WO2011074669A1

WO2011074669A1 - Turbine

Info

Publication number: WO2011074669A1
Application number: PCT/JP2010/072772
Authority: WO
Inventors: 淳史鳥井
Original assignee: 日本碍子株式会社
Priority date: 2009-12-17
Filing date: 2010-12-17
Publication date: 2011-06-23

Abstract

A turbine which converts the kinetic energy of fluid to the rotational energy of the rotor at high efficiency. A turbine (1) is provided with: a rotor (3) which is formed by stacking disks (21) on each other with gaps (24) therebetween; and a casing (2) which has a containing space (20) for rotatably containing the rotor (3), the containing space (20) being surrounded by a side wall section (16) which surrounds the outer periphery of the rotor (3) from the outside in the radial direction (R) relative to the rotation axis (10), and the containing space (20) being surrounded also by two end wall sections which cover the rotor (3) from both sides in the direction of the rotation axis (10) so as to sandwich the rotor (3). In the casing (2), a space portion in the containing space (20), the space portion being located between the side wall section (16) and the rotor (3) and extending along the side wall section (16), is defined as a flow path (13) for fluid (G). The casing (2) is also provided with an inlet opening (11) which causes the fluid (G) flowing to the flow path (13) to flow in one circumferential direction centering on the rotation axis (10), and the cross-sectional area of the flow path (13) is reduced from the inlet opening (11) in said circumferential direction.

Description

Turbine

The present invention relates to a turbine that rotates a rotor by the viscosity of a fluid.

The turbine converts the flow of fluid such as steam in the casing into the rotation of the rotor, and uses the energy of the rotation of the rotor for power generation.

Among the turbines, those equipped with rotors on which disks are stacked include the Tesla turbine invented by Tesla in 1913 and its improved turbine. In a Tesla turbine, the rotor has a structure in which a plurality of planar disks are stacked with a gap therebetween. Then, a rotational force is applied to the disk by the viscous resistance of the fluid wound inside the casing, and the rotor rotates.

An improved Tesla turbine is a combined viscous / impulsive solar pulse turbine (Patent Document 1). In this turbine, a protruding impulse element is provided on the disk surface. In this turbine, the rotational efficiency of the rotor is improved by utilizing the impulse and repulsive force generated when the fluid collides with the impulse element.

JP 2002-174166 A

However, in the conventional turbine, the efficiency of converting the kinetic energy of the fluid flowing into the casing into the rotation of the rotor is still low. Moreover, in the conventional viscous / impulsive composite type solar pulse turbine, the protrusion-shaped impulse element exists on the disk surface of the rotor, which obstructs the fluid flow in the gap between the disks.

In view of the above problems, an object of the present invention is to provide a turbine having high conversion efficiency from fluid kinetic energy to rotor rotational energy.

In order to solve the above-mentioned problems, the present inventors have intensively studied and as a result, have completed the present invention. That is, according to the present invention, the following turbine is provided.

[1] A rotor in which a plurality of discs are arranged on a single shaft and stacked with a gap between each other, and the rotor is rotatably accommodated with the shaft as a rotation shaft and has a radius with respect to the rotation shaft A casing having a housing space surrounded by a side wall portion that surrounds the outer periphery of the rotor on the outer side in the direction and two end wall portions that cover the rotor from both sides in the direction along the rotation axis. A space portion along the side wall portion between the side wall portion and the rotor in the accommodating space is a fluid flow path, and the fluid is transferred to the flow path in one circumferential direction around the rotation axis. A turbine provided with an inflow port for inflow, wherein a flow path cross-sectional area of the flow path decreases in the one circumferential direction from the inflow port.

[2] The turbine according to [1], wherein a plurality of the inlets are provided at different positions in the one circumferential direction in the casing.

[3] The turbine according to [1] or [2], wherein the flow path cross-sectional area gradually decreases at a constant rate in the one circumferential direction.

[4] The plurality of disks have a substantially circular outer edge and an annular shape having a width in a direction from the outer edge to the center, and the length of the width is a length from the center to the outer edge. The turbine according to any one of [1] to [3], which is less than or equal to one half of the above.

