JP4404986B2 - Spindle joint structure of high-speed rotor - Google Patents
Spindle joint structure of high-speed rotor Download PDFInfo
- Publication number
- JP4404986B2 JP4404986B2 JP10617999A JP10617999A JP4404986B2 JP 4404986 B2 JP4404986 B2 JP 4404986B2 JP 10617999 A JP10617999 A JP 10617999A JP 10617999 A JP10617999 A JP 10617999A JP 4404986 B2 JP4404986 B2 JP 4404986B2
- Authority
- JP
- Japan
- Prior art keywords
- disk
- main shaft
- rotor
- center
- disk part
- 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 - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Non-Positive Displacement Air Blowers (AREA)
Description
【0001】
【発明の属する技術分野】
本発明は高速回転体のロータ、特にターボ分子ポンプや複合分子ポンプにおけるロータの円盤部と主軸とを接合するのに最適な接合構造に関する。
【0002】
【従来の技術】
従来この種の分子ポンプのロータでは、主としてアルミ合金製のロータの円盤部と鋼製の主軸部とをボルト等を用いて締結し、一体に形成している。
【0003】
第1の従来例として複合分子ポンプの縦断面図の一例を図4に示した。
【0004】
即ち同図4において、ロータaの円盤部bの中心にテーパ穴cを貫通して設けると共に主軸Sの先を円錐状のテーパ部dに形成し、該テーパ部dをテーパ穴cに嵌入して押え金eを介してボルトfを締め付けることにより、これら円盤部bと主軸Sとを接合して一体のロータに形成している。
【0005】
又、図5に示す第2の従来例では、主軸S1の前部にフランジgを形成し、円盤部b1と主軸S1とを複数のボルトh1で締結すると共にノックピンkを用いて両者の位置決めを行なうようにしている。
【0006】
更に又、図6に示す第3の従来例では、円盤部b2の中心部に設けた貫通孔mに主軸S2の前端の円柱状の突出部nを締め代を有して嵌入させ、ボルトh2を用いて両者を締結して一体に形成している。
【0007】
【発明が解決しようとする課題】
しかし、図4に示す第1の従来例の主軸接合方法では、ロータaの高速回転時にテーパ穴c部に大きな応力が発生するという問題があった。更に同接合方法によれば、高速回転時の遠心力によって該テーパ穴cに変形を生じ、このため、該テーパ穴cと前記主軸Sのテーパ部dとの嵌合部の剛性が低下するという問題があった。
【0008】
次に、図5に示す第2の従来例の主軸接合方法においては、円盤部b1と主軸S1との再組立て時に、ロータa1のバランスの再現性が悪いという問題があった。更に同接合方法によれば、ボルトh1に働く廻り止め力は該ボルトh1の締め付け時の引張り力によるねじ部の摩擦力だけなので、該ボルトh1の締め付け部に緩みを生ずる危険性があった。
【0009】
次の図6に示す第3の従来例の主軸接合方法においては、前記第1の従来例におけると同様に、高速回転時に貫通孔m部に大きな応力が発生するという問題があった。
【0010】
更に又、前記第2の従来例と同様に、ボルトh2が緩む危険性があった。
【0011】
本発明はこれらの問題点を解消し、ロータの円盤部内に過大な応力の発生箇所がなく、締結ボルトに緩みを生ずる危険性がなく、又、再組立て時にもロータのバランスの再現性が優れている高速回転体のロータの主軸接合構造を提供することを特徴とする。
【0012】
【課題を解決するための手段】
本発明は上記の目的を達成すべく、ロータの円盤部の片面に主軸の前端面を当接させ、両者をボルトで締結してなる高速回転体のロータにおいて、前記円盤部の前記片面の中心部から円錐台状の中実の突出部を突出させると共に前記前端面の中心部に先細の円錐台状のテーパ穴を設け、両者を前記ボルトで締結したときに該突出部が該テーパ穴に締め代を有して嵌入すると共に該締結によって前記円盤部の弾発力に逆らって該円盤部の中心部近傍が背後方向に膨出し、該円盤部の腹側が凹んで前記当接面の内周側に狭い空間部を生ずるように形成したことを特徴とする。
【0013】
【発明の実施の形態】
本発明の第1の実施の形態を図1及び図2により説明する。
【0014】
図1は本発明の高速回転体のロータの主軸接合構造によるロータ1の円盤部2と主軸3の接合部の縦断面図を示し、4はこれら円盤部2と主軸3とを締結しているボルトで、同一のピッチ円上に多数のボルト4が配置されている。
【0015】
前記円盤部2はアルミ合金製で、該円盤部2は鋼製の主軸3の前端面と環状の当接面2bにおいて当接している。
【0016】
前記円盤部2の中心部からは円錐台状の中実の突出部2cが突出しており、前記主軸3の前端面の中心部に設けた円錐台状のテーパ穴3aに該突出部2cの大部分が締め代を有して嵌入した構造となっている。又、該嵌入部の外周には前記当接面2bとの間に狭いすき間の空間部2aを有している。
【0017】
尚、3bは主軸3の前端部に設けたフランジ部で、前記円盤部2との当接面2bを充分に得られるような大径に形成されている。
【0018】
図2は円盤部2と主軸3の組立て時の状態を示し、円盤側の突出部2cを主軸側のテーパ穴3aに係合させて、前記ボルト4は未だ捩じ込んでいない状態にある。この時、円盤部2と主軸3の前端面との間は僅かなすき間2eを存して両者が離間している。
【0019】
この状態においてボルト4を捩じ込むようにすれば、前記突出部2cとテーパ穴3aとの嵌合部の弾発力、及び前記円盤部2の弾発力に逆らってこれら円盤部2と主軸3とが締結され、前記環状の当接面2bが形成されると共に該円盤部2の中心部近傍が背後方向へ膨出し、該円盤部2の腹側が凹んで前記空間部2aが形成される。
【0020】
尚、円盤部2の前記膨出は、該円盤部2の弾性域内での変形となるようにした。
【0021】
次に、本実施の形態の作用及び効果について説明する。
【0022】
本実施の形態の円盤部2は中心部に貫通孔がないので、この種の貫通孔部に発生しがちな過大な応力の発生がない。
【0023】
又、円盤部2と主軸3とを締結しているボルト4は、前記円盤部2の弾発力によって常に該ボルト4の軸方向に引張り力を受けているので、これらのボルト4に緩みを生ずる心配がない。
【0024】
更に又、前記突出部2cとテーパ穴3aとの係合により円盤部2と主軸3との芯出しが容易に行なわれるので、ロータ1の再組立て時におけるロータバランスの再現性が良い。
【0025】
本発明の第2の実施の形態を図3により説明する。
【0026】
図3は本発明の高速回転体のロータの主軸接合方法の第2の実施の形態における円盤部5と主軸6の接合部の縦断面図を示す。
【0027】
円盤部5はアルミ合金製で、ボルト4の締付けにより該円盤部5と鋼製の主軸6の前端面とが環状の当接面5bにおいて当接している。
【0028】
前記円盤部5の中心部には先細の円錐台状のテーパ穴5cを貫通させずに設けてあり、前記主軸6の前端面の中心部に突出させて設けた中実の円錐台状の突出部6aの大部分が該テーパ穴5cに締め代を有して嵌入した構造としている。
【0029】
尚、当該円盤部5も前記ボルト4の締付けによって中心部近傍が背後方向へ膨出すると共に該円盤部5の腹側に空間部5aが形成される。
【0030】
次に本実施の形態の作用及び効果について説明する。
【0031】
本実施の形態においても前記第1の実施の形態におけるのと同様に、前記円盤部5の弾発力によって締結ボルト4の軸方向に常に引張り力が掛かっているので、これらのボルト4が緩むことがない。
【0032】
又、前記突出部6aとテーパ穴5cとの係合により円盤部5と主軸6との芯出しが容易に行なわれるので、再組立て時におけるロータバランスの再現性が良い。
【0033】
更に又、前記円盤部5のテーパ穴5cは貫通していないので、ロータの高速回転時にも貫通孔を有する従来の円盤部に較べて低い応力で済んでいる。
【0034】
【発明の効果】
このように本発明によれば、ロータの円盤部に過大な応力の発生箇所がなく、締結ボルトに緩みを生ずることがなく、又、再組立て時にもロータのバランスの再現性に優れているような高速回転体のロータの主軸接合構造を提供できる効果を有する。
【図面の簡単な説明】
【図1】本発明の第1の実施の形態における円盤部と主軸の接合部の縦断面図である。
【図2】同上円盤部と主軸の組立て途中の状態を示す縦断面図である。
【図3】本発明の第2の実施の形態における円盤部と主軸の接合部の縦断面図である。
【図4】円盤部と主軸の接合方法を用いた複合分子ポンプの第1の従来例の縦断面図である。
【図5】円盤部と主軸との接合方法の第2の従来例の縦断面図である。
【図6】円盤部と主軸との接合方法の第3の従来例の縦断面図である。
【符号の説明】
1 ロータ
2、5 円盤部
2a、5a 空間部
2b、5b 当接面
2c、6a 突出部
2e すき間
3、6 主軸
3a、5a テーパ穴
3b フランジ部
4 ボルト[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a joining structure that is optimal for joining a rotor and a main shaft of a rotor of a high-speed rotating body, particularly a turbo molecular pump or a composite molecular pump.
[0002]
[Prior art]
Conventionally, in a rotor of this type of molecular pump, a disk portion of a rotor made mainly of an aluminum alloy and a main shaft portion made of steel are fastened using bolts or the like, and are integrally formed.
[0003]
FIG. 4 shows an example of a longitudinal sectional view of a complex molecular pump as a first conventional example.
[0004]
That is, in FIG. 4, a tapered hole c is provided through the center of the disk part b of the rotor a, the tip of the main shaft S is formed into a conical tapered part d, and the tapered part d is fitted into the tapered hole c. By tightening the bolt f through the presser foot e, the disk part b and the main shaft S are joined to form an integral rotor.
[0005]
Further, in the second conventional example shown in FIG. 5, a flange g is formed at the front portion of the main shaft S1, the disk portion b1 and the main shaft S1 are fastened by a plurality of bolts h1, and positioning of both is performed using a knock pin k. I try to do it.
[0006]
Furthermore, in the third conventional example shown in FIG. 6, a cylindrical protrusion n at the front end of the main shaft S2 is fitted with a tightening margin into a through hole m provided at the center of the disk part b2, and a bolt h2 is inserted. The two are fastened together and formed integrally.
[0007]
[Problems to be solved by the invention]
However, the first conventional spindle joining method shown in FIG. 4 has a problem that a large stress is generated in the tapered hole c portion when the rotor a rotates at high speed. Further, according to the joining method, the taper hole c is deformed by the centrifugal force at the time of high speed rotation, so that the rigidity of the fitting part between the taper hole c and the taper part d of the spindle S is reduced. There was a problem.
[0008]
Next, the spindle joining method of the second conventional example shown in FIG. 5 has a problem that the reproducibility of the balance of the rotor a1 is poor when the disk part b1 and the spindle S1 are reassembled. Further, according to the joining method, since the detent force acting on the bolt h1 is only the frictional force of the screw portion due to the tensile force at the time of tightening the bolt h1, there is a risk of loosening the tightening portion of the bolt h1.
[0009]
In the spindle connecting method of the third conventional example shown in FIG. 6, there is a problem that a large stress is generated in the through-hole m part during high-speed rotation, as in the first conventional example.
[0010]
Furthermore, similarly to the second conventional example, there is a risk that the bolt h2 is loosened.
[0011]
The present invention solves these problems, there is no place where excessive stress is generated in the disk portion of the rotor, there is no risk of loosening of the fastening bolts, and the reproducibility of the balance of the rotor is excellent even during reassembly. The present invention provides a main shaft joining structure of a rotor of a high-speed rotating body.
[0012]
[Means for Solving the Problems]
To achieve the above object, the present invention provides a rotor of a high-speed rotating body in which a front end surface of a main shaft is brought into contact with one surface of a disk portion of a rotor and both are fastened with bolts, and the center of the one surface of the disk portion is A solid frustoconical protrusion is projected from the center and a tapered frustoconical taper hole is provided in the center of the front end surface, and when the two bolts are fastened together with the bolt, the protrusion becomes a taper hole. Inserted with a tightening allowance and, by the tightening , against the elastic force of the disk part, the vicinity of the center part of the disk part bulges backward, the ventral side of the disk part is recessed and the inside of the contact surface It is characterized by forming a narrow space on the circumferential side.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
A first embodiment of the present invention will be described with reference to FIGS.
[0014]
FIG. 1 is a longitudinal sectional view of a joint portion of a
[0015]
The
[0016]
A solid
[0017]
Incidentally, 3b is a flange portion provided at the front end portion of the main shaft 3, and has a large diameter so that a
[0018]
FIG. 2 shows a state in which the
[0019]
If the bolt 4 is screwed in this state, the
[0020]
The bulge of the
[0021]
Next, the operation and effect of the present embodiment will be described.
[0022]
Since the
[0023]
Further, the bolts 4 that fasten the
[0024]
Furthermore, since the centering of the
[0025]
A second embodiment of the present invention will be described with reference to FIG.
[0026]
FIG. 3 shows a longitudinal sectional view of the joint between the disk portion 5 and the
[0027]
The disk part 5 is made of an aluminum alloy, and the disk part 5 and the front end surface of the steel
[0028]
A solid frustoconical protrusion is provided at the center of the disk portion 5 without penetrating a tapered frustum-shaped tapered hole 5c and protruding from the center of the front end surface of the
[0029]
The disk portion 5 also bulges in the vicinity of the center portion by tightening the bolt 4, and a
[0030]
Next, the operation and effect of the present embodiment will be described.
[0031]
Also in the present embodiment, as in the first embodiment, the tensile force is always applied in the axial direction of the fastening bolt 4 due to the elastic force of the disk portion 5, so that these bolts 4 are loosened. There is nothing.
[0032]
Further, since the disk portion 5 and the
[0033]
Furthermore, since the taper hole 5c of the disk part 5 does not penetrate, even when the rotor rotates at a high speed, a lower stress is required as compared with a conventional disk part having a through hole.
[0034]
【The invention's effect】
As described above, according to the present invention, there is no location where excessive stress is generated in the disk portion of the rotor, the fastening bolt is not loosened, and the reproducibility of the balance of the rotor is excellent even during reassembly. This has the effect of providing a main shaft joining structure for a rotor of a high-speed rotating body.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a joint between a disk portion and a main shaft in a first embodiment of the present invention.
FIG. 2 is a longitudinal sectional view showing a state in the course of assembling the disk part and the spindle.
FIG. 3 is a longitudinal sectional view of a joint portion between a disk portion and a main shaft in a second embodiment of the present invention.
FIG. 4 is a longitudinal sectional view of a first conventional example of a complex molecular pump using a method of joining a disk portion and a main shaft.
FIG. 5 is a longitudinal sectional view of a second conventional example of a method for joining a disk portion and a main shaft.
FIG. 6 is a longitudinal sectional view of a third conventional example of a method for joining a disk portion and a main shaft.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1
Claims (4)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10617999A JP4404986B2 (en) | 1999-04-14 | 1999-04-14 | Spindle joint structure of high-speed rotor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10617999A JP4404986B2 (en) | 1999-04-14 | 1999-04-14 | Spindle joint structure of high-speed rotor |
Publications (2)
Publication Number | Publication Date |
---|---|
JP2000297782A JP2000297782A (en) | 2000-10-24 |
JP4404986B2 true JP4404986B2 (en) | 2010-01-27 |
Family
ID=14427022
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP10617999A Expired - Lifetime JP4404986B2 (en) | 1999-04-14 | 1999-04-14 | Spindle joint structure of high-speed rotor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP4404986B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102720679A (en) * | 2012-05-29 | 2012-10-10 | 苏州市太湖风机制造有限公司 | Stably operating fan |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7717684B2 (en) * | 2003-08-21 | 2010-05-18 | Ebara Corporation | Turbo vacuum pump and semiconductor manufacturing apparatus having the same |
KR101532820B1 (en) | 2010-02-16 | 2015-06-30 | 가부시키가이샤 시마쓰세사쿠쇼 | Vacuum pump |
CN102242728A (en) * | 2011-06-30 | 2011-11-16 | 常州市西城减速机有限公司 | Anti-flying transmission shaft |
JP6606365B2 (en) * | 2015-07-09 | 2019-11-13 | エドワーズ株式会社 | Vacuum pump and its rotor and rotor shaft |
-
1999
- 1999-04-14 JP JP10617999A patent/JP4404986B2/en not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102720679A (en) * | 2012-05-29 | 2012-10-10 | 苏州市太湖风机制造有限公司 | Stably operating fan |
CN102720679B (en) * | 2012-05-29 | 2015-05-13 | 苏州市太湖风机制造有限公司 | Stably operating fan |
Also Published As
Publication number | Publication date |
---|---|
JP2000297782A (en) | 2000-10-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP4339782B2 (en) | Fixing device for fixing the impeller to the shaft | |
US6896479B2 (en) | Turbocharger rotor | |
JP4705570B2 (en) | Wheel hub / Rotating joint / Assembly | |
JPS63184501A (en) | Wheel bearing/synchronous rotary joint unit | |
JP4404986B2 (en) | Spindle joint structure of high-speed rotor | |
JP2002519564A (en) | Turbomachine rotor | |
US6663343B1 (en) | Impeller mounting system and method | |
JPH06257669A (en) | Support structure for friction coupling drum | |
JP4905953B2 (en) | Flanged hub | |
JPS60129412A (en) | Press-in pin | |
JP4736092B2 (en) | Disc brake rotor | |
JPS5835203A (en) | Bucket locking mechanism | |
JP2001200701A (en) | Turbine rotor blade and coupling method therefor | |
JP2006523802A (en) | Self-locking nut and stack wheel assembly for rotor shaft stud shaft | |
JPS6248472B2 (en) | ||
JPH11325022A (en) | Fastening structure of low cycle fatigue service life parts | |
JPS6162618A (en) | Rotating body fixing tool | |
KR102119259B1 (en) | Wheel bearing assembly | |
JP2569318Y2 (en) | Floating brake disc | |
US20240011545A1 (en) | Welded torque converter component | |
JPS61104102A (en) | Rotor of gas bearing-supported turbo machine | |
JP3062558B2 (en) | Elastic joint | |
CN114382723A (en) | Fan with rotor and fan impeller | |
JP2001173597A (en) | Shaft fastening part of centrifugal impeller | |
JPH01153820A (en) | Fixing tool for rotary body |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20060410 |
|
A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20080825 |
|
A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20080827 |
|
A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20081008 |
|
A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20090413 |
|
A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20090708 |
|
A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20090708 |
|
A911 | Transfer to examiner for re-examination before appeal (zenchi) |
Free format text: JAPANESE INTERMEDIATE CODE: A911 Effective date: 20090807 |
|
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: 20091006 |
|
A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20091104 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20121113 Year of fee payment: 3 |
|
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: 20131113 Year of fee payment: 4 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
S531 | Written request for registration of change of domicile |
Free format text: JAPANESE INTERMEDIATE CODE: R313531 |
|
R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
EXPY | Cancellation because of completion of term |