JP2887126B2 - Fluid actuating device using swing fulcrum type lever device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid operating device using a swing fulcrum type lever device applied to, for example, a hydro turbine, a wind turbine, a wind turbine, a fluid pump, and the like.

[0002]

2. Description of the Related Art Fluid power generation, that is, wind power generation and hydroelectric power generation, are performed by rotating a windmill or waterwheel with kinetic energy caused by wind force or water falling, and rotating the windmill or waterwheel to rotate a generator. . A conventional water turbine is shown in FIG.
As shown in FIG. 3A, the blades 161a radially arranged at an angle of 60 degrees in the circumferential direction from the center of the water wheel 160,
161b are arranged so as to apply a water flow 162 having a flow rate Fc to the water wheel 160 to rotate in the direction of arrow A.

In this case, if the length of the blades 161a, 161b...
The torque T0 of rotation at the center C is T0 = r · Fc
It is represented by

For example, when the blade 161a comes to a position on a line connecting CS, the tip of the blade 161a becomes the surface 162a of the water flow 162.
The blade 161a receives a driving force from the water flow 162, rotates the water wheel 160, rotates 60 degrees, and
When it comes to the position, the tip moves away from the water flow 162.

When the blade 161a is at the CE position, the next blade 16
Since 1b comes to the position of CS, the water wheel 160 continuously rotates at a rotation speed corresponding to the flow velocity of the water flow 162.

For example, in a water turbine in which the blades are arranged at intervals of 30 degrees, if the three blades are always configured to receive water pressure, the angle of the blade at which substantially 90% efficiency can be obtained is 90 degrees ± The angle is 15 degrees, that is, as shown in FIG. 13B, the water flow direction is zero degree, and the range is from a position rotated 75 degrees from this to a position rotated 105 degrees.
The distance between the blades should be 3 so that the water flow always hits this area.
If it is set to 0 degree, the torque always holds a value near the peak value as shown in FIG.

[0007]

As will be understood from this description, in the conventional water turbine 160, only a fraction of the blades of the entire water turbine actually receive power from the water flow 162. Yes, the other wings are playing. For this reason, the equipment cost and idle space occupancy of the water turbine 160 in the hydroelectric power generation equipment are extremely large.

In the position where the water surface is indicated by 162a, the section where the blades 161a receive power from the water flow 162 is at a rotation angle of the water wheel 160 of 60 degrees. What is necessary is just to bring it to the position of 162b near the center C, for example. At this position, the rotation angle of the water wheel 160 is 120 degrees during the period when the blade 161a receives power from the water flow 162, but during the period when the blade 161a moves from S to S 'and E to E', The angle of the blade 161a with respect to the direction becomes small, the power received by the blade 161a from the water flow 162 becomes small, and the efficiency is poor.

On the other hand, as a fluid pump for rotating such a water turbine by the power of a motor, there are, for example, a viscous pump and a sirocco fan, all of which have a water turbine structure provided with blades all around. In addition, the flow path of the fluid is bent in a circular shape, and particularly in the case of a viscous body, the resistance increases and the efficiency becomes extremely poor. It is particularly inconvenient for pumping ready-mixed concrete.

Accordingly, an object of the present invention is to provide a fluid operating device using an oscillating fulcrum type lever device that can be reduced in size to a fraction of that of a conventional water turbine and can use power with high efficiency. I do.

[0011]

According to the present invention, there is provided a water turbine comprising: a pair of guide plates extending in a direction crossing a flow line of a fluid outside a fluid; a support member moving along the inside of the guide plates;
A lever member having a fulcrum pivotally supported by the moving support member, a pressure receiving blade formed at the point of force of the lever member and receiving the fluid pressure of the fluid, and the pressure receiving blade coupled to an action point of the lever member; It comprises a crank device for converting the movement of the lever member generated by receiving the fluid pressure into a rotational movement of the output shaft, and means for returning the pressure receiving blade from its end point to its start point.

Further, the fluid pump of the present invention has a fluid passage through which a fluid flows, a pair of guide plates extending in a direction crossing a flow line of the fluid flowing through the fluid passage, and a support moving along the inside of the guide plate. A lever member having a fulcrum pivotally supported by the moving support member, an operating blade formed at an action point of the lever member to apply pressure to the fluid, and coupled to a force point of the lever member And a crank device that receives power from the motor via an input shaft and transmits the power to the lever member.

With the configuration of the above-mentioned water turbine, a fraction of the conventional
The same torque can be generated at the same size, and the above-described configuration of the fluid pump enables the flow path of the viscous material to be made linear, so that a small and efficient fluid operating device such as a water wheel and a fluid pump is provided. it can.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 is a front view schematically showing the configuration of a first embodiment in which the present invention is applied to a water turbine, and a pair of water flow 10 having a flow velocity Fc extending in a direction crossing a streamline indicated by an arrow 10F. Are fixed to the frame via support members (not shown).

A roller 12 that moves vertically along the guide plates 11a and 11b is inserted inside the guide plates 11a and 11b. A fulcrum portion 13a at one end of a lever member 13 is pivotally supported by the roller 12. The other end of the lever member 13 is formed as an emphasis point.
The pressure receiving blade 14 receiving the fluid pressure is fixed.

An action point 1 is provided at an intermediate portion of the lever member 13.
3c is formed, and this action point 13c is
5 This crank arm 15 has an output shaft 16
The pressure receiving blade 14 is a device for converting the movement of the lever member 13 generated by receiving the flow pressure of the water flow 10 into the rotational movement of the output shaft 16.

Although not shown, the output shaft 16 is connected to a generator via, for example, a flywheel and a belt, thereby constituting a hydroelectric power generation facility.

When the pressure receiving blade 14 is located at the position 10a on the surface of the water flow 10, the roller 12 is located at an intermediate position between the position indicated by the two-dot chain line and the position indicated by the solid line.
Move forward under the pressure of
, And the tip of the pressure receiving blade 14 at this time draws a locus 17.

The other half of the trajectory 17 is drawn when the tip of the pressure receiving blade 14 returns from the position 10b to the position 10a. In this way, the trajectory 17 becomes a flat elliptical closed curve. In this latter half, the pressure of the water flow 10 does not act on the pressure receiving blade 14, and the tip of the pressure receiving blade 14 returns from the position 10 b to 10 a by the rotational force accumulated in the flywheel (not shown) connected to the output shaft 16. The return force may be applied by using, for example, a weak spring instead of the flywheel.

The tip of the pressure receiving blade 14 is moved from the position 10a to the position 10b.
When the lever member 13 moves, the lever member 13 moves between the points 10a and 10b of a part of the circumference of the circle 18 centered on the intermediate position between the fulcrum 13a, which is the axis of the roller 12 indicated by the two-dot chain line, and the center C. The robot moves along an elliptical trajectory 17, and its moving angle is about 30 degrees in this embodiment. In this manner, when the tip of the pressure receiving blade 14 moves from the position 10a to the position 10b along the locus 17 and returns to the position 10a, the action point 13c
Goes around the output shaft 16. At this time, assuming that the length of the lever member 13 is r, the torque T0 received by the lever member 13 is T0 = r · Fc due to the fluid pressure Fc, which is the same as that of the conventional water wheel 160 in FIG.

The movement of the pressure receiving blade 14 from the position 10a to the position 10b along the trajectory 17 in this way means that the blade 161a of the conventional water turbine 160 shown in FIG. Is equivalent to Assuming that the angle from S to E is 30 degrees in a conventional water turbine, the water turbine 16
0 itself rotates 30/360 = 1/12, that is, one-twelfth of one rotation.

On the other hand, in the embodiment shown in FIG. 1, the output shaft 16 makes a half turn with the movement of 30 degrees. In consideration of the return, the output shaft 16 makes one rotation at 60 degrees. The output shaft 16 is rotated at the rotation speed. In the embodiment of FIG. 1, if the angle at which the blade 14 receives the pressure of the water flow 10 is set to 60 degrees, the reciprocating angle is 120 degrees. As described above, in this embodiment, the same torque as that of the conventional device can be obtained by using a device having a size several times smaller than that of the conventional device, and the torque causes the output shaft 16 to rotate several times. It can be seen that a doubled one is obtained.

FIGS. 2 and 3 show an embodiment in which two water turbines of the embodiment of FIG. 1 are arranged side by side, and these two are the same as those of FIG. 1, respectively. The same reference numerals as in FIG. 1 are used.

