JPS5870096A - Stacked rotor for use in axial-flow compressor - Google Patents

Abstract

PURPOSE:To enable to reduce the bending stress produced by the centrifugal force acted to a stacking bolt considerably, by shaping the stacking bolt such that the portions of the stacking bolt to be inserted into drilled holes have substantially a rectangular cross section by cutting away the opposite sides thereof. CONSTITUTION:A stacking bolt 18 is shaped to have a circular cross section at the portions 18a thereof where it is inserted into reamed holes 4, 6 and to have a substantially rectangular cross section at the portions 18b thereof having a length l where it is to be inserted into drilled holes 5. Here, the width b at the portions 18b having a substantially rectangular cross section is selected to satisfy the following relationship, b 0.6d, where d is the diameter of the bot 18 at its portions 18a having a circular cross section. By thus shaping the stacking bolt 18 to have a rectangular cross section at several portions thereof, it is enalbed to reduce the weight per unit length of the bolt 18. Resultantly, the bending stress produced by the centrifugal force acted to the stacking bolt 18 when a rotor is turned can be reduced extremely.

Description

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, several disks for shielding blades are arranged in the axial direction, and the disk assemblies are connected to stacking holes extending at multiple locations in the circumferential direction. This invention relates to a stacked rotor of a type of stream pressure compressor that is tightened and connected with a nut.

FIG. 1 shows a stacked rotor commonly employed in gas turbines.

What is shown in this figure is a first disk l having reamed holes 4 which are a plurality of bolt holes in the circumferential direction.
The second disk 2. which is placed on both sides of the disk 1 of the M-shape 11 has a drilled hole 5 which is fitted with a bolt hole provided at a position corresponding to the reamed hole 4. WIJ3 is an end disk that connects the reamed hole 6 for bolt holes and the entry 7 for nuts to the south.
disks 3 are arranged in the axial direction, and these first disks 3 are aligned in the axial direction. Second
．． Insert the stacking bolts 8 into the reamed holes 4, drilled holes 5 and bolt holes 1)-6 of the disc assembly from the third disc 1, 2.3, and tighten the nuts 9 at both ends of the disc assembly. and tighten the nut 9 to connect.
It is assembled into a single stacked rotor. In addition, the first
Illustration number 10 is the first. 2nd and 3rd disks 1, 2. q
, 11 is the rotor shaft, 12 is the first. Second. The third disc 1,2°3 shows the iron layered blade.

In the PTff Todoroki stack rotor, the rotational torque due to the secret wJ is the first. Second. Since the transmission is made by the contact surface 100 degrees between the third disks 1, 2, and 3 degrees, Vc is applied to the first, second, and third disks by the stacking bolt 8 in order to obtain sufficient contact surface pressure to transmit one rotation torque. There are 8 parts that fully tighten the disc assembly consisting of the third disc 1, 2.3. - In the example, the tightening force of stacking bolt 8 is gQQ
The 4 major stresses are 34Kg/wr".

Therefore, in the stacked rotor VC, the 18 strands of the stacking bolt 8 are non-hanging VC power.

The stacked rotor described above generally has the following advantages.

(1) In the H1At type field machine, the blade is most severely damaged due to foreign matter being sucked in, but it is possible to replace the blade.

(2) Since the weight of the entire rotor can be reduced and the inertial force of the rotor can be reduced, the drive shaft can be made smaller.

However, in addition to the tightening force for assembling the disc assembly, the stacking bolt that connects the disc assembly generates centrifugal force in the rotor, and this retardation force causes large bending stress to act on it. It gives you peace of mind to be careful.

The centering force acts in the direction of causing the stacking bolt to pop out, and the force is stopped by the bolt hole of the disc. The problem here is
The problem is that all the disk bolt holes are in contact with the stacking bolts. That is, if the bolt hole clearance of all disks is reamed and the gap between the stacking bolt and the bolt diameter is made minute, a problem arises in that the stacking bolt cannot be pushed in at the 0 assembly level or later. On the other hand, make the bolt holes larger.

If the gap between the stacking bolt and the bolt hole is increased, the stacking bolt can be pushed in easily, but there is a problem that the contact points between the stacking bolt and the bolt hole are not constant.

Therefore, in the prior art shown in FIG.

The bolt hole of the first disk l is a reamed hole 4.

The bolt of the second disk 2 adjacent to the first disk 1 has a drilled hole 5 larger than the hole 4.
At the assembly stage, the presence of the drilled hole 5 facilitates the insertion of the stacking bolt 8, and during rotor operation, the centripetal force acting on the stacking bolt 8 is prevented through contact between the reamed hole 4 and the stacking bolt 8. .

However, the prior art shown in FIG. 1 has the following drawbacks. That is, during rotor operation, the first disk 1
At this point, the stacking bolt 8 and the reamed hole 4 come into contact, and the centrifugal force acting on the stacking bolt 8 can be stopped.

Since a gap exists between the stacking bolt 8 and the drilled hole 5 in the second disk 2, the stacking bolt 8 is bent by the bending stress caused by the central force.

FIG. 2 schematically shows the bending state of the stacking bolt 8 in the drilled hole 5 provided in the second disk 2 during rotor operation.

In one example, the width of the second disk 2 shown in FIG. 2, that is, the length of the drilled hole 5, t=160 m.

The length of the drilled hole 5 t The centrifugal force W supported by the dark stacking bolt 8 is 11 tons, and the bending stress generated at that time is 2
4Kg/m''.In addition, if the axial tensile stress acting on the stacking bolt 8VC for tightening the disk assembly is 34~/van'', then the tensile stress is 1Kg/m''.
The principal stress of bending becomes extremely large, reaching the 0.2% yield strength of the stacking bolt material, which is an extremely dangerous limit state. In addition, in a stacked rotor, if the stacking 7I belt 8 is broken, the disk assembly will disassemble, resulting in a serious accident.

As can be seen from the above, one of the parameters that affects the magnitude of the VC1 stress is the length of the gap corresponding to the span from the fulcrum of deformation, that is, Figs. 1 and 2. The length of the drilled hole 5 is t. By shortening the length t of this drilled hole 5, one bending stress can be reduced.

Figure 1g3 shows the numerical position ν with the length of the specified drill hole shortened.

In the example shown in this kIJ3 diagram, all disks 13
As for the reamed hole 14, which is half the length of the bolt hole,
The remaining half is made into a drilled hole 15, and the stacking bolt 16 is extended through the bolt hole in which the reamed hole 14 and the drilled hole 15 are aligned with each other. I keep it short. What is shown in this Figure 3.

It is true that the bending stress applied to the V stacking bolt is reduced compared to that shown in Fig. Difficult+, there are drawbacks that do not suit the production base.

Objective V of the present invention: To eliminate the drawbacks of the above-mentioned fecal mosquito treatment.

To provide a stacked rotor for a single flow press machine which can effectively reduce the stress caused by concaveness caused by an acute force acting on a stacking bolt, is easy to process and assemble, and can be applied to ready-made disks.

The organic disk of the present invention is a disk in which a first disk with a reamed hole M, a 5g2 disk with a drilled hole M, and disks W and S, which are end disks that fit into the reamed hole or the drilled hole, are arranged. assembly.

In a stacked rotor that is tightened and connected with a stacking bolt and a nut fitted into the stacking bolt.

The stacking bolt's nil perforated hole vC is pushed through the partial tone % l#T surface, which has the inner part cut out, is formed into a roughly rectangular shape, and with this configuration, all of the above objectives can be achieved in a distant manner.

The present invention will be described below based on FIG.

4, 5A and 5B illustrate an embodiment of the present invention, and 6.
The figure shows the relationship between stacking bolts and morphs/steller sea lions.

In the embodiment shown in FIG. 4, the first disk 1 has a reamed hole 4 which is a bolt hole, and a drilled hole 5 which is a bolt hole and is arranged on both sides of the first disk 1 in the axial direction. The second disc 2 has a reamed hole 6 and the entry 7 for the nut, and a third disc 3 which is an end disc located to the south and axially outside of the second disc 2. The assembly is constructed, a stacking bolt 18 is inserted into the bolt hole including the reamed hole 4, the drilled hole 5 and the other reamed hole 6 in the shielding disc assembly, and a nut 1 is inserted into the threaded portion of both ends of the stacking bolt 18.
9 is housed in the animal shelter, but the left side is partially omitted in this Figure 4.

@fid Several reamed holes 4 in the disk 1 of M1 are provided at equal intervals in the circumferential direction, and the diameter of the reamed holes 4 is such that no VC gap is created between the valley reamed holes 4 and the stacking bolt IB.hFpi table is formed.

The drill hole 5 of the second disk 2 is provided at a position corresponding to the reamer hole 4, and the stacking bolt 18
The dimensions are such that there is no gap between the two.

The reamed hole 6 of said third disk 3 is formed coterminously with the reamed hole 4 of the first disk 1.

As shown in FIGS. 4 and 5A and 5B, the stacking bolt 18F has a portion 188 inserted into the front hole 4.degree. 6 having a circular cross section.

The portion 18b inserted into the drilled hole 5 has a substantially rectangular cross section. The diameter of the portion 18b having a substantially rectangular cross section is sb?, where d is the diameter of the portion 18a having a circular cross section.
It is formed to 0.6 cl. Furthermore, the substantially rectangular portion 18b of the front dividing enclosure is set with its one direction and the longitudinal direction facing the radial direction of the second disk 2.

PJtJ Book 1. 2nd and 3rd disk 1, 2゜3
The disk assembly is assembled into a stacked rotor by tightening nuts 19 fitted to both ends of stacking bolts 1B inserted into each bolt hole.

In addition, No. 4 Kyouchu issue No. 10 is No. II No. 2. The contact surface of the third disk 1, 2.3, 11 is the rotor support.

12 is the first. 21 shows the blade loaded onto the third disk 1, 2.3.

In the stacked rotor of the M'Q example, the stacking bolt 18 is tf148b pushed through the drilled hole 5, which is the bolt hole of the second disk 2.

That is, an evaluation of the bending stress acting on a portion whose cross section is 1 second square can be considered by considering one piece as a beam supporting both ends of the second disk 2 with a length corresponding to -.

Now, if the centrifugal force applied to the stacking bolt 18 is treated as a uniformly distributed load in the length direction of the stacking bolt 18, then the frog bend of the stacking bolt 1B is caused by the stress σbrna
x occurs in Suba/medium heat, linear formula (1)% formula% Here, pigeon... direction @ (centered force)! ...Span (length of drilled hole) Z...=r=modulus Z in section modulus formula (1) The approximately rectangular part shown in FIG.

π z , == d S ・・
...(2) 2 ml a self 1 lj The diameter d of the circular part of the T plane and the height h of the rectangular cross section part are 7 degrees, and the surface constant Z1 of the part in the -T plane is The section modulus Z of the rectangular section part, and the I distance of the rectangular cross section, which is a combination of porcelain, is determined by the following equation (
4) It will look like this.

As you can see from this person (4), stacking bolt 1
8 is shown in FIG. 5B.

Even if the diameter d of the circular section on the Wr surface is approximately rectangular and the section of the rectangular section is +11bi and bζ0.6d, the section modulus Z remains the same. About this.

As shown in equation (1), the bending of the stacking bolt 18 means that the stress is the same whether the cross-sectional shape is circular or rectangular if the shear [l] coefficient Z is the same.

It is expressed in the above formula (1). The value of the reverse central force W acting on the stacking bolt 18 from the rotor rotation 1v- is.

It is determined by the following equation (5).

ΔW W=-・R・ω (5) However, ΔW... nkR per level length... Radius ω... Angular deviation As is clear from this equation (5) The centrifugal force W is proportional to itΔW per unit length. As a result, by making a portion of the stacking bolt 18 rectangular, the amount of electricity per unit length can be reduced.

It can be seen that the bending caused by the centrifugal force W caused by the rotation of the rotor of No. 7 can reduce the stress.

- As an example, the direct distance d of a circular cross-sectional part is 38φ.

If the M2S screw is fitted with a stacking bolt with a thread root shape d+=33φ and the cross-sectional engagement Z is the same value, the width b of the rectangular cross-sectional portion can be set to 23 m. In this case, when embedding with the cross-sectional area ratio, the side area of the circular cross-sectional area is 1
The length is 133 m", and the rolling value of the rectangular section is 886 m". As a result, a circular section and Il
The centrifugal force ratio of the Ill-shaped portion is 1/1.3, and the bending stress ratio is also 171.3. Therefore, when the bending stress of the circular section section is 24 kg/wrr, the bending stress of the -1 plane rectangular section is reduced to about 18 to 9/llll111.

As can be seen from the above explanation, compared to the prior art example in which stacking bolts made of cedar are used, the cross section of the portion corresponding to the length t of the drilled hole 5 of the second disk 2 of the disk assembly is In the case of using the stacking bolt 18 formed into a substantially rectangular shape, the bending stress can be significantly reduced.

In addition, part of the stacking bolt '1iJtr surface rectangle 7
1, there is a problem if the axial tensile stress due to the loading force of the disk assembly increases significantly.
The width of the approximately rectangular section is b: Q, (id, then the cross-sectional area of the approximately rectangular section is approximately the same as the diameter of the root of the stacking bolt screw, so No particular problem arises with respect to the tensile stress.

The present invention is based on one or more of the configurations described above.

According to the present invention, the part of the stacking bolt that is pushed through the drilled hole is cut out with a length of 9111 m per car.By making the part of the stacking bolt into a rectangular shape, the bending stress acting on the stacking bolt is significantly reduced, so the stacking There are young fruits that can greatly improve the reliability of bolts.

In addition, in the present invention, as in the conventional case, the first disk in the disk assembly is provided with a full bore hole.

The bolt holes of the second disk are drilled holes, and the bolt holes of the third disk are reamed holes or drilled holes, so it has a young pot that can process the bolt holes and assemble the disks at a high rate. There is also an effect that can be applied as is to ready-made disk assemblies.

[Brief explanation of the drawing]

Figure 1 is a vertical enclosure diagram of a portion of a conventional stacked rotor.
FIG. 2 is an explanatory diagram of the stacking bolt used in the prior art due to the centripetal force, and FIG. 3 is a longitudinal sectional view of a portion showing another example of the prior art. Fig. 4 is a longitudinal cross-sectional view of a portion showing an embodiment of the present invention, Fig. 5 A and B are enlarged cross-sectional views of A-A and B-B Iwakiri moe in Fig. 4, and Fig. 6 is a stacking This is a diagram showing the relationship between what is applied to the bolt and the moment. 1.2.3...First I constituting the task assembly
i2. i3 disc, 4... Reamed hole that is the bolt hole of the first disc, 5... Perforated hole that is the bolt hole of the IJIJ2 disc, 6... Reamed hole that is the bolt hole of the third disc. , 18...Stacking bolt. 18a... circular part of the stacking bolt facing vEJr. 18b...The same cross-sectional rectangular part, d...The diameter of the circular cross-sectional part, b...The vr plane is 1% of the approximately rectangular part, 19
...Natsuto. Agent Patent Attorney Oriyuki Hakata χ 17 λ) 21Zl ′Y53 Oro /4 /4 To /4≧1-544-

Claims (1)

[Scope of Claims] 1. Reamed holes are provided at several positions in the circumferential direction to fit bolt holes with no gaps between the stacking bolts, and reamed holes are provided on both sides of the first disk at positions that match the reamed holes. A second disk having a drilled hole, which is a bolt hole with a gap between the stacking bolts, is arranged, and these first disks are arranged. aR2
A third disk, which is an end disk having a reamed or drilled hole, is placed on each side of the row of disks of the first disk. m2. In the stacked rotor, a stacking bolt is inserted into a bolt hole including a pillar hole and a drilled hole of a disc assembly formed by arranging third discs, and the stacking bolt is tightened with a nut fitted to the bolt hole to connect the disc assembly. A stacked rotor for @fluid pressure #i machine, characterized in that the portion of the stacking bolt that is pushed through the pre-drilled hole is formed into a rectangular cross section with one side cut away. 2. The section of the one-way stacking bolt is approximately rectangular, and the vfJT plane is formed to be 0.6, where d is the diameter of the circular section. A stacked rotor of a cap style regular knitting machine according to Claims No. IJA, characterized in that: