JP2005133869A - Tapered roller bearing for transmission - Google Patents

Tapered roller bearing for transmission Download PDF

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Publication number
JP2005133869A
JP2005133869A JP2003371684A JP2003371684A JP2005133869A JP 2005133869 A JP2005133869 A JP 2005133869A JP 2003371684 A JP2003371684 A JP 2003371684A JP 2003371684 A JP2003371684 A JP 2003371684A JP 2005133869 A JP2005133869 A JP 2005133869A
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Prior art keywords
outer ring
housing
tapered roller
roller bearing
transmission
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Japanese (ja)
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Yuta Hamaguchi
雄太 濱口
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NSK Ltd
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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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing
    • 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
    • F16C19/34—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 for both radial and axial load
    • F16C19/36—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 for both radial and axial load with a single row of rollers
    • F16C19/364—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 for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing for a transmission capable of stably maintaining bearing performance for a long time by certainly preventing occurrence of creep. <P>SOLUTION: In the tapered roller bearing 10 for the transmission, an outer ring 11 has a notch 11e formed by diagonally notching part of a ring-like corner 11d formed of the outer peripheral surface 11b and the back surface 11c. The notch 11e is engaged with a projection 15e disposed in an inner corner 15d formed of the inner peripheral surface 15b and a side surface 15c of housing 15, thereby preventing the creep of the outer ring 11. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、トランスミッション用円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing for transmission.

従来、自動車用トランスミッションの回転軸は、対向して配置された一対のトランスミッション用円錐ころ軸受によって回動自在に支持されている。この円錐ころ軸受の外輪は、ハウジングの内側に内嵌固定されている。   2. Description of the Related Art Conventionally, a rotation shaft of an automobile transmission is rotatably supported by a pair of conical roller bearings for transmission that are arranged to face each other. The outer ring of this tapered roller bearing is fitted and fixed inside the housing.

一般的に、トランスミッションのハウジングは、軽量化を図るためにアルミニウム合金やマグネシウム合金から構成される。これに対して、トランスミッション用円錐ころ軸受の構成部品（外輪、内輪、円錐ころ等）は、耐久性を確保できるように軸受鋼等の鋼材から構成されており、該鋼材の硬度は、ハウジングの材料であるアルミニウム合金やマグネシウム合金より高い硬度を有している。また、アルミニウム合金やマグネシウム合金の線膨張係数は、円錐ころ軸受の材料である軸受鋼等の線膨張係数より大きい。   Generally, a transmission housing is made of an aluminum alloy or a magnesium alloy in order to reduce the weight. On the other hand, the component parts (outer ring, inner ring, tapered roller, etc.) of the tapered roller bearing for transmission are made of steel materials such as bearing steel so as to ensure the durability. It has higher hardness than aluminum alloy and magnesium alloy. Moreover, the linear expansion coefficient of aluminum alloy or magnesium alloy is larger than the linear expansion coefficient of bearing steel or the like which is a material of the tapered roller bearing.

硬度の低いアルミニウム合金やマグネシウム合金等からなるハウジングに組み込まれた円錐ころ軸受に、荷重が負荷された状態で回転軸（内輪）が回転すると、回転軸の回転に伴って外輪がハウジングの内側で回転する、いわゆるクリープが発生する場合がある。   When a rotating shaft (inner ring) rotates with a load on a tapered roller bearing built into a housing made of aluminum alloy, magnesium alloy or the like with low hardness, the outer ring moves inside the housing as the rotating shaft rotates. Rotating, so-called creep may occur.

クリープ力は、円錐ころ軸受に負荷される荷重が大きいほど大きくなる。従って、負荷される荷重の大きさに比例してクリープが発生し易くなる。特に、回転軸の回転に伴って円錐ころ軸受の温度が上昇すると、ハウジングと円錐ころ軸受との線膨張係数の差から締め代が減少し、ハウジングによる外輪の保持力が低下してクリープが発生する可能性が高くなる。   The creep force increases as the load applied to the tapered roller bearing increases. Accordingly, creep tends to occur in proportion to the applied load. In particular, if the temperature of the tapered roller bearing rises with the rotation of the rotating shaft, the allowance decreases due to the difference in linear expansion coefficient between the housing and the tapered roller bearing, and the holding force of the outer ring by the housing decreases and creep occurs. Is more likely to do.

クリープの発生によりハウジングと外輪との嵌合面で滑りが生じると、ハウジングの内周面や外輪、特に硬度の低いハウジングの内周面において異常摩耗する場合がある。このような異常摩耗が進行すると、ハウジングの内側で外輪のがたつきが生じ、異音、振動、焼付き等が発生して、円錐ころ軸受の性能を劣化させる原因となっていた。   If slippage occurs on the fitting surface between the housing and the outer ring due to the occurrence of creep, abnormal wear may occur on the inner peripheral surface of the housing and the outer ring, particularly on the inner peripheral surface of the housing with low hardness. When such abnormal wear progresses, the outer ring rattles inside the housing, causing abnormal noise, vibration, seizure, and the like, causing deterioration in the performance of the tapered roller bearing.

上述したクリープを防止する対策として、図４に示すような従来のトランスミッション用円錐ころ軸受１１０では、外輪１１１にフランジ１１１ａを設け、ボルト１１２によってフランジ１１１ａをハウジング１１５に固定して、外輪１１１とハウジング１１５とを機械的に強固に結合させたものがある。   As a countermeasure for preventing the above-described creep, in the conventional tapered roller bearing 110 for transmission as shown in FIG. 4, a flange 111a is provided on the outer ring 111, and the flange 111a is fixed to the housing 115 with a bolt 112. 115 is mechanically firmly bonded.

また、外輪に形成されたフランジの側面に突起部を有する樹脂層を設けると共に、ハウジングの側壁に凹部を形成して、突起部と凹部とを係合させながら外輪をハウジングに固定することによって、クリープの発生を防止するようにしたものが知られている（例えば、特許文献１参照）。
実開平５−８９９６０号公報（第４〜６頁、第２図） Also, by providing a resin layer having a protrusion on the side surface of the flange formed on the outer ring, forming a recess on the side wall of the housing, and fixing the outer ring to the housing while engaging the protrusion and the recess, A device that prevents the occurrence of creep is known (see, for example, Patent Document 1).
Japanese Utility Model Publication No. 5-89960 (pages 4-6, Fig. 2)

しかしながら、図４に示すような円錐ころ軸受１１０においては、フランジ１１１ａをボルト１１２によってハウジング１１５に固定する際に、円錐ころ軸受１１０の形状に歪みを生じさせる場合があり、軸受性能に悪影響を与える可能性があった。また、フランジ加工のためにコストが増大するという問題があった。   However, in the tapered roller bearing 110 as shown in FIG. 4, when the flange 111a is fixed to the housing 115 with the bolt 112, the shape of the tapered roller bearing 110 may be distorted, which adversely affects the bearing performance. There was a possibility. Further, there is a problem that the cost increases due to the flange processing.

また、特許文献１に開示されている転がり軸受は、突部と凹部との係合によりクリープを防止することができるが、この転がり軸受も、外輪のフランジ加工、ハウジングの装着部における凹部形成、及び突部を有する樹脂層により、コストが増大するという問題があった。   In addition, the rolling bearing disclosed in Patent Document 1 can prevent creep by the engagement between the protrusion and the recess, but this rolling bearing also has a flange processing of the outer ring, a recess formation in the mounting portion of the housing, In addition, there is a problem that the cost increases due to the resin layer having protrusions.

本発明は、前述した課題に鑑みてなされたものであり、その目的は、クリープの発生を確実に防止して、軸受性能を長期間、安定して維持できるトランスミッション用円錐ころ軸受を提供することにある。   The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a tapered roller bearing for transmission capable of reliably preventing creep and maintaining stable bearing performance for a long period of time. It is in.

本発明の上記目的は、下記構成により達成される。
外輪と、内輪と、前記外輪と前記内輪の軌道面間に転動自在に配置された複数個の円錐ころと、を備え、前記外輪の外周面と背面をハウジングの内周面と側面にそれぞれ対向させた状態で前記ハウジングに取り付け可能なトランスミッション用円錐ころ軸受であって、
前記外輪は、前記外周面と前記背面とから形成されるリング状角部の一部を斜めに切り欠くことで形成された切欠き部を備えており、前記切欠き部が前記ハウジングに設けられた突起部と係合することで、前記外輪のクリープを防止することを特徴とするトランスミッション用円錐ころ軸受。 The above object of the present invention is achieved by the following configurations.
An outer ring, an inner ring, and a plurality of tapered rollers arranged to roll between the raceway surfaces of the outer ring and the inner ring, and the outer peripheral surface and the back surface of the outer ring are respectively disposed on the inner peripheral surface and the side surface of the housing. A tapered roller bearing for a transmission that can be attached to the housing in an opposed state,
The outer ring includes a notch formed by obliquely notching a part of a ring-shaped corner formed from the outer peripheral surface and the back surface, and the notch is provided in the housing. A tapered roller bearing for transmission, wherein the outer ring is prevented from creeping by engaging with the protruding portion.

本発明のトランスミッション用円錐ころ軸受によれば、外輪は、その外周面と背面とから形成されるリング状角部の一部を斜めに切り欠くことで形成された切欠き部を備える。そして、この切欠き部がハウジングに設けられた突起部と係合することで、前記外輪のクリープを防止することができる。   According to the tapered roller bearing for transmission of the present invention, the outer ring includes a notch portion formed by obliquely notching a part of a ring-shaped corner portion formed from the outer peripheral surface and the back surface thereof. And the notch part engages with the projection part provided in the housing, so that creep of the outer ring can be prevented.

これによって、ハウジングの内周面の異常摩耗に起因して、外輪がハウジング内でがたつくことによる異音、振動、焼付き等の発生を防止することができ、軸受性能を長期間にわたって良好に維持することができる。   This prevents abnormal noise, vibration, seizure, etc. due to rattling of the outer ring in the housing due to abnormal wear on the inner peripheral surface of the housing, and maintains good bearing performance over a long period of time. can do.

また、フランジを不要とすることにより、フランジ加工に伴うコスト増大を抑制することができる。また、フランジのボルト締結に伴う円錐ころ軸受の形状歪みを回避でき、円錐ころ軸受本来の良好な軸受性能を発揮させることができる。   Moreover, the cost increase accompanying a flange process can be suppressed by making a flange unnecessary. Further, it is possible to avoid the shape distortion of the tapered roller bearing accompanying the bolt fastening of the flange, and to exhibit the original good bearing performance of the tapered roller bearing.

以下、本発明に係るトランスミッション用円錐ころ軸受の実施形態を図面を参照して詳細に説明する。   DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a tapered roller bearing for transmission according to the present invention will be described in detail with reference to the drawings.

図１は本発明に係るトランスミッション用円錐ころ軸受をハウジングの内側に嵌合させた状態を示す縦断面図であり、図２は図１におけるトランスミッション用円錐ころ軸受の外輪の要部斜視図である。また、図３は図１におけるハウジングの断面斜視図である。   1 is a longitudinal sectional view showing a state in which a tapered roller bearing for transmission according to the present invention is fitted inside a housing, and FIG. 2 is a perspective view of a main part of an outer ring of the tapered roller bearing for transmission in FIG. . FIG. 3 is a cross-sectional perspective view of the housing in FIG.

