JP2716375B2 - Turbine equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbine device for converting fluid energy into rotational force, and more particularly to a turbine device having two types of rotor blades having different operating principles.

[0002]

2. Description of the Related Art As a conventional turbine device, a rotating shaft provided in a casing has a plate shape substantially parallel to the rotating shaft, and a fluid outflow side is curved rearward in a rotating direction. There is known a structure in which a plurality of rotor blades are fixedly attached and a plurality of vane blades are arranged around the rotor blade. In such an apparatus, the direction of the working fluid flowing into the casing is adjusted by the vane blades, and collides with the rotor blades to rotate them.

[0003]

In the above-mentioned conventional turbine device, an impact is generated when the working fluid collides with the vane blades. This causes a problem that energy loss occurs and the efficiency of the device is reduced. The durability of the vane wings, rotor wings, etc. was not satisfactory. In particular, when solid particles are dispersed in a working fluid, the latter disadvantage is fatal.

[0004] The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a turbine device which eliminates an impact caused by collision of a fluid, improves device efficiency, and increases durability.

[0005]

In order to achieve the above object, a turbine apparatus according to the present invention rotatably supports a rotary shaft in a casing having an inlet port for a working fluid provided on an outer peripheral portion. A first rotor blade is fixedly mounted on the rotating shaft, and an annular chamber is formed in the casing radially outside the rotating shaft from the first rotor blade, while the rotating shaft is orthogonal to the rotating shaft. A plurality of disk-shaped second rotor blades are fixedly mounted in the annular chamber at intervals in the axial direction and housed in the annular chamber.

In the turbine device having the above structure, the working fluid enters the annular chamber in the casing from the inlet port and passes through a plurality of gaps between the annular rotor blades. The resulting shear forces cause the second rotor blade, and thus the rotating shaft, to rotate. The working fluid further collides with and rotates the first rotor blade to accelerate the rotating shaft, and flows out from the vicinity of the rotating shaft. Here, since the second rotor blades are arranged orthogonal to the rotation axis, the working fluid flowing into the casing does not directly collide with the second rotor blades, and does not cause any adverse impact.

In the above, the casing comprises a front member,
The annular chamber is formed by a rear member and an outer peripheral member connecting the rear member and the inner wall of the front member, the rear member, and the inner wall of the outer peripheral member. And the second
The rotor blade includes a front and rear rotor blade adjacent to the front member and the rear member, and an intermediate rotor blade located between the front and rear rotor blades and having an outer diameter larger than that of the front and rear rotor blades. Each of the inner walls of the front member and the rear member has a circular recess having an inner diameter larger than the outer diameter of the front and rear rotor blades and smaller than the outer diameter of the intermediate rotor blade, and accommodating the front and rear rotor blades. Each is preferably formed. If there is a gap between each plate portion of the front and rear rotor blades and each inner wall, the working fluid flows into the space and the efficiency of the device decreases, but the circular recesses as described above are provided so that the front and rear rotor blades are formed. When housed therein, the working fluid will always flow between the second rotor blades.

Here, it is preferable that one or more annular concave portions are formed in the circular concave portions. For example, an annular first recess is formed so as to be continuous with the outer peripheral edge of the circular recess, and one or more annular inner recesses wider than the first recess are adjacent to the outer edge of the first rotor blade. However, in this case, the working fluid passing through the small gap between the front and rear rotor blades and the inner wall recess does not flow out to the first rotor blade side through the recess. . Further, when the front and rear rotor blades are arranged such that the surfaces facing the intermediate rotor blades are located on substantially the same plane as the inner walls of the front and rear members, the flow of fluid is smooth. Is more preferable.

Further, an outlet port for a fluid having an inner diameter larger than the outer diameter of the first rotor blade is provided in communication with the front member. Further, the first rotor blades are formed in a plurality of plate shapes, each of which is composed of a flat plate portion substantially parallel to the rotation axis and a curved portion curved backward from the flat plate portion in the rotation direction of the rotation shaft. Preferably, a portion is located radially inward of the second rotor blade and a curved portion is located at the outlet port.

Further, a mounting edge is formed on the front rotor blade and the intermediate rotor blade so as to protrude inward from an inner peripheral edge of the rotor blade, and a through hole is formed in the mounting edge and the rear rotor blade. A fixing bolt is inserted into the through hole with a predetermined thickness interposed between the rotor blades to fix the rotor blades, and the rear rotor blades are extended radially inward to be fixed to the rotating shaft. It is preferable to do so. By using the interposed member having a predetermined thickness in this manner, the gap between the second rotor blades can be easily maintained at the optimum width.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the turbine device of the present invention will be described below in detail with reference to the drawings.

A turbine device according to the present invention includes a casing (housing) 1 fixedly attached to a base (not shown), a rotating shaft 2 rotatably supported by the casing 1, and a rotating shaft 2. A plurality of plate-shaped first rotor blades 3 mounted substantially in parallel with a plurality of annular plate-shaped first rotor blades 3 mounted on the rotating shaft 2 at intervals in the axial direction and mounted perpendicular to the rotating shaft 2. And a second rotor blade 4.

The casing 1 is formed by connecting a circular front member 5 and a rear member 6 with a cylindrical outer member 7. The inner wall of the front member 5, the rear member 6 and the inner wall of the outer member 7 define a predetermined inner diameter. Is formed. The outer peripheral member 7 of the casing 1 is provided with a gently curved inlet port 9, which is substantially the outer periphery of the outer peripheral member 7.
The working fluid flowing from the inlet port 9 flows in the tangential direction into the casing 1 and contacts the outer edge of the annular disk-shaped second rotor blade 4. It does not directly collide with the portion, but flows helically toward the center in the casing.

The inlet port 9 is connected to the nozzle 10. The depth (the width of the inlet port in the radial direction of the casing) corresponds to the outlet dimension of the nozzle 10, and the smaller the nozzle 10 is, the shallower the inlet port is. 9 and a larger entry results in a deeper entry port 9. If the outlet of the nozzle 10 has the same dimensions as the clearance between the casing 1 and the second rotor blade 4, the inlet port 9 will be part of a circular opening and fluid will flow from the nozzle through the casing 1 and the second rotor blade. It will flow directly into the opening between the edge of the wing 4. In the illustrated example, only one inlet port 9 is provided, but two or more inlet ports may be provided. Also, depending on the working fluid used, or if the thickness of the second rotor
In the case of the same size as the gap between the rotor blades, the inlet port 9 exceeds the range of approximately 1/4 arc of the outer periphery of the outer peripheral member 7, but in this case, the number of the inlet ports 9 to be attached is Limited.

At the center of the front member 5 and the rear member 6 of the casing 1, through holes 5a and 6a are formed coaxially. The rotary shaft 1 is inserted through the through holes 5a and 6a, and is rotatably attached to the casing 1 by a bearing member (not shown) housed in a concave portion outside the hub portion in which the through hole 6a of the rear member 6 is formed. It is supported. The rotary shaft 2 has a threaded portion at the tip, and is provided with a flange portion (shoulder portion) 12 protruding radially outward at a position adjacent to a portion where the bearing member is fitted. And
The flange portion 12 is also located in the through hole 6a.

The plurality of first rotor blades 3 are formed integrally with a sleeve member 13 fitted to the rotating shaft 2, and each of the first rotor blades 3 is a flat plate substantially parallel to the rotating shaft 2. And a curved portion 3b that curves backward from the flat plate portion 3a in the rotation direction of the rotating shaft 2. The flat plate portion 3a is located radially inward of the second rotor blade 4 and is bent. The portion 3b extends outward from the front member 5 through the through hole 5a of the front member 5. As is clear from FIG. 2, the through hole 5 a of the front member 5 has an inner diameter larger than the outer diameter of the flat plate portion 3 a of the first rotor blade 3. An outlet port 11 having an annular cross section, which is coaxial with 5a and whose diameter is gradually increased toward the front, is continuously provided.

