JPH0658044B2 - Turbine rotor and method for producing the same - Google Patents
Turbine rotor and method for producing the sameInfo
- Publication number
- JPH0658044B2 JPH0658044B2 JP59221138A JP22113884A JPH0658044B2 JP H0658044 B2 JPH0658044 B2 JP H0658044B2 JP 59221138 A JP59221138 A JP 59221138A JP 22113884 A JP22113884 A JP 22113884A JP H0658044 B2 JPH0658044 B2 JP H0658044B2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- ceramic
- turbine rotor
- metal shaft
- metal
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/025—Fixing blade carrying members on shafts
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明はタービンローターおよびその製造法に関するも
のある。さらに詳しくは、金属とセラミックスからなる
タービンローターとその製造法に関するものである。Description: TECHNICAL FIELD The present invention relates to a turbine rotor and a manufacturing method thereof. More specifically, the present invention relates to a turbine rotor made of metal and ceramics and a manufacturing method thereof.
（従来の技術） セラミックスは硬くて耐摩耗性にすぐれているうえ、高
温での機械的性質や耐蝕性にすぐれているため、高温で
の機械的強度や耐摩耗性が必要とされるガスタービンや
ターボチャージャーのローターの構造材料として適して
いる。このため、ガスタービンローターやターボチャー
ジャーローターのセラミック化が検討されている。例え
ば米国特許第４３９６４４５号明細書には，翼部と軸部
がセラミックスからなる構造のタービンローターが開示
されている。この構造のタービンローターではセラミッ
クス製軸部の一端にねじ部を設けて、金属製圧縮機イン
ペラを固定している。しかし、この構造のタービンロー
ターは圧縮機インペラを構成する金属材料と、軸部を構
成するセラミック材料との熱膨張差のため、タービンロ
ーターの使用中にセラミック軸のねじ部が破損する欠点
がある。また、セラミックスに対するねじ加工は高度の
技術を必要とし、時間と費用がかかる欠点がある。(Prior art) Gas turbines that require mechanical strength and wear resistance at high temperatures because ceramics are hard and have excellent wear resistance, as well as excellent mechanical properties and corrosion resistance at high temperatures. Suitable as a structural material for rotors of turbochargers. For this reason, the ceramicization of gas turbine rotors and turbocharger rotors is being considered. For example, U.S. Pat. No. 4,396,445 discloses a turbine rotor having a structure in which blades and shafts are made of ceramics. In the turbine rotor having this structure, a screw portion is provided at one end of the ceramic shaft portion to fix the metal compressor impeller. However, the turbine rotor of this structure has a drawback that the screw portion of the ceramic shaft is damaged during use of the turbine rotor due to a difference in thermal expansion between the metal material forming the compressor impeller and the ceramic material forming the shaft portion. . Further, there is a drawback in that screw processing for ceramics requires a high level of technology, which is time consuming and expensive.
この対策として、実開昭57-92097号公報には、タービン
ローターのセラミック軸を金属軸の端部に設けた筒状部
に嵌合する構造が開示されている。しかし、この構造で
は金属軸の筒状部先端がタービンローターシャフトを支
承する２ケのベアリングの間に位置しているため、ター
ビンローターのセラミック軸が破損すると、ベアリング
ハウジング内の潤滑油がタービンハウジングに漏出する
危険性がある。As a countermeasure against this, Japanese Utility Model Laid-Open No. 57-92097 discloses a structure in which a ceramic shaft of a turbine rotor is fitted to a tubular portion provided at an end of a metal shaft. However, in this structure, the tip of the tubular part of the metal shaft is located between the two bearings that support the turbine rotor shaft. Therefore, if the ceramic shaft of the turbine rotor is damaged, the lubricating oil in the bearing housing may cause the lubricating oil in the turbine housing. There is a risk of leakage.
一方、ドイツ特許第2728823号明細書には、タービンロ
ーターのセラミック軸の全長が中空の金属軸で被覆され
ているタービンローターの構造が開示されている。しか
し、この構造ではセラミック軸と金属軸の中空部内面と
がセラミック軸のほぼ全長にわたって密着して固定され
ているためセラミック軸から金属軸への伝熱面積が大き
い。このため、高温のタービン翼車から金属軸への伝熱
量が多くなり、金属軸の温度が過度に上昇し、金属軸上
に設けた密封と取付のための機構が劣化しやすい欠点が
ある。On the other hand, German Patent No. 2728823 discloses the structure of a turbine rotor in which the ceramic shaft of the turbine rotor is covered with a hollow metal shaft over its entire length. However, in this structure, since the ceramic shaft and the inner surface of the hollow portion of the metal shaft are closely attached and fixed over substantially the entire length of the ceramic shaft, the heat transfer area from the ceramic shaft to the metal shaft is large. Therefore, the amount of heat transferred from the high temperature turbine impeller to the metal shaft increases, the temperature of the metal shaft rises excessively, and the sealing and mounting mechanism provided on the metal shaft tends to deteriorate.
また、金属軸部の温度上昇にともなう、金属軸とセラミ
ック軸の熱膨張量の差のため、結合部界面に剪断応力が
発生し、金属軸が疲労しやすい欠点がある。さらにま
た、金属軸へ伝達される熱量が多いため、潤滑油の温度
が過度に上昇する欠点がある。Further, due to the difference in thermal expansion amount between the metal shaft and the ceramic shaft due to the temperature rise of the metal shaft portion, shear stress is generated at the interface of the joint portion, and the metal shaft is easily fatigued. Furthermore, since the amount of heat transferred to the metal shaft is large, there is a drawback that the temperature of the lubricating oil rises excessively.
さらに、上記構造では中空の金属軸とセラミック軸の結
合部のうち、タービン翼車側の部分が高温、潤滑ユニッ
ト内の部分が低温となり、結合部の軸方向には大きな温
度勾配が存在する。このため、結合部のセラミック軸表
面には、軸方向に引張の熱応力が発生し、セラミック軸
が破損する欠点がある。Further, in the above-mentioned structure, of the hollow metal shaft-ceramic shaft joint, the turbine impeller side has a high temperature and the lubrication unit has a low temperature, so that a large temperature gradient exists in the axial direction of the joint. For this reason, a tensile thermal stress is generated in the axial direction on the surface of the ceramic shaft of the joint portion, and the ceramic shaft is damaged.
なお、上記構造のように、セラミック軸と金属軸中空部
とをほぼ全長にわたって密着した状態で固定するために
はセラミック軸直径と金属軸中空部の加工に高精度の加
工が必要となり、実用上問題がある。In addition, as in the above structure, in order to fix the ceramic shaft and the hollow portion of the metal shaft in close contact with each other over substantially the entire length, it is necessary to process the ceramic shaft diameter and the hollow portion of the metal shaft with high accuracy, which is practically required. There's a problem.
本発明の第１の目的は、タービンローターのセラミック
軸と金属軸と結合した構造のタービンローターにおいて
セラミック軸から金属への伝熱量を最小に抑えて、潤滑
油の密封機構の劣化を防ぐことである。A first object of the present invention is to prevent the deterioration of the lubricating oil sealing mechanism by minimizing the amount of heat transfer from the ceramic shaft to the metal in the turbine rotor having a structure in which the ceramic shaft and the metal shaft of the turbine rotor are combined. is there.
本発明の第２の目的は、セラミック軸が破損した場合に
潤滑油の漏出を防止ないしは最小に抑えることである。A second object of the invention is to prevent or minimize leakage of lubricating oil in the event of a ceramic shaft failure.
本発明の第３の目的は、製造が容易で強固な結合を有す
るタービンローターとその製造法を提供することであ
る。A third object of the present invention is to provide a turbine rotor which is easy to manufacture and has a strong connection, and a manufacturing method thereof.
本発明の第４の目的は、セラミック軸や金属軸の破損が
起らない信頼性の高いタービンローターとその製造法を
提供することである。A fourth object of the present invention is to provide a highly reliable turbine rotor that does not damage a ceramic shaft or a metal shaft, and a manufacturing method thereof.
（問題点を解決するための手段） 本発明のタービンローターは、セラミック製翼車と一体
的に形成されているセラミック製軸が金属軸に設けられ
た有底中空筒状部の一部で固定されてタービンシャフト
を形成した構造のタービンローターにおいて、上記中空
筒状部は内径の異なる筒状部で構成され、しかも該筒状
部の開放端側の内径が残りの筒状部の内径より僅かに大
きく、セラミック製軸と該金属軸との結合が中空筒状部
の小径部でなされているとともに、該結合部がベアリン
グハウジング内において前記タービンシャフトを支承す
る２個の軸受間に位置し、しかも、該筒状部内径の大径
部内表面とセラミック製軸外表面の間に円筒状の空隙が
存在し、しかも中空筒状部の開放端先端と該セラミック
製軸のセラミック翼車への接続部との間に隙間が存在す
ることを特徴とするものである。(Means for Solving Problems) In a turbine rotor of the present invention, a ceramic shaft integrally formed with a ceramic impeller is fixed by a part of a bottomed hollow cylindrical portion provided on a metal shaft. In the turbine rotor having a structure in which the turbine shaft is formed, the hollow cylindrical portion is composed of cylindrical portions having different inner diameters, and the inner diameter on the open end side of the cylindrical portion is slightly smaller than the inner diameters of the remaining cylindrical portions. In addition, the ceramic shaft and the metal shaft are connected to each other by the small diameter portion of the hollow cylindrical portion, and the connecting portion is located between the two bearings that support the turbine shaft in the bearing housing. Moreover, there is a cylindrical void between the inner surface of the large diameter portion of the inner diameter of the cylindrical portion and the outer surface of the ceramic shaft, and the open end tip of the hollow cylindrical portion and the ceramic shaft are connected to the ceramic impeller. Between departments It is characterized by the presence of a gap in.
また、本発明のタービンローターの製造法は、セラミッ
ク製翼車と一体的に形成されているセラミック製軸に金
属軸を固定してタービンローターとする方法において、
金属軸の一端に、開放端側の内径が底部側の内径より大
である筒状部を設けたのち、該筒状部にセラミック製軸
を挿入し、筒状部内径の小径部でセラミック製軸を固定
するとともに該筒状部内径の大径部内表面とセラミック
製軸表面の間に空隙を設け、しかも中空筒状部の開放端
先端と該セラミック製軸のセラミック翼車への接続部と
の間に隙間を設けることを特徴とするものである。Further, the method for manufacturing a turbine rotor of the present invention is a method of fixing a metal shaft to a ceramic shaft integrally formed with a ceramic impeller to form a turbine rotor,
At one end of the metal shaft, a cylindrical part whose inner diameter on the open end side is larger than the inner diameter on the bottom side is provided, and then a ceramic shaft is inserted into the cylindrical part, and a ceramic part is inserted at the small diameter part of the cylindrical part. The shaft is fixed, and a gap is provided between the inner surface of the large-diameter portion of the inner diameter of the tubular portion and the surface of the ceramic shaft, and the open end tip of the hollow tubular portion and the connecting portion of the ceramic shaft to the ceramic impeller. It is characterized in that a gap is provided between them.
（作用） 本発明では、金属軸の一端に、開放端側の内径が底部側
の内径より大である筒状部を設けたのち、該筒状部にタ
ービンローターのセラミック軸を挿入して、筒状部内径
の小径部でセラミック軸を固定してタービンローターと
する。この場合のセラミック軸と金属軸の固定部は、タ
ービンローター使用中のローター軸部の温度が500℃以
下となる部位とするのが好ましく、該軸部の温度が350
℃以下の部位とするのがより好ましい。また、上記固定
部には軸方向の温度勾配が存在しないようにするのが望
ましい。(Operation) In the present invention, at one end of the metal shaft, after providing a tubular portion whose inner diameter on the open end side is larger than the inner diameter on the bottom portion side, insert the ceramic shaft of the turbine rotor into the tubular portion, The turbine shaft is fixed by fixing the ceramic shaft at the small diameter part of the inner diameter of the tubular part. In this case, the fixed portion of the ceramic shaft and the metal shaft is preferably a portion where the temperature of the rotor shaft portion during use of the turbine rotor is 500 ° C. or lower, and the temperature of the shaft portion is 350 ° C. or less.
It is more preferable to set the temperature at a temperature of not higher than ° C. Further, it is desirable that the fixed portion has no temperature gradient in the axial direction.
本発明のタービンローターの軸部を構成するセラミック
スと金属では、一般に金属の方がセラミックスより熱膨
張係数が大きいので、軸部温度が500℃以上になると、
両者の熱膨張差のため結合力が低下するので好ましくな
い。また、結合部の軸方向に温度勾配が存在すると、セ
ラミック軸と金属軸の結合界面において、セラミック軸
に引張の熱応力が発生し、セラミック軸が破損すること
があるので好ましくない。In the ceramic and the metal forming the shaft portion of the turbine rotor of the present invention, since the metal generally has a larger thermal expansion coefficient than the ceramic, when the shaft temperature is 500 ° C. or higher,
The difference in thermal expansion between the two lowers the binding force, which is not preferable. Further, if there is a temperature gradient in the axial direction of the joint, tensile thermal stress may be generated in the ceramic shaft at the joint interface between the ceramic shaft and the metal shaft, and the ceramic shaft may be damaged.
この問題の解決のためには、例えば本発明のタービンロ
ーターを使用して、ターボチャージャーとする場合に
は、セラミック軸と金属軸の固定部をベアリングハウジ
ング内に位置させるのが好ましく、該固定部をタービン
ローターの軸部を支承する２個のベアリング当接部の間
に位置させるのがより好ましい。これにより、セラミッ
ク軸と金属軸の固定部はベアリングハウジング内を循環
する潤滑油により強制的に冷却されるため、過度の温度
上昇が生じないばかりでなく、固定部内において軸方向
の温度勾配も生じないので、セラミック軸と金属軸の結
合力の低下やセラミック軸と金属軸との固定界面での引
張の熱応力の発生が防止される。In order to solve this problem, for example, when the turbine rotor of the present invention is used to form a turbocharger, it is preferable to locate the fixed portion of the ceramic shaft and the metal shaft in the bearing housing. Is more preferably located between the two bearing abutments bearing the shaft of the turbine rotor. As a result, the fixed part of the ceramic shaft and the metal shaft is forcibly cooled by the lubricating oil circulating in the bearing housing, so that not only an excessive temperature rise does not occur, but also a temperature gradient in the axial direction occurs in the fixed part. Since it does not exist, it is possible to prevent the decrease in the bonding force between the ceramic shaft and the metal shaft and the generation of tensile thermal stress at the fixed interface between the ceramic shaft and the metal shaft.
本発明のタービンローターでは、上記固定部よりタービ
ン翼車側の金属軸筒状部内表面とセラミック軸表面との
間に断熱効果を有する空隙が設けてある。該空隙が存在
するので、セラミック製のタービン軸の温度が上昇して
も金属軸筒状部への熱伝達が最小限に抑制され、金属軸
の過度の温度上昇が起こらない。このため、タービン翼
車が高温になっても、結合部のゆるみや熱応力によるセ
ラミック軸の破損は起らない。したがって、本発明のタ
ービンローターでは金属軸筒状部先端をタービン翼車近
くまで延長することが可能になるから、該筒状部外表面
に潤滑油の密封と取付に必要なすべての形状要素を設け
ることが可能となり、万一、セラミック軸が破損しても
潤滑油の漏出が生じない。In the turbine rotor of the present invention, a gap having a heat insulating effect is provided between the inner surface of the metal shaft cylindrical portion on the turbine impeller side of the fixed portion and the surface of the ceramic shaft. Due to the presence of the voids, even if the temperature of the ceramic turbine shaft rises, heat transfer to the tubular portion of the metal shaft is suppressed to a minimum, and an excessive temperature rise of the metal shaft does not occur. Therefore, even if the turbine impeller has a high temperature, the ceramic shaft is not damaged due to loosening of the joint or thermal stress. Therefore, in the turbine rotor of the present invention, it becomes possible to extend the tip of the tubular portion of the metal shaft to the vicinity of the turbine impeller, so that all the shape elements necessary for sealing and mounting the lubricating oil are attached to the outer surface of the tubular portion. It is possible to install it, and even if the ceramic shaft is damaged, leakage of lubricating oil does not occur.
本発明のタービンローターは、セラミック軸と金属軸の
固定を嵌合あるいは接合のいずれかの方法で行うことが
できる。In the turbine rotor of the present invention, the ceramic shaft and the metal shaft can be fixed by either fitting or joining.
このうち、嵌合は焼ばめ、冷しばめ、圧入のいずれかの
方法で行うことができる。焼ばめ、冷しばめはセラミッ
ク軸の直径を金属軸筒状部小径部内径より大きく加工
し、被嵌合部材の一方を加熱ないし冷却して、両部材間
にはめ込み可能な寸法差を生ぜしめ、その寸法差を利用
して両部材を嵌合するものであるから、嵌合部の寸法が
大きいタービンローターの結合方法として好ましいもの
である。Of these, fitting can be performed by any of shrink fitting, cold fitting, and press fitting. Shrink fit and cold fit process the diameter of the ceramic shaft to be larger than the inner diameter of the small diameter part of the metal shaft, and heat or cool one of the fitted parts to reduce the size difference that can be fitted between both parts. Since the two parts are fitted together by using the difference in size between them, they are preferable as a method for connecting the turbine rotors having a large fitting part size.
また、一般に金属材料の方がセラミック材料より熱膨張
係数が大きいので、金属を加熱する焼ばめの方が少ない
温度差で大きな寸法差が得られ、安定した焼ばめ操作が
できるのでより好ましいものである。この場合の焼ば
め、冷しばめの締代は、嵌合後に金属軸筒状部やセラミ
ック軸が破損せず、しかも本発明のタービンローターの
使用条件で嵌合部に必要とされる締付力が得られる大き
さとする。Further, in general, a metal material has a larger coefficient of thermal expansion than a ceramic material, so shrink fitting by heating a metal is more preferable because a large dimensional difference can be obtained with a small temperature difference and stable shrink fitting operation can be performed. It is a thing. In this case, the shrinkage margins of shrink fit and shrink fit are required for the fitting portion under the conditions of use of the turbine rotor of the present invention without damaging the metal shaft tubular portion or the ceramic shaft after fitting. Make sure that the tightening force can be obtained.
一方、圧入はタービンローターのセラミック軸を、金属
軸に設けた該セラミック軸より小径の筒状部に、荷重を
かけて強制的に押し込んで嵌合する方法である。上記セ
ラミック軸直径と金属軸筒状部内径の寸法差は金属軸筒
状部の変形により吸収されるので、圧入前のセラミック
軸直径と金属軸筒状部内径の仕上げ寸法公差は焼ばめ、
冷しばめの場合より大きくてもよい。このため、圧入は
嵌合部の寸法が小さいタービンローターの結合方法とし
てより好ましいものである。圧入部の形状と寸法は、圧
入時に作用する荷重によって、セラミック軸や金属軸筒
状部が破損しない形状及び寸法とする。また、セラミッ
ク軸と金属軸筒状部の嵌合部内径との寸法差は、嵌合部
が本発明のタービンローターの使用条件に応じた締付力
を有するとともに、圧入時にセラミック軸と金属軸筒状
部のいずれもが破壊しない大きさとする。このために
は、上記寸法差はセラミック軸直径を金属軸筒状部の嵌
合部内径より0.1％ないし10％大きくするのが好まし
く、１％なしい５％大きくするのがより好ましい。この
寸法差が0.1％以下では、圧入部の締付力が不足し、使
用中に圧入による嵌合部が抜けたり緩んだりする心配が
あるので好ましくない。寸法差が10％以上になると、圧
入に際しセラミック軸が破損したり、金属軸筒状部が破
損するので好ましくない。なお、金属軸筒状部内の嵌合
部の硬さが小さいときには上記寸法差を大きく、硬さが
大きいときには、上記寸法差を小さくすれば安定した結
合強度が得られる。この圧入は室温で行ってもよいし、
金属軸のみを加熱するかあるいは金属軸とセラミック軸
の両方を加熱して行ってもよい。しかし、両者を加熱し
て圧入する方法がもっとも好ましい。何となれば、両者
を加熱すると、金属軸筒状部の変形抵抗が減少し、圧入
に要する荷重が低下するので、セラミック軸や金属軸筒
状部の破損が起らなくなるうえ、圧入温度からの冷却に
際し、両者の熱膨張差にもとづく、締付力の増加が生ず
るからである。セラミック軸と金属軸の両方を加熱して
圧入する場合の加熱温度は、金属軸の熱処理温度あるい
は金属軸の表面硬化層の硬化温度のうちのいずれか低い
方の温度以下で、しかも圧入部の使用温度以上の温度が
好ましい。On the other hand, the press-fitting is a method in which the ceramic shaft of the turbine rotor is forcibly pushed in and fitted into a cylindrical portion provided on the metal shaft and having a diameter smaller than that of the ceramic shaft. Since the dimensional difference between the ceramic shaft diameter and the metal shaft tubular portion inner diameter is absorbed by the deformation of the metal shaft tubular portion, the finish dimension tolerance between the ceramic shaft diameter and the metal shaft tubular portion inner diameter before press fitting is shrink-fit,
It may be larger than in the case of cold fitting. For this reason, press-fitting is more preferable as a coupling method for turbine rotors having small fitting portions. The shape and size of the press-fitting part should be such that the ceramic shaft and the metal shaft tubular part are not damaged by the load applied during press-fitting. Further, the dimensional difference between the ceramic shaft and the inner diameter of the fitting portion of the metal shaft tubular portion is such that the fitting portion has a tightening force according to the usage conditions of the turbine rotor of the present invention, and the ceramic shaft and the metal shaft during press fitting. The size should be such that none of the tubular parts will break. For this purpose, the dimensional difference is preferably 0.1% to 10% larger than the inner diameter of the fitting portion of the metal shaft tubular portion, more preferably 1% or 5% larger than the fitting portion inner diameter of the metal shaft tubular portion. If this dimensional difference is 0.1% or less, the tightening force of the press-fitting portion will be insufficient, and there is a risk of the fitting portion coming off or loosening due to press-fitting during use, which is not preferable. If the dimensional difference is 10% or more, the ceramic shaft or the metal shaft tubular portion is damaged during press fitting, which is not preferable. When the hardness of the fitting portion in the metal shaft tubular portion is small, the above-mentioned dimensional difference is large, and when the hardness is large, the above-mentioned dimensional difference is small, so that stable bonding strength can be obtained. This press-fitting may be performed at room temperature,
It may be performed by heating only the metal shaft or by heating both the metal shaft and the ceramic shaft. However, the method of heating both and press-fitting them is most preferable. What happens is that if both are heated, the deformation resistance of the metal shaft tubular part will decrease and the load required for press fitting will decrease, so damage to the ceramic shaft and metal shaft tubular part will not occur, and the temperature from the press fitting temperature will not occur. This is because during cooling, the tightening force increases due to the difference in thermal expansion between the two. When heating both the ceramic shaft and the metal shaft and press-fitting them, the heating temperature is less than the heat treatment temperature of the metal shaft or the hardening temperature of the surface-hardened layer of the metal shaft, whichever is lower, and Temperatures above the use temperature are preferred.
ここで、金属軸の熱処理温度は金属軸筒状部の硬さ調整
のための熱処理温度を意味し、例えば該筒状部が析出硬
化型合金からなる場合には析出硬化処理温度、焼入れ硬
化鋼からなる場合には焼もどし温度に相当する。Here, the heat treatment temperature of the metal shaft means a heat treatment temperature for adjusting the hardness of the tubular portion of the metal shaft. For example, when the tubular portion is made of a precipitation hardening type alloy, the precipitation hardening treatment temperature, the quench hardening steel If it consists of, it corresponds to the tempering temperature.
また、表面硬化層の軟化温度は、表面硬化が窒化処理に
よる場合には窒化層の硬化温度、表面焼入れによる場合
には焼もどし温度に相当する。The softening temperature of the surface hardened layer corresponds to the hardening temperature of the nitrided layer when the surface hardening is nitriding, and the tempering temperature when the surface hardening is surface quenching.
圧入温度が金属軸の焼もどし温度より高い場合には金属
軸の硬さが低下し、圧入部の締付力が減少するので好ま
しくない。また、圧入温度が表面硬化層の軟化温度より
高い場合には、表面硬化処理の効果が減少するので好ま
しくない。さらにまた、圧入温度が金属軸の析出硬化処
理温度以上の場合には、加熱中に金属軸が硬化し展延性
が低下するため、圧入に際してセラミック軸や金属軸筒
状部が破損するので好ましくない。When the press-fitting temperature is higher than the tempering temperature of the metal shaft, the hardness of the metal shaft is lowered and the tightening force of the press-fitting part is reduced, which is not preferable. Further, if the press-fitting temperature is higher than the softening temperature of the surface-hardened layer, the effect of the surface-hardening treatment decreases, which is not preferable. Furthermore, when the press-fitting temperature is equal to or higher than the precipitation hardening temperature of the metal shaft, the metal shaft is hardened during heating and the malleability is lowered, so that the ceramic shaft or the metal shaft tubular portion is damaged during press-fitting, which is not preferable. .
圧入温度が圧入部の使用温度より低い場合には、圧入部
の温度が使用温度まで上昇すると、一般には金属軸の熱
膨張がセラミック軸の熱膨張より大きいので、圧入部が
緩み締付力が低下するので好ましくない。If the press-fitting temperature is lower than the operating temperature of the press-fitting part, when the temperature of the press-fitting part rises to the operating temperature, the thermal expansion of the metal shaft is generally larger than the thermal expansion of the ceramic shaft. It is not preferable because it decreases.
本発明のタービンローターのセラミック軸と金属軸は耐
熱性接着剤による接着あるいはろう付けにより接合して
もよい。接合をろう付けで行う場合には、タービンロー
ターのセラミック軸の被接合部表面にあらかじめ金属層
を設けておく。該金属層は金属粉末を主成分とするペー
スト状組成物をセラミック軸表面に塗布、乾燥したの
ち、焼付ける方法あるいはセラミック軸表面に金属を物
理蒸着あるいは化学蒸着などで蒸着させる方法で設ける
ことができる。金属層を設けたセラミック軸と金属軸の
接合は市販のろう合金を使用し、通常の方法で行えばよ
い。また、上記方法のほかに、活性金属を含むろう合金
を使用して、セラミック軸表面に金属層を設けることな
く、セラミック軸と金属軸を直接接合することができ
る。この活性金属としては、セラミックスが窒化物の場
合には、タンタル、アルミニウム、セリウム、チタン、
ジルコニウム等の金属、セラミックスが炭化物の場合に
は、クロム、タンタル、チタン、ジルコニウム、モリブ
デン等の金属が利用できる。The ceramic shaft and the metal shaft of the turbine rotor of the present invention may be joined by bonding with a heat resistant adhesive or brazing. When the joining is performed by brazing, a metal layer is provided in advance on the surface of the joined portion of the ceramic shaft of the turbine rotor. The metal layer is provided by applying a paste composition containing metal powder as a main component to the surface of the ceramic shaft, drying and baking the composition, or by depositing the metal on the surface of the ceramic shaft by physical vapor deposition or chemical vapor deposition. it can. The ceramic shaft provided with the metal layer and the metal shaft may be joined by using a commercially available brazing alloy by a usual method. In addition to the above method, a braze alloy containing an active metal can be used to directly bond the ceramic shaft to the metal shaft without providing a metal layer on the surface of the ceramic shaft. As the active metal, when the ceramic is a nitride, tantalum, aluminum, cerium, titanium,
When the metal such as zirconium or the ceramic is carbide, a metal such as chromium, tantalum, titanium, zirconium or molybdenum can be used.
本発明のタービンローターを構成するセラミック材料は
軽くて、高温強度と耐摩耗性にすぐれる窒化珪素、炭化
珪素、サイアロンなどのセラミック材料又はそれらのセ
ラミックスを主体とする複合材料から本発明のタービン
ローターの使用目的に応じて選択すればよい。The ceramic material constituting the turbine rotor of the present invention is light, and is made of a ceramic material such as silicon nitride, silicon carbide, sialon or the like which is excellent in high temperature strength and wear resistance, or a composite material mainly composed of those ceramics. It may be selected according to the purpose of use.
また、本発明のタービンローターを構成する金属材料は
析出硬化型合金あるいは浸炭、窒化、表面焼入れ、放電
硬化、メッキ等の方法で表面硬化が可能な市販の金属材
料を使用することができる。Further, as the metal material constituting the turbine rotor of the present invention, a precipitation hardenable alloy or a commercially available metal material which can be surface hardened by a method such as carburizing, nitriding, surface hardening, discharge hardening and plating can be used.
本発明のタービンローターを使用して、ターボチャージ
ャーとする場合には、金属軸表面を硬化させて金属軸の
ベアリング当接部表面の耐摩耗性を向上させる。金属軸
の材料として、析出硬化合金を使用する場合には、セラ
ミック軸と金属軸を結合したのち析出硬化処理を行う。
この場合の析出硬化型合金としては、マルエージング
鋼、析出硬化型ステンレス鋼、析出硬化型超合金の何れ
か一種以上が好ましいものである。When the turbine rotor of the present invention is used to form a turbocharger, the surface of the metal shaft is hardened to improve the wear resistance of the surface of the metal shaft bearing abutting portion. When a precipitation hardening alloy is used as the material of the metal shaft, the precipitation hardening treatment is performed after the ceramic shaft and the metal shaft are joined.
In this case, the precipitation hardening alloy is preferably one or more of maraging steel, precipitation hardening stainless steel, and precipitation hardening superalloy.
また、金属軸表面の硬化を窒化で行う場合には、ステン
レス鋼、ニッケル・クロム・モリブデン鋼、クロム・モ
リブデン鋼、アルミニウム・クロム・モリブデン鋼、合
金工具鋼などクロムを含有する合金の何れか一種以上が
好ましい。さらにまた、金属軸の硬化を表面焼入れで行
う場合には、ニッケル・クロム・モリブデン鋼・クロム
・モリブデン鋼、ニッケル・クロム鋼、クロム鋼の何れ
か一種以上が好ましい。When the surface of the metal shaft is hardened by nitriding, any one of chromium-containing alloys such as stainless steel, nickel / chromium / molybdenum steel, chromium / molybdenum steel, aluminum / chromium / molybdenum steel, and alloy tool steel. The above is preferable. Furthermore, when the surface of the metal shaft is hardened, at least one of nickel / chromium / molybdenum steel / chromium / molybdenum steel, nickel / chromium steel, and chromium steel is preferable.
かかる金属軸の表面硬化は、セラミック軸と金属軸の結
合前あるいは結合後のいずれで行ってもよいが、金属軸
筒状部内径の仕上げ加工前に実施するのが好ましい。The surface hardening of the metal shaft may be carried out either before or after the bonding of the ceramic shaft and the metal shaft, but it is preferably carried out before finishing the inner diameter of the tubular portion of the metal shaft.
なお、窒化処理のように、金属軸表面に硬くて脆い化合
物層が形成する方法で表面の硬化処理をした金属軸に、
セラミック軸を嵌合して結合する場合には、嵌合による
金属軸の変形に上記化合物層の変形が追随できずクラッ
クが発生する。この場合には、金属軸表面の一部に非表
面硬化帯を設け、セラミック軸と金属軸の嵌合による金
属軸の変形がこの非表面硬化帯で生ずようにするのが好
ましい。Incidentally, like the nitriding treatment, the metal shaft having the surface hardened by a method of forming a hard and brittle compound layer on the surface of the metal shaft,
When the ceramic shafts are fitted and joined together, the deformation of the metal shaft due to the fitting cannot follow the deformation of the compound layer, and cracks occur. In this case, it is preferable to provide a non-surface hardening zone on a part of the surface of the metal shaft so that the deformation of the metal shaft due to the fitting of the ceramic shaft and the metal shaft does not occur in this non-surface hardening zone.
本発明のタービンローターの金属軸筒状部の硬さは、金
属軸の材料が析出硬化型合金かなる場合には、その合金
の析出硬化で得られる硬さとする。金属軸の材料が析出
硬化型合金以外の金属材料からなる場合には、熱処理で
硬さをHV250〜450に調整する。When the material of the metal shaft of the turbine rotor of the present invention is a precipitation hardening alloy, the hardness of the metal shaft is the hardness obtained by precipitation hardening of the alloy. When the material of the metal shaft is made of a metal material other than the precipitation hardening alloy, the hardness is adjusted to HV250-450 by heat treatment.
金属軸表面の特定部位について、上記以外の硬さが必要
な場合には、前述した表面硬化を行う。セラミック軸と
金属軸の結合が嵌合による場合には、金属軸筒状部の硬
さがHV250以下ではセラミック軸と金属軸の結合力が不
足するので好ましくない。また、硬さがHV450を越す
と、嵌合時に金属軸筒状部の破壊が生じやすくなるので
好ましくない。When a hardness other than the above is required for a specific portion of the surface of the metal shaft, the surface hardening described above is performed. When the ceramic shaft and the metal shaft are joined by fitting, it is not preferable that the hardness of the tubular portion of the metal shaft is HV250 or less because the binding force between the ceramic shaft and the metal shaft is insufficient. Further, if the hardness exceeds HV450, the metal shaft tubular portion is easily broken during fitting, which is not preferable.
つぎに図面により本発明をさらに詳しく説明する。第１
図ないし第２図は本発明のタービンローターを使用して
ターボチャージャーとする場合の具体例の構造を示した
ものである。Next, the present invention will be described in more detail with reference to the drawings. First
1 to 2 show the structure of a concrete example of a turbocharger using the turbine rotor of the present invention.
第１図はセラミック製翼車１と一体的に形成されている
セラミック製軸２の主要部分が金属軸筒状部３で被覆さ
れている本発明のターボチャージャー用タービンロータ
ーの部分縦断面図である。セラミック軸とセラミック翼
車の接続部には応力集中を緩和するため丸み４が設けて
ある。金属軸は直径の異なる３つの部分から構成されて
いる。これらの部分はそれぞれセラミック翼車に隣接し
潤滑油の密封と取付に必要なすべての形状要素、例えば
オイルスリンガー、オイルシールリング溝（いずれも図
示せず）などを設けるための部分５、ベアリングユニッ
ト内で軸受６に支承される軸部７（以下ベアリング取付
軸という）およびコンプレッサー翼車取付軸部８であ
る。金属軸の上記5,7の部分には筒状部３が設けられて
いる。該筒状部３の内面は開放端側の内径D1が底部側の
内径D2より大であり、セラミック軸と金属軸は該筒状部
の小径部で結合されている。FIG. 1 is a partial longitudinal sectional view of a turbine rotor for a turbocharger of the present invention in which a main portion of a ceramic shaft 2 integrally formed with a ceramic impeller 1 is covered with a metal shaft tubular portion 3. is there. A roundness 4 is provided at the connecting portion between the ceramic shaft and the ceramic impeller to reduce stress concentration. The metal shaft is composed of three parts having different diameters. Each of these parts is adjacent to the ceramic impeller and is provided with all shape elements necessary for sealing and mounting the lubricating oil, for example, an oil slinger, an oil seal ring groove (neither of which is shown) 5 and a bearing unit. A shaft portion 7 (hereinafter referred to as a bearing mounting shaft) and a compressor impeller mounting shaft portion 8 which are supported by the bearing 6 therein. A tubular portion 3 is provided at the above-mentioned portions 5 and 7 of the metal shaft. The inner surface of the cylindrical portion 3 has an inner diameter D 1 on the open end side larger than the inner diameter D 2 on the bottom side, and the ceramic shaft and the metal shaft are connected by the small diameter portion of the cylindrical portion.
該筒状部内径の小径部の位置は、セラミック軸と金属軸
の結合部がベアリング取付軸７の軸受当接部の間に位置
するように決められている。金属軸筒状部開放端先端と
セラミック翼車背面との間には隙間９が設けてある。こ
の隙間の大きさは本発明のタービンローターの使用温度
において、該筒状部先端がセラミック翼車背面に接触し
ない大きさとする。この隙間が存在しない場合には、タ
ービンローターの使用に際し、軸部の温度が上昇する
と、金属軸の方がセラミック軸より熱膨張が大きいため
セラミック翼車背面を金属軸筒状部先端が押し、セラミ
ック軸に引張応力が発生してセラミック軸が破壊するこ
とがある。The position of the small-diameter portion of the inner diameter of the cylindrical portion is determined so that the connecting portion of the ceramic shaft and the metal shaft is located between the bearing contact portions of the bearing mounting shaft 7. A gap 9 is provided between the tip of the open end of the metal shaft tubular portion and the rear surface of the ceramic impeller. The size of this gap is such that the tip of the tubular portion does not contact the rear surface of the ceramic impeller at the operating temperature of the turbine rotor of the present invention. If this gap does not exist, when the temperature of the shaft rises when using the turbine rotor, the metal shaft has a larger thermal expansion than the ceramic shaft, so the tip of the metal shaft tubular part pushes the rear surface of the ceramic impeller, A tensile stress may be generated in the ceramic shaft and the ceramic shaft may be broken.
金属軸筒状部内径の大径部の内径D1の大きさはセラミッ
ク軸の直径以上とし、上記大径部内表面とセラミック軸
表面との間には断熱のための空隙を設ける。The inner diameter D 1 of the large diameter portion of the inner diameter of the metal shaft tubular portion is equal to or larger than the diameter of the ceramic shaft, and a space for heat insulation is provided between the inner surface of the large diameter portion and the ceramic shaft surface.
このタービンローターは例えばつぎのようにして製造す
ることができる。This turbine rotor can be manufactured, for example, as follows.
まず、窒化珪素でタービン翼車１とタービン軸２を一体
的に形成する。しかるのち、このタービン軸を所定寸法
に仕上げ加工する。つぎに、未析出硬化状態の時効硬化
型合金からなる金属軸の一端に開放端側の内径D1がセラ
ミック軸直径より大きく、底部側の内径D2がセラミック
軸直径より小さい所定形状の筒状部３を加工する。さら
に金属軸の外周をほぼ所定形状に近い形状に粗加工す
る。その後、該金属軸の析出硬化温度以下の温度で、こ
の金属軸の筒状部内径の小径部にタービン軸のセラミッ
ク軸を圧入して、セラミック軸と金属軸を結合して第１
図に示す形状のタービンローターとする。つぎに、該タ
ービンローターを所定の析出硬化処理温度に所定時間加
熱して金属軸を硬化させたのち、タービンローターの外
径を所定の寸法と形状に仕上げ、本発明のタービンロー
ターとする。First, the turbine wheel 1 and the turbine shaft 2 are integrally formed of silicon nitride. Then, the turbine shaft is finished into a predetermined size. Then, the inner diameter D 1 of the open end side to one end of the metal shaft consisting of age hardened alloy of non-precipitation hardening state is larger than the ceramic shaft diameter, the bottom side of the inner diameter D 2 is cylindrical smaller predetermined shape than ceramic shaft diameter The part 3 is processed. Further, the outer circumference of the metal shaft is roughly processed into a shape close to a predetermined shape. Then, at a temperature not higher than the precipitation hardening temperature of the metal shaft, the ceramic shaft of the turbine shaft is press-fitted into the small-diameter portion of the inner diameter of the tubular portion of the metal shaft to connect the ceramic shaft and the metal shaft to each other, and
The turbine rotor has the shape shown in the figure. Next, the turbine rotor is heated to a predetermined precipitation hardening treatment temperature for a predetermined time to harden the metal shaft, and then the outer diameter of the turbine rotor is finished to a predetermined size and shape to obtain the turbine rotor of the present invention.
第２図はセラミック製翼車１と一体的に形成されている
セラミック製軸２の一部分が金属軸筒状部３で被覆され
ている本発明のターボチャージャー用タービンローター
の部分縦断面図である。FIG. 2 is a partial longitudinal sectional view of a turbine rotor for a turbocharger of the present invention in which a ceramic shaft 2 formed integrally with a ceramic impeller 1 is partially covered with a metal shaft tubular portion 3. .
セラミック軸はセラミック翼車に隣接しかつ直径が大で
ある部分10と金属軸筒状部３で被覆され、直径が小であ
る部分２とから構成されている。セラミック軸の大径部
10とセラミック翼車の接続部およびセラミック軸の大径
部10と小径部２の接続部には丸み11と12が設けられてい
る。セラミック軸の大径部10の外周部には潤滑油の密封
と取付に必要なすべての形状要素（図示せず）が設けら
れている。金属軸はベアリング内で軸受６に支承される
軸部７（ベアリング取付軸）とコンプレッサー翼車取付
軸８からなり、ベアリング取付軸７の内部には筒状部３
が設けられている。該筒状部３の内面は開放端側の内径
D1が底部側の内径D2より大であり、セラミック軸と金属
軸は該筒状部内径の小径部で結合されている。The ceramic shaft is composed of a portion 10 adjacent to the ceramic impeller and having a large diameter, and a portion 2 covered with a metal shaft tubular portion 3 and having a small diameter. Large diameter part of ceramic shaft
Roundnesses 11 and 12 are provided at the connecting portion between 10 and the ceramic impeller and at the connecting portion between the large diameter portion 10 and the small diameter portion 2 of the ceramic shaft. On the outer peripheral portion of the large diameter portion 10 of the ceramic shaft, all the shape elements (not shown) necessary for sealing and mounting the lubricating oil are provided. The metal shaft is composed of a shaft portion 7 (bearing mounting shaft) supported by the bearing 6 in the bearing and a compressor impeller mounting shaft 8. Inside the bearing mounting shaft 7, the cylindrical portion 3 is provided.
Is provided. The inner surface of the tubular portion 3 has an inner diameter on the open end side.
D 1 is larger than the inner diameter D 2 on the bottom side, and the ceramic shaft and the metal shaft are connected at the small diameter portion of the inner diameter of the tubular portion.
該小径部はベアリング取付軸７の軸受当接部の間に位置
している。金属軸筒状部開放端先端とセラミック軸大径
部先端との間には隙間13が設けられている。また、金属
軸筒状部内径の大径部の内径D1の大きさはセラミック軸
２の直径以上であり、上記大径部内表面とセラミック軸
２表面との間には断熱のための空隙が設けてある。The small diameter portion is located between the bearing contact portions of the bearing mounting shaft 7. A gap 13 is provided between the tip of the open end of the cylindrical portion of the metal shaft and the tip of the large diameter portion of the ceramic shaft. Further, the size of the inner diameter D 1 of the large diameter portion of the inner diameter of the cylindrical portion of the metal shaft is equal to or larger than the diameter of the ceramic shaft 2, and there is a gap for heat insulation between the inner surface of the large diameter portion and the surface of the ceramic shaft 2. It is provided.
このタービンローターは例えば次のようにして作ること
ができる。窒化珪素でタービン翼車１とタービン軸を一
体的に形成する。しかるのち、このタービン軸を所定の
形状と寸法に加工する。一方、焼入れ、焼もどしで硬さ
を調整した金属軸の特定表面について、必要に応じて表
面硬化処理を行う。しかるのち、該金属軸の一端に開放
端側の内径D1がセラミック軸２の直径より大きく、底部
側の内径D2がセラミック軸２の直径より小さい筒状部を
加工する。This turbine rotor can be manufactured, for example, as follows. The turbine wheel 1 and the turbine shaft are integrally formed of silicon nitride. Then, the turbine shaft is processed into a predetermined shape and size. On the other hand, a specific surface of the metal shaft whose hardness has been adjusted by quenching and tempering is subjected to a surface hardening treatment, if necessary. After that, a cylindrical portion whose inner diameter D 1 on the open end side is larger than the diameter of the ceramic shaft 2 and whose inner diameter D 2 on the bottom side is smaller than the diameter of the ceramic shaft 2 is machined at one end of the metal shaft.
つぎに、金属軸の外周を所定形状と寸法に近い形状に粗
加工する。この金属軸筒状部３の内径の小径部にセラミ
ック軸２を、金属軸の焼もどし温度以下の温度で圧入し
て第２図に示す形状のタービンローターとする。Next, the outer periphery of the metal shaft is roughly processed into a shape close to a predetermined shape and dimensions. The ceramic shaft 2 is press-fitted into the small-diameter portion of the inner diameter of the metal shaft tubular portion 3 at a temperature not higher than the tempering temperature of the metal shaft to obtain a turbine rotor having the shape shown in FIG.
このタービンローターの外形を所定の形状と寸法に仕上
げ加工して、本発明のタービンローターとする。The outer shape of this turbine rotor is finished into a predetermined shape and size to obtain the turbine rotor of the present invention.
（実施例） 実施例１ 直径61mmのタービン翼車と直径9mm、長さ51mmのセラミ
ック軸を常圧焼結法による窒化珪素で一体的に作製し
た。その後タービン翼車とセラミック軸の接続部に半径
4mm以上の丸みを加工するとともにセラミック軸を直径6
mmに加工し、さらにセラミック軸先端にテーパ部を設け
た。また、固溶体化処理済の全長130mm、直径20mmの析
出硬化系ステンレス鋼(JIS-SUS630)の一端に開放端から
深さ32mmまでの内径が6.1mm、深さ32mmから50mmまでの
内径が5.8mmである深さ50mmの筒状部３を加工した。つ
ぎにこの析出硬化系ステンレス鋼の筒状部を設けた端部
側の外周に、オイルスリンガーとオイルシール溝からな
る潤滑油の密封と取付のための形状要素を加工するとと
もに、ベアリング取付軸とコンプレッサー翼車取付軸を
それぞれ仕上げ寸法よりやや大きな寸法に加工して、金
属軸を作製した。しかるのち、該金属軸筒状部にセラミ
ック軸を350℃で圧入してタービン翼車が窒化珪素、タ
ービン軸が析出硬化系ステンレス鋼からなる第１図に示
す形状のターボチャージャー用タービンローターを作製
した。このターボチャージャー用タービンローターを42
0℃で10時間加熱して析出硬化処理を行い析出硬化系ス
テンレス鋼を硬化させたのち所定寸法に仕上げ加工し
た。このターボチャージャー用タービンローターを高温
回転試験装置に組込んで、燃焼ガスにより150,000rpmで
100時間の回転試験を行ったが何ら異常は認められなか
った。(Example) Example 1 A turbine wheel having a diameter of 61 mm and a ceramic shaft having a diameter of 9 mm and a length of 51 mm were integrally manufactured from silicon nitride by an atmospheric pressure sintering method. Then the radius of the connection between the turbine wheel and the ceramic shaft
Processing a roundness of 4 mm or more and a ceramic shaft with a diameter of 6
It was machined to mm, and a taper portion was provided at the tip of the ceramic shaft. In addition, the solid solution treated total length 130 mm, diameter 20 mm precipitation hardening stainless steel (JIS-SUS630) at one end has an inner diameter of 6.1 mm from the open end to a depth of 32 mm, and an inner diameter of 5.8 mm from a depth of 32 mm to 50 mm. The cylindrical portion 3 having a depth of 50 mm was processed. Next, on the outer periphery on the end side where the tubular portion of this precipitation hardening stainless steel is provided, a shape element for sealing and mounting lubricating oil consisting of an oil slinger and an oil seal groove is processed, and a bearing mounting shaft and Each of the compressor impeller mounting shafts was machined to a size slightly larger than the finished size to produce a metal shaft. Thereafter, a ceramic shaft was press-fitted into the metal shaft tubular portion at 350 ° C. to produce a turbine rotor for turbocharger having a shape shown in FIG. 1, in which the turbine wheel is made of silicon nitride and the turbine shaft is made of precipitation hardening stainless steel. did. 42 turbine rotors for this turbocharger
Precipitation hardening treatment was performed by heating at 0 ° C. for 10 hours to harden the precipitation hardening stainless steel, and then finish processing to a predetermined size. This turbine rotor for turbocharger was installed in a high-temperature rotation tester, and combustion gas at 150,000 rpm
A rotation test was performed for 100 hours, but no abnormality was found.
実施例２ 直径61mmのタービン翼車と直径20mm、長さ51mmのセラミ
ック軸を常圧焼結法による窒化珪素で一体的に作製し
た。しかるのち、セラミック軸先端から34mmまでの部分
を直径6mm、34mmからタービン翼車背面までの部分を直
径18mmに加工するとともに、セラミック軸大径部と小径
部の接続部およびタービン翼車背面とセラミック軸大径
部の接続部にそれぞれ所定の丸ミを加工し、セラミック
軸先端にはテーパ部を設けた。また直径10mm、長さ115m
mのアルミニウム・クロム・モリブデン鋼(JIS-SACM64
5、以下窒化鋼という）丸棒を930℃に１時間加熱保持後
窒温の水中に焼入れし、その後600℃に１時間加熱保持
して焼もどしを行い、硬さをHV350に調整した。Example 2 A turbine wheel having a diameter of 61 mm and a ceramic shaft having a diameter of 20 mm and a length of 51 mm were integrally made of silicon nitride by an atmospheric pressure sintering method. After that, the portion from the tip of the ceramic shaft to 34 mm is processed to have a diameter of 6 mm, and the portion from 34 mm to the rear surface of the turbine impeller is processed to have a diameter of 18 mm, and the connection between the large diameter portion and the small diameter portion of the ceramic shaft and the rear surface of the turbine impeller and the ceramic. Predetermined rounded portions were machined at the connecting portion of the large diameter portion of the shaft, and a taper portion was provided at the tip of the ceramic shaft. Also diameter 10mm, length 115m
m aluminum / chrome / molybdenum steel (JIS-SACM64
(5, hereinafter referred to as nitrided steel) A round bar was heated and held at 930 ° C. for 1 hour, quenched in water at a nitrogen temperature, and then heated and held at 600 ° C. for 1 hour to be tempered to adjust the hardness to HV350.
この丸棒の直径を9.2mmに加工したのち、一端から16mm
離れた位置から34mm離れた位置までの区間（第２図のＡ
区間）の外表面を長さ18mmの軟鋼製カバーで覆い、残り
の部分の外表面を圧力：4Torrの等量の窒素と水素から
なる混合雰囲気中で550℃に加熱しながら20時間イオン
窒化処理を行い、表面硬化させた。上記条件でのイオン
窒化処理により、窒化処理部表面の硬さは、窒化処理前
のHV350からHV1100まで増加した。また、表面から0.2mm
の深さの位置での硬さはHV700を示した。16mm from one end after processing the diameter of this round bar to 9.2mm
Section from the distant position to the position 34mm away (A in Fig. 2)
The outer surface of the section) is covered with a 18 mm long mild steel cover, and the remaining outer surface is ion-nitrided for 20 hours while being heated to 550 ° C in a mixed atmosphere consisting of equal amounts of nitrogen and hydrogen at a pressure of 4 Torr. Then, the surface was hardened. By the ion nitriding treatment under the above conditions, the hardness of the surface of the nitriding portion increased from HV350 before nitriding treatment to HV1100. Also, 0.2mm from the surface
The hardness at the depth position of HV700 was HV700.
一方、軟鋼製カバーで被覆した幅18mmの区間の表面硬さ
は窒化処理前と同じHV350を示し、該区間の表面には窒
化物の生成も認められなかった。On the other hand, the surface hardness of the 18 mm wide section covered with the mild steel cover showed the same HV350 as that before the nitriding treatment, and no nitride was observed on the surface of the section.
このようにして得た一方の端面近くに幅18mmの非表面硬
化部を有する窒化鋼丸棒の非表面硬化部側端面から深さ
17mmまでの内径が6.1mm、深さ17mmから33mmまでの内径
が5.8mmである深さ33mmの筒状部を加工して金属軸を作
製した。しかるのち、該金属軸筒状部にセラミック軸を
350℃で圧入し、圧入にともなう金属軸筒状部の変形を
上記非表面硬化部内に限定せしめて、タービン翼車およ
びタービン軸の一部が窒化珪素、タービン軸の一部が窒
化鋼からなるタービンローターを作製した。このタービ
ンローターのタービン軸の外周に潤滑油の密封と取付の
ための形状要素（図示せず）、直径9.0mmのベアリング
取付軸、直径6.4mmのコンプレッサー翼車取付軸をそれ
ぞれ所定の形状に加工して、第２図に示す形状でベアリ
ング取付軸のベアリング当接部の表面硬さがHV700以上
であるターボチャージャー用タービンローターを作製し
た。The depth from the end surface on the non-surface hardened part side of the nitrided steel round bar having the non-surface hardened part with a width of 18 mm near one end surface obtained in this way
A metal shaft was produced by processing a cylindrical part having an inner diameter of up to 17 mm of 6.1 mm and an inner diameter of 17 mm to 33 mm of 5.8 mm and a depth of 33 mm. Then, attach the ceramic shaft to the tubular part of the metal shaft.
Press-fitting at 350 ° C, the deformation of the metal shaft tubular part due to the press-fitting is limited to the non-surface hardened part, and the turbine impeller and part of the turbine shaft are made of silicon nitride, and part of the turbine shaft is made of nitrided steel. A turbine rotor was produced. The turbine rotor shaft of this turbine rotor has a shape element (not shown) for sealing and mounting lubricating oil, a bearing mounting shaft with a diameter of 9.0 mm, and a compressor impeller mounting shaft with a diameter of 6.4 mm, each machined into a specified shape. Then, a turbine rotor for a turbocharger having a shape shown in FIG. 2 in which the surface hardness of the bearing contact portion of the bearing mounting shaft is HV700 or more was manufactured.
このターボチャージャー用タービンローターを高温回転
試験装置に組込んで、燃焼ガスにより150,000rpmで100
時間の回転試験を行ったが何ら異常は認められなかっ
た。This turbocharger turbine rotor was installed in a high-temperature rotation tester, and combustion gas produced 100 rpm at 150,000 rpm.
A time rotation test was conducted, but no abnormality was found.
なお、セラミック軸と金属軸の結合が接合でなされる場
合は、結合部の金属軸に変形が生じないので、金属軸の
結合部表面に非硬化帯を設ける必要がない。When the ceramic shaft and the metal shaft are joined by joining, the metal shaft of the joint does not deform, so that it is not necessary to provide an uncured zone on the surface of the joint of the metal shaft.
実施例３ 実施例１と２に使用したターボチャージャー用タービン
ローターと同一構造のタービンローターについて、高温
回転試験中に故意にセラミック軸部を破損させた。第１
の構造のタービンローターについてはセラミック軸が破
損しても、潤滑油のタービンハウジング内への漏出は全
く生じなかった。第２図の構造のタービンローターにつ
いても、潤滑油のタービンハウジング内への漏出は僅か
であり、使用上の重大な障害とはならなかった。Example 3 With respect to the turbine rotor having the same structure as the turbine rotor for a turbocharger used in Examples 1 and 2, the ceramic shaft portion was intentionally broken during the high temperature rotation test. First
Regarding the turbine rotor having the above structure, even if the ceramic shaft was broken, no leakage of lubricating oil into the turbine housing occurred. Also in the turbine rotor having the structure shown in FIG. 2, the leakage of lubricating oil into the turbine housing was slight, and it did not cause a serious obstacle in use.
実施例４ 直径10mm、長さ115mmのニッケル・クロム・モリブデン
鋼(JIS-SNCM420)丸棒を850℃で0.5時間加熱保持したの
ち油冷して焼入れし、その後500℃に１時間加熱保持し
て焼もどしを行い、硬さをHv370に調整した。この丸棒
を直径9.2mmに加工したのち、一端から50mmの区間につ
いて、表面から深さ２mmのところまで高周波焼入れによ
り表面硬化させた。しかるのち、350℃で１時間加熱保
持して焼もどしを行い、表面硬化部の硬さをHv430に調
整した。この表面硬化済丸棒の表面硬化部側端面から深
さ17mmまでの内径が6.1mm、深さ17mmから33mmまでの内
径が5.8mmである深さ33mmの筒状部を加工して金属軸を
作製した。Example 4 A nickel-chromium-molybdenum steel (JIS-SNCM420) round bar having a diameter of 10 mm and a length of 115 mm was heated and held at 850 ° C. for 0.5 hours, then oil-cooled and quenched, and then heated and held at 500 ° C. for 1 hour. It was tempered and the hardness was adjusted to Hv370. After processing this round bar to a diameter of 9.2 mm, the surface of 50 mm from one end was hardened by induction hardening to a depth of 2 mm from the surface. After that, tempering was performed by heating and holding at 350 ° C. for 1 hour, and the hardness of the surface-hardened portion was adjusted to Hv430. This surface-hardened round bar has an inner diameter of 6.1 mm from the end surface on the surface hardened side to a depth of 17 mm, and an inner diameter of 5.8 mm from a depth of 17 mm to 33 mm is machined into a cylindrical part with a depth of 33 mm to form a metal shaft. It was made.
この金属軸の筒状部に実施例２に記載のセラミック軸と
同一形状、同一寸法のセラミック軸をするセラミック製
タービン翼車のセラミック軸を350℃で圧入し、タービ
ン翼車およびタービン軸の一部が窒化珪素、タービン軸
の一部がニッケル・クロム・モリブデン鋼からなるター
ビンローターを作製した。The ceramic shaft of a ceramic turbine wheel having a ceramic shaft of the same shape and dimensions as the ceramic shaft of the second embodiment is press-fitted into the tubular portion of this metal shaft at 350 ° C. A turbine rotor having a part made of silicon nitride and a part of the turbine shaft made of nickel / chromium / molybdenum steel was manufactured.
このタービンローターのベアリング取付軸とコンプレッ
サー翼車取付軸をそれぞれ直径9.0mm、6.4mmに加工し
て、第２図に示す形状で、金属軸部表面の硬さがHv43
0、金属軸中心部の硬さがHv370であるターボチャージャ
ー用タービンローターを作製した。The bearing mounting shaft and compressor impeller mounting shaft of this turbine rotor were machined to diameters of 9.0 mm and 6.4 mm, respectively, and had the shape shown in Fig. 2 and the hardness of the metal shaft surface was Hv43.
A turbine rotor for a turbocharger having a hardness of 0 and a metal shaft center portion of Hv370 was manufactured.
上記タービンローターの軸部について、350℃でねじり
トルクを測定したところ3.0kg・ｍでセラミック軸が破
損した。When the torsional torque of the shaft portion of the turbine rotor was measured at 350 ° C., the ceramic shaft was broken at 3.0 kg · m.
実施例５ 溶体化処理済の全長130mm、直径20mmの析出硬化系ステ
ンレス鋼(JIS-SUS630)の一端に、開放端から深さ32mmま
での内径が6.1mm、深さ32mmから50mmまでの内径が5.8mm
である深さ50mmの筒状部３を加工した。この析出硬化系
ステンレス鋼の筒状部を設けた端部側の外周に、オイル
スリンガーと、オイルシール溝などからなる潤滑油の密
封と取付のための形状要素を加工するとともにベアリン
グ取付軸とコンプレッサー翼車取付軸をそれぞれ仕上げ
寸法より直径で0.2mm大きな寸法に加工して金属軸を作
製した。Example 5 At one end of solution-treated precipitation-hardening stainless steel (JIS-SUS630) with a total length of 130 mm and a diameter of 20 mm, the inner diameter from the open end to the depth of 32 mm was 6.1 mm, and the inner diameter from the depth of 32 mm to 50 mm was 5.8 mm
The cylindrical portion 3 having a depth of 50 mm was processed. On the outer circumference of the end side where the cylindrical part of this precipitation hardening stainless steel is provided, an oil slinger and a shape element for sealing and mounting the lubricating oil, such as an oil seal groove, are processed and the bearing mounting shaft and compressor Each of the impeller mounting shafts was machined to a size 0.2 mm larger in diameter than the finished size to produce a metal shaft.
しかるのち、該金属軸筒状部に実施例１に記載のセラミ
ック軸と同一形状、同一寸法のセラミック軸を有するセ
ラミック製タービン翼車のセラミック軸を350℃で圧入
し、タービン翼車が窒化珪素、タービン軸が析出硬化系
ステンレス鋼からなる第１図に示す形状のターボチャー
ジャー用タービンローターを作製した。Then, the ceramic shaft of a ceramic turbine impeller having a ceramic shaft having the same shape and dimensions as the ceramic shaft described in Example 1 is press-fitted into the metal shaft cylindrical portion at 350 ° C., and the turbine impeller is made of silicon nitride. A turbine rotor for a turbocharger having a shape shown in FIG. 1 in which the turbine shaft is made of precipitation hardening stainless steel was manufactured.
上記タービンローターを圧力4Torrの等量の窒素と水素
からなる混合雰囲気中で420℃に加熱しながら10時間イ
オン窒化処理を行うと同時に析出硬化処理を行った。こ
の結果、金属軸内部の硬さは加熱前のHv320から450に増
加し、金属軸表面の硬さはHv600に増加した。The turbine rotor was heated at 420 ° C. in a mixed atmosphere consisting of equal amounts of nitrogen and hydrogen at a pressure of 4 Torr to perform ion nitriding treatment for 10 hours and simultaneously precipitation hardening treatment. As a result, the hardness inside the metal shaft increased from Hv320 before heating to 450, and the hardness of the metal shaft surface increased to Hv600.
このタービンローターの軸部について、350℃でねじり
トルクを測定したところ、3.5kg・ｍでセラミック軸が
破損した。When the torsional torque of the shaft portion of this turbine rotor was measured at 350 ° C., the ceramic shaft was broken at 3.5 kg · m.
なお、上記各実施例のタービンローターの構造と材料の
組合せおよび製造法は、上述した実施例の組合せに限定
されるものでないことは本発明の趣旨からして明らかで
ある。It is apparent from the spirit of the present invention that the combination of the structure and material of the turbine rotor of each of the above-described embodiments and the manufacturing method are not limited to the combination of the above-described embodiments.
（発明の効果） 以上述べたことから明らかなように、本発明のタービン
ローターはセラミック軸が金属軸に設けられた筒状部の
一部で固定され、しかも該筒状部のタービン翼車側内表
面とセラミック軸表面との間に断熱効果を有する空隙が
存在するとともに、セラミック軸と金属軸の結合部がベ
アリングハウジング内に位置し、潤滑油により強制的に
冷却されるため、結合部の温度上昇あるいは軸と平行方
向の温度勾配の存在がないため安定した結合強度が得ら
れる。また上記空隙の存在のため、金属軸筒状先端をタ
ービン翼車背面近傍まで延長し、該金属軸外周上に潤滑
油の密封や取付けの形状要素を設けたり、あるいは金属
軸筒状部先端を軸受部よりタービン翼車側へ位置させる
ことができる。このためセラミック軸が破損しても、タ
ービンハウジング内への潤滑油の漏出が起こらない。(Effect of the Invention) As is clear from the above description, the turbine rotor of the present invention is such that the ceramic shaft is fixed by a part of the tubular portion provided on the metal shaft, and the turbine rotor side of the tubular portion is fixed. There is a gap that has a heat insulating effect between the inner surface and the surface of the ceramic shaft, and the joint between the ceramic shaft and the metal shaft is located inside the bearing housing and is forcibly cooled by the lubricating oil. Since there is no temperature rise or temperature gradient parallel to the axis, stable bond strength can be obtained. Further, because of the presence of the above-mentioned gap, the metal shaft cylindrical tip is extended to the vicinity of the turbine impeller rear surface, and a shape element for sealing or mounting lubricating oil is provided on the outer circumference of the metal shaft, or the metal shaft cylindrical portion tip is It can be located closer to the turbine wheel than the bearing. Therefore, even if the ceramic shaft is damaged, the lubricating oil does not leak into the turbine housing.
このように本発明のタービンローターは、セラミックス
の耐熱性、耐摩耗性、高強度、低比重などの特性を生か
して応答性および安全性にすぐれたタービンローターと
することができるので、ターボチャージャー用タービン
ローターとして有用である。As described above, the turbine rotor of the present invention can be made into a turbine rotor excellent in responsiveness and safety by taking advantage of the heat resistance, wear resistance, high strength, and low specific gravity of ceramics. It is useful as a turbine rotor.
第１図ないし第２図は本発明のタービンローターの具体
的な一応用例のターボチャージャー用タービンローター
の構造を示す部分縦断面図である。 １…セラミックタービン翼車 ２…セラミック軸、３…金属軸筒状部 ４…丸み ５…密封と取付の形状要素を設けるための軸部 ６…軸受、７…ベアリング取付軸 ８…コンプレッサー翼車取付軸 ９…隙間、10…セラミック軸大径部 11…丸み、12…丸み 13…隙間1 and 2 are partial vertical cross-sectional views showing the structure of a turbine rotor for a turbocharger, which is one specific application example of the turbine rotor of the present invention. DESCRIPTION OF SYMBOLS 1 ... Ceramic turbine impeller 2 ... Ceramic shaft 3 ... Metal shaft Cylindrical part 4 ... Roundness 5 ... Shaft part for providing shape elements for sealing and mounting 6 ... Bearing, 7 ... Bearing mounting shaft 8 ... Compressor impeller mounting Shaft 9… Gap, 10… Large diameter part of ceramic shaft 11… Roundness, 12… Roundness 13… Gap
Claims (15)
るセラミック製軸が金属軸に設けられた有底中空筒状部
の一部で固定されてタービンシャフトを形成した構造の
タービンローターにおいて、上記中空筒状部は内径の異
なる筒状部で構成され、しかも該筒状部の開放端側の内
径が残りの筒状部の内径より僅かに大きく、セラミック
製軸と該金属軸との結合が中空筒状部の小径部でなされ
ているとともに、該結合部がベアリングハウジング内に
おいて前記タービンシャフトを支承する２個の軸受間に
位置し、しかも、該筒状部内径の大径部内表面とセラミ
ック製軸外表面の間に円筒状の空隙が存在し、しかも中
空筒状部の開放端先端と該セラミック製軸のセラミック
翼車への接続部との間に隙間が存在することを特徴とす
るタービンローター。1. A turbine rotor having a structure in which a ceramic shaft integrally formed with a ceramic impeller is fixed by a part of a bottomed hollow cylindrical portion provided on a metal shaft to form a turbine shaft. The hollow cylindrical portion is composed of cylindrical portions having different inner diameters, and the inner diameter on the open end side of the cylindrical portion is slightly larger than the inner diameters of the remaining cylindrical portions, so that the ceramic shaft and the metal shaft are The connection is made by the small diameter portion of the hollow cylindrical portion, the connection portion is located between two bearings that support the turbine shaft in the bearing housing, and the inner surface of the large diameter portion of the inner diameter of the cylindrical portion is located. And a ceramic shaft outer surface, there is a cylindrical gap, and there is a gap between the open end tip of the hollow cylindrical portion and the connecting portion of the ceramic shaft to the ceramic impeller. Turbine turbine .
形状要素が金属軸の筒状部端部外表面に設けられている
特許請求の範囲第１項記載のタービンローター。2. A turbine rotor according to claim 1, wherein a shape element for mounting a member for sealing the lubricating oil is provided on the outer surface of the end portion of the tubular portion of the metal shaft.
形状要素が金属軸筒状部外のセラミック製軸に設けられ
ている特許請求の範囲第１項記載のタービンローター。3. The turbine rotor according to claim 1, wherein the shape element for mounting the member for sealing the lubricating oil is provided on the ceramic shaft outside the metal shaft tubular portion.
嵌合である特許請求の範囲第１項ないし第３項のいずれ
かに記載のタービンローター。4. The turbine rotor according to any one of claims 1 to 3, wherein the ceramic shaft and the metal shaft tubular portion are fixed to each other by fitting.
接合である特許請求の範囲第１項ないし第３項のいずれ
かに記載のタービンローター。5. The turbine rotor according to any one of claims 1 to 3, wherein the ceramic shaft and the metal shaft tubular portion are fixed to each other by joining.
素、炭化珪素又はサイアロンからなり、金属軸がステン
レス鋼、ニッケル・クロム・モリブデン鋼、クロム・モ
リブデン鋼、アルミニウム・クロム・モリブデン鋼、マ
ルエージング鋼、析出硬化型ステンレス鋼又は析出硬化
型超合金の１種以上からなる特許請求の範囲第１項ない
し第５項のいずれかに記載のタービンローター。6. The impeller and the shaft integrated therewith are made of silicon nitride, silicon carbide or sialon, and the metal shaft is made of stainless steel, nickel-chromium-molybdenum steel, chromium-molybdenum steel, aluminum-chromium-molybdenum steel. A turbine rotor according to any one of claims 1 to 5, which comprises one or more of: maraging steel, precipitation hardening stainless steel, and precipitation hardening superalloy.
よび、あるいは窒化処理または高周波焼入れにより硬化
されている特許請求の範囲第１項ないし第６項のいずれ
かに記載のタービンローター。7. A turbine rotor according to any one of claims 1 to 6, wherein a part or all of the metal shaft is hardened by precipitation hardening and / or nitriding or induction hardening.
るセラミック製軸に金属軸を固定してタービンローター
とする方法において、金属軸の一端に、開放端側の内径
が底部側の内径より大である筒状部を設けたのち、該筒
状部にセラミック製軸を挿入し、筒状部内径の小径部で
セラミック製軸を固定するとともに該筒状部内径の大径
部内表面とセラミック製軸表面の間に空隙を設け、しか
も中空筒状部の開放端先端と該セラミック製軸のセラミ
ック翼車への接続部との間に隙間を設けることを特徴と
するタービンローターの製造法。8. A method for fixing a metal shaft to a ceramic shaft integrally formed with a ceramic impeller to form a turbine rotor, wherein one end of the metal shaft has an inner diameter on the open end side and an inner diameter on the bottom side. After providing a larger tubular portion, a ceramic shaft is inserted into the tubular portion, and the ceramic shaft is fixed by the small diameter portion of the inner diameter of the tubular portion and the inner surface of the large diameter portion of the inner diameter of the tubular portion is A method for manufacturing a turbine rotor, characterized in that a gap is provided between surfaces of a ceramic shaft and a gap is provided between a tip of an open end of a hollow cylindrical portion and a connecting portion of the ceramic shaft to a ceramic impeller. .
により硬さをHv250〜450に調整した金属軸との嵌合であ
る特許請求の範囲第８項に記載のタービンローターの製
造法。9. The method for manufacturing a turbine rotor according to claim 8, wherein the fixing of the ceramic shaft and the metal shaft is fitting with the metal shaft whose hardness is adjusted to Hv250 to 450 by heat treatment.
直径が小径部内径より0.1〜10％大であるセラミック製
軸の圧入である特許請求の範囲第８項又は第９項に記載
のタービンローターの製造法。10. The method according to claim 8 or 9, wherein the fitting is press fitting of a ceramic shaft having a diameter of 0.1 to 10% larger than the inner diameter of the small diameter portion with respect to the small diameter portion of the metal shaft tubular portion. Manufacturing method for turbine rotors in Japan.
もどし温度以下または嵌合部の最高使用温度以上の温度
における圧入で行う特許請求の範囲第８項ないし第10項
のいずれかに記載のタービンローターの製造法。11. The method according to any one of claims 8 to 10, wherein the fitting is performed by press-fitting at a temperature not higher than a tempering temperature of a material forming the metal shaft or not lower than a maximum operating temperature of the fitting portion. A method for manufacturing the described turbine rotor.
硬化処理温度以下の温度における圧入で行う特許請求の
範囲第８項ないし第10項のいずれかに記載のタービンロ
ーターの製造法。12. The method of manufacturing a turbine rotor according to claim 8, wherein the fitting is performed by press fitting at a temperature not higher than a precipitation hardening treatment temperature of a material forming the metal shaft.
行う特許請求の範囲第８項に記載のタービンローターの
製造法。13. The method of manufacturing a turbine rotor according to claim 8, wherein the ceramic shaft and the metal shaft are fixed by joining.
セラミック製軸と金属軸を嵌合する特許請求の範囲第８
項ないし第12項のいずれかに記載のタービンローターの
製造法。14. After nitriding a part of the surface of the metal shaft,
Claim 8 wherein the ceramic shaft and the metal shaft are fitted together.
Item 13. A method for manufacturing a turbine rotor according to any one of items 1 to 12.
入れで硬化したのち、セラミック製軸と金属軸を嵌合す
る特許請求の範囲第８項ないし第12項のいずれかに記載
のタービンローターの製造法。15. The turbine rotor according to claim 8, wherein a ceramic shaft and a metal shaft are fitted to each other after part or all of the surface of the metal shaft is hardened by induction hardening. Manufacturing method.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59221138A JPH0658044B2 (en) | 1984-10-23 | 1984-10-23 | Turbine rotor and method for producing the same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59221138A JPH0658044B2 (en) | 1984-10-23 | 1984-10-23 | Turbine rotor and method for producing the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61101601A JPS61101601A (en) | 1986-05-20 |
| JPH0658044B2 true JPH0658044B2 (en) | 1994-08-03 |
Family
ID=16762052
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59221138A Expired - Fee Related JPH0658044B2 (en) | 1984-10-23 | 1984-10-23 | Turbine rotor and method for producing the same |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0658044B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4749334A (en) * | 1984-12-06 | 1988-06-07 | Allied-Signal Aerospace Company | Ceramic rotor-shaft attachment |
| US4722630A (en) * | 1985-09-20 | 1988-02-02 | The Garrett Corporation | Ceramic-metal braze joint |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2728823C2 (en) * | 1977-06-27 | 1982-09-09 | Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal | Gas turbine |
| JPS56150801U (en) * | 1980-04-11 | 1981-11-12 | ||
| JPS5973502U (en) * | 1982-11-11 | 1984-05-18 | 株式会社小松製作所 | turbine rotor shaft |
| JPS59131502U (en) * | 1983-02-23 | 1984-09-04 | 株式会社小松製作所 | Centrifugal turbocharger rotor shaft connection device |
-
1984
- 1984-10-23 JP JP59221138A patent/JPH0658044B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61101601A (en) | 1986-05-20 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |