EP2891873B1 - Support device for balance correction - Google Patents
Support device for balance correction Download PDFInfo
- Publication number
- EP2891873B1 EP2891873B1 EP13833183.0A EP13833183A EP2891873B1 EP 2891873 B1 EP2891873 B1 EP 2891873B1 EP 13833183 A EP13833183 A EP 13833183A EP 2891873 B1 EP2891873 B1 EP 2891873B1
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- EP
- European Patent Office
- Prior art keywords
- mandrel
- rotor
- outer peripheral
- support
- aerostatic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 230000002093 peripheral effect Effects 0.000 claims description 22
- 239000012530 fluid Substances 0.000 claims description 7
- 238000003780 insertion Methods 0.000 claims description 2
- 230000037431 insertion Effects 0.000 claims description 2
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 7
- 230000003068 static effect Effects 0.000 description 4
- 238000005259 measurement Methods 0.000 description 3
- 230000013011 mating Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/027—Arrangements for balancing
Definitions
- the present invention relates to a support apparatus for balance correction for rotatably supporting a rotating body using a vertical mandrel having an aerostatic bearing in order to correct the balance of the rotating body rotating at high speeds such as a turbocompressor rotor.
- a support apparatus for balance correction
- a support apparatus for rotatably supporting the rotor alone using a mandrel having an aerostatic bearing.
- most of the support apparatuses have a structure such that as the mandrel, there is used a cylindrical mandrel member which is fitted into a support hole with a circular cross section located at a rotation axis portion of the rotor, aerostatic radial bearings (each having radial bearing surface including a jet hole) are provided on an outer peripheral surface of the mandrel member, and aerostatic thrust bearings (each having a thrust bearing surface including a jet hole) are provided on the base end side of the mandrel member.
- the structure When the mandrel is fitted into the support hole of the rotor, the structure allows the entire rotor to be mounted on the mandrel. Then, compressible fluid (air for aerostatic bearings) is jetted onto internal surfaces of the support hole through the jet holes of the aerostatic radial bearings, and compressible fluid (air for aerostatic bearings) is jetted onto the periphery of the opening (end surface of the rotor) at the lower end of the support hole through the jet holes of the aerostatic thrust bearings, whereby the rotor is rotatably supported around the mandrel in a floating state.
- compressible fluid air for aerostatic bearings
- the amount of imbalance is measured by applying rotational force to the rotor in the floating state from outside, such as by jetting air for drive (drive fluid) onto the rotor surface, to rotate the rotor at high speeds, and then using various sensors provided in the balance correction apparatus to measure the behavior of the rotating rotor.
- Patent Document 1 Japanese Patent Laid-Open No. 2005-172538 ( Figure 5 )
- the support hole of the rotor is generally a hole having a cylindrical shape with a circular cross section, that is, a circular cross section in an entire axial direction. The reason for this is to fittingly insert the end of the shaft mating with the rotor into the support hole and to couple the shaft with the rotor by bolts or the like.
- compressible fluid jetted through the jet holes of the aerostatic bearings generally fills between an outer peripheral surface of the mandrel and an inner surface of the support hole serving as a portion supporting the rotor by aerostatic gas.
- the support hole has the same shape with a circular (perfect circular) cross section as the outer peripheral shape of the mandrel, a rotation of the rotor causes no pressure variation, thereby ensuring high measurement accuracy.
- the support hole has a polygon-shaped inner hollow portion, squeeze occurs between the polygon-shaped portion and the outer peripheral surface of the mandrel according to the rotation (displacement) of the rotor unlike the case where the support hole has the circular (perfect circular) cross section. The squeeze effect at this time causes pressure to repeatedly increase and decrease between the same.
- the rotor supported by the mandrel generates hunting vibration due to this pressure variation. This vibration tends to impair the accuracy of measuring the amount of imbalance of the rotor. This vibration also poses a problem in that the rotor is likely to contact the mandrel, which may prevent satisfactory measurement of the amount of imbalance as desired.
- an object of the present invention is to provide a support apparatus for balance correction capable of measuring the amount of imbalance of a rotating body having a support hole including a polygonal shaped portion with a high accuracy.
- the present invention provides a support apparatus for balance correction as defined in the claims
- the variation in pressure occurring in a space between the polygon-shaped cross-section portion of the support hole and the outer peripheral surface of the mandrel is relieved outside through the vent holes.
- This configuration can suppress the pressure variation in a space between the polygonal shape cross-section portion of the support hole and the outer peripheral surface of the mandrel due to squeeze.
- the present invention can measure the amount of imbalance of the rotating body having a support hole, part of which is formed in a polygonal shape, with a high accuracy.
- the present invention can avoid a risk that the rotating body may contact the mandrel. Further, the present invention requires only a simple structure.
- the present invention can evenly relieve the varied pressure from within a space between the polygonal shape cross-section portion and the outer peripheral surface of the mandrel through a large number of vent holes, thereby further exerting much higher effects.
- the present invention form the vent holes on the shortest route, which makes it much easier to relieve pressure outside, thereby further exerting much higher effects.
- FIGS. 1 to 7 an embodiment illustrated in FIGS. 1 to 7 .
- FIG. 1 illustrates a schematic configuration of a balance correction apparatus for measuring the amount of imbalance (amount of dynamic imbalance) of a rotating body such as a turbocompressor rotor 1 (e.g., compressor rotor), in which reference numeral 2 denotes a base plate of the apparatus, reference numeral 3 denotes a frame body standingly disposed on an upper surface of the base plate 2, and reference numeral 4 denotes a vibration bridge body disposed in front of the frame body 3.
- a turbocompressor rotor 1 e.g., compressor rotor
- Each portion of the vibration bridge body 4 is coupled with a plurality of support spring members 5a protruding from the front surface of the frame body 3 and support spring members 5b (only some of them being illustrated) protruding from the upper surface of the base plate 2 so as to displaceably support the entire vibration bridge body 4 leftward and rightward.
- a support arm body 6 extends in a band shape from a front portion of the vibration bridge body 4.
- a support apparatus 10 (corresponding to the support apparatus for balance correction of the present application) for supporting the turbocompressor rotor 1 is mounted on a front end portion of the band-shaped support arm body 6.
- reference numeral 8a denotes a mounting member for mounting the various sensors 8 on the base plate 2
- reference numeral 9a denotes a mounting member for mounting the jet head portion 9 on the base plate 2.
- the above support apparatus 10 uses a structure using the vertical mandrel 11 for rotatably supporting the rotor 1 (single body) by aerostatic bearings.
- the structure of the support apparatus 10 is illustrated in FIG. 2 .
- the rotor 1 serving as a component to be measured.
- the rotor 1 includes a rotor body 20 in which a large number of blades 1a are formed on a disc-shaped base surface portion 20a.
- the rotor body 20 includes a cylindrical boss portion 21 formed at a center portion of the base surface portion 20a.
- the rotation axis portion of the rotor body 20 and the boss portion 21 of the base surface portion 20a include a support hole 22 having a circular cross section and penetrating the portions in a straight line.
- the support hole 22 includes therein a shaft 23 having a circular cross section and mating with the rotor 1.
- an end portion 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 illustrated), whereby the rotor 1 is tightened between a receiving portion 23a receiving the end of the boss portion 21, thereby forming a module incorporating the rotor 1, that is, a rotor module.
- a fixing member such as a nut member (not illustrated)
- a structure having a polygonal shaped portion constituting part of the shaft 23 and support hole 22 is used (for example, for strong coupling, high precision axis alignment, and other purposes).
- the support hole 22 including an inner hollow portion having a circular cross section and covering the entire rotor 1 from one end to the other end thereof, and the shaft 23 having a circular cross section and corresponding to the support hole 22 are used.
- an end constituting part of the support hole 22 specifically, an inner surface of the boss portion 21 serving as the base end of the support hole 22 includes therein a triangular inner surface 26a as a polygon-shaped cross-section portion larger than the other inner hollow with a circular cross section, and the inside of the inner surface 26a is used as the triangular inner hollow portion 26.
- the shaft 23 includes a triangular flange portion 27 fitted into the triangular inner hollow portion 26. In other words, the rotor 1 and the shaft 23 are coupled with each other using a structure of fitting the triangular inner hollow portion 26 and the flange portion 27 to each other.
- the support apparatus 10 illustrated in FIGS. 1 and 2 includes a structure for stably supporting the rotor 1 using the support hole 22, part of which is formed in a polygonal shape.
- Reference numeral 11 denotes the aforementioned mandrel.
- the mandrel 11 includes a cylindrical mandrel member.
- the mandrel member is standingly disposed on an upper surface of a front end portion of the support arm body 6 so that the rotor 1 is mounted thereon from above the mandrel 11.
- the mandrel 11 includes a mounting seat 30 fixed on the support arm body 6, a disk-shaped portion 31 receiving the lower end of the rotor 1 (end of the boss portion 21), and a cylindrical portion 32 insertable into the rotor 1, in the order starting from the lower end thereof, and the mandrel 11 extends by a predetermined amount in the vertical direction from the support arm body 6.
- a portion on which the rotor body 20 on the front end side is mounted includes a pillar portion 32a with a circular cross section corresponding to the shape of a small diameter hole portion 22d occupying most of the support hole 22 of the rotor body 20. As illustrated in FIG.
- the portion on which the boss portion 21 on the base end side is mounted includes a pillar portion 32b having a diameter larger than that of the pillar portion 32a so as to fit the shape of a stepped portion 22a of the support hole 22.
- the portion corresponding to a triangular inner hollow portion 26 includes a pillar portion 32c (having a diameter smaller than that of the inner surface 26a) having a diameter smaller than that of the pillar portion 32b.
- the rotor 1 can be mounted around the mandrel 11 simply by inserting the mandrel 11 into the rotor 1 from an end (base end) of the support hole 22 without being affected by the presence or absence of the triangular inner hollow portion 26.
- an outer peripheral surface of the pillar portions 32a and 32b of the mandrel 11 includes aerostatic radial bearing surfaces 34b each having a large number of jet holes 34a to form an aerostatic radial bearing 34 receiving the inner surface of the support hole 22.
- the upper surface of the disk-shaped portion 31 includes an aerostatic thrust bearing surface 35b having a large number of jet holes 35a around the axis corresponding to the position of the end of the boss portion 21 to form therein an aerostatic thrust bearing 35 receiving the end surface (periphery of the opening of the support hole 22) of the boss portion 21 serving as the lower end of the rotor 1.
- the jet hole 34a is connected to an outside static pressure bearing gas supply device 37 through a path 36a having various hole diameters and formed along an axial portion of the mandrel 11 and a relay path 36b formed inside the support arm body 6.
- the jet hole 35a is connected to the aforementioned static pressure bearing gas supply device 37 through a path 38a formed in the disk-shaped portion 31 and a relay path 38b formed inside the support arm body 6.
- the outer peripheral surface of the pillar portion 32c facing the triangular inner hollow portion 26 (corresponding to the polygon-shaped cross-section portion of the present application) of the rotor 1 includes a vent hole 38.
- the vent hole 38 comprises a large number of vent holes, that is, here 9 vent holes, which are provided at equal intervals along a circumferential direction of the mandrel 11.
- any of the vent holes 38 includes a small diameter J-shaped path 39 in which an inlet 39a is opened in a space formed between the pillar portion 32c and the inner surface 26a, and an outlet 39b is opened outside the space.
- the inlet 39a of the path 39 is opened in an outer peripheral surface portion of the pillar portion 32c located near the lowest position in the space between the pillar portion 32c and the inner surface 26a; and the outlet 39b is opened at a position near and facing outside the aerostatic thrust bearing surface 35b, for example, at a position closer to the bearing surface 35b of the end surface of the disk-shaped portion 31 to form the path 39 by the shortest route.
- the path 39 formed by the shortest route provides a structure in which when the rotor 1 is rotated, a pressure variation occurring in a space between the triangular inner surface 26a and the outer peripheral surface of the pillar portion 32c with a circular cross section, particularly a rising pressure, is relieved outside.
- the mandrel 11 standing up in the vertical direction is fitted into the support hole 22 of the rotor 1 thereby to mount the rotor 1 on the mandrel 11.
- the hole portion 22d of the rotor 1 is disposed on the pillar portion 32a with a circular cross section of the mandrel 11 (including an upper aerostatic radial bearing 34)
- the stepped portion 22a of the rotor 1 is disposed on the pillar portion 32b (including a lower aerostatic radial bearing 34)
- the triangular inner hollow portion 26 of the rotor 1 is disposed on the pillar portion 32c.
- the end of the boss portion 21 of the rotor 1 is disposed on the aerostatic thrust bearing surface 35b.
- compressed air (compressible fluid) from the static pressure bearing gas supply device 37 is jetted by a predetermined amount through each of the jet holes 34a and 35a.
- air jetted through the jet hole 34a flows in between the aerostatic radial bearing surface 34b and the inner surface of the hole portion 22d and the inner surface of the stepped portion 22a, whereby the air flow flowing in therebetween rotatably supports the rotor 1 around the mandrel 11.
- the space (inner hollow portion 26) between the triangular inner surface 26a of the rotor 1 and the pillar portion 32c of the mandrel 11 is filled with air jetted through the jet holes 34a and 35a of the aerostatic bearings 34 and 35.
- the above described rotor causes no problem because the rotor is mounted on the mandrel with the same circular shape as each other, but the rotor 1 is specified such that the end of the support hole 22 has a polygon shape, specifically, a triangular shape. Therefore, as the rotor 1 is rotated, squeeze occurs between the boss portion 21 having the triangular inner hollow portion 26 and the pillar portion 32c with a circular cross section. For this reason, an increase and a decrease in pressure due to squeeze effect occurs repeatedly in the space between the triangular inner surface 26a and the pillar portion 32c with a circular cross section. Specifically, as illustrated in FIG. 5 , pressure is increased on the front side in the direction of the rotation of the varying triangular inner surface 26a, and pressure is decreased on the rear side in the direction of the rotation thereof.
- the rotor 1 generates hunting vibration due to the pressure variation. If left in this state, the rotor 1 is affected by the hunting vibration, which impairs the accuracy of measuring the amount of imbalance of the rotor 1.
- the mandrel 11 includes the vent hole 38 for relieving the pressure varying in the space between the triangular inner surface 26a and the pillar portion 32c with a circular cross section outside. Therefore, as illustrated by the arrows in FIGS. 2 and 5 , the pressure variation occurring in the space, that is, the rising pressure, is relieved out of the space (outside) through the vent hole 38. The falling pressure is compensated by the air of the aerostatic bearings 34 and 35.
- the amount of imbalance of the rotor 1 (rotating body) can be measured with a high accuracy.
- the measurement accuracy can be improved simply by forming the vent hole 38 at a position of the outer peripheral surface of the mandrel 11 facing the polygon-shaped cross-section portion of the support hole 22, which requires only a simple structure. Further, this structure can avoid a risk, and concern, that the rotor 1 may contact the mandrel 11.
- vent holes 38 are provided at equal intervals along a circumferential direction of the mandrel 11, which can evenly relieve the varied pressure outside, thereby further effectively can suppress the pressure variation.
- vent holes 38 are formed on the shortest route, which makes it easy to relieve the varied pressure outside, thereby more effectively suppress the pressure variation.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Testing Of Balance (AREA)
- Manufacture Of Motors, Generators (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
Description
- The present invention relates to a support apparatus for balance correction for rotatably supporting a rotating body using a vertical mandrel having an aerostatic bearing in order to correct the balance of the rotating body rotating at high speeds such as a turbocompressor rotor.
- It is known about the turbocompressor rotor rotating at high speeds (corresponding to the rotating body of the present application) that in order to eliminate imbalance (dynamic imbalance) caused by component tolerance at manufacturing, a balance correction apparatus is commonly used to measure the amount of imbalance, and then to correct the imbalance.
