JP2010255438A - Turbocharger - Google Patents

Turbocharger Download PDF

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Publication number
JP2010255438A
JP2010255438A JP2009103171A JP2009103171A JP2010255438A JP 2010255438 A JP2010255438 A JP 2010255438A JP 2009103171 A JP2009103171 A JP 2009103171A JP 2009103171 A JP2009103171 A JP 2009103171A JP 2010255438 A JP2010255438 A JP 2010255438A
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Prior art keywords
shaft
stepped portion
impeller
turbine
rolling bearing
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Pending
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JP2009103171A
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Japanese (ja)
Inventor
Masakazu Tabata
正和 田畑
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Toyota Motor Corp
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Toyota Motor Corp
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Priority to JP2009103171A priority Critical patent/JP2010255438A/en
Publication of JP2010255438A publication Critical patent/JP2010255438A/en
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    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbocharger in which an impeller is tightened by a sufficient axial force while suppressing the bending deformation of a shaft. <P>SOLUTION: The turbocharger 1 includes: a turbine 2; a shaft 4 to which a first step 4d and a second step 4e are formed, and which is coaxial and integral with the turbine 2; an impeller 3 coaxially fitted at a side closer to a tip than the second step 4e of the shaft 4; rolling bearings 5A, 5B fitted between the first step 4d and second step 4e of the shaft 4 and rotatably support shaft 4; and impeller nuts 11 disposed at tips of the shaft 4 to tighten the impeller 3 and inner rings 5b of the rolling bearings 5A, 5B toward the first step 4d. A low-rigidity member 12 lower in rigidity than the shaft 4 is disposed between the inner ring 5b of the rolling bearing 5A on a turbine 2 side and the first step 4d. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、内燃機関等に用いられるターボチャージャに関する。   The present invention relates to a turbocharger used for an internal combustion engine or the like.

内燃機関等に用いられるターボチャージャとして、転がり軸受の内輪間にスペーサを配置して軸受間の距離を一定に保持しつつ、タービンと一体のシャフトの途中に設けられた段付部に内輪の端面を突き当て、それらの内輪とスペーサとを、シャフトの先端部に装着されたコンプレッサのインペラとともに締付具で締め付けることにより、その締付具とシャフトの段付部との間でインペラ、内輪及びスペーサを挟み込んだターボチャージャが知られている（例えば、特許文献１〜４）。その他、本発明に関連する先行技術文献として特許文献５が存在する。   As a turbocharger used in internal combustion engines, etc., spacers are arranged between the inner rings of rolling bearings, and the distance between the bearings is kept constant, while the end face of the inner ring is provided on a stepped portion provided in the middle of the shaft integral with the turbine. And tightening the inner ring and the spacer together with the impeller of the compressor attached to the tip of the shaft with a fastening tool, the impeller, the inner ring and the shaft between the fastening tool and the stepped part of the shaft. A turbocharger in which a spacer is sandwiched is known (for example, Patent Documents 1 to 4). In addition, there is Patent Document 5 as a prior art document related to the present invention.

特開２００８−８８８５５号公報JP 2008-88855 A 特開２００７−７１３５６号公報JP 2007-71356 A 特開２００８−２９８２８４号公報JP 2008-298284 A 特開２００５−１７２０９９号公報JP 2005-172099 A 特開２００６−２００６５１号公報JP 2006-200651 A

上述した従来のターボチャージャでは、タービン側の軸線回りのアンバランスがすべり軸受使用時よりも増加して高調波の騒音がより顕著に発生する傾向がある。その原因は、転がり軸受の内輪がシャフトに圧入されているため、シャフトの段付部の直角度、あるいは軸受の内輪の段付部と接触する端面の直角度がばらついているため、締付具を締め付けることによりタービンの近傍にてシャフトに曲げ変形が生じることにある。インペラを締め付ける軸力を下げればシャフトの曲げ変形を低減できるが、その場合にはインペラがシャフトに対して回転するおそれがある。   In the conventional turbocharger described above, the unbalance around the axis on the turbine side tends to increase more than when a slide bearing is used, and harmonic noise tends to occur more prominently. The cause is that because the inner ring of the rolling bearing is press-fitted into the shaft, the perpendicularity of the stepped portion of the shaft or the perpendicularity of the end surface contacting the stepped portion of the inner ring of the bearing varies. By tightening, the shaft is bent in the vicinity of the turbine. If the axial force for tightening the impeller is lowered, the bending deformation of the shaft can be reduced. In this case, the impeller may rotate with respect to the shaft.

そこで、本発明は、シャフトの曲げ変形を抑えつつインペラを十分な軸力で締め付けることが可能なターボチャージャを提供することを目的とする。   Therefore, an object of the present invention is to provide a turbocharger that can tighten an impeller with a sufficient axial force while suppressing bending deformation of the shaft.

本発明のターボチャージャは、タービンと、前記タービンと同軸かつ一体に設けられ、前記タービン側が大径となる第１段付部、及び該第１段付部よりも先端側に位置しかつ前記第１段付部側が大径となる第２段付部がそれぞれ形成されたシャフトと、前記シャフトの前記第２段付部よりも先端側に同軸上に嵌め合わされるインペラと、前記シャフトの前記第１段付部と前記第２段付部との間に嵌め合わされ、前記シャフトを回転自在に支持する転がり軸受と、前記シャフトの前記第１段付部と前記転がり軸受の内輪との間に配置される少なくとも一つの筒状部材と、前記シャフトの先端部に設けられて、前記インペラ、前記転がり軸受の内輪及び前記筒状部材を前記第１段付部に向かって締め付ける締付具と、を備え、前記筒状部材のうち、少なくとも一つの筒状部材が前記シャフトよりも剛性の低い低剛性部材とされたものである。   The turbocharger according to the present invention is provided with a turbine, a first stepped portion provided coaxially and integrally with the turbine, the turbine side having a large diameter, and located on a tip side of the first stepped portion and the first stepped portion. A shaft formed with a second stepped portion having a large diameter on the first stepped portion side, an impeller fitted coaxially to the tip side of the second stepped portion of the shaft, and the first of the shaft A rolling bearing that is fitted between the first stepped portion and the second stepped portion and rotatably supports the shaft, and is disposed between the first stepped portion of the shaft and the inner ring of the rolling bearing. And at least one cylindrical member, and a fastener provided at a tip portion of the shaft for tightening the impeller, an inner ring of the rolling bearing, and the cylindrical member toward the first stepped portion. Comprising the cylindrical member In which at least one tubular member is a lower low rigidity member rigidity than said shaft.

本発明のターボチャージャによれば、締付具にてインペラを締め付けると、低剛性部材が軸線方向に圧縮変形し、それにより、第２段付部よりもシャフトの先端側に組み付けられた部品がタービン側に変位して第２段付部に突き当たり、それ以降は締付具の締め付けによる軸力が第２段付部と締付具との間に限定されて作用する。これにより、転がり軸受の内輪に加わる軸力を制限してシャフトの曲げ変形を抑えつつ、インペラを十分な軸力で締め付けることができる。   According to the turbocharger of the present invention, when the impeller is tightened with the tightening tool, the low-rigidity member is compressed and deformed in the axial direction, so that the component assembled on the tip end side of the shaft with respect to the second stepped portion is It is displaced to the turbine side and hits the second stepped portion, and thereafter, the axial force due to the tightening of the fastener is limited and acts between the second stepped portion and the fastener. Thereby, the impeller can be tightened with a sufficient axial force while limiting the axial force applied to the inner ring of the rolling bearing and suppressing the bending deformation of the shaft.

本発明の第１の形態に係るターボチャージャの要部を示した軸線方向断面図。The axial direction sectional view which showed the principal part of the turbocharger which concerns on the 1st form of this invention. 図１のターボチャージャにおける転がり軸受周辺の拡大図。FIG. 2 is an enlarged view around a rolling bearing in the turbocharger of FIG. 1. 低剛性部材の斜視図。The perspective view of a low-rigidity member. 低剛性部材の正面図。The front view of a low-rigidity member. インペラナットの締付トルクと軸力との関係を示す図。The figure which shows the relationship between the tightening torque of an impeller nut, and axial force. 第１の形態に対する変形例を示す図。The figure which shows the modification with respect to a 1st form. 本発明の第２の形態に係るターボチャージャの転がり軸受周辺の拡大図。The enlarged view around a rolling bearing of a turbocharger concerning the 2nd form of the present invention.

（第１の形態）
図１に示すように、第１の形態に係るターボチャージャ１は、タービン２と、インペラ３と、それらを一体回転可能に連結するシャフト４とを備えている。タービン２は不図示のタービンハウジングに、インペラ３は不図示のコンプレッサハウジングにそれぞれ収容されている。タービン２とシャフト４とは同軸かつ一体に形成されている。シャフト４は、シャフト４は、タービン２側からインペラ３側に向かって大径部４ａ、中間部４ｂ及び小径部４ｃが順次設けられることにより、タービン２側が大径となる第１段付部４ｄ、及びその第１段付部４ｄよりも先端側に位置しかつ第１段付部４ｄ側が大径となる第２段付部４ｅがそれぞれ形成された段付きシャフトである。さらに、小径部４ｃの先端部には雄ねじ部４ｆが設けられている。 (First form)
As shown in FIG. 1, a turbocharger 1 according to a first embodiment includes a turbine 2, an impeller 3, and a shaft 4 that couples them so as to be integrally rotatable. The turbine 2 is accommodated in a turbine housing (not shown), and the impeller 3 is accommodated in a compressor housing (not shown). The turbine 2 and the shaft 4 are formed coaxially and integrally. The shaft 4 includes a first stepped portion 4d having a large diameter on the turbine 2 side by sequentially providing a large diameter portion 4a, an intermediate portion 4b, and a small diameter portion 4c from the turbine 2 side toward the impeller 3 side. , And a stepped shaft formed with a second stepped portion 4e that is located on the tip side of the first stepped portion 4d and has a large diameter on the first stepped portion 4d side. Further, a male screw portion 4f is provided at the tip of the small diameter portion 4c.

シャフト４は、その中間部４ｂに嵌め合わされた一対の転がり軸受５Ａ、５Ｂ（但し、両者を区別する必要がないときは転がり軸受５と表記する。）により、その軸線ＣＬの回りに回転自在に支持されている。転がり軸受５はアンギュラコンタクト型のボールベアリングである。転がり軸受５の外輪５ａはホルダ６に収容されている。ホルダ６は軸受ハウジング７の内周に収容されてリテーナ８で軸線方向に抜け止めされている。一方、転がり軸受５の内輪５ｂはシャフト４の中間部４ｂに圧入されている。内輪５ｂ間には、筒状部材の一つとしてのスペーサ９が設けられ、そのスペーサ９により内輪５ｂの間隔が適正値に調整されている。シャフト４の小径部４ｃには、シーリングカラー１０が嵌め合わされている。そのシーリングカラー１０よりもシャフト４の先端側にインペラ３が嵌め合わされている。シャフト４の雄ねじ部４ｆには、締付具としてのインペラナット１１が取り付けられている。インペラナット１１を締め付けることにより、シャフト４上の各部品が第１段付部４ｄとインペラナット１１との間に挟み込まれて保持される。   The shaft 4 is rotatable around its axis CL by a pair of rolling bearings 5A and 5B fitted to the intermediate portion 4b (in the case where it is not necessary to distinguish between the two), the shaft 4 is described as a rolling bearing 5. It is supported. The rolling bearing 5 is an angular contact ball bearing. The outer ring 5 a of the rolling bearing 5 is accommodated in the holder 6. The holder 6 is accommodated in the inner periphery of the bearing housing 7 and is retained by the retainer 8 in the axial direction. On the other hand, the inner ring 5 b of the rolling bearing 5 is press-fitted into the intermediate portion 4 b of the shaft 4. A spacer 9 as one of the cylindrical members is provided between the inner rings 5b, and the interval between the inner rings 5b is adjusted to an appropriate value by the spacer 9. A sealing collar 10 is fitted into the small diameter portion 4 c of the shaft 4. The impeller 3 is fitted on the distal end side of the shaft 4 with respect to the sealing collar 10. An impeller nut 11 as a fastening tool is attached to the male screw portion 4 f of the shaft 4. By tightening the impeller nut 11, each component on the shaft 4 is sandwiched and held between the first stepped portion 4 d and the impeller nut 11.

図２により詳しく示したように、シャフト４の第１段付部４ｄとタービン側の転がり軸受５Ａの内輪５ｂとの間には低剛性部材１２が設けられている。低剛性部材１２は、一例として図３Ａ及び図３Ｂに示すように、円筒体１２ａに、周方向に延びる適宜の本数（図では３本）のスリット１２ｂを形成した構成を備えることにより、その剛性がシャフト４のそれよりも低く設定された筒状部材である。   As shown in more detail in FIG. 2, a low-rigidity member 12 is provided between the first stepped portion 4d of the shaft 4 and the inner ring 5b of the turbine-side rolling bearing 5A. As shown in FIGS. 3A and 3B as an example, the low-rigidity member 12 is provided with a configuration in which an appropriate number (three in the drawing) of slits 12b extending in the circumferential direction is formed in the cylindrical body 12a. Is a cylindrical member set lower than that of the shaft 4.

以上の構成によれば、インペラナット１１を締め付けることにより、その軸力がインペラ３、シーリングカラー１０、転がり軸受５Ｂ、スペーサ９及び転がり軸受５Ａを順次経由して低剛性部材１２に伝わる。低剛性部材１２はシャフト４よりも剛性が低いため、軸力で低剛性部材１２が軸線方向に圧縮変形し、それにより、転がり軸受５Ａからインペラ３に至るまでのシャフト４上の各部品がタービン２側に変位してシーリングカラー１０が第２段付部４ｅに突き当たる。シーリングカラー１０が第２段付部４ｅに突き当たった後もインペラナット１１の締め付けを継続すると、それ以降に発生する軸力は第２段付部４ｅとインペラナット１１との間に介在するシーリングカラー１０及びインペラ３に限定して作用する。   According to the above configuration, when the impeller nut 11 is tightened, the axial force is transmitted to the low-rigidity member 12 via the impeller 3, the sealing collar 10, the rolling bearing 5B, the spacer 9, and the rolling bearing 5A sequentially. Since the low-rigidity member 12 is lower in rigidity than the shaft 4, the low-rigidity member 12 is compressed and deformed in the axial direction by an axial force, whereby each component on the shaft 4 from the rolling bearing 5A to the impeller 3 is converted into a turbine. The sealing collar 10 abuts against the second stepped portion 4e by being displaced to the second side. If the tightening of the impeller nut 11 is continued even after the sealing collar 10 hits the second stepped portion 4e, the axial force generated thereafter is a sealing collar interposed between the second stepped portion 4e and the impeller nut 11. 10 and impeller 3 only.

すなわち、図４に示したように、インペラナット１１の締付トルクがＴａに達したときにシーリングカラー１０が第２段付部４ｅに突き当たったとすれば、締付トルクＴａ未満の領域では、第１段付部４ｄとインペラナット１１との間に挟まれた各部品に実線Ｌ１で示す軸力が等しく作用する。しかし、締付トルクＴａ以上の領域では、第１段付部４ｄから転がり軸受５Ｂまでの部品の軸力が実線Ｌ２で示すように一定値Ｆａに保持される一方、第２段付部４ｅとインペラナット１１との間に挟まれたシーリングカラー１０及びインペラ３の軸力は破線Ｌ３で示すように締付トルクに比例して増加する。その結果、インペラナット１１の締め付けを完了したときの締付トルクＴｂに対して、インペラ３には軸力Ｆｂが、転がり軸受５には軸力Ｆａ（＜Ｆｂ）が作用する。仮に、低剛性部材１２を省略して従来と同様の構造でインペラナット１１を締め付けた場合には、インペラ３及び転がり軸受５の軸力が想像線Ｌ４で示すように軸力Ｆｂまで締付トルクに比例して増加する。このように、本形態のターボチャージャ１によれば、転がり軸受５の内輪５ｂに作用する軸力を従来よりも低く制限してシャフト４の特にタービン２側での曲げ変形を抑えつつ、インペラ３を従来構造と同様に十分な軸力で締め付けることができる。   That is, as shown in FIG. 4, if the sealing collar 10 hits the second stepped portion 4e when the tightening torque of the impeller nut 11 reaches Ta, in the region below the tightening torque Ta, The axial force indicated by the solid line L1 acts equally on each component sandwiched between the stepped portion 4d and the impeller nut 11. However, in the region of the tightening torque Ta or higher, the axial force of the parts from the first stepped portion 4d to the rolling bearing 5B is held at a constant value Fa as indicated by the solid line L2, while the second stepped portion 4e The axial force of the sealing collar 10 and the impeller 3 sandwiched between the impeller nut 11 increases in proportion to the tightening torque as indicated by the broken line L3. As a result, the axial force Fb acts on the impeller 3 and the axial force Fa (<Fb) acts on the rolling bearing 5 with respect to the tightening torque Tb when the tightening of the impeller nut 11 is completed. If the low rigidity member 12 is omitted and the impeller nut 11 is tightened with the same structure as in the prior art, the tightening torque is up to the axial force Fb as indicated by the imaginary line L4 in the impeller 3 and the rolling bearing 5. It increases in proportion to. Thus, according to the turbocharger 1 of this embodiment, the axial force acting on the inner ring 5b of the rolling bearing 5 is limited to be lower than that of the conventional one, and the bending deformation of the shaft 4 particularly on the turbine 2 side is suppressed, and the impeller 3 is suppressed. Can be tightened with a sufficient axial force as in the conventional structure.

なお、低剛性部材１２は図３Ａ及び図３Ｂに示した構成に限らず、シャフト４よりも低剛性である限り適宜に変更可能である。例えば、皿ばね、内輪５ｂに比して肉厚が薄い円筒体等を低剛性部材１２として利用してもよい。図５に示したように、第１段付部４ｄとの接触面側にスリット１３ａが形成された低剛性部材１３を、図２の低剛性部材１２に代えて転がり軸受５Ａの内輪５ｂと第１段付部４ｄとの間に配置してもよい。   The low-rigidity member 12 is not limited to the configuration shown in FIGS. 3A and 3B, and can be appropriately changed as long as the rigidity is lower than that of the shaft 4. For example, a disc body, a cylindrical body having a thinner wall thickness than the inner ring 5 b may be used as the low-rigidity member 12. As shown in FIG. 5, the low-rigidity member 13 having the slit 13a formed on the contact surface side with the first stepped portion 4d is replaced with the inner ring 5b of the rolling bearing 5A and the You may arrange | position between 4 d of 1 step parts.

（第２の形態）
次に、図６を参照して本発明の第２の形態に係るターボチャージャを説明する。なお、本形態のターボチャージャは第１の形態と比較して低剛性部材を変更したものである。従って、ターボチャージャの概略構成は図１を参照し、かつ、図６において図２との共通部分には同一の参照符号を付してそれらの説明を省略する。 (Second form)
Next, a turbocharger according to a second embodiment of the present invention will be described with reference to FIG. In addition, the turbocharger of this form changes the low-rigidity member compared with the 1st form. Therefore, referring to FIG. 1 for the schematic configuration of the turbocharger, and in FIG. 6, the same reference numerals are assigned to the parts common to FIG. 2, and the description thereof is omitted.

図６に示したように、本形態のターボチャージャ１では、図２の低剛性部材１２が省略されて転がり軸受５Ａの内輪５ｂが第１段付部４ｄに突き当てられている。一方、内輪５ｂ間には、図２のスペーサ９に代えて、両端部以外の内周にぬすみ部１３ａを設けて肉厚を減少させたスペーサ１４が低剛性部材として設けられている。本形態においても、インペラナット１１を締め付けることによりスペーサ１４が軸線方向に圧縮変形してシーリングカラー１０が第２段付部４ｅに突き当たり、それ以降は第１段付部４ｄから転がり軸受５Ｂまでの各部品に作用する軸力を一定値に制限しつつインペラ３に作用する軸力を高めることが可能である。   As shown in FIG. 6, in the turbocharger 1 of this embodiment, the low-rigidity member 12 of FIG. 2 is omitted, and the inner ring 5b of the rolling bearing 5A is abutted against the first stepped portion 4d. On the other hand, between the inner rings 5b, instead of the spacer 9 in FIG. 2, a spacer 14 is provided as a low-rigidity member in which a thinned portion 13a is provided on the inner periphery other than both end portions to reduce the thickness. Also in this embodiment, when the impeller nut 11 is tightened, the spacer 14 is compressed and deformed in the axial direction so that the sealing collar 10 hits the second stepped portion 4e, and thereafter, from the first stepped portion 4d to the rolling bearing 5B. It is possible to increase the axial force acting on the impeller 3 while restricting the axial force acting on each component to a constant value.

本発明は上述した形態に限定されることなく、適宜の形態で実施してよい。例えば、
シャフトの支持構造は図示例に限らず、転がり軸受が少なくとも一つ設けられている限り、本発明を適用することができる。図示の形態では、シーリングカラー１０が第２段付部４ｅに突き当てられているが、それに限らず、インペラ３又はこれと一体化された部材、あるいはインペラ３及びシーリングカラー１０のいずれとも異なる部品が第２段付部に突き当てられるようにしてもよい。第１段付部と転がり軸受の内輪との間に配置される筒状部材の個数は適宜に変更可能であり、少なくとも一つの筒状部材が低剛性部材とされていればよい。例えば、図２の低剛性部材１２又は図５の低剛性部材１３と、図６の低剛性部材としてのスペーサ１４とを組み合わせて使用してもよい。締付具はインペラナット１１に限らず、シャフトの先端側からインペラ等を第１段付部に向かって締め付けることができるものであれば適宜に変更可能である。 The present invention is not limited to the form described above, and may be implemented in an appropriate form. For example,
The shaft support structure is not limited to the illustrated example, and the present invention can be applied as long as at least one rolling bearing is provided. In the illustrated embodiment, the sealing collar 10 is abutted against the second stepped portion 4e. However, the present invention is not limited thereto, and the impeller 3 or a member integrated with the impeller 3 or a part different from both the impeller 3 and the sealing collar 10 is used. May be abutted against the second stepped portion. The number of cylindrical members disposed between the first stepped portion and the inner ring of the rolling bearing can be changed as appropriate, and at least one cylindrical member only needs to be a low-rigidity member. For example, the low-rigidity member 12 in FIG. 2 or the low-rigidity member 13 in FIG. 5 and the spacer 14 as the low-rigidity member in FIG. 6 may be used in combination. The fastening tool is not limited to the impeller nut 11 and can be appropriately changed as long as it can fasten the impeller and the like from the tip end side of the shaft toward the first stepped portion.

１ ターボチャージャ
２ タービン
３ インペラ
４ シャフト
４ｄ 第１段付部
４ｅ 第２段付部
５Ａ、５Ｂ 転がり軸受
５ｂ 転がり軸受の内輪
９ スペーサ（筒状部材）
１０ シーリングカラー
１１ インペラナット（締付具）
１２ 低剛性部材（筒状部材）
１２ａ 円筒体
１２ｂ スリット
１３ 低剛性部材（筒状部材）
１３ａ スリット
１４ スペーサ（筒状部材、低剛性部材） DESCRIPTION OF SYMBOLS 1 Turbocharger 2 Turbine 3 Impeller 4 Shaft 4d 1st step part 4e 2nd step part 5A, 5B Rolling bearing 5b Inner ring of a rolling bearing 9 Spacer (tubular member)
10 Sealing collar 11 Impeller nut (clamp)
12 Low rigidity member (tubular member)
12a Cylindrical body 12b Slit 13 Low rigidity member (tubular member)
13a Slit 14 Spacer (tubular member, low rigidity member)

Claims (1)

タービンと、
前記タービンと同軸かつ一体に設けられ、前記タービン側が大径となる第１段付部、及び該第１段付部よりも先端側に位置しかつ前記第１段付部側が大径となる第２段付部がそれぞれ形成されたシャフトと、
前記シャフトの前記第２段付部よりも先端側に同軸上に嵌め合わされるインペラと、
前記シャフトの前記第１段付部と前記第２段付部との間に嵌め合わされ、前記シャフトを回転自在に支持する転がり軸受と、
前記シャフトの前記第１段付部と前記転がり軸受の内輪との間に配置される少なくとも一つの筒状部材と、
前記シャフトの先端部に設けられて、前記インペラ、前記転がり軸受の内輪及び前記筒状部材を前記第１段付部に向かって締め付ける締付具と、を備え、
前記筒状部材のうち、少なくとも一つの筒状部材が前記シャフトよりも剛性の低い低剛性部材とされたターボチャージャ。 A turbine,
A first stepped portion that is coaxially and integrally provided with the turbine and has a large diameter on the turbine side, and a first stepped portion on the first stepped portion side of the first stepped portion and a large diameter on the first stepped portion side. A shaft formed with two stepped portions,
An impeller that is coaxially fitted to the tip side of the second stepped portion of the shaft;
A rolling bearing which is fitted between the first stepped portion and the second stepped portion of the shaft and rotatably supports the shaft;
At least one tubular member disposed between the first stepped portion of the shaft and an inner ring of the rolling bearing;
A clamp provided on the tip of the shaft for tightening the impeller, the inner ring of the rolling bearing, and the tubular member toward the first stepped portion;
A turbocharger in which at least one of the cylindrical members is a low-rigidity member whose rigidity is lower than that of the shaft.
JP2009103171A 2009-04-21 2009-04-21 Turbocharger Pending JP2010255438A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015200315A (en) * 2014-04-08 2015-11-12 エフピーティー モーターエンフォーシュング エージー Method of making pinion to be fitted to turbine axis of internal combustion engine
JP2015200314A (en) * 2014-04-08 2015-11-12 エフピーティー モーターエンフォーシュング エージー Method for making pinion to be attached to turbine axis of internal combustion engine
US20160281648A1 (en) * 2015-03-09 2016-09-29 Caterpillar Inc. Turbocharger and Method
US9683520B2 (en) 2015-03-09 2017-06-20 Caterpillar Inc. Turbocharger and method
US9739238B2 (en) 2015-03-09 2017-08-22 Caterpillar Inc. Turbocharger and method

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Publication number Priority date Publication date Assignee Title
JPS639429U (en) * 1986-07-03 1988-01-22
JPH04159421A (en) * 1990-10-19 1992-06-02 Toyota Motor Corp Structure of bearing of turbo charger

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS639429U (en) * 1986-07-03 1988-01-22
JPH04159421A (en) * 1990-10-19 1992-06-02 Toyota Motor Corp Structure of bearing of turbo charger

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015200315A (en) * 2014-04-08 2015-11-12 エフピーティー モーターエンフォーシュング エージー Method of making pinion to be fitted to turbine axis of internal combustion engine
JP2015200314A (en) * 2014-04-08 2015-11-12 エフピーティー モーターエンフォーシュング エージー Method for making pinion to be attached to turbine axis of internal combustion engine
US20160281648A1 (en) * 2015-03-09 2016-09-29 Caterpillar Inc. Turbocharger and Method
US9683520B2 (en) 2015-03-09 2017-06-20 Caterpillar Inc. Turbocharger and method
US9739238B2 (en) 2015-03-09 2017-08-22 Caterpillar Inc. Turbocharger and method
US9752536B2 (en) * 2015-03-09 2017-09-05 Caterpillar Inc. Turbocharger and method

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