[5] A plurality of the rotors are provided so as to be able to rotate at different rotational speeds with the same rotation axis, and the rotor having the largest disk from the center to the outer edge among the plurality of rotors. The annular rotor in which a plurality of annular disks are stacked, and the remaining rotor is provided in a ring of the disk of the annular rotor. Turbine.

[6] In the annular rotor, the annular disk has a substantially circular outer edge and an annular shape having a width in the direction from the outer edge to the center, and the length of the width is from the center to the outer edge. The turbine according to [5], wherein the turbine is less than or equal to one half of the length up to.

The turbine of the present invention has a high conversion efficiency from fluid kinetic energy to rotor rotational energy.

It is a perspective view of one embodiment of the turbine of the present invention, and is a figure showing a rotor in accommodation space with a broken line. FIG. 2 is a transverse sectional view taken along line A-A ′ in FIG. 1. FIG. 2 is a longitudinal sectional view taken along line B-B ′ in FIG. 1. FIG. 2 is a schematic diagram of a portion sandwiched between parentheses C-C ′ in FIG. 1. It is a perspective view of one embodiment of a turbine of the present invention provided with two inflow mouths, and is a figure showing a rotor in accommodation space with a broken line. FIG. 6 is a transverse sectional view taken along line D-D ′ in FIG. 5. It is a longitudinal cross-sectional view of one embodiment of the turbine of the present invention including two rotors. FIG. 8 is a transverse cross-sectional view of the turbine at E-E ′ in FIG. 7. FIG. 8 is a perspective view of two rotors shown in FIG. 7. FIG. 10 is an explanatory diagram in which one disk is extracted from each of the two rotors illustrated in FIG. 9. FIG. 2 is a diagram illustrating an overview of turbines of Examples 1 to 3 and Comparative Examples 1 to 4 and turbine efficiency. It is a figure showing the outline | summary of the turbine of Example 4, 5 and turbine efficiency.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the following embodiments, and changes, modifications, and improvements can be added without departing from the scope of the present invention.

1. Overview of the turbine of the present invention:
FIG. 1 is a perspective view of a turbine 1 belonging to the technical scope of the present invention. The turbine 1 of the present invention accommodates the rotor 3 in the accommodating space 20 of the casing 2. In FIG. 1, the detailed structure of the rotor 3 such as the disk 21 is omitted and the outline is represented by a broken line.

FIG. 2 is a cross-sectional view of the turbine 1 at A-A ′ in FIG. FIG. 3 is a longitudinal sectional view of the turbine 1 taken along the line B-B ′ in FIG.

The rotor 3 is accommodated in the accommodating space 20 of the casing 2 while being supported by the shaft portion 4 so as to be able to rotate with the axis on which the centers 26 of the plurality of disks 21 are arranged as the rotation shaft 10. The shaft portion 4 is formed along the rotation shaft 10.

Referring to FIG. 3, the accommodation space 20 is surrounded by the side wall portion 16 and two

end wall portions

18 and 19 sandwiching the side wall portion 16.

The side wall 16 is a wall that surrounds the outer periphery of the rotor 3 on the outer side in the radial direction R with respect to the rotation shaft 10 when the rotor 3 is accommodated in the accommodation space 20.

The

end wall portions

18 and 19 are wall portions that cover the rotor 3 so as to sandwich the rotor 3 from both sides in the direction along the rotation shaft 10 when the rotor 3 is accommodated in the accommodation space 20.

2 and 3, in the rotor 3, in the rotor 3, the plurality of disks 21 are arranged with the centers 26 of the disks 21 on one axis, and the plurality of disks 21 are stacked with gaps 24 therebetween.

In particular, it is preferable that the disk 21 has a disk shape or a shape having a circulation hole 22 at the center as shown in FIG.

Since the plurality of disks 21 provided in the same rotor 3 can improve the efficiency and productivity of energy conversion of the fluid G, it is preferable that the outer edges 23 have the same shape. At this time, the shape of the outer edge 23 is more preferably a circle centered on the center 26 of the disk 21.

Of course, the shape and size of the disk 21 can all be the same or different one by one depending on the manufacturing method, the shape of the side wall portion 16 and the like.

FIG. 4 is a schematic diagram of the turbine 1 at a portion sandwiched between parentheses C-C ′ in FIG. The white arrow in FIG. 4 represents the flow of the fluid G.

In the accommodating space 20, a space portion along the side wall portion 16 between the side wall portion 16 and the rotor 3 is used as a flow path 13 for the fluid G.

The casing 2 is provided with an inlet 11 for allowing the fluid G to flow into the flow path 13. The inflow port 11 is formed so that the fluid G flows in one circumferential direction around the rotation shaft 10 in the flow path 13.

In FIG. 4, the inflow port 11 is formed by opening the side wall portion 16. As long as the fluid G can flow in the direction of rotation of the rotor 3 in the flow path 13, the inlet 11 may be formed by opening one of the end walls 18 and 19 (not shown). .

Referring to FIG. 2, the inlet 11 is preferably formed so that the direction D of the fluid G entering the flow path 13 is substantially perpendicular to the radial direction R from the rotating shaft 10. As a result, the moment at which the fluid tries to rotate the disk 21 is substantially maximized, so that the disk 21 can be effectively rotated.

Referring to FIG. 1, in the flow path 13, the flow path cross-sectional area S decreases in one circumferential direction in which the fluid G flows from the inlet 11.

The flow path cross-sectional area S of the flow path 13 is the area of the cross section of the flow path 13 on the surface from the rotating shaft 10 toward the radial direction R.

Referring to FIG. 4, since the flow path cross-sectional area S of the flow path 13 decreases as described above, the fluid G sequentially flows in the flow path 13 along the side wall portion 16 in one circumferential direction. Part of it flows into the gap 24 of the disk 21. The fluid G flows in the gap 24 so as to be wound toward the rotating shaft 10. Therefore, the friction between the fluid G flowing through the gap 24 and the surface 25 of the disk 21 and the viscosity of the fluid G cause a rotational force on the disk 21, and the rotor 3 and the shaft portion 4 that supports the rotor 3 rotate.

The disk 21 has a plate shape without protrusions and blades (blades) on the front and back surfaces 25. In this disk 21, since the surface 25 does not have a protruding shape, the fluid G flows in the gap 24 without being obstructed.

In the turbine 1 of the present invention, power can be obtained or electric power can be generated from the rotation of the shaft portion 4.

In the turbine 1 of the present invention, as in the embodiment shown in FIGS. 1 to 4 (hereinafter, “embodiment of FIG. 1”), the

end wall portions

18 and 19 on both sides in the direction along the rotary shaft 10 are rotors. 3 is preferably close to the disks 21 at both ends (see FIG. 3). Thereby, the fluid G flows intensively in the gaps 24 between the flow path 13 and the disk 21, and most of the fluid G flowing in from the inflow port 11 can contribute to the application of the rotational force of the disk 21.

1 includes a rotor 3 in which an outlet 12 is provided in an end wall portion 18 and a disk 21 having a circulation hole 22 is laminated. In the turbine 1 of the embodiment of FIG. 1, the fluid G flows from the flow path 13 into the gap 24 of the disk 21, then passes through the circulation hole 22 and is discharged from the outlet 12.

The embodiment described below can also be applied to the turbine 1 of the present invention.

2. Embodiments having multiple inlets:
The casing 2 is preferably provided with a plurality of inflow ports 11 at different positions in one circumferential direction around the rotation shaft 10.

In the embodiment in which the plurality of inlets 11 are provided as described above, when the fluid G flows from a certain inlet 11, it is sufficient that the fluid G flows through a short distance to the adjacent inlet 11 in the flow path 13. During such a short distance, there is little deceleration of the fluid G. Therefore, the fluid G can reliably flow at a speed sufficient to rotate the disk 21 in a space portion along substantially the entire circumference of the side wall portion 16 of the accommodation space 20. Therefore, in the embodiment in which such a plurality of inlets 11 are provided, the fluid G flows into the gap 24 of the disc 21 at a speed equal to or higher than a certain direction from each direction uniformly in the radial direction R, and the fluid G over the entire surface 25 of the disc 21. The disk 21 can be effectively rotated using this friction.

In the embodiment of the turbine 1 according to the present invention shown in Fig. 5, there are two

inflow ports

11a and 11b. FIG. 6 is a cross-sectional view taken along the line D-D ′ in FIG.

In the embodiment shown in FIGS. 5 and 6, two

inflow ports

11a and 11b are provided at positions symmetrical with respect to the rotation axis 10.

5 and 6, the side wall 16 and the outer edge 23 of the disk 21 are close to each other immediately before the inflow port 11b. Therefore, in the flow path 13a, the flow path cross-sectional area S decreases from the position of the inflow port 11a, and becomes extremely small immediately before the adjacent inflow port 11b. Fluid G ₁ flows from the inflow port 11a, a part of will flow into the gap 24 of the disk 21 gradually flows reliably into the gap 24 of the disc 21 before almost all reaches the position of the inlet port 11b Finish.

As described above, the flow path 13a is short from the inflow port 11a to just before the inflow port 11b, which corresponds to a portion along the substantially half circumference of the side wall portion 16. Therefore, the fluid G ₁ also flows immediately before the inlet port 11b along the side wall portion 16 corresponding to the flow path 13a end portion deceleration is small. Therefore, the fluid G1 can flow into the gap 24 of the disk 21 at a high speed even at a location immediately before the inflow port 11b at the end of the flow path 11a. The same applies to the flow path 13b starting from the inflow port 11b.

Therefore, in the embodiment of FIGS. 5 and 6, the fluids G ₁ and G ₂ flow into the gap 24 of the disk 21 at high speed without fail while flowing through a short distance in the space portion along the side wall portion 16, that is, the flow path 13. The disk 21 receives a greater force and can rotate the rotor 3 efficiently.

As described above, in the embodiment having the plurality of inlets 11, the channel cross-sectional area S of the channel 13 extending from one inlet 11 toward one circumferential direction is extremely small immediately before the adjacent inlet 11. It is more preferable.

3. Embodiment in which the channel cross-sectional area of the channel gradually decreases at a constant ratio:
In the turbine 1 of the present invention, it is preferable that the flow path cross-sectional area S of the flow path 13 gradually decreases at a constant rate in one circumferential direction.

In this embodiment, the fluid G gradually flows into the gap 24 of the disk 21 in a certain amount while flowing in the circumferential direction of the flow path 13. Therefore, the fluid G flows almost uniformly into the gaps 24 of the disk 21 from all directions in the radial direction R, and the surface 25 of the disk 21 receives the force from the fluid G evenly over the entire surface without being biased.

4). Embodiment comprising an annular shaped disc:
The plurality of disks 21 provided in the rotor 3 are preferably formed in an annular shape having a substantially circular outer edge 23 and a width W in the direction from the outer edge 23 to the center 26, as shown in FIG.

Furthermore, it is more preferable that the annular disk 21 has a width W that is less than or equal to one half of the length from the center 26 to the outer edge 23.

When the fluid G flows into the gap 24 from the flow path 13, first, the kinetic energy is transmitted to the disk 21 in a portion close to the outer edge 23 of the disk 21, and thereafter, without contributing to the increase in rotational energy of the disk 21. Then, it is discharged from the circulation hole 22. Therefore, it is desirable that the fluid G is discharged from the gap 24 of the disk 21 as soon as possible after the kinetic energy has been transmitted to the disk 21. This is because if the state in which the fluid G stays in the gap 24 continues, the rotation of the disk 21 may decrease due to the viscosity of the fluid G. For this reason, the disk 21 is formed into an annular shape, and the edge of the flow hole 22 is brought close to the outer edge 23 of the disk 21, that is, the length W of the annular disk 21 is the length from the center 26 to the outer edge 23. By setting it to 1/2 or less, it is possible to prevent the fluid G after the kinetic energy has been transmitted to the disk 21 from decreasing the rotation of the disk 21.

5. Embodiments with multiple rotors:
The embodiment including a plurality of rotors 3 can also be applied to the turbine 1 of the present invention. In an embodiment including a plurality of rotors 3, it is preferable that the plurality of rotors 3 be provided to be rotatable at different rotational speeds with the same rotation shaft 10.

In the embodiment including the plurality of rotors 3, each rotor 3 does not leak from the fluid G, and the energy of the fluid G can be converted into the rotational force of the rotor.

In the embodiment including a plurality of rotors 3, the shaft portions 4 provided in the respective rotors 3 may be connected to separate generators, or may be adjusted to the same number of revolutions by gears, and then the common power generation You may connect to the machine.

7 to 10 show an example of an embodiment including the above-described plurality of rotors. FIG. 7 is a longitudinal sectional view of a turbine 1 including two

rotors

3a and 3b. FIG. 8 is a cross-sectional view taken along line E-E ′ in FIG. Note that F-F 'in FIG. 8 indicates the position of the longitudinal sectional view of FIG. FIG. 9 is a perspective view of the two

rotors

3a and 3b shown in FIG. FIG. 10 shows one

disk

21a and 21b extracted from the

rotors

3a and 3b, respectively, and shows the relationship between these

disks

21a and 21b and the

shaft portions

4a and 4b. In the following description, the embodiment of the rotor 3 shown in FIGS. 7 to 10 will be referred to as the embodiment of FIG. 7 for convenience of explanation.

In the embodiment of FIG. 7, two

rotors

3a and 3b are provided, and one rotor 3b is an annular rotor 50 on which an annular disk 21 is stacked. The rotor 3 a is disposed in the ring of the annular disk 21 b of the annular rotor 50.

In the embodiment of FIG. 7, the annular disk 21b of the annular rotor 50 (rotor 3b) is fixed by a U-shaped connecting portion 28 and the gap 24 is held. The U-shaped connecting portion 28 includes two sides extending in parallel to the rotation shaft 10 and one side extending in a direction perpendicular to the rotation shaft 10 by connecting the two sides on one side. ing. In the U-shaped connecting portion 28, two side portions extending in parallel to the rotation axis 10 pass through two symmetrical positions with respect to the center 26 of the annular disk 21. A portion of one side extending in a direction perpendicular to the rotation shaft 10 of the U-shaped connection portion 28 is connected to the shaft portion 4 b at a location intersecting the rotation shaft 10.

In this way, the two rotors 3a and the annular rotor 50 (rotor 3b) are supported by the

independent shaft portions

4a and 4b, respectively, so that they can rotate at different rotational speeds (see FIGS. 9 and 10).

Referring to FIG. 8, in the annular disk 21b, for example, in the radial direction R, when the length from the rotation axis 10 (center 26) to the outer edge 23 is 20 cm, the outer edge 23 to the rotation axis 10 (center 26). If the width W toward the surface is about 30 mm, a sufficient rotational force can be obtained from the fluid G by the surface 25b.

In the embodiment of FIG. 7, the annular rotor 50 (rotor 3b) can obtain a large rotational force from the fluid G flowing on the surface 25b of the annular disk 21b at a high speed, as described above. The fluid G flowing in the ring is not affected by the decrease in the rotation of the annular disk 21b. Therefore, in this embodiment, the annular rotor 50 having the annular disk 21b can efficiently convert the kinetic energy of the fluid G into the rotational force of the rotor.

However, even if the fluid G consumes the kinetic energy from the initial level in the ring of the annular disk 21b, it still flows in a spiral toward the rotating shaft 10. Therefore, in the embodiment of FIG. 7, in the ring of the annular disk 21b, another rotor 3a can obtain a separate rotational force from the fluid G by the disk 21a.

As described above, in the embodiment including the plurality of rotors 3, the rotor 3 b having the longest disk 21 b from the center 26 to the outer edge 23 among the plurality of rotors 3 stacks the plurality of annular disks 21 b. More preferably, the remaining rotor 3a is provided to be rotatable at a rotational speed different from that of the annular rotor 50 in the ring of the disk 21b of the annular rotor 50.

It is to be noted that a plurality of annular rotors 50 having an annular disk 21 having a small outer edge 23 are sequentially accommodated in a ring of the disk 21 of the annular rotor 50 having an annular disk 21 having a large outer edge 23. An embodiment in which the rotor 50 is arranged in a nested manner around the single rotation shaft 10 (not shown) may be employed.

Hereinafter, the present invention will be described in more detail based on examples, but the present invention is not limited to these examples.

(1) Turbine The computer and the fluid introduction mode were set as follows using a computer simulation by the program FLUENT3.

Example 1
The disc had a circular outer edge with a radius of 10 cm and a circular circulation hole with a radius of 1.5 cm in the center, and was set to a thickness of 300 μm. The rotor was set so that the 25 discs adjacent to each other were laminated with a gap of 200 μm. As for the casing, it has one inflow port, the cross-sectional area at the inflow port is 45 mm ^2, and the cross-sectional area at the flow path starting from the inflow port is centered on the rotation axis along the rotation direction of the rotor The rotation angle is set to decrease at a rate of 0.125 mm ² per 1 degree. The fluid G was set to be continuously introduced at 12.6 g / sec in the tangential direction of the disk from the inlet. In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

(Example 2)
The cross-sectional area of the flow path at the inlet is 90 mm ^2, and the cross-sectional area of the flow path starting from the inlet is a ratio of 0.25 mm ² per rotation angle around the rotation axis along the rotation direction of the rotor The setting was the same as in Example 1, except that the fluid G was continuously introduced from the inlet in the tangential direction of the disk at 25.3 g / sec. In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

(Example 3)
The disk had a circular outer edge with a radius of 10 cm, an annular shape with a width of 4 cm in the direction from the outer edge toward the center, and the inside of the ring was a flow hole, and the thickness was set to 300 μm. The rotor was set so that the 25 discs were laminated with a gap of 200 μm between adjacent ones. The casing had the same shape as in Example 2 and was set to continuously introduce the fluid G from the inflow port in the tangential direction of the disk at 25.3 g / sec. In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

Example 4
The disc had a circular outer edge with a radius of 10 cm and a circular flow hole with a radius of 6.0 cm in the center, and was set to a thickness of 300 μm. The rotor was set so that the 25 discs adjacent to each other were laminated with a gap of 200 μm. The casing has one inlet, the flow path cross-sectional area at the inlet to about 180 mm ^2, the rotary shaft the flow path cross-sectional area of the flow path that starts from the inlet along the rotational direction of the rotor It was set to decrease at a rate of about 0.5 mm ² per one rotation angle of the center. The setting was such that the fluid G (water vapor at 300 ° C.) was continuously introduced from the inflow port in the tangential direction of the disk at 15.8 g / sec. The flow rate of the fluid at the inlet was set to 150 m / sec. In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

(Example 5)
The disc had a circular outer edge with a radius of 10 cm and a circular flow hole with a radius of 6.0 cm in the center, and was set to a thickness of 300 μm. The rotor was set so that the 25 adjacent discs were laminated with a gap of 200 μm. The casing has one inlet, the flow path cross-sectional area at the inlet was about 90 mm ^2, the rotary shaft the flow path cross-sectional area of the flow path that starts from the inlet along the rotational direction of the rotor It was set to decrease at a rate of 0.25 mm ² per one rotation angle of the center. The setting was such that the fluid G (water vapor at 300 ° C.) was continuously introduced from the inflow port in the tangential direction of the disk at 15.8 g / sec. The flow rate of the fluid at the inlet was set to 300 m / sec. In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

(Comparative Examples 1 to 3)
In Comparative Examples 1 to 3, the same rotor as in Example 1 was set to blow fluid from a nozzle provided at a predetermined position of the casing. In Comparative Example 1, fluid was introduced from one nozzle in the tangential direction of the disk at 1.58 g / sec. In Comparative Example 2, fluid was introduced from each of four nozzles in the tangential direction of the disk to 1.58 g / sec (total of 6.32 g In Comparative Example 3, the fluid was introduced at a rate of 1.58 g / sec (total 12.6 g / sec) in the tangential direction of the disk from each of the eight nozzles. In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

(Comparative Example 4)
In Comparative Example 4, fluid is blown into the rotor of Example 3 from the nozzles provided at 32 predetermined positions of the casing, and fluid is sent from each nozzle in the tangential direction of the disk to 1.58 g / sec (total of 50.5 g). / Sec). In addition, about the shape of a disc and arrangement | positioning of a flow path, explanatory drawing is shown in the right column of FIG.

(2) Turbine efficiency From the kinetic energy E1 of the fluid at the inlet or nozzle converted from the total pressure of the fluid, the torque of the rotor (the product of the shear stress and the area received by the disk), and the rotational speed of the rotor, the following turbine efficiency Was calculated. The results for Examples 1 to 3 and Comparative Examples 1 to 4 are shown in the graph of FIG. The results for Examples 4 and 5 are shown in the graph of FIG.
Turbine efficiency = (rotor torque x rotor speed) / fluid kinetic energy

From the data shown in FIG. 11, it was found that in Examples 1 to 3, the turbine efficiency was high when compared with Comparative Examples 1 to 4 at the same rotational speed. Further, from comparison between Example 2 and Example 3, it was found that a disk having an annular shape has higher turbine efficiency than a simple disk-shaped disk. From the data shown in FIG. 12, it was found that when steam is used as the fluid, the turbine efficiency is about 35 to 60%. Further, as can be understood by comparing the turbine efficiency of the fourth embodiment and the turbine efficiency of the fifth embodiment, it has been found that the turbine efficiency is increased at a lower speed by setting the flow velocity low.

The present invention can be used as a turbine that rotates a rotor by the viscosity of a fluid.

1: Turbine, 2: Casing, 3, 3a, 3b: Rotor, 4, 4a, 4b: Shaft, 10: Rotating shaft, 11, 11a, 11b: Inlet, 12: Outlet, 13, 13a, 13b: Channel: 16: Side wall portion, 18: End wall portion, 19: End wall portion, 20: Storage space, 21, 21a, 21b: Disc, 22: Flow hole, 23: Outer edge, 24: Gap, 25, 25a, 25b: surface, 26: center, 28: connecting portion, 50: annular rotor.

Claims

A rotor in which a plurality of disks are stacked with a gap between each other with a center on one axis;
The rotor is rotatably accommodated with the shaft as a rotation shaft, and is covered so as to sandwich the rotor from both sides in a direction along the rotation shaft and a side wall portion that surrounds the outer periphery of the rotor radially outward with respect to the rotation shaft. A casing having a housing space surrounded by two end walls,
In the casing, a space portion along the side wall portion between the side wall portion and the rotor in the housing space is used as a fluid flow path, and the fluid is supplied to the flow path on one circumference around the rotation axis. A turbine in which an inflow port is provided to flow in a direction, and a flow path cross-sectional area of the flow path decreases from the inflow port in the one circumferential direction.
The turbine according to claim 1, wherein a plurality of the inlets are provided at different positions in the one circumferential direction in the casing.
The turbine according to claim 1 or 2, wherein the flow path cross-sectional area gradually decreases at a constant rate in the one circumferential direction.
The plurality of disks have a substantially circular outer edge and an annular shape having a width in the direction from the outer edge to the center;
The turbine according to any one of claims 1 to 3, wherein a length of the width is equal to or less than a half of a length from the center to the outer edge.
A plurality of the rotors are provided so as to be able to rotate at different rotation speeds with the same rotation axis,
Of the plurality of rotors, the rotor having the largest disk from the center to the outer edge is an annular rotor in which a plurality of annular disks are stacked,
The turbine according to any one of claims 1 to 3, wherein the remaining rotor is provided in a ring of the disk of the annular rotor.
In the annular rotor, the annular disk has a substantially circular outer edge and an annular shape having a width in the direction from the outer edge to the center, and the length of the width is a length from the center to the outer edge. The turbine according to claim 5, wherein the turbine is less than or equal to one half.