JP2011033064A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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JP2011033064A
JP2011033064A JP2009177346A JP2009177346A JP2011033064A JP 2011033064 A JP2011033064 A JP 2011033064A JP 2009177346 A JP2009177346 A JP 2009177346A JP 2009177346 A JP2009177346 A JP 2009177346A JP 2011033064 A JP2011033064 A JP 2011033064A
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resin layer
peripheral surface
conical
cone
fixed portion
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Hirobumi Momoji
博文 百々路
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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
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller bearings
    • 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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C33/64—Special methods of manufacture
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing having superior assemblability, high rigidity, and high damping performance including a resin layer directly formed on a raceway ring. <P>SOLUTION: An outer ring 30 configuring the tapered roller bearing 10 includes an inner member 36 having an outer ring tapered raceway surface 32 on its inner periphery and a tapered outer peripheral surface 38 on its outer periphery, an outer member 40 having a tapered inner peripheral surface 42 on its inner periphery and a housing mounting surface 34 on its outer periphery, and the resin layer 44 interposed between the tapered outer peripheral surface 38 and the tapered inner peripheral surface 42. The resin layer 44 includes a fixed part and a non-fixed part in the circumferential direction with respect to at least one of the tapered outer peripheral surface 38 of the inner member 36 and the tapered inner peripheral surface 42 of the outer member 40. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

この発明は円錐ころ軸受に関する。さらに詳しくは、制振性が高く剛性に優れた円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing. More specifically, the present invention relates to a tapered roller bearing having high vibration damping properties and excellent rigidity.

自動車のトランスミッションに使用される円錐ころ軸受においては、軸側に生じた振動が円錐ころ軸受を介してハウジング側に伝わるという問題がある。そこで、トランスミッションに使用される円錐ころ軸受には制振性が求められる。そして、制振の方式としては、外輪とハウジングの間に制振用の樹脂層を設ける方法が考えられる。このとき、軸受の剛性確保のために樹脂層の厚さを薄く保つことが必要とされる。
特開２００７−２９４６号公報（特許文献１）には、外輪の外周面に円環状の樹脂製の防振層を螺着した転がり軸受が記載されている。しかし、特許文献１に記載の方法では、樹脂製の防振層の表面が露出する構成のため、防振層が薄いと、防振層を外輪に螺着する際または防振層を螺着した外輪をハウジングに取付ける際に樹脂製の防振層に亀裂が生じて防振性が低下してしまうおそれがある。そして、防振層が厚いと、軸受の剛性が不足して軸の芯ぶれが生じやすくなるという問題がある。 In a tapered roller bearing used for an automobile transmission, there is a problem that vibration generated on the shaft side is transmitted to the housing side via the tapered roller bearing. Therefore, the tapered roller bearing used in the transmission is required to have vibration damping properties. As a vibration control method, a method of providing a resin layer for vibration suppression between the outer ring and the housing can be considered. At this time, it is necessary to keep the resin layer thin in order to ensure the rigidity of the bearing.
Japanese Patent Laying-Open No. 2007-2946 (Patent Document 1) describes a rolling bearing in which an annular resin vibration-proof layer is screwed onto the outer peripheral surface of an outer ring. However, in the method described in Patent Document 1, since the surface of the resin vibration-proof layer is exposed, if the vibration-proof layer is thin, when the vibration-proof layer is screwed to the outer ring or the vibration-proof layer is screwed When attaching the outer ring to the housing, there is a possibility that the vibration-proof layer made of resin may crack and the vibration-proof performance may be lowered. When the vibration-proof layer is thick, there is a problem that the shaft is liable to run out due to insufficient rigidity of the bearing.

ハウジングへの軸受の取付け時に防振層に亀裂が生じるのを避ける方法として、特開２００８−２０２７８２号公報（特許文献２）には、樹脂サンドイッチ鋼板をスリーブ成形した防振部をハウジングと外輪の間に配置した円錐ころ軸受が記載されている。
図４に、特許文献２に記載された円錐ころ軸受とほぼ同一の構成の円錐ころ軸受１００を示す。円錐ころ軸受１００は、軸体１１０に固定され軸体１１０とともに回転する内輪１２０と、樹脂サンドイッチ鋼板をスリーブ成形した防振部１３０と、外周面を防振部１３０で被覆してハウジング１４０に固定される外輪１５０と、内輪１２０と外輪１５０の間に配設された円錐ころ１６０を備える。特許文献２に記載の円錐ころ軸受１００は、防振部１３０が樹脂サンドイッチ鋼板で構成されており、樹脂層の厚さを薄くすることができるため、軸受の剛性を確保することができる。そして、防振部１３０の樹脂層１３２は鋼板１３４でサンドイッチされており、防振部１３０をハウジング１４０に取付ける際に、樹脂層１３２が直接ハウジング１４０や外輪１５０に接触することがないので、樹脂層１３２に亀裂が生じるおそれがない。 As a method for preventing the vibration-proof layer from cracking when the bearing is attached to the housing, Japanese Patent Application Laid-Open No. 2008-202782 (Patent Document 2) describes a vibration-proof portion in which a resin sandwich steel plate is sleeve-formed between the housing and the outer ring. A tapered roller bearing arranged in between is described.
FIG. 4 shows a tapered roller bearing 100 having substantially the same configuration as the tapered roller bearing described in Patent Document 2. The tapered roller bearing 100 is fixed to the housing 140 by covering the inner ring 120 fixed to the shaft body 110 and rotating together with the shaft body 110, the vibration-proof portion 130 formed by sleeve-molding a resin sandwich steel plate, and the vibration-proof portion 130 covering the outer peripheral surface. An outer ring 150 and a tapered roller 160 disposed between the inner ring 120 and the outer ring 150. In the tapered roller bearing 100 described in Patent Document 2, the vibration isolator 130 is made of a resin sandwich steel plate, and the thickness of the resin layer can be reduced, so that the rigidity of the bearing can be ensured. The resin layer 132 of the vibration isolator 130 is sandwiched between the steel plates 134, and the resin layer 132 does not directly contact the housing 140 or the outer ring 150 when the vibration isolator 130 is attached to the housing 140. There is no risk of cracking in the layer 132.

特開２００７−２９４６号公報JP 2007-2946 A 特開２００８−２０２７８２号公報JP 2008-202782 A

しかしながら、特許文献２に記載の円錐ころ軸受では、防振部が別部材とされているため、部品点数が多くなり、軸受の組付けに手間がかかるという問題がある。   However, in the tapered roller bearing described in Patent Document 2, since the vibration isolator is a separate member, there is a problem that the number of parts increases and it takes time to assemble the bearing.

そこで、本発明が解決しようとする課題は、軌道輪に樹脂層を直接形成した、組付け性が良く制振性および剛性の高い円錐ころ軸受を提供することにある。   Accordingly, the problem to be solved by the present invention is to provide a tapered roller bearing in which a resin layer is directly formed on a raceway ring, which is easy to assemble and has high vibration damping and rigidity.

上記課題を解決するため、本発明にかかる円錐ころ軸受は次の手段をとる。
まず、本発明の第１の発明は、外周に内輪円錐軌道面を有する内輪と、内周に外輪円錐軌道面を有する外輪と、前記内輪円錐軌道面と前記外輪円錐軌道面との間に転動自在に配設される円錐ころとを備える円錐ころ軸受において、
前記外輪は、内周に前記外輪円錐軌道面を有するとともに、外周に円錐外周面を有する内部部材と、内周に円錐内周面を有するとともに、外周にハウジング取付面を有する外部部材と、前記円錐外周面と前記円錐内周面との間に介在する樹脂層とを備え、
前記樹脂層は、前記内部部材の円錐外周面および前記外部部材の円錐内周面の少なくとも一方に対して、周方向に固着部と非固着部とを有することを特徴とする。 In order to solve the above problems, the tapered roller bearing according to the present invention takes the following means.
First, the first invention of the present invention is an inner ring having an inner ring conical raceway surface on the outer periphery, an outer ring having an outer ring conical raceway surface on the inner circumference, and the inner ring conical raceway surface and the outer ring conical raceway surface. In a tapered roller bearing comprising a tapered roller movably disposed,
The outer ring has the outer ring conical raceway surface on the inner periphery, an inner member having a conical outer periphery surface on the outer periphery, an outer member having a cone inner peripheral surface on the inner periphery and a housing mounting surface on the outer periphery, A resin layer interposed between the outer circumferential surface of the cone and the inner circumferential surface of the cone,
The resin layer has a fixed portion and a non-fixed portion in a circumferential direction with respect to at least one of a conical outer peripheral surface of the inner member and a conical inner peripheral surface of the outer member.

この第１の発明によれば、外輪の内部部材の円錐外周面と、外輪の外部部材の円錐内周面の間に樹脂層を介在させている。そこで、内部部材と外部部材を軸方向に組み合わせた時に両円錐面の間に薄い隙間が形成される構成とすることで、両円錐面の間に介在させる樹脂層の厚さを薄く保つことができ、軸受の剛性を確保することができる。また、樹脂層は軌道輪である外輪に直接形成され、制振用の別部材を用いていないため、組み付け性がよい。
そして、樹脂層は、内部部材および外部部材の少なくとも一方に対して、周方向に固着部と非固着部とを有する構成とされている。そこで、樹脂層が内部部材に対して周方向に固着部と非固着部を有する場合は、内部部材が振動すると樹脂層の固着部では表面が内部部材と共に振動するが、樹脂層の非固着部では樹脂層が内部部材に対して滑るため振動が伝わりにくい。そのため樹脂層の固着部と非固着部の境にせん断応力が加わり樹脂が粘弾性により変形して振動を吸収し熱が生ずる。よって、振動エネルギーが熱に変換されて振動が吸収されるため、制振性が高められる。また、樹脂層が外部部材に対して周方向に固着部と非固着部を有する場合は、内部部材の振動が樹脂層の外部部材側に伝わった場合、固着部は外部部材により表面の振動が抑制され、非固着部は外部部材に対して滑って振動する。そのため、樹脂層の固着部と非固着部の境にせん断応力が加わり樹脂が粘弾性により変形して振動を吸収し熱が生ずる。よって、振動エネルギーが熱に変換されて振動が吸収されるため、制振性が高められる。
よって、軌道輪に樹脂層を直接形成した、組付け性が良く制振性および剛性の高い円錐ころ軸受を提供することができる。 According to the first aspect of the invention, the resin layer is interposed between the conical outer peripheral surface of the inner member of the outer ring and the conical inner peripheral surface of the outer member of the outer ring. Thus, by combining the inner member and the outer member in the axial direction, a thin gap is formed between the two conical surfaces, so that the thickness of the resin layer interposed between the two conical surfaces can be kept thin. The rigidity of the bearing can be ensured. In addition, the resin layer is formed directly on the outer ring, which is a raceway ring, and does not use a separate member for vibration suppression.
And the resin layer is set as the structure which has an adhering part and a non-adhering part in the circumferential direction with respect to at least one of an internal member and an external member. Therefore, when the resin layer has a fixed portion and a non-fixed portion in the circumferential direction with respect to the internal member, when the internal member vibrates, the surface of the fixed portion of the resin layer vibrates with the internal member, but the non-fixed portion of the resin layer Then, since the resin layer slides with respect to the internal member, vibration is hardly transmitted. Therefore, shear stress is applied to the boundary between the fixed portion and the non-fixed portion of the resin layer, and the resin is deformed by viscoelasticity to absorb vibration and generate heat. Therefore, vibration energy is converted into heat and vibration is absorbed, so that vibration damping is improved. Further, when the resin layer has a fixed portion and a non-fixed portion in the circumferential direction with respect to the external member, when the vibration of the internal member is transmitted to the external member side of the resin layer, the surface of the fixed portion is vibrated by the external member. The non-fixed portion is slid and vibrates with respect to the external member. Therefore, a shear stress is applied to the boundary between the fixed portion and the non-fixed portion of the resin layer, and the resin is deformed by viscoelasticity to absorb vibration and generate heat. Therefore, vibration energy is converted into heat and vibration is absorbed, so that vibration damping is improved.
Therefore, it is possible to provide a tapered roller bearing in which a resin layer is directly formed on the raceway ring, which is easy to assemble and has high vibration damping and rigidity.

次に、本発明の第２の発明は、上記第１の発明に係る円錐ころ軸受であって、前記樹脂層は、前記内部部材の円錐外周面および前記外部部材の円錐内周面の両方に対して周方向に固着部と、非固着部とを有し、
前記樹脂層と前記内部部材の円錐外周面との非固着部の周方向位置と該樹脂層と前記外部部材の円錐内周面との固着部の周方向位置が重なるとともに、前記樹脂層と前記外部部材の円錐内周面との非固着部の周方向位置と該樹脂層と前記内部部材の円錐外周面との固着部の周方向位置が重なることを特徴とする。
この第２の発明によれば、樹脂層は内部部材に固着する周方向位置では外部部材に非固着であるため、樹脂層の内部部材側の表面が内部部材と共に振動する周方向位置では、樹脂層は外部部材に対して滑るので、振動が樹脂層から外部部材へ伝わりにくい。また、樹脂層は内部部材側と外部部材側の双方で固着部と非固着部を有するので、樹脂層の両側で振動エネルギーが熱に変換されて振動が吸収される。よって、制振性がさらに高められる。 Next, a second invention of the present invention is the tapered roller bearing according to the first invention, wherein the resin layer is formed on both the conical outer peripheral surface of the inner member and the conical inner peripheral surface of the outer member. On the other hand, it has a fixed part and a non-fixed part in the circumferential direction,
The circumferential position of the non-fixed portion between the resin layer and the outer peripheral surface of the cone of the inner member overlaps the circumferential position of the fixed portion of the resin layer and the inner peripheral surface of the cone of the outer member, and the resin layer and the The circumferential position of the non-fixed portion between the outer member and the inner peripheral surface of the cone overlaps with the circumferential position of the fixed portion between the resin layer and the outer peripheral surface of the cone of the inner member.
According to the second invention, since the resin layer is not fixed to the external member at the circumferential position where the resin layer is fixed to the internal member, the resin layer is not fixed to the external member at the circumferential position where the surface of the resin layer on the internal member side vibrates together with the internal member. Since the layer slides with respect to the external member, vibration is not easily transmitted from the resin layer to the external member. Further, since the resin layer has a fixed portion and a non-fixed portion on both the inner member side and the outer member side, vibration energy is converted into heat on both sides of the resin layer, and vibration is absorbed. Accordingly, the vibration damping property is further improved.

上述の本発明の各発明によれば、次の効果が得られる。
まず、上述の第１の発明によれば、軌道輪に樹脂層を直接形成した、組付け性が良く制振性および剛性の高い円錐ころ軸受を提供することができる。
次に上述の第２の発明によれば、振動が樹脂層から外部部材へ伝わりにくく、樹脂層の両側で、振動エネルギーが熱に変換されて振動が吸収される。よって、制振性がさらに高められる。 According to each invention of the present invention described above, the following effects can be obtained.
First, according to the above-mentioned first invention, it is possible to provide a tapered roller bearing in which a resin layer is directly formed on the raceway ring, which is easy to assemble and has high vibration damping properties and high rigidity.
Next, according to the above-mentioned second invention, vibration is not easily transmitted from the resin layer to the external member, and vibration energy is converted into heat on both sides of the resin layer to absorb the vibration. Accordingly, the vibration damping property is further improved.

実施例１における円錐ころ軸受の軸平行断面図である。1 is an axial parallel sectional view of a tapered roller bearing in Embodiment 1. FIG. 図１のＡ−Ａ位置において外輪を輪切りにした断面図である。It is sectional drawing which cut the outer ring | wheel in the AA position of FIG. 実施例１における外輪の製造工程を示す図である。FIG. 5 is a diagram illustrating an outer ring manufacturing process according to the first embodiment. 従来技術における制振性を有する円錐ころ軸受を示す図である。It is a figure which shows the tapered roller bearing which has the damping property in a prior art.

以下、本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。   Hereinafter, modes for carrying out the present invention will be described according to examples.

［円錐ころ軸受の構成］
はじめに、実施例１における円錐ころ軸受１０の構成を説明する。図１に本発明の実施例１における円錐ころ軸受１０の軸平行断面図を示す。円錐ころ軸受１０は自動車のトランスミッションに使用される円錐ころ軸受である。そして、外周に内輪円錐軌道面１６を有する内輪１４と、内周に外輪円錐軌道面３２を有し外周に円筒状のハウジング取付面３４を有する外輪３０と、内輪円錐軌道面１６と外輪円錐軌道面３２との間に転動自在に配設される円錐ころ１８とを備えている。そして、内輪１４は軸体１２に取付けられて軸体１２と共に回転し、外輪３０はハウジング取付面３４でハウジング２０に固定される構成とされている。
そして、外輪３０は、内周に外輪円錐軌道面３２を有し、外周に円錐外周面３８を有する内部部材３６と、内周に円錐内周面４２を有し、外周にハウジング取付面３４を有する外部部材４０とを備えている。そして、内部部材３６の円錐外周面３８と外部部材４０の円錐内周面４２との間には樹脂層４４が形成されている。 [Configuration of tapered roller bearing]
First, the configuration of the tapered roller bearing 10 according to the first embodiment will be described. FIG. 1 shows an axial parallel sectional view of a tapered roller bearing 10 in Embodiment 1 of the present invention. The tapered roller bearing 10 is a tapered roller bearing used in an automobile transmission. Then, the inner ring 14 having the inner ring conical raceway surface 16 on the outer periphery, the outer ring 30 having the outer ring conical raceway surface 32 on the inner periphery and the cylindrical housing mounting surface 34 on the outer periphery, the inner ring conical raceway surface 16 and the outer ring conical track. A tapered roller 18 disposed between the surface 32 and the surface 32 is provided. The inner ring 14 is attached to the shaft body 12 and rotates together with the shaft body 12, and the outer ring 30 is fixed to the housing 20 by the housing attachment surface 34.
The outer ring 30 has an outer ring conical raceway surface 32 on the inner periphery, an inner member 36 having a conical outer peripheral surface 38 on the outer periphery, a cone inner peripheral surface 42 on the inner periphery, and a housing mounting surface 34 on the outer periphery. And an external member 40. A resin layer 44 is formed between the conical outer peripheral surface 38 of the inner member 36 and the conical inner peripheral surface 42 of the outer member 40.

図２に、図１のＡ−Ａ位置における、外輪３０の断面図を示す。図２に示すとおり、樹脂層４４は、内部部材３６の円錐外周面３８および外部部材４０の円錐内周面４２の両方に対して周方向に離型層５０が交互に設けられている。そして、樹脂層４４に離型層５０が設けられている部位は、樹脂層４４が円錐外周面３８および円錐内周面４２から浮いた状態の非固着部４８とされ、樹脂層４４に離型層５０が設けられていない部位は、樹脂層４４が内部部材３６の円錐外周面３８および外部部材４０の円錐内周面４２に固着した固着部４６とされている。
なお、後述の通り樹脂層４４の厚さは５０μｍ程度であり、図２では樹脂層４４の厚さを誇張して記載している。
そして、図２に示すとおり、樹脂層４４と円錐外周面３８との非固着部４８の周方向位置と樹脂層４４と円錐内周面４２との固着部４６の周方向位置が重なる構成とされている。また、樹脂層４４と円錐内周面４２との非固着部４８の周方向位置と樹脂層４４と円錐外周面３８との固着部４６の周方向位置が重なる構成とされている。 FIG. 2 shows a cross-sectional view of the outer ring 30 at the position AA in FIG. As shown in FIG. 2, in the resin layer 44, release layers 50 are alternately provided in the circumferential direction with respect to both the conical outer peripheral surface 38 of the inner member 36 and the conical inner peripheral surface 42 of the outer member 40. The part where the release layer 50 is provided in the resin layer 44 is a non-adhered portion 48 in a state where the resin layer 44 is lifted from the cone outer peripheral surface 38 and the cone inner peripheral surface 42. The portion where the layer 50 is not provided is a fixing portion 46 in which the resin layer 44 is fixed to the conical outer peripheral surface 38 of the inner member 36 and the conical inner peripheral surface 42 of the outer member 40.
As will be described later, the thickness of the resin layer 44 is about 50 μm, and the thickness of the resin layer 44 is exaggerated in FIG.
As shown in FIG. 2, the circumferential position of the non-fixed portion 48 between the resin layer 44 and the cone outer peripheral surface 38 and the circumferential position of the fixed portion 46 between the resin layer 44 and the cone inner peripheral surface 42 overlap each other. ing. Further, the circumferential position of the non-fixed portion 48 between the resin layer 44 and the conical inner peripheral surface 42 and the circumferential position of the fixed portion 46 between the resin layer 44 and the conical outer peripheral surface 38 overlap each other.

［外輪の製造方法］
次に、円錐ころ軸受１０を構成する外輪３０の製造方法について説明する。外輪３０は、内部部材３６と外部部材４０を各々作成し、内部部材３６の外周の円錐面と外部部材４０の内周の円錐面の間に樹脂層４４を挟んで一体化させることにより製造する。
図３（ａ）に内部部材３６の軸平行断面図を示す。内部部材３６は、鋼材を鍛造により厚みがほぼ一定の円錐筒状に成形し、切削、研磨により形を整えて形成する。内部部材３６の内周の円錐面は外輪円錐軌道面３２とされ、内部部材３６の外周の円錐面は円錐外周面３８とされる。内部部材３６に使用する鋼材はＪＩＳ高炭素クロム軸受鋼、たとえばＳＵＪ２とし、鍛造、切削、研磨により内部部材３６に形成の後に、焼き入れ焼き戻しの熱処理を行う。
図３（ｂ）に外部部材４０の軸平行断面図を示す。外部部材４０は、鋼材を鍛造により内周を円錐面、外周を円筒面とする形状に成形し、切削、研磨により形を整えて形成する。外部部材４０の内周の円錐面は円錐内周面４２とされ、外部部材４０の外周の円筒面はハウジング取付面３４とされる。外部部材４０に使用する鋼材は機械構造用炭素鋼、たとえばＳ３５Ｃ〜Ｓ５８Ｃとし、外部部材４０に形成の後に、熱処理はしない。 [Manufacturing method of outer ring]
Next, a method for manufacturing the outer ring 30 constituting the tapered roller bearing 10 will be described. The outer ring 30 is manufactured by creating the inner member 36 and the outer member 40, respectively, and integrating the resin layer 44 between the outer peripheral conical surface of the inner member 36 and the inner peripheral conical surface of the outer member 40. .
FIG. 3A shows an axial parallel sectional view of the internal member 36. The internal member 36 is formed by forming a steel material into a conical cylinder shape having a substantially constant thickness by forging, and adjusting the shape by cutting and polishing. An inner peripheral conical surface of the inner member 36 is an outer ring conical raceway surface 32, and an outer peripheral conical surface of the inner member 36 is a conical outer peripheral surface 38. The steel material used for the internal member 36 is JIS high carbon chrome bearing steel, for example, SUJ2, and is formed on the internal member 36 by forging, cutting, and polishing, followed by quenching and tempering heat treatment.
FIG. 3B shows an axial parallel sectional view of the external member 40. The external member 40 is formed by forging a steel material into a shape in which the inner periphery is a conical surface and the outer periphery is a cylindrical surface, and the shape is adjusted by cutting and polishing. An inner peripheral conical surface of the outer member 40 is a conical inner peripheral surface 42, and an outer peripheral cylindrical surface of the outer member 40 is a housing mounting surface 34. The steel material used for the external member 40 is carbon steel for mechanical structure, for example, S35C to S58C, and no heat treatment is performed after the external member 40 is formed.

内部部材３６の円錐外周面３８と外部部材４０の円錐内周面４２の母線の傾斜は同一であり、円錐外周面３８と円錐内周面４２を重ね合わせることができ、重ね合わせた状態から軸方向にずらすと、間隔が一定の円錐状の隙間が生じる構成とされている。そして、内部部材３６と外部部材４０の寸法精度と軸方向にずらす量を管理することで、内部部材３６の円錐外周面３８と外部部材４０の円錐内周面４２の間に形成される樹脂層４４の厚さを管理する。   The slopes of the generatrix of the cone outer peripheral surface 38 of the inner member 36 and the cone inner peripheral surface 42 of the outer member 40 are the same, and the cone outer peripheral surface 38 and the cone inner peripheral surface 42 can be overlapped. When shifted in the direction, a conical gap having a constant interval is formed. A resin layer formed between the conical outer peripheral surface 38 of the inner member 36 and the conical inner peripheral surface 42 of the outer member 40 by managing the dimensional accuracy of the inner member 36 and the outer member 40 and the amount shifted in the axial direction. Manage the thickness of 44.

内部部材３６と外部部材４０の間への樹脂層４４の形成は次の手順により行う。図３（ｃ）に示すように、まず、内部部材３６の円錐外周面３８の軸方向の一端から他端まで円錐外周面３８の母線に沿って、周方向の複数箇所に剥離剤を塗布して、離型層５０を設ける。塗布厚さは０．１〜０．５μｍとする。剥離剤としては、フッ素系潤滑剤（パーフルオロポリエステールまたはパーフルオロポリエーテルの末端の水酸基、イソシアネート基、アミド基、アミン、カルボキシル基、エステル基を形成したもの）を使用する。図３（ｃ）は剥離剤を塗布して円錐外周面３８に離型層５０を設けた内部部材３６を示す。
同様に、図３（ｄ）に示すように、外部部材４０の円錐内周面４２の軸方向の一端から他端まで円錐内周面４２の母線に沿って、周方向の複数箇所に剥離剤を塗布して離型層５０を設ける。図３（ｄ）は剥離剤を塗布して円錐内周面４２に離型層５０を設けた外部部材４０を示す。なお、剥離剤を塗布する周方向の間隔は、内部部材３６の円錐外周面３８に剥離剤を塗布する間隔と同じとする。 The resin layer 44 is formed between the internal member 36 and the external member 40 by the following procedure. As shown in FIG. 3C, first, a release agent is applied to a plurality of locations in the circumferential direction along the generatrix of the cone outer peripheral surface 38 from one end to the other end of the cone outer peripheral surface 38 of the internal member 36. Then, the release layer 50 is provided. The coating thickness is 0.1 to 0.5 μm. As the release agent, a fluorine-based lubricant (one having a terminal hydroxyl group, isocyanate group, amide group, amine, carboxyl group, or ester group of perfluoropolyester or perfluoropolyether formed) is used. FIG. 3C shows an internal member 36 in which a release agent is applied and a release layer 50 is provided on the outer circumferential surface 38 of the cone.
Similarly, as shown in FIG. 3D, a release agent is provided at a plurality of locations in the circumferential direction along the generatrix of the cone inner peripheral surface 42 from one end to the other end in the axial direction of the cone inner peripheral surface 42 of the external member 40. Is applied to provide the release layer 50. FIG. 3D shows the external member 40 in which a release agent is applied and a release layer 50 is provided on the inner circumferential surface 42 of the cone. The circumferential interval for applying the release agent is the same as the interval for applying the release agent to the conical outer peripheral surface 38 of the internal member 36.

次に、外部部材４０の円錐内周面４２の表面に例えばナイロン１１の樹脂粉末を静電塗装する。剥離剤がフッ素系なので、樹脂粉末は炭化水素系の樹脂としている。静電塗装の厚さは１０〜１００μｍが好ましく、実施例１では５０μｍとしている。なお、樹脂粉末を静電塗装するときは、外部部材４０の円錐内周面４２以外は表面をマスキングし、樹脂が付着しないようにしているがこれは必須ではない。
次に、静電塗装した外部部材４０を誘導加熱して、樹脂粉末を溶融させる。この際、剥離剤上の樹脂は円錐内周面４２の表面に固着されず、剥離剤のない所の樹脂は円錐内周面４２の表面に固着される。
次に、外部部材４０の円錐内周面４２の樹脂に接触するように内部部材３６を軸方向に移動させ当接させる。そして、再度、外部部材４０を誘導加熱し、樹脂を溶融させ、内部部材３６に固着して、内部部材３６と外部部材４０と樹脂層４４を一体化させて外輪３０とする。図３（ｅ）に外輪３０の軸平行断面図を示す。この時、内部部材３６と外部部材４０の軸方向位置の調整により樹脂層４４の厚さを制御することができる。樹脂層４４は５０μｍ程度の厚さであり、内部部材３６と外部部材４０の軸方向位置の調整による外輪３０の幅の変化は、樹脂層４４の厚さの調整量は２倍程度で済む。よって、樹脂層４４の厚さの調整による外輪３０の幅の変化は許容範囲である。 Next, for example, a resin powder of nylon 11 is electrostatically coated on the surface of the inner circumferential surface 42 of the outer member 40. Since the release agent is fluorine-based, the resin powder is a hydrocarbon-based resin. The thickness of the electrostatic coating is preferably 10 to 100 μm. In Example 1, the thickness is 50 μm. When the resin powder is electrostatically coated, the surfaces other than the conical inner peripheral surface 42 of the external member 40 are masked to prevent the resin from adhering, but this is not essential.
Next, the electrostatically coated external member 40 is induction-heated to melt the resin powder. At this time, the resin on the release agent is not fixed to the surface of the cone inner peripheral surface 42, and the resin without the release agent is fixed to the surface of the cone inner peripheral surface 42.
Next, the inner member 36 is moved in the axial direction so as to come into contact with the resin on the inner circumferential surface 42 of the outer member 40 and brought into contact therewith. Then, the external member 40 is again heated by induction, the resin is melted and fixed to the internal member 36, and the internal member 36, the external member 40, and the resin layer 44 are integrated to form the outer ring 30. FIG. 3E shows an axial parallel sectional view of the outer ring 30. At this time, the thickness of the resin layer 44 can be controlled by adjusting the axial positions of the internal member 36 and the external member 40. The resin layer 44 has a thickness of about 50 μm, and the change in the width of the outer ring 30 due to the adjustment of the axial positions of the inner member 36 and the outer member 40 can be about twice as much as the thickness of the resin layer 44. Therefore, the change in the width of the outer ring 30 due to the adjustment of the thickness of the resin layer 44 is within an allowable range.

樹脂層４４を内部部材３６に固着させる際、内部部材３６の円錐外周面３８も、剥離剤上の樹脂層４４は円錐外周面３８の表面に固着されず、剥離剤のない所の樹脂層４４は円錐外周面３８の表面に固着される。このとき、外部部材４０の円錐内周面４２の離型層５０の形成位置の周方向の中心が、内部部材３６の円錐外周面３８の離型層５０の形成位置の周方向の中心位置とずれるように当接させる。このことで、樹脂層４４と円錐外周面３８との非固着部４８の周方向位置と樹脂層４４と円錐内周面４２との固着部４６の周方向位置が重なるとともに、樹脂層４４と円錐内周面４２との非固着部４８の周方向位置と樹脂層４４と円錐外周面３８との固着部４６の周方向位置が重なる。   When the resin layer 44 is fixed to the internal member 36, the conical outer peripheral surface 38 of the internal member 36 is also not fixed to the surface of the conical outer peripheral surface 38, and the resin layer 44 where there is no release agent. Is fixed to the surface of the outer circumferential surface 38 of the cone. At this time, the center in the circumferential direction of the formation position of the release layer 50 on the inner circumferential surface 42 of the outer member 40 is the center position in the circumferential direction of the position of formation of the release layer 50 on the outer circumferential surface 38 of the inner member 36. Abut so as to shift. Accordingly, the circumferential position of the non-fixed portion 48 between the resin layer 44 and the cone outer peripheral surface 38 and the circumferential position of the fixed portion 46 between the resin layer 44 and the cone inner peripheral surface 42 are overlapped, and the resin layer 44 and the cone are overlapped. The circumferential position of the non-fixed portion 48 with the inner peripheral surface 42 and the circumferential position of the fixed portion 46 between the resin layer 44 and the conical outer peripheral surface 38 overlap.

ここで、内部部材３６に樹脂を固着するために外部部材４０を誘導加熱するのは、内部部材３６を誘導加熱すると、熱処理により硬化されている内部部材３６の焼きが抜けてしまうからである。もし、内部部材３６を誘導加熱するのであれば、誘導加熱で達する温度２００〜３００℃よりも高い温度で焼き戻ししておく。この場合は、内部部材３６に使用する鋼材は例えばＭ５０とする。   Here, the reason why the external member 40 is induction-heated in order to fix the resin to the internal member 36 is that when the internal member 36 is induction-heated, the internal member 36 that has been cured by the heat treatment is burned out. If the internal member 36 is induction-heated, it is tempered at a temperature higher than the temperature 200 to 300 ° C. reached by induction heating. In this case, the steel material used for the internal member 36 is, for example, M50.

［発明の効果］
実施例１によれば、外輪３０の内部部材３６の外周の円錐外周面３８と、外輪３０の外部部材４０の内周の円錐内周面４２の間に樹脂層４４を介在させている。そこで、内部部材３６と外部部材４０を軸方向に組み合わせた時に両円錐面の間に薄い隙間が形成される構成とすることで、両円錐面の間に介在させる樹脂層４４の厚さを薄く保つことができ、軸受の剛性を確保することができる。また、樹脂層４４は軌道輪である外輪３０に直接形成され、制振用の別部材を用いていないため、組付け性がよい。
そして、実施例１によれば、樹脂層４４は内部部材３６に固着する周方向位置では外部部材４０に非固着であるため、樹脂層４４の内部部材３６の側の表面が内部部材３６と共に振動する周方向位置では、樹脂層４４は外部部材４０に対して滑るので、振動が樹脂層４４から外部部材４０へ伝わりにくい。また、樹脂層４４は内部部材３６の側と外部部材４０の側の双方で固着部４６と非固着部４８を有するので、樹脂層の両側で振動エネルギーが熱に変換されて振動が吸収される。よって、制振性がさらに高められる。 [The invention's effect]
According to the first embodiment, the resin layer 44 is interposed between the outer circumferential cone surface 38 of the outer member 30 of the outer ring 30 and the inner cone surface 42 of the outer member 40 of the outer ring 30. Therefore, when the inner member 36 and the outer member 40 are combined in the axial direction, a thin gap is formed between the two conical surfaces, thereby reducing the thickness of the resin layer 44 interposed between the two conical surfaces. It is possible to maintain the rigidity of the bearing. Further, since the resin layer 44 is directly formed on the outer ring 30 which is a race, and does not use a separate member for vibration suppression, the assemblability is good.
According to the first embodiment, since the resin layer 44 is not fixed to the external member 40 at the circumferential position where the resin layer 44 is fixed to the internal member 36, the surface of the resin layer 44 on the internal member 36 side vibrates together with the internal member 36. At the circumferential position, the resin layer 44 slides with respect to the external member 40, so that vibration is not easily transmitted from the resin layer 44 to the external member 40. In addition, since the resin layer 44 has the fixed portion 46 and the non-fixed portion 48 on both the inner member 36 side and the outer member 40 side, vibration energy is converted into heat on both sides of the resin layer to absorb vibration. . Accordingly, the vibration damping property is further improved.

［変形例］
実施例１では、内部部材３６の円錐外周面３８と外部部材４０の円錐内周面４２の両方に剥離剤を塗布して非固着部を形成しているが、剥離剤を塗布して非固着部を形成するのは、内部部材３６の円錐外周面３８または外部部材４０の円錐内周面４２のいずれか一方のみとしても良い。
樹脂層４４が内部部材３６に対して周方向に固着部４６と非固着部４８を有する場合は、内部部材３６が振動すると樹脂層４４の固着部４６では表面が内部部材３６と共に振動するが、樹脂層４４の非固着部４８は内部部材３６に対して滑るため振動が伝わりにくい。そのため樹脂層４４の固着部４６と非固着部４８の境にせん断応力が加わり樹脂が粘弾性により変形して振動を吸収し熱が生ずる。よって、振動エネルギーが熱に変換されて振動が吸収されるため、制振性が高められる。また、樹脂層４４が外部部材４０に対して周方向に固着部４６と非固着部４８を有する場合は、内部部材３６の振動が樹脂層４４の外部部材４０の側に伝わった場合、固着部４６は外部部材４０により表面の振動が抑制され、非固着部４８は外部部材４０に対して滑って振動する。そのため、樹脂層４４の固着部４６と非固着部４８の境にせん断応力が加わり樹脂が粘弾性により変形して振動を吸収し熱が生ずる。よって、振動エネルギーが熱に変換されて振動が吸収されるため、制振性が高められる。 [Modification]
In Example 1, the release agent is applied to both the outer cone surface 38 of the inner member 36 and the inner cone surface 42 of the outer member 40 to form the non-fixed portion. The portion may be formed on only one of the conical outer peripheral surface 38 of the inner member 36 and the conical inner peripheral surface 42 of the outer member 40.
When the resin layer 44 has the fixed portion 46 and the non-fixed portion 48 in the circumferential direction with respect to the internal member 36, when the internal member 36 vibrates, the surface of the fixed portion 46 of the resin layer 44 vibrates together with the internal member 36. Since the non-fixed portion 48 of the resin layer 44 slides with respect to the internal member 36, vibration is not easily transmitted. Therefore, shear stress is applied to the boundary between the fixed portion 46 and the non-fixed portion 48 of the resin layer 44, and the resin is deformed by viscoelasticity to absorb vibration and generate heat. Therefore, vibration energy is converted into heat and vibration is absorbed, so that vibration damping is improved. Further, when the resin layer 44 has the fixed portion 46 and the non-fixed portion 48 in the circumferential direction with respect to the external member 40, when the vibration of the internal member 36 is transmitted to the external member 40 side of the resin layer 44, the fixed portion 46, the vibration of the surface is suppressed by the external member 40, and the non-fixed portion 48 slides and vibrates with respect to the external member 40. Therefore, a shear stress is applied to the boundary between the fixed portion 46 and the non-fixed portion 48 of the resin layer 44, and the resin is deformed by viscoelasticity to absorb vibration and generate heat. Therefore, vibration energy is converted into heat and vibration is absorbed, so that vibration damping is improved.

実施例１では、樹脂にナイロン１１を用いてるが樹脂はナイロン１１に限られず、ポリエステル、ポリエチレン、ポロプロピレン、ポリアミド１２、４６、６６、６、９Ｔ、ポリフェニルサルファイド、ポリイミド等の熱可塑性樹脂を用いても良い。
また、樹脂としてポリウレタン、ポリ尿素等の熱硬化性樹脂を用いることもできる。熱硬化性樹脂を用いるときは、内部部材３６と外部部材４０で樹脂を挟み、所定の位置に固定した後、焼き戻し温度以下の温度で放置して硬化させる。 In Example 1, nylon 11 is used as the resin, but the resin is not limited to nylon 11, and a thermoplastic resin such as polyester, polyethylene, polypropylene, polyamide 12, 46, 66, 6, 9T, polyphenyl sulfide, polyimide, or the like is used. It may be used.
Moreover, thermosetting resins, such as polyurethane and polyurea, can also be used as the resin. When a thermosetting resin is used, the resin is sandwiched between the internal member 36 and the external member 40, fixed at a predetermined position, and then allowed to stand at a temperature equal to or lower than the tempering temperature to be cured.

その他、本発明に係る円錐ころ軸受はその発明の思想の範囲で、各種の形態で実施できるものである。   In addition, the tapered roller bearing according to the present invention can be implemented in various forms within the scope of the idea of the invention.

１０ 円錐ころ軸受
１２ 軸体
１４ 内輪
１６ 内輪円錐軌道面
１８ 円錐ころ
２０ ハウジング
３０ 外輪
３２ 外輪円錐軌道面
３４ ハウジング取付面
３６ 内部部材
３８ 円錐外周面
４０ 外部部材
４２ 円錐内周面
４４ 樹脂層
４６ 固着部
４８ 非固着部
５０ 離型層

DESCRIPTION OF SYMBOLS 10 Tapered roller bearing 12 Shaft body 14 Inner ring 16 Inner ring conical track surface 18 Conical roller 20 Housing 30 Outer ring 32 Outer ring conical track surface 34 Housing mounting surface 36 Internal member 38 Conical outer peripheral surface 40 External member 42 Conical inner peripheral surface 44 Resin layer 46 adhering Part 48 non-adhering part 50 release layer

Claims (2)

外周に内輪円錐軌道面を有する内輪と、内周に外輪円錐軌道面を有する外輪と、前記内輪円錐軌道面と前記外輪円錐軌道面との間に転動自在に配設される円錐ころとを備える円錐ころ軸受において、
前記外輪は、内周に前記外輪円錐軌道面を有するとともに、外周に円錐外周面を有する内部部材と、内周に円錐内周面を有するとともに、外周にハウジング取付面を有する外部部材と、前記円錐外周面と前記円錐内周面との間に介在する樹脂層とを備え、
前記樹脂層は、前記内部部材の円錐外周面および前記外部部材の円錐内周面の少なくとも一方に対して、周方向に固着部と非固着部とを有することを特徴とする円錐ころ軸受。 An inner ring having an inner ring conical raceway surface on the outer periphery, an outer ring having an outer ring conical raceway surface on the inner periphery, and a tapered roller disposed rotatably between the inner ring conical raceway surface and the outer ring conical raceway surface. In the tapered roller bearing provided,
The outer ring has the outer ring conical raceway surface on the inner periphery, an inner member having a conical outer periphery surface on the outer periphery, an outer member having a cone inner peripheral surface on the inner periphery and a housing mounting surface on the outer periphery, A resin layer interposed between the outer circumferential surface of the cone and the inner circumferential surface of the cone,
The tapered roller bearing, wherein the resin layer has a fixed portion and a non-fixed portion in a circumferential direction with respect to at least one of a conical outer peripheral surface of the inner member and a conical inner peripheral surface of the outer member. 請求項１に記載の円錐ころ軸受けであって、
前記樹脂層は、前記内部部材の円錐外周面および前記外部部材の円錐内周面の両方に対して周方向に固着部と、非固着部とを有し、
前記樹脂層と前記内部部材の円錐外周面との非固着部の周方向位置と該樹脂層と前記外部部材の円錐内周面との固着部の周方向位置が重なるとともに、前記樹脂層と前記外部部材の円錐内周面との非固着部の周方向位置と該樹脂層と前記内部部材の円錐外周面との固着部の周方向位置が重なることを特徴とする円錐ころ軸受。
The tapered roller bearing according to claim 1,
The resin layer has an adhering portion and a non-adhering portion in the circumferential direction with respect to both the conical outer peripheral surface of the inner member and the conical inner peripheral surface of the outer member,
The circumferential position of the non-fixed portion between the resin layer and the outer peripheral surface of the cone of the inner member overlaps the circumferential position of the fixed portion of the resin layer and the inner peripheral surface of the cone of the outer member, and the resin layer and the A tapered roller bearing characterized in that a circumferential position of a non-fixed portion of the outer member with respect to the inner circumferential surface of the cone overlaps with a circumferential position of the fixed portion of the resin layer and the outer circumferential surface of the cone of the inner member.
JP2009177346A 2009-07-30 2009-07-30 Tapered roller bearing Pending JP2011033064A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20200096041A1 (en) * 2018-09-21 2020-03-26 Pratt & Whitney Canada Corp. Bearing housing with damping arrangement
CN112567146A (en) * 2018-08-08 2021-03-26 Ntn株式会社 Resin film-attached cage for rolling bearing

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112567146A (en) * 2018-08-08 2021-03-26 Ntn株式会社 Resin film-attached cage for rolling bearing
US20200096041A1 (en) * 2018-09-21 2020-03-26 Pratt & Whitney Canada Corp. Bearing housing with damping arrangement
US10767690B2 (en) * 2018-09-21 2020-09-08 Pratt & Whitney Canada Corp. Bearing housing with damping arrangement

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