TW201641810A - Propeller rotor - Google Patents

Abstract

Provided is a propeller rotor in which it is possible to vary the size of the blades of the rotor in a hydroelectric generator installed in a small water channel, as necessary and according to the local situation. In the horizontal shaft rotor of a hydraulic turbine device, a plurality of blade mounting parts are formed so as to radiate outward, on the peripheral surface on the rear of the hub, and the device is formed in such a manner that the mounting parts of the blade can be mounted to the blade mounting parts even if the mounting parts of the blades are reversed in a front-rear direction.

Description

Spiral rotor Field of invention

BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a helical rotor, and more particularly to a helical rotor that replaces a rotor vane of a waterwheel with respect to a condition that can match the flow rate of the waterway.

Background of the invention

A water wheel installed at the bottom of a waterway is disclosed, for example, in Patent Document 1.

Advanced technical literature Patent literature

[Patent Document 1] Japanese Patent Laid-Open Publication No. 2012-184746

Summary of invention

The waterwheel disclosed in Patent Document 1 is equipped with a water turbine turret on the basis of a water bottom construction.

When it is installed in a water channel, since the flow velocity of the water channel is different, it is difficult to efficiently generate power with a single rotor.

It is an object of the present invention to provide a spiral rotor which is capable of selecting a flow rate which is most suitable for a waterway when a waterwheel device is installed in a small waterway. The fins of the piece are mounted on the rotor.

The specific contents of the present invention are as follows.

(1) In the horizontal-axis rotor of the waterwheel device, in the horizontal-axis rotor of the waterwheel device, a plurality of fin attachment portions that face the radial direction are formed on the circumferential surface of the rear portion of the hub, and the mounting portion of the fin is reversed before and after. It can also be mounted on the wing mounting section.

(2) The spiral rotor according to the above (1) is selected from the fins having different water receiving areas, and the fins of the water receiving area which are most suitable for setting the flow velocity at the site are selected, and the mounting portion of the fin is attached to the fin of the hub. Installation department.

(3) The spiral rotor according to (1) or (2) above, wherein the waterwheel device is provided with a horizontal-axis rotor before and after the water tank body, and the front and rear hubs are respectively mounted in a reverse direction, and the front and rear fins are oriented toward the front. Install in the upstream direction.

(4) The spiral rotor according to any one of the above aspects, wherein the fin attachment portion of the hub is formed such that an insertion hole that is long in a rotation direction is formed to be orthogonal to an axial line. Further, the attachment portion formed at the base end portion of the flap may be fitted into the fitting hole when facing the front and rear directions.

(5) The spiral rotor according to any one of (1) to (4), wherein the mounting portion of the fin is cut away from the peripheral surface, and is compatible with the fin mounting hole of the hub, and the fin attached to the hub is mounted. At the time of the department, there is no drop in the contact.

(6) The spiral rotor according to any one of (1) to (5), wherein a maximum chord length portion in a state in which the aforementioned force type fin is erected In the cross section, the leading edge is a spherical surface, the curved surface from the diameter portion to the trailing edge, and the water flowing along the trailing flow line along the rear surface having the larger bulging portion is in the trailing edge relative to the center of the chord of the fin The lines are staggered by 30 to 45 degrees.

(7) The spiral rotor according to any one of (1) to (6), wherein the trailing edge is at a horizontal front line of the wing root of the suction type fin at 45 to 50 degrees with respect to the rotation direction line. Tilt in the back direction within the range.

(8) The spiral rotor according to any one of (1) to (7) above, wherein the front edge of the swell type fin is a semicircle of a perfect circle in a cross section, from the apex, the front and the back of the front and rear Connected.

(9) The spiral rotor according to any one of (1) to (8), wherein a front end of the maximum chord length portion is a base point, and a front end portion thereof is forwardd with respect to a rotation axis line in a front direction The edge direction is inclined downward by 13 degrees to 23 degrees.

According to the present invention, the following effects can be exhibited.

