JP5071150B2 - Bearing device for turbocharger - Google Patents

Bearing device for turbocharger Download PDF

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JP5071150B2
JP5071150B2 JP2008044326A JP2008044326A JP5071150B2 JP 5071150 B2 JP5071150 B2 JP 5071150B2 JP 2008044326 A JP2008044326 A JP 2008044326A JP 2008044326 A JP2008044326 A JP 2008044326A JP 5071150 B2 JP5071150 B2 JP 5071150B2
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preload
ball
pair
bearing
turbocharger
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JP2009204004A (en
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義樹 藤井
重徳 坂東
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JTEKT Corp
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JTEKT Corp
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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
    • F16C19/54—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
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Description

本発明は、自動車のターボチャージャの回転軸を回転自在に支持するターボチャージャ用軸受装置に関する。   The present invention relates to a turbocharger bearing device that rotatably supports a rotating shaft of a turbocharger of an automobile.

自動車のターボチャージャは、回転軸の一端側にタービンが取り付けられるとともに他端側にインペラが取り付けられ、回転軸の中間部がターボチャージャのハウジングの孔部に挿通されており、この中間部において、軸受装置により回転軸が回転可能に支持された構造になっている。
従来、かかるターボチャージャ用軸受装置として、単列のアンギュラ玉軸受を回転軸の軸方向両側にそれぞれ配置し、これらの間において、両アンギュラ玉軸受の外輪を軸方向両側に弾発付勢するコイルばねとスペーサとを設けたものが知られている（例えば、特許文献１及び２参照）。 The turbocharger of an automobile has a turbine attached to one end of the rotating shaft and an impeller attached to the other end, and an intermediate portion of the rotating shaft is inserted into a hole in the housing of the turbocharger. The rotating shaft is rotatably supported by the bearing device.
Conventionally, as such a turbocharger bearing device, a single row of angular ball bearings is arranged on both sides in the axial direction of the rotary shaft, and between them, the coil that elastically energizes the outer ring of both angular ball bearings on both sides in the axial direction. The thing provided with the spring and the spacer is known (for example, refer patent documents 1 and 2).

この従来のターボチャージャ用軸受装置では、玉を安定して回転させるために、通常、前記コイルばねにより玉の自転軸を一定方向固定させる程度の、大きめのアキシャル荷重が予圧として付与されている。
特開平１１−１０１１２８号公報 実用新案登録第２５７７０１１号公報 In this conventional turbocharger bearing device, in order to rotate the ball stably, a large axial load is usually applied as a preload to the extent that the rotation axis of the ball is fixed in a certain direction by the coil spring.
JP 11-101128 A Utility Model Registration No. 2577011

しかし、上記ターボチャージャ用軸受装置では、自転軸を一定方向に向けた状態で各玉が自転ながら、内輪及び外輪軌道に沿って転動するため、その自転軸に対応する赤道回りの同じ部分だけが内輪及び外輪軌道に接触することになる。
従って、このような転動状態で、硬質の異物が混入した潤滑油が軸受装置に供給されると、その異物が玉の転動部分に噛み込み、玉の外周赤道付近を周回するバンド状の摩耗痕が生じることがあり、この摩耗痕によって異常音が発生するおそれがある。 However, in the above turbocharger bearing device, each ball rolls along the inner ring and outer ring track while rotating with the rotation axis oriented in a fixed direction, so only the same part around the equator corresponding to the rotation axis is used. Will come into contact with the inner and outer ring raceways.
Therefore, when lubricating oil mixed with hard foreign matter is supplied to the bearing device in such a rolling state, the foreign matter bites into the rolling part of the ball and circulates around the outer equator of the ball. Wear marks may occur, and abnormal sounds may occur due to the wear marks.

本発明は、このような問題点に鑑み、アンギュラ玉軸受の玉にバンド状の摩耗痕が発生するのを防止して、異常音の発生を防止ないし抑制することができるターボチャージャ用軸受装置を提供することを目的とする。   In view of such problems, the present invention provides a turbocharger bearing device that can prevent the occurrence of band-like wear marks on the balls of an angular ball bearing and prevent or suppress the generation of abnormal noise. The purpose is to provide.

従来、ターボチャージャ用軸受装置では、玉を安定して回転させるために、玉の自転軸が一定方向に固定される程度の予圧を外輪に付与するのが技術常識であった。
ところが、本発明者らが鋭意研究を重ねたところ、単に玉の安定回転のみを重要視して外輪の予圧を設定すると、前記した通り、潤滑油中に硬質の異物が混入している場合には、自転軸が変動しない玉の転動部分に摩耗痕が発生し易く、これが異常音の発生の原因となることを見出した。 Conventionally, in a turbocharger bearing device, in order to rotate a ball stably, it has been common technical knowledge to apply a preload to the outer ring so that the rotation axis of the ball is fixed in a certain direction.
However, as a result of repeated extensive research conducted by the present inventors, if the preload of the outer ring is set simply considering only the stable rotation of the ball, as described above, when hard foreign matter is mixed in the lubricating oil. Have found that wear marks are likely to occur in the rolling part of the ball whose rotation axis does not change, and this causes abnormal noise.

本発明は、上記知見に基づいて完成したものであり、ターボチャージャの回転軸をハウジング内で回転自在に支持するターボチャージャ用軸受装置であって、前記回転軸の軸方向に離れた一対の内輪軌道を有する回転軸側に設けられた内輪と、前記内輪軌道に対向する外輪軌道を有するハウジング側に設けられた一対の外輪と、前記内輪軌道と前記外輪軌道との間に転動自在に複数の玉を配置してなる一対のアンギュラ玉軸受と、前記各玉の自転軸が一定方向に固定されない程度に前記各アンギュラ玉軸受にアキシャル方向の定圧予圧を付与する予圧付与部材とを備えていることを特徴とする。   The present invention has been completed based on the above knowledge, and is a bearing device for a turbocharger that rotatably supports a rotating shaft of a turbocharger within a housing, and a pair of inner rings separated in the axial direction of the rotating shaft. An inner ring provided on the rotating shaft side having a track, a pair of outer rings provided on the housing side having an outer ring track facing the inner ring track, and a plurality of freely rotatable between the inner ring track and the outer ring track A pair of angular ball bearings, and a preload applying member that applies a constant pressure preload in the axial direction to each angular ball bearing to such an extent that the rotation axis of each ball is not fixed in a certain direction. It is characterized by that.

本発明によれば、上記予圧付与部材が、各玉の自転軸が一定方向に固定されない程度に前記各アンギュラ玉軸受に定圧予圧を付与するので、自転時に生じるジャイロ力によって玉の自転軸が時間の経過とともに変動する。
このため、アンギュラ玉軸受の玉と内輪及び外輪軌道の間に供給される潤滑油に硬質の異物が混入していても、玉の外周面にバンド状の摩耗痕が発生するのを極力防止することができ、かかる摩耗痕に伴う異常音の発生を防止ないし抑制することができる。 According to the present invention, the preload applying member applies a constant pressure preload to each angular ball bearing to such an extent that the rotation shaft of each ball is not fixed in a certain direction. Fluctuates with the passage of time.
For this reason, even if hard foreign matter is mixed in the lubricating oil supplied between the balls of the angular ball bearings and the inner ring and outer ring raceway, band-shaped wear marks are prevented from being generated on the outer peripheral surface of the balls as much as possible. It is possible to prevent or suppress the generation of abnormal noise associated with such wear marks.

上記予圧付与部材は、具体的には、前記一対の外輪間に介装された一対のスリーブと、この各スリーブを介して前記各外輪にそれぞれアキシャル方向の予圧を付与すべく当該一対のスリーブ間に介装された予圧ばねとから構成することができる。
この場合、各玉の自転軸が一定方向に固定されない程度に各アンギュラ玉軸受に定圧予圧を付与するには、前記予圧ばねによるアキシャル方向の予圧荷重を、次の不等式（１）が成立する範囲内に設定すればよい。 Specifically, the preload applying member includes a pair of sleeves interposed between the pair of outer rings and a pair of sleeves for applying a preload in the axial direction to the outer rings via the sleeves. And a preload spring interposed between the two.
In this case, in order to apply constant pressure preload to each angular ball bearing to such an extent that the rotation axis of each ball is not fixed in a certain direction, the preload load in the axial direction by the preload spring is a range in which the following inequality (1) is satisfied. not good if set within.

Figure 0005071150
ただし、Ｆａ：予圧荷重（Ｎ）、μ：玉と軌道面との転がり摩擦定数、ｄ：玉径（ｍｍ）、Ｄ：玉のＰＣＤ（Pitch Circle Diameter）（ｍｍ）、Ｚ：玉の個数、θ：軸受接触角（度）、ｎ：軸受回転数（ｍｉｎ-1）である。
Figure 0005071150
 However, Fa: Preload (N), μ: Rolling friction constant between ball and raceway surface, d: Ball diameter (mm), D: Ball PCD (Pitch Circle Diameter) (mm), Z: Number of balls, θ: bearing contact angle (degrees), n: bearing rotation speed (min −1 ).

上記不等式（１）の右辺は、アンギュラ玉軸受の玉の自転軸を一定方向に固定させる場合に必要な、最小のアキシャル荷重を演算するための力学公式である。
従って、上記式（１）右辺の力学公式で演算可能なアキシャル荷重の最小値よりも予圧荷重Ｆａが小さい値となるように、予圧ばねの弾性常数、自然長及び圧縮量等を設定しておくことにより、アンギュラ玉軸受に対するアキシャル方向の予圧荷重を、各玉の自転軸が一定方向に固定されない程度に設定することができる。 The right side of the inequality (1) is a dynamic formula for calculating the minimum axial load necessary for fixing the rotation axis of the ball of the angular ball bearing in a fixed direction.
Accordingly, the elastic constant, the natural length, the compression amount, etc. of the preload spring are set so that the preload load Fa is smaller than the minimum value of the axial load that can be calculated by the dynamic formula on the right side of the equation (1). Thus, the preload in the axial direction with respect to the angular ball bearing can be set to such an extent that the rotation axis of each ball is not fixed in a certain direction.

以上の通り、本発明によれば、玉の自転軸を一定方向に固定しない程度の軽予圧を付与するようにしたので、玉にバンド状の摩耗痕が発生するのを防止でき、これによって異常音が発生するのを抑制ないし防止することができる。   As described above, according to the present invention, since a light preload that does not fix the rotation axis of the ball in a certain direction is applied, it is possible to prevent the formation of band-shaped wear marks on the ball, thereby causing abnormalities. The generation of sound can be suppressed or prevented.

以下、図面を参照しつつ、本発明の実施の形態を説明する。
図１は、本発明のターボチャージャ用軸受装置１の一実施形態を示す断面図である。
図２は、そのターボチャージャ用軸受装置１が組み込まれたターボチャージャＴの概略構成を示す断面図である。
図２に示すように、本実施形態のターボチャージャＴは、排気流路３１を流通する排気により、回転軸３２の一端側（図２の右側）に固定したタービン３３を回転させるようになっている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional view showing an embodiment of a bearing device 1 for a turbocharger according to the present invention.
FIG. 2 is a cross-sectional view showing a schematic configuration of a turbocharger T in which the turbocharger bearing device 1 is incorporated.
As shown in FIG. 2, the turbocharger T of the present embodiment rotates a turbine 33 fixed to one end side (the right side in FIG. 2) of the rotating shaft 32 by the exhaust gas flowing through the exhaust passage 31. Yes.

この回転軸３２の回転は、当該回転軸３２の他端側（図２の左側）に固定されたインペラ３４に伝わり、このインペラ３４が給気流路３５内で回転する。
この結果、給気流路３５の上流側開口から吸引された空気が圧縮され、これにより、ガソリンや軽油等の燃料とともに圧縮された空気が、図示しないエンジンのシリンダ室内に送り込まれる。 The rotation of the rotating shaft 32 is transmitted to the impeller 34 fixed to the other end side (left side in FIG. 2) of the rotating shaft 32, and the impeller 34 rotates in the air supply passage 35.
As a result, the air sucked from the upstream opening of the air supply passage 35 is compressed, and the compressed air together with fuel such as gasoline and light oil is sent into a cylinder chamber of an engine (not shown).

かかるターボチャージャＴの回転軸３２は、数万〜十数万（回／分）もの高速で回転し、しかも、エンジンの運転状況に応じて回転速度が頻繁に変化する。そのため、回転損失を低減すべくハウジング３６内に設けられたターボチャージャ用軸受装置１によって、回転軸３２をハウジング３６に対して小さな回転抵抗で支持している。
このターボチャージャ用軸受装置１は、ターボチャージャＴのハウジング３６内に設けられた円筒状の軸受支持部３６ａを備え、この筒内部に組み込まれている。一端にタービン３３が取り付けられかつ他端にインペラ３４が取り付けられた上記回転軸３２は、その中間部において、当該軸受装置１によって回転自在に支持される。 The rotating shaft 32 of the turbocharger T rotates at a high speed of tens of thousands to tens of thousands (times / minute), and the rotation speed frequently changes according to the operating state of the engine. Therefore, the rotating shaft 32 is supported with respect to the housing 36 with a small rotational resistance by the turbocharger bearing device 1 provided in the housing 36 in order to reduce the rotation loss.
The turbocharger bearing device 1 includes a cylindrical bearing support portion 36a provided in a housing 36 of the turbocharger T, and is incorporated inside the cylinder. The rotating shaft 32 having the turbine 33 attached to one end and the impeller 34 attached to the other end is rotatably supported by the bearing device 1 at an intermediate portion thereof.

図１に示すように、このターボチャージャ用軸受装置１は、上記軸受支持部３６ａと、この軸受支持部３６ａに同軸心状に挿通された回転軸３２の軸方向に離れて設けられた一対の玉軸受２ａ，２ｂ（第一の玉軸受２ａ及び第二の玉軸受２ｂ）とを備えている。
この両玉軸受２ａ，２ｂの内輪３の間には、内輪間座７が介装されている。また、両玉軸受２ａ，２ｂの外輪４の間には、一対のスリーブ８が介装され、この各スリーブ８の間には、第一の玉軸受２ａ及び第二の玉軸受２ｂに予圧荷重を付与する予圧ばね９が介装されている。 As shown in FIG. 1, the turbocharger bearing device 1 includes a pair of bearing support portions 36a and a pair of shaft support portions 36a provided apart from each other in the axial direction of a rotating shaft 32 inserted coaxially into the bearing support portion 36a. Ball bearings 2a and 2b (first ball bearing 2a and second ball bearing 2b) are provided.
An inner ring spacer 7 is interposed between the inner rings 3 of the ball bearings 2a and 2b. A pair of sleeves 8 are interposed between the outer rings 4 of the ball bearings 2a and 2b, and a preload is applied between the sleeves 8 on the first ball bearing 2a and the second ball bearing 2b. Is provided with a preload spring 9.

上記ハウジング３６内の軸受支持部３６ａに組み込まれた第一及び第二の玉軸受２ａ，２ｂは、いずれもアンギュラ玉軸受であって、両者の基本的構成はそれぞれ同じである。
第一の玉軸受２ａは、回転軸３２のタービン３３側（図１の右側）に配置され、第二の玉軸受２ｂは、回転軸３２のインペラ３４側（図１の左側）に配置されている。両玉軸受２ａ，２ｂは、それぞれ、外周側に内輪軌道３ａを有する内輪３，３と、内周側に外輪軌道４ａを有する外輪４，４と、これら内輪軌道３ａと外輪軌道４ａの間に転動自在に配置された複数の玉５とを備えている。 The first and second ball bearings 2a and 2b incorporated in the bearing support portion 36a in the housing 36 are both angular ball bearings, and the basic configurations of both are the same.
The first ball bearing 2a is disposed on the turbine 33 side (right side in FIG. 1) of the rotating shaft 32, and the second ball bearing 2b is disposed on the impeller 34 side (left side in FIG. 1) of the rotating shaft 32. Yes. The ball bearings 2a and 2b are respectively composed of inner rings 3 and 3 having an inner ring raceway 3a on the outer peripheral side, outer rings 4 and 4 having an outer ring raceway 4a on the inner peripheral side, and between the inner ring raceway 3a and the outer ring raceway 4a. And a plurality of balls 5 arranged so as to be able to roll.

内輪３は環状に形成されており、その外周に形成された内輪軌道３ａは所定の曲率半径を有するアンギュラ型の軌道であり、その軸線は斜め内側に向けられている。
また、外輪４も環状に形成されており、その内周には、内輪軌道３ａと対向して、所定の曲率半径を有するアンギュラ型の外輪軌道４ａが形成されている。そして、本実施形態のアンギュラ玉軸受２ａ，２ｂでは、その内輪３及び外輪４は、片側の肩部をなくしたいわゆるカウンタボアを有する断面形状とされている。 The inner ring 3 is formed in an annular shape, and the inner ring raceway 3a formed on the outer periphery thereof is an angular type raceway having a predetermined radius of curvature, and its axis is directed obliquely inward.
The outer ring 4 is also formed in an annular shape, and an angular outer ring raceway 4a having a predetermined radius of curvature is formed on the inner periphery of the outer ring 4 so as to face the inner ring raceway 3a. And in the angular ball bearings 2a and 2b of this embodiment, the inner ring 3 and the outer ring 4 have a cross-sectional shape having a so-called counterbore without a shoulder on one side.

転動体としての上記玉５は、円環状の保持器６に設けられた複数のポケット６ａ内に、それぞれ１個ずつ転動自在に保持され、この保持器６により、内輪軌道３ａと外輪軌道４ａとの間に形成された環状空間内に、その周方向に沿って所定の間隔おきに配列されている。
かかる第一及び第二の玉軸受２ａ，２ｂのそれぞれは、ハウジング３６の内側に設けられた軸受支持部３６ａに支持されている。 The balls 5 as rolling elements are each held in a plurality of pockets 6a provided in an annular retainer 6 so as to be able to roll one by one, and by this retainer 6, the inner ring raceway 3a and the outer ring raceway 4a. Are arranged at predetermined intervals along the circumferential direction in an annular space formed between the two.
Each of the first and second ball bearings 2 a and 2 b is supported by a bearing support portion 36 a provided inside the housing 36.

より詳しくは、両玉軸受２ａ，２ｂのそれぞれの外輪４，４は、軸受支持部８に対する軸方向変位が許容されるように、前記軸受支持部８の両端部内周面に対して比較的ルーズに内嵌されている。
また、両玉軸受２ａ，２ｂのぞれぞれの内輪３，３は、回転軸３２に対する軸方向変位も規制された状態で当該回転軸３２の中間部に外嵌固定され、これにより、回転軸３２の軸方向中間部が、軸方向に離れた一対の玉軸受２ａ，２ｂによってハウジング３６の軸受支持部８に回転自在に支持されている。 More specifically, the outer rings 4 and 4 of the ball bearings 2a and 2b are relatively loose with respect to the inner peripheral surfaces of the both ends of the bearing support 8 so that axial displacement with respect to the bearing support 8 is allowed. It is fitted inside.
Further, the inner rings 3 and 3 of the ball bearings 2a and 2b are externally fitted and fixed to the intermediate portion of the rotating shaft 32 in a state in which axial displacement with respect to the rotating shaft 32 is also restricted. An axially intermediate portion of the shaft 32 is rotatably supported on the bearing support portion 8 of the housing 36 by a pair of ball bearings 2a and 2b separated in the axial direction.

前記一対のスリーブ８，８は、互いに軸方向内側の端部８ａが回転軸３２の軸方向で対向するように、軸方向に離れた外輪４，４の間に介装されている。これら各スリーブ８，８は、その外径が外輪４の外径と同径の円筒状に形成され、従って、当該スリーブ８の外周面は外輪４の外周面と面一となっている。
各スリーブ８，８は、その外周面から内周面に向けて貫通形成された油孔１０を有しており、この油孔１０は、その内周面側の貫通出口が内輪軌道３ａの近傍に位置するように径方向に対して傾斜している。 The pair of sleeves 8, 8 are interposed between the outer rings 4, 4 separated in the axial direction so that the axially inner ends 8 a face each other in the axial direction of the rotating shaft 32. Each of the sleeves 8 and 8 is formed in a cylindrical shape whose outer diameter is the same as the outer diameter of the outer ring 4, so that the outer peripheral surface of the sleeve 8 is flush with the outer peripheral surface of the outer ring 4.
Each sleeve 8, 8 has an oil hole 10 formed so as to penetrate from the outer peripheral surface toward the inner peripheral surface, and the oil hole 10 has a through outlet on the inner peripheral surface side in the vicinity of the inner ring raceway 3 a. It inclines with respect to radial direction so that it may be located in.

また、図１左側のスリーブ８の外周面と軸受支持部３６ａの内周面の境界面にピン４０がルーズに嵌合されており、このスペーサ８は、このピン４０によって軸受支持部３６ａに対して軸方向及び周方向に位置決めされている。
軸方向に並ぶ一対のスリーブ８，８における内周側でかつ軸方向の対向端部側には、前記予圧ばね９を収納する環状空間を形成するための段差部８ｂが形成されている。この段差部８ｂは、コイル状の予圧ばね９の直径よりも若干大きい径で、スリーブ８，８の内周側の肉厚を環状に切り欠くことによって形成されている。 Further, a pin 40 is loosely fitted to the boundary surface between the outer peripheral surface of the sleeve 8 on the left side of FIG. 1 and the inner peripheral surface of the bearing support portion 36a, and the spacer 8 is connected to the bearing support portion 36a by the pin 40. Are positioned in the axial and circumferential directions.
A stepped portion 8b for forming an annular space for accommodating the preload spring 9 is formed on the inner peripheral side of the pair of sleeves 8 and 8 arranged in the axial direction and on the opposite end side in the axial direction. The stepped portion 8b has a diameter slightly larger than the diameter of the coiled preload spring 9, and is formed by notching the thickness of the inner peripheral side of the sleeves 8 and 8 in an annular shape.

各内輪３，３の間の内輪間座７は、その内径が内輪３の内径と同径の円筒状に形成され、当該内輪間座７の内周面は、内輪３の内周面と面一となっている。
また、各スリーブ８，８を互いに対向させた状態において、上記段差部８ｂと内輪間座７の外周面とによって環状空間が形成され、この環状空間に前記予圧ばね９が圧縮状態で収納されている。なお、
各スリーブ８，８の軸方向で対向する端面８ａの間には、軸方向長さが約数十μｍの隙間ｓが設けられている。 The inner ring spacer 7 between the inner rings 3 and 3 is formed in a cylindrical shape whose inner diameter is the same as the inner diameter of the inner ring 3, and the inner peripheral surface of the inner ring spacer 7 is the same as the inner peripheral surface of the inner ring 3. It is one.
Further, in a state where the sleeves 8 and 8 are opposed to each other, an annular space is formed by the stepped portion 8b and the outer peripheral surface of the inner ring spacer 7, and the preload spring 9 is stored in a compressed state in the annular space. Yes. In addition,
A gap s having an axial length of about several tens of μm is provided between the end faces 8a facing each other in the axial direction of the sleeves 8 and 8.

上記のように、軸受支持部３６ａ、アンギュラ玉軸受２ａ，２ｂ、スリーブ８及び予圧ばね９とにより、ターボチャージャ用軸受装置１が主構成されている。
図２に示すように、上記軸受支持部３６ａを収めたハウジング３６内には、給油通路３７が設けられ、この給油通路３７を通過する潤滑油で玉軸受２ａ，２ｂを潤滑するようになっている。 As described above, the turbocharger bearing device 1 is mainly constituted by the bearing support portion 36a, the angular ball bearings 2a and 2b, the sleeve 8, and the preload spring 9.
As shown in FIG. 2, an oil supply passage 37 is provided in the housing 36 in which the bearing support portion 36 a is accommodated, and the ball bearings 2 a and 2 b are lubricated with the lubricating oil passing through the oil supply passage 37. Yes.

より詳しくは、潤滑油は、ターボチャージャＴを装着したエンジンの運転時に、給油通路３７の上流側に設けたフィルタ３８により異物が除去された後、軸受支持部３６ａの内周面と第一及び第二の玉軸受２ａ，２ｂ及び各スリーブ８の外周面との間に存在する環状の隙間空間（図示せず）に送り込まれるようになっている。
なお、上記隙間空間は、軸受支持部３６ａと第一及び第二の玉軸受２ａ，２ｂ及びスリーブ８とを隙間嵌めすることにより設けられている。 More specifically, the lubricating oil is removed from the inner peripheral surface of the bearing support portion 36a by the filter 38 provided on the upstream side of the oil supply passage 37 when the engine equipped with the turbocharger T is operated. It is fed into an annular gap space (not shown) that exists between the second ball bearings 2 a and 2 b and the outer peripheral surface of each sleeve 8.
The gap space is provided by fitting the bearing support portion 36a with the first and second ball bearings 2a, 2b and the sleeve 8.

そして、上記隙間空間を潤滑油で満たすことにより、第一及び第二の玉軸受２ａ，２ｂ及びスリーブ８の外周面と軸受支持部３６ａの内周面との間に全周にわたって油膜（オイルフィルム）が形成され、第一及び第二の玉軸受２ａ，２ｂ及びスリーブ８の振動を軸受支持部３６ａに伝わり難くしている。
このように、上記隙間空間に満たされた潤滑油によって、回転軸３２の回転に基づく振動を減衰させるオイルフィルムダンパが形成されている。 Then, by filling the gap space with lubricating oil, an oil film (oil film) is formed over the entire circumference between the outer peripheral surfaces of the first and second ball bearings 2a and 2b and the sleeve 8 and the inner peripheral surface of the bearing support portion 36a. ) To prevent the vibrations of the first and second ball bearings 2a and 2b and the sleeve 8 from being transmitted to the bearing support portion 36a.
Thus, an oil film damper that attenuates vibration based on the rotation of the rotating shaft 32 is formed by the lubricating oil filled in the gap space.

上記隙間空間に送り込まれた潤滑油の一部は、各スリーブ８，８に形成された油孔１０から、第１及び第２の玉軸受２ａ，２ｂの内輪３の外周面に向けて、径方向外方から斜めに噴出するようになっている。また、第１及び第２の玉軸受２ａ，２ｂに向けて噴出した潤滑油は、ハウジング３６の排油口３９より排出される。
本実施形態のターボチャージャ用軸受装置１において、第一及び第二の玉軸受２ａ，２ｂは、互いに接触角の方向を逆にした背面組み合わせ型の状態に配置され、一つの上記予圧ばね９によって定圧予圧を受けている。 A portion of the lubricating oil fed into the gap space has a diameter from the oil holes 10 formed in the sleeves 8 and 8 toward the outer peripheral surface of the inner ring 3 of the first and second ball bearings 2a and 2b. It is designed to erupt diagonally from outside the direction. Further, the lubricating oil ejected toward the first and second ball bearings 2 a and 2 b is discharged from the oil discharge port 39 of the housing 36.
In the turbocharger bearing device 1 according to the present embodiment, the first and second ball bearings 2a and 2b are arranged in a back-combined state in which the directions of the contact angles are opposite to each other. A constant pressure preload is applied.

すなわち、予圧ばね９は、一対の外輪４，４に対して、軸方向においてそれらが互いに離れる向きの予圧荷重（定圧予圧）を付与するコイルばねよりなる。
具体的には、コイルばねよりなる上記予圧ばね９は、各スリーブ８，８の環状空間内で圧縮状態にあり、その両端をスリーブ８，８に当接させることで、これらのスリーブ８，８，を介して各外輪４，４を互いに離れる軸方向に付勢している。 That is, the preload spring 9 is composed of a coil spring that applies a preload (a constant pressure preload) in a direction in which the pair of outer rings 4 and 4 are separated from each other in the axial direction.
Specifically, the preload spring 9 made of a coil spring is in a compressed state in the annular space of the sleeves 8 and 8, and both sleeves 8 and 8 are brought into contact with the sleeves 8 and 8. , The outer rings 4 and 4 are urged in the axial direction away from each other.

そして、本実施形態の予圧ばね９は、これによるアキシャル方向の予圧荷重Ｆａが、次の不等式（１）が成立する範囲内に設定されている。

Figure 0005071150
In the preload spring 9 of the present embodiment, the axial preload load Fa is set within a range in which the following inequality (1) is established.
Figure 0005071150

ただし、上記不等式（１）において、各変数の意味と単位は次の通りである。
Ｆａ：アキシャル荷重（Ｎ）
μ：玉と軌道面との転がり摩擦定数
ｄ：玉径（ｍｍ）
Ｄ：玉のＰＣＤ（Pitch Circle Diameter）（ｍｍ）
Ｚ：玉の個数
θ：軸受接触角（度）
ｎ：軸受回転数（ｍｉｎ-1）
なお、上記不等式（１）において、アキシャル荷重Ｆａの下限値が記載されていないのは、外輪４にアキシャル方向の定圧予圧Ｆａを付与する以上は、そのＦａが０より大きい所定値（Ｆａ＞０）になることが自明だからである。 However, in the inequality (1), the meaning and unit of each variable are as follows.
Fa: Axial load (N)
μ: Rolling friction constant between ball and raceway surface d: Ball diameter (mm)
D: Ball PCD (Pitch Circle Diameter) (mm)
Z: Number of balls θ: Bearing contact angle (degrees)
n: Bearing rotation speed (min -1 )
In the above inequality (1), the lower limit value of the axial load Fa is not described, as long as the constant pressure preload Fa in the axial direction is applied to the outer ring 4, that Fa is a predetermined value greater than 0 (Fa> 0). This is because it is self-evident.

上記不等式（１）の右辺は、アンギュラ玉軸受２ａ，２ｂの玉５の自転軸を一定方向に固定させる場合に必要な、最小のアキシャル荷重を演算するための力学公式である。
従って、本実施形態では、上記式（１）右辺の力学公式で演算可能なアキシャル荷重の最小値よりもアキシャル方向の予圧荷重Ｆａが小さい値となるように、予圧ばね９の弾性常数、自然長及び圧縮量等を設定しておくことで、アンギュラ玉軸受２ａ，２ｂに対するアキシャル方向の予圧荷重が、各４玉の自転軸が一定方向に固定されない程度に設定されている。 The right side of the inequality (1) is a dynamic formula for calculating the minimum axial load necessary for fixing the rotation axis of the balls 5 of the angular ball bearings 2a and 2b in a fixed direction.
Therefore, in the present embodiment, the elastic constant and natural length of the preload spring 9 are set so that the preload load Fa in the axial direction is smaller than the minimum value of the axial load that can be calculated by the dynamic formula of the right side of the formula (1). By setting the compression amount and the like, the preload load in the axial direction on the angular ball bearings 2a and 2b is set to such an extent that the rotation shafts of the four balls are not fixed in a fixed direction.

このため、本実施形態の軸受装置１では、外輪間に介装された前記一対のスリーブ８，８と、この各スリーブ８，８を介して各外輪４，４にそれぞれアキシャル方向の定圧予圧を付与する上記予圧ばね８とにより、各玉４の自転軸が一定方向に固定されない程度に各アンギュラ玉軸受２ａ，２ｂにアキシャル方向の定圧予圧を付与する予圧付与部材が構成されている。   Therefore, in the bearing device 1 of the present embodiment, the pair of sleeves 8 and 8 interposed between the outer rings, and the constant pressure preload in the axial direction is applied to the outer rings 4 and 4 via the sleeves 8 and 8, respectively. The preload spring 8 to be applied constitutes a preload application member that applies a constant pressure preload in the axial direction to the angular ball bearings 2a and 2b to such an extent that the rotation axis of each ball 4 is not fixed in a certain direction.

以上の構成を有するターボチャージャ用軸受装置１によれば、上記不等式（１）を満たすアキシャル方向の予圧荷重Ｆａ、すなわち、玉５の自転軸を一定方向に固定しない程度の従来よりも比較的軽めの予圧荷重Ｆａが各玉軸受２ａ，２ｂに付与される。
このため、各玉軸受２ａ，２ｂの玉５の自転軸の方向が高速回転時に生じるジャイロ力によって時間の経過とともに変動し、この結果、軌道３ａ，４ａと接触する玉５の転動面が固定されずに変化するので、各玉５にバンド状の摩耗痕が発生するのを未然に防止することができ、ひいては異常音が発生を防止ないし抑制することができる。 According to the turbocharger bearing device 1 having the above-described configuration, the axial preload Fa satisfying the inequality (1), that is, the rotation speed of the ball 5 is relatively lighter than that of the conventional art. Preload force Fa is applied to each ball bearing 2a, 2b.
For this reason, the direction of the rotation axis of the ball 5 of each ball bearing 2a, 2b varies with time due to the gyro force generated during high-speed rotation, and as a result, the rolling surface of the ball 5 in contact with the tracks 3a, 4a is fixed. Therefore, it is possible to prevent the occurrence of band-shaped wear marks on each ball 5 and to prevent or suppress the occurrence of abnormal noise.

また、本実施形態の軸受装置１によれば、各スリーブ８，８間に介在させた予圧ばね９でアキシャル方向の予圧荷重を付与しているので、スリーブ８，８間の隙間ｓを比較的大きい寸法レンジ（例えば、数十μｍオーダー）で管理することが可能となる。
このため、例えば上記スリーブ８，８で定位置予圧を付与する場合に比べて、組み付け精度がラフでよく、組み立てが簡単であるとともに、アキシャル方向の振動を予圧ばね９で吸収できるため、より高速回転に適した軸受装置１を得ることができる。 Further, according to the bearing device 1 of the present embodiment, since the preload load in the axial direction is applied by the preload spring 9 interposed between the sleeves 8 and 8, the gap s between the sleeves 8 and 8 is relatively increased. It is possible to manage with a large size range (for example, on the order of several tens of μm).
For this reason, compared with the case where the fixed position preload is applied by the sleeves 8 and 8, for example, the assembly accuracy may be rough, the assembly is simple, and the vibration in the axial direction can be absorbed by the preload spring 9. A bearing device 1 suitable for rotation can be obtained.

なお、本発明は上記実施形態に限定されない。
上記実施形態では、一対のスリーブ８が、互いに軸方向の隙間ｓを有して対向しているが、スリーブ８，８の端部同士が直接対向しなければならないわけではなく、例えば、図３に示すように、軸受支持部３６ａの内面側に径方向内側に突出する突出部３６ａ１が形成され、この突出部３６ａ１とスリーブ８，８とが軸方向の隙間ｓ（数十μｍ程度）を有して対向していてもよい。 In addition, this invention is not limited to the said embodiment.
In the above embodiment, the pair of sleeves 8 face each other with an axial gap s, but the ends of the sleeves 8 and 8 do not have to face each other directly. For example, FIG. As shown in FIG. 5, a protrusion 36a1 protruding radially inward is formed on the inner surface side of the bearing support 36a, and the protrusion 36a1 and the sleeves 8 and 8 have an axial gap s (about several tens of μm). And may be opposed.

また、上記実施形態では、各玉軸受２ａ，２ｂの内輪３，３が軸方向に離れており、その間に内輪間座７を介在した構造になっているが、これらの内輪３，３と内輪間座７とを一体に有する内輪筒体を採用することもできる。
更に、保持器６の形式としては、図１に示すようなもみ抜き型だけなく、例えば波型のものを採用することもできる。 Further, in the above embodiment, the inner rings 3, 3 of the ball bearings 2a, 2b are separated in the axial direction, and the inner ring spacer 7 is interposed therebetween. However, the inner rings 3, 3 and the inner rings An inner ring cylinder having the spacer 7 integrally may be employed.
Furthermore, as a type of the cage 6, not only a hollow type as shown in FIG. 1 but also a wave type, for example, can be adopted.

ターボチャージャ用軸受装置の一実施形態を示す断面図である。It is sectional drawing which shows one Embodiment of the bearing apparatus for turbochargers. 上記軸受装置を有するターボチャージャの概略構成を示す断面図である。It is sectional drawing which shows schematic structure of the turbocharger which has the said bearing apparatus. ターボチャージャ用軸受装置の変形例を示す断面図である。It is sectional drawing which shows the modification of the bearing apparatus for turbochargers.

符号の説明Explanation of symbols

１ ターボチャージャ用軸受装置
２ アンギュラ玉軸受
２ａ 第一の玉軸受
２ｂ 第二の玉軸受
３ 内輪
４ 外輪
５ 玉
６ 保持器
７ 内輪間座
８ スリーブ（予圧付与部材）
９ 予圧ばね（予圧付与部材）
３２ 回転軸
３３ タービン
３４ インペラ
３６ ハウジング
３６ａ 軸受支持部
Ｔ ターボチャージャ DESCRIPTION OF SYMBOLS 1 Bearing device for turbochargers 2 Angular contact ball bearing 2a 1st ball bearing 2b 2nd ball bearing 3 Inner ring 4 Outer ring 5 Ball 6 Cage 7 Inner ring spacer 8 Sleeve (preloading member)
9 Preload spring (preload member)
32 Rotating shaft 33 Turbine 34 Impeller 36 Housing 36a Bearing support portion T Turbocharger

Claims (1)

ターボチャージャの回転軸をハウジング内で回転自在に支持するターボチャージャ用軸受装置であって、
前記回転軸の軸方向に離れた一対の内輪軌道を有する回転軸側に設けられた内輪と、
前記内輪軌道に対向する外輪軌道を有するハウジング側に設けられた一対の外輪と、
前記内輪軌道と前記外輪軌道との間に転動自在に複数の玉を配置してなる一対のアンギュラ玉軸受と、
前記各玉の自転軸が一定方向に固定されない程度に前記各アンギュラ玉軸受にアキシャル方向の定圧予圧を付与する予圧付与部材とを備えており、
前記予圧付与部材は、前記一対の外輪間に介装された一対のスリーブと、この各スリーブを介して前記各外輪にそれぞれアキシャル方向の定圧予圧を付与すべく当該一対のスリーブ間に介装された予圧ばねとからなり、
前記予圧ばねによるアキシャル方向の予圧荷重が、次の不等式（１）が成立する範囲内に設定されていることを特徴とするターボチャージャ用軸受装置。
Figure 0005071150
ただし、Ｆａ：予圧荷重（Ｎ）、μ：玉と軌道面との転がり摩擦定数、ｄ：玉径（ｍｍ）、Ｄ：玉ＰＣＤ（ｍｍ）、Ｚ：玉の個数、θ：軸受接触角（度）、ｎ：軸受回転数（ｍｉｎ ー１ ）である。 A turbocharger bearing device for rotatably supporting a rotating shaft of a turbocharger in a housing,
An inner ring provided on the rotating shaft side having a pair of inner ring raceways separated in the axial direction of the rotating shaft;
A pair of outer rings provided on the housing side having an outer ring raceway facing the inner ring raceway;
A pair of angular contact ball bearings in which a plurality of balls are arranged to freely roll between the inner ring raceway and the outer ring raceway;
A preload applying member that applies a constant pressure preload in the axial direction to each angular ball bearing to such an extent that the rotation axis of each ball is not fixed in a certain direction ;
The preload applying member is interposed between the pair of sleeves so as to apply a constant pressure preload in the axial direction to the outer rings via the pair of sleeves interposed between the pair of outer rings. A preload spring,
A turbocharger bearing device, wherein a preload in the axial direction by the preload spring is set within a range in which the following inequality (1) is satisfied .
Figure 0005071150
Where, Fa: Preload (N), μ: Rolling friction constant between ball and raceway surface, d: Ball diameter (mm), D: Ball PCD (mm), Z: Number of balls, θ: Bearing contact angle ( Degrees), n: bearing rotation speed (min -1 ).
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