JP2011247837A - Vertical balance measuring apparatus - Google Patents
Vertical balance measuring apparatus Download PDFInfo
- Publication number
- JP2011247837A JP2011247837A JP2010123661A JP2010123661A JP2011247837A JP 2011247837 A JP2011247837 A JP 2011247837A JP 2010123661 A JP2010123661 A JP 2010123661A JP 2010123661 A JP2010123661 A JP 2010123661A JP 2011247837 A JP2011247837 A JP 2011247837A
- Authority
- JP
- Japan
- Prior art keywords
- thrust
- supply hole
- radial
- bearing
- air
- 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.)
- Granted
Links
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Manufacturing Of Electrical Connectors (AREA)
- Testing Of Balance (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- General Physics & Mathematics (AREA)
Abstract
Description
本発明は、縦型バランス計測装置に係り、さらに詳しくはその軸受マウントに関する。 The present invention relates to a vertical balance measuring device, and more particularly to a bearing mount thereof.
図１は、従来の縦型バランス計測装置の模式図である。この図において、１は被検査物である回転軸、２は空気軸受、３は軸受マウント、４はマウント支持バネ、５は原点センサ、６は変位センサ、７は信号処理装置である。
回転軸１は、図で上端に羽根車１ａを有し、その一部に原点マーキングＭが設けられ、これを原点センサ５で検出して羽根車１ａの回転位置（方位）と回転速度を検出する。
FIG. 1 is a schematic diagram of a conventional vertical balance measuring apparatus. In this figure, 1 is a rotating shaft that is an object to be inspected, 2 is an air bearing, 3 is a bearing mount, 4 is a mount support spring, 5 is an origin sensor, 6 is a displacement sensor, and 7 is a signal processing device.
The rotary shaft 1 has an impeller 1a at the upper end in the figure, and an origin marking M is provided on a part thereof, and this is detected by the origin sensor 5 to detect the rotational position (azimuth) and rotational speed of the impeller 1a. To do.
縦型バランス計測装置は、回転軸１の軸心を鉛直に保持して、軸受マウント３に設けられた空気軸受２で回転可能に支持し、さらに軸受マウント３をマウント支持バネ４で支持する構造となっている。回転軸１が回転することで発生する振動は、軸受マウント３を介してマウント支持バネ４に伝わり、これを変位させる。この変位を変位センサ６（ピックアップ）で検出し、信号処理装置７演算することでアンバランの量と方位を求めるようになっている。 The vertical balance measuring device has a structure in which the shaft center of the rotary shaft 1 is held vertically, is rotatably supported by an air bearing 2 provided on the bearing mount 3, and the bearing mount 3 is supported by a mount support spring 4. It has become. The vibration generated by the rotation of the rotating shaft 1 is transmitted to the mount support spring 4 via the bearing mount 3 and is displaced. This displacement is detected by a displacement sensor 6 (pickup), and the signal processor 7 calculates to obtain the amount and direction of the amberlan.
なお、かかる縦型バランス計測装置は、例えば特許文献１に開示されている。 Such a vertical balance measuring apparatus is disclosed in, for example, Patent Document 1.
図２は、本発明が対象とする回転軸１の説明図である。なおこの図は、小型車両用過給機に組み込まれ、他端にコンプレッサインペラ８が取り付けられた状態を示している。 FIG. 2 is an explanatory diagram of the rotating shaft 1 targeted by the present invention. In addition, this figure has shown the state integrated in the supercharger for small vehicles, and the compressor impeller 8 being attached to the other end.
回転軸１は、同軸かつ順に間隔を隔てて配置されている羽根車１ａ、軸シール用のシール円板１ｂ、ラジアル支持用の第１円筒部１ｃ及び第２円筒部１ｄを有する。
羽根車１ａは、例えばタービンインペラであり、回転軸１に一体に形成されている。また、羽根車１ａは、シール円板１ｂより大きい外径の円形端面１ｅをシール円板側に有する。
シール円板１ｂは、羽根車１ａに向かう潤滑油を遠心力で飛散させ、かつ軸受ハウジングとの間で潤滑油の洩れをシールする。
第１円筒部１ｃ及び第２円筒部１ｄは、軸受ハウジングに設けられたラジアル軸受により支持される。
また、回転軸１に作用するスラストは、軸受ハウジングに設けられたスラスト軸受９により支持される。
The rotating shaft 1 has an impeller 1a, a shaft seal seal disc 1b, a radial support first cylindrical portion 1c, and a second cylindrical portion 1d that are coaxially arranged at intervals.