The spiral rotor according to the above (1) is formed such that a plurality of fin attachment portions that face the radial direction are formed on the circumferential surface of the rear portion of the hub in the horizontal axis rotor of the water tank device, and even if the attachment portion of the fin is reversed before and after, It can be attached to the fin mounting portion. Therefore, in the front and rear structures of the shaft after the rotor is mounted on the waterwheel device, even if the hub is installed backwards in the front and rear, the direction of the fins mounted thereon can be made. Both front and rear are easily installed in the upstream direction.

The spiral rotor according to the above (2) can select and replace the most suitable water receiving surface in accordance with the state of the flow rate of the water channel in which the waterwheel device is installed. The wing of the product.

The size of the generator and the hub can also be single. Therefore, when the flow rate of the set water channel is slow, a large piece of fin is used, and when the flow rate is fast, a small piece of the fin is selected, which appropriately corresponds to the condition of the site.

In the waterwheel device according to the above (3), since the rotor is disposed before the water tank body, the direction of the hub is reversed in the front and rear directions, and the fins are disposed on the upstream side in the same manner as the water receiving surface. In the case where the hub and the flap are fitted together, it is unusable, but it is possible in the present invention and can be replaced with a different size.

Since the spiral rotor described in the above (4) is a long insertion hole in the rotation direction of the fin attachment portion, even if the size of the fin is different, only the attachment portion of the fin may be fitted to the fin. The fitting hole of the mounting portion can be easily mounted, and can be easily mounted even if the flap is reversed before and after.

According to the spiral rotor described in the above (5), since the mounting portion of the fin is the same as the fitting hole in the hub, the fitting portion of the fin is attached to the wing mounting portion of the hub, and the joint does not fall, and the joint does not. Produce turbulent flow.

According to the invention of the above (6), after the extension line having the large bulging portion, the surface flow line is staggered at 30 to 45 degrees with respect to the rotation direction line in the trailing edge, so that when rotating, along the line The water flowing through the rear and the rear side becomes high speed due to the Coanda effect, and the amount of water flowing in a certain period of time is also large, and the rotational torque of the fin is increased as a reaction force.

The larger the stagger angle is, the thicker the fin is, and the larger the bulging portion is, so the passing speed due to the Coanda effect becomes high.

As a result, as a reaction force, the fin is strongly pushed in the rotation direction, and even when the rotation speed is slow, the rotation torque is large, and the power generation efficiency of, for example, a hydroelectric generator can be improved.

According to the invention of the above (7), the maximum thickness portion of the surface having the larger bulging portion is in the range of 25 to 35% of the maximum chord length.

In this case, when the chord length is the same and the maximum thickness becomes large, the bulging portion of the rear curved surface also becomes large, and when the fin rotates, the water flow passing along the surface having the bulging portion is due to the Coanda effect. The larger the bulge, the faster the speed becomes.

However, when the maximum thickness exceeds 35% of the chord length, the water flows in the front direction along the water flowing therethrough. Therefore, the reaction force is directed to the lateral direction with respect to the rotation direction, so that it is difficult to become a rotational force. Further, when it is 25% or less, the amount of water in a certain period of time due to the Coanda effect is reduced by the bulging portion in the back, and therefore the force of rotation by the reaction force is inevitably small.

According to the invention of the above (8), the front edge of the slanting type fin is a semicircular circle in the cross section, so that the water flow can be smoothly separated back and forth at any position before and after the impact of the airfoil, and the resistance is relatively smooth. small.

According to the invention of the above aspect (9), the maximum chord length portion is a base point, and the tip end portion is inclined at an angle of 13 to 23 degrees with respect to the rotation axis line in the front direction with respect to the rotation axis line to form an inclined portion. The water passing through the inclined portion passes through the water flow toward the trailing edge direction at 13 to 23 degrees, and the rotation efficiency is raised as a reaction force.

1‧‧‧Spiral rotor

2‧‧·wheels

3‧‧‧Flap mounting department

3A‧‧‧ screws

4‧‧‧ Mounting holes

5‧‧‧Yang-type wing

5A‧‧‧Maximum chord length

5B‧‧‧Installation Department

5C‧‧‧ inclined section

5D‧‧‧ leading edge

5E‧‧‧ trailing edge

5F‧‧‧ front

Behind 5G‧‧‧

5H‧‧‧fine bump

6‧‧‧Waterwheel device

7‧‧‧Support frame

8‧‧‧Cylinder

9A‧‧‧Upper frame

9B‧‧‧ lower frame

10‧‧‧ shaft tube

10A‧‧‧ bearing

11‧‧‧Waterwheel housing

12‧‧‧floor

13‧‧‧Water deflector

14,15‧‧‧Rotor shaft

14A, 15A‧‧‧ transmission gear

16,17‧‧‧ drive shaft

16A, 16B, 17A, 17B‧‧‧ Transmission gears

18‧‧‧ Output shaft

18A‧‧‧Transmission gear

G‧‧‧Watercourse bottom

S‧‧‧ axis

T‧‧‧Rotation direction line

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a front elevational view of a spiral rotor of the present invention.

Figure 2 is a plan view of the hub portion of Figure 1.

Figure 3 is a front elevational view of the flap of Figure 1.

Figure 4 is a side elevational view of the flap of Figure 3.

Figure 5 is a plan view of the flap of Figure 4.

Figure 6 is a side elevational view of a helical rotor mounted to a waterwheel device.

Fig. 7 is a front elevational view showing another embodiment of the present invention.

Figure 8 is a side elevational view of the flap of Figure 7.

Figure 9 is an enlarged plan view of the flap of Figure 7.

Figure 10 is a cross-sectional view taken along line X-X of Figure 7.

Figure 11 is a cross-sectional view taken along line XI-XI of Figure 7.

Figure 12 is a cross-sectional view taken along line XII-XII of Figure 7.

Figure 13 is a cross-sectional plan view of the half thickness of the flap of Figure 9.

Figure 14 is a plan view showing the advancement process of the fin of Figure 9.

Figure 15 is a plan view showing the advancement process of the fin of Figure 13;

Figure 16 is a cross-sectional plan view showing a modification of the airfoil.

Detailed description of the preferred embodiment

Hereinafter, embodiments of the invention will be described with reference to the drawings.

As shown in FIG. 1, the spiral rotor 1 of the present invention has a plurality of (five in the figure) fin mounting portions 3 formed in the radial direction on the circumferential surface of the rear portion of the hub 2.

The fin mounting portion 3 is mounted with the flap 5 so as not to be shaken, and protrudes to be screwed to the left and right heights, and the protruding end is as shown in FIG. 2, and the poppet type flap 5 (hereinafter simply referred to as a flap) can be fitted. Mounting hole of the mounting portion 5B of the base end portion 4 Go deep into the center of the sphere and form an orthogonal shape in the direction of the axis.

As shown in Fig. 3, the fin portion 5 has a maximum chord length portion 5A which is grown by about 50% of the radius of rotation, and the water receiving area is set to be large.

The mounting portion 5B is formed by forming a notch in the periphery of the wing end portion of the fin 5 from the base end surface to the depth of the mounting hole 4, and is attached to the mounting hole 4 of the fin mounting portion 3. The mounting portion 5B is formed with a screw hole 5C at a position corresponding to the screw hole of the blade mounting portion 3.

The fins 5 make the mounting portions 5B common, and can prepare a plurality of types having different water receiving areas. Thereby, even if the generator and the hub 2 are single, the fins 5 of any size can be fitted to the mounting holes 4. After the attachment portion 5B of the flap 5 is fitted into the attachment hole 4, it is fixed by the screw 3A.

After deciding to set the waterway of the waterwheel, the flow rate of the waterway can be used to determine how much power can be generated. Therefore, it can be reversed by the necessary water volume within one second, and when the flow velocity is slow, the airfoil 5 with a large water receiving area is selected. When the flow rate is fast, the fin 5 having a small water receiving area is selected and mounted on the hub 2, whereby the hydroelectric power generating device of the single hub 2 of a single generator is widely used for waterways having different conditions.

As shown in FIG. 5, the front piece 5D is inclined by 6 to 12 degrees with respect to the rotation direction line T and the trailing edge 5F in the rear direction. Further, the maximum chord length portion 5A is used as a starting point and the inclined portion 5C is inclined in the upstream direction.

The maximum thickness of the leading edge 5E of the fin 5 is 25 to 30% of the chord length in the wing root portion, and the Coanda effect is large and acts as a rotational force.

The blade mounting portion 3 of the hub 2 is shown with a mounting hole 4, but may also be a flat surface. The shape is formed, and the mounting portion 5B of the flap 5 is fitted to the recess, and the form is not limited. Since the rotational force and the centrifugal force are applied to the flap 5, they are fixed without shaking.

Fig. 6 is a side view showing a state in which the rotor 1 is attached to a water wheel. The waterwheel device 6 is an upper horizontal frame body 9A in which the water tank casing 11 is horizontally suspended from the support frame 7 which is formed by the column body 8 and the horizontal frame bodies 9A and 9B.

The bottom plate 12 is placed on the lower horizontal frame body 9B, and its front end portion protrudes forward, and is inclined to come into contact with the water channel bottom G as the water deflecting plate 13. The bottom plate 12 and the bottom surface of the water tank body 11 can be as narrow as possible. The bottom layer flow is guided from the water deflector 13 to the upper surface of the bottom plate 12, mixed with the upper layer flow, and then passed through the pressure, and the rotor 1 at the rear portion is rotated efficiently.

In the water tank casing 11, the rotor shafts 14, 15 are transversely stretched forward and backward, and the front end of the rotor shaft 14 at the front portion protrudes from the water tank casing 11 to fix the rotor 1. The rear end of the rotor shaft 15 at the rear side protrudes from the water tank casing 11 to fix the rotor 1. The transmission gears 14A, 15A are fixed to the inner end portions of the two rotor shafts 14, 15, and cooperate with the transmission gears 16A, 17A at the lower end portions of the transmission shafts 16, 17, respectively.

The shaft barrel 10 is formed to be long in front and rear as viewed in plan, and the left and right sides of the front portion are thicker and thinner toward the rear. The drive shafts 16, 17 that transmit the rotational force of the rotor 1 to the output shaft 18 are vertically supported inside. A transmission gear 16B, 17B that meshes with the transmission gear 18A of the output shaft 18 is fixed to the upper portion of each of the transmission shafts 16, 17.

At the upper portion of the barrel 10, the bearing portion 10A is supported by the support plate 10B, and the output shaft 18 is supported by the bearing portion 10A. Bearing part 10A can respond An auxiliary bearing (not shown) is lengthened to the upper portion as needed.

Thereby, when the rotor 1 rotates due to the water flow, the rotational force is transmitted to the output shaft 18 by the two transmission shafts 16, 17, and the output shaft 18 is simultaneously subjected to the torque of the front and rear rotors 1, so that it can be unillustrated. The generator rotates efficiently.

In Fig. 6, in the upper portion of the water tank casing 11, the adjustment plate 19 is horizontally placed on the support frame 7 at intervals along the height of the water tank casing 11. In Fig. 6, the flow of water flowing down the water tank body 11 impacts the front surface of the shaft cylinder 10 and then moves upward. Therefore, when the adjustment plate 19 is placed, the upward movement can be suppressed, and the pressure becomes high-speed and flows down. The rotor 1 at the rear is rotated efficiently.

Further, the front and rear rotors 1 are oriented in the upstream direction of the fins 5. However, the front and rear hubs 2, 2 are respectively oriented in opposite directions. That is, the fin 5 is fixed to the hub 2 and cannot be used.

In the rotor 1 of Figures 1 and 2, the hubs 2 are respectively mounted in opposite directions. On the other hand, the front and rear flaps 5 are oppositely mounted on the front and rear sides, respectively.

In this regard, since the attachment hole 4 of the fin attachment portion 3 of the hub 2 is formed to be long with respect to the rotation direction, the attachment portion 5B of the flap 5 can be easily attached even if the front and rear surfaces are reversed.

Figure 7 below is an illustration of the thickness of the fins. The same members as those in the previous example are given the same reference numerals and the description is omitted.

In Fig. 7, the front surface of the swell type fin 5 of the spiral rotor 1 has a chord length gradually increasing from the wing root to the wing end, and the front end is tapered from the maximum chord length portion 5A. The length of the chord of the maximum chord length 5A is a range of 40 to 50% of the radius of rotation, 7 is exemplified by 50%.

The flap 5 shown in Fig. 8 is viewed from the side, and the front face 5F is parallel to the rear face 5G, and the thickness of the maximum chord length portion 5A is set to a range of 25 to 35% of the maximum chord length, which is exemplified by 35% in Fig. 8 .

In Fig. 9, the longitudinal center line K in the chord length direction of the fin 5 is inclined by about 10 degrees in the backward direction with respect to the rotational direction line R, but may be 0 degree.

In FIGS. 9 and 10, the horizontal front line U of the maximum chord length portion 5A is inclined by about 23 degrees in the rear 5G direction with respect to the rotation direction line R.

Further, when the flap 5 is rotated, the stagger angle of the flow line V and the rotational direction line R behind the water flow flowing along the extension line of the rear 5G is about 30 degrees, and the longitudinal center line K of the fin 5 and the water flow. The stagger angle of the surface flow line V is then about 33 degrees.

In Fig. 9 and Fig. 10, an inclined portion 5C is formed, and the inclined portion 5C is inclined such that the end portion of the maximum chord portion 5A closer to the front end is inclined to the front direction orthogonal to the horizontal front line U of the maximum chord portion 5A by 30 to 45. The extent of the degree. Therefore, the T line orthogonal to the horizontal front line U is inclined by about 23 degrees with respect to the rotation axis line S toward the trailing edge 5E.

Thus, when the front piece 5F is rotated by the flow of water, the flap 5 is staggered by 56.5 degrees from about one-half of the 113 degrees of the horizontal axis S to the horizontal front line U, that is, about 56.5 degrees with respect to the horizontal front line U. The hydraulic forces indicated by the staggered W arrows are applied to the fins 5, which are staggered at about 33 degrees in the direction of rotation R, so that the hydraulic efficiency is excellent.

Moreover, when the flap 5 rotates, the water flow is indicated by the V arrow which flows at a high speed along the surface 5G having the larger bulging portion by the Coanda effect. The rotation direction line R is about 30 degrees, and flows at a high speed of about 35 degrees with respect to the chord length line (camber), and the flow rate in a certain period of time is large, and the rotation force of the fin 5 is increased as a reaction force. The direction of the reaction force is close to the direction indicated by the W arrow of the hydraulic force applied to the fin 5.

Fig. 13 is a comparison reference diagram for making the maximum thickness of the maximum chord length portion 5A of the fin 5 shown in Figs. 9 and 10 half, i.e., 17.5%.

The stagger angle of the horizontal front line U and the rotation direction line R is about 9 degrees.

Therefore, with the rotation axis S to one-half of the 97 degree of the horizontal front line U and 48.5 degrees, the W arrow staggered with the rotation axis R indicates that the line acts as a direction of hydraulic force. Therefore, even if the longitudinal center line K is 0 degrees, the stagger angle of the surface flow line V and the rotational direction line R after the water flow is as narrow as about 22 degrees, so that it is difficult to become a hydraulic force having a force in the rotational direction.

Thus, the thicker fins 5 shown in FIG. 9 which are staggered about the rotational direction line R by about 33 degrees with respect to the hydraulic action line W, and the half of the thickness of the fin 5 shown in FIG. It is an interlaced angle of 48.5 degrees with respect to the rotational direction line R, which is closer to the rotational direction line R than that shown in FIG. 9, so that the thicker fin 5 shown in FIG. 9 is thicker than that shown in FIG. The thinner fins 5 will be 1 to 1.469%, and the hydraulic utilization efficiency is good.

In Fig. 13, the stagger angle of the water flow V arrow passing through the rear surface 5G of the fin 5 and the rotational direction line R is about 18 degrees. In Fig. 9, the difference between the rear flow lines V and the R arrows indicating that the line is staggered by 30 degrees is understood to be the speed difference of the high speed flow caused by the Coanda effect.

Figure 14 is an enlarged plan view showing the process of moving the flap 5 shown in Figure 10 in a stream of water. In Fig. 14, the leading edge (point A) of the flap 5 is a perfect circle. Hemispherical surface, so the maximum thickness is the diameter of a perfect circle.

Therefore, if the length of the radius is advanced from the center point O of the perfect circle, half of the maximum thickness can be moved, so that in the rear portion, the flow velocity is accelerated by the Coanda effect, and the resistance of the water during the rotation is small.

As described above, the ratio of the length from the center point O to the radius with respect to the full chord length from the leading edge (point A) of the fin 5 to the trailing edge (point B) is about 16.8%.

In Fig. 14, the leading edge (point A) advances its radius of the perfect circle, and when moving to the position of the fixed point C, the water in the range of the fixed points G, I, C, J, H, A, G is along the fin 5 It moves to the rear of the circumference.

In this case, by the advancement of the flap 5, the trailing edge (point B) of the flap 5 advances only to the point D, creating a void of negative pressure at the rear portion thereof, and the surrounding water fills the void of its negative pressure.

Further, the water pushed forward by the flap 5 is not simply pushed forward by the cold pressing device, but is slid on the surface of the leading edge (point A) of the flap 5 in a thin layer and The peripheral surface of the flap 5 is then moved to the rear.

That is, when the flap 5 advances, a space of negative pressure is formed in the range of the fixed points G, B, H, D, G, and thus is pushed by the leading edge (point A) of the flap 5 into a high-pressure water by attaching The wall effect is filled at a high speed to form a negative pressure space at the rear, but in reality the negative pressure space is directly filled with the surrounding water, so the water pushed by the leading edge (point A) will enter due to the water pressure difference. It is a portion of the negative pressure space at the rear of the atmospheric pressure, and because of its backlash, the flap 5 is pushed forward and rotated.

Therefore, the range of the fixed points G, I, C, J, H, A, G and the fixed points G, B, H, D, G are the same volume. Water pressure from the surrounding Adding and filling in a space formed in the range of the fixed points G, A, H, D, G, but the water in the range of the fixed points G, I, C, J, H, A, G is caused by the movement of the fins 5 The water pressure is increased by pressurization, and when the Coanda effect moves rearward, the water pressure thereof pushes the flap 5 as a reaction force.

Therefore, the more the amount of water, the higher the rotational torque of the fins 5. In this case, in the thinner fins shown in FIGS. 13 and 15 to be described later, the reaction force of the water moved by the Coanda effect is small, and the rotational torque is low.

In this case, since the distances of the fixed points A, H, and B are longer than the fixed points A, G, and B, the speed of the water flowing through the surface 5G along the fixed points A, H, and B is higher than that of the front 5F. Quickly enter the aforementioned negative pressure space formed at the rear.

Next, when the fixed point C moves to the position of the fixed point E, the water in the front portion pushed by the leading edge 5D (point A) moves within the range of the fixed points I, F, J, H, F, and I. At this time, since a negative pressure is generated in the range of the fixed points I, F, J, H, F, and I, it is the same as the previous example.

Figure 15 is an enlarged plan view showing the flap of the blade 5 of Figure 13 as it moves due to water flow. The thickness of the flap 5 is half that of the flap 5 of FIG.

The fins 5 in Fig. 14 are only one-half of the thickness of the advancement, and the advancement of the fins 5 in Fig. 15 is the same distance as the thickness.

As a result, in Fig. 15, when the fixed point a moves to the fixed point h, the water in the range of the fixed points j, k, b, i, h, g moves. When compared with the range of the fixed points G, B, H, D, and G, there is a possibility that the difference in size cannot be compared, and the difference in the reaction force caused by the water flow moving at a high speed due to the Coanda effect is larger than the thicker one.

The flap 5 of Fig. 15 seems to accelerate in speed due to hydraulic rotation, but it is difficult to generate a high-speed flow due to the Coanda effect. This fin 5 cannot achieve an increase in the rotational speed of the Coanda effect.

On the other hand, the thick fin 5 exceeding 30% of the chord length in FIG. 14 seems to have difficulty in increasing the rotational speed caused by the hydraulic force, but by the large Coanda effect due to the large enlarged portion of the rear 5G, along the The reaction force of the high-speed flow passing through the rear 5G makes the rotational torque large. This is the difference between the child's hand and the contrast of the sumo wrestler's hand.

Let the thickness of the fin 5 be 17.5 of the chord length as illustrated in Fig. 13, and the strong V-arrow indicating the water flow caused by the Coanda effect cannot be obtained. According to the experiment, with a thickness of 26% of the maximum chord length, the V arrow indicates that the line is at an angle of about 14 degrees with respect to the horizontal front line U.

Further, since the horizontal front line U is 11 degrees with respect to the rotation direction line R, the direction of the force of the hydraulic force that hits the front surface is staggered by about 40 degrees and 45 degrees or less with respect to the rotation direction line R, so the rotation efficiency is higher than that of FIG. high.

Figure 16 is a cross-sectional plan view of the largest chord length portion of the airfoil 5. An innumerable fine unevenness 5H is formed from the semicircular portion of the leading edge 5D toward the rear surface, so that the sliding of the water in the thicker portion is better.

The fine unevenness 5H can be arbitrarily used as a line such as a straight stripe, a lattice, a wicker, or the like, or a coating of a granule or a sprayer. Since the thickness of the leading edge 5D is thick, when the fine unevenness 5H has an infinite number of thick portions, fine turbulence is generated, and the resistance caused by the viscosity of the fluid can be suppressed to make the sliding better.

Industrial availability

The spiral rotor of the present invention can select a fin suitable for the flow velocity of the water channel, so that even if the generator and the hub are single, the fins can be used for hydroelectric generators in water passages having different flow rates.

Since the thickness of the fin is thick, the rotation torque can be increased even at a low speed flow, and therefore, when used in a tidal current generator or the like, efficient power generation can be performed.

1‧‧‧Spiral rotor

2‧‧·wheels

3‧‧‧Flap mounting department

3A‧‧‧ screws

5‧‧‧Yang-type wing

Claims (9)

A spiral rotor characterized in that: in a horizontal-axis rotor of a waterwheel device, a plurality of fin mounting portions facing a radial direction are formed on a circumferential surface of a rear portion of the hub, and the mounting portion of the fin can be mounted even if the mounting portion of the fin is reversed In the wing mounting section. A spiral rotor characterized in that, from a fin having a different water receiving area, a fin that is most suitable for a water receiving area at a flow rate at a site is selected, and a mounting portion of the fin is attached to a fin mounting portion of the hub. The spiral rotor of claim 1 or 2, wherein the waterwheel device is provided with a horizontal axis rotor before and after the water tank body, the front and rear hubs are respectively mounted in a reverse direction, and the front and rear fins are mounted in the upstream direction. The spiral rotor according to any one of claims 1 to 3, wherein the fin mounting portion of the hub is formed such that the fitting hole having a longer rotation direction is formed to be orthogonal to the axial line and formed on the base of the fin The mounting portion of the end portion can also be fitted into the fitting hole when facing the front and rear directions. The spiral rotor according to any one of claims 1 to 4, wherein the mounting portion of the fin is cut off from the circumferential surface and conforms to the fin mounting hole of the hub, and is mounted as a joint when mounted on the fin mounting portion of the hub There is no gap. The spiral rotor according to any one of claims 1 to 5, wherein in the cross section of the maximum chord length portion in a state in which the aforementioned force type fin is erected, the leading edge is a spherical surface, and a curved surface is formed from a diameter portion to a trailing edge thereof. The flow of water passing along the trailing flow line along the back surface having the larger bulge is staggered by 30 to 45 degrees with respect to the central line of the chord of the fin in the trailing edge. The spiral rotor according to any one of claims 1 to 6, wherein the trailing edge is inclined in a rear direction in a range of 45 to 50 degrees with respect to a rotation direction line at a horizontal front line of the wing root of the suction type fin. A spiral rotor according to any one of claims 1 to 7, wherein the leading edge of the aforementioned force type fin is a semicircle of a perfect circle in cross section, and is connected from the front and rear vertices, front and rear. The spiral rotor according to any one of claims 1 to 8, wherein a front end of the aforementioned maximum chord length is used as a base point, and a more advanced end portion thereof is inclined in a front direction with respect to a rotation axis line toward a trailing edge direction and downwardly 13 Degree ~ 23 degrees.