JP6540281B2 - Double row ball bearing - Google Patents

Double row ball bearing Download PDF

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JP6540281B2
JP6540281B2 JP2015131039A JP2015131039A JP6540281B2 JP 6540281 B2 JP6540281 B2 JP 6540281B2 JP 2015131039 A JP2015131039 A JP 2015131039A JP 2015131039 A JP2015131039 A JP 2015131039A JP 6540281 B2 JP6540281 B2 JP 6540281B2
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diameter
raceway surface
ring raceway
inner ring
ball
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JP2017015148A (en
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下石　元
元 下石
翔 吉田
翔 吉田
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NSK Ltd
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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
    • 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
    • F16C19/18—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 two or more rows of balls
    • F16C19/181—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 two or more rows of balls with angular contact
    • F16C19/183—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 two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—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 two or more rows of balls with angular contact with two rows at opposite angles 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

Description

本発明は、複列玉軸受に関する。本発明は、特に、両端部にタービンとインペラとを支持固定したターボチャージャの回転軸をハウジングの内側に回転自在に支持する複列玉軸受に関する。   The present invention relates to a double row ball bearing. More particularly, the present invention relates to a double row ball bearing which rotatably supports a rotating shaft of a turbocharger, which supports and fixes a turbine and an impeller at both ends, inside a housing.

排気量を変えずにエンジンの出力を増大させるための過給機として、エンジンに送り込む空気を排気のエネルギにより圧縮するターボチャージャが広く使用されている。図５は、ターボチャージャの一例を示している。このターボチャージャ１は、排気流路２を流通する排気により、回転軸３の一端（図５の右端）に固定したタービン４を回転させる。この回転軸３の回転は、回転軸３の他端（図５の左端）に固定したインペラ５に伝わり、このインペラ５が給気流路６内で回転する。この結果、給気流路６の上流端開口から吸引された空気が圧縮されて、ガソリン、軽油等の燃料と共にエンジンのシリンダ室内に送り込まれる。   As a supercharger for increasing the output of the engine without changing the displacement, a turbocharger is widely used which compresses the air fed into the engine with the energy of the exhaust. FIG. 5 shows an example of a turbocharger. The turbocharger 1 rotates the turbine 4 fixed to one end (right end in FIG. 5) of the rotating shaft 3 by the exhaust gas flowing through the exhaust flow path 2. The rotation of the rotation shaft 3 is transmitted to the impeller 5 fixed to the other end (left end in FIG. 5) of the rotation shaft 3, and the impeller 5 rotates in the air supply flow passage 6. As a result, the air drawn from the upstream end opening of the air supply flow passage 6 is compressed and fed into the cylinder chamber of the engine together with fuel such as gasoline and light oil.

回転軸３は、数万〜十数万ｍｉｎ−１（ｒ．ｐ．ｍ．）もの高速で回転し、しかも、エンジンの運転状況に応じてその回転速度が頻繁に変化するため、回転軸３はハウジング７に対して小さな回転抵抗で支持される必要がある。 The rotating shaft 3 rotates at a high speed of tens to hundreds of thousands of min -1 (r.p.m.), and the rotating speed changes frequently according to the operating condition of the engine. Needs to be supported by the housing 7 with a small rotational resistance.

そのため、従来、ターボチャージャの回転軸の支持に、複列玉軸受を用いることが提案されている。図５に示すように、複列玉軸受５０は、単一円筒で形成された外輪５１と、タービン４側の第一の内輪５５およびインペラ５側の第二の内輪５８と、タービン４側の第一の保持器６１およびインペラ５側の第二の保持器６２と、を備える。第一の保持器６１には複数の第一の玉６５が転動自在に保持されており、第二の保持器６２には複数の第二の玉６６が転動自在に保持されている（例えば特許文献１、２参照。）。このような複列玉軸受５０によれば、回転軸３をハウジング７に対して小さな回転抵抗で支持することができる。   Therefore, conventionally, it has been proposed to use a double row ball bearing for supporting the rotating shaft of the turbocharger. As shown in FIG. 5, the double-row ball bearing 50 has an outer ring 51 formed of a single cylinder, a first inner ring 55 on the turbine 4 side, a second inner ring 58 on the impeller 5 side, and the turbine 4 side. A first holder 61 and a second holder 62 on the impeller 5 side are provided. A plurality of first balls 65 are rotatably held by the first cage 61, and a plurality of second balls 66 are rotatably held by the second cage 62 ( See, for example, Patent Documents 1 and 2.). According to such a double-row ball bearing 50, the rotary shaft 3 can be supported on the housing 7 with a small rotational resistance.

また、複列玉軸受により回転軸を支持する構成において、タービン側よりもインペラ側で外径が小さくなるように形成された回転軸を用い、タービン側の内輪の内径よりもインペラ側の内輪の内径を小さくすることによって、回転軸の内輪への圧入抵抗を軽減することが提案されている（例えば、特許文献３参照）。   Further, in the configuration in which the rotary shaft is supported by the double row ball bearings, the rotary shaft formed so that the outer diameter is smaller on the impeller side than on the turbine side is used. It has been proposed to reduce press-in resistance of the rotating shaft to the inner ring by reducing the inner diameter (see, for example, Patent Document 3).

特開２０１２−９２９３４号公報JP 2012-92934 A 特開２０１４−９７７９号公報JP, 2014-9779, A 特開２０１４−１２６０８４号公報JP, 2014-126084, A

ところで、上述したように、ターボチャージャの回転軸は高速回転するため、複列玉軸受の転動体である玉には大きな遠心力がかかる。玉の公転時に作用する遠心力が増大して接触面圧や接触面内のすべり速度が増大すると、発熱や摩擦損失の増加といった問題を引き起こし、寿命低下など軸受性能の低下を招いてしまう虞がある。   Incidentally, as described above, since the rotating shaft of the turbocharger rotates at a high speed, a large centrifugal force is applied to the balls which are rolling elements of the double row ball bearing. If the centrifugal force acting at the time of ball revolution increases and the contact pressure and the sliding speed in the contact surface increase, problems such as heat generation and increase in friction loss may be caused, which may lead to deterioration of the bearing performance such as life reduction. is there.

本発明は上記事情に鑑みてなされたものであり、その目的は、ターボチャージャの回転軸の高速回転に起因した発熱や摩擦損失を低減可能な複列玉軸受を提供することである。   The present invention has been made in view of the above circumstances, and an object thereof is to provide a double row ball bearing capable of reducing heat generation and friction loss caused by high speed rotation of a rotating shaft of a turbocharger.

本発明の上記目的は、下記の構成により達成される。
（１） 両端部にタービンとインペラとを支持固定したターボチャージャの回転軸をハウジングの内側に回転自在に支持する複列玉軸受であって、
単一円筒から形成され、タービン側の第一の軌道面とインペラ側の第二の軌道面とを内径面両端近傍に有する外輪と、
前記回転軸に外嵌され、前記第一の外輪軌道面に対向する第一の内輪軌道面を外径面に有する第一の内輪と、
前記回転軸に外嵌され、前記第二の外輪軌道面に対向する第二の内輪軌道面を外径面に有する第二の内輪と、
前記第一の外輪軌道面と前記第一の内輪軌道面との間を転動可能な複数の第一の玉と、
前記第二の外輪軌道面と前記第二の内輪軌道面との間を転動可能な複数の第二の玉と、
前記第一の玉を周方向に等間隔に保持する第一の保持器と、
前記第二の玉を周方向に等間隔に保持する第二の保持器と、を備える複列玉軸受であって、
前記第二の玉のピッチ円径が、前記第一の玉のピッチ円径よりも小さい、複列玉軸受。
（２） 前記第二の玉の径が、前記第一の玉の径よりも小さい、（１）に記載の複列玉軸受。 The above object of the present invention is achieved by the following constitution.
(1) A double-row ball bearing rotatably supporting a rotary shaft of a turbocharger, which supports and fixes a turbine and an impeller at both ends, inside a housing,
An outer ring formed of a single cylinder and having a first raceway surface on the turbine side and a second raceway surface on the impeller side near both ends of the inner diameter surface;
A first inner ring having an outer diameter surface and a first inner ring raceway that is externally fitted to the rotation shaft and faces the first outer ring raceway surface;
A second inner ring having an outer diameter surface and a second inner ring raceway surface externally fitted to the rotation shaft and facing the second outer ring raceway surface;
A plurality of first balls capable of rolling between the first outer ring raceway surface and the first inner ring raceway surface;
A plurality of second balls capable of rolling between the second outer ring raceway surface and the second inner ring raceway surface;
A first cage for holding the first balls at equal intervals in the circumferential direction;
And a second retainer for holding the second balls at equal intervals in the circumferential direction.
The double row ball bearing in which the pitch circle diameter of the second ball is smaller than the pitch circle diameter of the first ball.
(2) The double row ball bearing according to (1), wherein a diameter of the second ball is smaller than a diameter of the first ball.

本発明に係る複列玉軸受によれば、ターボチャージャの回転軸の高速回転に起因した発熱や摩擦損失を低減することが可能となる。   According to the double row ball bearing according to the present invention, it is possible to reduce heat generation and friction loss caused by high speed rotation of the rotating shaft of the turbocharger.

本発明の一実施形態に係る複列玉軸受の断面図である。It is a sectional view of a double row ball bearing concerning one embodiment of the present invention. ピッチ円径差に対する動トルクの低減率を示すグラフである。It is a graph which shows the reduction rate of dynamic torque to pitch circle diameter difference. ピッチ円径差に対する発熱量の低減率を示すグラフである。It is a graph which shows the reduction rate of calorific value to pitch circle diameter difference. 本発明の変形例に係る複列玉軸受の断面図である。It is sectional drawing of the double row ball bearing concerning the modification of this invention. 従来の複列玉軸受が組み込まれたターボチャージャの断面図である。It is sectional drawing of the turbocharger in which the conventional double row ball bearing was integrated.

以下、本発明に係る複列玉軸受の各実施形態を図面に基づいて詳細に説明する。本発明の特徴は、両端部にタービン４とインペラ５とを支持固定したターボチャージャ１の回転軸３をハウジング７（図５参照）の内側に回転自在に支持するために用いる複列玉軸受の構造にある。ターボチャージャ１の構造については従来と同様であるので、同等部分に関する図示および説明は省略または簡略にし、以下、本発明の特徴部分を中心に説明する。   Hereinafter, each embodiment of the double row ball bearing according to the present invention will be described in detail based on the drawings. The feature of the present invention is a double row ball bearing used for rotatably supporting the rotary shaft 3 of the turbocharger 1 supporting and fixing the turbine 4 and the impeller 5 at both ends inside the housing 7 (see FIG. 5). It is in structure. The structure of the turbocharger 1 is the same as that of the prior art, so the illustration and description of the equivalent parts will be omitted or simplified, and the following description will be made centering on the features of the present invention.

図１は、本発明の一実施形態に係る複列玉軸受１０の断面図を示す。複列玉軸受１０は、両端部にタービンとインペラとを支持固定したターボチャージャの回転軸を、ハウジングの内側に回転自在に支持するために用いるものであり、外輪１１と、第一の内輪２１と、第二の内輪２５と、を備える。以降、本明細書では、図中右側（すなわち第一の内輪２１側）にタービン、図中左側（すなわち第二の内輪２５側）にインペラが配置されるものとして説明する。   FIG. 1 shows a cross-sectional view of a double row ball bearing 10 according to an embodiment of the present invention. The double row ball bearing 10 is used to rotatably support the rotating shaft of the turbocharger, which supports and fixes the turbine and the impeller at both ends, inside the housing, and the outer ring 11 and the first inner ring 21. And a second inner race 25. Hereinafter, in the present specification, the turbine will be described on the right side (i.e., the first inner ring 21 side) in the figure, and the impeller will be disposed on the left side (i.e., the second inner ring 25 side) in the figure.

外輪１１は単一円筒から形成されており、図中右側に位置するタービン側の端部近傍において第一の外輪軌道面１３を内径面に有し、図中左側に位置するインペラ側の端部近傍において第二の外輪軌道面１４を内径面に有する。外輪１１は、ターボチャージャのハウジングに内嵌される。   The outer ring 11 is formed of a single cylinder, has the first outer ring raceway surface 13 in the inner diameter surface near the end on the turbine side located on the right side in the figure, and the end on the impeller side located on the left side in the figure In the vicinity, the second outer ring raceway surface 14 is provided on the inner diameter surface. The outer ring 11 is internally fitted in the turbocharger housing.

第一の内輪２１は、第一の外輪軌道面１３と対向する第一の内輪軌道面２２を外径面に有する。第一の外輪軌道面１３と第一の内輪軌道面２２との間には、第一の保持器２４によって等間隔に保持された複数の第一の玉１８が転動自在に配置されている。ターボチャージャの回転軸が内嵌される第一の内輪２１の内径面２３は、図中左側に位置するインペラ側内径面２３ｂが、図中右側に位置するタービン側内径面２３ａよりも小径となった段差構造となっている。第一の内輪２１の内径面２３が段差構造を有することにより、回転軸の圧入抵抗を低減でき、回転軸の組み付けを容易にすることができる。   The first inner race 21 has a first inner raceway surface 22 opposed to the first outer raceway surface 13 on the outer diameter surface. Between the first outer ring raceway surface 13 and the first inner ring raceway surface 22, a plurality of first balls 18 held at equal intervals by the first cage 24 are rotatably disposed. . In the inner diameter surface 23 of the first inner ring 21 into which the rotary shaft of the turbocharger is internally fitted, the impeller side inner diameter surface 23b located on the left side in the figure has a smaller diameter than the turbine side inner diameter surface 23a located on the right side It has a stepped structure. Since the inner diameter surface 23 of the first inner ring 21 has a stepped structure, the press-in resistance of the rotation shaft can be reduced, and the assembly of the rotation shaft can be facilitated.

第二の内輪２５は、第二の外輪軌道面１４と対向する第二の内輪軌道面２６を外径面に有する。第二の外輪軌道面１４と第二の内輪軌道面２６との間には、第二の保持器２９によって等間隔に保持された複数の第二の玉１９が転動自在に配置されている。ターボチャージャの回転軸が内嵌される第二の内輪２５の内径面２７は、図中左側に位置するインペラ側内径面２７ｂが、図中右側に位置するタービン側内径面２７ａよりも小径となった、段差構造となっている。第二の内輪２５の内径面２７が段差構造を有することにより、回転軸の圧入抵抗を低減でき、回転軸の組み付けを容易にすることができる。   The second inner race 25 has a second inner raceway surface 26 opposed to the second outer raceway surface 14 on the outer diameter surface. Between the second outer ring raceway surface 14 and the second inner ring raceway surface 26, a plurality of second balls 19 held at equal intervals by the second cage 29 are rotatably disposed. . The inner diameter surface 27b of the second inner ring 25 on which the rotary shaft of the turbocharger is internally fitted is smaller in diameter than the inner diameter surface 27a of the impeller on the right side in the drawing. It has a step structure. Since the inner diameter surface 27 of the second inner ring 25 has a stepped structure, the press-in resistance of the rotation shaft can be reduced, and the assembly of the rotation shaft can be facilitated.

第二の内輪２５のタービン側内径面２７ａの内径は、隣り合う第一の内輪２１のインペラ側内径面２３ｂの内径と略等しく形成されている。したがって、第二の内輪軌道面２６が形成された第二の内輪２５のインペラ側内径面２７ｂは、第一の内輪軌道面２２が形成された第一の内輪２１のタービン側内径面２３ａよりも小径となっている。   The inner diameter of the turbine-side inner diameter surface 27 a of the second inner ring 25 is formed substantially equal to the inner diameter of the impeller-side inner diameter surface 23 b of the adjacent first inner ring 21. Therefore, the impeller-side inner diameter surface 27b of the second inner ring 25 in which the second inner ring raceway surface 26 is formed is greater than the turbine-side inner diameter surface 23a of the first inner ring 21 in which the first inner ring raceway surface 22 is formed. It is small diameter.

本実施形態においては、第一の内輪２１のタービン側内径面２３ａと第二の内輪２５のインペラ側内径面２７ｂとの内径差に対応して、第二の玉１９のピッチ円径Ｄｉを、第一の玉１８のピッチ円径Ｄｔよりも小さくしている。当該構成によって、運転時の玉公転により第二の玉１９に作用する遠心力が軽減され、第二の玉１９と第二の外輪軌道面１４との間における接触面圧や接触面内の滑り速度を減少できる。これにより、複列玉軸受１０の発熱、および動トルクひいては摩擦損失を低減して、軸受寿命を向上することができる。   In the present embodiment, the pitch circle diameter Di of the second ball 19 corresponding to the inner diameter difference between the turbine side inner diameter surface 23a of the first inner ring 21 and the impeller side inner diameter surface 27b of the second inner ring 25 is It is smaller than the pitch circle diameter Dt of the first ball 18. According to this configuration, the centrifugal force acting on the second ball 19 by the ball revolution during operation is reduced, and the contact pressure and the slip in the contact surface between the second ball 19 and the second outer ring raceway surface 14 You can reduce the speed. Thereby, the heat generation of the double row ball bearing 10 and the dynamic torque and hence the friction loss can be reduced to improve the bearing life.

また、第二の玉１９のピッチ円径Ｄｉを小さくすることにより、外輪１１の肉厚を図中左側のインペラ側で大きくすることができ、外輪１１の剛性を高めることができる。これにより、ハウジング内での複列玉軸受１０の振動を抑制することができ、騒音を低減することができる。   Further, by reducing the pitch circle diameter Di of the second ball 19, the thickness of the outer ring 11 can be increased on the impeller side on the left side in the drawing, and the rigidity of the outer ring 11 can be enhanced. Thereby, vibration of double row ball bearing 10 in a housing can be controlled, and noise can be reduced.

ここで、本実施形態に係る複列玉軸受１０において、第一の玉１８と第二の玉１９のピッチ円径の差を変化させたときの動トルクの低減率と発熱量の低減率を計算した。ここでは、外輪外径２２ｍｍ、内輪内径８ｍｍ、各列の玉数８個、玉径３．９６９ｍｍであるＳＵＪ２（軸受鋼）製の複列玉軸受に、ラジアル荷重７８Ｎ、アキシアル荷重４９Ｎを負荷し、動粘度１８ｍｍ２／ｓのオイル潤滑で２０万ｍｉｎ−１で運転したものとした。そして、第一の玉１８のピッチ円径を１５ｍｍに固定し、第二の玉１９のピッチ円径を１５ｍｍ、１４．５ｍｍ、１４ｍｍ、１３ｍｍ、１２ｍｍ、１１ｍｍ、１０ｍｍに変化させたものとして計算を行った。このとき、第二の内輪２５のインペラ側内径面２７ｂの径も、それぞれ８ｍｍ、７．５ｍｍ、７ｍｍ、６ｍｍ、５ｍｍ、４ｍｍ、３ｍｍに変化するものとする。 Here, in the double row ball bearing 10 according to the present embodiment, the dynamic torque reduction rate and the heat generation amount reduction rate when the difference in the diameter of the pitch circle of the first ball 18 and the second ball 19 is changed. Calculated. Here, a radial load of 78N and an axial load of 49N are applied to a double row ball bearing made of SUJ2 (bearing steel), which has an outer ring outer diameter of 22 mm, an inner ring inner diameter of 8 mm, and eight balls in each row and a ball diameter of 3.969 mm. It was operated at 200,000 min- 1 with oil lubrication having a kinematic viscosity of 18 mm 2 / s. Then, the calculation is made assuming that the pitch circle diameter of the first ball 18 is fixed at 15 mm and the pitch circle diameter of the second ball 19 is changed to 15 mm, 14.5 mm, 14 mm, 13 mm, 12 mm, 11 mm, 10 mm. went. At this time, the diameter of the impeller-side inner diameter surface 27b of the second inner ring 25 is also changed to 8 mm, 7.5 mm, 7 mm, 6 mm, 5 mm, 4 mm, and 3 mm, respectively.

図２は、第一の玉１８と第二の玉１９のピッチ円径差（Ｄｉ−Ｄｔ）に対する動トルクの低減率の計算結果を示すグラフである。図２から明らかなように、ピッチ円径差が大きくなるほど、複列玉軸受１０の動トルクを低減でき、ひいては摩擦損失を低減できる。また、図３は、第一の玉と第二の玉のピッチ円径差（Ｄｉ−Ｄｔ）に対する発熱量の低減率の計算結果を示すグラフである。図３から明らかなように、ピッチ円径差が大きくなるほど、複列玉軸受１０の発熱を低減できる。したがって、軸径による寸法制約の範囲内で、玉ピッチ円径差が好ましくは０．５ｍｍ以上となるように第一の玉と第二の玉のピッチ円径を設定すれば、５％以上の動トルク低減効果および発熱低減効果が得られることがわかる。   FIG. 2 is a graph showing the calculation results of the dynamic torque reduction rate with respect to the pitch circle diameter difference (Di-Dt) of the first ball 18 and the second ball 19. As apparent from FIG. 2, the dynamic torque of the double-row ball bearing 10 can be reduced and the friction loss can be reduced as the pitch circle diameter difference becomes larger. Moreover, FIG. 3 is a graph which shows the calculation result of the reduction rate of the emitted-heat amount with respect to the pitch circle diameter difference (Di-Dt) of a 1st ball and a 2nd ball. As is clear from FIG. 3, the heat generation of the double row ball bearing 10 can be reduced as the pitch circle diameter difference becomes larger. Therefore, if the pitch circle diameter of the first ball and the second ball is set so that the difference in ball pitch circle diameter is preferably 0.5 mm or more within the range of dimensional constraints by the shaft diameter, it is 5% or more It can be seen that the dynamic torque reduction effect and the heat generation reduction effect can be obtained.

このように、本実施形態の複列玉軸受１０によれば、ターボチャージャのインペラ側に位置する第二の玉１９のピッチ円径Ｄｉが、タービン側に位置する第一の玉１８のピッチ円径Ｄｔよりも小さいことにより、第二の玉１９に作用する遠心力を低減することができる。これにより、ターボチャージャの回転軸の高速回転に起因した発熱や摩擦損失を低減し、軸受寿命を向上することができる。   Thus, according to the double row ball bearing 10 of the present embodiment, the pitch circle diameter Di of the second ball 19 located on the impeller side of the turbocharger is the pitch circle of the first ball 18 located on the turbine side By making the diameter smaller than the diameter Dt, the centrifugal force acting on the second ball 19 can be reduced. As a result, it is possible to reduce heat generation and friction loss caused by the high speed rotation of the rotating shaft of the turbocharger, and to improve the bearing life.

（変形例）
本発明の変形例に係る複列玉軸受を、図４を参照して説明する。尚、外輪１１、第一の内輪２１および第二の内輪２５、第一の保持器２４および第二の保持器２９、ならびに第一の玉１８の構成については上述した実施形態と同様であるので、ここでは説明を省略する。 (Modification)
A double row ball bearing according to a modification of the present invention will be described with reference to FIG. The configurations of the outer ring 11, the first inner ring 21 and the second inner ring 25, the first cage 24 and the second cage 29, and the first ball 18 are the same as in the above-described embodiment. , I omit the explanation here.

図４は本発明の変形例に係る複列玉軸受４０の断面図を示す。本変形例に係る複列玉軸受４０においては、第二の玉３９のピッチ円径Ｄｉが第一の玉１８のピッチ円径Ｄｔよりも小さいことに加え、第二の玉３９の径が、第一の玉１８の径よりも小さい。これにより、運転時に第二の玉３９にかかる遠心力をさらに低減することができ、複列玉軸受４０の発熱や摩擦損失をさらに低減し、軸受寿命をさらに向上することができる。   FIG. 4 shows a cross-sectional view of a double row ball bearing 40 according to a modification of the present invention. In the double row ball bearing 40 according to the present modification, in addition to the fact that the pitch circle diameter Di of the second ball 39 is smaller than the pitch circle diameter Dt of the first ball 18, the diameter of the second ball 39 is It is smaller than the diameter of the first ball 18. Thereby, the centrifugal force applied to the second ball 39 at the time of operation can be further reduced, the heat generation and friction loss of the double row ball bearing 40 can be further reduced, and the bearing life can be further improved.

尚、本発明は、上記した各実施形態に限定されるものではなく、適宜変更、改良等が可能である。   The present invention is not limited to the above-described embodiments, and appropriate changes, improvements, and the like can be made.

本発明は、ターボチャージャの回転軸をハウジングの内側に回転自在に支持するために使用される複列玉軸受として好適に利用可能である。   The present invention can be suitably used as a double row ball bearing used for rotatably supporting the rotating shaft of a turbocharger inside a housing.

１ ターボチャージャ
３ 回転軸
４ タービン
５ インペラ
１０ 複列玉軸受
１１ 外輪
１３ 第一の外輪軌道面
１４ 第二の外輪軌道面
１８ 第一の玉
１９ 第二の玉
２１ 第一の内輪
２２ 第一の内輪軌道面
２４ 第一の保持器
２５ 第二の内輪
２６ 第二の内輪軌道面
２９ 第二の保持器
Ｄｔ 第一の玉のピッチ円径
Ｄｉ 第二の玉のピッチ円径 DESCRIPTION OF SYMBOLS 1 Turbocharger 3 Rotor shaft 4 Turbine 5 Impeller 10 Double-row ball bearing 11 Outer ring 13 first outer ring raceway surface 14 second outer ring raceway surface 18 first ball 19 second ball 21 first inner ring 22 first Inner ring raceway surface 24 first cage 25 second inner ring 26 second inner ring raceway 29 second cage Dt first ball pitch circle diameter Di second ball pitch circle diameter

Claims (2)

両端部にタービンとインペラを支持固定したターボチャージャの回転軸をハウジングの内側に回転自在に支持する複列玉軸受であって、
単一円筒から形成され、タービン側の第一の外輪軌道面とインペラ側の第二の外輪軌道面とを内径面両端近傍に有する外輪と、
前記回転軸に外嵌され、前記第一の外輪軌道面に対向する第一の内輪軌道面を外径面に有する第一の内輪と、
前記回転軸に外嵌され、前記第二の外輪軌道面に対向する第二の内輪軌道面を外径面に有する第二の内輪と、
前記第一の外輪軌道面と前記第一の内輪軌道面との間を転動可能な複数の第一の玉と、
前記第二の外輪軌道面と前記第二の内輪軌道面との間を転動可能な複数の第二の玉と、
前記第一の玉を周方向に等間隔に保持する第一の保持器と、
前記第二の玉を周方向に等間隔に保持する第二の保持器と、を備える複列玉軸受であって、
前記第二の玉のピッチ円径が、前記第一の玉のピッチ円径よりも小さい、複列玉軸受。 A double-row ball bearing rotatably supporting a rotary shaft of a turbocharger having a turbine and an impeller supported and fixed at both ends inside a housing,
An outer ring formed from a single cylinder and having a first outer ring raceway surface on the turbine side and a second outer ring raceway surface on the impeller side in the vicinity of both ends of the inner diameter surface;
A first inner ring having an outer diameter surface and a first inner ring raceway that is externally fitted to the rotation shaft and faces the first outer ring raceway surface;
A second inner ring having an outer diameter surface and a second inner ring raceway surface externally fitted to the rotation shaft and facing the second outer ring raceway surface;
A plurality of first balls capable of rolling between the first outer ring raceway surface and the first inner ring raceway surface;
A plurality of second balls capable of rolling between the second outer ring raceway surface and the second inner ring raceway surface;
A first cage for holding the first balls at equal intervals in the circumferential direction;
And a second retainer for holding the second balls at equal intervals in the circumferential direction.
The double row ball bearing in which the pitch circle diameter of the second ball is smaller than the pitch circle diameter of the first ball. 前記第二の玉の径が、前記第一の玉の径よりも小さい、請求項１に記載の複列玉軸受。   The double row ball bearing according to claim 1, wherein a diameter of the second ball is smaller than a diameter of the first ball.
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