KR101988465B1

KR101988465B1 - Support device for balance correction

Info

Publication number: KR101988465B1
Application number: KR1020157007285A
Authority: KR
Inventors: 타케시 후지마키; 카주마사 미야하라; 요시오 시모쿠라
Original assignee: 가부시키가이샤 아이에이치아이 로테이팅 머시너리 엔지니어링
Priority date: 2012-08-30
Filing date: 2013-08-29
Publication date: 2019-06-12
Also published as: HK1212019A1; KR20150047566A; EP2891873A4; EP2891873A1; CN104769404A; EP2891873B1; JP2014048091A; WO2014034769A1; JP5415601B1; CN104769404B

Abstract

The balance correcting wager according to the present invention is characterized in that among the outer circumferential surface of the mandrel 11 to which the support hole 22 of the magnet body 1 having the section 26 formed in a polygonal cross- A discharge hole 38 for discharging a pressure varying in the space between the cross-sectional portion of the polygon and the outer circumferential surface of the mandrel in accordance with the rotation of the entire fabric is provided at a position facing the cross-sectional shape portion 26a of the mandrel.

Description

{SUPPORT DEVICE FOR BALANCE CORRECTION}

In order to perform a balance correction of a rotating assembly rotating at high speed such as a rotor of a turbocompressor, the present invention is applied to a rotating member of a turbo compressor by rotating a whole of the rotating assembly by using a vertical mandrel equipped with a static- The present invention relates to a balance device for correcting a balance to be able to support a material freely.

In order to solve the unbalance (dynamic unbalance) caused by the component tolerance at the time of manufacture, the unbalance amount is measured using a normal balance correcting device in the rotor of the turbo compressor rotating at high speed The unbalance is corrected.

In a balance correcting device, a mandrel equipped with a static pressure gas bearing is used so that a measurement of an unbalance amount is performed with high accuracy. Device) is used. Most of the mandrel is a cylindrical mandrel member in which a circular support hole in the rotation center portion of the rotor is tightly fitted as shown in Fig. 5 of Patent Document 1, A radial bearing (formed by a radial bearing surface with an ejection hole) is provided on the outer circumferential surface of the member, and a hydrostatic gas thrust bearing (having an ejection hole on the proximal side of the mandrel member) Thrust bearing surface) is provided.

With this structure, when the support hole of the rotor is inserted into the mandrel, the entire rotor is mounted on the mandrel. Thereafter, a compressive fluid (air; for a static-pressure gas bearing) is ejected from the ejection hole of the static-pressure gas radial bearing to the inner surface of the support hole, (Air; for a static-pressure gas bearing), the rotor rotates around the mandrel while being levitated.

The measurement of the unbalance amount (dynamic unbalance amount) is carried out by applying a rotational force from the outside to the rotor in the floating state, for example, by jetting the driving air (driving fluid) toward the rotor surface to rotate the rotor at a high speed, And measuring the behavior of the rotating rotor by various sensors provided in the correction device.

Japanese Patent Application Laid-Open No. 2005-172538 (Fig. 5)

Normally, as the support hole of the rotor, a hole having a circular cross-sectional shape, that is, a circular cross-sectional shape as a whole, is used, as disclosed in Citation 1. This is intended to connect the shaft to the rotor by fastening bolts by inserting the end of the shaft mated with the rotor into the supporting hole.

However, in the field of various systems in which a turbo compressor is used for the rotor of the turbocompressor, many demands are being made such as connecting the shaft to the shaft strongly and matching the shaft center of the rotor with the axis of the shaft with high precision.

In recent years, in order to meet this demand, a rotor type rotor has been proposed in which not only a circular cross-section but also a multi-rotor type rotor is combined with a shaft by connecting the rotor and shaft. In order to realize this connection method, it has been studied to form an internal cavity portion of a polygonal cross-sectional shape which engages with a polygonal portion formed on the shaft, on the end side of the support hole of the rotor .

However, if the support hole having the lapped portion of the polygonal shape is adopted, there is a fear that the unbalance amount of the rotor can not be measured satisfactorily.

That is, when measuring the unbalance amount of the rotor, the compressible fluid ejected from the ejection hole of the static-pressure gas bearing is filled between the outer peripheral surface of the mandrel, which is a portion supporting the rotor with the regulator body, and the inner surface of the support hole.

At this time, if the support hole has the same circular section (full circle) as the outer circumferential shape of the mandrel, the pressure fluctuation does not occur even if the rotor rotates, and thus high measurement precision is ensured. However, if the supporting hole has a polygonal lumen, a squeeze occurs between the portion of the polygonal shape and the outer peripheral surface of the mandrel due to the rotation (displacement) of the rotor, unlike the case of the circular section (full circle). Due to the squeeze effect at this time, the pressure rise and fall are repeated within the copper.

This pressure fluctuation causes a hunting vibration in the mandrel rotor. Therefore, the accuracy of measuring the unbalance amount of the rotor tends to be impaired. In addition, there is a problem that the rotor is likely to come into contact with the mandrel, and measurement of the unbalance amount at a desired period may not be performed satisfactorily.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a balance device for balance correction capable of measuring the unbalance amount of the entire workpiece with a part of the support hole being formed into a polygonal shape with high precision.

According to the present invention, in the outer peripheral surface of a vertically oriented mandrel in which the support hole of the entire workpiece having a portion formed by a polygonal cross-sectional shape is mounted on the end side, A vent hole for externally discharging a pressure varying in a space between the cross-sectional shape of the polygon and the outer peripheral surface of the mandrel is provided (claim 1).

With this configuration, even when a part of the support hole has a polygonal sectional shape, when measuring the unbalance amount (dynamic unbalance amount), the fluctuation of the pressure occurring in the space between the end surface of the polygon of the support hole and the outer peripheral surface of the mandrel Is discharged to the outside through the discharge hole. Therefore, the pressure fluctuation between the end face of the polygonal shape of the support hole and the outer peripheral face of the mandrel due to the squeeze is suppressed, and the unbalance amount of the entire workpiece is measured with high accuracy.

Preferably, in addition to the above-mentioned objects, the discharge holes are provided at equal intervals in the main direction (circumferential direction) on the outer peripheral surface of the mandrel so as to uniformly discharge the fluctuating pressure (claim 2).

Preferably, in addition to the above-mentioned object, the discharge hole has an inlet near the lowermost portion of the space between the cross-sectional shape of the polygon in the mandrel and the outer peripheral surface of the mandrel so as to facilitate output of the fluctuating pressure, And a passage formed by the shortest path is used (claim 3).

According to the present invention, when measuring the unbalance amount of the entire fabric, variations in the pressure occurring in the space between the end face of the polygon of the support hole and the outer peripheral surface of the mandrel are released to the outside through the discharge hole. Thereby, the pressure fluctuation can be suppressed in the space between the end face of the polygonal shape of the support hole and the outer peripheral face of the mandrel, which is caused by the squeeze.

As a result, it is possible to measure the unbalance amount with high accuracy in the entire workpiece having a part of the support hole in a polygonal shape. In addition, it is possible to avoid the concern that the entire mandrel is brought into contact with the mandrel. In addition, a simple structure is solved (claim 1).

In addition to the above effect, the changed pressure can be uniformly discharged from the space between the cross-sectional portion of the polygonal shape and the outer peripheral surface of the mandrel through the plurality of discharge holes, and the effect is further enhanced (Claim 2).

In addition to the above effect, since the discharge hole is further formed in the shortest path, the pressure can be further exerted to the outside, resulting in a further higher effect (claim 3).

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a perspective view showing a balance correcting device according to an embodiment of the present invention, together with a balance correcting device to which the apparatus is applied. Fig.
Fig. 2 is a cross-sectional view showing the structure of each part of the balance correcting wager; Fig. 2 is a view showing a state in which a rotor (entire assembly) is mounted on a mandrel;
3 is a cross-sectional view taken along line AA in Fig.
4 is a sectional view taken along line BB in Fig.
5 is a cross-sectional view for explaining an in-space behavior between a cross section of a polygon of the support hole and an outer peripheral surface of the mandrel when the rotor rotates;
6 is a perspective view for explaining a rotor (entire assembly) of a turbo compressor for measuring an unbalance amount;
7 is a perspective view illustrating a connection structure using a polygonal portion of the rotor.

Hereinafter, the present invention will be described based on one embodiment shown in Figs. 1 to 7. Fig.

Fig. 1 shows a schematic configuration of a balance correcting device for measuring the unbalance amount (dynamic unbalance amount) of the entire rotor, for example, the rotor 1 of the turbocompressor (here, for example, a compressor rotor) Reference numeral 2 denotes a substrate of the apparatus, reference numeral 3 denotes a frame member standing upright on the upper surface of the substrate 2, and reference numeral 4 denotes a vibrating bridge member disposed in front of the frame member 3.

Each part of the vibration bridge body 4 includes a plurality of support spring members 5a projecting from the front surface of the frame body 3 and a support spring member 5b projecting from the upper surface of the substrate 2 So that the entire vibrating bridge member 4 is supported so as to be displaceable in the left-right direction. A supporting arm body 6 extends from the front of the vibrating bridge body 4 in a band shape. A tip end portion of the belt-like support arm body 6 is mounted with a take-up unit 10 (corresponding to the balance-correcting take-up unit of the present invention) to hold the rotor 1 of the turbo compressor.

Various sensors 8 for detecting the vibration transmitted to the vibration bridge body 4 are provided on the side of the vibrating bridge body 4 and the rotor 1 is rotated around the waving apparatus 10 And a pair of ejection head portions 9 (rotational force portion) for ejecting compressed air are provided. Reference numeral 8a in FIG. 1 denotes a mounting member for mounting various sensors 8 on the substrate 2, and reference numeral 9a denotes a mounting member for mounting the jetting head 9 on the substrate 2.

A structure in which the rotor 1 (single unit) is rotatably held by a constant-pressure gas bearing is used for the above-mentioned wagering device 10 by using a vertical mandrel 11. The structure of the same 10 is shown in Fig.

Before describing the structure of the wagon 10, the rotor 1 to be a component to be measured will be described. For example, as shown in Fig. 6, the rotor 1 includes a plurality of blades 1a Has a rotor body 20 formed on a disc-shaped base surface portion 20a. The rotor main body 20 includes a cylindrical boss portion 21 formed at the center of the base surface portion 20a. The rotary shaft portion of the rotor main body 20 and the boss portion 21 of the base surface portion 20a have support holes 22 each having a circular cross section and linearly penetrating these portions. A shaft 23 having a circular cross section and mating with the rotor 1 abuts the support hole 22. Concretely, the end of the shaft 23 is inserted into the support hole 22, and the insertion end is fixed by a fixing member such as a nut member (not shown) And a receiving portion 23a for receiving the end of the rotor portion 21, thereby forming a module in which the rotor 1 is engaged, that is, a rotor module.

Here, the shaft 23 and the support hole 22 have a structure in which a part or a polygonal shape is used for connecting the rotor 1 and the shaft 23 (for example, a strong connection, a high precision For alignment, etc.).

