JP2016011637A - Oscillation type fluid power device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power device that is not utilized in conventional power devices using a rotation type fluid machine element, can correspond flexibly even from flow of fluid having low energy density without greatly changing natural flow, can take out power stably, and has high cost-effectiveness.SOLUTION: An oscillation type fluid power device includes a wing receiving kinetic energy of flow and generating lifting force. By regularly inverting the elevation angle of the wing positively or negatively, the oscillation type fluid power device inverts the direction of lifting force acting on the wing with constant regularity, makes continuous oscillation operation excited in the oscillation arm of an oscillation mechanism with alternating lifting force as exciting force, and converts the oscillation operation to rotational operation to take it out as power.

Description

  The present invention relates to an oscillating fluid power device that extracts power from a fluid flow.

In order to reduce the burden on the natural environment, it has been a long time since further development of unutilized natural energy was advocated, and solar power and wind power generation have become extremely popular. Although it is not true, trials for small-scale hydropower generation using small river flows and demonstration experiments of power generation technologies targeting tidal and tidal currents have been started.
However, they all use the velocity head of the fluid, except for special cases that use wave power and temperature differences, and are not extended from the extension of conventional technology using a turbine or rotor blade. However, the scope of application is limited to flows with high energy density, and it has not reached the stage of practical use and diffusion.

Even today, there are many unused natural energy resources. For example, general river flows, ocean tides and tidal currents.
River flows and tidal currents that are not currently used are common in that they have low energy density, and it is difficult to use them effectively with conventional technologies using water turbines and rotor blades. It has not been used for the reason that the effect is remarkably inferior.
For rivers, the lack of technology that can flexibly cope with different flow conditions at different locations due to topography has prevented them from being used as an effective power source for purposes such as power generation.

  In order to utilize these unutilized energy resources for power generation, etc., it is effective even for flows with low energy density (wide application range) and flexibly supports flows that exhibit various aspects at each location (flexible (Adaptability) is possible, and the development of technologies with low construction costs (including cost-effectiveness) including incidental work is awaited.

Against this background, regardless of the conventional technology using a turbine or rotor blade, the lift generated in the blade is used as a power source to cause a reciprocating motion in the direction perpendicular to the flow, and this is converted into rotational power. Thus, a “fluid power device” has been proposed as a method for extracting electric power. (Patent Document 1)
The outline of the “fluid power device” proposed in Patent Document 1 is as follows.
That is, “one or more wing members are mounted on a movable member guided by a fixed shaft extending in a direction substantially perpendicular to the fluid flow and reciprocating along the fixed shaft. The member is pivotally supported by the movable member via a rotating shaft, and is generated in the wing member by changing the angle of attack of the wing member with respect to the flow from positive to negative or from negative to positive. This is a “fluid power device” in which the lift force is reversed to cause the movable member to reciprocate, and the reciprocating motion is converted into rotational motion by appropriate means.

JP2011-169289A

However, the prior art still has some problems to be solved as pointed out below.
In other words, 1) Although it is unavoidable to increase the size of the apparatus when trying to obtain a large output, it is natural that it is necessary to increase the travel distance (stroke) of the moving body. To that end, it is expected that construction costs including incidental construction will rapidly expand, and it will be difficult to select power conversion means when the size is increased.
When reciprocating motion is converted to rotational motion, the crankshaft is conventionally used, and it can be said that the crankshaft is assumed to be clearly used in the prior art. Therefore, it is necessary to increase the crank radius in order to extend the stroke. It causes an increase in starting resistance due to an increase in moment of inertia, and is recommended because it requires a large installation space for securing a safe distance. Furthermore, the most troublesome problem when using a crankshaft is the existence of the top and bottom dead centers of the crankshaft. The top and bottom dead center (hereinafter referred to as “thought point”) is literally a deadlock point, and it requires a stronger force to get over this point, but the point in time coincides with the point in time when the moving body reverses the direction of movement. You must keep in mind. In addition, when the moving body reverses the moving direction, the driving force acting on the moving body decreases, passes through “zero” (= 0) and then increases, and the thought point and the driving force “zero”. Match. Therefore, if it is assumed that the prior art uses the crankshaft as the power conversion means, the problem related to the thought point of the crankshaft cannot be avoided, but the rotation is continued after the thought point is overcome. I have to say that it is impossible. This is also closely related to the wing reversing means to be touched next.
2) The reliability of the blade reversing means is the most important matter, but the prior art does not have the blade reversing means that works actively, which is the most serious defect.
In the prior art, a method of directly using the force that the blade itself receives from the fluid is used to invert the blade. When this is verified dynamically, it becomes apparent that uncertainty is inherent in the operating principle for the following reasons. In other words, the blade reversing means in the prior art is provided with a stopper at a position where the tip of the blade comes into contact so that the blade is standing in the direction of flow when it reaches the stroke end of the moving body. However, if you imagine a series of movements where the wings are reversed, the wings are inverted from the moment the moving body approaches the stroke end and the tip of the wings starts to come into contact with the stopper (the tip of the wing faces the upstream direction of the flow) The angle of attack on the wing flow gradually decreases in the process until and begins until it reaches zero. As a result, the lift gradually decreases, and the lift becomes zero when it is inverted. Of course, it should pass through the point where the force acting on the wing and the force due to the load antagonize in the process. Then, depending on the relationship between the two, there is a risk of causing a bridging state (also called a bridge state or a shelf-suspended state), and when the bridging state is reached, the moving body stops running and stops its function as an engine. It becomes. FIG. 33 and FIG. 34 are for illustrating the blade inverting means in the prior art and are not quoted from the patent document. FIG. 33 is a power diagram in the running state, and FIG. 34 is a power diagram after the time when the moving body approaches the stroke end and the tip of the wing starts to contact the stopper. According to FIG. 34, it is unlikely that the state of bridging (bridge) due to the relationship between the propulsive force and the load is likely to be a melancholy.
It should be pointed out that the uncertainties of blade reversal described here are not limited only when the crankshaft is used as the power conversion means, but are not eliminated even when other power conversion means are used. In addition, while the movable member is reciprocating, the wings must maintain a predetermined angle of attack, but since there is no function to fix and hold the wings during this time, for some reason, There is a possibility of changing the angle of attack of the wing when an external force is applied due to an unexpected reason such as a collision of the air flow or a disturbance in the flow, and this also includes the possibility of exhibiting a function.

The present invention solves the above-described problems of the prior art,
1) It can be applied to flows with low energy density,
2) A mechanism that can flexibly cope with the diversity of fluid flow in the natural world and facilitates scale-up and optimization.
3) The aim is to provide an oscillating fluid power unit that is cost-effective.

In the prior art, a mechanism in which a “movable member” reciprocates on a linear axis is used. A wing is attached to the movable member and the angle of attack of the wing is reversed to cause the movable member to reciprocate. It is assumed that it is converted into rotational motion and taken out as power.
On the other hand, as a first means for solving the above-described problem, in the present invention, a swinging member (hereinafter referred to as a swinging arm) that reciprocates (oscillates) around a fulcrum shaft, A mechanism consisting of an oscillating body that is engaged with the free end of the arm and reciprocates on an arc locus is used. The oscillating body is provided with a blade, and the force of the flow acting on the wing is used as a power source. A mechanism for exciting a reciprocating angular motion on the swing arm was used. (In the following description, the motion mechanism composed of the fulcrum shaft and the swing arm is called the “swing mechanism”, and the combination of the moving arm and the swing body is collectively called the “swing part”. The oscillating portion includes a wing and a part of wing operating means described later.)
That is, the present invention regularly and repeatedly reverses the angle of attack of the blade facing the fluid flow, thereby modulating the lift acting on the blade to an alternating force and using the alternating force as an excitation force to the swing mechanism. An oscillating fluid power device (Claim 1) that excites continuous oscillation and converts a reciprocating angular motion of the oscillation mechanism into a rotational motion to serve as a power source. A fulcrum shaft is fixedly installed extending in a direction substantially perpendicular to the flow direction, and an oscillating body that is pivotally supported by the fulcrum shaft and oscillates with the flow direction as a reference (center). A movable body that is held at the free end of the rocking body and reciprocates on an arc locus; a wing that is rotatably mounted on the movable body via a blade rotation shaft; and the blade rotation shaft is operated. Blade operation means for reversing the angle of attack of the blade with respect to the flow according to a predetermined repeating pattern, and the reciprocating angle of the oscillator And create a rocking type fluid power device including a power converting means for converting the movement in a certain direction rotational motion (claim 2).

  In addition, in the prior art, it was pointed out that the lack of a blade reversing means that actively operates as a blade angle-of-attack reversing means is a serious defect, which may lead to malfunction. As a second means for solving the problem, the blade operating means in the present invention includes an actuator that operates by external auxiliary power, and a transmission system that transmits the output of the actuator to the blade (distribution when there are a plurality of blades). Including a mechanism), left and right sensors for detecting that the swing arm has reached the left and right amplitude limits, and a control device for controlling the movement of the actuator (claim 6). In association with the dynamic motion (swing angle), blade operation means for regularly operating the blade is provided. That is, the blade operating means of the present invention starts the blade reversal operation at the moment when the swinging body reaches the left or right amplitude limit, and changes the predetermined angle of attack of the blade from positive to negative, or from negative to positive. While the direction of movement of the oscillator is changed by reversing (turning mirror-inverted with the flow direction as the reference line), the interval other than the angle-of-attack reversing operation of the blade is the interval. The blade operating means is fixed and held so that the blade does not rotate freely, and maintains a predetermined angle of attack, either positive or negative. Incidentally, when an angle or a moment is expressed in relation to an angle or a turning motion, a value measured counterclockwise in accordance with the convention is positive, and a clockwise rotation is negative.

  Another method for operating the blades is to use the rotational energy stored in the flywheel attached to the crankshaft as a power source without relying on external auxiliary power, and the intermittent operation principle of the gear train and Geneva mechanism. In addition to reversing the angle of attack of the blade from positive to negative or from negative to positive corresponding to the crank angle, the blade is in a predetermined posture (attack) except for the operation of reversing the blade. It is also possible to select a mechanical blade operating means that does not use external auxiliary power that is fixedly held so as to remain at the corner. (Claim 14)

One of the reasons why it is not appropriate to use a crankshaft as power conversion means in the prior art has been pointed out in the length of the stroke. In the present invention, the swing arm and the crankshaft are connected to the connecting rod. The connecting position of the connecting pin arranged on the swing arm can be determined at an arbitrary position on the long axis of the swing arm, so that an appropriate value is set as the crank radius of the crank shaft. In addition to being freed from restrictions on the stroke length, there is an advantage that the force transmitted to the crankshaft can be adjusted according to the lever principle.
Since this is a flow with a low energy density, it is possible to determine the equipment specifications so that the power unit functions stably even when the force acting on the swing arm is weak.

は、いわば余力に相当するものであって、制限された揺動域を超えてもなお運動を継続せんとする余力を残していることを示している。即ち十分な余勢い（思案点乗越えエネルギー）を持って思案点に到達することが出来ることとなる。更に、翼の反転時期を正確に制御して、思案点到達後直ちに翼を反転させることで、翼力（揚力及び抗力）の方向を反転させ、それまでと逆の方向のモーメントを生じさせて揺動腕を逆方向に揺動開始させる。更なる補強策として、本発明では、該クランク軸にフライホイールを装着して慣性モーメントを加増させ、フライホイール効果（回転を平準化する働きと、回転を維持し続けようとする働き）の助けを借りて思案点の乗越えをより確実なものとした。
即ち、フライホイール効果でクランク軸が思案点に達した後も、回転を維持し、且つ回転の方向付けをする働きをし、反転後の翼の翼力はクランク軸の回転を加速する方向のモーメントを生じることとなり、思案点を乗り越えて同じ方向に回転を持続しようとする効果をもたらした。 Since the crank mechanism is used as the power conversion means, the problem of the thought points related to the crankshaft is the most important matter in the present invention as in the prior art.
Naturally, it is clear that the energy of the appropriate amount (referred to as the surpassing energy) is necessary to get over the point of the crankshaft. In connection with this, the utility of limiting the swing range of the swing arm will be described with reference to FIG.
In the graph, the state indicated by the solid line is that the swinging arm released from the connection with the crankshaft is placed in the flow, and the moments around the fulcrum shaft against the swinging arm acting on the wing and the lift acting on the wing. Shows the state of staying in balance. Further, when the swing arm represented by an imaginary line is connected to the crankshaft, both amplitude angles of the swing arm are 2θ.
Therefore, the angle β in the figure is

Is equivalent to a surplus force, and indicates that there remains a surplus force that continues the motion even after exceeding the limited swing range. In other words, it is possible to reach the thought point with sufficient surplus energy (energy exceeding the thought point). In addition, by accurately controlling the timing of wing reversal and inverting the wing immediately after reaching the thought point, the direction of wing force (lift and drag) is reversed, and a moment in the opposite direction is generated. Start swinging the swinging arm in the reverse direction. As a further reinforcement measure, in the present invention, a flywheel is attached to the crankshaft to increase the moment of inertia, thereby assisting in the flywheel effect (function of leveling rotation and maintaining rotation). Borrowed to make sure that the point of thought was overcome.
That is, even after the crankshaft reaches the ideal point due to the flywheel effect, it maintains the rotation and functions to direct the rotation, and the blade force of the inverted blade is in the direction of accelerating the rotation of the crankshaft. A moment was generated, and the effect of trying to continue the rotation in the same direction over the thought point was brought about.

In addition, as a measure to further increase the certainty of passing over the thought point, a plurality of sets of a set of power units (called basic units) according to the present invention are connected to combine each other's outputs and output fluctuations to each other. Created a form to complement each other. (Please refer to Figure 18)
Here, “connect” means that a plurality of output shafts (crankshafts) of a plurality of (same type) basic units are connected dynamically and mechanically united to form a single engine. .
Specifically, a plurality of basic units are arranged so that the respective fulcrum shafts are on the same line, and the axes of the respective crankshafts are connected in alignment.
The basic unit should be called a single-action type, whereas a form created as a result of connecting two or more sets of basic units is called a double-action type.
FIG. 18 is an example of the double-acting type, and the double-acting crankshaft created for this purpose will be described later, but in this case, the connected crankshaft has two crank arms, In order to avoid overlapping of the timings at which the basic units pass the thought points, it is important to have a phase difference with respect to the phase (assignment) of the crank arm.
Needless to say, a phase difference inevitably occurs in the swing angle of the swing arms.

The prior art is based on a mechanism in which the movable member reciprocates on a linear axis using the flow force (lift) acting on the wings attached to the movable member as a driving force. The basic mechanism is swing motion, and the biggest advantage of using the swing mechanism is that the lever principle can be applied even when the lift acting on the wing is small, and the length of the swing arm By changing the lever ratio by changing the height, the moment acting on the swing arm can be increased.
This is a significant advantage in the prior art as compared with the fact that the propulsive force exerted by the fluid on the moving body is transmitted to the crankshaft in a one-to-one relationship.

  The swing mechanism in which the swing arm is pivotally supported by the fulcrum shaft is a very simple mechanism, and a bearing unit (bearing) can be used. Compared to the linear motion mechanism of the prior art, mechanical friction loss is achieved. Is much less and has the effect of improving mechanical efficiency.

  Regarding compatibility with the installation site conditions, it is important to determine the direction in which the swing axis extends in consideration of the characteristics of the cross-sectional shape of the flow, that is, the spread in the width direction and the height direction. The width of the flow in the wide (narrow / narrow) range can be adjusted by adjusting the length and angle of the swing arm, and the flow is thin (thin / thick) in the direction in which the swing shaft extends. In addition, by adjusting the number of double-acting units or by adjusting the blade width, it is also possible to adjust the flow strength by adjusting the size and number of blades. Made possible. This also has the effect of dramatically increasing the degree of freedom of scale-up.

  Since the entire apparatus has a structure that is supported by a fulcrum shaft, it is sufficient to have a structure that can be attached to the fulcrum shaft and that has strength to support the force caused by the flow applied to the fulcrum shaft. Therefore, it is possible to divert existing structures, and if the scope of application is limited to river flow, it is possible to omit or reduce incidental work such as flow path maintenance and large-scale civil engineering work. Combined with the mechanism, it is cost-effective and the restrictions on the installation location can be relaxed.

  In the prior art, it has been pointed out that the wing reversing means is not an active mechanism and may malfunction, but the present invention has a clear wing operating means for reversing the wings. Thus, the uncertainties of inversion can be removed, and the effect of enabling stable operation was brought about. In addition, in the prior art, because of the reversing means, only flat plate wings that are symmetric with respect to the neutral line can be selected. However, by providing clear means, some of the more preferable wing types described later are included. The ability to select the one that matches the installation location conditions also contributed to the improvement of efficiency.

  The use of a crank mechanism as the power conversion means is the most general and reliable method for converting the reciprocating motion into the rotational motion.

若しくは、

と表すことができる。
このことは、クランク軸のクランク半径ｒ と、揺動腕にとりつける取付ける連結ピンの位置(支点軸と連結ピンの距離) l により揺動域〈両振幅角〉が確定し、前記揺動腕の左右の振幅限は前記クランク軸のクランク角が０°乃至１８０°（思案点）にある時であり、前記揺動腕が揺動の中心位置に在る時はクランク角が９０°若しくは２７０°の時に当たる。従って、クランク角が９０°乃至２７０°の時に前記揺動腕が流体の流れの方向を向くように設置することで前記揺動腕は該流れの方向を中心として左右均等の振幅域の中を揺動することとなる。 The use of the crank mechanism also has the following merits and will be described with reference to FIG.
Here, when the crank radius is r, the link length of the swing arm (distance between the fulcrum shaft and the connecting pin) is l, and both amplitude angles of the swing arm are 2θ, the following relational expression is established:

Or

It can be expressed as.
This is because the swing range <both amplitude angle> is determined by the crank radius r of the crankshaft and the position of the connecting pin to be attached to the swinging arm (distance between the fulcrum shaft and the connecting pin) l. The left and right amplitude limits are when the crank angle of the crankshaft is between 0 ° and 180 ° (thought point), and when the swing arm is at the center of swing, the crank angle is 90 ° or 270 °. It hits at the time of. Therefore, when the crank angle is 90 ° to 270 °, the swinging arm is installed so as to face the direction of the fluid flow, so that the swinging arm has a right and left amplitude range centered on the flow direction. It will swing.

  The point to be noted here is that the torque transmitted to the power conversion means is not necessarily constant depending on the angular position of the swing arm from the principle of operation of the present invention, and shows a characteristic like a curve shown in FIG. is there. Therefore, it is expected that the fluctuation range is reduced by connecting (superimposing) a plurality of basic units, and that the fluctuation of the output torque of the crankshaft is leveled.

  There are various types of swing mechanisms, and the blades can be selected from the types disclosed in the embodiments. This contributes to an increase in cost effectiveness when the invention is carried out.

What has been described in (0018) to (0023) not only gives flexibility in responding to the installation site conditions, but also shows the ease of scale-up of the apparatus.

  It is feared that the prior art is sensitively influenced by changes in the strength of the flow, and it is considered that the prior art is easily affected by fluctuations in the flow direction. Therefore, in the implementation, it may be necessary to consider the construction of the flow path for rectification and incidental work, but the present invention limits the swing range against fluctuations in the flow direction. By doing so, it is possible to give a sufficient tolerance.

Components and operating principle of the present invention

  This section is originally intended to describe “modes for carrying out the invention”, but before entering the main topic, a prototype (hereinafter referred to as “prototype”) having the simplest configuration to be called is described in advance. Therefore, I would like to start by explaining a series of components and operating principles of the present invention.

  There are two types of the above-mentioned “prototype” due to the difference in the swing mechanism, and these are shown in FIGS. 1 and 2. FIG. 1 uses a simple pendulum-like swing mechanism. FIG. 2 shows an application of a parallel motion mechanism (referred to as a parallel link type). Both of these should be called the rudimentary prototypes of the present invention. FIG. 3 and FIG. 4 show the movements of the former two operating states in a step-by-step manner.

Now, if the outline of the mechanism of the present invention is described with the two prototypes described above, the present invention is necessarily composed of the following four components (components).
That is,
1) “Oscillation mechanism” (A) comprising a fulcrum shaft, which is a mechanism underlying the present invention, and an oscillating member (oscillating arm) that reciprocates around the fulcrum shaft;
2) A swinging body that is held at the tip of the swinging mechanism and reciprocates on an arc trajectory, and a blade that is attached to the swinging body. The blade receives the energy of the fluid flow and receives the fluid flow energy. "Oscillator" (B), which plays a role of giving excitation force to
3) “wing operation means” (C) that operates the blade according to a predetermined pattern and reverses the direction of lift to generate an excitation force;
4) “Power conversion means” (D) that uses the oscillating motion of the oscillating mechanism as a power source instead of a rotational motion.
Here, the structure and operation of each component will be briefly described individually.

First, the swing mechanism (A) is a combination of the fulcrum shaft 2 and the swing arm 3, and the normal swing arm is an elongate or beam (beam) -like long structure, and the swing arm 3 shown in FIG. The tip portion of this member serves as the moving body, and in the case of FIG. 2, includes two swinging arms 3a and 3b and a link member 4 (which also functions as a moving body) that connects the leading ends of the swinging arms. A four-node parallel movement mechanism (hereinafter, the parallel movement mechanism is also simply referred to as “swinging arm”) is configured.
1 and 2, a fulcrum shaft 2 extending in a direction substantially perpendicular to the flow direction (direction perpendicular to the plan view) is fixed to a support structure 1 (not shown), and a swing arm 3 Is a mechanism that is pivotally supported by the fulcrum shaft 2 and performs a pendulum motion evenly in the left-right direction around the flow direction (represented simply as “oscillating motion” by a reciprocating arc motion).
The plane on which the oscillating arm 3 (3a and 3b) oscillates may be either a horizontal plane or a vertical plane, and it is determined by the cross-sectional shape of the flux.
A rocking body 4 is attached to the tip of the rocking arm 3, and the rocking body 4 reciprocates on an arc locus along with the reciprocating angular movement of the rocking arm 3. It should be added that a structure in which the swing arm and the swing body are combined can be adopted.

