JP2005331054A - Tapered roller bearing, and structure for supporting pilot portion shaft of transmission - Google Patents

Tapered roller bearing, and structure for supporting pilot portion shaft of transmission Download PDF

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JP2005331054A
JP2005331054A JP2004151237A JP2004151237A JP2005331054A JP 2005331054 A JP2005331054 A JP 2005331054A JP 2004151237 A JP2004151237 A JP 2004151237A JP 2004151237 A JP2004151237 A JP 2004151237A JP 2005331054 A JP2005331054 A JP 2005331054A
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tapered roller
bearing
row
roller
tapered
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Yasuhiro Uehori
泰裕 上堀
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2004151237A priority Critical patent/JP2005331054A/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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • 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
    • F16C19/38—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 two or more rows of rollers
    • F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered 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
    • 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
    • F16C33/34—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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing which hardly causes skewing even if the total length of rollers becomes long, and can cope with a high-speed rotation by keeping a contact pressure at a flange portion low, and is compact, and can reduce its cost, and further to provide a structure for supporting the pilot portion shaft of a transmission. <P>SOLUTION: The tapered roller bearing has conical raceway surfaces 1aa, 1ab on the outside periphery of an inner race 1 so as to correspond to respective rows of the double row rollers 3A, 3B. The tapered roller bearing is configured such that flange surfaces 5a, 7a, 7b, 6a are provided on both sides of the respective raceway surfaces 1aa, 1ab, and the cone centers of the raceway surfaces 1aa, 1ab of the respective rows coincide with each other at a point. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は、各種の機器、例えば高ミスアライメント環境下で使用される自動車のトランスミッションパイロット部の支持などに用いられる円すいころ軸受、およびトランスミッションのパイロット部軸支持構造に関する。   The present invention relates to a tapered roller bearing used for supporting various devices, for example, a transmission pilot portion of an automobile used in a high misalignment environment, and a pilot portion shaft support structure of a transmission.

自動車のトランスミッションのパイロット部支持に用いられる円すいころ軸受は、トランスミッションの構造上の制約から、円すいころを細くて長い形状としている。また、使用条件として、この円すいころ軸受では、ミスアライメントが大きく、外輪がギヤからなり、このギヤの内径面が外輪軌道面となる。そのため、スキューに起因した破損が円すいころに発生することがある。
そこで、この対策として、円すいころを長さ方向に並ぶ複数個の分割ころに分割し、内輪および外輪の軌道面を各分割ころに対応する軸方向部分間にわたって連続した１つの円すい状面とした円すいころ軸受が提案されている（特許文献１）。
特開２００３−１８４８８５号公報 Tapered roller bearings used for supporting a pilot portion of an automobile transmission have a tapered roller shape that is thin and long due to structural limitations of the transmission. Further, as a use condition, in this tapered roller bearing, misalignment is large, the outer ring is made of a gear, and the inner diameter surface of this gear is the outer ring raceway surface. Therefore, damage due to skew may occur in the tapered rollers.
Therefore, as a countermeasure, the tapered roller is divided into a plurality of divided rollers arranged in the length direction, and the raceway surfaces of the inner ring and the outer ring are formed as one conical surface continuous over the axial portion corresponding to each divided roller. Tapered roller bearings have been proposed (Patent Document 1).
JP 2003-184885 A

上記円すいころ軸受では、長さ方向に並ぶ複数個の分割ころが、保持器の同じポケット内に保持されていて、１つの分割ころの大端面は隣り合う他の１つの分割ころの小端面に接触した状態にある。そのため、荷重が作用したときに、分割ころ列の複数列に作用する荷重を、軌道面と１つの鍔面で支える構造となり、鍔面には複数列分の荷重が掛かる。そのため、鍔部の接触面圧が高くなり、高速回転で使用すると、鍔面に潤滑不足等を生じる恐れがある。   In the tapered roller bearing, a plurality of divided rollers arranged in the length direction are held in the same pocket of the cage, and a large end surface of one divided roller is a small end surface of another adjacent divided roller. In contact. Therefore, when a load is applied, the load acting on a plurality of rows of the split roller rows is supported by the raceway surface and one ridge surface, and a load for a plurality of rows is applied to the ridge surface. For this reason, the contact surface pressure of the heel portion becomes high, and if used at a high speed, there is a risk of insufficient lubrication on the heel surface.

上記した鍔部の接触面圧を低減する対策として、例えば図６に示すように、通常の円すいころ軸受２１を、内輪間座２３および外輪間座２４を介して軸方向に複数列（ここでは２列）配置することも可能である。しかし、この場合には、構成部品が多くなるため、コンパクトに構成できずコスト増を招くことにもなる。   As a measure for reducing the contact surface pressure of the above-described collar portion, for example, as shown in FIG. 6, a normal tapered roller bearing 21 is arranged in a plurality of rows (here, through an inner ring spacer 23 and an outer ring spacer 24). (2 rows) can also be arranged. However, in this case, since the number of components increases, a compact configuration cannot be achieved, resulting in an increase in cost.

この発明の目的は、ころ長さの総和が長くなっても、スキューが発生し難く、鍔部の接触面圧を低く抑えることができて高速回転に対応可能で、かつコンパクトに構成でき低コスト化が可能な円すいころ軸受を提供することである。
この発明の他の目的は、パイロット部軸受のスキューが発生し難く、鍔部の接触面圧を低く抑えることができて高速回転に対応可能で、かつコンパクトに構成でき低コスト化が可能なトランスミッションのパイロット部軸支持構造を提供することである。 The object of the present invention is that skew does not easily occur even when the total length of the rollers becomes long, the contact surface pressure of the collar portion can be kept low, can cope with high-speed rotation, can be configured compactly, and is low in cost. It is to provide a tapered roller bearing that can be made.
Another object of the present invention is that the pilot part bearing is less likely to be skewed, the contact surface pressure of the collar part can be kept low, can cope with high-speed rotation, can be configured compactly, and can be reduced in cost. It is providing the pilot part shaft support structure.

この発明の円すいころ軸受は、内輪の外周に、複数列の各ころ列に対する円すい面状の軌道面を有し、各軌道面の両側に鍔面を有し、各列の軌道面のコーンセンタが１点で交わるものとしている。
この構成によると、各列のころが個別の鍔面で支えられるので、鍔面を形成する鍔への接触面圧を低く抑えることができ、限られた寸法内で大きな定格荷重を得ることができる。その結果、ころのスキューに起因する破損を防止でき、高速回転に対応できる。また、各列のころは、スキューについて、それぞれが独立して挙動する。このため、各列のころのスキューが発生し難くなる。さらに、一般の円すいころ軸受を軸方向に複数列並べて構成する場合に比べて、部品点数が少なくなるので、構成がコンパクトになり、かつ低コストで製作できる。各列の軌道面はコーンセンタが１点で交わるものとしているため、各列が同じ向きとなる複列の円すいころ軸受としながら、各列のころと軌道面との間で周速差が生じることが回避でき、円滑な動作が得られる。 The tapered roller bearing according to the present invention has a tapered raceway surface for each of a plurality of rows of roller rows on the outer periphery of the inner ring, and has flanges on both sides of each raceway surface, and the cone center of each row of raceway surfaces. Are supposed to meet at one point.
According to this configuration, the rollers of each row are supported by individual flange surfaces, so that the contact surface pressure to the flanges forming the flange surface can be kept low, and a large load rating can be obtained within a limited size. it can. As a result, breakage due to roller skew can be prevented and high-speed rotation can be handled. Each row of rollers behaves independently with respect to skew. For this reason, it becomes difficult for skew of each row to occur. Furthermore, since the number of parts is reduced as compared with the case where general tapered roller bearings are arranged in a plurality of rows in the axial direction, the configuration becomes compact and can be manufactured at low cost. Since the raceway surfaces of each row intersect at a single cone center, a circumferential speed difference occurs between the rollers of each row and the raceway surface while using double row tapered roller bearings in which each row has the same orientation. Can be avoided, and smooth operation can be obtained.

この発明において、大径側列のころのころ径を、小径側列のころのころ径よりも小さくし、大径側列のころの転走する軌道面に対する小鍔面を省略しても良い。
この構成の場合、内輪における小径側列の軌道面に対して大径側列の軌道面が段差をなし、その段差面が小径側列のころの大端面が接する大鍔面となる。そのため、内輪の加工が容易になりコストの低減が可能となる。 In this invention, the roller diameter of the roller in the large diameter side row may be made smaller than the roller diameter of the roller in the small diameter side row, and the small flange surface with respect to the raceway surface on which the roller in the large diameter side row rolls may be omitted. .
In the case of this configuration, the raceway surface of the large-diameter side row forms a step with respect to the raceway surface of the small-diameter side row in the inner ring, and the step surface becomes a large flange surface where the large end surface of the roller of the small-diameter side row contacts. Therefore, the inner ring can be easily processed, and the cost can be reduced.