The second rotor blade 4 includes a front rotor blade 4a adjacent to the front member 5, a rear rotor blade 4b adjacent to the rear member 6 having the same outer diameter as the front rotor blade 4a, and a front rotor and a rear rotor. A plurality of intermediate rotor blades 4c located between the rotor blades 4a and 4b and having an outer diameter larger than those of the rotor blades, and an outer peripheral edge of the intermediate rotor blade 4c extends inward from an inner peripheral surface of the outer peripheral member 7; The inner peripheral edges of the intermediate rotor blades 4c and the front rotor blades 4a are slightly separated outward from the rotation trajectory of the first rotor blades 3 to ensure smooth rotation of the rotor blades. The front rotor blades 4a and the intermediate rotor blades 4c are provided with a plurality (three in the illustrated example) of mounting edges 14 at positions not within the rotation locus of the first rotor blades 3 and from the inner peripheral edge of the second rotor blades. It is formed so as to protrude inward in the radial direction, and through holes are formed in the mounting edge portion 14 and the rear rotor blade 4b. The mounting bolt 15 is inserted into the through hole.
a is a washer having a predetermined thickness between the rotor blades (intervening member)
The rotor blades are fixed to each other by being inserted with the rotor blades 15b interposed therebetween. The rear rotor blade 4 b extends radially inward and is fixed to the rotating shaft 2 together with the first rotor blade 3. That is, a through hole is formed in the rear rotor blade 4b, and the rear rotor blade 4b is inserted into the rotating shaft 2 through the through hole.
It is fixed to the flange portion 12 via a plurality of bolts. On the other hand, the first rotor blade 3 fits the sleeve member 13 on the rotating shaft 2 and abuts against the rear rotor blade 4b,
A nut member 16 is screwed into a threaded portion at the tip of, pressed against the flange portion 12 and fixed to the rotating shaft 2. As described above, both the first rotor blade 3 and the second rotor blade 4 are fixed to the rotating shaft 2 by screwing, and constitute a single rotor as a whole.

On the inner walls of the front member 5 and the rear member 6,
Circular recesses 17 and 18 having inner diameters larger than the outer diameters of the front rotor blades 4a and the rear rotor blades 4b and smaller than the outer diameters of the intermediate rotor blades 4c are formed, respectively. Front rotor blades 4a and rear rotor blades 4b
Are accommodated with a slight gap between the inner wall of the recess.

The circular recesses 17 and 18 are formed so as to have a depth such that the front and rear rotor blades do not protrude from the recesses 17 and 18 or protrude only slightly if they do. In the illustrated example, the front member 5
The surface of the inner wall of the rear member 6 and the inner side surfaces of the front rotor blades 4a and the rear rotor blades 4b (the surfaces facing the intermediate rotor blades 4c) are substantially the same. Further, in the circular recesses 17 and 18, annular first recesses 19 a and 20 a are formed continuously with the outer peripheral edges of the circular recesses 17 and 18,
Annular second concave portions 19b and 20b wider than the first concave portions 19a and 20a are formed on the side adjacent to the outer edge of the first rotor blade 3, and the same annular third concave portion 19 is formed.
c, 20c are the first concave portions 19a, 20a and the second concave portion 19
b and 20b. The second concave portion (inward concave portion) 19b, 20b and the third concave portion (inward concave portion)
19c and 20c each have a radially outer side surface of 12
It is inclined at an angle of 0 to 150 degrees, and is formed so that a radially inner side surface is vertical (90 degrees).

In the turbine device configured as described above, the working fluid passes through the flow path from the nozzle 10 to the inlet port 9 and comes into contact with the outer edge of the annular disk-shaped second rotor blade 4. While flowing into the casing 1 at an angle and passing through a plurality of gaps between the second rotor blades 4 and spirally flowing toward the center, a shear force is applied to the second rotor blades 4 while passing through the gaps. To transmit torque to the second rotor blades 4 and thus to the rotating shaft 2. Then, the working fluid that has rotated the second rotor blades 4 further flows into the first rotor blades 3, and the flat portion 3 a of the first rotor blades 3 is located inside the second rotor blades 4. The working fluid collides with the flat plate portion 3a according to the same principle as that of the conventional turbine device, and the rotation of the rotary shaft 2 is accelerated by the impact. And discharged from the discharge nozzle into the atmosphere as it is, or discharged after being evacuated. As described above, in the above-mentioned turbine device, the flow of the fluid when passing between the second rotor blades 4 is dominated by the flow component spirally inward in the radial direction in the casing, but the center first rotor When reaching the blade 3, the flow is changed to an axial flow instead of a radial flow, and when leaving the first rotor blade 3, the flow becomes an axial flow having almost no radial component.

Here, since the second rotor blades 4 are a plurality of annular plate members disposed orthogonal to the rotation shaft 2, the working fluid does not directly collide with the second rotor blades Since it flows into the gap between the rotor blades 4 and rotates the second rotor blades by the shearing force, no impact acts on the second rotor blades.

Further, the above-described annular blade-shaped rotor blade 4
Is easy to manufacture because it can be used as it is without bending the plate member, and it is also easy to manufacture with a low-cost material or to use a material suitable for steam or corrosive fluid. . Further, it can be used for a fluid containing ash and various solid particles, and can be suitably used for combustion of a coal-water mixed fuel, and also suitably used for a multi-phase fluid.

Further, if there is a gap between each plate portion of the front and rear rotor blades and each inner wall, the working fluid flows into the gap and the efficiency of the apparatus is reduced. Circular recesses 17 and 18 are formed in the inner wall of the member 6, respectively, and the front rotor blades 4a and the rear rotor blades 4b are accommodated in the circular recesses 17 and 18 with a slight gap from the inner wall of the recess. . Therefore, the working fluid does not pass between the inner wall and the rotor blades and acts on only one surface, so that the working fluid can always pass through the gap between the second rotor blades to be operated, thereby improving the efficiency of the apparatus. .

The circular recesses 17 and 18 have the first
Since the concave portions such as the concave portions 19a and 20a and the second concave portions 19b and 20b are formed, even if a fluid flows into a small gap between the front rotor blades 4a and the rear rotor blades 4b and the inner wall of the concave portion, these concave portions are formed. Cannot pass through the recesses 17, 18, so that the working fluid is
, And is restricted only to pass through the gap between the adjacent annular disk-shaped second rotor blades 4. Therefore,
There is no loss of work and the efficiency of the device increases.

Further, when the rotor blades are fixed to each other, an intervening member having a predetermined thickness is used, so that the gap between the second rotor blades 4 can be easily adjusted to an optimum width according to the conditions of the working fluid and the like. Can be set and maintained. Further, since the mounting bolts 15 for fixing the second rotor blades 4 to each other are inserted through the mounting edge portions 14 formed to project radially inward from the inner peripheral edge of the second rotor blades, the second rotor blades 4 are fixed. It does not partially obstruct the flow of the fluid that operates the.

In the above embodiment, only one exhaust port is provided, and the rear rotor blades 4c in which the rotor blades used for mounting the second rotor blades 4 are arranged at the rear are used.
One of the intermediate rotor blades may be extended to be attached to the rotating shaft, the first rotor blade 3 may be structured to have curved portions on both sides, and the discharge ports may be provided on both sides. In addition, the first concave portions 19a, 2
0a, second concave portions 19b, 20b, third concave portions 19c, 20
Although three recesses c were formed, the number of recesses is not limited to this. Furthermore, the relative dimensions of the second rotor blades 4 with respect to the first rotor blades 3 should be set optimally in consideration of the type of working fluid, the use of the turbine device, and the like. Further, in the above description, a standard rotor is used as the first rotor blade 3, but a known rotor having another structure may be used, or a multi-plate rotor may be used. Depending on the structure of the first rotor, the conversion to the axial flow is not possible or insufficient, but in such a case, a suction means such as a vacuum pump is connected to the outlet port side.

[0027]

In the turbine apparatus according to the present invention, the working fluid enters the annular chamber in the casing from the inlet port and passes through a plurality of gaps between the annular rotor blades. Since the second rotor blades are rotated by the shearing force generated at that time, the working fluid does not directly collide with the second rotor blades, and no undesired impact occurs. In addition, since not only the second rotor blades but also the first rotor blades similar to the rotor blades of the conventional turbine device are combined, a sufficient turbine output can be secured.

If there is a gap between each of the plate portions of the front and rear rotor blades and each of the inner walls, the working fluid flows into the space to reduce the efficiency of the device. In the turbine device of the present invention, however, the inner wall of the casing has a circular shape. Since the recess is provided to accommodate the front and rear rotor blades therein, the working fluid always flows between the second rotor blades. Further, by forming one or more recesses in the circular recess, the working fluid passing through a small gap between the front and rear rotor blades and the inner wall recess flows out to the first rotor blade side through the recess. Never. Accordingly, the operation of the second rotor blade by the working fluid is efficiently performed, and the efficiency of the apparatus is improved. Further, the second rotor blades are interposed between the second rotor blades with a predetermined thickness interposed therebetween.
Since the rotor blades are fixed to each other, there is an advantage that the gap between the second rotor blades can be easily maintained at the optimum width.

