JPH08145053A - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JPH08145053A JPH08145053A JP6288506A JP28850694A JPH08145053A JP H08145053 A JPH08145053 A JP H08145053A JP 6288506 A JP6288506 A JP 6288506A JP 28850694 A JP28850694 A JP 28850694A JP H08145053 A JPH08145053 A JP H08145053A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- ball bearing
- ball
- outer ring
- axial direction
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
- F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、ガスタービンやター
ボチャージャ等の高速回転軸に用いられる軸受装置の改
良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a bearing device used for a high speed rotating shaft such as a gas turbine or a turbocharger.
【０００２】[0002]
【従来の技術】ガスタービン等の高速回転軸の軸受装置
として従来から一対の玉軸受を用いたスクイズフィルム
ダンパ式の軸受装置が知られている。2. Description of the Related Art A squeeze film damper type bearing device using a pair of ball bearings has been conventionally known as a bearing device for a high-speed rotating shaft such as a gas turbine.
【０００３】図８は、本出願人が先に提案した特開平６
−１１７４３４号公報記載の軸受装置を示すもので、ガ
スタービン発電機３１の回転軸３２が一対の玉軸受３
３，３４でもって軸受ハウジング３５に回転自在に支持
されているとともに、回転軸３２にロータ３６が取り付
けられ、かつ該ロータ３６外周を囲むように軸受ハウジ
ング３５側にステータ４１が取り付けられている。FIG. 8 is a diagram of Japanese Patent Laid-Open No. Hei 6 (1994) proposed by the present applicant.
Fig. 1 shows a bearing device described in JP-A-117434, in which a rotating shaft 32 of a gas turbine generator 31 has a pair of ball bearings 3;
3, 34 are rotatably supported by the bearing housing 35, the rotor 36 is attached to the rotary shaft 32, and the stator 41 is attached to the bearing housing 35 side so as to surround the outer circumference of the rotor 36.
【０００４】ここで、上記玉軸受３３，３４は、内輪の
軌道の逆与圧側に分離防止用肩を有する非分離型アンギ
ュラ玉軸受からなり、かつ、それぞれの正与圧側肩が互
いに外側となるように配置されている。そして、各玉軸
受３３，３４の内輪３３ｂ，３４ｂは、回転軸３２に軸
方向に固定してある。Here, the ball bearings 33, 34 are non-separable angular ball bearings having a separation preventing shoulder on the reverse pressurizing side of the race of the inner ring, and the respective positive pressurizing side shoulders are on the outside. Are arranged as follows. The inner rings 33b and 34b of the ball bearings 33 and 34 are fixed to the rotary shaft 32 in the axial direction.
【０００５】また一方の玉軸受３３の外輪３３ａは、ダ
ンパスリーブ３７を介して軸受ハウジング３５に保持さ
れている。このダンパスリーブ３７は径方向に微動し得
るようになっており、油膜を介して外輪３３ａを保持し
ているが、軸方向については外輪３３ａは実質的に固定
されている。また他方の玉軸受３４の外輪３４ａは、ダ
ンパスリーブ３８を介して軸受ハウジング３５に保持さ
れている。このダンパスリーブ３８は、ダンパスリーブ
３７と同様に径方向に微動し得るようになっており、油
膜を介して外輪３４ａを保持している。そして、この外
輪３４ａを保持するダンパスリーブ３８は、軸方向に移
動可能となっており、かつ与圧用スプリング３９によっ
て外側に付勢されている。また、図９に詳示するよう
に、この玉軸受３４の転動体３４ｃに潤滑油を供給する
ノズル部４０が、軸受３４の内側に配置されている。The outer ring 33a of the other ball bearing 33 is held in the bearing housing 35 via a damper sleeve 37. The damper sleeve 37 is adapted to be capable of fine movement in the radial direction and holds the outer ring 33a through an oil film, but the outer ring 33a is substantially fixed in the axial direction. The outer ring 34 a of the other ball bearing 34 is held by the bearing housing 35 via a damper sleeve 38. Like the damper sleeve 37, the damper sleeve 38 can be slightly moved in the radial direction, and holds the outer ring 34a via an oil film. The damper sleeve 38 holding the outer ring 34a is movable in the axial direction and is biased outward by the pressurizing spring 39. Further, as shown in detail in FIG. 9, a nozzle portion 40 for supplying lubricating oil to the rolling elements 34 c of the ball bearing 34 is arranged inside the bearing 34.
【０００６】[0006]
【発明が解決しようとする課題】上記従来の構成におい
ては、ロータ３６の軸方向の動きは、両玉軸受３３，３
４のほかに、上記ノズル部４０がダンパスリーブ３８と
当接することによっても規制されるが、図９に示すよう
に、ノズル部４０とダンパスリーブ３８との間には、軸
方向に比較的大きな間隙ｔが存在するので、この軸受装
置を備えたガスタービン発電機を輸送する際に受ける衝
撃や、何らかの物がぶつかった際の衝撃などによってロ
ータ３６が図８の右方向へ移動し、一方の軸受３３の転
動体３３ｃを傷つけるという問題がある。つまり、外輪
３３ａと内輪３３ｂとが相対的に軸方向へずれる結果、
転動体３３ｃが軌道から外れて分離防止用肩に強く衝突
し、傷ついてしまうのであり、これによって、玉軸受３
３の寿命が低下するおそれがある。In the above-mentioned conventional structure, the axial movement of the rotor 36 causes the double ball bearings 33, 3 to move.
4, the nozzle portion 40 is also regulated by abutting against the damper sleeve 38. However, as shown in FIG. 9, a relatively large axial distance exists between the nozzle portion 40 and the damper sleeve 38. Since the gap t exists, the rotor 36 moves to the right in FIG. 8 due to an impact received when the gas turbine generator including this bearing device is transported, an impact caused when something hits the rotor 36, or the like. There is a problem that the rolling element 33c of the bearing 33 is damaged. That is, as a result of the outer ring 33a and the inner ring 33b being relatively displaced in the axial direction,
The rolling element 33c is disengaged from the raceway and collides strongly with the separation preventing shoulder, and is damaged, so that the ball bearing 3
3 may shorten the life.
【０００７】[0007]
【課題を解決するための手段】そこで、請求項１の発明
は、内輪の逆与圧側に分離防止用肩を有する一対の非分
離型アンギュラ玉軸受を、それぞれの正与圧側肩が互い
に外側となるように配置するとともに、各玉軸受の内輪
を回転部品の軸に軸方向に固定し、かつ第１の玉軸受の
外輪を軸受箱に軸方向に固定し、第２の玉軸受の外輪を
軸受箱に軸方向に移動可能に保持し、これらの一対の玉
軸受でもって上記回転部品を回転自在に支持するように
した軸受装置において、上記第１の玉軸受のアキシャル
すきまよりも回転部品の軸方向の移動可能量が小さくな
るように、回転部品と軸受箱側の各部との間の軸方向の
最も小さな間隙を上記アキシャルすきまより小さく設定
したことを特徴としている。Therefore, the invention of claim 1 provides a pair of non-separable angular contact ball bearings having separation preventing shoulders on the reverse pressurizing side of the inner ring, wherein the respective positive pressurizing side shoulders are on the outside. And the inner ring of each ball bearing is fixed axially to the shaft of the rotating component, the outer ring of the first ball bearing is fixed axially to the bearing housing, and the outer ring of the second ball bearing is fixed. In a bearing device which is movably held in a bearing box in an axial direction and rotatably supports the rotary component by a pair of these ball bearings, the rotary component of the rotary component is more than the axial clearance of the first ball bearing. It is characterized in that the smallest axial gap between the rotary component and each part on the bearing housing side is set to be smaller than the axial clearance so that the movable amount in the axial direction becomes small.
【０００８】また請求項２の発明は、同様の軸受装置に
おいて、上記第１の玉軸受のアキシャルすきまよりも回
転部品の軸方向の移動可能量が小さくなるように、上記
第２の玉軸受の外輪側の一部と軸受箱側の一部との軸方
向の間隙を上記アキシャルすきまより小さく設定したこ
とを特徴としている。According to a second aspect of the present invention, in the same bearing device, the axial movement of the rotating component is smaller than the axial clearance of the first ball bearing, so that the second ball bearing has a smaller movable amount. It is characterized in that an axial gap between a part of the outer ring side and a part of the bearing box side is set smaller than the axial clearance.
【０００９】また請求項３の発明は、同様の軸受装置に
おいて、上記第１の玉軸受のアキシャルすきまをｔ１、
上記第２の玉軸受の外輪側の一部と軸受箱側の一部との
軸方向の間隙をｔ２、回転部品と軸受箱側の各部との間
の軸方向の最も小さな間隙をｔ３としたときに、ｔ２＜
ｔ３＜ｔ１となるように、各間隙を設定したことを特徴
としている。According to a third aspect of the present invention, in the same bearing device, the axial clearance of the first ball bearing is t1,
The axial gap between the outer ring side part and the bearing box side part of the second ball bearing is t2, and the smallest axial gap between the rotating parts and the bearing box side part is t3. Sometimes t2 <
Each of the gaps is set so that t3 <t1.
【００１０】また請求項４の発明では、上記第２の玉軸
受の外輪が与圧用スプリングでもって第１の玉軸受から
離間する方向へ付勢されている。Further, in the invention of claim 4, the outer ring of the second ball bearing is biased by the pressurizing spring in a direction away from the first ball bearing.
【００１１】さらに請求項５の発明では、上記各玉軸受
の外輪が油膜を介して軸受箱に支持されるスクイズフィ
ルムダンパ式の軸受装置となっている。Further, in the invention of claim 5, there is provided a squeeze film damper type bearing device in which the outer ring of each of the ball bearings is supported by the bearing box through an oil film.
【００１２】[0012]
【作用】請求項１の発明では、回転部品が軸方向へ移動
しようとした際に、該回転部品と軸受箱側の一部とが干
渉することにより、軸方向の移動量が上記第１の玉軸受
のアキシャルすきまより小さく抑制される。そのため、
転動体が分離防止用肩に衝突することがない。According to the first aspect of the invention, when the rotating component tries to move in the axial direction, the rotating component interferes with a part of the bearing box side, so that the moving amount in the axial direction is the same. It is suppressed to be smaller than the axial clearance of the ball bearing. for that reason,
The rolling element does not collide with the separation preventing shoulder.
【００１３】また請求項２の発明では、回転部品が軸方
向へ移動しようとした際に、第２の玉軸受の外輪側の一
部と軸受箱側の一部とが干渉することにより、同様に、
回転部品の軸方向の移動量が上記第１の玉軸受のアキシ
ャルすきまより小さく抑制される。そのため、転動体が
分離防止用肩に衝突することがない。According to the second aspect of the present invention, when the rotary component tries to move in the axial direction, a part of the outer ring side of the second ball bearing and a part of the bearing box side interfere with each other. To
The amount of movement of the rotary component in the axial direction is suppressed to be smaller than the axial clearance of the first ball bearing. Therefore, the rolling element does not collide with the separation preventing shoulder.
【００１４】また請求項３の発明では、同じく回転部品
が軸方向へ移動しようとした際に、該回転部品と軸受箱
側の一部、あるいは第２の玉軸受の外輪側の一部と軸受
箱側の一部とが干渉することにより、回転部品の軸方向
の移動量が上記第１の玉軸受のアキシャルすきまより小
さく抑制される。しかも、その際に、後者の第２の玉軸
受の外輪側の一部と軸受箱側の一部とが優先的に干渉す
るので、高速回転中に衝撃が加わった場合でも、支障が
ない。According to the third aspect of the present invention, when the rotary component is about to move in the axial direction, the rotary component and a part of the bearing housing side, or the outer ring side of the second ball bearing and the bearing. Due to the interference with a part of the box side, the amount of axial movement of the rotary component is suppressed to be smaller than the axial clearance of the first ball bearing. Moreover, in that case, a part of the outer ring side of the latter second ball bearing and a part of the bearing box side preferentially interfere with each other, so that there is no problem even if a shock is applied during high speed rotation.
【００１５】請求項４の構成では、軸方向へ移動可能な
第２の玉軸受の外輪が与圧用スプリングでもって第１の
玉軸受から離間する方向へ付勢され、これによって両玉
軸受に与圧が付与される。According to the structure of claim 4, the outer ring of the second ball bearing which is movable in the axial direction is biased by the pressurizing spring in the direction away from the first ball bearing, thereby imparting to both ball bearings. Pressure is applied.
【００１６】また請求項５の構成では、各玉軸受の外輪
が油膜を介して支持され、回転軸の不釣り合いによる振
動が制振される。Further, according to the fifth aspect of the invention, the outer ring of each ball bearing is supported through the oil film, and the vibration due to the imbalance of the rotating shaft is suppressed.
【００１７】[0017]
【実施例】以下、この発明の一実施例を図面に基づいて
詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to the drawings.
【００１８】図１は、この発明の軸受装置が適用された
ガスタービン発電機を示しており、回転部品として一端
にタービン８を備えた回転軸２が、軸受箱となる軸受ハ
ウジング３に一対の玉軸受４，５でもって回転自在に支
持されている。回転軸２の両玉軸受４，５の間には発電
機ロータ１が固定され、かつ該発電機ロータ１を囲むよ
うに軸受ハウジング３ａ側にステータ６が設けられてい
る。回転軸２には、さらにカラー７を介してインペラ９
が取り付けられており、これらの各部品がロックナット
１０によって軸方向に固定されている。FIG. 1 shows a gas turbine generator to which the bearing device of the present invention is applied. A rotary shaft 2 having a turbine 8 at one end as a rotary component is mounted on a bearing housing 3 which serves as a bearing box. It is rotatably supported by ball bearings 4 and 5. A generator rotor 1 is fixed between the ball bearings 4 and 5 of the rotary shaft 2, and a stator 6 is provided on the bearing housing 3a side so as to surround the generator rotor 1. On the rotary shaft 2, an impeller 9 is further provided via a collar 7.
Are attached, and each of these parts is axially fixed by a lock nut 10.
【００１９】一対の玉軸受４，５は、図２および図３に
示すように、球状の転動体４ａ，５ａを有するアンギュ
ラ玉軸受からなり、それぞれの正与圧側肩１１が互いに
外側となるように配置されている。また、これらの玉軸
受４，５は、外輪４ｂ，５ｂの軌道の逆与圧側に分離防
止用肩１２を形成した非分離型の構成となっている。こ
れらの玉軸受４，５の内輪４ｃ，５ｃは、いずれも上記
回転軸２に上記ロックナット１０によって軸方向に固定
されている。As shown in FIGS. 2 and 3, the pair of ball bearings 4 and 5 are angular ball bearings having spherical rolling elements 4a and 5a, and their respective positive pressure side shoulders 11 are located outside each other. It is located in. Further, these ball bearings 4 and 5 have a non-separation type structure in which a separation preventing shoulder 12 is formed on the reverse pressurizing side of the races of the outer rings 4b and 5b. Inner rings 4c and 5c of these ball bearings 4 and 5 are axially fixed to the rotary shaft 2 by the lock nut 10.
【００２０】回転軸２のインペラ９側を支持する第１の
玉軸受４の外輪４ｂは、軸受ハウジング３の凹部内に油
膜１３を介して支持されるようになっているが、軸方向
については、その移動が規制されている。つまり、軸方
向には固定されている。なお、上記の油膜１３には、潤
滑油供給口１４から潤滑油通路１５を介して常に潤滑油
が供給される。The outer ring 4b of the first ball bearing 4 supporting the impeller 9 side of the rotary shaft 2 is supported in the recess of the bearing housing 3 through an oil film 13, but in the axial direction. , Its movement is regulated. That is, it is fixed in the axial direction. The lubricating oil is constantly supplied to the oil film 13 from the lubricating oil supply port 14 through the lubricating oil passage 15.
【００２１】ここで、第１の玉軸受４には、図２の
（ａ），（ｂ）に示すように、若干のアキシャルすきま
ｔ１が存在する。つまり、内輪４ｃを正スラスト方向に
押した際には、図２（ａ）のように内輪４ｃの端面と外
輪４ｂの端面とが一致するが、反スラスト方向に緩く押
すと、図２（ｂ）のように両者の端面がアキシャルすき
まｔ１だけずれることになる。この範囲内であれば、転
動体４ａが分離防止用肩１２に衝突して傷つくことはな
い。The first ball bearing 4 has a slight axial clearance t1 as shown in FIGS. 2 (a) and 2 (b). That is, when the inner ring 4c is pushed in the forward thrust direction, the end face of the inner ring 4c and the end face of the outer ring 4b coincide with each other as shown in FIG. 2A, but when pushed gently in the anti-thrust direction, FIG. ), The end faces of both are displaced by the axial clearance t1. Within this range, the rolling element 4a does not collide with the separation preventing shoulder 12 and get damaged.
【００２２】また回転軸２のロックナット１０側を支持
する第２の玉軸受５の外輪５ｂは、図３に示すように、
略円筒状をなすダンパスリーブ１６に嵌合している。そ
して、このダンパスリーブ１６が軸受ハウジング３の円
筒状軸受面に緩く嵌合して保持されており、その嵌合面
に油膜１７が形成されている。この油膜１７には、上記
潤滑油供給口１４から潤滑油通路１８を介して常に潤滑
油が供給される。なお、外輪５ｂとダンパスリーブ１６
との間に、さらに油膜を形成するようにしてもよい。ダ
ンパスリーブ１６は、軸受ハウジング３に対し軸方向に
摺動可能となっており、一端のフランジ部１６ａと軸受
ハウジング３との間に与圧用スプリング１９が圧縮状態
で配設されている。また、他端のスラスト係止片１６ｂ
が外輪５ｂの内側の端面に当接している。従って、この
第２の玉軸受５の外輪５ｂが第１の玉軸受４から離間す
る方向に常時付勢され、これによって両玉軸受４，５に
適宜な与圧が付与されている。The outer ring 5b of the second ball bearing 5 supporting the lock nut 10 side of the rotary shaft 2 is, as shown in FIG.
The damper sleeve 16 having a substantially cylindrical shape is fitted. The damper sleeve 16 is loosely fitted and held on the cylindrical bearing surface of the bearing housing 3, and an oil film 17 is formed on the fitting surface. Lubricating oil is constantly supplied to the oil film 17 from the lubricating oil supply port 14 through the lubricating oil passage 18. The outer ring 5b and the damper sleeve 16
An oil film may be further formed between and. The damper sleeve 16 is slidable in the axial direction with respect to the bearing housing 3, and a pressurizing spring 19 is arranged in a compressed state between the flange portion 16 a at one end and the bearing housing 3. Further, the thrust locking piece 16b at the other end
Is in contact with the inner end surface of the outer ring 5b. Therefore, the outer ring 5b of the second ball bearing 5 is constantly urged in the direction away from the first ball bearing 4, whereby an appropriate pressurization is applied to both ball bearings 4, 5.
【００２３】また第２の玉軸受５の内側の端面に沿って
軸受ハウジング３からノズル部２０が突出形成されてい
る。このノズル部２０は、転動体５ａへ向けて潤滑油を
噴出する潤滑油通路２１を有している。ここで、上記ノ
ズル部２０とスラスト係止片１６ｂの端面との間には、
軸方向に僅かな間隙ｔ２が確保されている。A nozzle portion 20 is formed so as to project from the bearing housing 3 along the inner end surface of the second ball bearing 5. The nozzle portion 20 has a lubricating oil passage 21 that ejects lubricating oil toward the rolling elements 5a. Here, between the nozzle portion 20 and the end surface of the thrust locking piece 16b,
A small gap t2 is secured in the axial direction.
【００２４】そして、第１の実施例においては、上記間
隙ｔ２が第１玉軸受４のアキシャルすきまｔ１より小さ
く設定されている。つまり、ｔ２＜ｔ１となっている。In the first embodiment, the gap t2 is set smaller than the axial clearance t1 of the first ball bearing 4. That is, t2 <t1.
【００２５】従って、この実施例の構成によれば、ガス
タービン発電機を輸送する際の振動による衝撃や、同発
電機を落とした場合の衝撃等によって、ロータ１等を備
えた回転軸２が軸方向に移動しようとしても、第２の玉
軸受５側のダンパスリーブ１６と軸受ハウジング３側の
ノズル部２０とが先に接触することにより、回転軸２の
移動量が第１の玉軸受４のアキシャルすきまｔ１より小
さく抑制される。そのため、第１の玉軸受４の転動体４
ａが分離防止用肩１２に衝突することがなく、転動体４
ａの損傷が防止される。Therefore, according to the structure of this embodiment, the rotary shaft 2 including the rotor 1 and the like is protected from the shock caused by the vibration when the gas turbine generator is transported, the shock caused when the generator is dropped, and the like. Even if an attempt is made to move in the axial direction, the damper sleeve 16 on the side of the second ball bearing 5 and the nozzle portion 20 on the side of the bearing housing 3 come into contact with each other first, so that the amount of movement of the rotary shaft 2 becomes smaller than that of the first ball bearing 4. Is smaller than the axial clearance t1. Therefore, the rolling element 4 of the first ball bearing 4
a does not collide with the separation preventing shoulder 12, and the rolling element 4
Damage to a is prevented.
【００２６】次に、図４は、この発明の第２実施例を示
している。この実施例は、回転軸２に軸方向に固定され
ているカラー７のフランジ部７ａと該フランジ部７ａに
対向する軸受ハウジング３の段部との間の軸方向の間隙
ｔ３を、第１玉軸受４のアキシャルすきまｔ１より小さ
く設定したものであり、つまり、ｔ３＜ｔ１となってい
る。Next, FIG. 4 shows a second embodiment of the present invention. In this embodiment, the axial gap t3 between the flange portion 7a of the collar 7 fixed to the rotary shaft 2 in the axial direction and the step portion of the bearing housing 3 facing the flange portion 7a is set to the first ball. It is set to be smaller than the axial clearance t1 of the bearing 4, that is, t3 <t1.
【００２７】従って、この実施例においては、ガスター
ビン発電機を輸送する際の振動による衝撃や、同発電機
を落とした場合の衝撃等によって、ロータ１等を備えた
回転軸２が軸方向に移動しようとした場合に、上記フラ
ンジ部７ａと軸受ハウジング３とが先に接触することに
なり、上述した実施例と同様に、回転軸２の移動量が第
１の玉軸受４のアキシャルすきまｔ１より小さく抑制さ
れる。そのため、第１の玉軸受４の転動体４ａが分離防
止用肩１２に衝突することがなく、転動体４ａの損傷が
防止される。Therefore, in this embodiment, the rotary shaft 2 provided with the rotor 1 and the like is axially moved by an impact due to vibration during transportation of the gas turbine generator, an impact when the generator is dropped, or the like. When trying to move, the flange portion 7a and the bearing housing 3 come into contact with each other first, so that the moving amount of the rotating shaft 2 is the axial clearance t1 of the first ball bearing 4 as in the above-described embodiment. It is suppressed smaller. Therefore, the rolling element 4a of the first ball bearing 4 does not collide with the separation preventing shoulder 12, and damage to the rolling element 4a is prevented.
【００２８】次に、図５は、この発明の第３実施例を示
している。この実施例は、回転軸２に軸方向に固定され
ているインペラ９と該インペラ９が対向するバックプレ
ート２２との間の軸方向の間隙ｔ４を、第１玉軸受４の
アキシャルすきまｔ１より小さく設定したものであり、
つまり、ｔ４＜ｔ１となっている。Next, FIG. 5 shows a third embodiment of the present invention. In this embodiment, the axial gap t4 between the impeller 9 fixed to the rotary shaft 2 in the axial direction and the back plate 22 facing the impeller 9 is smaller than the axial clearance t1 of the first ball bearing 4. Is set,
That is, t4 <t1.
【００２９】従って、この実施例においては、ガスター
ビン発電機を輸送する際の振動による衝撃や、同発電機
を落とした場合の衝撃等によって、ロータ１等を備えた
回転軸２が軸方向に移動しようとした場合に、上記イン
ペラ９とバックプレート２２とが先に接触することにな
り、上述した実施例と同様に、回転軸２の移動量が第１
の玉軸受４のアキシャルすきまｔ１より小さく抑制され
る。そのため、第１の玉軸受４の転動体４ａが分離防止
用肩１２に衝突することがなく、転動体４ａの損傷が防
止される。Therefore, in this embodiment, the rotary shaft 2 provided with the rotor 1 and the like is axially moved by an impact due to vibration during transportation of the gas turbine generator or an impact when the generator is dropped. When attempting to move, the impeller 9 and the back plate 22 come into contact with each other first, and the moving amount of the rotary shaft 2 is the first as in the above-described embodiment.
It is suppressed to be smaller than the axial clearance t1 of the ball bearing 4. Therefore, the rolling element 4a of the first ball bearing 4 does not collide with the separation preventing shoulder 12, and damage to the rolling element 4a is prevented.
【００３０】次に、図６は、この発明の第４実施例を示
している。この実施例は、回転軸２と一体のタービン８
前端縁と該タービン８に対向するシュラウド２３との間
の軸方向の間隙ｔ５を、第１玉軸受４のアキシャルすき
まｔ１より小さく設定したものであり、つまり、ｔ５＜
ｔ１となっている。Next, FIG. 6 shows a fourth embodiment of the present invention. In this embodiment, the turbine 8 integrated with the rotary shaft 2 is used.
The axial gap t5 between the front edge and the shroud 23 facing the turbine 8 is set smaller than the axial clearance t1 of the first ball bearing 4, that is, t5 <.
It is t1.
【００３１】従って、この実施例においては、ガスター
ビン発電機を輸送する際の振動による衝撃や、同発電機
を落とした場合の衝撃等によって、ロータ１等を備えた
回転軸２が軸方向に移動しようとした場合に、上記ター
ビン８とシュラウド２３とが先に接触することになり、
上述した実施例と同様に、回転軸２の移動量が第１の玉
軸受４のアキシャルすきまｔ１より小さく抑制される。
そのため、第１の玉軸受４の転動体４ａが分離防止用肩
１２に衝突することがなく、転動体４ａの損傷が防止さ
れる。Therefore, in this embodiment, the rotary shaft 2 provided with the rotor 1 and the like is axially moved by an impact due to vibration during transportation of the gas turbine generator, an impact when the generator is dropped, or the like. When trying to move, the turbine 8 and the shroud 23 come into contact first,
Similar to the above-described embodiment, the movement amount of the rotary shaft 2 is suppressed to be smaller than the axial clearance t1 of the first ball bearing 4.
Therefore, the rolling element 4a of the first ball bearing 4 does not collide with the separation preventing shoulder 12, and damage to the rolling element 4a is prevented.
【００３２】また図７に示す第５実施例においては、上
述した各部の間隙ｔ２〜ｔ５およびアキシャルすきまｔ
１が、「ｔ２＜ｔ３，ｔ４，ｔ５＜ｔ１」の関係となっ
ている。つまり、カラー７のフランジ部７ａと軸受ハウ
ジング３との間の間隙ｔ３、インペラ９とバックプレー
ト２２との間の間隙ｔ４およびタービン８とシュラウド
２３との間の間隙ｔ５のいずれも、アキシャルすきまｔ
１よりは小さく、かつ第２の玉軸受５側のダンパスリー
ブ１６と軸受ハウジング３側のノズル部２０との間の間
隙ｔ２よりは大きい。Further, in the fifth embodiment shown in FIG. 7, the above-mentioned gaps t2 to t5 and the axial clearance t of each part.
1 has a relationship of “t2 <t3, t4, t5 <t1”. That is, the clearance t3 between the flange portion 7a of the collar 7 and the bearing housing 3, the clearance t4 between the impeller 9 and the back plate 22 and the clearance t5 between the turbine 8 and the shroud 23 are all axial clearances t.
It is smaller than 1 and larger than the gap t2 between the damper sleeve 16 on the second ball bearing 5 side and the nozzle portion 20 on the bearing housing 3 side.
【００３３】従って、この実施例では、ガスタービン発
電機を輸送する際の振動による衝撃や、同発電機を落と
した場合の衝撃等によって、ロータ１等を備えた回転軸
２が軸方向に移動しようとした場合に、高速回転中の部
分と軸受ハウジング３側とが干渉する前に、回転運動し
ないダンパスリーブ１６と軸受ハウジング３とが接触す
ることになる。そのため、発電機の運転中に何らかの衝
撃が加わった場合にも、回転軸２の移動量を第１の玉軸
受４のアキシャルすきまｔ１より小さく抑制できる。Therefore, in this embodiment, the rotary shaft 2 provided with the rotor 1 and the like moves in the axial direction due to an impact due to vibration during transportation of the gas turbine generator, an impact when the generator is dropped, or the like. In this case, the damper sleeve 16 that does not rotate and the bearing housing 3 come into contact with each other before the portion that is rotating at high speed interferes with the bearing housing 3 side. Therefore, even if some shock is applied during the operation of the generator, the movement amount of the rotary shaft 2 can be suppressed to be smaller than the axial clearance t1 of the first ball bearing 4.
【００３４】[0034]
【発明の効果】以上の説明で明らかなように、この発明
に係る軸受装置によれば、外輪が軸受箱に軸方向に固定
されている第１の玉軸受のアキシャルすきまよりも回転
部品の軸方向移動量が小さく抑制されるため、第１の玉
軸受の転動体が分離防止用肩に衝突して損傷するおそれ
がなくなり、第１の玉軸受の耐久性が向上する。As is apparent from the above description, according to the bearing device of the present invention, the shaft of the rotary component is more than the axial clearance of the first ball bearing in which the outer ring is axially fixed to the bearing housing. Since the directional movement amount is suppressed to be small, there is no possibility that the rolling element of the first ball bearing collides with the separation preventing shoulder and is damaged, and the durability of the first ball bearing is improved.
【００３５】特に、請求項２あるいは請求項３のように
第２の玉軸受の外輪側の一部と軸受箱側の一部とを接触
させるようにすれば、非回転の部分同士が接触するた
め、回転中の衝撃にも対処できる。また請求項１のよう
に回転部品の一部を軸受箱側に接触させるようにすれ
ば、各部の熱膨張等に影響されずに回転部品の移動量を
確実に規制できる。In particular, if a part of the outer ring side of the second ball bearing and a part of the bearing box side of the second ball bearing are brought into contact with each other, the non-rotating parts come into contact with each other. Therefore, it is possible to deal with a shock during rotation. Further, if a part of the rotating component is brought into contact with the bearing box side as in the first aspect, the moving amount of the rotating component can be reliably regulated without being affected by thermal expansion of each part.
【図１】この発明に係る軸受装置の第１実施例を示すガ
スタービン発電機の断面図。FIG. 1 is a sectional view of a gas turbine generator showing a first embodiment of a bearing device according to the present invention.
【図２】第１の玉軸受のみを示し、（ａ）は正スラスト
方向に押された場合の状態、（ｂ）は反スラスト方向に
押された場合の状態をそれぞれ示す断面図。FIG. 2 is a cross-sectional view showing only the first ball bearing, (a) showing a state when pushed in a positive thrust direction and (b) showing a state when pushed in an anti-thrust direction.
【図３】第２の玉軸受部分の拡大図。FIG. 3 is an enlarged view of a second ball bearing portion.
【図４】この発明の第２実施例を示す断面図。FIG. 4 is a sectional view showing a second embodiment of the present invention.
【図５】この発明の第３実施例を示す断面図。FIG. 5 is a sectional view showing a third embodiment of the present invention.
【図６】この発明の第４実施例を示す断面図。FIG. 6 is a sectional view showing a fourth embodiment of the present invention.
【図７】この発明の第５実施例を示す断面図。FIG. 7 is a sectional view showing a fifth embodiment of the present invention.
【図８】従来の軸受装置の一例を示す断面図。FIG. 8 is a sectional view showing an example of a conventional bearing device.
【図９】その要部を拡大して示す断面図。FIG. 9 is an enlarged cross-sectional view showing a main part thereof.
２…回転軸 ３…軸受ハウジング ４…第１玉軸受 ５…第２玉軸受 ７…カラー ９…インペラ １６…ダンパスリーブ １９…与圧用スプリング ２０…ノズル部 2 ... Rotating shaft 3 ... Bearing housing 4 ... First ball bearing 5 ... Second ball bearing 7 ... Collar 9 ... Impeller 16 ... Damper sleeve 19 ... Pressurizing spring 20 ... Nozzle part
Claims (5)
一対の非分離型アンギュラ玉軸受を、それぞれの正与圧
側肩が互いに外側となるように配置するとともに、各玉
軸受の内輪を回転部品の軸に軸方向に固定し、かつ第１
の玉軸受の外輪を軸受箱に軸方向に固定し、第２の玉軸
受の外輪を軸受箱に軸方向に移動可能に保持し、これら
の一対の玉軸受でもって上記回転部品を回転自在に支持
するようにした軸受装置において、上記第１の玉軸受の
アキシャルすきまよりも回転部品の軸方向の移動可能量
が小さくなるように、回転部品と軸受箱側の各部との間
の軸方向の最も小さな間隙を上記アキシャルすきまより
小さく設定したことを特徴とする軸受装置。1. A pair of non-separable angular contact ball bearings having separation preventing shoulders on the reverse pressurizing side of the inner ring are arranged such that the respective positive pressurizing side shoulders are on the outside, and the inner ring of each ball bearing is First fixed to the axis of the rotating component in the axial direction and
The outer ring of the ball bearing is fixed to the bearing box in the axial direction, the outer ring of the second ball bearing is held in the bearing box so as to be movable in the axial direction, and the rotating parts are rotatably supported by the pair of ball bearings. In the bearing device supported, the axial distance between the rotary component and each part on the bearing housing side is set so that the movable amount of the rotary component in the axial direction is smaller than the axial clearance of the first ball bearing. A bearing device characterized in that the smallest gap is set to be smaller than the above axial clearance.
一対の非分離型アンギュラ玉軸受を、それぞれの正与圧
側肩が互いに外側となるように配置するとともに、各玉
軸受の内輪を回転部品の軸に軸方向に固定し、かつ第１
の玉軸受の外輪を軸受箱に軸方向に固定し、第２の玉軸
受の外輪を軸受箱に軸方向に移動可能に保持し、これら
の一対の玉軸受でもって上記回転部品を回転自在に支持
するようにした軸受装置において、上記第１の玉軸受の
アキシャルすきまよりも回転部品の軸方向の移動可能量
が小さくなるように、上記第２の玉軸受の外輪側の一部
と軸受箱側の一部との軸方向の間隙を上記アキシャルす
きまより小さく設定したことを特徴とする軸受装置。2. A pair of non-separable angular contact ball bearings having separation preventing shoulders on the reverse pressurizing side of the inner ring are arranged so that the respective positive pressurizing side shoulders are on the outside, and the inner ring of each ball bearing is First fixed to the axis of the rotating component in the axial direction and
The outer ring of the ball bearing is fixed to the bearing box in the axial direction, the outer ring of the second ball bearing is held in the bearing box so as to be movable in the axial direction, and the rotating parts are rotatably supported by the pair of ball bearings. In the bearing device to be supported, a part of the second ball bearing on the outer ring side and the bearing housing are arranged so that the movable amount of the rotary component in the axial direction is smaller than the axial clearance of the first ball bearing. A bearing device characterized in that an axial gap with a part of the side is set to be smaller than the axial clearance.
一対の非分離型アンギュラ玉軸受を、それぞれの正与圧
側肩が互いに外側となるように配置するとともに、各玉
軸受の内輪を回転部品の軸に軸方向に固定し、かつ第１
の玉軸受の外輪を軸受箱に軸方向に固定し、第２の玉軸
受の外輪を軸受箱に軸方向に移動可能に保持し、これら
の一対の玉軸受でもって上記回転部品を回転自在に支持
するようにした軸受装置において、上記第１の玉軸受の
アキシャルすきまをｔ１、上記第２の玉軸受の外輪側の
一部と軸受箱側の一部との軸方向の間隙をｔ２、回転部
品と軸受箱側の各部との間の軸方向の最も小さな間隙を
ｔ３としたときに、ｔ２＜ｔ３＜ｔ１となるように、各
間隙を設定したことを特徴とする軸受装置。3. A pair of non-separable angular contact ball bearings having separation preventing shoulders on the reverse pressurizing side of the inner ring are arranged so that the respective positive pressurizing side shoulders are on the outer side, and the inner ring of each ball bearing is First fixed to the axis of the rotating component in the axial direction and
The outer ring of the ball bearing is fixed to the bearing box in the axial direction, the outer ring of the second ball bearing is held in the bearing box so as to be movable in the axial direction, and the rotating parts are rotatably supported by the pair of ball bearings. In the bearing device supported, the axial clearance of the first ball bearing is t1, the axial gap between a part of the outer ring side of the second ball bearing and a part of the bearing housing is t2, and rotation is performed. A bearing device, wherein each gap is set such that t2 <t3 <t1 where t3 is the smallest axial gap between the component and each part on the bearing box side.
ングでもって第１の玉軸受から離間する方向へ付勢され
ていることを特徴とする請求項１〜３のいずれかに記載
の軸受装置。4. The outer ring of the second ball bearing is biased by a pressurizing spring in a direction away from the first ball bearing, according to claim 1. Bearing device.
箱に支持されるスクイズフィルムダンパ式の軸受装置で
あることを特徴とする請求項１〜４のいずれかに記載の
軸受装置。5. The bearing device according to claim 1, wherein the outer ring of each ball bearing is a squeeze film damper type bearing device supported by a bearing box through an oil film.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6288506A JPH08145053A (en) | 1994-11-24 | 1994-11-24 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6288506A JPH08145053A (en) | 1994-11-24 | 1994-11-24 | Bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08145053A true JPH08145053A (en) | 1996-06-04 |
Family
ID=17731112
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6288506A Pending JPH08145053A (en) | 1994-11-24 | 1994-11-24 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08145053A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003056362A (en) * | 2001-08-14 | 2003-02-26 | Ishikawajima Harima Heavy Ind Co Ltd | Gas-turbine engine |
| JP2010242822A (en) * | 2009-04-03 | 2010-10-28 | Ihi Corp | Bearing structure of turbine generator |
| CN117469194A (en) * | 2023-12-28 | 2024-01-30 | 诺顿风机(潍坊)有限公司 | Novel intelligent monitoring's special bearing box of axial fan |
-
1994
- 1994-11-24 JP JP6288506A patent/JPH08145053A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003056362A (en) * | 2001-08-14 | 2003-02-26 | Ishikawajima Harima Heavy Ind Co Ltd | Gas-turbine engine |
| JP2010242822A (en) * | 2009-04-03 | 2010-10-28 | Ihi Corp | Bearing structure of turbine generator |
| CN117469194A (en) * | 2023-12-28 | 2024-01-30 | 诺顿风机(潍坊)有限公司 | Novel intelligent monitoring's special bearing box of axial fan |
| CN117469194B (en) * | 2023-12-28 | 2024-03-08 | 诺顿风机(潍坊)有限公司 | Bearing box special for intelligent monitoring axial flow fan |
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