JP2006226487A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP2006226487A
JP2006226487A JP2005043777A JP2005043777A JP2006226487A JP 2006226487 A JP2006226487 A JP 2006226487A JP 2005043777 A JP2005043777 A JP 2005043777A JP 2005043777 A JP2005043777 A JP 2005043777A JP 2006226487 A JP2006226487 A JP 2006226487A
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Prior art keywords
tapered roller
contact
contact surface
protrusion
flange
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JP2005043777A
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Japanese (ja)
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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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Priority to JP2005043777A priority Critical patent/JP2006226487A/en
Publication of JP2006226487A publication Critical patent/JP2006226487A/en
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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
    • 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
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • 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
    • F16C19/225—Details of the ribs supporting the end of the rollers
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing whose pre-load given to an assembled object when assembled is easily adjustable. <P>SOLUTION: The tapered roller bearing used in oil lubrication comprises an inner ring 1, an outer ring, and a rolling element composed of a tapered roller 3 rotatably provided between the inner and outer rings. The inner ring 1 has a collar 4 formed with a contact face 5 in contact with the large end face 7 of the tapered roller 3 for guiding the tapered roller 3 to roll. A fine protruded portion 6 is formed on the contact face 5 of the collar portion 4. The protruded portion 6 suppresses the formation of an oil film between the contact face 5 of the collar 4 and the large end face 7 of the tapered roller 3 at the beginning of usage and then permits the formation of the oil film between the contact face 5 of the collar 4 and the large end face 7 of the tapered roller 3, when worn. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は、オイル潤滑下で使用される円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing used under oil lubrication.

従来より知られている円錐ころ軸受は、内輪と、外輪と、これら内外輪間に転動自在に設けられた転動体としての円錐ころとを備えており、例えば内輪に、円錐ころの端面と接触して当該円錐ころの転走を案内する接触面を有する鍔部が形成されている。つまり、鍔部の接触面に、ころの端面が滑り接触（摺動）するよう構成されている。
この滑り接触による抵抗を小さくさせている低トルク軸受では、鍔部の接触面及びころの端面を表面粗さが小さくなるよう平滑にしている。さらに、特許文献１においては、低トルク化のために鍔部の接触面ところの端面との間に厚い油膜を形成させるよう、鍔部の接触面に微小凹部（深さ０．１８μｍ〜０．２μｍ）を形成している。 Conventionally known tapered roller bearings include an inner ring, an outer ring, and a tapered roller as a rolling element provided between the inner and outer rings so as to be able to roll. A flange having a contact surface that contacts and guides the rolling of the tapered roller is formed. That is, the roller end surface is configured to be in sliding contact (sliding) with the contact surface of the collar portion.
In the low torque bearing in which the resistance due to the sliding contact is reduced, the contact surface of the flange portion and the end surface of the roller are smoothed so that the surface roughness is reduced. Further, in Patent Document 1, a minute recess (depth 0.18 μm to 0. 0 mm) is formed on the contact surface of the heel so that a thick oil film is formed between the contact surface of the heel and the end surface in order to reduce torque. 2 μm).

また、例えば自動車のデファレンシャルやトランスアクスルなどの車両用ピニオン軸支持装置や、トランスミッションなどに使用される円錐ころ軸受においては、組み付けの際に軸受に予圧が与えられており、この予圧の管理は、低速回転でのトルク（以下、組み付けトルクという）によって管理がなされている。この組み付けトルクのばらつきが大きいと、過大予圧の場合は早期焼き付き、過小予圧の場合は剛性低下などの不具合に発展する。そこで、この組み付けトルクのばらつきを小さくさせるために、特許文献２、特許文献３のように、ころの端面、鍔部の接触面の粗さなどを所定の値に設定したものがある。例えば、ころの端面、鍔部の接触面の粗さは、大きくても１μｍ（Ｒｚ）程度、または通常それ以下とされており、０．１μｍ以下で設定されているものもある。つまり、従来のこれらにおける表面粗さは、１／１０μｍ〜１／１００μｍの小さいレベルで設定されている。   Further, for example, in a pinion shaft support device for a vehicle such as an automobile differential or a transaxle, or a tapered roller bearing used for a transmission or the like, a preload is applied to the bearing at the time of assembly. Management is performed by torque at low speed (hereinafter referred to as assembly torque). If the variation in the assembly torque is large, it will lead to problems such as early seizure in the case of an excessive preload, and a decrease in rigidity in the case of an excessive preload. Therefore, in order to reduce the variation in the assembly torque, there are some in which the roughness of the roller end face, the contact surface of the flange portion, etc. is set to a predetermined value as in Patent Document 2 and Patent Document 3. For example, the roughness of the roller end face and the contact surface of the flange is at most about 1 μm (Rz), or less than that, and is usually set to 0.1 μm or less. That is, the conventional surface roughness is set at a small level of 1/10 μm to 1/100 μm.

特開平６−２４１２３５号公報JP-A-6-241235 特開２００１−１０７９５２号公報JP 2001-107952 A 特開２００２−２２１２２３号公報JP 2002-221223 A

しかし、特許文献１に記載されている円錐ころ軸受は、鍔部ところとの間において油膜を厚い状態に維持させて低トルク化を図るのみであり、組付けトルクが安定しないため、組み付けトルクを基準とする予圧調整作業は困難である。また特許文献２、特許文献３においては、組み付けトルクを安定させて（一定とさせて）、組み付けトルクを基準とした予圧の調整作業を容易にさせる一方で、定常使用時におけるトルクが大きくなる。   However, the tapered roller bearing described in Patent Document 1 only reduces the torque by maintaining the oil film in a thick state between the flange portions and the assembly torque is not stable. The standard preload adjustment work is difficult. In Patent Document 2 and Patent Document 3, the assembly torque is stabilized (constant), and the preload adjustment operation based on the assembly torque is facilitated, while the torque during steady use increases.

そこでこの発明は、前記問題点に鑑みてなされたものであり、組み付け対象部に組み付ける際に与える予圧の調整が簡単に行え、また、予圧のばらつきを抑え、予圧管理の精度を向上させることができるとともに、定常使用時はトルクの小さい円錐ころ軸受を提供することを目的とする。   Therefore, the present invention has been made in view of the above-described problems, and can easily adjust the preload applied when assembling to the assembly target portion, and can suppress variations in preload and improve the accuracy of preload management. An object of the present invention is to provide a tapered roller bearing with a small torque during normal use.

前記目的を達成するためのこの発明の円錐ころ軸受は、内輪と、外輪と、これら内外輪間に転動自在に設けられた円錐ころとを備え、前記内輪と外輪の少なくとも一方に前記円錐ころの端面と接触して当該円錐ころの転走を案内する接触面を有する鍔部が形成されており、油潤滑下で使用される円錐ころ軸受において、前記鍔部の接触面とこの接触面と接触する前記円錐ころの端面の少なくとも一方に、使用初期では当該鍔部の接触面と当該円錐ころの端面との間の油膜の形成を抑制し、その後摩耗して当該鍔部の接触面と当該円錐ころの端面との間において油膜の形成を可能とさせる微細突起部が形成されていることを特徴としている。
このような構成の円錐ころ軸受によれば、軸受を組み付け対象部へ組み付け時（回転を開始させた使用初期）には、前記微細突起部によって鍔部の接触面と円錐ころの端面との間において油膜の形成が抑制されて、当該微細突起部を、対面する相手側の面に直接的に接触（押圧）させることができる。これにより、鍔部の接触面と円錐ころの端面との間において油膜の形成を抑制できるため、トルクが安定して、トルク管理による予圧調整が容易になる。そして、使用（回転）が開始されるとやがて突起部が摩耗（摩滅）して、円錐ころの端面と鍔部の接触面との間に油膜を形成させることができるため、定常使用時のトルクを小さくできる。
これにより、軸受部に予圧を与えかつ予圧の調整をすることができるだけの必要な大きさの組み付けトルクを確保しつつ、軸受の使用が開始されると低トルク化が可能となる。 In order to achieve the above object, a tapered roller bearing according to the present invention comprises an inner ring, an outer ring, and a tapered roller provided between the inner and outer rings so as to be capable of rolling, and the tapered roller is provided on at least one of the inner ring and the outer ring. A tapered portion having a contact surface that contacts the end surface of the tapered roller and guides the rolling of the tapered roller is formed. In the tapered roller bearing used under oil lubrication, the contact surface of the flange portion and the contact surface At least one of the end surfaces of the tapered rollers in contact with each other suppresses formation of an oil film between the contact surface of the flange portion and the end surface of the tapered roller in the initial stage of use, and then wears to contact the contact surface of the flange portion with the contact surface of the flange portion. It is characterized in that a fine projection is formed between the end faces of the tapered rollers to enable formation of an oil film.
According to the tapered roller bearing having such a configuration, when the bearing is assembled to the assembly target portion (in the initial stage of use when rotation is started), the fine protrusions cause a gap between the contact surface of the collar portion and the end surface of the tapered roller. In this case, the formation of an oil film is suppressed, and the fine protrusion can be directly brought into contact (pressed) with the opposing surface. Thereby, since formation of an oil film can be suppressed between the contact surface of the flange and the end surface of the tapered roller, the torque is stabilized and preload adjustment by torque management is facilitated. Then, when the use (rotation) is started, the protrusions will eventually wear out (wear), and an oil film can be formed between the end surface of the tapered roller and the contact surface of the flange portion. Can be reduced.
As a result, it is possible to reduce the torque when the use of the bearing is started, while securing an assembly torque of a necessary magnitude that can preload the bearing portion and adjust the preload.

また、内輪と、外輪と、これら内外輪間に転動自在に設けられた円錐ころと、を備え、前記内輪と外輪の少なくとも一方に前記円錐ころの端面と接触して当該円錐ころの転走を案内する接触面を有する鍔部が形成されている円錐ころ軸受において、前記鍔部の接触面とこの接触面と接触する前記円錐ころの端面の少なくとも一方に、高さ寸法が２μｍ〜１０μｍの微細突起部が形成されていることを特徴としている。
これによれば、軸受を組み付け対象部への組み付ける際、突起部により円錐ころの端面と鍔部の接触面との間の油膜の形成を抑制して、突起部を対面する相手側の面に直接的に接触させることができる。従って、回転トルクが安定して、トルク管理による予圧調整が容易になる。さらに、使用（回転）が開始されると早期に突起部を摩耗させることができ、鍔部の接触面ところの端面との間に油膜を形成させることができ、定常使用時において、低トルク化が実現できる。 And an inner ring, an outer ring, and a tapered roller provided between the inner and outer rings so as to be able to roll, and at least one of the inner ring and the outer ring is brought into contact with an end surface of the tapered roller to roll the tapered roller. In a tapered roller bearing in which a flange having a contact surface for guiding the contact is formed, at least one of the contact surface of the flange and the end surface of the tapered roller in contact with the contact surface has a height dimension of 2 μm to 10 μm. It is characterized in that fine protrusions are formed.
According to this, when the bearing is assembled to the assembly target portion, the protrusion suppresses the formation of an oil film between the end surface of the tapered roller and the contact surface of the flange portion, so that the protrusion faces the mating surface. Direct contact can be made. Accordingly, the rotational torque is stabilized and preload adjustment by torque management is facilitated. In addition, when the use (rotation) is started, the protrusions can be worn at an early stage, and an oil film can be formed between the end surface of the contact part of the collar part, and the torque can be reduced during normal use. Can be realized.

また、前記突起部は、前記鍔部の前記接触面に周方向に沿って形成されているのが好ましい。これによれば、突起部と鍔部の円環状の接触部が、周方向の全域にわたり均一になるため、トルクが安定し、トルク管理による予圧調整をより正確に行うことができる。また、突起部の摩耗後の接触も安定するため、低トルク時のトルクも安定する。   Moreover, it is preferable that the said projection part is formed in the said contact surface of the said collar part along the circumferential direction. According to this, since the annular contact portion between the protrusion and the collar becomes uniform over the entire circumferential direction, the torque is stabilized, and the preload adjustment by torque management can be performed more accurately. In addition, since the contact of the protrusion after wear is stabilized, the torque at the time of low torque is also stabilized.

本発明の円錐ころ軸受によれば、軸受に予圧を与えかつ調整することができるだけの必要な大きさの組み付けトルクを確保させることができる。従って、組み付けトルクを基準とした予圧を付与する作業が簡単となるとともに、定常使用時のトルクを小さくできる。   According to the tapered roller bearing of the present invention, it is possible to ensure an assembling torque having a necessary magnitude that allows the bearing to be preloaded and adjusted. Therefore, the operation of applying the preload based on the assembly torque is simplified and the torque during steady use can be reduced.

以下、この発明の実施の形態について図面を参照しながら説明する。
図１はこの発明の実施の一形態に係る円錐ころ軸受を示す縦断面図である。この円錐ころ軸受は、内輪１と、外輪２と、内輪１と外輪２との間に転動自在に設けられた転動体とを備えている。転動体は複数個の円錐ころ３からなる。そして、この軸受は、内輪１と円錐ころ３、外輪２と円錐ころ３との間に潤滑剤（オイル）を介在させて回転の際の摩擦トルクを小さくさせることのできるオイル潤滑式のものである。円錐ころ３は保持器１０により保持されている。 Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a tapered roller bearing according to an embodiment of the present invention. The tapered roller bearing includes an inner ring 1, an outer ring 2, and rolling elements provided between the inner ring 1 and the outer ring 2 so as to be able to roll. The rolling element is composed of a plurality of tapered rollers 3. The bearing is of an oil lubrication type in which a lubricant (oil) is interposed between the inner ring 1 and the tapered roller 3 and between the outer ring 2 and the tapered roller 3 to reduce the friction torque during rotation. is there. The tapered roller 3 is held by a cage 10.

内輪１は、その外周面にテーパ状の軌道面１１が形成されており、軌道面１１の軸方向の両端部に鍔部４，１４が形成されている。そして、円錐ころ３の直径が大きい側である大端面７が大径側の鍔部４の内側の接触面５に接触して、円錐ころ３の転走が案内されている。具体的には内輪１の外周側部において、円錐ころ３の外周面と接触するテーパ状の軌道面１１と、軌道面１１の軸方向一端部側から径方向外方に突出する大径の鍔部４の接触面５と、軌道面１１の他端部側から径方向外方に突出する小径の鍔部１４の内側面１５とにより周溝が形成されており、大径の鍔部４の接触面５が円錐ころ３の大端面７の周縁部に接触している。鍔部４は内輪１に全周にわたって連続して形成されており、鍔部４は環状となる。
外輪２は内輪１の径方向外方に設けられており、その内周面に円錐ころ３の外周面と接触するテーパ状の軌道面１２が形成されている。 The inner ring 1 has a tapered raceway surface 11 formed on the outer peripheral surface thereof, and flanges 4 and 14 are formed at both ends of the raceway surface 11 in the axial direction. And the large end surface 7 which is the side with the large diameter of the tapered roller 3 contacts the contact surface 5 inside the collar part 4 of the large diameter side, and the rolling of the tapered roller 3 is guided. Specifically, at the outer peripheral side portion of the inner ring 1, a tapered raceway surface 11 that contacts the outer peripheral surface of the tapered roller 3, and a large-diameter flange that protrudes radially outward from one axial end side of the raceway surface 11. A circumferential groove is formed by the contact surface 5 of the portion 4 and the inner side surface 15 of the small-diameter flange 14 protruding radially outward from the other end portion side of the raceway surface 11. The contact surface 5 is in contact with the peripheral edge portion of the large end surface 7 of the tapered roller 3. The collar part 4 is continuously formed on the inner ring 1 over the entire circumference, and the collar part 4 is annular.
The outer ring 2 is provided radially outward of the inner ring 1, and a tapered raceway surface 12 that contacts the outer peripheral surface of the tapered roller 3 is formed on the inner peripheral surface thereof.

そして、図２は図１のＡ部を示す拡大断面図であり、図３は内輪１の鍔部４の接触面５を軸心方向から見た断面図である。図２において円錐ころ３を二点鎖線で示している。これらに示すように、鍔部４の接触面５に微細の突起部６が形成されている。
接触面５及び円錐ころ３の大端面７は研摩加工されて極微細な凹凸による粗さを有する滑らかな面とされている。そして、この突起部６は、このように滑らかな面とされている接触面５から突出するよう形成されている。つまり、この突起部６は、平滑面を得るために研摩加工を行っても必然的に生じてしまう粗さによる凸部ではなく、平滑面よりも意図的に一段高く形成したものである。言い換えると、接触面５に所定の高さの段差部を設け、この段差部を突起部６としている。 2 is an enlarged cross-sectional view showing a portion A of FIG. 1, and FIG. 3 is a cross-sectional view of the contact surface 5 of the flange portion 4 of the inner ring 1 as viewed from the axial direction. In FIG. 2, the tapered roller 3 is indicated by a two-dot chain line. As shown in these figures, a fine protrusion 6 is formed on the contact surface 5 of the flange 4.
The contact surface 5 and the large end surface 7 of the tapered roller 3 are polished to be smooth surfaces having roughness due to extremely fine irregularities. And this projection part 6 is formed so that it may protrude from the contact surface 5 made into such a smooth surface. That is, the protrusion 6 is not a convex portion due to roughness that is inevitably generated even if polishing is performed to obtain a smooth surface, but is intentionally formed one step higher than the smooth surface. In other words, a step portion having a predetermined height is provided on the contact surface 5, and the step portion is used as the protrusion 6.

そして、以上のように構成された円錐ころ軸受を組み付け対象部位（図示せず）に組み付ける際、この軸受には内輪１が軸方向に押圧されて予圧が付与される。この予圧は、組み付けの際に軸受に低速回転でのトルクが与えられることによって、その大小の管理がなされている。つまり、低速回転による組み付けトルクを基準として予圧の調整作業を行っている。
従って、相互に接触する円錐ころ３の大端面７と鍔部４の接触面５との間においては、使用状態（機器の運転状態）では低トルク化のために油膜を形成させて摩擦抵抗を低下させる必要があるが、予圧を調整して組み付ける際は、これらの間にある程度の大きさの摩擦抵抗が必要となる。 And when the tapered roller bearing comprised as mentioned above is assembled | attached to an assembly | attachment object site | part (not shown), the inner ring | wheel 1 is pressed to an axial direction to this bearing, and a preload is provided. The preload is controlled in magnitude by applying a torque at low speed rotation to the bearing during assembly. That is, the preload adjustment work is performed based on the assembly torque due to the low-speed rotation.
Accordingly, an oil film is formed between the large end surface 7 of the tapered roller 3 and the contact surface 5 of the flange portion 4 that are in contact with each other in order to reduce the torque in a use state (operating state of the device), thereby reducing frictional resistance. Although it is necessary to lower it, when the preload is adjusted and assembled, a certain amount of frictional resistance is required between them.

そこで、鍔部４の接触面５に前記突起部６が形成されており、軸受を組み付け対象部へ組み付けて回転を開始させた使用初期において、この突起部６は円錐ころ３の大端面７の周縁部と鍔部４の接触面５との間の油膜の形成を抑制している。そして、この突起部６の頂部を（油膜を介さずに）直接的に相手側である円錐ころ３の大端面７に接触させて、相互間において必要な摩擦抵抗を確保させ、組み付けトルクを基準として所定の予圧を軸受に付与し、組み付けが完了する。
一方、所定の予圧を持って組み付けられた軸受を備えた機器が動作し、軸受が回転すると、つまり使用初期の後において、突起部６は微細なものであるために早期に（徐々に）摩耗し、円錐ころ３の大端面７と鍔部４の接触面５との間において、比較的広い面積での接触となり、油膜の形成が可能となる。 Therefore, the protrusion 6 is formed on the contact surface 5 of the flange 4, and this protrusion 6 is formed on the large end surface 7 of the tapered roller 3 in the initial stage of use when the bearing is assembled to the assembly target portion and rotation is started. The formation of an oil film between the peripheral edge portion and the contact surface 5 of the flange portion 4 is suppressed. And the top part of this projection part 6 is made to contact the large end surface 7 of the tapered roller 3 which is the other party directly (without going through an oil film), ensuring a necessary frictional resistance between them, and assembling torque as a reference A predetermined preload is applied to the bearing to complete the assembly.
On the other hand, when a device having a bearing assembled with a predetermined preload operates and the bearing rotates, that is, after the initial stage of use, the protrusion 6 is fine, and thus wears out early (gradually). However, the contact between the large end surface 7 of the tapered roller 3 and the contact surface 5 of the flange portion 4 is a contact in a relatively wide area, and an oil film can be formed.

以上の実施形態において、鍔部４の接触面５に形成した突起部６により、軸受を組み付け対象部に組み付ける際には、突起部６の頂部を円錐ころ３の大端面７に直接的に接触させ、円錐ころ３の大端面７と鍔部４の接触面５との間における摩擦抵抗を小さくさせる油膜の形成を抑制することができる。そして、回転が開始されるとやがて突起部６が摩耗して円錐ころ３の大端面７と鍔部４の接触面５との間の全面にわたって油膜を形成させることができる。
従って、軸受を予圧調整して組み付け対象部へ組み付ける際、組み付けトルクを必要なだけ大きくさせることができ、トルクの大小の差を明確にできる。これにより、組み付けトルクを基準とした予圧の調整作業が容易となる。そして、軸受の使用が開始されれば低トルク化が実現できる。また、軸受の組み付けの際の予圧のばらつきを抑えることができ、予圧管理の精度を向上させることができる。 In the above embodiment, when the bearing is assembled to the assembly target portion by the projection 6 formed on the contact surface 5 of the flange portion 4, the top of the projection 6 directly contacts the large end surface 7 of the tapered roller 3. Thus, the formation of an oil film that reduces the frictional resistance between the large end surface 7 of the tapered roller 3 and the contact surface 5 of the flange 4 can be suppressed. Then, when the rotation is started, the protrusion 6 is eventually worn and an oil film can be formed over the entire surface between the large end surface 7 of the tapered roller 3 and the contact surface 5 of the flange portion 4.
Therefore, when the bearing is preloaded and assembled to the assembly target portion, the assembly torque can be increased as much as necessary, and the difference in torque can be clarified. Thereby, the preload adjustment work based on the assembly torque is facilitated. And if use of a bearing is started, torque reduction is realizable. In addition, variations in preload during assembly of the bearing can be suppressed, and the accuracy of preload management can be improved.

そして、この突起部６は微小な高さ、微小な幅寸法、つまり、頂部において微小な接触面積を持つよう形成されている。具体的には、突起部６の高さ寸法ｈは２μｍ〜１０μｍとされているのが好ましい。
突起部６の高さ寸法ｈが２μｍ未満の場合、高さが低すぎて組み付け対象部への組み付けの際においても油膜が形成されてしまうおそれがあり、必要な大きさの組み付けトルクを確保させることができないおそれがある。また、高さ寸法ｈが１０μｍを超えると、高さが高すぎて、使用初期の後において、摩擦抵抗を小さくさせる油膜を形成させるだけの突起部６の摩滅が進まず、長期にわたり回転トルクが大きくなってしまう。 And this projection part 6 is formed so that it may have a minute height, a minute width dimension, that is, a minute contact area at the top. Specifically, the height h of the protrusion 6 is preferably 2 μm to 10 μm.
If the height dimension h of the protrusion 6 is less than 2 μm, the height is too low and an oil film may be formed even when assembled to the assembly target part, and assembling torque of a necessary size is ensured. There is a risk that it will not be possible. Further, if the height dimension h exceeds 10 μm, the height is too high, and after the initial use, the wear of the protrusion 6 that only forms an oil film that reduces the frictional resistance does not progress, and the rotational torque does not increase over a long period of time. It gets bigger.

さらに、突起部６の幅寸法ｗは、円錐ころ軸受全体の大きさにも左右されるが、突起部６の幅寸法ｗを１００μｍ〜２００μｍとするのが好ましい。
突起部６の幅寸法ｗが１００μｍ未満であると、ころ端面との接触により押しつぶされるか、組み付け完了前に摩耗が進み、組み付け対象部への組み付けの際においても油膜が形成されてしまうおそれがある。また、幅寸法ｗが２００μｍを超えると、使用（回転）開始後も突起部の摩耗が進み難くなり、突起部６と対面する相手側の面との間において、長期間にわたり摩擦抵抗が大きくなって回転トルクが大きくなったり、その部分において焼き付きが生じるおそれがある。なお、図２の幅寸法ｗは突起部６の頂部（当接面）の寸法を示している。
なお、突起部６の数は、前記摩耗が適度に進行するよう、接触条件や軸受寸法などに応じて適切に設定すればよい。 Furthermore, although the width dimension w of the protrusion 6 depends on the overall size of the tapered roller bearing, the width dimension w of the protrusion 6 is preferably 100 μm to 200 μm.
If the width dimension w of the protrusion 6 is less than 100 μm, it may be crushed by contact with the roller end face, or wear may progress before the assembly is completed, and an oil film may be formed even when assembled to the assembly target part. is there. Further, if the width dimension w exceeds 200 μm, it is difficult for the protrusions to progress even after the start of use (rotation), and the frictional resistance increases between the protrusions 6 and the opposing surface facing the protrusions over a long period of time. As a result, the rotational torque may increase or seizure may occur at that portion. In addition, the width dimension w of FIG. 2 has shown the dimension of the top part (contact surface) of the projection part 6. FIG.
In addition, what is necessary is just to set the number of the projection parts 6 suitably according to a contact condition, a bearing dimension, etc. so that the said abrasion progresses moderately.

また、図３に示すように、突起部６は、鍔部４の接触面５上であってその周方向に沿って形成されている。つまり、突起部６は内輪１（鍔部４）の軸心側を中心とする仮想環状線ｅに沿って形成されている。この場合、突起部６の前記幅寸法ｗは、径方向の幅寸法となる。なお、突起部６は、周方向の全周にわたって連続して形成させるのが好ましい。
これによれば、突起部６と鍔部４の円環状の接触部が、周方向の全域にわたり均一になるため、トルクが安定し、トルク管理による予圧調整をより正確に行うことができる。また、突起部６の摩耗後の接触も安定するため、低トルク時のトルクも安定する。
また、旋削により接触面５を形成する際に同時に突起部６を形成することができ、接触面５を砥石により研摩する際に段付き状の砥石により同時に突起部６を研摩することができる。なお、図示しないが突起部６を周方向に沿って間欠状に形成してもよい。
このように突起部６を周方向に沿って形成することにより、円錐ころ軸受の使用が開始され、突起部６が摩耗し、鍔部４の接触面５と円錐ころ３の大端面７との間の全周にわたって形成が開始された油膜を途切れさせることがなく、運転開始後の早い時期に、鍔部４の接触面５全面に油膜を形成させることができる。 Moreover, as shown in FIG. 3, the projection part 6 is formed on the contact surface 5 of the collar part 4 along the circumferential direction. That is, the protrusion 6 is formed along a virtual annular line e centering on the axial center side of the inner ring 1 (the flange 4). In this case, the width dimension w of the protrusion 6 is a radial width dimension. The protrusion 6 is preferably formed continuously over the entire circumference in the circumferential direction.
According to this, since the annular contact portion of the protrusion 6 and the flange portion 4 is uniform over the entire circumferential direction, the torque is stabilized and the preload adjustment by torque management can be performed more accurately. Moreover, since the contact after the protrusion 6 is worn is stabilized, the torque at the time of low torque is also stabilized.
Further, when the contact surface 5 is formed by turning, the protrusion 6 can be formed at the same time, and when the contact surface 5 is polished with a grindstone, the protrusion 6 can be simultaneously polished with a stepped grindstone. Although not shown, the protrusions 6 may be formed intermittently along the circumferential direction.
By forming the protrusion 6 along the circumferential direction in this way, the use of the tapered roller bearing is started, the protrusion 6 is worn, and the contact surface 5 of the flange 4 and the large end surface 7 of the tapered roller 3 The oil film that has been formed over the entire circumference is not interrupted, and an oil film can be formed on the entire contact surface 5 of the flange 4 at an early time after the start of operation.

さらに図２に示すように、突起部６は、鍔部４の環状の接触面５において径方向中間位置よりも内方側の位置に形成されている。さらに説明すると、突起部６は、鍔部４の接触面５と軌道面１１との間の隅部に形成されている凹溝部１６の近傍に（突起部６の内周面が凹溝部１６の内周面と連続するよう）設けられている。なお、凹溝部１６は円錐ころ３と接触しない部分であり、環状の空間部が形成されている。これにより、円錐ころ３の回転により生じる突起部６の摩耗粉を、この凹溝部１６に収容させることができ、摩耗粉が軸受に悪影響を与えるのを防ぐことができる。   Further, as shown in FIG. 2, the protrusion 6 is formed on the annular contact surface 5 of the flange portion 4 at a position on the inner side of the radial intermediate position. More specifically, the protrusion 6 is located near the groove 16 formed at the corner between the contact surface 5 of the flange 4 and the raceway surface 11 (the inner peripheral surface of the protrusion 6 is the groove 16). To be continuous with the inner peripheral surface). In addition, the concave groove part 16 is a part which does not contact the tapered roller 3, and the cyclic | annular space part is formed. Thereby, the abrasion powder of the protrusion part 6 which arises by rotation of the tapered roller 3 can be accommodated in this recessed groove part 16, and it can prevent that an abrasion powder has a bad influence on a bearing.

また、図４は本発明の円錐ころ軸受の他の実施の形態の要部を示す拡大断面図であり、この軸受は、突起部６が円錐ころ３の大端面７側に形成されている。つまり、突起部６は円錐ころ３の大端面７のうち鍔部４の接触面５と接触する部分に形成されている。さらに説明すると、突起部６は、円錐ころ３の軸心を中心として円錐ころ３の大端面７の周縁部に周状に形成されており、大端面７の周縁部の外径側寄りに設けられている。図４において、内輪１を二点鎖線で示している。   FIG. 4 is an enlarged cross-sectional view showing a main part of another embodiment of the tapered roller bearing according to the present invention. In this bearing, the protrusion 6 is formed on the side of the large end surface 7 of the tapered roller 3. That is, the protrusion 6 is formed on a portion of the large end surface 7 of the tapered roller 3 that is in contact with the contact surface 5 of the flange 4. More specifically, the protrusion 6 is formed on the peripheral edge of the large end surface 7 of the tapered roller 3 around the axis of the tapered roller 3, and is provided closer to the outer diameter side of the peripheral edge of the large end surface 7. It has been. In FIG. 4, the inner ring 1 is indicated by a two-dot chain line.

また、本発明の円錐ころ軸受は、図示する形態に限らずこの発明の範囲内において他の形態のものであっても良く、突起部６は、鍔部４の接触面５とこの接触面５と接触する円錐ころ３の大端面７の接触部分の少なくとも一方に形成されていればよい。従って、図２、図４以外にも、図示しないが、鍔部４の接触面５に第１の突起部６が形成され、かつ、円錐ころ３の大端面７であって鍔部４の接触面５と接触する部分にも第２の突起部６が形成され、第１の突起部６と第２の突起部６同士が接触する位置に夫々形成されるようしてもよい。なお、この場合、第１の突起部６と第２の突起部６との合計高さ寸法が、前記の２μｍ〜１０μｍとなるようしている。
また、突起部６の断面形状を図２と図４においては台形としているが、これ以外に円弧部を有する形状などとしてもよい。 Further, the tapered roller bearing of the present invention is not limited to the illustrated form, and may be of other forms within the scope of the present invention, and the protrusion 6 has the contact surface 5 of the flange 4 and the contact surface 5. What is necessary is just to be formed in at least one of the contact parts of the large end surface 7 of the tapered roller 3 which contacts. Therefore, although not shown in FIGS. 2 and 4, the first protrusion 6 is formed on the contact surface 5 of the flange 4, and the large end surface 7 of the tapered roller 3 is in contact with the flange 4. The second protrusions 6 may also be formed at portions that contact the surface 5 and may be formed at positions where the first protrusions 6 and the second protrusions 6 contact each other. In this case, the total height of the first protrusion 6 and the second protrusion 6 is set to 2 μm to 10 μm.
Moreover, although the cross-sectional shape of the protrusion 6 is a trapezoid in FIGS. 2 and 4, it may be a shape having an arc portion in addition to this.

本発明の実施の一形態に係る円錐ころ軸受を示す縦断面図である。1 is a longitudinal sectional view showing a tapered roller bearing according to an embodiment of the present invention. 鍔部と円錐ころとの接触部の一部を示す拡大断面図である。It is an expanded sectional view which shows a part of contact part of a collar part and a tapered roller. 内輪の鍔部の接触面を軸心方向から見た断面図である。It is sectional drawing which looked at the contact surface of the collar part of the inner ring | wheel from the axial center direction. 鍔部と円錐ころとの接触部の変形例を示す拡大断面図である。It is an expanded sectional view which shows the modification of the contact part of a collar part and a tapered roller.

符号の説明Explanation of symbols

１ 内軸
２ 外輪
３ 円錐ころ
４ 鍔部
５ 接触面
６突起部
７ 大端面
ｈ 高さ寸法
ｗ 幅寸法 DESCRIPTION OF SYMBOLS 1 Inner shaft 2 Outer ring 3 Tapered roller 4 Collar part 5 Contact surface 6 Protrusion part 7 Large end surface h Height dimension w Width dimension

Claims (3)

内輪と、外輪と、これら内外輪間に転動自在に設けられた円錐ころと、を備え、前記内輪と外輪の少なくとも一方に前記円錐ころの端面と接触して当該円錐ころの転走を案内する接触面を有する鍔部が形成されており、油潤滑下で使用される円錐ころ軸受において、前記鍔部の接触面とこの接触面と接触する前記円錐ころの端面の少なくとも一方に、使用初期では当該鍔部の接触面と当該円錐ころの端面との間の油膜の形成を抑制し、その後摩耗して当該鍔部の接触面と当該円錐ころの端面との間において油膜の形成を可能とさせる微細突起部が形成されていることを特徴とする円錐ころ軸受。   An inner ring, an outer ring, and a tapered roller provided between the inner and outer rings so as to be capable of rolling, and at least one of the inner ring and the outer ring contacts an end surface of the tapered roller to guide the rolling of the tapered roller. In the tapered roller bearing used under oil lubrication, at least one of the contact surface of the flange portion and the end surface of the tapered roller in contact with the contact surface is initially used. Then, the formation of an oil film between the contact surface of the flange and the end surface of the tapered roller is suppressed, and then the oil film can be formed between the contact surface of the flange and the end surface of the tapered roller by wearing. A tapered roller bearing having a fine protrusion to be formed. 内輪と、外輪と、これら内外輪間に転動自在に設けられた円錐ころと、を備え、前記内輪と外輪の少なくとも一方に前記円錐ころの端面と接触して当該円錐ころの転走を案内する接触面を有する鍔部が形成されている円錐ころ軸受において、前記鍔部の接触面とこの接触面と接触する前記円錐ころの端面の少なくとも一方に、高さ寸法が２μｍ〜１０μｍの微細突起部が形成されていることを特徴とする円錐ころ軸受。   An inner ring, an outer ring, and a tapered roller provided between the inner and outer rings so as to be capable of rolling, and at least one of the inner ring and the outer ring contacts an end surface of the tapered roller to guide the rolling of the tapered roller. In a tapered roller bearing in which a flange having a contact surface is formed, a fine protrusion having a height of 2 μm to 10 μm is formed on at least one of the contact surface of the flange and the end surface of the tapered roller in contact with the contact surface A tapered roller bearing in which a portion is formed. 前記突起部は、前記鍔部の前記接触面に周方向に沿って形成されている請求項１又は２に記載の円錐ころ軸受。   The tapered roller bearing according to claim 1, wherein the protrusion is formed on the contact surface of the flange along the circumferential direction.
JP2005043777A 2005-02-21 2005-02-21 Tapered roller bearing Pending JP2006226487A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2357127A1 (en) * 2008-12-26 2011-04-19 Construcciones Y Auxiliar De Ferrocarriles, S.A. Bearing lubrication device through lubricant fluid. (Machine-translation by Google Translate, not legally binding)
KR101398983B1 (en) * 2012-11-15 2014-05-27 주식회사 베어링아트 Bearing assembly

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2357127A1 (en) * 2008-12-26 2011-04-19 Construcciones Y Auxiliar De Ferrocarriles, S.A. Bearing lubrication device through lubricant fluid. (Machine-translation by Google Translate, not legally binding)
KR101398983B1 (en) * 2012-11-15 2014-05-27 주식회사 베어링아트 Bearing assembly

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