JPS62148102A - Main spindle device - Google Patents
Main spindle deviceInfo
- Publication number
- JPS62148102A JPS62148102A JP28810885A JP28810885A JPS62148102A JP S62148102 A JPS62148102 A JP S62148102A JP 28810885 A JP28810885 A JP 28810885A JP 28810885 A JP28810885 A JP 28810885A JP S62148102 A JPS62148102 A JP S62148102A
- Authority
- JP
- Japan
- Prior art keywords
- main spindle
- channels
- bearing
- silicon nitride
- linear expansion
- 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.)
- Pending
Links
Landscapes
- Turning (AREA)
- Sliding-Contact Bearings (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は超精密研削盤等に使用する主軸装置、特に主軸
を静圧軸受により支持してなる主軸装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a spindle device used in an ultra-precision grinder or the like, and particularly to a spindle device in which the spindle is supported by a hydrostatic bearing.
この種の静圧軸受を用いた主軸装置は、軸受の支持剛性
が大であるので外力による主軸の変位が少なく、従って
精度の高い主軸装置を得ることができる。また、主軸の
回転に伴う軸受面付近の発熱等により主軸が膨張して変
位するのを減少させるために、主軸の本体部を通常の鋼
材よりも線膨張係数の小さいセラミックスにより形成し
たものもあるが、静圧軸受メタルとしては、砲金等の通
常の材料が使用されていた。In a spindle device using this type of hydrostatic bearing, the support rigidity of the bearing is high, so the displacement of the spindle due to external force is small, and therefore a highly accurate spindle device can be obtained. In addition, in order to reduce expansion and displacement of the spindle due to heat generation near the bearing surface as the spindle rotates, the main body of the spindle is sometimes made of ceramic, which has a smaller coefficient of linear expansion than ordinary steel. However, ordinary materials such as gunmetal were used for the hydrostatic bearing metal.
しかしながら、セラミックスと砲金では線膨張係数の差
が大であるので温度変化により軸受すきまが大幅に変化
し、焼付きを考慮すると軸受すきまを充分に小さくする
ことができず、このため軸受の支持剛性の向上による主
軸装置の精度の向上に限界が生ずるという問題があった
。本発明は主軸の本体部と静圧軸受メタルの材質を適切
に選定して上記問題を解決したものである。However, since there is a large difference in the coefficient of linear expansion between ceramics and gunmetal, the bearing clearance changes significantly due to temperature changes, and it is not possible to reduce the bearing clearance sufficiently when seizure is taken into consideration. There has been a problem in that there is a limit to the improvement in accuracy of the spindle device due to improvement in . The present invention solves the above problems by appropriately selecting the materials of the main shaft body and the hydrostatic bearing metal.
このために、本発明よる主軸装置は、添付図面に例示す
る如く、主軸台１１に固定され支持面２０ａ、２０ｂ、
２１ａ、３０ａに円周方向に複数の静圧ポケット２２．
３１を形成した静圧軸受メタル２０，２１．３０と、前
記支持面２０ａ、２０ｂ、２１ａ、３０ａにより回転自
在に支持された主軸４０を備えてなる主軸装置において
、前記主軸４０の主要部をなし前記支持面２０ａ、２０
ｂ、２１ａ、３０ａに支持される本体部４１は窒化珪素
系セラミックスにより形成され、前記静圧軸受メタル２
０，２１．３０はニッケル含有量を調整して線膨張係数
を前記窒化珪素系セラミックスの線膨張係数とほぼ同一
としたニレジスト系鋳鉄により形成したことを特徴とす
るものである。For this purpose, the spindle device according to the present invention is fixed to the spindle stock 11 and has support surfaces 20a, 20b,
A plurality of static pressure pockets 22.21a, 30a circumferentially.
31, and a main shaft 40 rotatably supported by the supporting surfaces 20a, 20b, 21a, 30a, the main part of the main shaft 40 is The support surfaces 20a, 20
b, 21a, and 30a is formed of silicon nitride-based ceramics, and is supported by the hydrostatic bearing metal 2.
No. 0,21.30 is characterized by being made of Niresist cast iron whose linear expansion coefficient is approximately the same as that of the silicon nitride ceramic by adjusting the nickel content.
主軸４０が回転すれば、その本体部４１と各支持面２０
ａ、 ２０ ｂ、 ２１ ａ、 ３０ ａの間
には潤滑油の流体摩擦等による発熱が生じ、本体部４１
及び静圧軸受メタル２０．２１．３０の温度は上昇する
。この温度上昇により本体部４工及び静圧軸受メタル２
０，２１．３０は共に熱膨張するが、この両者をそれぞ
れ形成する窒化珪素系セラミックスとニレジスト系鋳鉄
とは線膨張係数かはソ同一であるので軸受すきまは殆ど
変化しない。When the main shaft 40 rotates, its main body 41 and each support surface 20
A, 20 b, 21 a, and 30 a generate heat due to fluid friction of lubricating oil, etc., and the main body part 41
And the temperature of the hydrostatic bearing metal 20.21.30 increases. Due to this temperature rise, the main body part 4 and the hydrostatic bearing metal 2
0 and 21.30, both undergo thermal expansion, but the silicon nitride ceramics and Niresist cast iron that form them respectively have the same coefficient of linear expansion, so the bearing clearance hardly changes.
上述の如く、本発明による主軸装置は温度変化による軸
受すきまの変化が殆どないので、この軸受すきまの変化
による焼付きを考慮することなく軸受すきまを必要最低
限の値に設定することができる。従って、軸受の支持剛
性を最大に高めることができ、主軸及び静圧軸受メタル
の線膨張係数が小さいことと相まって、外力や温度変化
による変位が少ない高精度の主軸装置を得ることができ
る。As described above, in the spindle device according to the present invention, the bearing clearance hardly changes due to temperature changes, so the bearing clearance can be set to the minimum necessary value without considering seizure caused by changes in the bearing clearance. Therefore, the support rigidity of the bearing can be maximized, and this combined with the small coefficient of linear expansion of the main shaft and hydrostatic bearing metal makes it possible to obtain a highly accurate main shaft device with little displacement due to external forces or temperature changes.
以下に、添付図面に示す実施例の説明をする。 The embodiments shown in the accompanying drawings will be described below.
図示の如（、ベッド１０上に設置された主軸台１１には
３個の静圧軸受メタル２０． ２１． ３０が同軸に固
定され、此等の静圧軸受メタル２０゜２１．３０により
主軸４０が回転自在に支持されている。主軸４０は、そ
の左端には砥石取付板４８を介して砥石車４９が固定さ
れ、右端部に設けたビルトインモータ１５により回転駆
動される。As shown in the figure (three hydrostatic bearing metals 20, 21, 30 are coaxially fixed to the headstock 11 installed on the bed 10, and the main shaft 40 is A grinding wheel 49 is fixed to the left end of the main shaft 40 via a grinding wheel mounting plate 48, and the main shaft 40 is rotationally driven by a built-in motor 15 provided at the right end.
主軸４０の主要部は窒化珪素系セラミックス（線膨張係
数：３〜４．５ ｘ １０−′／”ｃ）からなり中央に
フランジ部４１ａが形成された本体部４１であり、主軸
４０はこの本体部４１と、その左右端の凹部に接着固定
された鉄製の結合部材４２．４３と、本体部４１の軸方
向貫通孔を通りスラスト軸受４５を介して両結合部材４
２．４３を締着する締付ボルト４４により構成されてい
る。砥石取付板４８は左端の結合部材４２にボルト止め
されている。The main part of the main shaft 40 is a main body part 41 made of silicon nitride ceramics (linear expansion coefficient: 3 to 4.5 x 10-'/''c) and has a flange part 41a formed in the center. 41 , iron connecting members 42 and 43 adhesively fixed to the recesses at the left and right ends, and both connecting members 4 passing through the axial through hole of the main body 41 and via the thrust bearing 45 .
2.43 is constituted by a tightening bolt 44. The grindstone mounting plate 48 is bolted to the coupling member 42 at the left end.
第１静圧軸受メタル２０は主軸台１１の左側に嵌合固定
され、その内周に形成された円筒状のラジアル支持面２
０ａには、円周方向に間をおいて複数の静圧ボケッ）２
２（１個のみを図示）が形成され、また各静圧ポケット
２２の間には排出溝２３（ＩＩＩＩのみを図示）が形成
されている。ラジアル支持面２０ａ内には僅かの軸受す
きまをおいて主軸４０の本体部４１の外周面が嵌合され
、潤滑油ポンプ（図示せず）からの加圧潤滑油が第１静
圧軸受メタル２０の外周に設けられた環状溝２４、絞り
２５及び油路２６を介して各静圧ポケット２２に供給さ
れ、主軸４０の本体部４１を回転自在に静圧支持してい
る。主軸台１１の右側には、ラジアル支持面２１ａ、静
圧ポケット２２及び排出溝２３を有する第２静圧軸受メ
タル２１が、第１静圧軸受メタル２０と同軸に嵌合固定
され、第１静圧軸受メタル２０と同様、各静圧ポケット
２２には環状溝２４．絞り２５及び油路２６を介して加
圧潤滑油が供給されて、本体部４１を回転自在に静圧支
持している。The first hydrostatic bearing metal 20 is fitted and fixed on the left side of the headstock 11, and has a cylindrical radial support surface 2 formed on its inner circumference.
0a has a plurality of static pressure holes spaced apart in the circumferential direction)2
2 (only one is shown), and a discharge groove 23 (only III is shown) is formed between each static pressure pocket 22. The outer peripheral surface of the main body portion 41 of the main shaft 40 is fitted into the radial support surface 20a with a slight bearing clearance, and pressurized lubricating oil from a lubricating oil pump (not shown) is applied to the first hydrostatic bearing metal 20. It is supplied to each static pressure pocket 22 through an annular groove 24, a throttle 25, and an oil passage 26 provided on the outer periphery of the main shaft 40, and supports the main body portion 41 of the main shaft 40 with static pressure so as to be rotatable. On the right side of the headstock 11, a second static pressure bearing metal 21 having a radial support surface 21a, a static pressure pocket 22, and a discharge groove 23 is fitted and fixed coaxially with the first static pressure bearing metal 20. Similar to the pressure bearing metal 20, each static pressure pocket 22 has an annular groove 24. Pressurized lubricating oil is supplied through the throttle 25 and the oil passage 26, and the main body 41 is rotatably supported under static pressure.
第１静圧軸受メタル２０の右端には第３静圧軸受メタル
３０が固定され、両静圧軸受メタル２０゜３０の間には
、主軸４０の本体部４１に形成されたフランジ部４１ａ
の両側面を僅かの軸受すきまをおいて挟持するスラスト
支持面２０ｂ、３０ａが形成されている。各スラスト支
持面２０ｂ、３０ａには円周方向に間をおいて複数の静
圧ボケット３１ （１個のみを図示）がそれぞれ形成さ
れ、また各静圧ポケット３１の間には排出溝３２ （１
個のみを図示）がそれぞれ形成されている。各静圧ボケ
ッ１−３１．３１には第１静圧軸受メタル２０の環状溝
２４からこれに連通された油路３３゜３４．３４及び絞
り３５．３５を経て加圧潤滑油が供給され、主軸４０の
本体部４１をフランジ部４１ａを介して幅方向移動不能
にかつ回転自在に静圧支持している。A third static pressure bearing metal 30 is fixed to the right end of the first static pressure bearing metal 20, and a flange portion 41a formed on the main body portion 41 of the main shaft 40 is located between the two static pressure bearing metals 20°30.
Thrust support surfaces 20b and 30a are formed to sandwich both side surfaces of the bearing with a slight bearing gap. A plurality of static pressure pockets 31 (only one is shown) are formed on each thrust support surface 20b, 30a at intervals in the circumferential direction, and discharge grooves 32 (one
(only one of which is shown in the figure) is formed respectively. Pressurized lubricating oil is supplied to each static pressure socket 1-31.31 from the annular groove 24 of the first static pressure bearing metal 20 through an oil passage 33° 34.34 and a throttle 35.35 communicating therewith, The main body portion 41 of the main shaft 40 is supported by static pressure via a flange portion 41a so as to be immovable in the width direction and rotatable.
各静圧軸受メタル２０．２１．３０はニッケルを含有す
るニレジスト系鋳鉄により形成されてい−る。ニレジス
ト系鋳鉄の線膨張係数は３〜５×１０−′／’Ｃである
が、その値はニッケルの含有量を調整して変えることが
でき、本発明においては、この調整によりその線膨張係
数を、主軸４０の本体部４１を形成する窒化珪素系セラ
ミックスの線膨張係数とはり同一としたものである。Each hydrostatic bearing metal 20, 21, 30 is made of nickel-containing cast iron. The coefficient of linear expansion of Niresist cast iron is 3 to 5 × 10-'/'C, but this value can be changed by adjusting the nickel content. is made to be the same as the coefficient of linear expansion of the silicon nitride ceramic forming the main body portion 41 of the main shaft 40.
本主軸装置の作動に際しては、各静圧軸受メタル２０．
２１．３０の支持面２０ａ、２０ｂ、２１ａ＋ ３０
ａの単位時間当りの発熱量は主軸４０の回転速度のはソ
゛自乗に比例して増大し、これに応じて主軸４０の本体
部４１及び各静圧軸受メタル２０，２１．３０の温度は
上昇する。この温度上昇により本体部４１及び各静圧軸
受メタル２０゜２１．３０は共に熱膨張するが、この両
者をそれぞれ形成する窒化珪素系セラミックスとニレジ
スト系鋳鉄とは線膨張係数が共に小さいので熱膨張を小
さく抑えることができる。しかも両者の線膨張係数がは
り同一であるので軸受すきまは殆ど変化しない。従って
成る温度において軸受すきまを必要最低限の値に設定す
れば、温度が変化しても軸受すきまが増大して支持剛性
が低下したり、あるいは軸受すきまが減少して本体部４
１と支持面２０ａ、２０ｂ、２１ａ、３０ａとが直接接
触・して焼付きを生じたりすることがない。When operating this spindle device, each hydrostatic bearing metal 20.
21.30 support surfaces 20a, 20b, 21a+ 30
The amount of heat generated per unit time a increases in proportion to the square of the rotational speed of the main shaft 40, and the temperature of the main body 41 of the main shaft 40 and each of the hydrostatic bearing metals 20, 21, 30 rises accordingly. do. Due to this temperature rise, both the main body part 41 and each of the hydrostatic bearing metals 20, 21, and 30 expand thermally, but the silicon nitride ceramics and Niresist cast iron that make up both have small coefficients of linear expansion, so they expand thermally. can be kept small. Moreover, since the linear expansion coefficients of both are the same, the bearing clearance hardly changes. Therefore, if the bearing clearance is set to the minimum necessary value at the temperature, the bearing clearance will increase and the support rigidity will decrease even if the temperature changes, or the bearing clearance will decrease and the main body
1 and the supporting surfaces 20a, 20b, 21a, and 30a do not come into direct contact and cause seizure.
なお、上記実施例においては、ラジアル軸受部及びスラ
スト軸受部の両方に本発明を実施した主軸装置につき説
明したが、本発明はラジアル軸受部のみに、あるいはス
ラスト軸受部のみに実施することも可能である。In addition, in the above embodiment, a main shaft device in which the present invention is applied to both the radial bearing portion and the thrust bearing portion is explained, but the present invention can also be implemented only to the radial bearing portion or only to the thrust bearing portion. It is.
添付図面は本発明による主軸装置の一実施例の縦断面図
である。
符号の説明
１１・・・主軸台、２０，２１．３０・・・静圧軸受メ
タル、２０ａ、２１ａ・・・支持面（ラジアル支持面）
、２０ｂ、３０ａ・・・支持面（スラスト支持面）、２
２．３１・・・静圧ポケット、４０・・・主軸、４１・
・・本体部。The accompanying drawing is a longitudinal sectional view of an embodiment of the spindle device according to the present invention. Explanation of symbols 11... Headstock, 20, 21. 30... Hydrostatic bearing metal, 20a, 21a... Support surface (radial support surface)
, 20b, 30a... support surface (thrust support surface), 2
2.31...Static pressure pocket, 40...Main shaft, 41.
・Body part.
Claims (1)
トを形成した静圧軸受メタルと、前記支持面により回転
自在に支持された主軸を備えてなる主軸装置において、
前記主軸の主要部をなし前記支持面に支持される本体部
は窒化珪素系セラミックスにより形成され、前記静圧軸
受メタルはニッケル含有量を調整して線膨張係数を前記
窒化珪素系セラミックスの線膨張係数とほぼ同一とした
ニレジスト系鋳鉄により形成したことを特徴とする主軸
装置。A spindle device comprising a hydrostatic bearing metal fixed to a spindle stock and having a plurality of static pressure pockets formed in a circumferential direction on a support surface, and a spindle rotatably supported by the support surface,
The main body, which forms the main part of the main shaft and is supported by the support surface, is formed of silicon nitride ceramics, and the hydrostatic bearing metal has a linear expansion coefficient of the silicon nitride ceramics by adjusting the nickel content. A spindle device characterized in that it is made of Niresist cast iron with almost the same coefficient.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28810885A JPS62148102A (en) | 1985-12-20 | 1985-12-20 | Main spindle device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28810885A JPS62148102A (en) | 1985-12-20 | 1985-12-20 | Main spindle device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62148102A true JPS62148102A (en) | 1987-07-02 |
Family
ID=17725903
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28810885A Pending JPS62148102A (en) | 1985-12-20 | 1985-12-20 | Main spindle device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62148102A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61252912A (en) * | 1985-04-30 | 1986-11-10 | Mazda Motor Corp | Crankshaft bearing structure in engine |
| JPS6338903U (en) * | 1986-08-27 | 1988-03-12 | ||
| JPH01171922U (en) * | 1988-05-24 | 1989-12-06 | ||
| EP0779127A1 (en) * | 1995-11-24 | 1997-06-18 | Toyoda Koki Kabushiki Kaisha | Grinding spindle with hydrostatic bearings |
| CN102661323A (en) * | 2012-05-17 | 2012-09-12 | 焦正玉 | Hydrostatic bearing |
| CN102979816A (en) * | 2011-09-05 | 2013-03-20 | 株式会社安川电机 | Main shaft device |
| JP2014037051A (en) * | 2012-08-20 | 2014-02-27 | Liebherr-Verzahntechnik Gmbh | Tool device and machining center |
| JP2016138607A (en) * | 2015-01-28 | 2016-08-04 | 株式会社ジェイテクト | Thrust support device of operation member and machine tool having support device |
| CN105952797A (en) * | 2016-03-22 | 2016-09-21 | 宁波圣圭精工科技有限公司 | Static-pressure spindle |
| CH711186A1 (en) * | 2015-06-15 | 2016-12-15 | Reishauer Ag | A spindle unit for a machine tool for the fine machining of workpieces with groove-shaped profiles. |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56139848A (en) * | 1980-03-27 | 1981-10-31 | Makino Milling Mach Co Ltd | Spindle device for machine tool |
| JPS60179520A (en) * | 1984-02-24 | 1985-09-13 | Eguro Tekkosho:Kk | Bearing of machine tool and its forming method |
-
1985
- 1985-12-20 JP JP28810885A patent/JPS62148102A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56139848A (en) * | 1980-03-27 | 1981-10-31 | Makino Milling Mach Co Ltd | Spindle device for machine tool |
| JPS60179520A (en) * | 1984-02-24 | 1985-09-13 | Eguro Tekkosho:Kk | Bearing of machine tool and its forming method |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61252912A (en) * | 1985-04-30 | 1986-11-10 | Mazda Motor Corp | Crankshaft bearing structure in engine |
| JPS6338903U (en) * | 1986-08-27 | 1988-03-12 | ||
| JPH01171922U (en) * | 1988-05-24 | 1989-12-06 | ||
| JPH0536094Y2 (en) * | 1988-05-24 | 1993-09-13 | ||
| EP0779127A1 (en) * | 1995-11-24 | 1997-06-18 | Toyoda Koki Kabushiki Kaisha | Grinding spindle with hydrostatic bearings |
| US5833522A (en) * | 1995-11-24 | 1998-11-10 | Toyoda Koki Kabushiki Kaisha | Machining spindle apparatus having a hydrostatic bearing for machine tools |
| CN102979816A (en) * | 2011-09-05 | 2013-03-20 | 株式会社安川电机 | Main shaft device |
| CN102661323A (en) * | 2012-05-17 | 2012-09-12 | 焦正玉 | Hydrostatic bearing |
| CN102661323B (en) * | 2012-05-17 | 2015-09-16 | 焦正玉 | A kind of hydrostatic bearing |
| JP2014037051A (en) * | 2012-08-20 | 2014-02-27 | Liebherr-Verzahntechnik Gmbh | Tool device and machining center |
| JP2016138607A (en) * | 2015-01-28 | 2016-08-04 | 株式会社ジェイテクト | Thrust support device of operation member and machine tool having support device |
| CH711186A1 (en) * | 2015-06-15 | 2016-12-15 | Reishauer Ag | A spindle unit for a machine tool for the fine machining of workpieces with groove-shaped profiles. |
| WO2016202598A3 (en) * | 2015-06-15 | 2017-02-16 | Reishauer Ag | Spindle unit for a machine tool for fine-machining workpieces that have grooved-shaped profiles |
| CN105952797A (en) * | 2016-03-22 | 2016-09-21 | 宁波圣圭精工科技有限公司 | Static-pressure spindle |
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