[Brief description of the drawings]

FIG. 1 is a partially cutaway front view showing a turbine device of the present invention.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a sectional view taken along line III-III in FIG. 1;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Casing 2 ... Rotating shaft 3 ... 1st rotor blade 3a ... Flat part 3b ... Curved part 4 ... Second rotor blade 4a ... Front rotor blade 4b ... Rear rotor blade 4c ... Intermediate rotor blade 5 ... Front member 6 ... Rear Member 7 ... Outer peripheral member 8 ... Chamber 9 ... Inlet port 14 ... Mounting edge 17, 18 ... Circular recess 19a, 20a ... First recess 19b, 20b ... Second recess (inner recess) 19c, 20c ... Third recess (Inward recess)

Claims (7)

(57) [Claims] A rotary shaft is rotatably supported in a casing provided with an inlet port for a working fluid at an outer peripheral portion thereof. The rotary shaft has a flat plate portion substantially parallel to the rotary shaft and the flat plate portion.
And a curved portion that curves backward from the shape portion in the rotation direction of the rotating shaft.
To together with the first rotor blade is fixedly attached, while the annular chamber radially outside the rotational axis than the first rotor blade is formed in the casing, the said rotation axis is perpendicular to the rotational axis A plurality of annular plate-shaped second
A turbine device, wherein rotor blades are fixedly mounted in a state of being spaced apart in the axial direction and housed in the annular chamber. 2. A working fluid inlet port is provided on an outer peripheral portion.
The rotating shaft is rotatably supported in the casing
The first rotor blade is fixedly attached to the rotating shaft.
In the casing, the rotation axis of the first rotor blade is
An annular chamber is formed radially outside, while
The rotating shaft has a plurality of annular plates arranged perpendicular to the rotating shaft.
Second rotor blades are spaced apart in the axial direction, and
While being housed in the chamber, it is fixedly attached,
The casing includes a front member, a rear member, and an outer peripheral member that connects the front member and the rear member. The annular chamber is formed by the inner wall of the front member, the rear member, and the inner wall of the outer peripheral member. A front rotor blade adjacent to the front member, a rear rotor blade adjacent to the rear member, and an intermediate rotor blade located between the front and rear rotor blades and having an outer diameter larger than that of the front and rear rotor blades. Each of the inner walls of the front member and the rear member has an inner diameter larger than the outer diameter of the front and rear rotor blades and smaller than the outer diameter of the intermediate rotor blade, and accommodates the front and rear rotor blades. A turbine device comprising a circular recess. 3. The turbine device according to claim 2, wherein one or more annular concave portions are formed in said circular concave portions. 4. The annular concave portion has a first concave portion formed continuously with an outer peripheral edge of the circular concave portion, and a side wider than the first concave portion and adjacent to an outer edge of the first rotor blade. 4. The turbine device according to claim 3, further comprising one or more inward concave portions formed in said at least one inner concave portion. 5. Each of the front and rear rotor blades is disposed such that a surface facing the intermediate rotor blade is located on substantially the same plane as the inner walls of the front and rear members. The turbine device according to claim 2. 6. The front member is provided with a fluid outlet port having an inner diameter larger than the outer diameter of the first rotor blade in communication therewith, while the first rotor blade has a plurality of plate shapes. A flat portion that is substantially parallel to the rotation axis, and a curved portion that curves rearward from the flat portion in the rotation direction of the rotation shaft. The flat portion is radially inward of the second rotor blade. The turbine device according to claim 2, wherein the curved portion is located at the outlet port. 7. A mounting edge is formed on the front rotor blade and the intermediate rotor blade so as to protrude inward from an inner peripheral edge of the rotor blade, and a through hole is formed between the mounting edge and the rear rotor blade. At the same time, a mounting bolt is inserted into the through hole with a predetermined thickness interposed between the rotor blades so that the rotor blades are fixed to each other, and the rear rotor blades extend radially inward to rotate the rotor blades. The turbine device according to claim 2, wherein the turbine device is fixed to a shaft.