In the embodiment shown in FIGS. 2 and 3, a pair of guide plates 11a and 11b extending in a direction perpendicular to the streamline of the water flow 10, a roller 12 moving along the inside of the guide plates 11a and 11b, A fulcrum 13 pivotally supported by the moving roller 12
a of the lever member 13 having a.
Pressure-receiving blade 1 formed in 3b and receiving the flow pressure of the water flow 10
4 and a crank arm 15 that is coupled to the action point 13c of the lever member 13 and converts the movement of the lever member 13 generated by the pressure receiving blade 14 receiving the flow pressure of the water flow 10 into the rotational movement of the output shaft 16. First water turbine unit 18 having
And the first water turbine unit 1 with the output shaft 16 interposed therebetween.
A crank arm 25 coupled to the output shaft 16 with a phase difference of 180 degrees from the crank arm 15 of FIG.
It comprises a second water turbine unit 19 formed similarly to the first water turbine unit 18.

That is, the second water wheel unit 19 has a roller 22 that moves along the inside of a pair of guide plates arranged similarly to the guide plates 11a and 11b, and is rotatably supported by the moving roller 22. Lever member 23 having fulcrum 23a
A pressure receiving blade 24 formed at the point of force 23 b of the lever member 23 and receiving the flow pressure of the water flow 10;
And a crank arm 25 which is connected to the action point 23c, and converts the movement of the lever member 23 generated by the pressure receiving blade 24 receiving the flow pressure of the water flow 10 into the rotational movement of the output shaft 16. FIG. 3 is a perspective view of the embodiment shown in FIG.

In the embodiment of FIG. 2, the two turbine units 18 and 19 are connected to each other with a phase difference of 180 degrees by a crank device. When in the position of 10a, the second
The blade 24 of the water turbine unit 19 is located at the position 10b in FIG. 2 (b). Therefore, while the blades 14 of the first water turbine unit 18 come from the position 10a to the position 10b in FIG. 2B, the blades 24 of the second water turbine unit 19
It returns from the position 10b of (b) to the position 10a.

On the contrary, the blade 2 of the second water turbine unit 19
When 4 is at the position 10a in FIG. 2B, the blade 14 of the first water turbine unit 18 is at the position 10b in FIG. 2B. Therefore, while the blades 24 of the second water turbine unit 19 come from the position 10a to the position 10b in FIG. 2B, the blades 14 of the first water turbine unit 18
It returns from the position 10b of (b) to the position 10a.

Thus, the first and second water turbine units 18 and 19 continue to operate with a phase difference of 180 degrees from each other, and the output shaft 16 continues to rotate. Here, the first and second
The blades 14 and 24 of the water turbine units 18 and 19 respectively move on the trajectory 17 of FIG. 2B with a phase difference of 180 degrees from each other, but the water flow 10 at the position 10a corresponding to the zero position of the elliptical trajectory 17 respectively. And the elliptical trajectory 17
Is released from the water flow 10 at a position 10b corresponding to the 180-degree position.

Here, the first and second water turbine units 18,
Assuming that the movement angle of each of the 19 blades 14 and 24 is 30 degrees, the output shaft 16 makes one rotation twice at 30 degrees, that is, at 60 degrees. That is, in the embodiment of FIG.
The output shaft 16 is rotated at six times the number of rotations as compared with the conventional example of FIG.

Since both the blades 14 and 24 come out of the water surface at the position of 180 degrees of the elliptical trajectory 17, there is no loss due to the resistance of the water, and the pressure of the water flow is efficiently reduced by the output shaft 16 The power can be obtained by converting the rotation into rotation.

Further, in the embodiment shown in FIG. 2, since driving is performed with a phase difference of 180 degrees from each other, all vibrations of second and higher order are canceled out, which is extremely convenient. Also, unlike the embodiment of FIG. 1, rotation continues even without a flywheel or the like. However, as shown in FIG. 3, a flywheel 28 is provided on the output shaft 16 and a belt 29 hung on the flywheel 28 is If the generator 30 is driven via the motor, smoother rotation can be realized.

The first and second water turbine units 18, 1
Assuming that the moving angle of each of the wings 14 and 24 is 30 degrees, the two wings 14 and 24 are arranged at intervals of 30 degrees just as in the conventional waterwheel 160 shown in FIG. Therefore, the output torque curve is also as shown in FIG.

That is, if the blades 14 and 24 are arranged so as to move within a range of 75 ° to 105 °, which is 90 ° ± 15 ° at which 90% efficiency can be obtained in the conventional case, 90% efficiency can be obtained. It can be maintained. Here, this conventional 75
Range from 105 degrees to 105 degrees.
As described above, in the case of (1), it is equivalent to 0 to 180 degrees.
With the use of 4 and 24, an output with a rotation speed six times that of the related art is obtained.

The torque generated when the blades 14, 24 move from the position 10a to the position 10b in FIG. 2B substantially follows a sine curve.
The operation is extremely stable because it does not include a vibration component higher than the next order.

FIG. 4 shows a two-part configuration of the embodiment of FIGS.
This is an example in which four pieces are connected to each other. In this embodiment, four water turbine units 31, 3 shown in FIG.
Action points 31a, 32a, 33a, 34 of 2, 33, 34
The position of the output shaft 16 in FIG. 3A, that is, the position of the crank arm on the crankshaft is arranged with a phase difference of 90 degrees from each other as shown in FIG. 3B.

FIG. 4B shows four water turbine units 31,
Although a front view of the water turbine unit 31 of 32, 33, and 34 is shown, its configuration is the same as that of the water turbine unit of the embodiment of FIGS. 1 and 2, and the description thereof is omitted here. The remaining water turbine units 32, 33, and 34 have the same configuration.

As described above, the four water turbine units 31-34
Action points 31a, 32a, 33 of lever members 35-38,
By arranging the respective 34a around the output shaft 16 with a phase difference of 90 degrees from each other, even in addition to the embodiment of FIGS. 2 and 3, even-number vibrations can be suppressed, and complete vibration-free operation becomes possible. Thus, the durability of the water turbine structure is also improved. In addition, in the quadruple configuration of FIG. 4, when the moving angle of the blades of each of the water turbine units 31, 32, 33, and 34 by the water flow 10 is 30 degrees, the four blades become 120 degrees. Output shaft 1 times as fast as water turbine
6 can be rotated.

Here, referring to FIG. 5, taking the embodiment of FIG. 1 as an example, the operation of the water turbine and the conventional water turbine shown in FIG.

FIG. 5 (a) shows a part of a conventional water turbine 160. When the length of the blade 161a is L and the flow velocity is Fc, the torque T0 at the center C is T0 = L · Fc.

FIG. 5B shows a part of the embodiment of FIG. Assuming that the radius of the crank arm 15 is r and the force that the crank arm 15 receives from the lever member 13 at the action point 13c of the lever member 13 is Fr, the output shaft 16
The torque Tz at (Z0) is as follows: Tz = r · Fr.

Here, assuming that the action point 13c of the lever member 13 is located at the center of the length L of the lever member 13 and L1 = L2, Fr = 2Fc according to the principle of leverage, so that Tz = r.Fr = r · 2Fc. On the other hand, assuming that the angle between CZ0 and the lever member 13 is θ, r = L2 · sin θ = L / 2 · sin θ, so that Tz = 2L2 · Fc = L · Fc. That is, Tz = T0, and it can be seen that the torque at the center C of the conventional water turbine 160 is equal to the torque at the output shaft 16 in the embodiment of FIG.

In the embodiments shown in FIGS. 2, 3 and 4, two to four water turbine units are connected to the same output shaft 16 via a crank arm.
Although one output is taken out, the use of this water turbine unit as a wind turbine requires less installation space than in the case of a water channel, so two or more wind turbine units are connected to separate output shafts. And they can be extracted as separate outputs.

The embodiment shown in FIG. 6 is an example in which two wind turbine units having the same basic configuration as those shown in FIG. One windmill unit 42 includes a pair of guide plates 4 extending in a direction perpendicular to a streamline of air in the flow path 41.
4a, 44b, a roller 45 moving along the inside of the guide plates 44a, 44b, a lever member 46 having a fulcrum 46a pivotally supported by the moving roller 45, and a force point 46b of the lever member 46. And a pressure receiving blade 47 receiving the wind pressure of the flow path 41 and an operating point 4 of the lever member 46.
6c, a crank arm 49 for converting the movement of the lever member 46 generated by the pressure receiving blade 47 receiving the wind pressure of the flow path 41 into the rotational movement of the output shaft 48.

Further, a crank arm 51 coupled to an output shaft 50 similarly disposed at a position symmetrical with the first windmill unit 42 with the flow path 41 interposed therebetween is provided. A second windmill unit 43 formed similarly to 42 is arranged.

That is, the second wind turbine unit 43 includes guide plates 54a and 54b, a roller 55 that moves along the inside of the guide plates 54a and 54b, and a fulcrum 56a that is supported by the moving roller 55. A lever member 56 having
The flow path 41 formed at the force point 56b of the lever member 56
A pressure receiving blade 57 receiving the flow pressure of the air flowing therethrough, and the movement of the lever member 56 which is coupled to the action point 56c of the lever member 56 and is generated by the pressure receiving blade 57 receiving the flow pressure of the air rotates the output shaft 50. Crank arm 51 to convert to motion
And

In the embodiment of FIG. 6, when the blade 47 of the first wind turbine unit 42 is at the position 58a, the blade 57 of the second wind turbine unit 43 is at the position 59b. Therefore, while the blades 47 of the first windmill unit 42 come from the position 58a to the position 58b, the blades 57 of the second windmill unit 43 return from the position 59b to the position 59a.

On the contrary, the blade 5 of the second wind turbine unit 43
When 7 is at the position 59a, the blade 47 of the first windmill unit 42 is at the position 58b. Therefore, the blades 57 of the second wind turbine unit 43 are moved 5 degrees from the position of 59a.
The blade 47 of the first wind turbine unit 42 returns from the position of 58b to the position of 58a while the position reaches 9b.

Thus, the first and second wind turbine units 42 and 43 continue to operate with a phase difference of 180 degrees from each other, and the output shafts 48 and 50 continue to rotate. Here, the blades 47, 57 of the first and second windmill units 42, 43 are both elliptical trajectories 61, 6 intersecting each other as shown in FIG.
2 move at a phase difference of 180 degrees from each other, but at positions 58a, 5a corresponding to the zero positions of the elliptical trajectories 61, 62, respectively.
At 9a, it starts to be driven by the air flow 41,
Air is released from the airflow 41 at positions 58b and 59b corresponding to the 180-degree position 62.

Thus, the blade 47 of the wind turbine unit 42
Is in the flow path 41, the blades 57 of the windmill unit 43
Is outside the flow path 41, and conversely, when the blade 57 of the windmill unit 43 is in the airflow 41, the blade 47 of the windmill unit 42 is outside the flow path 41, so that the two blades 47,
It is sufficient that the flow path 41 has a diameter corresponding to the dimensions of the blades 47 and 57 without the 57 contacting each other and disturbing the streamlines of the air.

FIG. 7 shows a pair of wind turbines 42 and 43 shown in FIG.
An example is shown in which four of the pair configurations are arranged side by side along the same flow path 41. That is, the first to fourth pair windmills 66, 67,
68 and 69 are arranged at regular intervals along the flow path 41 from downstream to upstream. In this case, a total of eight output shafts 66a, 66b, 67a, 67b, 68, 68b, 6
9, 69b are provided separately, for example, output shafts 66a, 67a, 68a,
69a is connected to the shaft of one generator via a gear device (not shown), and output shafts 66b, 67b, 68b, 6 of opposite phases are connected.
9b may be connected to another generator shaft via a gear device (not shown).

In this embodiment, a windmill is taken as an example.
What is necessary is just to use it as a waterwheel with exactly the same structure, and to flow water in the flow path 41. However, in this case, it is difficult to dispose the water turbine below the water channel 41, and therefore, for example, a pair of wind turbines 42, 43
May be arranged obliquely upward at an angle of 90 degrees with respect to the same flow path 41.

The embodiment shown in FIGS. 8 and 9 is a schematic structural view of still another embodiment of the wind turbine as viewed from the front and above. In this embodiment, two crank arms 82A1 and 82A2 are formed with a phase difference of 180 degrees with respect to a crankshaft 81A connected to a first output shaft 80A, and two windmill units 83A and 84A are respectively provided. Provide.

The wind turbine unit 83A is
A lever member 83a whose operation point is pivotally supported by A1, a pressure receiving blade 83b coupled to a force point of the lever member 83a, and a swing fulcrum pivotally supported by a roller 83c inserted between a pair of guide plates (not shown). Having. The other windmill unit 84
A also includes a lever member 84a whose working point is pivotally supported by the crank arm 82A2, a pressure receiving blade 84b coupled to the force point of the lever member 84a, and a roller 84c inserted between a pair of guide plates (not shown). And a swing fulcrum.

Similarly, a second output shaft 80B is provided in parallel with the first output shaft 80A. This second output shaft 8
18B relative to the crankshaft 81B connected to
The two crank arms 82B1, with a phase difference of 0 degrees
82B2, each having two windmill units 85
A, 86A are provided.

The wind turbine unit 85A is connected to the crank arm 82.
A lever member 85a whose operating point is pivotally supported by B1, a pressure receiving blade 85b coupled to a force point of the lever member 85a, and a swing fulcrum pivotally supported by a roller 85c inserted between a pair of guide plates (not shown). Having. The other windmill unit 86
A also includes a lever member 86a whose working point is pivotally supported by the crank arm 82B2, a pressure receiving blade 86b coupled to the force point of the lever member 86a, and a roller 86c inserted between a pair of guide plates (not shown). And a swing fulcrum.

Gears 87A and 87B are fixed to the output shafts 80A and 80B, respectively.
87B are provided in mesh with each other. A first power generation system including first and second wind turbine units 83A and 84A is coupled to a first generator 88A, and a third and fourth wind turbine unit 8 is provided.
The second power generation system composed of 5A and 86A is a second power generator 88.
B, the powers obtained from the two generators 88A and 88B are independent of each other, but since they are connected to each other by the gears 87A and 87B, these powers are output at the same frequency and synchronized with each other. Becomes

The entire power generation equipment shown in FIG. 8 is covered with a cover 89 as shown in FIG. This cover 89 has a gear 87
A, 87B is symmetrical with respect to a plane passing through the meshing point, and a smooth inclined surface 89 is formed toward the wind receiving point 89a of the cover 89.
b, 89c, and an opening 8 at a portion corresponding to the pressure receiving blades 83b to 86b at the rear of the inclined surfaces 89b, 89c.
9d and 89e are formed, and among the pressure receiving blades 83b to 86b, the blade in the pressure receiving stroke protrudes from the openings 89d and 89e to receive wind pressure. In the case of FIG. 8, the blades 83b and 85b are in the pressure receiving stroke and protrude. The remaining blades 84b and 86b are in the return stroke, and are drawn into the cover 89 from the openings 89d and 89e so as not to receive wind pressure.

Thus, in the embodiment shown in FIGS. 8 and 9, the output shafts 80A and 80A are driven by the engagement of the gears 87A and 87B.
Since the movement of the pressure receiving blades 83b to 86b coupled to B is regulated, the wind pressure on the blades protruding from the openings 89d and 89e is balanced on the left and right, and the smooth inclined surfaces 89b and 89c are symmetrical toward the wind receiving point 89a. When the entire power generation equipment including the cover 89 is configured to be freely rotatable 360 degrees in the horizontal direction with a support (not shown), the laminar flow from the wind receiving point 89a toward the openings 89d and 89e is formed. Thus, the wind receiving point 89a can automatically follow the wind direction.

In each of the embodiments described above, the present invention is applied to water turbines and wind turbines to generate power using kinetic energy of water and air. The present invention is further applicable to tube pumps and the like driven by electric motors. It can be applied to a viscous pump, a fan or a dust collection pump.

FIG. 10 is a view showing a schematic configuration of an embodiment applied to a tube pump which is a viscous material pump.
2 and 93 are placed, and these pressure feed rollers 92 and 93 are rotatably supported at the application points of the lever members 94 and 95, respectively.

The fulcrum of one lever member 94 is a roller 97 rotatably guided between a pair of guide plates 96a and 96b.
, And the point of force is coupled to the rotating shaft of a motor 99 via a crank arm 98.

The fulcrum of the other lever member 95 is also rotatably supported by a roller rotatably guided between a pair of guide plates (not shown), and the point of force is transmitted to the motor via a crank arm 100 having a phase difference of 180 degrees with the crank arm 98. It is coupled to 99 rotation axes.

The construction of this embodiment is similar to that of the pressure feeding rollers 92 and 93.
If the motors 99 are coupled to the output shaft 16 and the blades 14 and 24 are provided instead of the water turbine, the configuration is exactly the same as that of the double water turbine shown in FIG.
It is clear that the two and 93 move alternately along the outside of the flexible tube 91 along the elliptical trajectory 101, whereby the viscous material inside is transferred in the direction of the arrow.

In this embodiment, since the flexible tube 91 can be arranged in a straight line, the resistance of the viscous material to be transferred from the flexible tube 91 is minimized, and the pump efficiency is extremely low. high.

The embodiment shown in FIG. 11 is a fan which is mainly used in place of the sirocco fan for conveying gas. Except for using the blades 111 and 112 instead of the pressure feed rollers 92 and 93 in the embodiment shown in FIG. Since the configuration may be the same as that of the embodiment, the same reference numeral is assigned, and further description is omitted.

In the embodiment shown in FIG.
The fan and the entire fan are covered by a cover 114 so that gas does not leak outside. By driving the motor 99 in this state, the blades 111 and 112 alternately
13, the gas is transferred at a constant rate in the direction of the arrow.

FIG. 12 is a diagram schematically showing a configuration of an embodiment in which the present invention is applied to a dust collecting apparatus. In the embodiment of FIG. 12, a fan having the same configuration as that of FIG. 11 is installed in the vacuum chamber 120, and the motor 99 is driven. Is sucked out, and the dust-removed air is exhausted from the pipe 124 to the outside through a filter provided in the partition 123.

When the dust collector having such a configuration is applied to a vacuum cleaner for home use, the power consumption is, for example, about 600 watts in the prior art.
It was found that the same dust collecting ability was obtained at about 00 watts. Moreover, it can be configured to be small and lightweight.

[0070]

As described in detail above, according to the present invention,
Compared to conventional water turbines and wind turbines, the size can be reduced to a fraction, the natural power such as hydraulic power and wind power can be used with high efficiency, and the swing fulcrum lever such as a small, light and low power consumption type pump can be used. A fluid operating device using the device can be provided.

[Brief description of the drawings]

FIG. 1 is a diagram simply showing a configuration of an embodiment in which the present invention is applied to a water turbine.

FIG. 2 is a diagram simply showing the configuration of another embodiment in which the present invention is applied to a water turbine.

FIG. 3 is a perspective view of the apparatus of the embodiment shown in FIG. 2;

FIG. 4 is a configuration diagram of an embodiment configured by combining two embodiments of FIG. 2;

FIG. 5 is an explanatory diagram of torque generated in a conventional water turbine and the water turbine of the embodiment of FIG. 1;

FIG. 6 is a diagram simply showing the configuration of an embodiment in which the present invention is applied to a wind turbine.

FIG. 7 is a configuration diagram of an embodiment configured by using four configurations of the embodiment of FIG. 6;

FIG. 8 is a diagram showing a schematic configuration of another embodiment of the wind turbine according to the present invention.

FIG. 9 is a top view of the windmill of FIG. 8;

FIG. 10 is a simplified configuration diagram of an embodiment in which the present invention is applied to a viscous pump.

FIG. 11 is a simplified configuration diagram of an embodiment in which the present invention is applied to a fan.

FIG. 12 is a simplified configuration diagram of an embodiment in which the present invention is applied to a dust collecting device.

FIG. 13 is a diagram for briefly explaining the configuration and operation of a conventional water turbine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 ... Fluid 11a, 11b ... Guide plate 12 ... Roller 13 ... Lever member 13a ... Swing fulcrum 13b ... Power point 13c ... Application point 14 ... Pressure receiving blade 15 ... Crank arm 16 ... Output shaft

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F03B 17/06 F03B 11/00 F16H 21/18

Claims (8)

(57) [Claims] 1. A pair of guide plates extending in a direction crossing a fluid flow line outside a fluid, a support member moving along the inside of the guide plate, and a fulcrum pivotally supported by the movable support member. A lever member formed at a point of force of the lever member and receiving a fluid pressure of the fluid; and a lever member coupled to an action point of the lever member and receiving the fluid pressure of the fluid. A water turbine comprising: a crank device that converts a motion into a rotational motion of an output shaft; and means for returning the pressure receiving blade from an end point to a start point of the stroke. 2. The water turbine according to claim 1, wherein the pressure receiving blade moves in a range of a predetermined center angle of a circle having the entire length of the lever member as a radius and along a locus of a predetermined closed curve. 3. A lever member having a pair of guide plates extending in a direction crossing a fluid flow line, a support member moving along the inside of the guide plate, and a fulcrum pivotally supported by the movable support member. And a pressure receiving blade formed at the point of force of the lever member and receiving the fluid pressure of the fluid, and outputting the movement of the lever member generated by receiving the fluid pressure of the fluid and coupled to the point of action of the lever member. A first hydraulic turbine unit having a crank device for converting the rotational motion of the shaft into a rotary motion; and a crank arm coupled to the output shaft with a phase difference of 180 degrees from the crank device of the first hydraulic turbine unit across the output shaft. And a second water turbine unit formed similarly to the first water turbine unit. 4. A lever member having a pair of guide plates extending in a direction traversing a fluid flow line, a support member moving along the inside of the guide plate, and a fulcrum pivotally supported by the movable support member. And a pressure receiving blade formed at the point of force of the lever member and receiving the fluid pressure of the fluid, and outputting the movement of the lever member generated by receiving the fluid pressure of the fluid and coupled to the point of action of the lever member. A first water turbine unit having a crank device for converting the rotation into a rotary motion of the shaft; and the output device having a phase difference of 90 degrees, 180 degrees, and 270 degrees with the crank device of the first water turbine unit across the output shaft. A crankshaft coupled to the shaft, wherein the first
And a second, fourth and fourth water turbine units formed in the same manner as the water wheel unit of (1). 5. A lever member having a pair of guide plates extending in a direction crossing a streamline of air, a support member moving along the inside of the guide plate, and a fulcrum pivotally supported by the movable support member. A pressure receiving blade formed at the point of force of the lever member and receiving the air pressure; and a movement of the lever member generated at the pressure point of the lever member when the pressure receiving blade is coupled to the point of action of the lever member and receives the flow pressure of the air. At least one first wind turbine unit having a crank device for converting the rotational motion of the first output shaft into a rotary motion; a pair of guide plates extending in a direction crossing the streamline of air; A moving supporting member, a lever member having a fulcrum pivotally supported by the moving supporting member, a pressure receiving blade formed at a force point of the lever member and receiving the flow pressure of the air, and coupled to an operating point of the lever member And the pressure receiving blade is At least one second windmill unit having a crank device for converting the movement of the lever member generated by receiving the fluid pressure into the rotational movement of a second output shaft; and each of the first and second windmill units. And a flow guiding means for guiding an air flow to the pressure receiving blade at the wind receiving position. 6. The wind guide means has an opening at a wind receiving position of each of the first and second wind turbine units, and receives wind on a line passing through an intermediate portion between the first and second wind turbine units. Have a center,
The multiple wind turbine according to claim 5, further comprising a wind guide path that guides an air flow from the wind receiving center to the pressure receiving blade protruding into the opening. 7. A fluid is formed by a flexible material and flows inside the flexible material.
A fluid passage, which is provided outside the fluid passage and deforms the fluid passage.
ToFirstPressing body and thisFirstPressing body attached to point of actionFirstLeverage
Components and thisFirstFormed at the fulcrum of the lever memberFirstFulcrum support
Components and thisFirstA fulcrum support member is provided for the fluid flowing through the fluid passage.
Guide in a direction crossing the streamlineFirstA guide member;FirstPower from the motor coupled to the power point of the lever member
Through the input shaftFirstTransmit to lever members
A crank device,The fluid passage provided outside the fluid passage is deformed.
A second pressing body, The second lever is attached to the second lever with the second lever
Components, A second fulcrum support formed at a fulcrum of the second lever member
Components, This second fulcrum support member is connected to the fluid flowing through the fluid passage.
A second guide member for guiding in a direction crossing the streamline; Power from the motor coupled to the point of force of the second lever member
With a phase difference of 180 degrees with the first lever member
Crank of the crank device for transmitting to a second lever member
Arms and  A fluid pump comprising: 8. A fluid passage for flowing a fluid, and extending in a direction crossing a flow line of the fluid flowing in the fluid passage.
FirstA pair of guide plates and thisFirstMove along the inside of the signFirstSupport
Wood and this moveFirstHas a fulcrum pivotally supported by the support member
FirstLever member and thisFirstFormed at the point of application of the lever member to the fluid
To give pressureFirstAn operating blade;FirstPower from the motor coupled to the power point of the lever member
Through the input shaftFirstTransmit to lever members
A crank device,Extending in a direction crossing a flow line of the fluid flowing through the fluid passage
A second pair of guide plates, A second support portion that moves along the inside of the second guide plate
Materials and Having a fulcrum pivotally supported by the moving second support member.
A second lever member, Formed at the point of action of the second lever member,
A second working blade for applying pressure Power from the motor coupled to the point of force of the second lever member
With a phase difference of 180 degrees with the first lever member
Crank of the crank device for transmitting to a second lever member
Arms and A fluid pump comprising: