JPH02294501A - Variable stator blade type turbo machine - Google Patents

Abstract

PURPOSE:To adjust a gap between ends of stator blades and the outer periphery of a rotor disk according to the running condition by moving the stator blades in the radial direction of a casing in synchronization with the adjustment of an attack angle of the stator angle to a main flow. CONSTITUTION:A stator blade varying mechanism for adjusting an attack angle of a stator blade 1 to a main flow is composed of a stator blade rotary shaft 2, a stator blade rotating gear 4 and a rotatably driving gear 3. A stator blade moving mechanism for moving the stator blade 1 in the radial direction of a casing 5 in synchronization with the adjustment of an attach angle of the stator blade 1 to the main flow is composed of a fixed piece 11, a rotary piece 12, an inclined cam surface 13 and a compression spring 14. When the stator blade 1 is adjusted from its attitude in the partial load running to that in rated running through the stator blade varying mechanism, the stator blade 1 is moved to a position for providing the minimum gap 8 between the end of the stator blade 1 and the outer peripheral surface 7' of a rotor disk 7 by the actions of the fixed piece 11, rotary piece 12 and inclined cam surface 13 in synchronization with said adjustment to be held in said position.

Description

[Detailed Description of the Invention] [Industrial Field of Application] The present invention provides a vane with an adjustable angle of incidence with respect to the main stream.
This variable static vane type turbomachine is suitable for adjusting the minimum gap between the tip of the stator vane and the tapered surface of the outer periphery of the rotor disk when adjusting the internal angle of attack. Pile related to airfoil turbomachinery [Prior art] A conventional stator vane ISJ variant turbomachinery is described in the Journal of Turbomachinery 108 (1986), pp. 233 to 239 (J. of 'rubomachinery).
ery108 (1986) pp. 233-239), a detailed sectional view of the IJf variable stator vane portion of this multistage axial flow compressor as a variable stator vane type turbomachine is shown in FIG. The multistage axial flow compressor shown in this document consists of a rotor and a stator. The rotor has rotor disk 7
A large number of rotor blades 6 are implanted around the outer periphery of the rotor disk, and these rotor disks are stacked in multiple stages in the axial direction and tightened with five stacking bolts 8, which rotates as a unit at high speed. The stator is an assembly of five stator blades 1 placed midway between each stage of rotor blades 6, and is fixed to the outer casing 5. In general, in this multi-stage axial flow compressor, in order to stabilize unsteady fluid characteristics especially during the startup or shutdown process, the stator blade rotation axis 2 is designed so that the direction of the stator blade 1 can be changed. It has an elliptical shape that can be rotated by the rotary drive gear 3 via the stationary blade rotation gear 4 integrated with the stator vane rotation gear 4.

[Problem to be solved by the invention]

Next, Fig. 11(A). (B) shows the gap between the tip of the stator vane and the taper surface of the outer circumference of the rotor disk and the attitude of the stator blade with respect to the mainstream under rated operating conditions in the conventional technology, and Figures 12 (A) and (H) Figure 2 shows the interference between the tips of the stator blades and the Taper surface on the outer periphery of the rotor disk during startup, and the attitude of the stator blades with respect to the main flow. In the prior art, when the rotor has a tapered surface 7' in one direction, especially at the outer circumference of the rotor disk 7,
As shown in Fig. 11 (A), the gap between the tip of the stationary blade 1 and the taper 7' on the outer periphery of the rotor disk 7 is made to be a sufficiently small minimum gap δ during rated operation. In order to rotate the stator blade 1 in a direction that closes it to the main flow so that the angle of attack θ' shown in FIG. 12 (}l) is obtained during partial load operation such as when the stator blade is stuck, the angle shown in FIG. 12 (A) is
As shown in the figure, the tip of the stationary blade 1 and the taper 7' on the outer periphery of the rotor disk 7 come into contact or bite 9. In order to avoid the contact or digging-in 9 during partial load operation, it is necessary to cut the tip of the stator blade 1 to the position shown by the two-dot chain line in Fig. 11 (Δ). If , the maximum gap between the tip of the stator blade 1 and the outer periphery of the rotor disk 1 becomes δ' during rated operation.