The oscillating body (B) corresponds to an engine if the present invention is compared to an automobile or an airplane, and the oscillating body is equipped with a main wing for extracting power. As for the blade, several types of blades can be used as will be described later. First, the structure of the blade will be described by taking up the flat plate blade shown in FIG.
The wing body 11 shown in the diagram is a flat wing having a structure in which the wing portion 11a and the rotary shafts 11b and 11c are rigidly connected to the blade long end. The blades are rotatably mounted on the rocking body 4 via the rotation shafts 11b and 11c, and the angle of attack with respect to the flow is changed by rotating the rotation shaft 11b with the operation lever 24.
Further, FIG. 11 shows the shape of the camber wing, but the dimensional specifications related to the wing are shown by a diagram.
Now, the angle of attack of the wing is the inclination angle of the wing measured with reference to the direction of flow. (Counterclockwise is positive and clockwise is negative)
As a reaction of turning the direction of the flow, the blade acts as a force that pushes the blade in a direction substantially perpendicular to the blade surface. In the present specification, this force is referred to as blade force.
Usually, the wing force is handled by breaking it into two component forces by calling the component force in the direction perpendicular to the flow as lift and calling the component force in the flow direction as drag.
The ratio between the lift and drag values is called the lift-drag ratio, and is often determined by the cross-sectional shape and angle of attack of the wing, and is usually a value obtained by experiments. In the wing used in the present invention, the lift-drag ratio is 5 Larger values are recommended.
The drag of component force has both positive (loss) and negative (loss) effects, and the effect is not negligible.

That is, when the swing arm reaches either the left or right amplitude limit and the blade inversion is finished, the swing arm starts swinging in the opposite direction. Here, the moment around the fulcrum of lift and drag acting on the blade is considered. When,
If the swinging arm acts in the swinging direction as active (active) and the reverse acting in the opposite direction is negative (negative), lift is always in the swinging direction of the swinging arm. On the other hand, the drag is active as well as lift in the first half (until the swing arm passes through the swing center), but the second half (the swing arm passes through the swing center). Until the next wing inversion) works negatively, and the result of superimposing the effects of both lift and drag is all the action of the fluid acting on the wing. FIG. 7 shows a model for verifying the above contents, and FIG. 8 shows the relationship between the angle of the swing arm and the torque around the fulcrum shaft due to the blade force.
The graph shows a simulation of the torque change when the lift-drag ratio is 5. If the swing angle is within 30 °, the negative influence of the drag is negligible over the entire amplitude range. Show.
In this specification, unless otherwise specified, the force acting on the wing is expressed as lift when referring only to the component force in a direction substantially perpendicular to the fluid flow, and acts on the wing including drag. When referring to force, it shall be described collectively as wing force.
The wing force acting on the wing 5 is transmitted to the oscillating arm 3 through the moving body 4 to generate a moment about the fulcrum shaft 2, and causes the oscillating arm 3 to move in the right (or left) direction. .

The role of the blade operation means (C) is to always control the angle of attack of the blade body 11 attached to the moving body 4 with respect to the flow in association with the angular motion of the swing arm 3.
The pattern for operating the angle of attack of the wing by the wing operating means (hereinafter referred to as wing operation pattern) is independent of the posture of the moving body 4 (whether or not there is an angle change) except during the wing reversal operation (hereinafter referred to as wing reversal) Continues to maintain a predetermined angle of attack (sign is positive or negative) with respect to the flow, and immediately after the timing of blade reversal, blade reversal (sign of attack angle changes from positive to negative, or from negative to positive). ) To work.
FIG. 9 shows a time chart of the blade operation pattern.
Detailed explanations regarding the mechanism and operating principle of the blade operating means will be described in detail in separate sections (0047) to (0050).

The power conversion means (D) is power conversion means for converting the swinging motion of the swing arm 2 into a rotational motion, and the crankshaft 61 and the connecting rod 62 function as a set. The crank shaft 61 is arranged in the vicinity of the swing region of the swing arm 3 and parallel to the fulcrum shaft 2 and is rotatably supported by a bearing unit 65 attached to the support structure 1 (not shown). .
The crankshaft 61 is provided with a pair of crank arms 61b and a crankpin 61c, and a flywheel 64 is fitted and fixed to the shaft portion 61a.
The connecting rod 62 connects the connecting pin 63 fixed to the middle of the swing arm 3 and the crank arm pin 61c, and converts the swing motion of the swing arm 3 into the rotational motion of the crank shaft 61.

In the case where further explanation is required regarding these four components (A) to (D) employed in the embodiment of the present invention, supplementary explanation will be added each time.
In the following description, for simplification, the parts that swing together with the swinging arm are collectively called “movement”, and the above four components are fully functioning. A set is called a “basic unit”.
This is the end of the description of the present invention. However, each component has several variations and different methods, and various embodiments can be created by combining them. Is possible. Especially, depending on the type of rocking mechanism, there are significant differences in appearance, so before moving on to the “preferred form for carrying out the present invention” in the main topic, various deformation types (forms) of the rocking mechanism will be mentioned. I want to go.

Various deformation types of the swing mechanism in the embodiment

FIGS. 12 to 15 show four variations (variations) positioned as the basic mold of the present invention, and are expressed as follows from the characteristics of the type of each swing arm. These individual details are left to (0043) in the subsequent stage.
1) FIG. 12 shows a swing mechanism of type-1 and is called a “double-head / yoke (balance) type”.
2) FIG. 13 is a swing mechanism of type-2 and is called “single-head / cantilever type”.
3) FIG. 14 is a swing mechanism of type-3 and is called “double-headed / parallel link type”.
4) FIG. 15 shows a swing mechanism of type-4 and is called “single head / parallel link type”.
In the drawing, the wings are uniformly used as flat wings.

  FIG. 16 is a supplementary explanation of FIG. 13 and FIG. 17 is a supplementary explanation of FIG. 14, and only the “swing mechanism” (A) and “swing body” (B) are extracted and shown in perspective view. .

  Each of the figures shown in the diagram is called a single-acting type because there is only one movement (the part that oscillates), and the type in which multiple basic units that are touched next are connected is called a double-acting type. Distinguish.

The double-acting type is a form in which multiple basic units (limited to the same type) of type-1 to type-4 described in the previous section are connected (multiple) as a single engine. If the number of units to be used is N, it will be named “N Duplex”.
The mechanical coupling means that the crankshafts belonging to each other's basic units are mechanically connected to each other or replaced with a single-acting double-acting crankshaft so that they are integrated as one engine. This overlaps with the contents already described in (0016).
In the case of type-1 double-headed / cantilever type or type-2 single-headed / yoke (balance) type, each has one fulcrum shaft, and type-3 double-headed / parallel link type, Alternatively, the type-4 single-head / parallel link type has two fulcrum shafts, but in each case, the opposite fulcrum shafts are aligned coaxially and the crankshafts are connected (directly connected). ) Is no different.
In this way, the result is that multiple sets of movements and one double-acting crankshaft are combined via a connecting rod for each movement and integrated as one engine, and the appearance of a single engine is exhibited. It becomes. FIG. 18 is a perspective view when the mold-2 of the prototype is double-connected. Other components combined with the swing mechanism may be forced to change. Accordingly, the detailed description of each style based on the above classification and the components related thereto is transferred to other sections of “Supplementary explanations about components” later.

Preferred form for carrying out the invention

From here on, the “preferred form for carrying out the invention” of the subject will be referred to.
First, a general-purpose embodiment that does not limit the application location is taken as an example, and further, an embodiment in which the application target is defined as tidal current and river flow is shown.

FIG. 19 shows one embodiment of the present invention, which is a double continuous type-1 (a plan view of a double continuous type / yoke type),
FIG. 20 is an exploded view of the operation. In both figures, the flux also spreads in the vertical direction (vertical direction) with respect to the paper surface, and is a flow that wraps the entire apparatus, is parallel to the plane represented by the paper surface, and flows in the direction of the white arrow. The swing plane of the swing arm is parallel to the paper surface.
The fulcrum shaft 1 extends in a direction perpendicular to the paper surface and is fixedly installed on a support structure (not shown). In this figure, the first yoke-type swing arm and the second yoke-type swing arm, which are congruent with each other, are pivotally supported by a fulcrum shaft at the center of each of the upper and lower two stages.
Both ends of each swinging arm also function as a moving body frame, and each wing is mounted so as to be freely rotatable. In this figure, the blade operation means is not shown, but the blade operation means in this case is a remote operation type using a telescopic actuator that operates with external auxiliary power, and the blade operation means in the form shown in FIG. Is mounted on each swing arm. The crankshaft is a mechanically coupled double-acting crankshaft, and the phase difference between the two crank arms is 135 °.

Embodiments of the present invention for tidal currents

Two embodiments of the present invention for tidal currents are shown.
In the form shown in FIG. 21, a floating structure tethered on the ocean is regarded as a fixed base, and this device is mounted on this structure. It is affected by the water depth and the bottom topography compared to the case of seabed installation. In addition, there is an advantage that a salvage method is not required, and changes in the direction of the ocean current can be appropriately handled. The top view and the elevation view are shown in the dredger. The floating structure (truck) 71 is anchored and anchored on the ocean, and the columnar support structure 72 (from the bottom of the floating structure 71 toward the seabed) A suspender is attached to the lower end of the suspender, and a fulcrum shaft of the oscillating fluid power take-out device is fixedly supported in a posture extending in the horizontal direction via a support metal.
The swing mechanism used in this figure is a “triple-coupled double-head / parallel-link swing mechanism” that is a triple unit of three double-head / parallel-link swing mechanisms that are congruent to each other. FIG. 22 shows a “B” portion of FIG. 21 in a bird's-eye view. However, the blade operating means is not shown. In FIG. 21, the tidal current is parallel to the elevation plane (paper surface) and flows in the direction of the white arrow, and each movement swings on a plane parallel to the vertical plane. In addition, the crankshafts of the respective units are motively connected to each other via shaft couplings, and the phase difference of the crank arms is 120 ° which is obtained by dividing 360 ° into three equal parts. FIG. 23 is an elevation view of the seabed installation type, in which a foundation is constructed and installed on the seabed. In these two examples, the movement is submerged in seawater, and therefore, special consideration is required for seawater corrosion resistance. In particular, since the swing arm is a movable part and is a structural member as well as a strength member, it is required to be made of a material having excellent seawater corrosion resistance and high specific strength. Therefore, FRP (fiber reinforced plastic) is adopted as the structural member. Furthermore, the part which requires especially high intensity | strength can be reinforced using carbon fiber. Metal precision used in locations where precise machining accuracy and high strength are required and the use of metal materials is unavoidable, such as fulcrum shafts and crankshafts, where the metal surface is directly exposed to seawater It is necessary to select parts considering seawater corrosion resistance and wear resistance, and aluminum bronze and titanium alloys are recommended.

FIG. 24 is a general view of a form in which the present invention is specialized for a river flow, and shows a plan view and an elevation view. The swing mechanism employed in this embodiment is a modification of type-1 (double-head / yoke-type swing mechanism), and the notable point is that two single units having different lengths are stacked in two stages. It is a connected point. That is, the lengths of the first swing arm and the second swing arm are different, and the wing dimensions are also different. In this embodiment, only the blades are submerged in the flow, most of the swing mechanism is at a position higher than the surface of the water flow, and the common fulcrum shaft extends in the vertical direction at the approximate center of the flow. It is fixed and installed. The first swing arm and the second swing arm are supported on the fulcrum shaft at a point near the center of each arm length in order from the bottom at a position higher than the water surface. Is in a swingable state. This is a consideration for eliminating unnecessary resistance that the swing arm receives from water. The first swing arm and the second swing arm have different lengths, but both have wings attached to both ends of the arm. The wings mounted on each of the first swing arm and the second swing arm are in separate space areas and do not interfere with each other. Here, since the arm length of the first swing arm is shorter than the arm length of the second swing arm, the blade attached to the first swing arm is swung compared to the blade attached to the second swing arm. Consideration has been made to ensure that both moments are approximately equal by providing the ability (lift magnitude) inversely proportional to the length ratio of the moving arm. Further, the integrated crankshaft of the power conversion means in this case has two crank arms, the arm radii of each crank arm are equal, and the phase difference between the two crank arms is 135 °. The first swing arm and the second swing arm have pins for joining to the connecting rods at a radius R from the fulcrum shaft, respectively, and are connected to the opposite crank arms of the crank shaft by connecting rods. Has been. The swing arm used in the present embodiment is a bowl-like structure, and the required characteristic as a structure is a box cross section or a truss structure to minimize deformation against bending and twisting, and FRP (fiber reinforced plastic) with high specific strength is used to reduce weight. In this case, it is desirable to select the resin to be used in consideration of the countermeasure against ultraviolet rays.
The blade rotation axis is cantilevered.

Other supplementary explanations for the examples

Now, the description of the swing mechanism shown in FIGS. 12 to 15 will be added again without overlapping the description of the embodiment of the present invention. Each type described here is a single-acting type. However, in practice, a plurality of sets are linked and connected in principle.
1) Type-1 “Double-headed, yoke (balance) type”
The mold-1 shown in FIG. 12 is pivotally supported on a fulcrum shaft at one point substantially in the center in the longitudinal direction of the swing arm, and a movable body having blades attached to both ends of the swing arm is a rigid body. Connected. (This part may be called the head)
In this case, the wings mounted on both heads are operated so that the attack angles are opposite (positive / negative) so as to generate a couple. In the case of this type, the oscillating arm can also serve as a moving body by attaching a wing directly to the tip of the oscillating arm.
2) Type-2 “Single-head / cantilever”
The mold-1 shown in FIG. 13 is balanced to eliminate one of the swinging arms from the fulcrum shaft of the double-head / yoke (balance) mold of the mold-1 and eliminate the static imbalance around the fulcrum shaft. A weight is attached, and it is pivotally supported on a fulcrum shaft at one point biased to one end of the swing arm, and a moving body with wings is rigidly connected to the other end. And the heel swings like the pendulum of a pendulum clock. In the case of this type as well, as in the previous section, the swinging arm can also serve as the moving body by attaching the wing directly to the tip of the swinging arm.
3) Type-3 “Double-headed / Parallel link type”
The swing mechanism of type-3 shown in FIG. 14 is a so-called “parallel link” modification in mechanistics.
An inherent parallel link is a form of a four-bar linkage mechanism, where four links are parallelograms, one of the four links is a fixed link, and the parallel links are located on opposite sides of the fixed link. The moving link reciprocates on the circular arc locus while being always parallel to the fixed link.
This double parallel / parallel link type is obtained by modifying the original parallel link as follows. In other words, both ends of the fixed link having the link length S and two links having the same shape (referred to as swing links) are individually pin-joined (axially supported) at the left and right end points of the fixed link at one central point. The two swing links are connected by two translation links with a link length of S between the two end points of the two swing links. It moves back and forth. In the double-head / parallel link type, the fixed link corresponds to a line segment connecting two fulcrum points (centers of fulcrum axes), that is, the two fulcrum axes are parallel to each other and the distance between them is S. The line connecting the cores of the two fulcrum shafts is perpendicular to the flow of the fluid, and the two swinging arms with the same shape are at a single point in the center and can be freely rotated on each fulcrum shaft individually. The two oscillating links are angularly supported by the shaft, and the two oscillating arms are connected to the both ends of the oscillating arms by the parallel moving links with the link length equal to the distance between the fulcrum shafts. A parallelogram is formed. As a result, the two parallel movement links reciprocate on the circular locus while always being parallel to the line connecting the two fulcrums. {In this case, strictly speaking, one of the two rocking links is one rigid body, and the other rocking link is pin-joined (divided) rocking at the position of the fulcrum shaft. It must be a dynamic link. Note that the oscillating body can be joined and held by two parallel moving links, or the oscillating body itself can also serve as the translating link. One or more wings are mounted on the rocking body along the axis thereof.
4) Type-4 “Single-head / Parallel link type”
The swing mechanism of the mold-4 shown in FIG. 15 is a modification of the double-head / parallel link type of the above-described mold-3, and one side ahead of the respective fulcrum shafts of the two swing-arms of the double-head / parallel link type. (Same side) is cut out and a balance weight is attached to eliminate static imbalance around the fulcrum axis. That is, the two fulcrum shafts are parallel to each other and the distance between them is set at S, and the line connecting the cores of the two fulcrum shafts is perpendicular to the fluid flow, and the same arm length is attached to each fulcrum shaft. Each of the two swinging arms having a length is individually pivotally supported on a fulcrum shaft at one point biased to one end, and at the other end, one translation link having a link length S is supported. The parallel movement link reciprocates on the circular arc locus while always being parallel to the line segment connecting the cores of the two fulcrum shafts. Note that the oscillating body can be joined and held on the translation link, or the oscillating body itself can also serve as the translation link. One or more wings are mounted on the rocking body along the axis thereof.

Supplementary explanation about other components

  An embodiment of each component other than the rocking mechanism and its modified or different methods will be described separately below.

但し、Ｎ＝２即ち二重連の場合は特例として、位相差を１２０°〜１５０°とすることが望ましい。これは二つのクランクアームが同時に死点に在ることを回避すると共に、揺動角によるトルク特性を平均化する意味からである。図２５に三重連した場合のクランク軸の斜視図をしめしておく。 With regard to the crankshaft of the power conversion means, in the double-action type having a plurality of movements, the crankshaft has the same number of crank arms as the movement and is called a double-action type crankshaft. It is as follows.
That is, it is strictly avoided that the crank arms are arranged at the same angle, and with respect to the relative angle (phase) of each other, the phase difference in the case of the N-fold series is basically assigned as follows.

However, in the case of N = 2, that is, in the case of double ream, as a special case, the phase difference is desirably set to 120 ° to 150 °. This is because the two crank arms are avoided from being at the dead point at the same time, and the torque characteristics according to the swing angle are averaged. FIG. 25 is a perspective view of the crankshaft when triple-connected.

  Similarly, with regard to the power conversion means, by connecting a small speed reduction motor to one end of the crankshaft via a clutch, it is possible to make the start easy during the start operation of the present invention.

  As for the blade operation means, there are two methods, that is, a method using an actuator that operates with external auxiliary power and a method that uses a part of the energy stored inside without using external auxiliary power.

In the blade operation means that uses external auxiliary power, an actuator is used. In that case, there are two methods, a remote operation method and a direct acting method. Depending on the combination of the swing mechanism, the remote operation method or the direct acting method is available. One of these will be selected. That is, in the case of the yoke type, the swinging arm always performs an angular motion, and therefore the angle of attack of the blade cannot be controlled based on this. For this reason, a remote control method using a link mechanism must be adopted.
On the other hand, in the case of the parallel link type, the moving body (parallel link) always moves in a posture perpendicular to the flow, so the angle of attack of the wings can be manipulated based on the moving body itself. The actuator can be directly mounted on the moving body. That is, it is possible to adopt a direct acting system.

  Details of the blade operating means operated by the actuator will be described with reference to FIGS. FIG. 26 is a partial detail view of the blade operating means adapted to FIG. 12 (or FIG. 13). The は diagram is an example of a remote control type using an extendable air cylinder as the actuator (a type that can stop at an intermediate position is desirable for starting and stopping the device). The mechanism and function of the blade operating means will be described. The air cylinder 21 shown in the drawing is a head side trunnion type, and is supported by a pin fitting to a support fitting, and the support fitting is fixed to a support structure not shown in the figure at a position close to the fulcrum shaft. Has been. The expansion / contraction operation of the air cylinder 21 is transmitted to the rotating shaft of the blade at the tip of the swing arm by the link mechanism and functions to reverse the angle of attack of the blade by remote operation or to maintain a predetermined angle of attack. The drive lever 22 of the link mechanism is pivotally supported by a lever shaft 20 on an extension line of the fulcrum shaft 2 and is pushed and pulled by the expansion and contraction of the air cylinder 21. The movement of the drive lever 22 is transmitted via a connecting rod 23 to a blade turning lever 24 that is fixedly mounted on the blade operating shaft. The link mechanism includes a swing arm 3 and constitutes a so-called parallel link. Even when the swing arm 3 changes the swing angle by a swing motion, the air cylinder 21 is not in the blade reversing operation. Adhering to one of the "extended" and "contracted" states, the wing is held at a predetermined angle of attack and its sign is positive (+) or negative (-). In addition, the angle of attack of the wing can be reversed from positive to negative or from negative to positive during the reversing operation. FIG. 27 is a partial detailed view of blade operating means applicable to the parallel link type. (Type-3 / Type-4) In the case of the parallel link type, the moving body 4 (parallel link) always moves while maintaining a substantially perpendicular posture with respect to the flow. You can manipulate the corners. Therefore, the actuator 31 can be directly mounted on the moving body. That is, as shown in the drawing, a rotary actuator (RA) 31 of a swing lever type is directly attached to the moving body, and the output lever of the RA and the blade turning levers 33 and 34 are connected, thereby reversing the blade. Allows retention.

  Regarding the method not using the external auxiliary power, the method of using the rotational energy stored in the flywheel mounted on the crankshaft as the power source in the item (0011) has already been described, but a more detailed explanation will be added again. FIG. 28 applies the intermittent operation of the Geneva mechanism. While the input shaft (driver) 43 of the Geneva mechanism rotates 360 °, the output shaft (follower) 46 is, for example, a four-leaf wheel. While the follower is in a paused state during a rotation angle of 270 °, the follower is driven only during the remaining rotation angle of 90 ° to perform GO-STOP motion that rotates 90 °. That is, by connecting the crankshaft and the input shaft with a gear train having a gear ratio of 1: 2, the driver rotates once during the half rotation of the crankshaft, and accordingly, the follower rotates for 3/4 cycle. Rotate 90 ° with GO for ¼ cycle with STOP. If the rotation of this output shaft is doubled and transmitted to the crankshaft for blade reversal, rotation of 180 ° can be obtained, and if it is converted to linear reciprocating motion by driving the crank arm, it is a direct acting actuator Can perform the same function. That is, while the crankshaft makes one revolution, the crankshaft for blade reversal performs STOP-GO twice and repeats the 180 ° turn twice. FIG. 27 shows an example using a four-leaf geneva mechanism as a specific form of the above description, but it is recommended to use six to eight-leaf geneva in order to perform inversion in a shorter time. Is done.

FIG. 29 to FIG. 32 show four types as examples of the blades employed in the present invention.
Each wing has its own merits and demerits, and the qualities of each are compared.
First, although the flat blade shown in FIG. 29 is inferior in performance to others, it has a simple structure, excellent durability, and the lowest cost. On the other hand, the bent wing of FIG. 32 is the most expensive in terms of performance, but is the most expensive because of its complicated structure. The sail-type wing shown in FIG. 30 is located between the flat wing and the bent wing in terms of performance and requires daily maintenance, but is relatively inexpensive in terms of cost. The shovel type wing shown in FIG. 31 can be used in a camber wing shape, and therefore can be designed with an emphasis on wing performance and is excellent in durability. However, it is necessary to rotate 180 ° in order to reverse. It is different from the format. Since the moving body is used as a reference for inversion, it can be used only for the parallel link type. In consideration of the above characteristics, selecting the one that seems to be preferable according to the application conditions also contributes to enhancing the cost effectiveness of the facility. For reference, the names of specifications that define the shape of the wing are shown in FIG.

The present invention opens up the path of mainly utilizing the energy of an unused fluid flow that has been overlooked for power generation by using inexpensive equipment as power. Applicable objects can be found everywhere. Needless to say, a gas flow can be applied if the flow direction and flow rate are relatively stable. As for the water flow of the river, a promising part can be easily found by examining the vicinity of the river mouth. If you turn your eyes to tidal currents and tidal currents, promising candidate subjects have no time to enumerate. Some of the specific examples of promising objects include:
・ The Kuroshio and Oyashio currents flow in the Tsugaru Strait, which is a very promising part.
・ Regarding tidal currents, for example, there is a large concentration of flow in the Saikai Strait, where Omura Bay meets the open sea, and there are promising tidal currents everywhere in the Seto Inland Sea.
・ If we meditate on the disadvantage of the separation distance from the land, it is an exaggeration to say that the two major tides of the Kuroshio and Oyashio currents flow along the coast in the ocean surrounding Japan, and that the total energy is literally inexhaustible. No way.

The structure of the single head and pendulum type which is the first prototype of the present invention is shown. The structure of the single head / parallel link type which is the second prototype of the present invention is shown. It is a figure for demonstrating operation | movement of the 1st original form shown in FIG. 1, and it decomposed | disassembled a series of movement and put it in order. In order to explain the operation of the second prototype shown in FIG. 2, a series of movements are disassembled and arranged in order. It is a figure explaining that there exists an effective part (margin) besides the restricted swinging region, taking a single head / pendulum type as an example. The higher the wing lift-drag ratio, the greater the margin and the greater the load. In addition, the margin works positively to overcome the thought point. The figure which shows the relationship between the space | interval l from the fulcrum axis | shaft of a rocking | swiveling arm to a connecting pin, the crank radius r, and rocking angle (theta). A model to verify the effects of lift and drag acting on the wing on the angle of the swing arm and the moment around the fulcrum. The characteristic curve which shows the relationship between the angle of the rocking | fluctuating arm of FIG. 7, and the moment around a fulcrum. Sequence diagram (time chart) of blade operation means. The figure which shows the structure of a wing | blade with a flat blade. It is a figure which shows the name of the dimension item concerning a wing | blade for a camber wing | blade as an example. It is a swing mechanism of “double head / yoke (balance) type” classified into type-1. It is a “single-headed / cantilevered” swing mechanism that is classified as type-2. This is a swing mechanism of “double-headed / parallel-link type” classified into type-3. It is a “single head / parallel link type” swing mechanism classified into type-4. It is a perspective view of the rocking | swiveling part of type | mold-2. It is a perspective view of the rocking | swiveling part of type | mold-3. This is a form in which Type-2 (single head / cantilever type) is double connected. Double-link double-head / yoke-type embodiment The operation | movement exploded view of FIG. An embodiment for tidal currents, a triple-link double-headed / parallel-link embodiment mounted on a support structure suspended from the floating structure (ship) anchored offshore. And shown in plan and elevation views. The perspective view of the "B" part of FIG. This is an embodiment for tidal currents, and is a double-linked double-headed / parallel-link type (deformation type) embodiment in which a support structure is installed on the seabed. A double-headed, yoke-type embodiment specialized for river use. This is a double action type crankshaft for triple use. The example of the wing | blade operation means using an expansion-contraction type actuator. An example of parallel link type blade operation means using an oscillating lever actuator (rotary actuator). An example of blade operation means that uses the Geneva mechanism with the inertial force stored in the flywheel as the power source, regardless of the auxiliary power. It is explanatory drawing of angle-of-attack reversal of a flat wing, and shows the state before and behind operation with a perspective view It is explanatory drawing of angle-of-attack reversal of a sail type wing, and shows the state before and behind operation with a perspective view It is explanatory drawing of the angle-of-attack reversal of a shovel type wing | blade, and shows the state before and behind operation | movement with a perspective view. It is explanatory drawing of the angle-of-attack reversal of a bending wing | blade, and shows the state before and behind operation | movement with a perspective view. With respect to the prior art, the force acting on the wings in the running state is shown in the diagram as shown in the figure. With respect to the prior art, the force acting on the blade in the blade reversal process is shown as a diagram in the drawing.

1 support structure 2 fulcrum shaft 2a fulcrum shaft A
2b fulcrum shaft B
3 Oscillating arm 3a Oscillating arm 3b Oscillating arm 4 Oscillating body 11 Wing body 11a Wing plate 11b Rotating shaft A
11c Rotation axis B
20 Lever shaft 21 Telescopic actuator 22 Drive lever 23 Connecting rod 24 Wing rotation lever 25 Limit switch 31 Oscillating actuator 32 Connecting rod A
33 Wing swivel lever A
34 Wing swivel lever B
35 Linkage B
36 limit switch 41 input gear 42 pinion 43 input shaft 44 Geneva drive wheel 45 Geneva driven wheel 46 driven shaft 47 output gear 48 pinion 49 crank arm 50 slider 51 guide rail
61 Crankshaft 62 Connecting rod 63 Connecting pin 64 Flywheel 65 Bearing unit 66 Shaft coupling 71 Floating structure (float)
72 Columnar support structure (suspender)
81 Guide shaft 82 in the prior art Moving body 83 in the prior art Wings 84 in the prior art Stopper in the prior art

Claims (15)

 By regularly and repeatedly reversing the angle of attack of the blade facing the fluid flow, the lift acting on the blade is modulated into an alternating force, and the alternating force is used as an excitation force to continuously swing the swing mechanism. Is used to convert the reciprocating angular motion of the oscillating mechanism into a rotational motion and use it as a power source.  The fulcrum shaft in the oscillating mechanism extends in a direction substantially perpendicular to the flow direction and is fixedly installed. The fulcrum shaft is pivotally supported by the fulcrum shaft and swings with the flow direction as a reference (center). An oscillating body that dynamically moves, a moving body that is held by the free end of the oscillating body and reciprocates on an arc locus, a wing that is rotatably mounted on the moving body via a wing rotation shaft, and the wing Blade operating means for operating the rotating shaft to reverse the angle of attack of the blade with respect to the flow in accordance with a predetermined repetitive pattern; and power conversion means for converting the reciprocating angular motion of the oscillator into a constant direction rotational motion. The oscillating fluid moving device according to claim 1. The swing mechanism is composed of a combination of one fulcrum shaft and one swing arm,
The fulcrum shaft is fixedly installed on a separately constructed structure in a posture extending in a direction substantially perpendicular to a horizontal plane or a vertical plane including a flow direction (vector), and the flow is the main oscillating fluid. We are responsible for the force exerted on the power take-out device,
The swing arm is a long and narrow girder-like structure when viewed from directly above the swing plane, and the movable body is attached to the tip of the swing arm or the tip of the swing arm The oscillating fluid power device according to claim 1 or 2, wherein a part has a function of the movable body. The swing mechanism applies the principle of a so-called parallel motion mechanism, which is a form of a double lever mechanism, and is parallel to the flow with a distance S between the axes. Two oscillating arms having the same link length and congruent with each other are pivotally supported on each of the two fulcrum shafts fixed to the fulcrum, and one or both of the oscillating arms can be freely supported. A parallel motion mechanism that appears by connecting ends with a connecting member having a link length of S,
The oscillating fluid power device according to claim 1, wherein the moving body is joined to the connecting member, or the connecting member itself plays a role of the moving body.   A single oscillating fluid power take-off device created in connection with claim 3 or claim 4 having the same configuration (referred to as a basic unit) is combined in two or more sets to make an apparent number of 2. The oscillating fluid power device according to claim 1, wherein the oscillating fluid power unit is integrated with one engine having the oscillating mechanism, and at the same time, a phase difference of oscillating motion is provided between the oscillating mechanisms.  The blade operating means reverses the sign of the angle of attack of the wing from positive to negative or from negative to positive (attack angle reversal) at the moment when the swing arm reaches the left or right amplitude limit. The oscillating body moves the direction of movement of the oscillating body while the wing does not move during other than the angle-of-attack reversing operation. The oscillating fluid power unit according to any one of claims 1 to 5, wherein the oscillating fluid power unit is a blade operating unit that functions to maintain.  The blade operating means includes an actuator that operates with auxiliary power, a transmission system that transmits the output of the actuator to the blade (via a distributor if necessary), a sensor that detects the position of the swing arm, The oscillating fluid power device according to any one of claims 1 to 6, wherein the oscillating fluid power device is a blade operation unit including a programmable controller that controls the movement of the actuator.  The blade operating means uses a part of rotational energy stored in a flywheel mounted on a crankshaft as a power source, and combines the gear train and the intermittent operation principle of a Geneva mechanism. 7. A mechanical blade operating means that does not rely on external auxiliary power and that operates in accordance with the timing at which the shaft passes through the dead center to reverse the angle of attack of the blade. The oscillating fluid power device described in 1.  The blade is capable of reversing the direction of lift received from the flow by operating a blade operation shaft, which is a part of the blade, from the outside, and is held by the moving body via the blade operation shaft. The oscillating fluid power device according to any one of claims 1 to 8, wherein  The blade is a slender spindle-shaped flat blade whose cross-sectional shape is symmetrical with respect to the neutral line of the thickness, and is located at a position biased to the front edge side between the leading edge and the trailing edge from the blade width end surface to the blade width direction. 10. A blade operating shaft protruding in the shape of the blade, and the blade operating shaft is pivotally supported by the movable body through a bearing. The oscillating fluid power device according to item.  The wing is constituted by a combination of a rectangular frame made of an elongated material and a canvas or sheet-like membrane material, and the membrane material is stretched as a peripheral fixing inside the rectangular frame, and the membrane material is In response to the flow of the fluid, it is a sail-type wing that bulges in a convex shape on the side of the pressure-receiving surface and the membrane material has a circular arc shape and functions as a so-called arc wing, from the middle of the rectangular frame to the front It is equipped with a blade operation shaft that protrudes in the vertical direction from the upper and lower sides at a position biased to the side, and the direction of lift is reversed by turning the blade operation shaft upside down to reverse the bulge of the membrane material The oscillating fluid power device according to any one of claims 1 to 9.  The wing is an articulated bending wing, and segments divided into at least two in the chord length direction are connected to each other by pin joints so that they can be bent, and the cross-sectional shape when bent is a camber wing. A composite wing that has an approximate cross-sectional shape. One segment located at a position deviated from the middle in the chord length direction to the front side has a wing operation shaft that protrudes in the wing width direction. Or, by swiveling to the right, the composite wing has a mechanism in which the cross-sectional shape of the camber wing is a mirror object, and the direction of the lift is reversed, by bending forward or backward. The oscillating fluid power device according to any one of claims 1 to 9, wherein the oscillating fluid power device has a function to be enabled and is attached to the moving body via the blade operating shaft.  The oscillating mechanism is a parallel motion mechanism according to claim 4, wherein the wing is an excavator-type wing, and the excavator-type wing is mounted on a parallel moving body via a rotating shaft. The oscillating fluid power device according to any one of claims 1 to 9.  The power conversion means is composed of one crankshaft, a pair of bearings for freely supporting the crankshaft, and one connecting rod, and one flywheel is fitted and fixed to the crankshaft. The connecting pin attached at a suitable point in the middle of the swing arm and the crank arm pin of the crankshaft are connected by the connecting rod to reciprocate the swing arm to rotate the crankshaft. The oscillating fluid power device according to claim 1, wherein the oscillating fluid power device is converted into motion.  In connection with claim 5, the power conversion means in the case of connecting and integrating a plurality of basic units is a structure in which the crankshafts attached to each basic unit are joined together by means such as a shaft coupling, or instead of being joined together. By replacing the double-acting crankshaft, the outputs of a plurality of basic units are combined, and in this case, the assignment of the crank arm is performed when the N single units are combined. As a general rule, the phase difference of the crank arm should be 360 ° for N minutes. However, with the exception of the phase difference between any two crank arms being 180 °, the phase of one crank arm is advanced or delayed by 30 ° or more to avoid this, and each other is considered at the same time (above The swing type power take-off device according to claim 14, wherein consideration is given to avoid being at bottom dead center.

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