- In order to allow the balance correction apparatus to measure the amount of imbalance with a high accuracy, there is used a support apparatus (support apparatus for balance correction) for rotatably supporting the rotor alone using a mandrel having an aerostatic bearing. As disclosed in
Figure 5 ofPatent Document 1, most of the support apparatuses have a structure such that as the mandrel, there is used a cylindrical mandrel member which is fitted into a support hole with a circular cross section located at a rotation axis portion of the rotor, aerostatic radial bearings (each having radial bearing surface including a jet hole) are provided on an outer peripheral surface of the mandrel member, and aerostatic thrust bearings (each having a thrust bearing surface including a jet hole) are provided on the base end side of the mandrel member. - When the mandrel is fitted into the support hole of the rotor, the structure allows the entire rotor to be mounted on the mandrel. Then, compressible fluid (air for aerostatic bearings) is jetted onto internal surfaces of the support hole through the jet holes of the aerostatic radial bearings, and compressible fluid (air for aerostatic bearings) is jetted onto the periphery of the opening (end surface of the rotor) at the lower end of the support hole through the jet holes of the aerostatic thrust bearings, whereby the rotor is rotatably supported around the mandrel in a floating state.
- The amount of imbalance (amount of dynamic imbalance) is measured by applying rotational force to the rotor in the floating state from outside, such as by jetting air for drive (drive fluid) onto the rotor surface, to rotate the rotor at high speeds, and then using various sensors provided in the balance correction apparatus to measure the behavior of the rotating rotor.
- Patent Document 1: Japanese Patent Laid-Open No.
2005-172538 Figure 5 ) - As disclosed in
Patent Document 1, the support hole of the rotor is generally a hole having a cylindrical shape with a circular cross section, that is, a circular cross section in an entire axial direction. The reason for this is to fittingly insert the end of the shaft mating with the rotor into the support hole and to couple the shaft with the rotor by bolts or the like. - By the way, there has been an increasing demand from various system fields using the turbocompressor for the turbocompressor rotor, such as allowing the rotor to be firmly coupled with the shaft, allowing the rotor axis to be aligned with the shaft axis with a high accuracy, and other requests.
- In view of this, in order to meet such demands for the turbocompressor rotor, there has recently been proposed a structure of a coupling system of coupling by fittingly inserting the shaft into the rotor using a polygonal shaped portion, in addition to coupling by a hole with a circular cross section. In order to achieve the coupling system, it is beginning to be considered that an inner hollow portion with a polygon-shaped cross section into which a polygonal shaped portion formed on the shaft is fitted is formed on an end side of the support hole of the rotor.
- However, if a support hole having a polygonal shaped inner hollow portion is employed, the amount of imbalance of the rotor may not be satisfactorily measured.
- Specifically, when the amount of imbalance of the rotor is measured, compressible fluid jetted through the jet holes of the aerostatic bearings generally fills between an outer peripheral surface of the mandrel and an inner surface of the support hole serving as a portion supporting the rotor by aerostatic gas.
- At this time, if the support hole has the same shape with a circular (perfect circular) cross section as the outer peripheral shape of the mandrel, a rotation of the rotor causes no pressure variation, thereby ensuring high measurement accuracy. However, if the support hole has a polygon-shaped inner hollow portion, squeeze occurs between the polygon-shaped portion and the outer peripheral surface of the mandrel according to the rotation (displacement) of the rotor unlike the case where the support hole has the circular (perfect circular) cross section. The squeeze effect at this time causes pressure to repeatedly increase and decrease between the same.
- The rotor supported by the mandrel generates hunting vibration due to this pressure variation. This vibration tends to impair the accuracy of measuring the amount of imbalance of the rotor. This vibration also poses a problem in that the rotor is likely to contact the mandrel, which may prevent satisfactory measurement of the amount of imbalance as desired.
- In view of this, an object of the present invention is to provide a support apparatus for balance correction capable of measuring the amount of imbalance of a rotating body having a support hole including a polygonal shaped portion with a high accuracy.
- The present invention provides a support apparatus for balance correction as defined in the claims
- According to the present invention, when the amount of imbalance of the rotating body is measured, the variation in pressure occurring in a space between the polygon-shaped cross-section portion of the support hole and the outer peripheral surface of the mandrel is relieved outside through the vent holes. This configuration can suppress the pressure variation in a space between the polygonal shape cross-section portion of the support hole and the outer peripheral surface of the mandrel due to squeeze.
- Therefore, the present invention can measure the amount of imbalance of the rotating body having a support hole, part of which is formed in a polygonal shape, with a high accuracy. In addition, the present invention can avoid a risk that the rotating body may contact the mandrel. Further, the present invention requires only a simple structure.
- In addition to the above effect, further the present invention can evenly relieve the varied pressure from within a space between the polygonal shape cross-section portion and the outer peripheral surface of the mandrel through a large number of vent holes, thereby further exerting much higher effects.
- In addition to the above effect, further the present invention form the vent holes on the shortest route, which makes it much easier to relieve pressure outside, thereby further exerting much higher effects.
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FIG. 1 is a perspective view illustrating a support apparatus for balance correction according to an embodiment of the present invention together with a balance correction apparatus to which the same apparatus is applied. -
FIG. 2 is a sectional view illustrating a structure of each portion of the support apparatus for balance correction together with a state in which a rotor (rotating body) is mounted on a mandrel. -
FIG. 3 is a sectional view along line A-A ofFigure 2 . -
FIG. 4 is a sectional view along line B-B ofFigure 2 . -
FIG. 5 is a sectional view for describing a behavior in a space between a polygon-shaped cross-section portion of a support hole and an outer peripheral surface of the mandrel when the rotor is rotated. -
FIG. 6 is a perspective view for describing the rotor (rotating body) of a turbocompressor when the amount of imbalance is measured. -
FIG. 7 is a perspective view for describing a coupling structure using the polygonal shaped portion of the rotor. - Hereinafter, the present invention will be described
-
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FIG. 1 is a perspective view illustrating a support apparatus for balance correction according to an embodiment of the present invention together with a balance correction apparatus to which the same apparatus is applied. -
FIG. 2 is a sectional view illustrating a structure of each portion of the support apparatus for balance correction together with a state in which a rotor (rotating body) is mounted on a mandrel. -
FIG. 3 is a sectional view along line A-A ofFigure 2 . -
FIG. 4 is a sectional view along line B-B ofFigure 2 . -
FIG. 5 is a sectional view for describing a behavior in a space between a polygon-shaped cross-section portion of a support hole and an outer peripheral surface of the mandrel when the rotor is rotated. -
FIG. 6 is a perspective view for describing the rotor (rotating body) of a turbocompressor when the amount of imbalance is measured. -
FIG. 7 is a perspective view for describing a coupling structure using the polygonal shaped portion of the rotor. - Hereinafter, the present invention will be described based on an embodiment illustrated in
FIGS. 1 to 7 . -
FIG. 1 illustrates a schematic configuration of a balance correction apparatus for measuring the amount of imbalance (amount of dynamic imbalance) of a rotating body such as a turbocompressor rotor 1 (e.g., compressor rotor), in whichreference numeral 2 denotes a base plate of the apparatus,reference numeral 3 denotes a frame body standingly disposed on an upper surface of thebase plate 2, andreference numeral 4 denotes a vibration bridge body disposed in front of theframe body 3. - Each portion of the
vibration bridge body 4 is coupled with a plurality ofsupport spring members 5a protruding from the front surface of theframe body 3 and supportspring members 5b (only some of them being illustrated) protruding from the upper surface of thebase plate 2 so as to displaceably support the entirevibration bridge body 4 leftward and rightward. Asupport arm body 6 extends in a band shape from a front portion of thevibration bridge body 4. A support apparatus 10 (corresponding to the support apparatus for balance correction of the present application) for supporting theturbocompressor rotor 1 is mounted on a front end portion of the band-shapedsupport arm body 6. - By the way,
various sensors 8 for detecting vibration transmitted to thevibration bridge body 4 are installed on a side of thevibration bridge body 4, and a pair of jet head portions 9 (rotational force applying portion) for jetting compressed air to rotate therotor 1 are installed around thesupport apparatus 10. InFIG. 1 ,reference numeral 8a denotes a mounting member for mounting thevarious sensors 8 on thebase plate 2, andreference numeral 9a denotes a mounting member for mounting thejet head portion 9 on thebase plate 2. - The
above support apparatus 10 uses a structure using thevertical mandrel 11 for rotatably supporting the rotor 1 (single body) by aerostatic bearings. The structure of thesupport apparatus 10 is illustrated inFIG. 2 . - Here, before describing the structure of the
support apparatus 10, therotor 1 serving as a component to be measured will be described. For example, as illustrated inFIG. 6 , therotor 1 includes arotor body 20 in which a large number of blades 1a are formed on a disc-shapedbase surface portion 20a. Therotor body 20 includes acylindrical boss portion 21 formed at a center portion of thebase surface portion 20a. The rotation axis portion of therotor body 20 and theboss portion 21 of thebase surface portion 20a include asupport hole 22 having a circular cross section and penetrating the portions in a straight line. Thesupport hole 22 includes therein ashaft 23 having a circular cross section and mating with therotor 1. Specifically, an end portion of theshaft 23 is inserted into thesupport hole 22, and the insertion end is fixed by a fixing member such as a nut member (not illustrated), whereby therotor 1 is tightened between a receivingportion 23a receiving the end of theboss portion 21, thereby forming a module incorporating therotor 1, that is, a rotor module. - Here, in order to couple the
rotor 1 with theshaft 23, a structure having a polygonal shaped portion constituting part of theshaft 23 andsupport hole 22 is used (for example, for strong coupling, high precision axis alignment, and other purposes). - Specifically, in general, the
support hole 22 including an inner hollow portion having a circular cross section and covering theentire rotor 1 from one end to the other end thereof, and theshaft 23 having a circular cross section and corresponding to thesupport hole 22 are used. However, here, as illustrated inFIGS. 6 and7 , an end constituting part of thesupport hole 22, specifically, an inner surface of theboss portion 21 serving as the base end of thesupport hole 22 includes therein a triangularinner surface 26a as a polygon-shaped cross-section portion larger than the other inner hollow with a circular cross section, and the inside of theinner surface 26a is used as the triangular innerhollow portion 26. Theshaft 23 includes atriangular flange portion 27 fitted into the triangular innerhollow portion 26. In other words, therotor 1 and theshaft 23 are coupled with each other using a structure of fitting the triangular innerhollow portion 26 and theflange portion 27 to each other. - The
support apparatus 10 illustrated inFIGS. 1 and2 includes a structure for stably supporting therotor 1 using thesupport hole 22, part of which is formed in a polygonal shape. - With reference to
FIGS. 1 and2 , each portion of thesupport apparatus 10 will be described.Reference numeral 11 denotes the aforementioned mandrel. Themandrel 11 includes a cylindrical mandrel member. The mandrel member is standingly disposed on an upper surface of a front end portion of thesupport arm body 6 so that therotor 1 is mounted thereon from above themandrel 11. - Specifically, the
mandrel 11 includes a mountingseat 30 fixed on thesupport arm body 6, a disk-shapedportion 31 receiving the lower end of the rotor 1 (end of the boss portion 21), and acylindrical portion 32 insertable into therotor 1, in the order starting from the lower end thereof, and themandrel 11 extends by a predetermined amount in the vertical direction from thesupport arm body 6. Specifically, of thecylindrical portion 32, a portion on which therotor body 20 on the front end side is mounted (except the boss portion 21) includes apillar portion 32a with a circular cross section corresponding to the shape of a smalldiameter hole portion 22d occupying most of thesupport hole 22 of therotor body 20. As illustrated inFIG. 3 , the portion on which theboss portion 21 on the base end side is mounted includes apillar portion 32b having a diameter larger than that of thepillar portion 32a so as to fit the shape of a steppedportion 22a of thesupport hole 22. In particular, as illustrated inFIG. 4 , the portion corresponding to a triangular inner hollow portion 26 (inner surface 26a) includes apillar portion 32c (having a diameter smaller than that of theinner surface 26a) having a diameter smaller than that of thepillar portion 32b. As illustrated inFIG. 2 , therotor 1 can be mounted around themandrel 11 simply by inserting themandrel 11 into therotor 1 from an end (base end) of thesupport hole 22 without being affected by the presence or absence of the triangular innerhollow portion 26. - In addition, an outer peripheral surface of the
pillar portions mandrel 11 includes aerostatic radial bearing surfaces 34b each having a large number ofjet holes 34a to form an aerostaticradial bearing 34 receiving the inner surface of thesupport hole 22. The upper surface of the disk-shapedportion 31 includes an aerostaticthrust bearing surface 35b having a large number ofjet holes 35a around the axis corresponding to the position of the end of theboss portion 21 to form therein an aerostatic thrust bearing 35 receiving the end surface (periphery of the opening of the support hole 22) of theboss portion 21 serving as the lower end of therotor 1. - As illustrated in
FIG. 2 , of them, thejet hole 34a is connected to an outside static pressure bearinggas supply device 37 through apath 36a having various hole diameters and formed along an axial portion of themandrel 11 and arelay path 36b formed inside thesupport arm body 6. In addition, thejet hole 35a is connected to the aforementioned static pressure bearinggas supply device 37 through apath 38a formed in the disk-shapedportion 31 and arelay path 38b formed inside thesupport arm body 6. Then, when a compressible fluid, such as air, supplied from the static pressure bearinggas supply device 37 is jetted through each of thejet holes aerostatic bearings rotor 1 in radial and thrust directions, whereby theentire rotor 1 can be rotatably supported while being floated by a predetermined amount around themandrel 11. - When air is jetted to the
rotor 1 in the floating state through the pair ofjet head portions 9, therotor 1 is rotated at high speeds. The behavior (vibration condition) at this time is transmitted through thesupport arm body 6 and thevibration bridge body 4, and then is detected by thevarious sensors 8 to measure the amount of imbalance of therotor 1. - Further, as illustrated in
FIGS. 1 ,2 , and4 (sectional view along line B-B ofFigure 2 ), of the outer peripheral surface of themandrel 11, the outer peripheral surface of thepillar portion 32c facing the triangular inner hollow portion 26 (corresponding to the polygon-shaped cross-section portion of the present application) of therotor 1 includes avent hole 38. Thevent hole 38 comprises a large number of vent holes, that is, here 9 vent holes, which are provided at equal intervals along a circumferential direction of themandrel 11. - As illustrated in
FIG. 2 , any of the vent holes 38 includes a small diameter J-shapedpath 39 in which aninlet 39a is opened in a space formed between thepillar portion 32c and theinner surface 26a, and anoutlet 39b is opened outside the space. Specifically, theinlet 39a of thepath 39 is opened in an outer peripheral surface portion of thepillar portion 32c located near the lowest position in the space between thepillar portion 32c and theinner surface 26a; and theoutlet 39b is opened at a position near and facing outside the aerostaticthrust bearing surface 35b, for example, at a position closer to thebearing surface 35b of the end surface of the disk-shapedportion 31 to form thepath 39 by the shortest route. Thepath 39 formed by the shortest route provides a structure in which when therotor 1 is rotated, a pressure variation occurring in a space between the triangularinner surface 26a and the outer peripheral surface of thepillar portion 32c with a circular cross section, particularly a rising pressure, is relieved outside. - Next, the relief of the pressure variation will be described.
- First, as illustrated in
FIG. 2 , when the amount of imbalance of therotor 1 is measured, themandrel 11 standing up in the vertical direction is fitted into thesupport hole 22 of therotor 1 thereby to mount therotor 1 on themandrel 11. As a result, thehole portion 22d of therotor 1 is disposed on thepillar portion 32a with a circular cross section of the mandrel 11 (including an upper aerostatic radial bearing 34), the steppedportion 22a of therotor 1 is disposed on thepillar portion 32b (including a lower aerostatic radial bearing 34), and the triangular innerhollow portion 26 of therotor 1 is disposed on thepillar portion 32c. In addition, the end of theboss portion 21 of therotor 1 is disposed on the aerostaticthrust bearing surface 35b. - Then, compressed air (compressible fluid) from the static pressure bearing
gas supply device 37 is jetted by a predetermined amount through each of thejet holes FIG. 2 , air jetted through thejet hole 34a flows in between the aerostaticradial bearing surface 34b and the inner surface of thehole portion 22d and the inner surface of the steppedportion 22a, whereby the air flow flowing in therebetween rotatably supports therotor 1 around themandrel 11. At the same time, as illustrated by the arrows inFIG. 2 , air jetted through thejet hole 35a pushes theboss portion 21 while flowing in between the aerostaticthrust bearing surface 35b and the end surface of theboss portion 21 thereby to float theentire rotor 1 by a predetermined amount. As a result, themandrel 11 rotatably supports therotor 1 while floating therotor 1 by a predetermined amount. - Then, when air is jetted toward the blades 1a of the floating
rotor 1 through thejet holes 9b (only some of them being illustrated inFIG. 1 ) of the pair ofjet head portions 9, therotor 1 is rotated around themandrel 11 at high speeds. The behavior (vibration condition) of therotor 1 at this time is transmitted to thevarious sensors 8 through thesupport arm body 6 and thevibration bridge body 4, and then is detected by thevarious sensors 8 to measure the amount of imbalance of therotor 1. - At this time, the space (inner hollow portion 26) between the triangular
inner surface 26a of therotor 1 and thepillar portion 32c of themandrel 11 is filled with air jetted through thejet holes aerostatic bearings - Note that the above described rotor causes no problem because the rotor is mounted on the mandrel with the same circular shape as each other, but the
rotor 1 is specified such that the end of thesupport hole 22 has a polygon shape, specifically, a triangular shape. Therefore, as therotor 1 is rotated, squeeze occurs between theboss portion 21 having the triangular innerhollow portion 26 and thepillar portion 32c with a circular cross section. For this reason, an increase and a decrease in pressure due to squeeze effect occurs repeatedly in the space between the triangularinner surface 26a and thepillar portion 32c with a circular cross section. Specifically, as illustrated inFIG. 5 , pressure is increased on the front side in the direction of the rotation of the varying triangularinner surface 26a, and pressure is decreased on the rear side in the direction of the rotation thereof. - The
rotor 1 generates hunting vibration due to the pressure variation. If left in this state, therotor 1 is affected by the hunting vibration, which impairs the accuracy of measuring the amount of imbalance of therotor 1. To avoid this problem, themandrel 11 includes thevent hole 38 for relieving the pressure varying in the space between the triangularinner surface 26a and thepillar portion 32c with a circular cross section outside. Therefore, as illustrated by the arrows inFIGS. 2 and5 , the pressure variation occurring in the space, that is, the rising pressure, is relieved out of the space (outside) through thevent hole 38. The falling pressure is compensated by the air of theaerostatic bearings - This suppresses the pressure variation, as a factor for impairing the accuracy, in the space between the polygonal shaped cross-section portion (triangular inner hollow portion 26) of the
support hole 22 and the outer peripheral surface with a circular cross section of themandrel 11. - Therefore, the amount of imbalance of the rotor 1 (rotating body) can be measured with a high accuracy. In addition, the measurement accuracy can be improved simply by forming the
vent hole 38 at a position of the outer peripheral surface of themandrel 11 facing the polygon-shaped cross-section portion of thesupport hole 22, which requires only a simple structure. Further, this structure can avoid a risk, and concern, that therotor 1 may contact themandrel 11. - In particular, a large number of vent holes 38 are provided at equal intervals along a circumferential direction of the
mandrel 11, which can evenly relieve the varied pressure outside, thereby further effectively can suppress the pressure variation. - In addition, the vent holes 38 are formed on the shortest route, which makes it easy to relieve the varied pressure outside, thereby more effectively suppress the pressure variation.
-
- 1 rotor (rotating body)
- 10 support apparatus (support apparatus for balance correction)
- 11 mandrel
- 22 support hole
- 26 triangular inner hollow portion (polygon-shaped cross-section portion)
- 26a triangular inner surface (polygon-shaped inner surface)
- 34 aerostatic radial bearing
- 35 aerostatic thrust bearing
- 38 vent hole
- 39a inlet
- 39b outlet
Claims (3)
- A support apparatus for balance correction comprising:a rotating body (1) having a support hole (22) with a circular cross section at a rotation center portion, in which an end side of the support hole is formed in a polygon-shaped cross section, and a vertical mandrel (11) on which the rotating body is mounted in a vertical direction by insertion into the support hole, wherein an outer peripheral surface of the mandrel includes an aerostatic radial bearing (34) rotatably receiving an inner surface with a circular cross section of the support hole, a base end side includes an aerostatic thrust bearing (35) rotatably receiving a periphery of an opening at a lower end of the support hole, and a structure is configured such that compressible fluid for aerostatic bearing is jetted from the aerostatic radial bearing and the aerostatic thrust bearing to rotatably support the rotating body while floating the rotating body around the mandrel, to allow the amount of imbalance to be measured by applying a rotational force to the rotating body in a floating state, characterized in thatof the outer peripheral surface of the mandrel, an outer peripheral surface portion facing the polygon-shaped cross-section portion of the support hole includes a vent hole (38) for relieving pressure varying in a space between the polygon-shaped cross-section portion and the outer peripheral surface of the mandrel outside according to rotation of the rotating body.
- The support apparatus for balance correction according to claim 1, characterized in that the vent hole (38) comprises a large number of vent holes provided at equal intervals along a circumferential direction on the outer peripheral surface of the mandrel (11).
- The support apparatus for balance correction according to claim 1 or 2, characterized in that the vent hole (38) is a path, the path having an inlet (39a) near a lowest position in a space between the polygon-shaped cross-section portion of the mandrel (11) and the outer peripheral surface of the mandrel, the path having an outlet (39b) at a position facing outside near the aerostatic thrust bearing surface (35b).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012189633A JP5415601B1 (en) | 2012-08-30 | 2012-08-30 | Balance correction support device |
PCT/JP2013/073118 WO2014034769A1 (en) | 2012-08-30 | 2013-08-29 | Support device for balance correction |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2891873A1 EP2891873A1 (en) | 2015-07-08 |
EP2891873A4 EP2891873A4 (en) | 2016-04-06 |
EP2891873B1 true EP2891873B1 (en) | 2017-07-26 |
Family
ID=50183574
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13833183.0A Active EP2891873B1 (en) | 2012-08-30 | 2013-08-29 | Support device for balance correction |
Country Status (6)
Country | Link |
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EP (1) | EP2891873B1 (en) |
JP (1) | JP5415601B1 (en) |
KR (1) | KR101988465B1 (en) |
CN (1) | CN104769404B (en) |
HK (1) | HK1212019A1 (en) |
WO (1) | WO2014034769A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10054129B2 (en) * | 2014-03-24 | 2018-08-21 | Ihi Rotating Machinery Enginering Co., Ltd. | Support apparatus for balance correction |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018029795A1 (en) * | 2016-08-10 | 2018-02-15 | 国際計測器株式会社 | Dynamic balancing tester |
US12065934B2 (en) * | 2017-06-16 | 2024-08-20 | Trane International Inc. | Aerostatic thrust bearing and method of aerostatically supporting a thrust load in a scroll compressor |
JP7005372B2 (en) * | 2018-02-09 | 2022-02-10 | 三菱電機株式会社 | Rotating electric machine, electric vacuum cleaner, balance test method of rotating electric machine, manufacturing method of rotating electric machine, and manufacturing method of electric vacuum cleaner |
CN117072470A (en) * | 2023-09-07 | 2023-11-17 | 佛山市南海区绿智电机设备有限公司 | Fresh air system centrifugal fan blade with positioning structure and balance correction device |
Family Cites Families (7)
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EP0903465B1 (en) * | 1997-09-19 | 2003-09-03 | ABB Turbo Systems AG | Compressor wheel-shaft connection for high speed turbomachinery |
JP3918809B2 (en) * | 2003-12-10 | 2007-05-23 | 石川島播磨重工業株式会社 | Support device for balance adjustment of rotating body |
JP2005172537A (en) * | 2003-12-10 | 2005-06-30 | Ishikawajima Harima Heavy Ind Co Ltd | Support apparatus for correcting balance of rotational body |
JP2006316951A (en) * | 2005-05-16 | 2006-11-24 | Valeo Thermal Systems Japan Corp | Power transmission of compressor |
JP2009281462A (en) * | 2008-05-21 | 2009-12-03 | Ntn Corp | Aerostatic journal bearing spindle |
JP5660292B2 (en) * | 2010-08-09 | 2015-01-28 | 株式会社Ihi | Balance correction apparatus and method |
CN203443733U (en) * | 2013-08-15 | 2014-02-19 | 甘肃酒钢集团宏兴钢铁股份有限公司 | High-speed wire transmission cabinet cooling fan dynamic balance correcting apparatus |
-
2012
- 2012-08-30 JP JP2012189633A patent/JP5415601B1/en active Active
-
2013
- 2013-08-29 CN CN201380051020.5A patent/CN104769404B/en active Active
- 2013-08-29 WO PCT/JP2013/073118 patent/WO2014034769A1/en active Application Filing
- 2013-08-29 EP EP13833183.0A patent/EP2891873B1/en active Active
- 2013-08-29 KR KR1020157007285A patent/KR101988465B1/en active IP Right Grant
-
2015
- 2015-12-24 HK HK15112671.4A patent/HK1212019A1/en unknown
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10054129B2 (en) * | 2014-03-24 | 2018-08-21 | Ihi Rotating Machinery Enginering Co., Ltd. | Support apparatus for balance correction |
Also Published As
Publication number | Publication date |
---|---|
KR20150047566A (en) | 2015-05-04 |
JP5415601B1 (en) | 2014-02-12 |
CN104769404A (en) | 2015-07-08 |
KR101988465B1 (en) | 2019-06-12 |
HK1212019A1 (en) | 2016-06-03 |
CN104769404B (en) | 2018-02-27 |
WO2014034769A1 (en) | 2014-03-06 |
JP2014048091A (en) | 2014-03-17 |
EP2891873A4 (en) | 2016-04-06 |
EP2891873A1 (en) | 2015-07-08 |
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