この発明において、自動車のトランスミッションパイロット部に設置される軸受であっても良い。
自動車のトランスミッションパイロット部では、パイロット部軸受に大きな負荷容量が要求されることから、そのパイロット部軸受は、ころ長さの長い円すいころ軸受となる。しかも、このパイロット部軸受はミスアライメントが生じ易いものとなる。しかし、このパイロット部軸受として、この発明の円すいころ軸受を用いた場合、そのスキュー防止の効果が上がり、パイロット部軸受の軸受寿命が向上する。 In the present invention, a bearing installed in a transmission pilot portion of an automobile may be used.
In a transmission pilot part of an automobile, since a large load capacity is required for the pilot part bearing, the pilot part bearing is a tapered roller bearing having a long roller length. Moreover, this pilot part bearing is likely to be misaligned. However, when the tapered roller bearing of the present invention is used as the pilot portion bearing, the effect of preventing skew is increased, and the bearing life of the pilot portion bearing is improved.

この発明のトランスミッションのパイロット部軸支持構造は、ハウジングに軸受を介して入力側軸が回転自在に支持され、入力側軸と同一軸心上に下段側軸が配置され、両軸を互いに回転自在に支持するパイロット部軸受が、下段側軸の外周と入力側軸の内周の間に設けられたパイロット部軸支持構造において、上記パイロット部軸受を、この発明の上記いずれかの構成の円すいころ軸受としたことを特徴とする。
このパイロット部軸支持構造によると、パイロット部軸受のスキューが発生し難く、鍔部の接触面圧を低く抑えることができて高速回転に対応可能で、かつコンパクトに構成でき低コスト化が可能となる。 In the transmission pilot shaft support structure of the present invention, the input side shaft is rotatably supported by the housing via the bearing, the lower stage side shaft is disposed on the same axis as the input side shaft, and both shafts are rotatable relative to each other. In the pilot part shaft support structure in which the pilot part bearing that is supported between the outer periphery of the lower stage side shaft and the inner periphery of the input side shaft is provided, the pilot part bearing is a tapered roller having any one of the above configurations of the present invention. It is a bearing.
According to this pilot part shaft support structure, the pilot part bearing is less likely to be skewed, the contact surface pressure of the collar part can be kept low, can be adapted to high-speed rotation, and can be configured compactly and at a low cost. Become.

この発明の円すいころ軸受は、内輪の外周に、複数列の各ころ列に対する円すい面状の軌道面を有し、各軌道面の両側に鍔面を有し、各列の軌道面のコーンセンタが１点で交わるものとしたため、ころ長さの総和が長くなっても、スキューが発生し難く、鍔部の接触面圧を低く抑えることができて高速回転に対応可能で、かつコンパクトに構成でき低コスト化が可能な円すいころ軸受とすることができる。
この発明のトランスミッションのパイロット部軸支持構造は、パイロット部軸受にこの発明の円すいころ軸受を用いたため、パイロット部軸受に要求される大きな負荷容量に対して、ころ長さの総和の長い円すいころ軸受となっても、パイロット部軸受のスキューが発生し難く、鍔部の接触面圧を低く抑えることができて高速回転に対応可能で、かつコンパクトに構成でき低コスト化が可能なものとなる。 The tapered roller bearing according to the present invention has a tapered raceway surface for each of a plurality of rows of roller rows on the outer periphery of the inner ring, and has flanges on both sides of each raceway surface, and the cone center of each row of raceway surfaces. Since the crossing at one point, even if the total roller length is long, skew is unlikely to occur, the contact surface pressure of the buttocks can be kept low, and high speed rotation can be achieved, and the structure is compact. Therefore, it can be a tapered roller bearing capable of reducing the cost.
In the pilot part shaft support structure of the transmission according to the present invention, the tapered roller bearing according to the present invention is used for the pilot part bearing. Therefore, the tapered roller bearing having a long total roller length with respect to a large load capacity required for the pilot part bearing. Even in this case, it is difficult for the pilot portion bearing to be skewed, the contact surface pressure of the collar portion can be kept low, it is possible to cope with high-speed rotation, a compact configuration can be achieved, and the cost can be reduced.

この発明の第１の実施形態を図１および図２と共に説明する。この円すいころ軸受は、内輪１と、外輪２と、これら内外輪１，２の軌道面１ａ，２ａの間に転動自在に円周方向に配列された複数個の円すいころ３と、保持器４とを備える。内輪１の外周および外輪２の内周に形成される前記各軌道面１ａ，２ａは円すい面状とされている。内輪１の軌道面１ａは、その小径側に小鍔５を、大径側に大鍔６を、小径側と大径側の中間位置に別の中間鍔７をそれぞれ有する。   A first embodiment of the present invention will be described with reference to FIGS. The tapered roller bearing includes an inner ring 1, an outer ring 2, a plurality of tapered rollers 3 arranged in a circumferential direction so as to be freely rollable between raceway surfaces 1a and 2a of the inner and outer rings 1 and 2, a cage 4. The raceway surfaces 1a and 2a formed on the outer periphery of the inner ring 1 and the inner periphery of the outer ring 2 are conical. The raceway surface 1a of the inner ring 1 has a small collar 5 on the small diameter side, a large collar 6 on the large diameter side, and another intermediate collar 7 at an intermediate position between the small diameter side and the large diameter side.

この軌道面１ａは、前記中間鍔７によって２列の軌道面１ａａ，１ａｂに分割されていて、これら両列の軌道面１ａａ，１ａｂのコーンセンタは、図２のように外輪２の軌道面２ａのコーンセンタと共に１点Ｏで交わるようにされている。これら２列の軌道面１ａａ，１ａｂに対応させて、各円すいころ３は長さ方向に並ぶ２列の円すいころ３Ａ，３Ｂとされている。すなわち、小径側列の円すいころ３Ａは軌道面１ａａ上に、大径側列の円すいころ３Ｂは軌道面１ａｂ上にそれぞれ配列される。   The raceway surface 1a is divided into two rows of raceway surfaces 1aa and 1ab by the intermediate rod 7, and the cone center of the raceway surfaces 1aa and 1ab of both rows is the raceway surface 2a of the outer ring 2 as shown in FIG. It intersects with the cone center at 1 point O. Corresponding to these two rows of raceway surfaces 1aa, 1ab, the tapered rollers 3 are two rows of tapered rollers 3A, 3B arranged in the length direction. That is, the tapered roller 3A of the small diameter side row is arranged on the raceway surface 1aa, and the tapered roller 3B of the large diameter side row is arranged on the raceway surface 1ab.

前記小鍔５の内側の側面は、円すいころ３Ａの小端面が接する小鍔面５ａとされる。中間鍔７の円すいころ３Ａ側に向く側面は、円すいころ３Ａの大端面が接する大鍔面７ａとされ、中間鍔７の円すいころ３Ｂ側に向く側面は、円すいころ３Ｂの小端面が接する小鍔面７ｂとされる。大鍔６の内側の側面は、円すいころ３Ｂの大端面が接する大鍔面６ａとされる。
各列の円すいころ３Ａ，３Ｂの両側の端面における外周縁には面取りが施されている。円すいころ３の長さ方向の列数は、この実施形態では２列としているが、３列以上とし、その列数に合わせて前記軌道面１ａの列を増やしても良い。この場合、前記軌道面１ａの軸方向中間の中間鍔７の数も増やすことになる。このような列数の増加は、軸受幅が広い場合に有効である。 The inner side surface of the gavel 5 is a gavel surface 5a with which the small end surface of the tapered roller 3A contacts. The side surface of the intermediate roller 7 facing the tapered roller 3A side is a large flange surface 7a that contacts the large end surface of the tapered roller 3A, and the side surface of the intermediate roller 7 facing the tapered roller 3B side is a small surface that contacts the small end surface of the tapered roller 3B. It is set as the collar surface 7b. The inner side surface of the large collar 6 is a large collar surface 6a with which the large end surface of the tapered roller 3B contacts.
Chamfering is performed on the outer peripheral edges of the end faces on both sides of the tapered rollers 3A and 3B in each row. The number of rows in the length direction of the tapered rollers 3 is two in this embodiment, but may be three or more, and the number of rows of the raceway surface 1a may be increased in accordance with the number of rows. In this case, the number of intermediate rods 7 in the middle of the track surface 1a in the axial direction is also increased. Such an increase in the number of rows is effective when the bearing width is wide.

外輪２は鍔無しとされ、その内周の軌道面２ａは２列の円すいころ３Ａ，３Ｂに対応する軸方向区間にわたって連続した１つの円すい面状とされている。外輪２は、独立した軸受部品であっても、またギヤや軸など、他の機械部品を兼用するものであっても良い。例えば、この円すいころ軸受をトランスミッションのパイロット部用の軸受とする場合は、外輪２はギヤを兼用する部品とされる。   The outer ring 2 has no wrinkles, and the raceway surface 2a on the inner periphery thereof has a conical surface shape continuous over the axial section corresponding to the two rows of tapered rollers 3A and 3B. The outer ring 2 may be an independent bearing part, or may also be used as another mechanical part such as a gear or a shaft. For example, when this tapered roller bearing is used as a bearing for a pilot portion of a transmission, the outer ring 2 is a component that also serves as a gear.

保持器４は、円すいころ３を保持するポケット４ａを円周方向の複数箇所に有するものである。同じ円周方向位置に並ぶ２列の円すいころ３Ａ，３Ｂは、保持器４の幅方向に並ぶ２つのポケット４ａ内にそれぞれ分けて保持している。保持器４に対する円すいころ３の組み立て方法は、各列の円すいころ３Ａ，３Ｂを２個並べる点が単一円すいころの場合と異なるだけであり、保持器４を底拡げし、加締める方法で、軸受への円すいころ３の組み立てが行える。
なお、この例では２列の円すいころ３Ａ，３Ｂを１つの保持器４で保持しているが、各列ごとに別々の保持器で円すいころ３Ａ，３Ｂを保持するようにしても良い。また、この例では保持器４は鉄板製であるが、樹脂製としても良い。 The cage 4 has pockets 4a for holding the tapered rollers 3 at a plurality of locations in the circumferential direction. Two rows of tapered rollers 3 </ b> A and 3 </ b> B aligned at the same circumferential position are separately held in two pockets 4 a aligned in the width direction of the cage 4. The method of assembling the tapered roller 3 with respect to the cage 4 is different from the case of a single tapered roller in that two tapered rollers 3A and 3B are arranged in each row, and the cage 4 is expanded and crimped. The tapered roller 3 can be assembled to the bearing.
In this example, two rows of tapered rollers 3A and 3B are held by one cage 4. However, the tapered rollers 3A and 3B may be held by separate cages for each row. In this example, the cage 4 is made of iron plate, but may be made of resin.

この構成の円すいころ軸受によると、各列が同じ向きとなる複列の円すいころ軸受としたが、各列の軌道面１ａａ，１ａｂのコーンセンタが１点Ｏで交わるものとしたため、各列のころ３Ａ，３Ｂと内輪軌道面１ａａ，１ａｂや、外輪軌道面２ａとの間で周速差が生じることが回避でき、円滑な動作が得られる。このように、複数列の円すいころ３Ａ，３Ｂを、内輪１の外周に設けた円すい面状の複数列の軌道面１ａａ，１ａｂ上にそれぞれ配列し、各軌道面１ａａ，１ａｂの両側に各列の円すいころ３Ａ，３Ｂの端面に接する鍔面５ａ，７ａ，７ｂ，６ａを設けたため、円すいころ３Ａ，３Ｂに荷重が作用したときに、各列の円すいころ３Ａ，３Ｂは個別の鍔面で支えられることになる。そのため、鍔面を形成する各鍔５，６，７への接触面圧を低く抑えることができ、限られた寸法内で大きな定格荷重を得ることができる。その結果、円すいころ３Ａ，３Ｂのスキューに起因する破損を防止でき、高速回転に対応できる。また、各列の円すいころ３Ａ，３Ｂは、スキューについて、それぞれが独立して挙動する。このため、各列の円すいころ３Ａ，３Ｂのスキューが発生し難くなる。さらに、一般の円すいころ軸受を軸方向に複数列並べて構成する場合に比べて、部品点数が少なくなるので、構成がコンパクトになり、かつ低コストで製作できる。   According to the tapered roller bearing of this configuration, the double row tapered roller bearings have the same orientation in each row. However, since the cone centers of the raceway surfaces 1aa and 1ab in each row intersect at one point O, A difference in peripheral speed between the rollers 3A, 3B and the inner ring raceway surfaces 1aa, 1ab and the outer ring raceway surface 2a can be avoided, and a smooth operation can be obtained. In this way, a plurality of rows of tapered rollers 3A, 3B are arranged on a plurality of tapered surface raceway surfaces 1aa, 1ab provided on the outer periphery of the inner ring 1, and each row is arranged on both sides of each raceway surface 1aa, 1ab. Since the flange surfaces 5a, 7a, 7b, and 6a that are in contact with the end surfaces of the tapered rollers 3A and 3B are provided, when a load is applied to the tapered rollers 3A and 3B, the tapered rollers 3A and 3B in each row are formed by individual flange surfaces. It will be supported. Therefore, the contact surface pressure to each of the ridges 5, 6, and 7 forming the ridge surface can be kept low, and a large load rating can be obtained within a limited size. As a result, breakage due to the skew of the tapered rollers 3A and 3B can be prevented, and high-speed rotation can be handled. Further, the tapered rollers 3A and 3B in each row behave independently of each other with respect to skew. For this reason, the skew of the tapered rollers 3A and 3B in each row is less likely to occur. Furthermore, since the number of parts is reduced as compared with the case where general tapered roller bearings are arranged in a plurality of rows in the axial direction, the configuration becomes compact and can be manufactured at low cost.

図３および図４はこの発明の他の実施形態を示す。この実施形態の円すいころ軸受は、図１に示した第１の実施形態において、大径側列の円すいころ３Ｂのころ径を、小径側列の円すいころ３Ａのころ径よりも小さくすると共に、内輪１における軸方向中間位置の中間鍔７を省略したものである。また、これに対応させて、内輪１の軌道面１ａは、小径側列の軌道面１ａａと大径側列の軌道面１ａｂとが段差を成すように構成されており、その段差面が小径側列の円すいころ３Ａの大端面が接する大鍔面７ａとされている。ただし、内輪１の段差を成す両軌道面１ａａ，１ａｂのコーンセンタは、図４に示すように、外輪２の軌道面２ａと共に１点Ｏで交わるようにされている。また、この実施形態では、各列の円すいころ３Ａ，３Ｂが、それぞれ別々の保持器４Ａ，４Ｂで保持されている。その他の構成は図１に示した第１の実施形態の場合と同じである。   3 and 4 show another embodiment of the present invention. In the tapered roller bearing of this embodiment, in the first embodiment shown in FIG. 1, the roller diameter of the tapered roller 3B in the large diameter side row is made smaller than the roller diameter of the tapered roller 3A in the small diameter side row, The intermediate rod 7 at the intermediate position in the axial direction in the inner ring 1 is omitted. Correspondingly, the raceway surface 1a of the inner ring 1 is configured such that the raceway surface 1aa of the small diameter side row and the raceway surface 1ab of the large diameter side row form a step, and the step surface is on the small diameter side. The large tapered surface 7a is in contact with the large end surface of the tapered roller 3A in the row. However, the cone centers of both raceway surfaces 1aa and 1ab forming the step of the inner ring 1 intersect with the raceway surface 2a of the outer ring 2 at one point O as shown in FIG. In this embodiment, the tapered rollers 3A and 3B in each row are held by separate cages 4A and 4B, respectively. Other configurations are the same as those of the first embodiment shown in FIG.

この構成の円すいころ軸受では、内輪１における小径側列の軌道面１ａａに対して、大径側列の軌道面１ａｂが段差を成すようにして、その段差面を小径側列の円すいころ３Ａの大端面が接する大鍔面７ａとしている。このため、第１の実施形態における軸方向中間位置の中間鍔７が省略され、これにより、内輪１の加工が容易になりコストの低減が可能となる。この場合、大径側列の円すいころ３Ｂに対する小鍔面が無いが、外輪２を組み込む前の状態では、大径側列の保持器４Ｂが小径側列の保持器４Ａに当たるので、大径側列の円すいころ３Ａおよび保持器４Ｂが内輪１から外れるのを防止できる。その他の効果は第１の実施形態の場合と同じである。   In the tapered roller bearing of this configuration, the raceway surface 1ab of the large-diameter side row forms a step with respect to the raceway surface 1aa of the small-diameter side row in the inner ring 1, and the step surface of the tapered roller 3A of the small-diameter side row is formed. A large ridge surface 7a is in contact with the large end surface. For this reason, the intermediate rod 7 at the axially intermediate position in the first embodiment is omitted, thereby making it easy to process the inner ring 1 and reducing the cost. In this case, there is no small flange surface for the tapered roller 3B in the large diameter side row, but in a state before the outer ring 2 is assembled, the cage 4B in the large diameter side row hits the cage 4A in the small diameter side row. It is possible to prevent the tapered rollers 3 </ b> A and the cage 4 </ b> B from being detached from the inner ring 1. Other effects are the same as those of the first embodiment.

図５は、この発明の円すいころ軸受を装備したトランスミッションのパイロット部軸支持構造の一例を示す。このトランスミッションは、自動車のマニュアルトランスミッションである。ハウジング１１に軸受１２を介してインプットシャフトとなる入力側軸１３が回転自在に支持され、入力側軸１３と同一軸心上に、メインシャフトとなる下段側軸１４が配置されている。両軸１３，１４は、パイロット部軸受１５により、互いに相対回転自在に支持されている。パイロット部軸受１５は、下段側軸１４の外周と入力側軸１３の内周の間に設けられている。   FIG. 5 shows an example of a pilot portion shaft support structure of a transmission equipped with the tapered roller bearing of the present invention. This transmission is a manual transmission of an automobile. An input side shaft 13 serving as an input shaft is rotatably supported by the housing 11 via a bearing 12, and a lower stage shaft 14 serving as a main shaft is disposed on the same axis as the input side shaft 13. Both shafts 13 and 14 are supported by a pilot portion bearing 15 so as to be rotatable relative to each other. The pilot portion bearing 15 is provided between the outer periphery of the lower stage side shaft 14 and the inner periphery of the input side shaft 13.

パイロット部軸受１５は、この発明における図１の実施形態にかかる円すいころ軸受である。パイロット部軸受１５の内輪１は、下段側軸１４の外径面に嵌合して装着されている。パイロット部軸受１５の外輪２は、入力側軸１３の軸端に設けられた中空軸部で構成され、外周にギヤ１６が形成されている。すなわち、外輪２は、ギヤ１６と兼用する部品として構成され、また入力側軸１３と一体に構成されている。ギヤ１６は、下段側軸１４と平行なカウンタシャフト（図示せず）に設けられたギヤと噛み合う。入力側軸１３のギヤ１６の隣接部には、ドッグクラッチ１７におけるドッグ歯１８が一体に設けられており、入力側軸１３の回転は、シンクロナイザを有するドッグクラッチ１７を介して下段側軸１４に伝達可能である。また、入力側軸１３の回転は、上記カウンタシャフトを介して上記とは別の伝達経路（図示せず）から下段側軸１４に伝達可能である。   The pilot portion bearing 15 is a tapered roller bearing according to the embodiment of FIG. The inner ring 1 of the pilot portion bearing 15 is fitted and attached to the outer diameter surface of the lower stage side shaft 14. The outer ring 2 of the pilot unit bearing 15 is constituted by a hollow shaft portion provided at the shaft end of the input side shaft 13, and a gear 16 is formed on the outer periphery. That is, the outer ring 2 is configured as a part that also serves as the gear 16, and is configured integrally with the input side shaft 13. The gear 16 meshes with a gear provided on a counter shaft (not shown) parallel to the lower stage side shaft 14. The dog teeth 18 of the dog clutch 17 are integrally provided in the adjacent portion of the gear 16 of the input side shaft 13, and the rotation of the input side shaft 13 is transferred to the lower stage side shaft 14 via the dog clutch 17 having a synchronizer. It can be transmitted. Further, the rotation of the input side shaft 13 can be transmitted to the lower side shaft 14 through a transmission path (not shown) different from the above through the counter shaft.

この構成のトランスミッションのパイロット部によると、パイロット部軸受１５に大きな負荷容量が要求される。したがって、パイロット部軸受１５は、ころ総長さの長い円すいころ軸受となる。しかも、このパイロット部軸受１５は、軸１３，１４間の撓みによるミスアライメントが生じ易いものとなる。しかし、パイロット部軸受１５として、上記実施形態の円すいころ軸受を用いたため、そのスキュー防止の効果が上がり、パイロット部軸受１５の軸受寿命が向上する。   According to the pilot portion of the transmission having this configuration, the pilot portion bearing 15 is required to have a large load capacity. Therefore, the pilot portion bearing 15 is a tapered roller bearing having a long total roller length. Moreover, the pilot portion bearing 15 is likely to be misaligned due to the bending between the shafts 13 and 14. However, since the tapered roller bearing of the above embodiment is used as the pilot portion bearing 15, the effect of preventing skew is increased, and the bearing life of the pilot portion bearing 15 is improved.

なお、図５に示したトランスミッションのパイロット部は、入力側軸１３がインプットシャフトであって、かつ下段側軸１４がメインシャフトとなるものであるが、上記したトランスミッションのパイロット部軸支持構造は、同軸心に配置された下段側軸の外周と入力側軸の内周の間に設けられたパイロット部軸受一般に適用することができる。例えば図５のトランスミッションのパイロット部において、下段側軸１４が互いに上段側および下段側の軸となるパイロットシャフトとメインシャフトとに軸方向に分割されていて、両シャフト間にパイロット部軸受（図示せず）が設けられた構造のトランスミッションである場合に、そのパイロット部軸受にこの発明の円すいころ軸受を用いても良い。   In the pilot portion of the transmission shown in FIG. 5, the input side shaft 13 is the input shaft and the lower stage side shaft 14 is the main shaft. The present invention can be generally applied to pilot section bearings provided between the outer periphery of the lower stage side shaft disposed coaxially and the inner periphery of the input side shaft. For example, in the pilot portion of the transmission shown in FIG. 5, the lower shaft 14 is divided in the axial direction into a pilot shaft and a main shaft which are upper and lower shafts. 3), the tapered roller bearing of the present invention may be used as the pilot portion bearing.

この発明の第１の実施形態にかかる円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing concerning 1st Embodiment of this invention. 同円すいころ軸受における軌道面コーンセンタの説明図である。It is explanatory drawing of the raceway surface cone center in the same tapered roller bearing. この発明の他の実施形態にかかる円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing concerning other embodiment of this invention. 同円すいころ軸受における軌道面コーンセンタの説明図である。It is explanatory drawing of the raceway surface cone center in the same tapered roller bearing. 第１の実施形態にかかる円すいころ軸受を応用したトランスミッションのパイロット部軸支持構造の断面図である。It is sectional drawing of the pilot part shaft support structure of the transmission which applied the tapered roller bearing concerning 1st Embodiment. 従来例の断面図である。It is sectional drawing of a prior art example.

符号の説明Explanation of symbols

１…内輪
１ａ，１ａａ，１ａｂ…軌道面
２…外輪
２ａ…軌道面
３，３Ａ，３Ｂ…円すいころ
５ａ，７ｂ…小鍔面
６ａ，７ａ…大鍔面
１５…パイット部軸受 DESCRIPTION OF SYMBOLS 1 ... Inner ring 1a, 1aa, 1ab ... Raceway surface 2 ... Outer ring 2a ... Raceway surface 3, 3A, 3B ... Tapered roller 5a, 7b ... Small collar surface 6a, 7a ... Large collar surface 15 ... Pit part bearing

Claims (4)

内輪の外周に、複数列の各ころ列に対する円すい面状の軌道面を有し、各軌道面の両側に鍔面を有し、各列の軌道面のコーンセンタが１点で交わるものとした円すいころ軸受。   The outer ring of the inner ring has a conical raceway surface for each row of rollers, and has a flange surface on both sides of each raceway surface, and the cone centers of the raceway surfaces of each row intersect at one point. Tapered roller bearings. 請求項１において、大径側列のころのころ径を、小径側列のころのころ径よりも小さくし、大径側列のころの転走する軌道面に対する小鍔面を省略した円すいころ軸受。   2. The tapered roller according to claim 1, wherein the roller diameter of the roller in the large diameter side row is made smaller than the roller diameter of the roller in the small diameter side row, and the small flange surface with respect to the raceway surface on which the roller in the large diameter side row rolls is omitted. bearing. 請求項１または請求項２において、自動車のトランスミッションパイロット部に設置される軸受である円すいころ軸受。   The tapered roller bearing according to claim 1 or 2, wherein the tapered roller bearing is a bearing installed in a transmission pilot portion of an automobile. ハウジングに軸受を介して入力側軸が回転自在に支持され、入力側軸と同一軸心上に下段側軸が配置され、両軸を互いに回転自在に支持するパイロット部軸受が、下段側軸の外周と入力側軸の内周の間に設けられたトランスミッションのパイロット部軸支持構造において、上記パイロット部軸受を、請求項１または請求項２に記載の円すいころ軸受としたことを特徴とするトランスミッションのパイロット部軸支持構造。   The input side shaft is rotatably supported by the housing via the bearing, the lower stage side shaft is disposed on the same axis as the input side axis, and the pilot section bearing that supports both the shafts in a rotatable manner is provided on the lower side axis. 3. A transmission having a pilot portion shaft support structure provided between an outer periphery and an inner periphery of an input side shaft, wherein the pilot portion bearing is the tapered roller bearing according to claim 1 or 2. Pilot part shaft support structure.
JP2004151237A 2004-05-21 2004-05-21 Tapered roller bearing, and structure for supporting pilot portion shaft of transmission Pending JP2005331054A (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006119738A1 (en) * 2005-05-13 2006-11-16 Schaeffler Kg Four-row tapered roller bearing
JP2009024742A (en) * 2007-07-18 2009-02-05 Ntn Corp Double row tapered roller bearing
DE102010013627A1 (en) * 2010-04-01 2011-10-06 Aktiebolaget Skf Bearing arrangement and gearbox
JP2012021557A (en) * 2010-07-13 2012-02-02 Jtekt Corp Tapered roller bearing
EP2598762B1 (en) * 2010-07-30 2016-01-20 Aktiebolaget SKF Bearing arrangement and gearbox
WO2017026353A1 (en) * 2015-08-07 2017-02-16 透一 野渡 Thrust roller bearing

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006119738A1 (en) * 2005-05-13 2006-11-16 Schaeffler Kg Four-row tapered roller bearing
US7871202B2 (en) 2005-05-13 2011-01-18 Schaeffler Kg Four-row tapered roller bearing
JP2009024742A (en) * 2007-07-18 2009-02-05 Ntn Corp Double row tapered roller bearing
DE102010013627A1 (en) * 2010-04-01 2011-10-06 Aktiebolaget Skf Bearing arrangement and gearbox
WO2011120833A1 (en) * 2010-04-01 2011-10-06 Aktiebolaget Skf Multi-row tapered roller bearing and transmission comprising such a bearing
CN102844577A (en) * 2010-04-01 2012-12-26 Skf公司 Multi-row tapered roller bearing and transmission comprising such a bearing
US8939651B2 (en) 2010-04-01 2015-01-27 Aktiebolaget Skf Multi-row tapered roller bearing and transmission having such a bearing
JP2012021557A (en) * 2010-07-13 2012-02-02 Jtekt Corp Tapered roller bearing
EP2598762B1 (en) * 2010-07-30 2016-01-20 Aktiebolaget SKF Bearing arrangement and gearbox
WO2017026353A1 (en) * 2015-08-07 2017-02-16 透一 野渡 Thrust roller bearing

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