An increase in this gap during rated operation results in a significant decrease in the efficiency of the multistage axial flow compressor, which is a turbomachine.
The first object of the present invention is to reduce the gap between the tip of the stator blade and the tapered surface of the outer circumference of the rotor disk during rated operation, and to reduce the gap between the tip of the stator blade and the rotor disk during partial load operation such as during startup. An object of the present invention is to provide a variable-mouth stator vane type turbomachine that does not touch or bite into the tapered surface of the outer periphery of the turbomachine. The second object of the present invention is to always prevent the Taber blood 111 on the tips of stator blades and the outer periphery of the rotor disk, regardless of whether during rated operation or partial load operation such as IJJ operation.
An object of the present invention is to provide a 11f variable static relaxation type turbomachine that can set a gap of 1 to a minimum gap. A third object of the present invention is to provide a UF variable stator vane type turbomachine that can drive a stator vane moving mechanism that moves the stator vanes in the radial direction of the casing independently of the stator vane moving mechanism if necessary. It is in. A fourth object of the present invention is to provide a +Jf variable stator vane type turbo machine that can always maintain the gap between the tip of the stator vane and the tapered surface of the outer periphery of the rotor disk at an appropriate target gap under any operating conditions. The goal is to provide the following. A fifth object of the present invention is to provide a variable quiet and relaxed turbomachine that can improve fluid performance under rated operating conditions.

[Means to solve the problem]

The first purpose is to have a stator blade u that adjusts the angle of attack of the stator blade relative to the main stream (a variable mechanism includes a stator blade U that moves the stator blade in the radial direction of the casing in synchronization with the adjustment of the angle of attack of the stator blade relative to the main stream). The second objective is achieved by separating the static and relaxed movement mechanism from a stator blade rotating shaft connected to the outer end of the stator blade, and a stator blade rotating shaft connected to the outer end of the stator blade. This is achieved by attaching the stationary blade rotating shaft in a direction forming an octagon with respect to the taber r/Ij on the outer periphery of the rotor disk.

The third object is achieved by driving the stationary vane shifting mechanism independently of the stationary vane opening changing mechanism and arranging the stationary vane to move in the radial direction of the casing. The fourth purpose is to control the temperature and thermal deformation of the rotor and casing during operation, and to control the temperature and thermal deformation of the rotor and casing during operation.
A total of 81 caps! L L. This is achieved by providing a control system that controls the stator blade moving mechanism according to the measurement information.

The fifth purpose of the front 1d is to shape the entire surface of the tips of the stator blades into a curved surface so that the gap between the tapers on the outer periphery of the opposing rotor disks is equal in the quiet position during rated operation. This is achieved by forming the

[Effect]

In the present invention, the stator blade is moved to the stator blade aJ change mechanism! The same JIJI L is operated next to the FLL aircraft. As a result,
When the stationary blade is rotated from the rated operation position to the partial load operation position such as during start-up operation using the static xI1■ change mechanism,
The stator blade is moved in the radial direction of the casing by the stator blade moving mechanism from the state during rated operation, where the gap between the tip of the stator blade and the taper surface of the outer periphery of the rotor disk is set to the minimum gap. The tip of the rotor disk is held in a position where it does not come into contact with or become wedged in the taper blood on the outer periphery of the rotor disk. In addition, when the stator blade is adjusted from the position during partial load operation to the position during rated operation by the stator blade pJ change mechanism, the stator blade moves! l!
The lI mechanism moves the vane to b't, where the gap between the tip of the stator vane and the outer periphery of the rotor disk becomes the minimum gap, and holds it at that position.

Further, in the present invention, the stator blade rotational f-changing mechanism is constituted by a stator blade rotation axis and its rotation drive part, and the stator blade rotation axis is perpendicular to the Taper surface of the outer peripheral part of the rotor disk. Since it is installed in the direction, if the gap between the tip of the stator vane and the tapered surface of the outer periphery of the rotor disk is set to the minimum gap during manufacturing, it will work regardless of whether it is in rated operation or partial load operation. The gap between the tip of the stator vane and the tapered surface of the outer circumference of the rotor disk can always be maintained at the maximum gap. Furthermore, in the present invention, the static The stationary vanes can be moved in the radial direction of the casing.

In the present invention, the control system measures the temperature and thermal deformation of the rotor and casing during operation, as well as the gap between the rotor and casing during operation, and controls the stator blade movement mechanism according to the measurement information. That's what I do. Therefore, under any operating conditions, the gap between the tip of the stator vane and the tapered surface of the outer circumference of the rotor disk is always set to the appropriate i:
In addition, in the present invention, in the position of the stator blade during rated operation, the entire surface of the tip of the stator blade can be maintained at the gap between the taper blades on the outer periphery of the opposing blade. Since it is formed into a curved surface so that the values are equal, it is possible to improve fluid performance under rated operating conditions. [Example] Hereinafter, an example of the present invention will be explained with reference to Figures u+i. 1st
Figure, No. 21ll! 1I shows the first embodiment of the present invention, and FIG. 1(A) is a section Ij of the stator blade portion in the rotor axial direction at the time of rated operation, and FIG. 1(B) is at the same rated operation. Figure 2 (
A) is a cross-sectional view of the IIJ variable stator vane portion in the rotor axial direction during start-up operation, and Figure 2 (B) is a diagram showing the attitude of the stator blade with respect to the mainstream during the same start-up operation. In the first embodiment shown in these figures, a stator blade pedestal 15 is integrally attached to the radially outer end of the casing 5 of the stator blade 1. A rotating stationary blade @2 is connected to the stationary blade pedestal 15, and a rotating piece 1 is connected to the stationary blade rotating shaft 2.
2 are attached together. The rotating piece 12 has a.
A stator blade rotation gear 4 is attached, and a rotation drive gear 3 is meshed with this stator blade rotation gear 4. On the other hand, the casing 5 has a stator vane platform stator storage section formed on the inner circumferential side, and a spring storage section formed on the outside thereof.The casing 5 also has a stator blade rotation shaft insertion hole formed therein. It has been done. The stator vane pedestal 15 is housed in the stator vane pedestal storage section. A gap 16 is provided in the radial direction of the casing 5 between the stator blade pedestal storage portion and the stator blade pedestal 15,
By providing this gap nllllf3, the stationary X1 can be moved in the radial direction of the casing 5. A compression spring 14 is stored in the spring storage portion.
This compression spring 14 pushes the stator blade 1 toward the center of the casing 5 via the static pedestal 15. The stator vane rotating shaft 2 is inserted into the rotating shaft insertion hole. Inside the casing 5, a sealing device 17 such as an O-ring is provided around the stator blade rotating shaft 2. This sealing device 17 prevents the working fluid from leaking from the plow lift l 6 to the outside of the casing 5 through the rotary shaft insertion hole.

A fixing piece 11 is attached to the outer peripheral side of the casing 5. This fixed piece 11 is in contact with a rotating piece 12 attached to the stationary blade rotation shaft 2 through an inclined cam 13. A gap is provided between the tip of the stationary blade 1 and the tapered surface 7' of the outer circumference of the rotor disk 7. In this embodiment, the stator blade rotation 4llll2, the stator blade rotation gear 4, and the rotary drive wheel 3 constitute a stator blade+lIr image mechanism that adjusts the angle of attack of the D blade 1 with respect to the mainstream. In addition, the fixed piece 11, the rotating piece 12, the inclined cam blood 13 which is the contact 1nI between the fixed piece 11 and the rotating piece 12, and the compression spring 14 synchronize with the adjustment of the angle of attack with respect to the main flow of the static R1. This constitutes a stator blade moving mechanism that slides the stator blade 1 in the radial direction of the casing 5. In the above-described first embodiment, the fixed piece 11 and the rotating piece 12 are arranged at an angle. They are in contact with each other through a cam 13, and this inclined cam 13 is given an appropriate pressure by a compression spring 14. In addition, the initial setting positions of the fixed piece 11 and rotating piece 12 at the inclined cam 13 are as follows. As shown in Figure 1 (B), the minimum gap δ can be ensured during rated operation. On the other hand, as shown in Figure 2 (13), during partial load operation such as startup operation, the Rotate the blade 1 in the direction of closing it to the mainstream, and change the angle of attack with respect to the mainstream from θ to θ′ (θ
′〉θ). In this case, in this example @2
As can be seen from Figure (A), the rotating piece 12 is tilted by the inclined cam +h
i J 3, and moves the stator blade 1 toward the outside of the casing 5 in the radial direction through the stator blade rotation axis 2.

Therefore, by appropriately setting the inclination angle of the jet cam 13, it can be synchronized with the rotation of the static X1.
The gap between the tip of the static X1 and the taper 7' on the outer periphery of the rotor disk 'l can always be controlled to the required minimum gap δ. In addition, when the stator blade 1 is adjusted from the posture during partial load operation to the posture during rated operation via the rotary drive gear 3, the stator blade rotation gear 4, and the stator blade rotation shaft 2, the stator blade 1 is synchronously adjusted. Inclined cam 13 between fixed piece 11 and rotating piece 12
Due to the action of
It moves to a position where the gap between the tapers 7' on the outer periphery becomes the minimum gap δ shown in FIG. 1(A), and is held at that position.

In FIG. 2(A), δ' indicates the maximum gap between the tip of the stationary blade 1 and the taper 7' on the outer circumference of the rotor disk 7 during partial load operation such as startup operation. Next, FIGS. 3 and 4 show a second embodiment of the present invention, and FIG. Figure 3 (H) is a diagram showing the attitude of the stationary blade with respect to the main flow during the same rated operation, and Figure 4 (
A) is a cross-sectional view in the rotor axial direction of the carbonized stator blade portion during startup operation, and FIG. 4(B) is a diagram showing the attitude of the stator blade with respect to the mainstream during the same startup operation. In the second embodiment shown in these figures, a thread 18 is formed at the end of the rotary stator blade @2, and a nut 19 having a female thread that engages with the male thread 18 is fixed to the outer peripheral side of the casing 5. It has been done. Then, the male screw 18 and the nut 19
This constitutes a stator blade moving mechanism that moves the stator blade 1 in the radial direction of the casing 5 in synchronization with the adjustment of the angle of attack of the stator blade 1 relative to the mainstream. In this second embodiment, the stationary blade rotating shaft 2 is rotated, and the stationary
When the angle of attack with respect to the main stream 1 is adjusted, the stator blade rotating shaft 2 is moved in the axial direction by the screw action of the male screw 18 and nut 19 in synchronization with this. Therefore, the stator blade rotation I1l
The stationary blade 1 can be moved in the radial direction of the casing 5 via the 1ll2. Other configurations of this second embodiment,
The operation is similar to that of the first embodiment. Next, FIGS. 5 and 6 show a third embodiment of the present invention, and FIG. 5(A) is a sectional view in the rotor axial direction of the cII variable vane portion during rated operation, and FIG. (B) is a diagram showing the attitude of the stationary blade with respect to the main flow during the same rated operation, No. 6
Figure (A) is a sectional view of the variable stator vane portion in the rotor axial direction during start-up operation, and Figure 6 (B) is a diagram showing the attitude of the stator blade with respect to the mainstream during the same start-up operation. In the third embodiment shown in these figures, a stator vane pedestal housing portion is formed on the inner circumferential side of the casing 5 and has a substantially triangular shape when viewed from a direction perpendicular to the rotor axis direction. On the other hand, a substantially triangular stator vane pedestal 20 is integrally attached to the radially outer end of the stator vane 1 to be inserted into the stator vane pedestal storage portion. A stator blade rotating shaft 251 is attached to the stator blade pedestal 20 in a direction perpendicular to the tapered surface 7' of the outer peripheral portion of the rotor disk 7. A stator blade rotation gear 4 is connected to the stator blade rotation shaft 21, and the stator blade rotation gear 4 is meshed with the rotation drive gear 36. The angle of attack of the stator blade 1 relative to the main flow can be adjusted via the stator blade co-rotating shaft 21 by the rotary gear 4. In this third embodiment, the stationary blade rotating shaft 21 is attached in a direction perpendicular to the tapered surface 7' of the outer part of the rotor disk 7, so that ), the gap between the tip of the stationary blade 1 and the taper 7' on the outer periphery of the rotor disk 7 is always kept at the minimum gap, regardless of whether during rated operation or during partial load operation such as startup operation. It can be set to δ. Next, FIG. 7 shows a fourth embodiment of the present invention.
FIG. 3 is a cross-sectional view of the variable stator blade portion in the rotor axial direction. In this fourth embodiment, an engagement groove 25 is formed on the outside of the casing 5.

On the other hand, a male thread 22 is formed at the outer end of the stator blade rotating shaft 2. Furthermore, a stator blade rotation gear 4 is integrally attached to the end of the male thread 22 of the stator blade rotation shaft 2. This stator blade rotation gear 4 is a rotary drive gear. It is meshed with 3. On the other hand, the male thread 22 of the stator blade rotating shaft 2 has a female thread 24.
A stationary blade moving gear 24 having a diameter of 1.a is screwed together. This stationary blade moving gear 24 is provided with an annular projection 24b, and this annular projection 24b is engaged with an engagement groove 25 formed in the casing 5. As a result, the stationary blade moving gear 24 can rotate at a predetermined position in the axial direction of the stationary blade rotating shaft 2. Further, the stationary blade moving gear 24 is meshed with a drive gear 23 dedicated to moving the stationary blade.

In this fourth embodiment, the stator blade rotation 411112, the stator blade rotation direction wheel 4, and the rotary drive gear 3 constitute a stator blade variable mechanism that adjusts the attack angle of the tO blade 1 with respect to the main stream. ．． Further, an annular protrusion 24b is attached to the male thread 22 formed on the stator vane rotation 4+lil2 and the male thread 22 through the female thread 24a, and is attached to the engagement groove 25 formed on the casing 5.
A gear 24 for static and relaxing movement engaged through the gear 24, a gear 23 exclusively for moving the stator blade, a stator blade pedestal storage portion formed on the inner circumferential side of the casing 5, and a gap 16 formed therein. The stator blade pedestal 15 housed in the stator blade pedestal 15 constitutes a #iI blade shifting mechanism that functions independently of the stator blade Ilf shifting mechanism.
When the stator blade moving gear 24 is rotated by the driving gear 23, the stator blade moving mechanism engages the engagement groove 25 and the annular engagement groove 2.
4b, the static R moving gear 24 moves to the stator blade rotation shaft 2.
rotates at a fixed position in the axial direction. When the stator blade moving gear 24 rotates at a predetermined position in the axial direction, the stator blade rotating shaft 2 is moved in the axial direction by the screw action of the male thread 22 and the female thread 24a. therefore. In this embodiment, the static '
Separately from adjusting the attitude of R1, if necessary, move the stationary blade fli
The stationary 'Rl- can be moved in the radial direction of the casing 5 by the t mechanism.

For other configurations of this fourth embodiment, see %n1f, Section 1.
This is similar to the example in . Furthermore, FIG. 8 is a partially cutaway system diagram showing a fifth embodiment of the present invention.

In this fifth embodiment, similarly to the fourth embodiment, the stationary blades of variable 4! In addition to the structure and the stator blade moving mechanism being configured to function independently, a control system is provided to control the stator blade moving mechanism.

In the above control system, @the tip of the wing and the casing lf
The gap of tl is 71113 in total using the gap sensor 107.
Then, the gap in the axial direction between the rotor and the casing is measured using a gap sensor 108. Also, the temperature of the casing,
The temperature of the rotor and the temperature of the working fluid are measured by temperature sensor 109. , 110, 111. These measured values 101 and the rotation angle 10 of the stationary blade at that time
From the data of 2. At that time, calculate the gap between the tip of the stationary blade and the outer circumference of the rotor disk (No. 8
The figure shows the calculation and display of the stator blade tip gap amount). This calculated value 103 is compared with the target gap 104 (in Fig. 8, the stator blade tip target gap and table box) are compared, and the difference between the two is calculated. Then, based on the difference between the previous ddn constant value 103 and the target gap 104, the servo amplifier 105 is adjusted to match the two.
A 618 signal is sent to the actuator 106 through the 618 signal, which drives the gear 23 of the stator blade moving mechanism, rotates the blade moving gear 24, and rotates the stator blade rotating shaft 2 by the screw action of the male screw 22 and female screw 24a. direction, and adjust the gap between the tip part of the stator blade 1 and the taper 7' of the external wetted part of the rotor disk 7.6 As a result, under any operating conditions, the tip part of the stator blade 1 and the rotor The gap between the Taber's blood 7' on the outer periphery of the disk 7 can always be maintained at an appropriate target gap 104. Proceeding, FIG. 9 shows a sixth embodiment of the present invention,
Figure 9 (A) is a diagram showing the position of the stationary blade with respect to the main flow during rated operation, Figure 9 (B), ((.:) are B-}3 & IA and C-C in Figure 9 (A), respectively) This is a line cross-sectional view. In this sixth embodiment, at the position of the stationary blade 1 during rated operation, the entire surface of the tip 26 of . It is formed in a curved shape so that the gap between the two and According to the described invention, the stator blade iiJ variable mechanism that adjusts the angle of attack with respect to the main stream of the rotor blade is provided with a stator blade that moves the front Kd stator blade in the radial direction of the casing in synchronization with the adjustment of the angle of attack with respect to the main stream of the rotor blade. Since a blade moving mechanism is provided, the gap between the tips of the stator blades and the outer periphery of the rotor disk is the minimum gap during rated operation, and the tips of the stator blades are kept at the minimum gap during partial load operation such as during startup. This has the effect of eliminating the problem of contact with or getting stuck in the Tauber's blood on the outer periphery of the rotor disk.

Further, according to the invention recited in claim 2 of the present invention, 0 wing if
The variable mechanism is composed of a stator vane rotation shaft and its rotation drive part, and the stator vane rotation shaft is attached in a direction perpendicular to the tapered surface of the outer circumference of the rotor disk. By setting the gap between the tip of the stator vane and the tapered surface of the outer part of the rotor disk to the minimum gap, both during rated operation and partial load II! ! Regardless of the time of change,
This has the effect of always keeping the gap between the tip of the stationary blade and the tapered surface 1fJJ of the outer periphery of the rotor disk at the minimum gap. Furthermore, according to the third aspect of the present invention, since the static blade moving mechanism is configured to be able to be driven independently of the D blade variable mechanism, the static blade moving AFI mechanism can be moved statically if necessary. It is driven separately from the vane mechanism and has the effect of moving the stationary blades in the radial direction of the casing. According to the fourth aspect of the present invention, the temperature and thermal deformation of the rotor and casing during operation and the gap between the rotor and casing during operation are measured by the control system, and a total of 811 pieces of information are obtained. Therefore, under various operating conditions, the tip of the stator blade and the cap in the direction of the taper on the outer periphery of the rotor disk are always set at an appropriate target. In addition, according to the invention set forth in claim 5 of the present invention, in the position of the stator vane during rated operation, the entire surface of the tip of the stator vane is connected to the outer circumference of the opposing rotor disk. Since it is formed in a curved shape so that the gap between the tapers is equal,
This has the effect of improving fluid performance under rated operating conditions.

[Brief explanation of drawings]

Figures 1 and 2 show a first embodiment of the present invention.
Figure 1 (A) is a 1-meter cross section of the variable Ir# blade section in the direction of the rotor cap during rated operation, Figure 11 (13) is a diagram showing the attitude of the stationary blade with respect to the mainstream during rated operation, and Figure 2 (A) is a sectional view of the variable stator vane portion in the rotor phase direction during start-up operation, Fig. 2 (B) is a view showing the attitude of the stator blade with respect to the mainstream during start-up operation, Figs. 3 and 4 shows the second embodiment of the present invention, and FIG. 3(A) shows the rated 'M
Cross-sectional view of the variable stator vane portion in the rotor axial direction during rotation,
Fig. 3 (H) is a diagram showing the upstream attitude of Seikan during the same rated operation, and Fig. 4 (A) is a diagram showing the L position during start-up operation.
Cross-sectional view of the If variable vane portion in the rotor axial direction, Fig. 4 (B)
is a diagram showing the attitude of the stationary blade with respect to the main stream during 1jJ operation, Figures 5 and 6 show the third embodiment of the present invention, and Figure 5 (A) is the attitude during rated operation. A cross-sectional view of the Ijf variable stator vane portion in the rotor axial direction, Fig. 5 (B) is a diagram showing the attitude of the stator blade with respect to the mainstream during the same rated operation, and Fig. 6 (A) is the variable stator vane portion during startup operation. FIG. 6(B) is a cross-sectional view of the rotor in the axial direction, FIG. ．． If the low part of the change/relaxation part
Fig. 8 is a partially cutaway system diagram showing the fifth embodiment of the present invention, and Fig. 9 shows the sixth embodiment of the present invention. A) is a diagram showing the position of the stationary blade relative to the main stream during rated operation, and Figures 9 (B) and (C) are the B-B line and c-cH diagram of Figure 9 (A), respectively. ．． Figure 10 is a cross-sectional view of a multi-stage axial flow compressor, which is an iJ variable stator vane type turbomachinery, Figures 11 and 12 show conventional technology, and Figure 11 (A) shows the flow rate during rated operation. A cross-sectional view of the stator blade portion in the rotor axial direction, FIG. 11 (H) is a diagram showing the attitude of the stator blade with respect to the mainstream during the same rated operation,
FIG. 12(A) is a sectional view of the variable stator vane portion in the rotor axial direction during startup operation, and FIG. 12(H) is a diagram showing the attitude of the D blade with respect to the mainstream during the same startup operation. 1... Stator blade, 2... Stator blade rotation axis, 3... Rotary drive!
l! lI1 tooth 11L, 4...Stator blade rotation gear, 5...
・Casing, 7... Rotor disk, 7'... Tapered, 11... Fixed piece, 12... Rotating piece, 13...
...Tilting force l1 plane, 14...Compression spring, δ...Minimum gap, 17...Sealing device, 18...Male thread, 1
9...Nut, 21...Stator blade rotation ÷llll. 22・
・・Male thread, 23 ・・Drive gear exclusively for moving stator blades, 24
...Stator blade moving gear, 24a...Female thread, 24b.
... Annular projection, 25 ... Engagement groove, 26 ... Tip of stator blade, 101 ... Temperature, thermal deformation, measured value of rotor blade tip gap, 102 ... Rotation angle of stator blade, 103... Calculated value of the gap between the tip of the stationary blade and the taper of the rotor disk, 104... Target gap, 105... Servo amplifier, 106... Actuator, 10'7, 10
8. Gap sensor, 109, 110, ill...Temperature sensor. CB) υ case 1 house call (B) Start 1 transfer point V 5--1γ1〉n7゛゜22-- 9 ,? 'L L- Z5 ---I play meeting i number Q Z6 1%. ! ,1 Scarce ■ Com Tomi/ρ Figure l ? - 11th 2 zoyashi ph. ■ Shitoko (A) (E3) Teioi Tenginka ・z 1 (A) (F3)

Claims (1)

[Claims] 1. A stator vane is attached to the inner peripheral side of the casing, and a tapered surface inclined in the rotor rotation axis direction is formed on the outer peripheral part of the rotor disk located at the tip of the stator vane. In a variable stator vane type turbomachine provided with a variable stator blade mechanism that adjusts an angle of attack of the stator blade relative to the main stream, the variable stator blade mechanism is provided with a casing for the stator blade in synchronization with adjustment of the angle of attack of the stator blade relative to the main stream. A variable stator vane type turbomachine characterized by being provided with a stator blade moving mechanism that moves the stator blade in the radial direction. 2. A stator vane is attached to the inner peripheral side of the casing, and a tapered surface inclined in the direction of the rotor rotation axis is formed on the outer peripheral part of the rotor disk located at the tip of the stator vane, and a taper surface is formed on the outer periphery of the rotor disk located at the tip of the stator vane. In a variable stator vane type turbomachine equipped with a variable stator vane mechanism that adjusts the angle, the variable stator blade mechanism is connected to a stator blade rotating shaft connected to an outer end of the stator blade, and a rotation of this stator blade rotating shaft. 1. A variable stator vane turbomachine comprising: a drive unit, wherein the stator vane rotating shaft is attached in a direction perpendicular to a tapered surface of an outer peripheral portion of the rotor disk. 3. The variable stator vane type turbomachine according to claim 1, wherein the stator vane moving mechanism is configured to be driven independently of the variable stator vane mechanism so that the stator vanes can be moved in the radial direction of the casing. . 4. A control system is provided that measures the temperature and thermal deformation of the rotor and casing during operation, and the gap between the rotor and casing during operation, and controls the stator blade moving mechanism according to the measurement information. The variable stator vane type turbomachine according to claim 3. 5. The entire surface of the tip of the stator vane is formed into a curved surface so that the gap between the tapered surfaces of the outer periphery of the opposing rotor disks is equal in the position of the stator vane during rated operation. The variable stator vane type turbomachine according to claim 1, 2, 3, or 4.