JP3533818B2 - Flywheel equipment - Google Patents
Flywheel equipmentInfo
- Publication number
- JP3533818B2 JP3533818B2 JP08343596A JP8343596A JP3533818B2 JP 3533818 B2 JP3533818 B2 JP 3533818B2 JP 08343596 A JP08343596 A JP 08343596A JP 8343596 A JP8343596 A JP 8343596A JP 3533818 B2 JP3533818 B2 JP 3533818B2
- Authority
- JP
- Japan
- Prior art keywords
- flywheel
- fixed
- convex portion
- outer periphery
- adjusting
- 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.)
- Expired - Fee Related
Links
Landscapes
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Description
【発明の詳細な説明】
【0001】
【発明の属する技術分野】この発明は、固定フライホイ
ルに慣性調整のための調整フライホイルを取り付けたフ
ライホイル装置に関するものである。
【0002】
【従来の技術】図4は従来の高速用のフライホイル装置
の縦断面図を示し、1は軸受台2に軸受台3を介して回
転自在に支持された回転軸、4は回転軸1から径方向に
突出し、回転軸1と一体的に設けられた固定フライホイ
ルであり、その側面には凹部4aが設けられている。5
は中心に中心孔5aを有するとともに、側面の中心孔5
aの周辺部に凸部5bを有する調整フライホイルであ
り、凹部4aと凸部5bは嵌合し、かつ調整フライホイ
ル5は固定フライホイル4にボルト6により固定され
る。又、調整フライホイル5の外径は固定フライホイル
4の外径より大きくなっている。
【0003】上記構成において、静止時には凹部4aの
内周と凸部5bの内周即ち中心孔5aの内周とは径方向
の隙間なく嵌合し、凹部4aの外周と凸部5bの外周と
の間には径方向の隙間7が形成されている。ここで、回
転軸1を回転させると、調整フライホイル5の方が外径
方向へのふくらみ量(変位量)が大きいため、回転数が
上昇するに従って隙間7が次第に小さくなり、最終的に
零となる。このため、調整フライホイル5の偏心は凹部
4aの外周との係合によりある程度に抑制され、偏心に
よる振動も抑制される。
【0004】
【発明が解決しようとする課題】図5は調整フライホイ
ル5の振動の振幅と回転速度との関係を示し、イは外周
インロー部がない場合、即ち凹部4aなどがない場合で
あり、このような場合には回転速度に従って調整フライ
ホイル5の振動の振幅は大きくなる。又、ロは外周イン
ロー部がある場合であり、回転速度が高速域になると、
凹部4aの外周に凸部5bの外周が当接し、調整フライ
ホイル5の振動の振幅は小さくなる。ところが、図中に
示した中速域では、調整フライホイル5は偏心が生じ始
めて凹部4aの内周と凸部5bの内周との間に隙間がで
き始めているが、凹部4aの外周と凸部5bの外周が十
分に当接しないために振動の振幅は大きくなった。そこ
で、回転速度がもっと低い段階から凸部5bの外周と凹
部4aの外周とが当接するようにすると、高回転域で凹
部4aの外周は凸部5bの外周に押圧されて大きな応力
が加わるようになり、破損する恐れがあった。
【0005】この発明は上記のような課題を解決するた
めに成されたものであり、調整フライホイルの偏心によ
る振動を抑制するとともに、固定フライホイルの破損を
防止することができるフライホイル装置を得ることを目
的とする。
【0006】
【課題を解決するための手段】この発明に係るフライホ
イル装置は、固定フライホイルの側面にその凹部に固定
フライホイルより径が小さな調整フライホイルの凸部を
それぞれの外周が当接して嵌合するように調整フライホ
イルを取り付け、固定フライホイルの凹部及び調整フラ
イホイルの凸部を固定フライホイルの凹部の外周の遠心
力による半径方向ふくらみ量と調整フライホイルの凸部
の外周の遠心力による半径方向ふくらみ量が等しい位置
に設けたものである。
【0007】
【発明の実施の形態】以下、この発明の実施の形態を図
面とともに説明する。図1はこの実施形態によるフライ
ホイル装置の一部縦断正面図を示し、8は鍛造により回
転軸1と一体に形成された固定フライホイルであり、そ
の両側面には凹部8aが形成されている。9は中心に中
心孔9aを有するとともに、側面の中心孔9aの周辺部
に凹部8aと嵌合する凸部9bを有する調整フライホイ
ルであり、中心孔9aに回転軸1を挿通するとともに、
凸部9bを凹部8aに嵌合し、調整フライホイル9に挿
通したボルト6を固定フライホイル8に螺着することに
より調整フライホイル9を固定フライホイル8に固定す
る。
【0008】又、固定フライホイル8の外径は調整フラ
イホイル9の外径より大きく形成され、凹部8aの外周
と凸部9bの外周、及び凹部8aの内周と凸部9bの内
周とはいずれも隙間なく嵌合している。さらに、凹部8
aの外周と凸部9bの外周は両フライホイル8,9の遠
心力による半径方向ふくらみ量が等しくなる位置に設け
られている。
【0009】図2(a),(b)は固定フライホイル8
及び調整フライホイル9における半径位置と回転時の応
力との関係図を示し、外周インロー部10とは凹部8a
及び凸部9bの外周嵌合部のことである。又、σrは半
径方向応力,σtは周方向応力を示す。固定フライホイ
ル8では中心に最も大きな応力が加わり、調整フライホ
イル9では中心孔9aの内周に最も大きな応力が加わる
ことが解る。ここで、中心孔がない一様厚さの回転円
板、及び中心孔がある一様厚さの回転円板の半径方向ふ
くらみ量δ1,δ2はそれぞれ式(1),(2)により
計算される。
【0010】
【数1】
【0011】上式において、ρは回転円板の密度,ωは
角速度,Eは弾性係数,νはポアソン比,aは中心孔の
半径,bは回転円板の半径,rは半径位置である。式
(1),(2)で計算した結果をグラフで示すと、図3
(a),(b)のようになり、図3(a)は固定フライ
ホイル8にほぼ相当し、図3(b)は調整フライホイル
9にほぼ相当する。そこで、それぞれの中心から半径位
置が等しく、かつ半径方向ふくらみ量が等しい点(この
ような点が存在するのは、固定フライホイル8の外径が
調整フライホイル9の外径より大きいときのみであ
る。)を検出し、外周インロー部10即ち凹部8aの外
周及び凸部9bの外周をこの半径位置に一致させる。な
お、図2,図3の特性は回転数400rpmのときのも
のであるが、回転数が変化しても外周インロー部10で
の半径方向ふくらみ量は一致したままである。又、ボル
ト6は実際にはばか孔に挿通され、遠心力応力を分担す
ることはなく、無視できる。
【0012】上記実施形態においては、固定フライホイ
ル8の凹部8aの外周及び調整フライホイル9の凸部9
bの外周が遠心力による半径方向ふくらみ量(伸び)δ
1=δ2の位置に設けられており、回転速度全域におい
てこの双方の間に隙間は生じず、しかも凸部9bの外周
から凹部8aの外周へ大きな応力が加わることもない。
このように外周インロー部10での伸びや応力の干渉が
ないために、偏心による振動は抑制され、応力による破
損も生じない。又、強度計算が単純となり、高精度の強
度計算を行うことができる。
【0013】
【発明の効果】以上のようにこの発明によれば、固定フ
ライホイルの外径を調整フライホイルの外径より大きく
し、かつ相互に嵌合する固定フライホイルの凹部の外周
と調整フライホイルの凸部の外周を両フライホイルの遠
心力による半径方向ふくらみ量が一致する位置に設けて
おり、全回転域において両者間に隙間は生じず、大きな
応力も加わらない。このため、偏心による振動や応力に
よる破損を防止することができる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flywheel device in which an adjustment flywheel for adjusting inertia is attached to a fixed flywheel. 2. Description of the Related Art FIG. 4 is a longitudinal sectional view of a conventional high-speed flywheel device, wherein 1 is a rotary shaft rotatably supported on a bearing base 2 via a bearing base 3 and 4 is a rotary shaft. It is a fixed flywheel that projects radially from the shaft 1 and is provided integrally with the rotating shaft 1, and has a recess 4 a on the side surface. 5
Has a central hole 5a at the center and a central hole 5
This is an adjusting flywheel having a convex portion 5b at the periphery of the portion a. The concave portion 4a and the convex portion 5b are fitted, and the adjusting flywheel 5 is fixed to the fixed flywheel 4 by bolts 6. The outer diameter of the adjusting flywheel 5 is larger than the outer diameter of the fixed flywheel 4. In the above configuration, at rest, the inner periphery of the concave portion 4a and the inner periphery of the convex portion 5b, that is, the inner periphery of the center hole 5a are fitted without a radial gap, and the outer periphery of the concave portion 4a and the outer periphery of the convex portion 5b are fitted. A radial gap 7 is formed between them. Here, when the rotating shaft 1 is rotated, the adjusting flywheel 5 has a larger swelling amount (displacement amount) in the outer diameter direction, so that the gap 7 gradually decreases as the rotation speed increases, and finally the zero is zero. It becomes. For this reason, the eccentricity of the adjustment flywheel 5 is suppressed to some extent by engagement with the outer periphery of the concave portion 4a, and the vibration due to the eccentricity is also suppressed. FIG. 5 shows the relationship between the amplitude of the vibration of the adjusting flywheel 5 and the rotation speed. FIG. 5 shows the case where there is no outer peripheral spigot, that is, the case where there is no recess 4a. In such a case, the amplitude of the vibration of the adjustment flywheel 5 increases according to the rotation speed. Also, b is the case where there is an outer spigot part, and when the rotation speed becomes a high speed region,
The outer periphery of the convex portion 5b abuts the outer periphery of the concave portion 4a, and the amplitude of the vibration of the adjusting flywheel 5 decreases. However, in the middle speed range shown in the drawing, the adjusting flywheel 5 starts to be eccentric and a gap starts to be formed between the inner periphery of the concave portion 4a and the inner periphery of the convex portion 5b. The amplitude of the vibration was increased because the outer periphery of the portion 5b did not sufficiently contact. Therefore, when the outer periphery of the convex portion 5b and the outer periphery of the concave portion 4a are brought into contact with each other from a lower rotation speed stage, the outer periphery of the concave portion 4a is pressed against the outer periphery of the convex portion 5b in a high rotation region so that a large stress is applied. And could be damaged. SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems, and provides a flywheel device capable of suppressing vibration due to eccentricity of an adjustable flywheel and preventing breakage of a fixed flywheel. The purpose is to get. A flywheel device according to the present invention is provided with a convex portion of an adjusting flywheel having a smaller diameter than the fixed flywheel in a concave portion on a side surface of the fixed flywheel.
Attach the adjusting flywheel so that the outer circumferences abut against each other, and fit the concave portion of the fixed flywheel and the adjusting flywheel.
Fix the convex part of the foil. Centrifuge the outer circumference of the concave part of the flywheel.
But on the radial bulge amount equal position by centrifugal force in the radial direction swelling amount and an outer periphery of the convex portion of the adjusting flywheel by force. Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a partially longitudinal front view of a flywheel device according to this embodiment. Reference numeral 8 denotes a fixed flywheel integrally formed with the rotary shaft 1 by forging, and concave portions 8a are formed on both side surfaces thereof. . Numeral 9 is an adjusting flywheel having a center hole 9a at the center and a convex portion 9b fitted around the center hole 9a on the side surface and fitted with the concave portion 8a. The rotating flywheel 1 is inserted through the center hole 9a,
The adjusting flywheel 9 is fixed to the fixed flywheel 8 by fitting the convex portion 9b into the concave portion 8a and screwing the bolt 6 inserted into the adjusting flywheel 9 to the fixed flywheel 8. The outer diameter of the fixed flywheel 8 is formed larger than the outer diameter of the adjusting flywheel 9, and the outer periphery of the concave portion 8a and the outer periphery of the convex portion 9b, and the inner periphery of the concave portion 8a and the inner periphery of the convex portion 9b. Are fitted without any gap. Further, the recess 8
a of the flywheels 8 and 9
It is provided at a position where the amount of bulge in the radial direction due to the heart force is equal. FIGS. 2A and 2B show a fixed flywheel 8.
FIG. 4 is a diagram showing a relationship between a radial position of the adjustment flywheel 9 and a stress at the time of rotation.
And the outer peripheral fitting portion of the convex portion 9b. Further, σ r indicates a radial stress and σ t indicates a circumferential stress. It can be seen that the largest stress is applied to the center in the fixed flywheel 8 and the largest stress is applied to the inner periphery of the center hole 9a in the adjustment flywheel 9. Here, the radial bulge amounts δ1 and δ2 of a rotating disk having a uniform thickness without a center hole and a rotating disk having a uniform thickness with a center hole are calculated by equations (1) and (2), respectively. You. [0010] In the above equation, ρ is the density of the rotating disk, ω is the angular velocity, E is the elastic coefficient, ν is the Poisson's ratio, a is the radius of the center hole, b is the radius of the rotating disk, and r is the radial position. . FIG. 3 is a graph showing the results calculated by equations (1) and (2).
3A and 3B, FIG. 3A substantially corresponds to the fixed flywheel 8, and FIG. 3B substantially corresponds to the adjustment flywheel 9. Therefore, a point where the radial position is equal from each center and the radial swell amount is equal (such a point exists only when the outer diameter of the fixed flywheel 8 is larger than the outer diameter of the adjustment flywheel 9). Is detected), and the outer periphery of the outer peripheral spigot portion 10, that is, the outer periphery of the concave portion 8a and the outer periphery of the convex portion 9b are made to coincide with this radial position. Note that the characteristics in FIGS. 2 and 3 are obtained when the rotational speed is 400 rpm, but the radial bulge amount in the outer peripheral spigot portion 10 remains the same even when the rotational speed changes. Further, the bolt 6 is actually inserted into the fool hole and does not share the centrifugal stress and can be ignored. In the above embodiment, the outer periphery of the concave portion 8a of the fixed flywheel 8 and the convex portion 9 of the adjusting flywheel 9 are formed.
b is the radial swelling (elongation) δ due to centrifugal force
1 = δ2, there is no gap between the two over the entire rotation speed range, and no large stress is applied from the outer periphery of the convex portion 9b to the outer periphery of the concave portion 8a.
As described above, since there is no interference of the elongation and the stress in the outer peripheral spigot portion 10, the vibration due to the eccentricity is suppressed, and the damage due to the stress does not occur. Further, the strength calculation becomes simple, and the strength calculation can be performed with high accuracy. As described above , according to the present invention, the outer diameter of the fixed flywheel is made larger than the outer diameter of the adjusting flywheel, and the outer diameter of the concave portion of the fixed flywheel fitted with the adjusting wheel is adjusted. The outer periphery of the convex portion of the flywheel is provided at a position where the amounts of radial bulge due to the centrifugal force of both flywheels coincide with each other, so that there is no gap between the two over the entire rotation range, and no large stress is applied. For this reason, damage due to vibration or stress due to eccentricity can be prevented.
【図面の簡単な説明】
【図1】この発明によるフライホイル装置の一部縦断正
面図である。
【図2】この発明による固定フライホイル及び調整フラ
イホイルの回転時の応力分布図である。
【図3】この発明による固定フライホイル及び調整フラ
イホイルの半径方向ふくらみ量の分布図である。
【図4】従来のフライホイル装置の縦断面図である。
【図5】従来のフライホイル装置の調整フライホイルの
振幅と回転速度との関係図である。
【符号の説明】
1…回転軸
8…固定フライホイル
8a…凹部
9…調整フライホイル
9a…中心孔
9b…凸部
10…外周インロー部BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial longitudinal front view of a flywheel device according to the present invention. FIG. 2 is a stress distribution diagram during rotation of a fixed flywheel and an adjusting flywheel according to the present invention. FIG. 3 is a distribution diagram of a radial swelling amount of a fixed flywheel and an adjustment flywheel according to the present invention. FIG. 4 is a longitudinal sectional view of a conventional flywheel device. FIG. 5 is a diagram showing a relationship between amplitude and rotation speed of an adjusting flywheel of a conventional flywheel device. [Description of Signs] 1 ... Rotating shaft 8 ... Fixed flywheel 8a ... Recess 9 ... Adjustment flywheel 9a ... Center hole 9b ... Protrusion 10 ... Outer peripheral spigot
Claims (1)
面に凹部を有する固定フライホイルと、中心に孔を有す
るとともに、側面に固定フライホイルの凹部とそれぞれ
の外周が当接するように嵌合する凸部を有し、固定フラ
イホイルの側面に取り付けられた調整フライホイルを備
えたフライホイル装置において、固定フライホイルの外
径を調整フライホイルの外径より大きくするとともに、
固定フライホイルの凹部及び調整フライホイルの凸部を
該凹部の外周の遠心力による半径方向ふくらみ量と調整
フライホイルの凸部の外周の遠心力による半径方向ふく
らみ量が等しくなる位置に設けたことを特徴とするフラ
イホイル装置。(57) is formed in a [Claims 1] together with the rotating shaft, and a fixed flywheel having a recess on a side surface, and has a hole in the center, respectively the recess of the fixed flywheel to the side surface
In the flywheel device having a convex portion fitted so that the outer circumference of the flywheel abuts and having an adjustment flywheel attached to the side surface of the fixed flywheel, the outer diameter of the fixed flywheel is made larger than the outer diameter of the adjusted flywheel. As well as
Adjust the recess of the fixed flywheel and the protrusion of the adjustment flywheel.
Flywheel and wherein the amount bulging radially due to centrifugal force of the outer periphery of the convex portion of the radial bulge amount and adjustment flywheel due to the centrifugal force of the outer periphery of the concave portion is provided at equal positions.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP08343596A JP3533818B2 (en) | 1996-04-05 | 1996-04-05 | Flywheel equipment |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP08343596A JP3533818B2 (en) | 1996-04-05 | 1996-04-05 | Flywheel equipment |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH09273601A JPH09273601A (en) | 1997-10-21 |
JP3533818B2 true JP3533818B2 (en) | 2004-05-31 |
Family
ID=13802362
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP08343596A Expired - Fee Related JP3533818B2 (en) | 1996-04-05 | 1996-04-05 | Flywheel equipment |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3533818B2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103727177B (en) * | 2013-12-04 | 2015-11-18 | 中广核工程有限公司 | There is the nuclear power main pump flywheel of over-speed protection function |
CN114383828A (en) * | 2021-12-13 | 2022-04-22 | 常州莱可智能科技有限公司 | Assembled rack for flywheel stress experiment |
-
1996
- 1996-04-05 JP JP08343596A patent/JP3533818B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH09273601A (en) | 1997-10-21 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP3505469B2 (en) | Rotational speed damper | |
JPH10508084A (en) | Drive | |
KR20080021736A (en) | A constant-velocity joint for a driven wheel | |
US20050231023A1 (en) | Wheel assembly | |
JPS591607B2 (en) | Vibration damping device in automobile drive system | |
JP4911333B2 (en) | Wheel mounting structure in a wheel bearing device | |
JPS6014634A (en) | Distorted waveform transmission assembly | |
JP3533818B2 (en) | Flywheel equipment | |
JPH0599231A (en) | Rolling bearing | |
JPH0211639Y2 (en) | ||
JPS59226727A (en) | Dynamic damper of engine | |
JP2001311442A (en) | Brake rotor and wheel bearing device provided with the same | |
JP3154648B2 (en) | Rotary cutting tool | |
JP2605157Y2 (en) | damper | |
JPS61248019A (en) | Rotor, especially polyhedral mirror | |
JPH0723639Y2 (en) | Torsional damper | |
JPS6110014Y2 (en) | ||
JPS6141464Y2 (en) | ||
JP2564679Y2 (en) | Center bearing support | |
JP2931343B2 (en) | Motor shaft bearing device for massage machine | |
JPS6162618A (en) | Rotating body fixing tool | |
JPH0121185Y2 (en) | ||
JPH0729327Y2 (en) | Torsional damper | |
JP2000262004A (en) | Spindle motor | |
JP3195867B2 (en) | Auto tensioner |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20040115 |
|
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: 20040217 |
|
A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20040301 |
|
R150 | Certificate of patent or registration of utility model |
Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080319 Year of fee payment: 4 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090319 Year of fee payment: 5 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090319 Year of fee payment: 5 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100319 Year of fee payment: 6 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110319 Year of fee payment: 7 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110319 Year of fee payment: 7 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120319 Year of fee payment: 8 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130319 Year of fee payment: 9 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20140319 Year of fee payment: 10 |
|
LAPS | Cancellation because of no payment of annual fees |