JP2573181Y2 - Rotor vibration prevention device - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a method in which a plurality of rotor parts are joined so as to be integrally rotatable and a rotor fastened by fastening bolts suppresses the vibration of the fastening bolts during rotation and the rotor vibrates. The present invention relates to a device for preventing the above.

[0002]

2. Description of the Related Art When a plurality of rotor parts are joined to form a rotor, the rotor parts are joined so as to be integrated in the rotational direction by a carbic coupling or the like such as meshing of gears, and then passed therethrough. A rotor having a double structure is fastened in the axial direction with the fastening bolts described above.

FIG. 4 shows, as an example, a fan 1 of a compressor as a rotor part and impellers 2 and 3 of a turbine as a rotor part, which are arranged side by side in the axial direction and joined, and these are fastened by fastening bolts 4. A rotor which is fastened in the axial direction to form a rotor is shown. In the case of the conventional rotor shown in FIG. 4, the fan 1 and the turbine of the compressor are fastened to a fastening bolt 4 in which a thread 4 a at one end is screwed and fixed to the axial position of the compressor-side bearing 5. Of the compressor side bearing 5 and the fan 1, the fan 1 and the impeller 2, the impeller 2 and 3, the impeller 3 and the turbine. The side bearing portions 6 are sequentially engaged with each other by a Carvic coupling portion 7 and joined. Finally, a shaft end nut 8 is screwed into a screw portion 4b on the other end side of the fastening bolt 4, and a force of several tons is applied. They are tightened and fastened.

[0004] As described above, when a plurality of rotor parts are joined at the carvic coupling portion 7 and the rotor fastened by the fastening bolts 4 is rotated at a high speed, the fastening bolts 4 and the electric fan 1 are rotated as shown in FIG. When the rotation speed of the rotor reaches the vicinity of the natural frequency of the fastening bolt 4, the fastening bolt 4 generates vibration due to a gap between the impeller 2 and the impeller 2. When the fastening bolt 4 vibrates, the rotor vibrates.

For this reason, conventionally, as shown in FIG. 4, a projection 9 is integrally formed at or near the antinode of the vibration mode of the fastening bolt 4, and the projection 9 is brought into contact with the inner surface of the impeller 2. As a result, the fastening bolt 4 is restrained, and the vibration of the fastening bolt 4 is prevented.

[0006]

However, in the conventional system in which the projection 9 is formed at an intermediate position of the fastening bolt 4 to restrain the fastening bolt 4, the fan of the compressor is not considered from the viewpoint of strength. It is better to reduce the inner diameter of the fan 1 in order to reduce the gap between the fan 1 and the fastening bolt 4, but if the inner diameter of the fan 1 is reduced, Hits the projections 9, making it impossible to assemble the rotor. Due to the above, the inner diameter of the electric wheel 1 cannot be reduced, and there remains a problem in strength. The electric wheel 1 as a rotor component outside the fastening bolt 4. And the impellers 2 and 3 have a large elongation due to centrifugal force during rotation of the rotor.
And the fastening bolt 4 is applied with several tons of axial force to fasten the rotor parts, so that the projection 9 is provided or the cooling air is applied to the projection 9. When a groove serving as a passage is provided, there is a problem that stress is concentrated here and the life of the fastening bolt is shortened.

Therefore, according to the present invention, the rotor can be assembled even if the clearance between the rotor component and the fastening bolt is reduced.
Further, it is intended to prevent vibration of the fastening bolt.

[0008]

According to the present invention, in order to solve the above-mentioned problems, a plurality of rotor parts arranged outside a fastening bolt are joined together so as to be integrally formed in a rotational direction, and the above-mentioned fastening is performed. In the rotor formed by fastening the respective rotor parts with the bolts, or in the vicinity of the antinode of the vibration mode which is the intermediate position of the fastening bolts, a rotor part outside of the fastening bolt intermediate position with a plurality of cracked structures is provided. A vibration prevention metal fitting having a small-diameter portion having an outer diameter capable of being press-fitted into a gap between the small-diameter portion and a large-diameter portion having a diameter larger than the small-diameter portion and capable of engaging with a rotor component. Thus, the fastening bolt is restrained to prevent the vibration of the rotor.

[0009] Further, a cooling air passage is provided in the vibration preventing fitting.

[0010]

The vibration preventing bracket is attached to the intermediate position of the fastening bolt to restrain the fastening bolt, so that the vibration of the fastening bolt can be prevented. Since the rotor component that does not engage with the vibration prevention fitting can have a smaller inner diameter and a smaller gap with the fastening bolt, the strength of the rotor component can be increased.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.

FIGS. 1 to 3 show an embodiment of the present invention. Similar to the case shown in FIG. 4, the rotor component of the rotor is a fan 1 of a compressor and an impeller 2 of a turbine. 3
An example is shown in which the present invention is applied to a structure in which are joined in the axial direction and fastened in the axial direction by the fastening bolts 4. That is,
On the outer side of the fastening bolt 4 in which the screw portion 4a at one end is screwed and fixed to the axial center portion of the compressor-side bearing portion 5, the fan 1 of the compressor, the impellers 2 and 3 of the turbine, and the turbine-side bearing. The bolts 4 are fitted in order and joined so as to be integral with each other in the rotation direction at the Carvic coupling portion 7, and the shaft end nut 8 is screwed into the screw portion 4b on the other end side of the fastening bolt 4 to be fastened. In such a configuration, in order to restrain a portion of the vibration mode antinode of the fastening bolt 4 or its vicinity during rotation of the rotor, the vibration-prevention metal fitting 10 having a plurality of cracks (two in the embodiment) is used. 4, the vibration preventing bracket 10 is fixed by the impellers 2 and 3, and the fastening bolt 4 is restrained to prevent vibration.

The anti-vibration bracket 10 includes a fastening bolt 4
A small-diameter portion 10a having an inner diameter substantially equal to the outer diameter of the fastening bolt 4 so that it can be fitted to the outside of the bolt, and having an outer diameter corresponding to the inner diameter of the impeller 2 on the outer peripheral portion; A large-diameter portion 10b which has a large diameter so as to be engaged between the impellers 2 and 3 so as to be engaged and prevented from falling off. And a passage 11 for flowing cooling air is provided in the inner diameter portion over the entire length in the axial direction.
One end is partially cut away to provide a projection 12 so as to form an air passage.

In the case where vibration is prevented by restraining the fastening bolts 4 of the rotor by using the above-mentioned vibration preventing bracket 10, a fan 1 and an impeller 2 as rotor parts are provided outside the fastening bolts 4. Is fitted from the other end side of the fastening bolt 4, and the two are joined by the carbic coupling part 7.
Is fitted and mounted from the lateral direction and moved in the axial direction along the fastening bolt 4 to press the small-diameter portion 10 a into the gap between the impeller 2 and the fastening bolt 4. Next, the impeller 3 is fitted to the outside of the fastening bolt 4 and joined to the impeller 2 by the carvic coupling portion 7, and the large-diameter portion 10 b of the anti-vibration bracket 10 is attached to the inner diameters of the impellers 2 and 3. To pinch it,
By fitting the turbine-side bearing portion 6 and fastening the fastening bolt 4 with the shaft end nut 8 with an axial force of several tons, the impellers 2 and 3 are engaged with the vibration preventing fitting 10 and fixed.

Normally, when the rotation speed of the rotor reaches the vicinity of the natural frequency of the fastening bolt 4, the fastening bolt 4 resonates. In the present invention, the vibration preventing bracket 10 is fastened. Since the vibration of the fastening bolt 4 is restrained, the apparent natural frequency of the fastening bolt 4 acts to increase, and the vibration can be prevented.

In the present invention, a plurality of split-type vibration preventing brackets 10 are attached to the fastening bolts 4 so as to be able to be fitted and detached without providing a projection on the shaft of the fastening bolts 4 as in the conventional system. Therefore, it is not necessary to increase the inner diameter of the fan 1 of the compressor as a rotor part.
The gap between the bolt and the fastening bolt 4 can be reduced, and the strength can be increased.

Although the present invention is not limited to the above embodiment, the rotor part includes the fan 1 of the compressor and the impellers 2 and 3 of the turbine, but other parts may be used as the rotor part. Although the case where the cooling air passage 11 is provided along the inner peripheral surface of the vibration preventing bracket 10 is shown, the cooling air passage 11 may be provided on the outer peripheral portion. In this case, the size of the passage varies depending on the amount of air flowing. Of course, various changes can be made without departing from the scope of the present invention.

[0018]

As described above, according to the rotor vibration preventing apparatus of the present invention, a rotor having a double structure in which a plurality of rotor parts are joined by a carbic coupling and fastened by fastening bolts is used. In order to prevent the rotor from vibrating due to the vibration of the fastening bolt, a plurality of cracking anti-vibration brackets are detachably attached to the fastening bolt,
The fastening bolt is restrained via the vibration preventing fitting by engaging the vibration preventing fitting with the rotor component on the outside thereof, so that the fastening bolt is restrained and does not vibrate during rotation of the rotor. Since the vibration of the rotor can be prevented, and the anti-vibration bracket can be attached to and detached from the fastening bolt, it is possible to omit processing such as projections on the fastening bolt itself, and it is not necessary to increase the inner diameter of other rotor parts. The restriction on the inner diameter shape is reduced, the clearance between the rotor component and the fastening bolt can be reduced, which is advantageous in terms of strength. Further, the processing of the fastening bolt itself such as projections can be omitted, and vibration can be prevented. By providing a passage for cooling air in the bracket, stress is not concentrated on the fastening bolt, and the life of the fastening bolt can be extended,
And the like.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing an embodiment of a rotor vibration prevention device of the present invention.

FIG. 2 is an enlarged view of a portion II in FIG.

FIG. 3 is a view taken in the direction of arrows III-III in FIG. 2;

FIG. 4 is a cross-sectional view illustrating an example of a conventional rotor vibration prevention device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Electric fan (rotor part) 2, 3 Wing wheel (rotor part) 4 Fastening bolt 10 Vibration prevention fitting 10a Small diameter part 10b Large diameter part

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masaru Sakakida 3-1-1-15 Toyosu, Koto-ku, Tokyo Ishikawa Shima-Harima Heavy Industries Co., Ltd. (56) References 5-1-5567 (JP, U) 57- 92001 (JP, U) (58) Field surveyed (Int. Cl. ⁶ , DB name) F04D 29/66 F16F 15/10 F01D 5/04 F01D 5/06

Claims (1)

(57) [Scope of request for utility model registration] A plurality of rotor components arranged outside a fastening bolt are joined together so as to be integral with each other in a rotational direction, and the rotor bolt is fastened to each rotor component by the fastening bolt. At the intermediate position of the bolt, a small-diameter portion having an outer diameter capable of being press-fitted into a gap between the bolt and the rotor component outside the intermediate position of the fastening bolt and having a plurality of cracks, and having a larger diameter than the small-diameter portion, relate to the rotor component. A vibration preventing device for a rotor, comprising a vibration preventing bracket having a large diameter portion adapted to be fitted, and restraining a fastening bolt with the vibration preventing bracket to prevent the rotor from vibrating.