 and 7 of the present application, and its configuration and use to its modifications The same applies to the improved form of FIG.

As mentioned above, the apparatus of the present invention is used to control the movement of a movable body, such as a ship, and also to generate energy, in particular electrical energy or power, using the apparatus to drive an alternator.

Of course, in the application of the device, it is advantageous to have a device capable of detecting the direction of the wind or other fluid. This detection device can operate the servo control device which automatically directs the axis X-X 'of the main body so as to generate a predetermined angle of incidence i with respect to the wind direction.

As a specific example when the driving force or driving force generating device of the present invention is applied to energy production, in a place where wind or other fluid is present, a closed circuit is formed by vertically or horizontally several several driving force generating devices as described herein. Arranged so as to form, it is possible to drive the generator to generate electricity by operating the device in conjunction with this circuit around one fixed point by the wind. The apparatus may also be used as a horizontal shaft, double or multiple wing vanes, as a vane of a wind generator. Here, the rotational force about this axis of the device as their vane is used to drive the generator or pump directly by the driving force generated in the direction of rotation. In this case, rotation of the apparatus forming the vane automatically occurs due to the spinning of the flap, and air is sucked into the inside by the centrifugal force and moved toward the periphery thereof. Due to the high driving force obtained by the apparatus of the present invention, even in a wind driven generator having a single vane element, an effect comparable to that of a conventional multi-wing wind driven generator can be obtained. Finally, the device of the present invention may be used as a replacement for conventional vanes or vanes of a substantial variety of types of rotary or propulsion devices.

The present invention is not limited to the above specific embodiments, and includes all modifications thereof. Therefore, the captive fill may change from the one end to the other end. Similarly, the positions of the various devices constituting the suction device, the discharge device and the flap may be different, and may gradually change from one end of the length of the main body to the other end. For this purpose, the body may be subdivided into a number of parts that can be directed independently of one another. The flap is also made of soluble material, which may occupy different positions from one end of the body to the other end.

Claims (24)

It is located in a fluid moving in a first direction to generate a driving force in a second direction relative to the first direction, and has a profile that is symmetric in cross section with respect to the axis of symmetry that forms an angle with the first direction when used in the fluid. The profile has elongated leading edges whose thickness increases from front to back and trailing edges whose thickness decreases from front to back, the maximum thickness of the profile being between 50% and 100% of the length in the direction of the symmetry axis. A means installed in the trailing edge of the profile for controlling the boundary layer of the fluid flowing on the surface of the body, the hollow body having an elongated hollow body, and the fluid flowing smoothly on the surface of the body; Extending outwardly from the body along the trailing edge of the profile on the side opposite the side of the profile to be generated. In a device having a wrap, the leading edge (110a) has a substantially elliptical cross-sectional shape, the trailing edge (110b) is a cross-section in which a portion is a circular arc smaller than a semicircle, and the remaining portion is smoothly connected to the circular arc smaller than a semicircle. Apparatus for generating a force in a fluid, characterized in that it has a shape. 2. The main body (110) according to claim 1, wherein the main body (110) has fluid permeation zones (54, 16) on a surface on at least one side of the trailing edge with respect to the axis of symmetry, and the boundary layer control means controls the boundary layer to generate a driving force. And means for sucking fluid from the fluid permeation zone (54, 16) on one side of the trailing edge (110b) of the desired profile into the body (110). The flap (14a, 14b, 24a, 24b, 34a) of claim 1 or 2, characterized in that the flap (14a, 14b, 24a, 24b, 34a) is on a movable non-permeable container portion 106 disposed to surround the fluid permeation zone (54). Device. Apparatus according to claim 1 or 2, characterized in that the arc of the trailing edge (110b) is symmetric to the axis of symmetry of the profile. The device of claim 1 or 2, wherein the arc has an internal angle of about 90 degrees around the center of curvature. 59. The apparatus of claim 56, wherein the remainder of the profile of the body (110) has a non-arc shape that is smoothly connected to the arc. 4. The body (110) according to claim 3, wherein the body (110) has two fluid permeation zones (54, 54 '), and the non-permeable container portion (106) is one of the fluid permeation zones (54, 54') or And optionally directed to surround the other. 3. The body (110) according to claim 2, wherein the main body (110) has two or more coaxial container portions (103, 104; 105, 106), and at least one of the container portions (104, 106) is oriented fluid impermeable. Device having at least one slot (16) therein defining a portion of the fluid permeation zone, while the other container portion (103, 105) is fluid permeable. 9. An apparatus according to claim 8, wherein the body has two fluid impermeable container portions directed independently of each other to adjust the width of the slots (16). 9. The body of claim 8 wherein the body comprises a non-permeable container portion forming two fluid permeation zones symmetric about the axis of the profile (X-X '), and an arcuate orientation surrounding one or the other of the fluid permeation zones. And an impermeable container portion (104, 106). The apparatus of claim 1 or 2, wherein the body has one or more non-permeable container portions having gates that open inwardly to form a fluid permeation zone. 3. The device according to claim 1 or 2, having two rigid flaps 14a, 14b; 24a, 24b, each of which is movable relative to the body so as to occupy an inactive position that does not change the profile of the body. Also, the two flaps may be positioned in the non-acting position when one side (eg 14a, 24a) protrudes from the body, depending on the side of the profile from which the driving force is to be generated. Apparatus characterized in that the installation is symmetrical about the axis of symmetry of the profile. 13. The flap (14a) (14b) according to claim 12, wherein the flaps (14a, 14b) are installed radially with respect to the main body (10) in a planar shape and can also be contracted by sliding in parallel in the slots (18a, 18b) formed in the main body (10). Apparatus, characterized in that. 2. An apparatus according to claim 1, having two expansion restraining flaps positioned symmetrically with respect to the symmetry axis of the profile such that one is retracted and the other is expanded along the axis of the profile from which the driving force is to be generated. 3. The rigid flap 34a according to claim 1 or 2, which is provided radially with respect to the main body, and the flap 34a also depends on the side of the profile to generate the driving force. On the trailing edge (110b) of the profile, the device is characterized as moving relative to the body (10) from one side of the axis of symmetry (X-X ') to the other side. 13. The device of claim 12, wherein the flaps (24a, 24b) are pressed against the body so as to conform to the profile of the body. The device according to claim 1 or 2, wherein discs are attached to both ends of the main body. 18. The disk of claim 17, wherein each disk is integral with the body and has means for inhaling fluid into the body zone located at one side of the trailing edge of the body on an adjacent surface with the body. Device. 18. The apparatus of claim 17, wherein at least one fan having an axis parallel to the longitudinal axis of the body sucks fluid into the body through a fluid permeation zone and discharges the fluid out of the body through at least one of the end disks. In order to do so, it is provided in the main body of at least one vicinity of the both ends of a main body, The apparatus characterized by the above-mentioned. 20. The apparatus of claim 19, wherein the fan discharges fluid into at least one opening of an arc shape formed around a corresponding disk. 3. An apparatus according to claim 1 or 2, which is directed to have an angle of inclination of at least 30 [deg.] Between the axis of symmetry (X-X ') and the first direction. 22. The apparatus of claim 21, wherein the angle of incidence is between 30 degrees and 35 degrees. The device according to claim 1 or 2, characterized in that the flaps (14a, 14b, 24a, 24b, 34a) are directed at an angle of 45 degrees or less with respect to the axis of symmetry (X-X '). 3. An apparatus according to claim 2, wherein said means for aspirating fluid through the fluid permeation zone (54, 54 ') provides an energy consumption coefficient of 0.1 to 0.2.

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