The impeller 1a is a turbine impeller, for example, and is formed integrally with the rotary shaft 1. The impeller 1a has a circular end face 1e having an outer diameter larger than that of the seal disc 1b on the seal disc side.
The seal disc 1b scatters the lubricating oil toward the impeller 1a by centrifugal force and seals the leakage of the lubricating oil between the bearing housing and the seal disc 1b.
The 1st cylindrical part 1c and the 2nd cylindrical part 1d are supported by the radial bearing provided in the bearing housing.
The thrust acting on the rotary shaft 1 is supported by a thrust bearing 9 provided in the bearing housing.
図３は、従来の縦型バランス計測装置における軸受マウント３の構造図である。この図において、軸受マウント３は、図２の回転軸１に対応して、スラスト給気孔３ａ、ラジアル給気孔３ｂ，３ｃ、及び排気孔３ｄ，３ｅを有する。
スラスト給気孔３ａは、シール円板１ｂの下面に加圧空気を供給して上向きのスラスト力を発生させ、シール円板１ｂの下面にスラスト空気軸受を形成する。
ラジアル給気孔３ｂ，３ｃは、ラジアル支持用の第１円筒部１ｃ及び第２円筒部１ｄに加圧空気を供給して半径方向のラジアル力を発生させ、第１円筒部１ｃ及び第２円筒部１ｄとの間にラジアル空気軸受を形成する。
排気孔３ｄ，３ｅは、ラジアル給気孔３ｂ，３ｃから出た加圧空気がシール円板１ｂ側に回り込むのを防ぐために設けられている。
FIG. 3 is a structural diagram of the bearing mount 3 in the conventional vertical balance measuring apparatus. In this figure, the bearing mount 3 has a thrust air supply hole 3a, radial air supply holes 3b, 3c, and exhaust holes 3d, 3e corresponding to the rotary shaft 1 of FIG.
The thrust supply hole 3a supplies pressurized air to the lower surface of the seal disc 1b to generate an upward thrust force, and forms a thrust air bearing on the lower surface of the seal disc 1b.
The radial air supply holes 3b and 3c supply pressurized air to the first cylindrical portion 1c and the second cylindrical portion 1d for radial support to generate a radial radial force, and the first cylindrical portion 1c and the second cylindrical portion. A radial air bearing is formed between 1d and 1d.
The exhaust holes 3d and 3e are provided in order to prevent the pressurized air from the radial air supply holes 3b and 3c from flowing around to the seal disc 1b side.
空気軸受２（ラジアル空気軸受）は給気口から加圧空気を供給し、軸との間に形成された圧力勾配で軸を保持するものである。従って、供給する加圧空気の圧力を高くするほど空気軸受の軸受剛性を高めることができる。
また、図１に示した従来の縦型バランス計測装置では、空気軸受２が剛であればあるほどマウント支持バネ４の変位量が大きくなるため、計測精度が良くなる。
The air bearing 2 (radial air bearing) supplies pressurized air from an air supply port and holds the shaft with a pressure gradient formed between the air bearing 2 and the shaft. Therefore, the bearing rigidity of the air bearing can be increased as the pressure of the supplied pressurized air is increased.
Further, in the conventional vertical balance measuring apparatus shown in FIG. 1, the more rigid the air bearing 2 is, the larger the displacement amount of the mount support spring 4 is, so that the measurement accuracy is improved.
しかし、図４に模式的に示すように、図３に示した軸受マウント３において、シール円板１ｂと第１円筒部１ｃとの直径差が小さく、シール円板１ｂの下面面積が小さいため、シール円板１ｂの下面に発生する圧力Ｐ１が低く、スラスト給気孔３ａからの供給のみでは、回転軸１の自重を支持するためのスラスト空気軸受のスラスト力が不足する問題点があった。 However, as schematically shown in FIG. 4, in the bearing mount 3 shown in FIG. 3, the difference in diameter between the seal disc 1b and the first cylindrical portion 1c is small, and the bottom surface area of the seal disc 1b is small. The pressure P1 generated on the lower surface of the seal disc 1b is low, and the thrust force of the thrust air bearing for supporting the weight of the rotary shaft 1 is insufficient only by the supply from the thrust supply hole 3a.
そのため、従来は、この不足を補うためにラジアル側の圧力Ｐ２を高く設定し、その排気を積極的にスラスト側に回り込ませて、回転軸１を浮上させていた。その結果、ラジアル側の圧力Ｐ２を自由に設定できない問題点があった。 Therefore, conventionally, in order to make up for this shortage, the radial pressure P2 is set high, and the exhaust shaft is actively circulated to the thrust side to float the rotary shaft 1. As a result, there is a problem that the radial pressure P2 cannot be freely set.
また、シール円板１ｂの下面に形成されるスラスト空気軸受は、軸受隙間が微小な状態で剛性を発揮するので、ラジアル側から回り込んだ排気で回転軸１を浮上させると、スラスト空気軸受の剛性が低くなり、自励振動が発生しやすくなる問題点があった。 Further, since the thrust air bearing formed on the lower surface of the seal disc 1b exhibits rigidity when the bearing gap is minute, if the rotary shaft 1 is levitated by the exhaust air that circulates from the radial side, the thrust air bearing There is a problem that the rigidity becomes low and self-excited vibration is likely to occur.
本発明は、上述した問題点を解決するために創案されたものである。すなわち、本発明の目的は、スラスト給気孔から供給する加圧空気で形成されるスラスト空気軸受のスラスト力を高めて、回転軸の自重をスラスト空気軸受のみで支持することができ、かつスラスト空気軸受及びラジアル空気軸受に供給する加圧空気の圧力を独立に制御してそれぞれの剛性を独立に制御することができる縦型バランス計測装置を提供することにある。 The present invention has been developed to solve the above-described problems. That is, the object of the present invention is to increase the thrust force of the thrust air bearing formed by the pressurized air supplied from the thrust air supply hole, so that the weight of the rotating shaft can be supported only by the thrust air bearing, and the thrust air An object of the present invention is to provide a vertical balance measuring apparatus capable of independently controlling the pressure of pressurized air supplied to a bearing and a radial air bearing and independently controlling the rigidity of each.
本発明によれば、羽根車、軸シール用のシール円板、ラジアル支持用の円筒部が同軸かつ順に間隔を隔てて配置されている回転軸をその軸心を鉛直に保持して回転させ、そのアンバランスの量と方位を求める縦型バランス計測装置であって、
前記羽根車はシール円板より大きい外径の円形端面をシール円板側に有しており、
前記回転軸をその軸心を鉛直に保持して支持する軸受マウントを備え、
該軸受マウントは、羽根車の前記円形端面の下面に加圧空気を供給するスラスト給気孔と、
前記ラジアル支持用の円筒部に加圧空気を供給するラジアル給気孔と、
前記スラスト給気孔とラジアル給気孔の間に位置しその間から加圧空気を排気するスラスト側排気孔とを有する、ことを特徴とする縦型バランス計測装置が提供される。
According to the present invention, the impeller, the seal disc for the shaft seal, and the rotating shaft in which the radial support cylindrical portion is arranged coaxially and sequentially spaced apart are rotated while holding the shaft center vertically, A vertical balance measuring device that calculates the amount and direction of the unbalance,
The impeller has a circular end surface with an outer diameter larger than that of the seal disc on the seal disc side,
A bearing mount for supporting the rotating shaft while maintaining its axis vertically;
The bearing mount includes a thrust supply hole for supplying pressurized air to the lower surface of the circular end surface of the impeller;
A radial air supply hole for supplying pressurized air to the radial support cylindrical portion;
There is provided a vertical balance measuring device having a thrust side exhaust hole located between the thrust air supply hole and the radial air supply hole and exhausting pressurized air from the space.
上記本発明の構成によれば、羽根車の円形端面の下面面積が、シール円板より大きいので、円形端面の下面にスラスト給気孔から加圧空気を上向きに供給することで発生する圧力もシール円板より高くなり、面積×圧力で定まるスラスト空気軸受のスラスト力を大幅に高めることができる。
従って、スラスト空気軸受のスラスト力の不足が解消でき、回転軸の自重をスラスト空気軸受のみで支持することができる。
According to the configuration of the present invention, since the lower surface area of the circular end surface of the impeller is larger than the seal disc, the pressure generated by supplying pressurized air upward from the thrust supply hole to the lower surface of the circular end surface is also sealed. The thrust force of the thrust air bearing, which is higher than the disk and determined by area × pressure, can be greatly increased.
Accordingly, the shortage of the thrust force of the thrust air bearing can be solved, and the weight of the rotating shaft can be supported only by the thrust air bearing.
また、スラスト側排気孔が、スラスト給気孔とラジアル給気孔の間に位置し、その間から加圧空気を排気するので、スラスト給気孔とラジアル給気孔の中間位置の圧力が常に外気圧に保たれ、スラスト空気軸受とラジアル空気軸受の空気の相互干渉が無くなり、スラスト空気軸受及びラジアル空気軸受に供給する加圧空気の圧力を独立に制御してそれぞれの剛性を独立に制御することができる。
In addition, the thrust side exhaust hole is located between the thrust air supply hole and the radial air supply hole, and the pressurized air is exhausted between the thrust air supply hole and the radial air supply hole, so that the pressure at the intermediate position between the thrust air supply hole and the radial air supply hole is always maintained at the external pressure. The mutual interference between the air of the thrust air bearing and the radial air bearing is eliminated, and the pressure of the pressurized air supplied to the thrust air bearing and the radial air bearing can be controlled independently to control the rigidity of each independently.
本発明を実施するための実施形態を図面に基づいて説明する。なお、各図において共通する部分には同一の符号を付し、重複した説明を省略する。 An embodiment for carrying out the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.
図５は、本発明の縦型バランス計測装置における軸受マウントの構造図である。
本発明の縦型バランス計測装置は、図２に示した回転軸１を検査対象とする。すなわち、本発明の縦型バランス計測装置が検査対象とする回転軸１は、羽根車１ａ、軸シール用のシール円板１ｂ、ラジアル支持用の円筒部１ｃ，１ｄが同軸かつ順に間隔を隔てて配置されている。
また、羽根車１ａはシール円板１ｂより大きい外径の円形端面１ｅをシール円板側に有している。円形端面１ｅの直径は、円形端面１ｅの軸部を除くドーナツ形状部分に作用する圧力（後述する円形端面１ｅの下面に発生する圧力Ｐ３）により、面積×圧力で定まる上向きのスラスト力が回転軸１の自重より大きくなる大きさであるのがよい。
また、円形端面１ｅは、回転軸１の軸線に直交する平面であるのが好ましいが、軸線に対して対象である限りで、傾斜していてもよい。
なお、この例において、ラジアル支持用の円筒部１ｃ，１ｄは、ラジアル支持用の第１円筒部１ｃと第２円筒部１ｄであるが、円筒部１ｃ，１ｄが一体であってもよい。
FIG. 5 is a structural diagram of a bearing mount in the vertical balance measuring apparatus of the present invention.
The vertical balance measuring apparatus of the present invention uses the rotating shaft 1 shown in FIG. In other words, the rotary shaft 1 to be inspected by the vertical balance measuring apparatus of the present invention has an impeller 1a, a shaft disk seal disc 1b, and radial support cylindrical portions 1c, 1d coaxially and sequentially spaced apart. Has been placed.
The impeller 1a has a circular end face 1e having an outer diameter larger than that of the seal disc 1b on the seal disc side. The diameter of the circular end surface 1e is such that the upward thrust force determined by area × pressure is determined by the pressure acting on the donut-shaped portion excluding the shaft portion of the circular end surface 1e (pressure P3 generated on the lower surface of the circular end surface 1e described later). The size should be larger than the weight of one.
The circular end face 1e is preferably a plane orthogonal to the axis of the rotary shaft 1, but may be inclined as long as it is a target with respect to the axis.
In this example, the radial support cylindrical portions 1c and 1d are the first cylindrical portion 1c and the second cylindrical portion 1d for radial support, but the cylindrical portions 1c and 1d may be integrated.
本発明の縦型バランス計測装置は、回転軸１をその軸心を鉛直に保持して回転させ、そのアンバランスの量と方位を求める縦型バランス計測装置であり、その全体構成は、図１の模式図と同じである。 The vertical balance measuring device of the present invention is a vertical balance measuring device that rotates the rotating shaft 1 while maintaining its axis vertically, and obtains the amount and orientation of the unbalance. The overall configuration is shown in FIG. It is the same as the schematic diagram.
本発明の縦型バランス計測装置は、回転軸１をその軸心を鉛直に保持して支持する軸受マウント１０を備える。この軸受マウント１０は、図１の模式図における軸受マウント３に相当する。
この場合、回転軸１は、羽根車１ａが上になるように、軸受マウント１０の軸線に沿って設けられた中空開口孔に上方から挿入する。
The vertical balance measuring apparatus according to the present invention includes a bearing mount 10 that supports the rotating shaft 1 while maintaining the axis of the rotating shaft 1 vertically. The bearing mount 10 corresponds to the bearing mount 3 in the schematic diagram of FIG.
In this case, the rotary shaft 1 is inserted from above into a hollow opening provided along the axis of the bearing mount 10 so that the impeller 1a is on the top.
図５において、本発明の軸受マウント１０は、全体として軸線に沿って設けられた中空開口孔を有する中空円筒部材であり、その内部にスラスト給気孔１２、ラジアル給気孔１４，１５、スラスト側排気孔１６、及びラジアル側排気孔１８を有する。
スラスト給気孔１２、及びラジアル給気孔１４，１５には、図示しないそれぞれ独立したフレキシブルパイプを介して、空圧源から加圧空気が供給される。また、各給気孔１２，１４，１５に供給する加圧空気の圧力はそれぞれ独立して制御できるようになっている。
In FIG. 5, a bearing mount 10 of the present invention is a hollow cylindrical member having a hollow opening hole provided along the axis as a whole, and a thrust supply hole 12, radial supply holes 14, 15 and thrust side exhaust are provided therein. A hole 16 and a radial exhaust hole 18 are provided.
Pressurized air is supplied to the thrust supply hole 12 and the radial supply holes 14 and 15 from an air pressure source through independent flexible pipes (not shown). Moreover, the pressure of the pressurized air supplied to each air supply hole 12, 14, 15 can be controlled independently.
スラスト給気孔１２は、軸受マウント１０の内部を通り、その上端から鉛直上向きに開口した孔であり、羽根車１ａの円形端面１ｅの下面に加圧空気を供給する。スラスト給気孔１２は、軸受マウント１０の軸線を中心として周方向に均等に複数（例えば、４〜８個）が設けられている。 The thrust air supply hole 12 is a hole that passes through the bearing mount 10 and opens vertically upward from the upper end thereof, and supplies pressurized air to the lower surface of the circular end surface 1e of the impeller 1a. A plurality (for example, 4 to 8) of thrust supply holes 12 are provided equally in the circumferential direction around the axis of the bearing mount 10.
ラジアル給気孔１４，１５は、軸受マウント１０の内部を通り、その内端から半径方向内向きに開口した孔であり、ラジアル支持用の円筒部１ｃ，１ｄに加圧空気を供給する。ラジアル給気孔１４，１５は、軸受マウント１０の軸線を中心として周方向に均等に複数（例えば、４〜８個）が設けられている。 The radial air supply holes 14 and 15 are holes that pass through the inside of the bearing mount 10 and open radially inward from the inner ends thereof, and supply pressurized air to the cylindrical portions 1c and 1d for radial support. A plurality (for example, 4 to 8) of radial air supply holes 14 and 15 are provided equally in the circumferential direction around the axis of the bearing mount 10.
スラスト側排気孔１６は、スラスト給気孔１２とラジアル給気孔１４の間に位置し、その間から加圧空気を排気する。この例では、スラスト側排気孔１６はシール円板１ｂの位置にあるが、シール円板１ｂより上側であってもよい。また、スラスト側排気孔１６は、スラスト給気孔１２とラジアル給気孔１４から供給される加圧空気により中空開口孔内の圧力が上昇しないように、十分大きく設定されている。 The thrust side exhaust hole 16 is located between the thrust air supply hole 12 and the radial air supply hole 14, and exhausts pressurized air from the space. In this example, the thrust side exhaust hole 16 is at the position of the seal disc 1b, but may be above the seal disc 1b. Further, the thrust side exhaust hole 16 is set sufficiently large so that the pressure in the hollow opening hole is not increased by the pressurized air supplied from the thrust air supply hole 12 and the radial air supply hole 14.
ラジアル側排気孔１８は、この例で、ラジアル支持用の第１円筒部１ｃと第２円筒部１ｄの間に位置し、その間から加圧空気を排気する。この例では、ラジアル側排気孔１８は、第１円筒部１ｃと第２円筒部１ｄの中間位置にあるが、上下のラジアル給気孔１４，１５から供給される加圧空気により中空開口孔内の圧力が上昇しないように、十分大きく設定されている。 In this example, the radial-side exhaust hole 18 is located between the first cylindrical portion 1c and the second cylindrical portion 1d for radial support, and exhausts pressurized air from there. In this example, the radial-side exhaust hole 18 is in an intermediate position between the first cylindrical portion 1c and the second cylindrical portion 1d, but the pressurized air supplied from the upper and lower radial air supply holes 14 and 15 has the inside of the hollow opening hole. It is set sufficiently large so that the pressure does not increase.
図６は、図５のＡ部の模式図である。
この図に示すように、上述した本発明の構成によれば、羽根車１ａの円形端面１ｅの下面面積が、シール円板１ｂより大きいので、円形端面１ｅの下面にスラスト給気孔１２から加圧空気を上向きに供給することで円形端面１ｅの下面に発生する圧力Ｐ３は、シール円板１ｂの下面に供給した場合より高くなり、面積×圧力で定まるスラスト空気軸受のスラスト力を大幅に高めることができる。
従って、スラスト空気軸受のスラスト力の不足が解消でき、回転軸１の自重をスラスト空気軸受のみで支持することができる。
FIG. 6 is a schematic diagram of a portion A in FIG.
As shown in this figure, according to the configuration of the present invention described above, the lower surface area of the circular end surface 1e of the impeller 1a is larger than the seal disc 1b, and therefore the lower surface of the circular end surface 1e is pressurized from the thrust air supply hole 12 to the lower surface. By supplying air upward, the pressure P3 generated on the lower surface of the circular end face 1e becomes higher than when it is supplied to the lower surface of the seal disc 1b, and the thrust force of the thrust air bearing determined by area × pressure is greatly increased. Can do.
Accordingly, the shortage of the thrust force of the thrust air bearing can be solved, and the weight of the rotating shaft 1 can be supported only by the thrust air bearing.
また、スラスト側排気孔１６が、スラスト給気孔１２と上側のラジアル給気孔１４の間に位置し、その間から加圧空気を排気するので、スラスト給気孔１２とラジアル給気孔１４の中間位置の圧力が常に外気圧（大気圧）に保たれ、スラスト空気軸受とラジアル空気軸受の空気の相互干渉が無くなり、スラスト空気軸受及びラジアル空気軸受に供給する加圧空気の圧力を独立に制御してそれぞれの剛性を独立に制御することができる。 Further, since the thrust side exhaust hole 16 is located between the thrust air supply hole 12 and the upper radial air supply hole 14, the pressurized air is exhausted between the thrust air supply hole 12 and the pressure at the intermediate position between the thrust air supply hole 12 and the radial air supply hole 14. Is always maintained at the external pressure (atmospheric pressure), the mutual interference between the thrust air bearing and the radial air bearing is eliminated, and the pressure of the pressurized air supplied to the thrust air bearing and the radial air bearing is controlled independently. Stiffness can be controlled independently.
なお、本発明は上述した実施形態に限定されず、特許請求の範囲の記載によって示され、さらに特許請求の範囲の記載と均等の意味および範囲内でのすべての変更を含むものである。 In addition, this invention is not limited to embodiment mentioned above, is shown by description of a claim, and also includes all the changes within the meaning and range equivalent to description of a claim.
１ 回転軸、１ａ 羽根車、１ｂ シール円板、
１ｃ 第１円筒部、１ｄ 第２円筒部、１ｅ 円形端面、
２ 空気軸受、３ 軸受マウント、３ａ スラスト給気孔、
３ｂ，３ｃ ラジアル給気孔、３ｄ，３ｅ 排気孔、
４ マウント支持バネ、５ 原点センサ、
６ 変位センサ、７ 信号処理装置、
８ コンプレッサインペラ、１０ 軸受マウント、
１２ スラスト給気孔、１４，１５ ラジアル給気孔、
１６ スラスト側排気孔、１８ ラジアル側排気孔
1 rotating shaft, 1a impeller, 1b sealing disc,
1c 1st cylindrical part, 1d 2nd cylindrical part, 1e circular end surface,
2 Air bearing, 3 Bearing mount, 3a Thrust air supply hole,
3b, 3c Radial air supply holes, 3d, 3e exhaust holes,
4 Mount support spring, 5 Origin sensor,
6 displacement sensor, 7 signal processor,
8 Compressor impeller, 10 Bearing mount,
12 Thrust air holes, 14,15 Radial air holes,
16 Thrust side exhaust hole, 18 Radial side exhaust hole
Claims (1)
前記羽根車はシール円板より大きい外径の円形端面をシール円板側に有しており、
前記回転軸をその軸心を鉛直に保持して支持する軸受マウントを備え、
該軸受マウントは、羽根車の前記円形端面の下面に加圧空気を供給するスラスト給気孔と、
前記ラジアル支持用の円筒部に加圧空気を供給するラジアル給気孔と、
前記スラスト給気孔とラジアル給気孔の間に位置しその間から加圧空気を排気するスラスト側排気孔とを有する、ことを特徴とする縦型バランス計測装置。
The impeller, the seal disc for shaft seal, and the cylindrical portion for radial support are arranged coaxially and sequentially spaced apart while rotating the shaft while maintaining its axis vertically, and the amount of unbalance A vertical balance measuring device for obtaining a bearing,
The impeller has a circular end surface with an outer diameter larger than that of the seal disc on the seal disc side,
A bearing mount for supporting the rotating shaft while maintaining its axis vertically;
The bearing mount includes a thrust supply hole for supplying pressurized air to the lower surface of the circular end surface of the impeller;
A radial air supply hole for supplying pressurized air to the radial support cylindrical portion;
A vertical balance measuring device having a thrust side exhaust hole that is located between the thrust supply hole and the radial supply hole and exhausts pressurized air from between the thrust supply hole and the radial supply hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010123661A JP5622171B2 (en) | 2010-05-31 | 2010-05-31 | Vertical balance measuring device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010123661A JP5622171B2 (en) | 2010-05-31 | 2010-05-31 | Vertical balance measuring device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2011247837A true JP2011247837A (en) | 2011-12-08 |
| JP5622171B2 JP5622171B2 (en) | 2014-11-12 |
Family
ID=45413257
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2010123661A Active JP5622171B2 (en) | 2010-05-31 | 2010-05-31 | Vertical balance measuring device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP5622171B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015146735A1 (en) * | 2014-03-24 | 2015-10-01 | 株式会社Ｉｈｉ回転機械 | Support device for balance correction |
| CN105300597A (en) * | 2015-08-04 | 2016-02-03 | 上海卫星工程研究所 | Three-axis air floating table center-of-mass balance adjustment method and device thereof |
| CN112179563A (en) * | 2016-08-10 | 2021-01-05 | 国际计测器株式会社 | Dynamic balance testing machine |
| CN114018476A (en) * | 2020-12-25 | 2022-02-08 | 南京乾利合科技有限责任公司 | Air suspension rotary frame of static balancing machine and air suspension static balancing machine |
| CN117968939A (en) * | 2024-03-29 | 2024-05-03 | 山东伊康清真肉类股份有限公司 | Dynamic balance testing device for meat grinder rotor |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105092156A (en) * | 2015-09-21 | 2015-11-25 | 上海卫星工程研究所 | Triaxial air bearing table high-precision mass center balance adjusting device and method |
| JP7081347B2 (en) | 2018-07-03 | 2022-06-07 | オムロン株式会社 | Semiconductor relay module and semiconductor relay circuit |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0220135U (en) * | 1988-07-25 | 1990-02-09 | ||
| JP2000018248A (en) * | 1998-07-03 | 2000-01-18 | Shin Meiwa Ind Co Ltd | Bearing device and sealing mechanism for bearing device |
| US6231302B1 (en) * | 1999-06-08 | 2001-05-15 | G. Fonda Bonardi | Thermal control system for gas-bearing turbocompressors |
-
2010
- 2010-05-31 JP JP2010123661A patent/JP5622171B2/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0220135U (en) * | 1988-07-25 | 1990-02-09 | ||
| JP2000018248A (en) * | 1998-07-03 | 2000-01-18 | Shin Meiwa Ind Co Ltd | Bearing device and sealing mechanism for bearing device |
| US6231302B1 (en) * | 1999-06-08 | 2001-05-15 | G. Fonda Bonardi | Thermal control system for gas-bearing turbocompressors |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015146735A1 (en) * | 2014-03-24 | 2015-10-01 | 株式会社Ｉｈｉ回転機械 | Support device for balance correction |
| JP2015184086A (en) * | 2014-03-24 | 2015-10-22 | 株式会社Ｉｈｉ回転機械 | Support device for balance correction |
| CN106133497A (en) * | 2014-03-24 | 2016-11-16 | 株式会社Ihi回转机械 | Supporting device for correcting balance |
| US10054129B2 (en) | 2014-03-24 | 2018-08-21 | Ihi Rotating Machinery Enginering Co., Ltd. | Support apparatus for balance correction |
| CN105300597A (en) * | 2015-08-04 | 2016-02-03 | 上海卫星工程研究所 | Three-axis air floating table center-of-mass balance adjustment method and device thereof |
| CN112179563A (en) * | 2016-08-10 | 2021-01-05 | 国际计测器株式会社 | Dynamic balance testing machine |
| CN113176037A (en) * | 2016-08-10 | 2021-07-27 | 国际计测器株式会社 | Dynamic balance testing machine |
| US11549857B2 (en) | 2016-08-10 | 2023-01-10 | Kokusai Keisokuki Kabushiki Kaisha | Dynamic balance testing device |
| CN112179563B (en) * | 2016-08-10 | 2023-03-14 | 国际计测器株式会社 | Dynamic balance testing machine |
| CN114018476A (en) * | 2020-12-25 | 2022-02-08 | 南京乾利合科技有限责任公司 | Air suspension rotary frame of static balancing machine and air suspension static balancing machine |
| CN117968939A (en) * | 2024-03-29 | 2024-05-03 | 山东伊康清真肉类股份有限公司 | Dynamic balance testing device for meat grinder rotor |
| CN117968939B (en) * | 2024-03-29 | 2024-06-04 | 山东伊康清真肉类股份有限公司 | Dynamic balance testing device for meat grinder rotor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5622171B2 (en) | 2014-11-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5622171B2 (en) | Vertical balance measuring device | |
| RU2425341C2 (en) | Procedure and design for dynamic measurement of rotor unbalance | |
| JP6546759B2 (en) | Rotary machine, bearing and method for manufacturing said rotary machine | |
| US7252000B2 (en) | Method and machine for rotor imbalance determination | |
| CN108344573A (en) | A kind of Aerostatic thrust bearing high speed performance test system and test method | |
| Kumar et al. | Dynamic analysis and identification of unbalance and misalignment in a rigid rotor with two offset discs levitated by active magnetic bearings: a novel trial misalignment approach | |
| CN102778313A (en) | Device for testing dynamic friction torque of precise micro rolling bearing | |
| US20200096384A1 (en) | Blade abnormality detecting device, blade abnormality detecting system, rotary machine system, and blade abnormality detecting method | |
| JP5262392B2 (en) | Rotating machine support device and design method thereof | |
| JP2010190350A (en) | Static pressure gas bearing device | |
| JP5440792B2 (en) | Vertical balance measuring device | |
| JP6716080B2 (en) | Rotating machines and equipment for energy conversion including such machines | |
| KR20070019910A (en) | Measurement system for axial load | |
| KR101343870B1 (en) | Measuring apparatus for thrust of turbo machine | |
| JP2009008593A (en) | Torque measuring device of tapered roller bearing | |
| JP2004340939A (en) | Balancing test method and supporting device for balancing test for rotor without journal | |
| JP5370647B2 (en) | Equilibrium testing device with hydrostatic gas bearing device | |
| JP2005181012A (en) | Bearing system applied to dynamic-balancing machine | |
| JP2004191146A (en) | Bearing inspection apparatus | |
| CN103499406B (en) | Perpendicularly-hung high-precision torque testing device in thermal vacuum environment | |
| JP6194616B2 (en) | Turbocharger | |
| JP2012080657A (en) | Rotating apparatus | |
| JP2008275363A (en) | Inspection method of fluid dynamic pressure bearing, and spindle motor equipped with same | |
| KR101251418B1 (en) | Vertical type turbo device | |
| KR100967398B1 (en) | Centrifugal turbo machine for monitoring bearing operation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20130220 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20140409 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20140508 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20140613 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20140901 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 5622171 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20140914 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |