JPS62138040A - Rotary electric machine of vertical shaft type - Google Patents

Abstract

PURPOSE:To reduce the stress of a welded section and enhance reliability, by enlarging the rim side of the cross section of the bearing plate of an elastic transformation type telescoping mechanism for bearing the load of the rim and a magnetic pole and for telescoping the rim uniformly in the radical direction. CONSTITUTION:A spoke 3 is organized with an upper disc 9, a lower disc 10, and a vertical frame 11. A stationary plate 20 is fitted firmly on a rim 6, and a bearing plate 24 is welded on the inner diameter side of the stationary plate 20. ON the upper section of the lower disc 10 of the spoke 3, a bearer 22 having a groove bearing the bearing plate 24 is welded via a liner 23. When the mechanism is rotated, then a centrifugal force is generated on the rim 6, and so a bending stress is applied to the bearing plate 24. The bearing plate 24 is made thinner on the side of the bearer 22, and so that stress is concentrated on the thinner plate section on the side of the bearer 22, and the stress of the welded section between the stationary plate 20 and the bearing plate 24 is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to an axle-type rotary II machine such as an axle-shaft water turbine generator, and more particularly to an axle-shaft rotary N machine with an improved support structure for a rotor rim.

[Technical background of the invention and its problems] This type of vertical shaft rotating electric machine includes a water turbine generator, which is a large-diameter machine, and a flywheel generator, which is used as a power source for the nuclear fusion experiment Soga, which is operated in a special manner with significant speed fluctuations. Wheel generators and the like are known.

FIG. 7 is a partial sectional view of the rotor of this stacked shaft type rotating electric machine, and FIG. 8 is a partial sectional view thereof.

In FIGS. 7 and 8, the outer periphery of a spoke 3 connected to the main shaft 1 with a bolt 2 has a jaw portion 4a projecting in the radial direction at its lower end. The rim 6 with the magnetic pole 5 mounted thereon is supported by this jaw portion 4a. The rim 6 is constructed by tightening a fan-shaped iron plate 7 from both sides with reamer studs 8a and nuts 8b.

Usually, the spokes 3 are composed of an upper disc 9, a lower disc 10, and a plurality of longitudinal bones 11 connecting them, and the ribs 4 are formed by connecting the longitudinal bones 11 to 10.
It is installed in contact with 1. Further, 12 is a stator that faces the magnetic poles 5 in the rotor via an air gap G, and includes a stator core 13, a stator coil 14, a stator frame 15
It is composed of etc.

In addition, key grooves 16 are provided on the outer circumference of the rib 4 and the inner circumference of the rim 6.
is machined, and a key 17 for transmitting torque between it and the rim 6 is inserted.

Further, the jaw portion 4a has a notch 6b formed in the end plate 6a of the rim 6, as shown in detail in FIG.
A sliding member 18 is interposed between the jaw portion 4a and the corresponding jaw portion 4a. This sliding member 18 includes a sliding plate 18a and anti-friction materials 18b on both sides thereof.

It has a configuration in which 18c is arranged
92743, JP-A-59-47942).

In the above configuration, when the rim 6 extends in the radial direction due to centrifugal force, the contact surface between the jaws 4a of the spokes 3 and the rim 6 is constrained by frictional force, causing the rim 6 to become non-circular ( It attempts to transform into a petal-like shape. To deal with this deformation, in the conventional rim support structure, the jaws 4 of the spokes 3
The sliding member 18 is interposed on the contact surface between the rim 6 and the rim 6, thereby preventing the above deformation.

However, especially in large-diameter water turbine generators where the inner diameter of the rotor rim is 10 m or more, the elongation reaches 15 to 2 o# in diameter at unrestrained speed, and the contact surface is several tens of m. This makes it difficult to maintain the levelness of the contact surface on the rim side, and it may not be possible to adjust the surface pressure to be uniform over the entire circumference in the circumferential direction, which may not be counteracted by the structure for preventing deformation of the rim 6 using the sliding member 18. Something happened.

Also, the nuclear fusion experimental device lit! In the case of a flywheel generator used for
As shown in the figure, the power reception mode and the power generation mode are repeatedly performed, and as a result, speed fluctuations become extremely significant in a short period of time. In this case, even if the size of the rim elongation is 1 m,
Even if it is only a small amount, in the conventional rim support structure described above, the members do not rapidly slip due to the frictional contact between the members, and this contraction of about 1#1 can be absorbed in a short time of 1 second or less. I couldn't.

Therefore, if the above-mentioned expansion and contraction is not absorbed, sliding congestion and galling will occur between the rim and spokes, resulting in an imbalance in the amount of slippage depending on the location. As a result, a serious problem has arisen as a rotating electric machine in that the electrical characteristics are abnormal due to misalignment of the axis and unevenness of the air gap between the rotary electric machine and the stator, and normal operation cannot be performed.

[Object of the Invention] The present invention has been made based on the above-mentioned circumstances, and its object is to prevent axis misalignment even when the rim has a large diameter or when the speed fluctuates significantly, and furthermore, to maintain the relationship between the rim and the stator. An object of the present invention is to provide a vertical shaft type rotating electrical machine with excellent electrical characteristics by keeping the air gap uniform.

[Summary of the Invention] In order to achieve the above object, the present invention fixes the rim support structure of the rotor at multiple locations on the circumference between the spokes and the rim, and at multiple locations on the outer periphery of the spokes. a plurality of spoke base plates having concave portions, one end portion of which is fixed at a plurality of axial positions on the inner periphery of the rim different from the fixed position of the spoke base plate, and the other end portion of which is in contact with the concave portion of the spoke base plate; a plurality of elongated elastically deformable members that are in contact with each other and have a cross section of the corresponding contact portion larger than the one end side, and support the load of the magnetic pole and the rim on the spokes and extend in the radial direction of the rim. It is characterized by the arrangement of an elastically deformable expansion and contraction mechanism that expands and contracts evenly.

[Embodiments of the Invention] First, prior to a detailed explanation of the present invention, Figs. This will be explained with reference to the figures.

The rib 3 is composed of an upper disc, a lower disc 10, and a plurality of vertical ribs 11 connecting them, and has a rib 4 on its outer periphery into which a key 17 for transmitting torque is inserted. A fixing plate 20 is fixed to the rim 6, and the rim 6 is fixed together with the laminated iron core 7 by tightening with reamer studs 88 and bolts 8b.
is firmly fixed to. Further, a support plate 21 is welded to the inner diameter side of the fixed plate 2o. A receiver 22 having a groove for receiving a support plate 21 is welded to the upper part of the lower disk 10 of the spoke 3 via a liner 23 for height adjustment. Rim 6 configured like this! A plurality of sets of elastic deformation type expansion/contraction mechanisms are arranged around the circumference of the rotor to support the weight of one pole 5 and to expand/contract the rim 6 in the radial direction.

That is, the weight of the rim 6 and the I4i pole 5 is supported by the lower disc of the spoke 3 via the fixed plate 20, the support plate 21, and the support plate 22.

Next, the rim 6 and spokes 3 created by the operation of the rotating Kaminarimon.
The relative displacement with respect to the above will be explained with reference to FIG. When the rim 6 extends radially by ΔR due to centrifugal force during movement, the fixed plate 20 changes in the outer circumferential direction by ΔR, and since the receiver is fixed to the lower disc 10 of the spoke on the base 22, the support plate 21
causes bending elastic deformation as shown in FIG. When the rotating electric machine stops operating, the radial displacement of the rim 6 disappears,
The support plate 21 returns to its original shape again.

Due to the radial displacement of the rim 6 due to the start and stop of the vertical shaft type rotating electric machine, the welded portion of the fixed plate 20 and the support plate 21 receives repeated bending stress (σ1), and the deformed support plate 21 is bent against the rim 6. Bending stress (σ2) due to supporting 5 layers of magnetic poles
I will also receive it.

Furthermore, the support plate 21 also receives compressive stress (σ3) due to supporting the weight of the rim 6 and the magnetic pole 5.

The stress (σ
) is σ wealth σ1 + σ2 + σ3 ・・・・・・・・・・・・
(11, and due to the start and stop of the vertical shaft type rotating electric machine, the welded part between the fixed plate 20 and the support plate 21 is subjected to a compressive stress of σ3 as shown in FIG. 14, and the A and 8 sides of the support plate 21 are σ
It is subjected to a varying bending stress of 1+σ2.

PΔR 2-2・・・・・・・・・・・・(3) Here E...
・Young's modulus■...Moment of inertia of the cross section of the support plate...Support plate length 2...Section modulus of the support plate P...The weight fluctuation stress of the rim and magnetic pole per unit support plate is the Number of starts and stops during operation period, fixed plate 20
The rotor rim support structure is designed so as not to cause fatigue failure of the welds, since this acts on the welds of the support plate 21.

This support structure can be rotated with large radial displacement of the rim 6.
In order to be used as a shield, the variable stress (σ1+σ2) acting on the welded portion between the fixed plate 20 and the support plate 21 must be lower than the fatigue strength of the welded portion. To reduce fluctuating stress, (
There is a method of increasing the length of the support plate 21 as shown in equation 2).

However, when the support plate 21 is lengthened, as is clear from equation (5) below, the buckling load (Pk) generated within the proportional limit decreases in inverse proportion to the square of the length of the support plate 21.

Here, n... is a coefficient determined by the support plate terminal conditions, here 0.25. Therefore, the length Jl) of the support plate 21 cannot be increased indefinitely.

As a result, as shown in Fig. 15, the fatigue strength of the welded part (
σmax) and the buckling limit (,1,max) narrow the range of application to rotations Ill with large radial changes of the rim 6. Further, the length 1) of the support plate 21 may be restricted due to the structure of the rotating electric machine.

The present invention has been made in order to solve the problems of the above-mentioned earlier application.

Hereinafter, one embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a partial sectional view of an embodiment of a vertical shaft rotating electric machine to which a rotor rim support structure according to the present invention is applied, and FIG. 2 is a detailed view of the rotor rim support structure. That is, spoke 3
is composed of an upper disc 9, a lower disc 10, and a plurality of vertical ribs 11 connecting them, and is provided with a rib 4 on the outer periphery into which a key 12 for torque transmission is inserted. A fixing plate 20 is fixed to the rim 6, and a reamer stud 8 is attached to the laminated iron core 7.
It is firmly fixed to the rim 6 by tightening the bolt 8b and the bolt 8b. As shown in FIG.
A support plate 24 is welded to the inner diameter side. This support plate 21 is thinner in the lower part of the support plate 21 in the longitudinal direction. A support plate 24 is provided on the upper part of the lower disk 10 of the spoke 3.
A support having a groove for receiving the support is welded to a base 22 via a liner 23 for height adjustment. A plurality of sets of elastically deformable rotor rim support mechanisms that support the weight of the rim 6 and the magnetic poles 5 configured in this way and expand and contract the rim 6 in the radial direction are arranged around the circumference.

Next, the operation of this embodiment configured as described above will be explained. That is, the radial displacement of the rim 6 of the rotating electric machine is determined by centrifugal force and rotor rigidity, and the support plate 24 is repeatedly subjected to constant displacement. Here, since the support plate 24 is a comb with a thinner plate thickness on the side of the base 22, the moment of inertia of area is also reduced, and as a result, the radial displacement of the rim 6 is reduced at the part where the plate thickness is reduced compared to the conventional support plate. The amount of absorption increases compared to a board. The length of the support plate is 1, and the length of the part where the thickness of the support plate is reduced is J! , 2. The second moment of area is I! , assuming that the moment of inertia of the thin part is 12, the fluctuating stress of the support plate weld (σa) and the maximum fluctuating stress of the thin part (σb)
is expressed by equations (6) and (7).

Here, Kt-J12/11 is 2-I2/It S... Bending stress of conventional type welded part (Here, S-1 is used for comparison) Figure 3 shows J12/Jl-0,2~ Stress in the weld (σa) and maximum stress in the thinned part (σb) in the case of 0.9
This figure shows the relationship between the moment of inertia ratio (12/It) and the second moment of area ratio (12/It).

The plate thickness ratio (t 2 / ri) is 0.8 (since the moment of inertia of area is proportional to the cube of the plate thickness, [2/It-〇, 5
becomes. ), when J12/Jls -0.7, Oa -0.74, σb ``'' 0. compared to the case where the plate thickness is constant.
83, and a large stress reduction can be achieved by only slightly changing the cross section of the support plate 21.

Furthermore, FIG. 4 shows the reduction in bending stress of the welded portion according to this embodiment. Portion (A) surrounded by the maximum bending stress (σ8) of the conventional support plate 24, the allowable fatigue strength of the welded part (σmax), and the buckling limit <IA) of the support plate 24
and the maximum bending stress (σ
The area (B) surrounded by 8), the allowable fatigue strength (σ1Ilax), and the buckling limit <Jla> due to a partial reduction in plate thickness is the applicable range of each rotor rim support structure.

In this embodiment, as shown in equation (5), by reducing the thickness of a part of the support plate 24, the moment of inertia of area is also reduced, which reduces the buckling load. Although the length of the support plate 24 is reduced from JlA to 1 day to prevent this, the range of application is rather expanded by significantly reducing the stress at the welded portion between the support plate 24 and the fixed plate 20. As a result, structural restrictions on rotation iii are reduced, and the fatigue strength of the rotor rim support structure is increased, making it possible to provide an axle-type rotating electric machine with high reliability and excellent electrical characteristics.

Other embodiments of the present invention are shown in FIGS. 5 and 6.

FIG. 5 shows an example in which the width of the support plate 25 is continuously tapered toward the stand 22 side in order to reduce the fluctuating bending stress at the welded part between the fixed plate 20 and the support plate 25, and FIG. is support plate 2
This is an example in which the plate width of the bridge on the stand 22 side is reduced from the middle of G.

In this embodiment as well, the bending stress at the welded portion between the fixed plate 2o and the support plates 25 and 26 is reduced as in the previous embodiment.

Also, the plate thickness and plate width of the support plates 25 and 26 can be adjusted at the same time.
Of course, the same effect can be obtained even if the amount is reduced on the second side.

[Effects of the Invention] As described above, according to the present invention, the load of the rim and the magnetic pole is supported at multiple locations on the circumference between the spokes and the rim, and the rim is evenly expanded and contracted in the radial direction by welding. By enlarging the cross section of the support plate of the connected elastically deformable expansion-contraction groove on the rim side, it is possible to

[Brief explanation of drawings]

FIG. 1 is a partial sectional view showing a first embodiment of a vertical shaft rotating electric machine using a rotor rim support structure according to the present invention, FIG. 2 is a perspective view showing details of the first embodiment, and FIG. 4 is a detailed view of the present invention; FIG. 5 is a perspective view showing details of a rotor rim support structure according to a second embodiment of the present invention; FIG. 6 is a detailed view of the present invention; is a perspective view showing details of a D-terminal support structure showing a third embodiment of the present invention;
Figure 7 is a partial plan view of a conventional vertical axis rotary electric pump, Figure 8 is a partial sectional view of Figure 7, Figure 9 is a detailed view of the jaw in Figure 8, and Figure 10 is a nuclear fusion experimental device. Figure 11 is a partial cross-sectional view of a vertical shaft type rotating electrical machine using the rotor rim support structure that was filed earlier, and Figure 12 is a diagram showing an example of the operating mode of the flywheel generator used as a power source for
13 is a diagram explaining the action of the support structure in FIG. 11, FIG. 14 is a diagram explaining the bending stress acting on the support plate of the support structure in FIG. 11, and FIG. 15 is a detailed diagram of the support structure in FIG. is the 11th
It is an explanatory view of the application range of the support structure of a figure. 1...Main shaft, 2...Bolt, 3...Spoke, 4
...Rib, 5...-! i pole, 6... rim, 7...
Laminated iron core, 8a... Reamer stud, 8b... Bolt, 9... Upper disk, 10... Lower disk, 11...
・Vertical frame, 12... Stator, 13... Stator core, 1
4... Stator coil, 5... Stator width, 16...
key groove, 17...key, 18...sliding member, 20.
...Fixing plate, 22...Base is stand, 23...Liner,
24.25.26...Support plate. Applicant's representative Patent attorney Takehiko Suzue Figure 2 Figure 3 Figure 4 Figure 50 Figure 6 Figure 7 Figure 12 Figure 13 0 0.2 0.4 0.6 0.8
1.0! Figure 14

Claims (3)

[Claims] (1) Vertical shaft type rotation in which spokes are fixed to the outer periphery of a rotating shaft, an annular rim is provided on the outer periphery of the spoke via a key for transmitting torque, and magnetic poles are provided on the outer periphery of the rim. In a vertical shaft type rotating electric machine having a stator arranged on the vertical shaft rotor through an air gap, a plurality of outer circumferential portions of the spokes are provided at a plurality of locations on the circumference between the spokes and the rim. a plurality of spoke base plates each having a concave portion fixed thereto; one end fixed to an axial position different from the plurality of spoke base plate fixing positions on the inner periphery of the rim; and the other end fixed to the spoke base plate a plurality of elongated elastically deformable members that abut the recess and have a cross section on the corresponding contact side larger than the one end side;
A vertical shaft type rotating electrical machine, characterized in that an elastic deformation type expansion/contraction mechanism is disposed that supports the loads of the magnetic poles and the rim on the spokes and expands/contracts the rim evenly in the radial direction. (2) The vertical shaft rotating electric machine according to claim 1, wherein the elongated elastically deformable member has a plate thickness larger at one end fixed to the rim than at the other end. (3) The vertical shaft rotating electric machine according to claim 1, wherein the long elastic deformable member has a plate width larger at one end fixed to the rim than at the other end.