JP2013064463A - Roller bearing device - Google Patents

Roller bearing device Download PDF

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JP2013064463A
JP2013064463A JP2011204335A JP2011204335A JP2013064463A JP 2013064463 A JP2013064463 A JP 2013064463A JP 2011204335 A JP2011204335 A JP 2011204335A JP 2011204335 A JP2011204335 A JP 2011204335A JP 2013064463 A JP2013064463 A JP 2013064463A
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outer ring
hole
sleeve
inner ring
oil
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Yoshitaka Waseda
義孝 早稲田
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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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/005—Fluid passages not relating to lubrication or cooling
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44—Needle bearings
    • F16C19/48—Needle bearings with two or more rows of needles
    • 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
    • F16C2360/18—Camshafts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a roller bearing device leading oil supplied from an oil pressure supply source to an oil passage of a shaft member while suppressing drop of the oil pressure of the oil with a simple structure.SOLUTION: Dual rows of rolling bodies 61, 66 are disposed between an outer ring 41 and an inner ring 51. In portions in the axial direction of the outer ring 41 and the inner ring 51 positioned in the middle of the dual rows of rolling bodies 61, 66, an outer ring hole 47 and an inner ring hole 57 for leading the oil supplied from the oil pressure supply source to the oil passage 25 of the shaft member 20 are formed respectively. Between the outer ring 41 and the inner ring 51, a sleeve constituting a slide bearing between either of the outer ring hole 47 and the inner ring hole 57 is disposed. In the sleeve 70, a communication hole 71 for connecting the outer ring hole 47 with the inner ring hole 57 is formed.

Description

この発明は、カムシャフト、バランサシャフト等の軸部材の油路に油圧を供給する転がり軸受装置に関する。   The present invention relates to a rolling bearing device that supplies hydraulic pressure to an oil passage of a shaft member such as a camshaft and a balancer shaft.

従来、例えば、カムシャフトの軸端に組み付けられる可変バルブタイミング機構に油圧を供給するために、例えば、シリンダヘッドとキャップ部材との間に構成されるカムジャーナル（１番ジャーナル）にカムシャフトを回転可能に支持する滑り軸受にカムシャフトの油路に連通する連通孔が形成されたものが知られている（特許文献１参照）。
また、滑り軸受は、転がり軸受に比べ摩擦抵抗によるトルク損失が大きい。このため、カムジャーナルに転がり軸受を用いてカムシャフトを回転可能に支持することが知られている。
しかしながら、滑り軸受に換えて摩擦抵抗が小さい転がり軸受によってカムシャフトを回転可能に支持した場合、転がり軸受の内部を通して油を供給する構成となる。
この場合、油圧供給源から供給される油が転がり軸受の内部を通してカムシャフトの油路に流れる際、転がり軸受の内部において油圧が低下し、可変バルブタイミング機構に悪影響を及ぼすことが想定される。
また、転がり軸受の内部に流入した油が転がり軸受の転動体の転動抵抗となることも想定される。
そこで、油圧供給源から供給される油圧の低下を抑制しながら油をカムシャフト側の油路に導くようにした転がり軸受装置が、例えば、特許文献２に開示されている。
特許文献２においては、転がり軸受の外輪に油圧供給源に通じる油孔が形成される。
また、外輪の複列の外輪軌道面の間に位置する内周面に、軸方向に所定間隔を隔て両環状溝がそれぞれ形成され、これら両環状溝に外径部分が嵌込まれて環状の両シール部材が配設される。そして、両シール部材の間に、外輪の油孔をカムシャフトの油路にシール状態を保って連通させる連通路が構成される。 Conventionally, for example, in order to supply hydraulic pressure to a variable valve timing mechanism assembled to the shaft end of a camshaft, for example, the camshaft is rotated to a cam journal (first journal) configured between a cylinder head and a cap member. There is known a sliding bearing in which a communication hole communicating with an oil passage of a camshaft is formed in a sliding bearing that can be supported (see Patent Document 1).
Further, the sliding bearing has a larger torque loss due to the frictional resistance than the rolling bearing. For this reason, it is known that the camshaft is rotatably supported by using a rolling bearing on the cam journal.
However, when the camshaft is rotatably supported by a rolling bearing having a small frictional resistance instead of the sliding bearing, oil is supplied through the inside of the rolling bearing.
In this case, when the oil supplied from the hydraulic pressure supply source flows into the oil passage of the camshaft through the inside of the rolling bearing, it is assumed that the hydraulic pressure is reduced inside the rolling bearing and adversely affects the variable valve timing mechanism.
Moreover, it is assumed that the oil which flowed into the inside of a rolling bearing becomes rolling resistance of the rolling element of a rolling bearing.
Therefore, for example, Patent Document 2 discloses a rolling bearing device that guides oil to an oil passage on the camshaft side while suppressing a decrease in hydraulic pressure supplied from a hydraulic pressure supply source.
In Patent Document 2, an oil hole leading to a hydraulic pressure supply source is formed in the outer ring of the rolling bearing.
In addition, both annular grooves are formed in the inner peripheral surface located between the outer ring raceway surfaces of the double rows of the outer rings at predetermined intervals in the axial direction, and the outer diameter portions are fitted into these annular grooves to form an annular shape. Both seal members are disposed. A communication passage is formed between the seal members so that the oil hole of the outer ring communicates with the oil passage of the camshaft while maintaining a sealed state.

特開２００７−３２７３６２号公報JP 2007-327362 A 特開２０１１−２７０８３号公報JP 2011-27083 A

ところで、特許文献２においては、油圧供給源から供給される油圧の低下を抑制しながら油を軸部材（カムシャフト）の油路に導くことができる。
しかしながら、特許文献２においては、外輪の内周面に、軸方向に所定間隔を隔て両環状溝を形成し、これら両環状溝に両シール部材の外径部分を嵌込んで組み付けなければならず、部品点数や組付工数が多くなりコスト高となる。 By the way, in patent document 2, oil can be guide | induced to the oil path of a shaft member (camshaft), suppressing the fall of the hydraulic pressure supplied from a hydraulic pressure supply source.
However, in Patent Document 2, both annular grooves are formed on the inner peripheral surface of the outer ring at predetermined intervals in the axial direction, and the outer diameter portions of both seal members must be fitted and assembled into these annular grooves. In addition, the number of parts and assembly man-hours increase, resulting in high costs.

この発明の目的は、前記問題点に鑑み、簡単な構造によって油圧供給源から供給される油圧の低下を抑制しながら油を軸部材の油路に導くことができる転がり軸受装置を提供することである。   In view of the above problems, an object of the present invention is to provide a rolling bearing device capable of guiding oil to an oil passage of a shaft member while suppressing a decrease in hydraulic pressure supplied from a hydraulic supply source with a simple structure. is there.

前記課題を解決するために、この発明の請求項１に係る転がり軸受装置は、外輪と内輪との間に複列の転動体が配設され、
前記複列の転動体の中間に位置する前記外輪と前記内輪との軸方向部分に、油圧供給源から供給される油を軸部材の油路に導くための外輪孔と内輪孔とがそれぞれ形成され、
前記外輪と前記内輪との間には、前記外輪孔又は前記内輪孔の一方との間で滑り軸受を構成するスリーブが配設され、
前記スリーブには、前記外輪孔と前記内輪孔とを連通する連通孔が形成されていることを特徴とする。 In order to solve the above problems, in the rolling bearing device according to claim 1 of the present invention, double row rolling elements are disposed between the outer ring and the inner ring,
An outer ring hole and an inner ring hole for guiding oil supplied from a hydraulic pressure supply source to an oil passage of a shaft member are formed in axial portions of the outer ring and the inner ring located in the middle of the double row rolling elements, respectively. And
Between the outer ring and the inner ring, a sleeve constituting a sliding bearing is disposed between the outer ring hole or one of the inner ring holes,
The sleeve is formed with a communication hole that communicates the outer ring hole and the inner ring hole.

前記構成によると、油圧供給源から供給される油は、外輪孔と、連通孔と、内輪孔とを順に経て軸部材の油路に導かれる。
また、スリーブは、シール部材としても機能するため、外輪孔、連通孔及び内輪孔に流入した油が複列の転動体側へ漏出することを抑制することができる。
前記したように、外輪と内輪との間に、スリーブを配設するという極めて簡単な構造によって、油圧の低下を抑制しながら油を軸部材の油路に良好に導くことができる。 According to the said structure, the oil supplied from a hydraulic pressure supply source is guide | induced to the oil path of a shaft member through an outer ring hole, a communicating hole, and an inner ring hole in order.
Further, since the sleeve also functions as a seal member, it is possible to suppress the oil that has flowed into the outer ring hole, the communication hole, and the inner ring hole from leaking to the double row rolling element side.
As described above, with a very simple structure in which a sleeve is disposed between the outer ring and the inner ring, oil can be guided well to the oil path of the shaft member while suppressing a decrease in hydraulic pressure.

請求項２に係る転がり軸受装置は、請求項１に記載の転がり軸受装置であって、
外輪の内周面の両端部には、外輪軌道面よりも小径の端鍔部がそれぞれ形成され、
前記外輪の内周面のスリーブが配設される部分には、中間鍔部が形成され、
前記中間鍔部の内径寸法は、前記端鍔部の内径寸法よりも小さく設定され、
前記中間鍔部の内周面に前記スリーブが嵌合されていることを特徴とする。 The rolling bearing device according to claim 2 is the rolling bearing device according to claim 1,
At both ends of the inner peripheral surface of the outer ring, end flanges having a smaller diameter than the outer ring raceway surface are formed, respectively.
In the portion where the sleeve on the inner peripheral surface of the outer ring is disposed, an intermediate collar is formed,
The inner diameter dimension of the intermediate collar is set smaller than the inner diameter dimension of the end collar,
The sleeve is fitted to the inner peripheral surface of the intermediate flange.

前記構成によると、外輪の中間鍔部の内径寸法が、端鍔部の内径寸法よりも小さく設定されるため、外輪の中間鍔部の内周面を旋削加工する際や中間鍔部の内周面にスリーブを圧入によって嵌合する際に、端鍔部が妨害物とならない。このため、外輪の中間鍔部の加工や中間鍔部の内周面に対するスリーブの組み付けが容易となる。   According to the above configuration, since the inner diameter dimension of the intermediate collar portion of the outer ring is set smaller than the inner diameter dimension of the end collar portion, when turning the inner peripheral surface of the intermediate collar portion of the outer ring, When the sleeve is fitted into the surface by press fitting, the end flange does not become an obstruction. For this reason, it becomes easy to process the intermediate collar portion of the outer ring and to assemble the sleeve to the inner peripheral surface of the intermediate collar portion.

この発明の実施例１に係る転がり軸受装置がカムシャフトの１番ジャーナルに採用された状態を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state by which the rolling bearing apparatus which concerns on Example 1 of this invention was employ | adopted as the 1st journal of the camshaft. この発明の実施例１に係る転がり軸受装置を拡大して示す縦断面図である。It is a longitudinal cross-sectional view which expands and shows the rolling bearing apparatus which concerns on Example 1 of this invention. スリーブの変更例を示す縦断面図である。It is a longitudinal cross-sectional view which shows the example of a change of a sleeve.

この発明を実施するための形態について実施例にしたがって説明する。   A mode for carrying out the present invention will be described in accordance with an embodiment.

この発明の実施例１を図面にしたがって説明する。
この発明の実施例１に係る転がり軸受装置は、カムシャフトに採用される場合を例示するものであり、図１に示すように、シリンダヘッド１とキャップ部材５との間に構成されるカムジャーナル（例えば、１番ジャーナル）に、軸部材としてのカムシャフト２０を回転可能に支持する。 A first embodiment of the present invention will be described with reference to the drawings.
The rolling bearing device according to the first embodiment of the present invention exemplifies a case where the rolling bearing device is employed in a camshaft, and as shown in FIG. (For example, the first journal) rotatably supports the camshaft 20 as a shaft member.

なお、カムシャフト２０は、軸体２１と、この軸体２１の軸上に所定間隔を隔てて配置される複数のカム駒２２とを備えている。
カムシャフト２０には径方向の縦孔２６と軸方向の横孔２７とを有する油路２５が形成されている。
また、カムシャフト２０の軸体２１の一端面には、ノックピン２３が打ち込まれ、軸体２１の一端部にはノックピン２３によって位置決めされた状態でタイミングギヤ３３、可変バルブタイミング機構３１が組み付けられる。
そして、可変バルブタイミング機構３１には、カムシャフト２０側の油路２５の横孔２７の端部が連通して接続される。また、キャップ部材５には、油圧供給源（油圧ポンプ）に通じる油孔７が形成される。 The camshaft 20 includes a shaft body 21 and a plurality of cam pieces 22 arranged on the shaft of the shaft body 21 at a predetermined interval.
An oil passage 25 having a radial vertical hole 26 and an axial horizontal hole 27 is formed in the camshaft 20.
A knock pin 23 is driven into one end surface of the shaft body 21 of the camshaft 20, and a timing gear 33 and a variable valve timing mechanism 31 are assembled to one end portion of the shaft body 21 while being positioned by the knock pin 23.
The variable valve timing mechanism 31 is connected to the end of the lateral hole 27 of the oil passage 25 on the camshaft 20 side. The cap member 5 is formed with an oil hole 7 communicating with a hydraulic supply source (hydraulic pump).

転がり軸受装置は、転がり軸受４０と、滑り軸受を構成するスリーブ７０とを備えている。
転がり軸受４０は、外輪４１と、内輪５１と、複列の転動体としてのころ６１、６６と、保持器６２、６７とを備えている。
外輪４１は、シリンダヘッド１の円弧凹部とキャップ部材５の円弧凹部との間に締め付けられて固定される。この外輪４１の内周面には、複列のころ６１、６６に対応する両外輪軌道面４５、４６が軸方向に所定距離を隔てて形成されている。
また、外輪４１の内周面の両端部には、両外輪軌道面４５、４６よりも小径の端鍔部４２、４３がそれぞれ形成されている。
さらに、外輪４１の内周面の両外輪軌道面４５、４６の間（後述するスリーブ７０が配設される部位）には、中間鍔部４４が形成されている。
そして、中間鍔部４４の内径寸法Ａは、端鍔部４２、４３の内径寸法Ｂよりも小径に設定されている。 The rolling bearing device includes a rolling bearing 40 and a sleeve 70 constituting a sliding bearing.
The rolling bearing 40 includes an outer ring 41, an inner ring 51, rollers 61 and 66 as double row rolling elements, and cages 62 and 67.
The outer ring 41 is fastened and fixed between an arc recess of the cylinder head 1 and an arc recess of the cap member 5. On the inner peripheral surface of the outer ring 41, both outer ring raceway surfaces 45 and 46 corresponding to the double row rollers 61 and 66 are formed at a predetermined distance in the axial direction.
Further, end flange portions 42 and 43 having a smaller diameter than both outer ring raceway surfaces 45 and 46 are formed at both ends of the inner peripheral surface of the outer ring 41.
Further, an intermediate flange 44 is formed between the outer ring raceway surfaces 45 and 46 on the inner peripheral surface of the outer ring 41 (a portion where a sleeve 70 described later is disposed).
The inner diameter dimension A of the intermediate collar part 44 is set to be smaller than the inner diameter dimension B of the end collar parts 42 and 43.

内輪５１は、カムシャフト２０の軸体２１の外周面に圧入されて固定される円筒状に形成され、その外周面には、両外輪軌道面４５、４６に対応する両内輪軌道面５５、５６が軸方向に所定距離を隔てて形成されている。
そして、外輪４１の両外輪軌道面４５、４６と、内輪５１の両内輪軌道面５５、５６ととの間には、保持器６２、６７によって保持された状態で複列のころ６１、６６が転動可能に組み付けられる。 The inner ring 51 is formed in a cylindrical shape that is press-fitted and fixed to the outer peripheral surface of the shaft body 21 of the camshaft 20, and both inner ring raceway surfaces 55, 56 corresponding to both outer ring raceway surfaces 45, 46 are formed on the outer peripheral surface. Are formed at a predetermined distance in the axial direction.
Then, between the outer ring raceway surfaces 45 and 46 of the outer ring 41 and the inner ring raceway surfaces 55 and 56 of the inner ring 51, double row rollers 61 and 66 are held by the cages 62 and 67. It is assembled so that it can roll.

図２に示すように、複列のころ６１、６６の中間に位置する外輪４１と内輪５１との軸方向部分には、油圧供給源から供給される油をカムシャフト２０の油路２５に導くための外輪孔４７と内輪孔５７とがそれぞれ形成されている。
また、外輪４１と、内輪５１との間には、外輪孔４７と内輪孔５７との一方との間で滑り軸受を構成するスリーブ７０が配設されている。
スリーブ７０は、外輪４１や内輪５１よりも軟質の金属（例えば銅系金属）又は合成樹脂材によって円筒状に形成されている。
そして、スリーブ７０は、外輪４１の中間鍔部４４の内周面に嵌合（圧入嵌合）されて固定される一方、スリーブ７０の内周面と内輪５１の外周面との間には微小な隙間８０が設定されている。
また、スリーブ７０には、外輪孔４７と内輪孔５７とを連通する連通孔７１が形成されている。
また、スリーブ７０の連通孔７１と内輪孔５７とを常時連通させるために、例えば、スリーブ７０の内周面側に開口する連通孔７１の開口端には、スリーブ７０の内周面に沿って環状をなす環状溝７２が形成されている。 As shown in FIG. 2, the oil supplied from the hydraulic supply source is guided to the oil passage 25 of the camshaft 20 in the axial direction portion between the outer ring 41 and the inner ring 51 positioned in the middle of the double row rollers 61 and 66. For this purpose, an outer ring hole 47 and an inner ring hole 57 are formed.
Between the outer ring 41 and the inner ring 51, a sleeve 70 constituting a slide bearing is disposed between one of the outer ring hole 47 and the inner ring hole 57.
The sleeve 70 is formed in a cylindrical shape from a softer metal (for example, copper-based metal) or a synthetic resin material than the outer ring 41 and the inner ring 51.
The sleeve 70 is fixed by being fitted (press-fit) to the inner peripheral surface of the intermediate flange portion 44 of the outer ring 41, while the inner surface of the sleeve 70 and the outer peripheral surface of the inner ring 51 are very small. A clear gap 80 is set.
In addition, a communication hole 71 that connects the outer ring hole 47 and the inner ring hole 57 is formed in the sleeve 70.
Further, in order to allow the communication hole 71 of the sleeve 70 and the inner ring hole 57 to always communicate with each other, for example, the opening end of the communication hole 71 opened on the inner peripheral surface side of the sleeve 70 is along the inner peripheral surface of the sleeve 70. An annular groove 72 having an annular shape is formed.

この実施例１に係る転がり軸受装置は上述したように構成される。
したがって、油圧供給源からキャップ部材５の油孔７に油（油圧）が供給ると、外輪４１の外輪孔４７と、スリーブ７０の連通孔７１と、内輪５１の内輪孔５７とを順に経て、カムシャフト２０の油路２５に導かれる。そして、油路２５から可変バルブタイミング機構３１に供給される油圧によってタイミングギヤ３３とカムシャフト２０とが相対的に回転制御（進角制御あるいは遅角制御）される。 The rolling bearing device according to the first embodiment is configured as described above.
Therefore, when oil (hydraulic pressure) is supplied from the hydraulic supply source to the oil hole 7 of the cap member 5, the outer ring hole 47 of the outer ring 41, the communication hole 71 of the sleeve 70, and the inner ring hole 57 of the inner ring 51 are sequentially passed through. It is guided to the oil passage 25 of the camshaft 20. The timing gear 33 and the camshaft 20 are relatively controlled to rotate (advance control or retard control) by the hydraulic pressure supplied from the oil passage 25 to the variable valve timing mechanism 31.

前記したように、油圧供給源から供給される油が、外輪４１の外輪孔４７と、スリーブ７０の連通孔７１と、内輪５１の内輪孔５７とを順に経て、カムシャフト２０の油路２５に導かれる際、スリーブ７０は、シール部材としても機能する。
このため、外輪孔４７、連通孔７１及び内輪孔５７に流入した油が複列のころ６１、６６へ向けて過剰に漏出することを抑制することができる。
このように、外輪４１と内輪５１との間に、スリーブ７０を配設するという極めて簡単な構造によって、油圧の低下を抑制しながら油をカムシャフト２０の油路２５に良好に導くことができる。
また、長期間の使用によって複列のころ６１、６６が摩耗した場合、スリーブ７０の内周面が内輪５１の外周面に接して摺動するため、軸受機能の延命を果たすことも可能となる。 As described above, the oil supplied from the hydraulic pressure supply source passes through the outer ring hole 47 of the outer ring 41, the communication hole 71 of the sleeve 70, and the inner ring hole 57 of the inner ring 51 in order, and enters the oil passage 25 of the camshaft 20. When guided, the sleeve 70 also functions as a seal member.
For this reason, it can suppress that the oil which flowed into the outer ring hole 47, the communication hole 71, and the inner ring hole 57 leaks excessively toward the double row rollers 61 and 66.
As described above, the oil can be favorably guided to the oil passage 25 of the camshaft 20 while suppressing a decrease in the hydraulic pressure by an extremely simple structure in which the sleeve 70 is disposed between the outer ring 41 and the inner ring 51. .
Further, when the double-row rollers 61 and 66 are worn due to long-term use, the inner peripheral surface of the sleeve 70 slides in contact with the outer peripheral surface of the inner ring 51, so that the life of the bearing function can be extended. .

また、この実施例１において、外輪４１の中間鍔部４４の内径寸法Ａが、端鍔部４２、４３の内径寸法Ｂよりも小さく設定されている。このため、外輪４１の中間鍔部４４の内周面を旋削加工する際や、中間鍔部４４の内周面にスリーブ７０を圧入によって嵌合する際に、端鍔部４２、４３が妨害物とならない。このため、外輪４１の中間鍔部４４の加工や中間鍔部４４の内周面に対するスリーブ７０の組み付けが容易となる。   In the first embodiment, the inner diameter dimension A of the intermediate collar portion 44 of the outer ring 41 is set smaller than the inner diameter dimension B of the end collar portions 42 and 43. For this reason, when turning the inner peripheral surface of the intermediate flange portion 44 of the outer ring 41 or when fitting the sleeve 70 to the inner peripheral surface of the intermediate flange portion 44 by press-fitting, the end flange portions 42 and 43 are obstructed. Not. For this reason, it becomes easy to process the intermediate flange 44 of the outer ring 41 and to assemble the sleeve 70 to the inner peripheral surface of the intermediate flange 44.

なお、この発明は前記実施例１に限定するものではなく、この発明の要旨を逸脱しない範囲内において、種々の形態で実施することができる。
例えば、前記実施例１においては、スリーブ７０が、外輪４１の中間鍔部４４の内周面に嵌合（圧入嵌合）されて固定される一方、スリーブ７０の内周面と内輪５１の外周面との間に微小な隙間８０が設定される場合を例示したが、図３に示すように、スリーブ７０が、外輪４１の中間鍔部４４に位置する内輪５１の外周面に嵌合（圧入嵌合）されて固定される一方、中間鍔部４４の内周面との間に微小な隙間８０が設定されるように配設されても同等の作用効果を奏する。
また、前記実施例１においては、カムシャフトに採用される転がり軸受装置である場合を例示したが、軸部材の油路に油圧を供給する必要があるクランクシャフト、バランサシャフト等に対してもこの発明の転がり軸受装置を採用することが可能である。 In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can implement with a various form.
For example, in the first embodiment, the sleeve 70 is fixed by being fitted (press-fit) to the inner peripheral surface of the intermediate flange 44 of the outer ring 41, while the inner peripheral surface of the sleeve 70 and the outer periphery of the inner ring 51 are fixed. The case where a minute gap 80 is set between the outer ring 41 and the surface is illustrated, but as shown in FIG. 3, the sleeve 70 is fitted (press-fit) to the outer circumferential surface of the inner ring 51 located at the intermediate flange 44 of the outer ring 41. On the other hand, even if it is arranged so that a minute gap 80 is set between the inner flange portion 44 and the inner peripheral surface of the intermediate flange portion 44, the same effect can be obtained.
Further, in the first embodiment, the case of the rolling bearing device adopted for the camshaft has been exemplified, but this is also applied to the crankshaft, balancer shaft, etc. that need to supply hydraulic pressure to the oil passage of the shaft member. It is possible to employ the rolling bearing device of the invention.

２０ カムシャフト（軸部材）
２５ 油路
４０ 転がり軸受
４１ 外輪
４２、４３ 端鍔部
４４ 中間鍔部
４５、４６ 外輪軌道面
４７ 外輪孔
５１ 内輪
５５、５６ 内輪軌道面
５７ 内輪孔
６１、６６ ころ（転動体）
７０ スリーブ
７１ 連通孔
７２ 環状溝
８０ 隙間 20 Camshaft (shaft member)
25 oil passage 40 rolling bearing 41 outer ring 42, 43 end flange 44 intermediate flange 45, 46 outer ring raceway surface 47 outer ring hole 51 inner ring 55, 56 inner ring raceway surface 57 inner ring hole 61, 66 roller (rolling element)
70 Sleeve 71 Communication hole 72 Annular groove 80 Clearance

Claims (2)

外輪と内輪との間に複列の転動体が配設され、
前記複列の転動体の中間に位置する前記外輪と前記内輪との軸方向部分に、油圧供給源から供給される油を軸部材の油路に導くための外輪孔と内輪孔とがそれぞれ形成され、
前記外輪と前記内輪との間には、前記外輪孔又は前記内輪孔の一方との間で滑り軸受を構成するスリーブが配設され、
前記スリーブには、前記外輪孔と前記内輪孔とを連通する連通孔が形成されていることを特徴とする転がり軸受装置。 Double row rolling elements are arranged between the outer ring and the inner ring,
An outer ring hole and an inner ring hole for guiding oil supplied from a hydraulic pressure supply source to an oil passage of a shaft member are formed in axial portions of the outer ring and the inner ring located in the middle of the double row rolling elements, respectively. And
Between the outer ring and the inner ring, a sleeve constituting a sliding bearing is disposed between the outer ring hole or one of the inner ring holes,
The rolling bearing device according to claim 1, wherein a communication hole that communicates the outer ring hole and the inner ring hole is formed in the sleeve. 請求項１に記載の転がり軸受装置であって、
外輪の内周面の両端部には、外輪軌道面よりも小径の端鍔部がそれぞれ形成され、
前記外輪の内周面のスリーブが配設される部分には、中間鍔部が形成され、
前記中間鍔部の内径寸法は、前記端鍔部の内径寸法よりも小さく設定され、
前記中間鍔部の内周面に前記スリーブが嵌合されていることを特徴とする転がり軸受装置。 The rolling bearing device according to claim 1,
At both ends of the inner peripheral surface of the outer ring, end flanges having a smaller diameter than the outer ring raceway surface are formed, respectively.
In the portion where the sleeve on the inner peripheral surface of the outer ring is disposed, an intermediate collar is formed,
The inner diameter dimension of the intermediate collar is set smaller than the inner diameter dimension of the end collar,
A rolling bearing device, wherein the sleeve is fitted to an inner peripheral surface of the intermediate flange.
JP2011204335A 2011-09-20 2011-09-20 Roller bearing device Withdrawn JP2013064463A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105570312A (en) * 2016-03-03 2016-05-11 如皋市非标轴承有限公司 High-speed ultra-wide roller oil supply bearing
JP6184648B1 (en) * 2016-03-01 2017-08-23 三菱電機株式会社 Bearing unit and compressor
WO2017149820A1 (en) * 2016-03-01 2017-09-08 三菱電機株式会社 Bearing unit and compressor
US20200088234A1 (en) * 2017-03-15 2020-03-19 Thyssenkrupp Rothe Erde Gmbh Hybrid hydrostatic bearing assembly and wind turbine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6184648B1 (en) * 2016-03-01 2017-08-23 三菱電機株式会社 Bearing unit and compressor
WO2017149820A1 (en) * 2016-03-01 2017-09-08 三菱電機株式会社 Bearing unit and compressor
CN105570312A (en) * 2016-03-03 2016-05-11 如皋市非标轴承有限公司 High-speed ultra-wide roller oil supply bearing
CN105570312B (en) * 2016-03-03 2018-07-27 如皋市非标轴承有限公司 High speed ultra-wide roller is for oil bearing
US20200088234A1 (en) * 2017-03-15 2020-03-19 Thyssenkrupp Rothe Erde Gmbh Hybrid hydrostatic bearing assembly and wind turbine
US10935072B2 (en) * 2017-03-15 2021-03-02 Thyssenkrupp Rothe Erde Gmbh Hybrid hydrostatic bearing assembly and wind turbine

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