図１に示すように、トランスミッション用円錐ころ軸受１０は、外輪１１と、内輪１２と、転動体である複数個の円錐ころ１３とを備えている。外輪１１の内周面には、外輪軌道面１１ａが形成されており、内輪１２の外周面には、内輪軌道面１２ａが形成されている。円錐ころ１３は、保持器１４によって円周方向に所定の間隔で保持されながら、外輪軌道面１１ａと内輪軌道面１２ａとの間に転動自在に配置されている。   As shown in FIG. 1, the transmission tapered roller bearing 10 includes an outer ring 11, an inner ring 12, and a plurality of tapered rollers 13 that are rolling elements. An outer ring raceway surface 11 a is formed on the inner peripheral surface of the outer ring 11, and an inner ring raceway surface 12 a is formed on the outer peripheral surface of the inner ring 12. The tapered roller 13 is rotatably disposed between the outer ring raceway surface 11a and the inner ring raceway surface 12a while being held at a predetermined interval in the circumferential direction by the cage 14.

円錐ころ軸受１０は、外輪１１をハウジング１５の軸受収容部１５ａ内に嵌合させて配置されている。具体的には、外輪１１の外周面１１ｂとハウジング１５の内周面１５ｂが締め代をもって嵌合しており、外輪１１の外周面１１ｂを軸受収容部１５ａの内周面１５ｂに対向させ、外輪１１の背面１１ｃを軸受収容部１５ａの側面１５ｃに対向させた状態で、円錐ころ軸受１０はハウジング１５に取り付けられる。   The tapered roller bearing 10 is arranged with the outer ring 11 fitted in the bearing housing portion 15 a of the housing 15. Specifically, the outer peripheral surface 11b of the outer ring 11 and the inner peripheral surface 15b of the housing 15 are fitted with tightness, the outer peripheral surface 11b of the outer ring 11 is opposed to the inner peripheral surface 15b of the bearing housing portion 15a, and the outer ring The tapered roller bearing 10 is attached to the housing 15 with the back surface 11c of 11 facing the side surface 15c of the bearing housing portion 15a.

なお、外輪１１、内輪１２、円錐ころ１３は、軸受鋼、高速度鋼、ステンレス鋼等の高い硬度を有し、線膨張係数の小さな金属材料から構成されている。一方、トランスミッションのハウジング１５は、アルミニウム合金やマグネシウム合金等の外輪１１より低い硬度を有し、線膨張係数の大きな金属材料から構成されており、軽量化が図られている。   The outer ring 11, the inner ring 12, and the tapered roller 13 are made of a metal material having a high hardness such as bearing steel, high-speed steel, stainless steel, etc. and having a small linear expansion coefficient. On the other hand, the transmission housing 15 is made of a metal material having a hardness lower than that of the outer ring 11 such as an aluminum alloy or a magnesium alloy and having a large linear expansion coefficient, so that weight reduction is achieved.

図２に示すように、外輪１１は、外周面１１ｂと背面１１ｃとで規定されるリング状角部１１ｄにおいて、その一部に円錐ころ軸受１０の軸線Ｌに対して斜めに切り欠くことで形成された、略三日月形状を有する切欠き部１１ｅを備える。   As shown in FIG. 2, the outer ring 11 is formed by notching at an angle with respect to the axis L of the tapered roller bearing 10 at a part of the ring-shaped corner portion 11 d defined by the outer peripheral surface 11 b and the back surface 11 c. The cutout portion 11e having a substantially crescent shape is provided.

また、図３に示すように、ハウジング１５に形成された軸受収容部１５ａは、内周面１５ｂと側面１５ｃとで規定されるリング状内隅部１５ｄの一部に、嵌合される外輪１１側へ膨出し、切欠き部１１ｅと同一形状とされた略三日月形状を有する突起部１５ｅを備える。   Further, as shown in FIG. 3, the bearing housing portion 15a formed in the housing 15 is fitted to a part of a ring-shaped inner corner portion 15d defined by the inner peripheral surface 15b and the side surface 15c. A protrusion 15e having a substantially crescent moon shape that bulges to the side and has the same shape as the notch 11e is provided.

そして、図１に示すように、円錐ころ軸受１０がハウジング１５に取り付けられる際、外輪１１をハウジング１５の軸受収納部１５ａに内嵌させると同時に、外輪１１の切欠き部１１ｅが突起部１５ｅと係合する。   As shown in FIG. 1, when the tapered roller bearing 10 is attached to the housing 15, the outer ring 11 is fitted into the bearing housing portion 15 a of the housing 15, and at the same time, the notch portion 11 e of the outer ring 11 is connected to the protruding portion 15 e. Engage.

従って、円錐ころ軸受１０がハウジング１５に取り付けられた状態で、内輪１２の内周面に嵌合する回転軸（図示せず）が回転すると、該回転に伴って外輪１１にも内輪１２の回転方向と同一方向の回転力がクリープ力として作用する。しかしながら、外輪１１に作用するクリープ力は、切欠き部１１ｅと突起部１５ｅとの係合、及び外輪１１のハウジング１５への圧入による抵抗力によって抑止され、外輪１１が軸受収容部１５ａ内で回動することはない。従って、クリープの発生は防止される。   Accordingly, when a rotating shaft (not shown) fitted to the inner peripheral surface of the inner ring 12 rotates with the tapered roller bearing 10 attached to the housing 15, the outer ring 11 rotates along with the rotation. A rotational force in the same direction as the direction acts as a creep force. However, the creep force acting on the outer ring 11 is suppressed by the resistance force due to the engagement between the notch portion 11e and the protrusion 15e and the press-fitting of the outer ring 11 into the housing 15, and the outer ring 11 rotates in the bearing housing portion 15a. It doesn't move. Therefore, the occurrence of creep is prevented.

また、回転に伴って円錐ころ軸受１０の温度が上昇すると、外輪１１及びハウジング１５は、熱によって膨張する。鋼材より大きな線膨張係数を有するアルミニウム合金やマグネシウム合金等から作成されているハウジング１５は、外輪１１より大きく膨張する。このため、外輪１１と軸受収容部１５ａとの締め代が減少して、外輪１１の軸受収容部１５ａへの圧入による抵抗力は弱まる。しかし、外輪１１の切欠き部１１ｅが突起部１５ｅと係合しているので、円錐ころ軸受１０の温度が上昇しても外輪１１が軸受収容部１５ａ内で回転することはなく、クリープの発生が確実に防止される。   Further, when the temperature of the tapered roller bearing 10 increases with rotation, the outer ring 11 and the housing 15 expand due to heat. The housing 15 made of an aluminum alloy, a magnesium alloy or the like having a larger linear expansion coefficient than the steel material expands larger than the outer ring 11. For this reason, the tightening allowance between the outer ring 11 and the bearing housing portion 15a is reduced, and the resistance force due to the press fitting of the outer ring 11 into the bearing housing portion 15a is weakened. However, since the notch 11e of the outer ring 11 is engaged with the protrusion 15e, the outer ring 11 does not rotate in the bearing housing 15a even when the temperature of the tapered roller bearing 10 rises, and creep occurs. Is reliably prevented.

従って、トランスミッション等のように、外輪１１より硬度の低いアルミニウム合金やマグネシウム合金等からハウジング１５が形成されていても、軸受収容部１５ａの内周面１５ｂが異常摩耗や変形することはなく、外輪１１が軸受収容部１５ａ内でがたつくことによる異音、振動、焼付き等の発生が防止され、軸受性能に与える悪影響を防止することができる。   Therefore, even if the housing 15 is formed of an aluminum alloy, magnesium alloy, or the like having a lower hardness than the outer ring 11 as in a transmission or the like, the inner peripheral surface 15b of the bearing housing portion 15a is not abnormally worn or deformed. The occurrence of abnormal noise, vibration, seizure and the like due to rattling 11 in the bearing housing portion 15a is prevented, and adverse effects on bearing performance can be prevented.

よって、本発明に係るトランスミッション用円錐ころ軸受１０によれば、外輪１１は、その外周面１１ｂと背面１１ｃとから形成されるリング状角部１１ｄの一部を斜めに切り欠くことで形成された切欠き部１１ｅを備える。そして、この切欠き部１１ｅがハウジング１５の内周面１５ｂと側面１５ｃとから形成される内隅部１５ｄに設けられた突起部１５ｅと係合することで、前記外輪のクリープを防止することができる。   Therefore, according to the tapered roller bearing 10 for transmission according to the present invention, the outer ring 11 is formed by obliquely notching a part of the ring-shaped corner portion 11d formed by the outer peripheral surface 11b and the back surface 11c. A notch 11e is provided. And this notch part 11e engages with the projection part 15e provided in the inner corner part 15d formed from the internal peripheral surface 15b and the side surface 15c of the housing 15, and it can prevent the creep of the said outer ring | wheel. it can.

また、これによって、軸受収容部１５ａの内周面１５ｂが異常摩耗して外輪１１が軸受収容部１５ａ内でがたつくことによる異音、振動、焼付き等の発生を防止し、軸受性能を長期間にわたって良好に維持することができる。   This also prevents abnormal noise, vibration, seizure, etc. due to abnormal wear of the inner peripheral surface 15b of the bearing housing portion 15a and rattling of the outer ring 11 in the bearing housing portion 15a. Can be maintained well over.

また、フランジを不要とすることにより、フランジ加工に伴うコスト増大を抑制することができる。また、フランジのボルト締結に伴う円錐ころ軸受の形状歪みを回避でき、円錐ころ軸受本来の良好な軸受性能を発揮させることができる。   Moreover, the cost increase accompanying a flange process can be suppressed by making a flange unnecessary. Further, it is possible to avoid the shape distortion of the tapered roller bearing accompanying the bolt fastening of the flange, and to exhibit the original good bearing performance of the tapered roller bearing.

尚、本発明は、前述した実施形態に限定されるものではなく、適宜、変形、改良等が可能である。   In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

なお、本発明のトラスミッション用円錐ころ軸受は、トランスミッション部分と最終減速機が組み込まれたトランスアクスル内のいずれかの回転軸を支承するための軸受に適用されるもので、一対の円錐ころ軸受を回転軸の両側に組み合わせて配置することが好ましい。
また、本発明における切り欠き部は、リング状角部に少なくとも一つ形成されていればよく、複数箇所に形成されてもよい。 The tapered roller bearing for a truss transmission of the present invention is applied to a bearing for supporting any rotating shaft in a transaxle in which a transmission portion and a final reduction gear are incorporated, and a pair of tapered roller bearings Are preferably arranged in combination on both sides of the rotating shaft.
Moreover, the notch part in this invention should just be formed in the ring-shaped corner | angular part at least one, and may be formed in multiple places.

本発明のトランスミッション用円錐ころ軸受をハウジングの軸受収容部に嵌合させた状態を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state which fitted the tapered roller bearing for transmissions of this invention to the bearing accommodating part of the housing. 図１におけるトランスミッション用円錐ころ軸受の外輪の要部斜視図である。It is a principal part perspective view of the outer ring | wheel of the tapered roller bearing for transmissions in FIG. 図１におけるハウジングの断面斜視図である。It is a cross-sectional perspective view of the housing in FIG. 従来のトランスミッション用円錐ころ軸受をハウジングに嵌合させ、フランジをボルトでハウジングに固定した状態を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state which fitted the conventional tapered roller bearing for transmissions with the housing, and fixed the flange to the housing with the volt | bolt.

符号の説明Explanation of symbols

１０ トランスミッション用円錐ころ軸受
１１ 外輪
１１ａ 外輪軌道面
１１ｂ 外周面
１１ｃ 背面
１１ｄ リング状角部
１１ｅ 切欠き部
１２ 内輪
１２ａ 内輪軌道面
１３ 円錐ころ
１５ ハウジング
１５ａ 軸受収容部
１５ｂ 軸受収容部の内周面
１５ｄ リング状内隅部
１５ｅ 突起部 DESCRIPTION OF SYMBOLS 10 Transmission tapered roller bearing 11 Outer ring 11a Outer ring raceway surface 11b Outer peripheral surface 11c Back surface 11d Ring-shaped corner | angular part 11e Notch part 12 Inner ring 12a Inner ring raceway surface 13 Tapered roller 15 Housing 15a Bearing accommodating part 15b Inner peripheral surface 15d of a bearing accommodating part Ring-shaped inner corner 15e Protrusion

Claims (1)

外輪と、内輪と、前記外輪と前記内輪の軌道面間に転動自在に配置された複数個の円錐ころと、を備え、前記外輪の外周面と背面をハウジングの内周面と側面にそれぞれ対向させた状態で前記ハウジングに取り付け可能なトランスミッション用円錐ころ軸受であって、
前記外輪は、前記外周面と前記背面とから形成されるリング状角部の一部を斜めに切り欠くことで形成された切欠き部を備えており、前記切欠き部が前記ハウジングに設けられた突起部と係合することで、前記外輪のクリープを防止することを特徴とするトランスミッション用円錐ころ軸受。 An outer ring, an inner ring, and a plurality of tapered rollers arranged to roll between the raceway surfaces of the outer ring and the inner ring, and the outer peripheral surface and the back surface of the outer ring are respectively disposed on the inner peripheral surface and the side surface of the housing. A tapered roller bearing for a transmission that can be attached to the housing in an opposed state,
The outer ring includes a notch formed by obliquely notching a part of a ring-shaped corner formed from the outer peripheral surface and the back surface, and the notch is provided in the housing. A tapered roller bearing for transmission, wherein the outer ring is prevented from creeping by engaging with the protruding portion.
JP2003371684A 2003-10-31 2003-10-31 Tapered roller bearing for transmission Pending JP2005133869A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003371684A JP2005133869A (en) 2003-10-31 2003-10-31 Tapered roller bearing for transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2003371684A JP2005133869A (en) 2003-10-31 2003-10-31 Tapered roller bearing for transmission

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Publication Number Publication Date
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007092863A (en) * 2005-09-28 2007-04-12 Jtekt Corp Bearing device
JP2009036320A (en) * 2007-08-02 2009-02-19 Nsk Ltd Bearing unit and method for fixing rolling bearing
CN103256376A (en) * 2012-02-15 2013-08-21 本田技研工业株式会社 Bearing fixing structure
CN107795586A (en) * 2016-09-07 2018-03-13 斯凯孚公司 Bearing assembly
US10060478B2 (en) * 2015-05-28 2018-08-28 Robert Bosch Gmbh Roller bearing and hydrostatic axial piston machine of swashplate design with a roller bearing

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007092863A (en) * 2005-09-28 2007-04-12 Jtekt Corp Bearing device
JP2009036320A (en) * 2007-08-02 2009-02-19 Nsk Ltd Bearing unit and method for fixing rolling bearing
CN103256376A (en) * 2012-02-15 2013-08-21 本田技研工业株式会社 Bearing fixing structure
US10060478B2 (en) * 2015-05-28 2018-08-28 Robert Bosch Gmbh Roller bearing and hydrostatic axial piston machine of swashplate design with a roller bearing
CN107795586A (en) * 2016-09-07 2018-03-13 斯凯孚公司 Bearing assembly
US10240635B2 (en) * 2016-09-07 2019-03-26 Aktiebolaget Skf Bearing assembly

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