In other words, generally, the entire portion from one end of the rotor 1 to the other end is used as the support portion 22 and the shaft 23 having the circular section in the shape of a circle fitting to the support hole 22, As shown in Figs. 6 and 7, for example, the inner surface of the boss 21 serving as a part of the support hole 22, specifically, the base end of the support hole 22, Sectional shape of a large polygon, for example, an inner surface 26a of a triangular shape, and an inner side of the inner surface 26a is a triangular inner-surface portion 26. As shown in Fig. The shaft 23 has, for example, a triangular-shaped flange portion 27 engaged with the inner-strength portion 26 of the triangular shape. That is, the rotor 1 and the shaft 23 are connected by using a structure in which the inner-strength portion 26 and the flange portion 27 of the triangular shape are engaged with each other.

A structure for stably holding the rotor 1 having a part of the support hole 22 in a polygonal shape is used in the wager 10 of Figs. 1 and 2.

Referring to Figs. 1 and 2, the respective components of the wagon 10 will be described. Reference numeral 11 denotes the mandrel described above. The mandrel 11 is constituted by a cylindrical mandrel member. The mandrel member is placed on the upper surface of the distal end portion of the support arm body 6 and the rotor 1 is mounted from above the mandrel 11. [

That is, the mandrel 11 includes, in order from the bottom, an installation seat 30 fixed on the support arm body 6, a disk-shaped portion 31 for accommodating the lower end of the rotor 1 (end of the boss portion 21) And extends from the predetermined amount supporting arm body 6 in the vertical direction. Specifically, the portion (excluding the boss portion 21) where the rotor main body 20 on the tip end side among the columnar portions 32 is disposed is a small diameter portion occupying most of the support holes 22 of the rotor main body 20 And a columnar section 32a having a circular section in section matching the shape of the hole section 22d having a small diameter. The portion where the base end boss portion 21 is disposed is larger in diameter than the column portion 32a in conformity with the shape of the end portion (stepped portion) 22a of the support hole 22 as shown in Fig. As shown in Fig. Particularly, as shown in Fig. 4, the portion corresponding to the inner-strength portion 26 (inner surface 26a) of the triangular shape is smaller than the column portion 32c (smaller in inner surface 26a) than the column portion 32b As shown in Fig. 2, only by inserting the rotor 1 into the mandrel 11 from the end (base end) of the support hole 22, the mandrel 11 is not affected by the presence or absence of the inner- (11).

A constant pressure gas radial bearing surface 34b having a plurality of spray holes 34a is provided on the outer circumferential surface of each of the column portions 32a and 32b of the mandrel 11, Thereby forming a radial bearing 34. On the upper surface of the disk-shaped portion 31, there is provided a static-pressure gas-thrust bearing surface 35b having a large number of spray holes 35a around the shaft center in conformity with the end of the boss portion 21, And forms a static pressure gas thrust bearing 35 for accommodating the end surface of the lower boss portion 21 (around the opening of the support hole 22).

As shown in Fig. 2, the spray hole 34a has a passage 36a of various pore diameters formed along the shaft center of the mandrel 11, a relay passage 36b formed inside the support arm body 6 To the external gas supply device 37 for hydrostatic bearings. The spray hole 35a is connected to the gas supply device 37 for the static pressure bearing through the passage 38a formed in the disk-like portion 31 and the relay passage 38b formed in the support arm body 6. [ The rotor 1 is moved from the static pressure gas bearings 34 and 35 to the ladle 34 by blowing out the compressible fluid supplied from the static pressure bearing gas supply device 37, It is possible to rotate the rotor 1 while being lifted up by a predetermined amount around the mandrel 11 from the thrust direction.

When air is ejected from the pair of ejection head portions 9 to the rotor 1 in the floating state, the rotor 1 is rotated at a high speed, and the behavior (vibration state) 6, and the vibrating bridge member 4, and is detected by various sensors 8, and the unbalance amount of the rotor 1 is measured.

In addition, as shown in Figs. 1, 2 and 4 (section BB in Fig. 2), among the outer circumferential surfaces of the mandrel 11, the inner circumferential portion 26 (Corresponding thereto), a discharge hole 38 is provided on the outer circumferential surface of the column portion 32c. The discharge holes 38 are provided at regular intervals along the main direction of the mandrel 11, in this case, nine.

Either of the discharge holes 38 is opened in the space where the inlet 39a is formed between the column portion 32c and the inner surface 26a and the outlet 39b is opened out of the same space as shown in Fig. And a J-shaped passage 39 having a small diameter. The inlet 39a of the passage 39 is opened to the outer peripheral portion of the column portion 32c which is the lowermost vicinity of the space between the column portion 32c and the inner surface 26a and the outlet 39b is open to the outside of the column portion 32c, For example, near the bearing surface 35b of the end surface of the disk-shaped portion 31, and the passage 39 is formed in the shortest path in the vicinity of the bearing surface 35b . A pressure fluctuation in the space between the inner surface 26a of the triangular shape and the outer circumferential surface of the circular columnar section 32c of the circular cross section, especially the rising pressure, is reduced when the rotor 1 is rotated in the passage 39 formed by this shortest path It is structured to be exported to the outside.

Next, the point that this pressure fluctuation is transmitted will be described.

2, the support hole 22 of the rotor 1 is fitted in a mandrel 11 which stands up in the vertical direction, and the rotor 1 is inserted into the mandrel 11 ). Thus, the hole portion 22d of the rotor 1 is disposed in the circular columnar section 32a (including the stationary-gas radial bearing 34 at the upper stage) of the mandrel 11, The end portion 22a of the rotor 1 is disposed in the bearing portion 32b of the rotor 1 (including the static pressure radial bearing 34 in the lower stage) A steel portion 26 is disposed. The end of the boss portion 21 of the rotor 1 is disposed above the static pressure gas-thrust bearing surface 35b.

Thereafter, the compressed air (compressible fluid) from the gas supply device 37 for the static pressure bearing is ejected by a predetermined amount from each of the ejection holes 34a and 35a. 2, the air ejected from the spray hole 34a flows between the inner surface of the fixed-gas radial bearing surface 34b and the hole portion 22d or the inner surface of the end portion 22a, And rotatably supports the rotor 1 around the mandrel 11 with an air flow flowing between the coils. At the same time, as shown by arrows in FIG. 2, the air ejected from the spray hole 35a flows between the static pressure thrust bearing surface 35b and the end surface of the boss 21 while pushing up the boss 21, The entire rotor 1 is floated by a predetermined amount. That is, the rotor 1 is lifted by a predetermined amount by the mandrel 11 and is wound around the rotor.

Thereafter, when air is blown from the ejection holes 9b (only a part of which is shown in FIG. 1) of the pair of ejection head portions 9 to the blade 1a of the floating rotor 1, the rotor 1 Thereby rotating around the mandrel 11 at a high speed. At this time, the behavior (vibration state) of the rotor 1 is transmitted to the various sensors 8 via the support arm body 6 and the vibration bridge body 4, The unbalance amount is measured.

At this time, the space (the inner circumferential portion 26) between the inner surface 26a of the triangular shape of the rotor 1 and the column portion 32c of the mandrel 11 is formed by the spouting holes (not shown) of the hydrostatic bearings 34, 34a, and 35a, respectively.

Here, since the rotor so far is paired with the mandrel, it is not a problem, but the end of the support hole 22 of the rotor 1 is polygonal, Squeeze occurs between the boss portion 21 having the triangular inner wall portion 26 and the columnar portion 32c having the circular section. Therefore, in the space between the inner surface 26a of the triangular shape and the columnar portion 32c of the circular circular section, the pressure rises at the front side in the rotational direction of the triangular inner surface 26a displaced as shown in Fig. 5 , The pressure rise and fall due to the squeeze effect in which the pressure is lowered in the rotational direction rear side (rear side) are repeated in the space.

Hunting vibration occurs in the rotor 1 due to this pressure fluctuation. The accuracy of the measurement of the unbalance amount of the rotor 1 is impaired due to the influence of the hunting vibration. However, since the mandrel 11 is provided with the discharge hole 38 for discharging the varying pressure in the space between the inner surface 26a of the triangular shape and the columnar portion 32c of the circular section in the section, The pressure fluctuation, i.e., the rising pressure, which is generated in the same space as shown by an arrow in FIG. The descending pressure is supplemented by the air of the hydrostatic gas bearings 34, 35.

This suppresses the pressure fluctuation between the end face of the polygonal shape of the support hole 22 (the inner peripheral portion 26 of the triangular shape) and the outer peripheral surface of the mandrel 11 which is circular in cross section.

Therefore, it is possible to perform the measurement of the unbalance amount of the rotor 1 (the entire assembled body) with high accuracy. In addition, since the measurement accuracy is improved only by forming the discharge hole 38 at a position where the end face of the polygon of the support hole 22 comes into contact with the outer peripheral face of the mandrel 11, a simple structure is solved. Moreover, it is possible to avoid the concern and worry that the rotor 1 is brought into contact with the mandrel 11.

In particular, since the discharge holes 38 are arranged at equal intervals at equal intervals along the main direction of the mandrel 11, the fluctuating pressure can be uniformly discharged to the outside, and the pressure fluctuation can be suppressed more effectively.

In addition, if the discharge hole 38 is formed in the shortest path, the fluctuating pressure can be easily exported to the outside, so that the pressure fluctuation can be suppressed more effectively.

The present invention is not limited to the above-described embodiment, and various changes may be made without departing from the gist of the present invention. For example, in the above-described embodiment, the polygonal portion of the support hole is a triangular lumen portion, but the present invention is not limited to this, but another polygonal lumen portion may be used. In the embodiment described above, nine ejection holes are provided. However, the present invention is not limited to this, and it is sufficient that the effect of suppressing the pressure fluctuation can be sufficiently secured even if nine or more ejection holes are provided. no. Of course, in the above-described embodiment, the rotor of the turbocompressor is used. However, the present invention is not limited to this, and the present invention can be applied to any assembly requiring measurement of the unbalance amount.

1: Rotor (full assembly)
10: Standby device (balance device for balance adjustment)
11: Mandrel
22: Support hole
26: inner-strength portion of the triangular shape (portion of the cross-sectional shape of the polygon)
26a: inner surface of triangle (inner surface of polygon)
34: Constant-pressure gas radial bearing
35: Static thrust bearings
38: vent hole
39a: entrance
39b: exit

Claims

(1) having a support hole having a circular section in the center of rotation and having a polygonal cross-section at the end of the support hole, Shaped mandrel to be mounted on the base member,
Wherein the mandrel has a constant-pressure gas radial bearing for rotatably accommodating an inner surface of a circular section of the support hole on the outer circumferential surface thereof, and on the proximal end side, A thrust bearing for receiving a static pressure gas thrust bearing for receiving a static pressure gas bearing thrust bearing from said static gas radial bearing and said static thrust bearing for discharging a pressurized fluid for said static gas bearing from said static gas radial bearing, And is capable of measuring an unbalance amount by applying a rotational force to the entire fabricated state in a floating state,
Wherein a pressure fluctuating in a space between the cross-sectional portion of the polygon and the outer peripheral surface of the mandrel according to the rotation of the entire machined portion is formed in the outer peripheral surface portion of the outer peripheral surface of the mandrel, And a discharging hole is provided for discharging the toner.

The method according to claim 1,
Wherein the discharge hole is provided at a plurality of equally spaced intervals along the main direction (circumferential direction) on the outer circumferential surface of the mandrel.

3. The method according to claim 1 or 2,
Wherein the discharge hole has an inlet at a lowermost position in a space between a section of the polygon and an outer peripheral surface of the mandrel and has an outlet at a point outside the vicinity of the static pressure gas thrust bearing surface Wherein the through hole is a through hole.