JP2010209955A - Roller bearing - Google Patents

Roller bearing Download PDF

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JP2010209955A
JP2010209955A JP2009054365A JP2009054365A JP2010209955A JP 2010209955 A JP2010209955 A JP 2010209955A JP 2009054365 A JP2009054365 A JP 2009054365A JP 2009054365 A JP2009054365 A JP 2009054365A JP 2010209955 A JP2010209955 A JP 2010209955A
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Prior art keywords
pin
peripheral surface
type cage
pin type
ring
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JP2009054365A
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Japanese (ja)
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Yutaka Kanda
裕 神田
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/52—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers
    • F16C33/523—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers
    • F16C33/526—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers extending through the rollers and joining two lateral cage parts
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/46—Gap sizes or clearances

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure reducing stress applied to a connection part between each pin 12 of a pin-type cage 7a and each of annular plates 13a, 13b without a cost increase. <P>SOLUTION: The pin-type cage 7a is guided by the outer peripheral surfaces of large diameter side and small diameter side collars 10, 11 of an inner ring 5 facing in proximity to the inner peripheral surfaces of the respective annular plates 13a, 13b. A space D between the outer peripheral surface of each pin 12 and the inner peripheral surface of a through-hole 9 of each roller 6 is therefore made larger than spaces d<SB>1</SB>, d<SB>2</SB>between the inner peripheral surfaces of the respective annular plates 13a, 13b and the outer peripheral surfaces of the respective large diameter side and small diameter side collars 10, 11. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、例えば産業用機械、建設用機械、鉱山用機械、鉄鋼用圧延機等の、外部から大きな荷重、振動及び衝撃が加わる設備等で使用される、円筒ころ軸受や円すいころ軸受、自動調心ころ軸受等のころ軸受の改良に関する。   The present invention relates to a cylindrical roller bearing, a tapered roller bearing, an automatic machine, etc., which is used in equipment, such as industrial machines, construction machines, mining machines, steel rolling mills, etc., to which a large load, vibration and impact are applied from the outside. The present invention relates to improvements in roller bearings such as spherical roller bearings.

従来から、大きな荷重、振動及び衝撃を加わる様な設備等で使用される転がり軸受として、負荷容量の大きい円筒ころ軸受や円すいころ軸受、自動調心ころ軸受等のころ軸受を使用する事が行われている。又、この様なころ軸受として、中空ころの中にピンを通した構造のピン型保持器を使用する事も、従来から行われている。この様なピン型保持器を使用する場合には、円周方向に隣り合うころ同士の間から保持器の柱部分をなくし、ころ間の隙間を小さくして転がり軸受に組み込まれるころ数を増し、転がり軸受の負荷容量の増大を図れる。   Conventionally, roller bearings such as cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings with large load capacities have been used as rolling bearings used in facilities that are subject to large loads, vibrations, and shocks. It has been broken. Further, as such a roller bearing, a pin type cage having a structure in which a pin is passed through a hollow roller has been conventionally used. When such a pin type cage is used, the column portion of the cage is eliminated from between the circumferentially adjacent rollers, and the gap between the rollers is reduced to increase the number of rollers incorporated in the rolling bearing. The load capacity of the rolling bearing can be increased.

この様なピン型保持器を組み込んだころ軸受として、例えば特許文献１、２に記載されたものが知られている。図２は、このうちの特許文献１に記載されたころ軸受１を示している。円すいころ軸受である、このころ軸受１は、内周面に円すい凹面状の外輪軌道２を有する外輪３と、外周面に円すい凸面状の内輪軌道４を有する内輪５と、これら外輪軌道２と内輪軌道４との間に転動自在に設けられた、それぞれが円すいころである複数のころ６と、これら各ころ６を回転自在に保持するピン型保持器７とから成る。又、このうちの各ころ６は、それぞれの外周面を、上記外輪軌道２及び内輪軌道４に転がり接触する、円すい凸面状の転動面８とすると共に、それぞれが軸方向に貫通する通孔９を設けた、中空状のものとしている。又、上記内輪５の外周面両端部のうち、大径側端部には大径側鍔部１０を、小径側端部には小径側鍔部１１を、それぞれ全周に亙って形成している。   As roller bearings incorporating such pin type cages, for example, those described in Patent Documents 1 and 2 are known. FIG. 2 shows a roller bearing 1 described in Patent Document 1 among them. The roller bearing 1, which is a tapered roller bearing, includes an outer ring 3 having a conical concave outer ring raceway 2 on an inner peripheral surface, an inner ring 5 having a conical convex inner ring raceway 4 on an outer peripheral surface, and the outer ring raceway 2. It comprises a plurality of rollers 6 each of which is a tapered roller provided between the inner ring raceway 4 and a pin-type cage 7 that holds the rollers 6 rotatably. Each of the rollers 6 has a conical and convex rolling surface 8 that is in rolling contact with the outer ring raceway 2 and the inner ring raceway 4 on the outer peripheral surface thereof, and each has a through-hole penetrating in the axial direction. 9 is provided and is hollow. Further, of the outer peripheral surface both ends of the inner ring 5, a large-diameter side collar 10 is formed at the large-diameter end, and a small-diameter collar 11 is formed at the small-diameter end along the entire circumference. ing.

又、この様なころ軸受１を構成する、上記ピン型保持器７は、上記各ころ６の通孔９にそれぞれ挿通されて、これら各ころ６を回転自在に保持する複数本のピン１２と、互いに平行に、且つ同心に配置され、これら各ピン１２の両端部を連結固定する１対の環状板１３ａ、１３ｂとから成る。図示の例の場合、上記各ピン１２の一端部（図２の左端部）に、テーパねじ部１４を設けると共に、上記両環状板１３ａ、１３ｂのうちの一方（図２の左方）の環状板１３ａに、複数のテーパねじ孔１５を、周方向に亙り等間隔に形成している。そして、上記各ピン１２の一端部に形成した上記テーパねじ部１４を、上記一方の環状板１３ａの各テーパねじ孔１５にそれぞれ螺合し、この一方の環状板１３ａと各ピン１２とを連結している。   Further, the pin type cage 7 constituting such a roller bearing 1 is inserted into the through holes 9 of the respective rollers 6 and a plurality of pins 12 for rotatably holding the respective rollers 6 and And a pair of annular plates 13a and 13b which are arranged in parallel and concentric with each other and which connect and fix both ends of each pin 12. In the case of the illustrated example, a taper screw portion 14 is provided at one end portion (left end portion in FIG. 2) of each pin 12, and one of the annular plates 13a and 13b (left side in FIG. 2) has an annular shape. A plurality of taper screw holes 15 are formed in the plate 13a at equal intervals in the circumferential direction. The taper screw portion 14 formed at one end of each pin 12 is screwed into each taper screw hole 15 of the one annular plate 13a, and the one annular plate 13a and each pin 12 are connected. is doing.

又、上記１対の環状板１３ａ、１３ｂのうちの他方（図２の右方）の環状板１３ｂは、上記各ピン１２の他端部（図２の右端部）を内嵌支持する為の複数のピン受け孔１６を、周方向に亙り等間隔に形成している。そして、上記各ピン１２の他端部を、上記他方の環状板１３ｂの各ピン受け孔１６に内嵌支持した状態で、これら各ピン１２の他端部外周面に設けた段部１７ａと各ピン受け孔１６の内周面に設けた段部１７ｂとに掛け渡す状態で溶接を施し、上記各ピン１２と上記他方の環状板１３ｂとを、図示しない溶接体により連結している。   The other of the pair of annular plates 13a and 13b (the right side in FIG. 2) has an annular plate 13b for internally fitting and supporting the other end portion (the right end portion in FIG. 2) of each pin 12. A plurality of pin receiving holes 16 are formed at equal intervals in the circumferential direction. Then, in a state in which the other end portion of each pin 12 is fitted and supported in each pin receiving hole 16 of the other annular plate 13b, a step portion 17a provided on the outer peripheral surface of the other end portion of each pin 12 and each Welding is performed in a state of being spanned over a stepped portion 17b provided on the inner peripheral surface of the pin receiving hole 16, and the pins 12 and the other annular plate 13b are connected by a welded body (not shown).

ところで、上述の様な図２に示したころ軸受１の場合は、ピン型保持器７の案内を、各ころ６により行っている。即ち、これら各ころ６と、これら各ころ６の通孔９に挿通したピン１２との位置関係に基づいて、上記ピン型保持器７の径方向並びに回転方向の位置決めを図っている。但し、この様な構造の場合、運転時に加わる大きな荷重、振動及び衝撃等に伴い、例えば上記ピン型保持器７が径方向に変位し、このピン型保持器７を構成する各ピン１２に各ころ６から加わる力が過大になり、これら各ピン１２と各環状板１３ａ、１３ｂとの連結部に大きな応力が加わる可能性がある。そして、この応力の大きさによっては、例えば、上記各ピン１２の他端部と他方の連結板１３ｂとの間に施した溶接部が損傷する（例えば、溶接体が剥がれると言った損傷を生じる）可能性がある。   Incidentally, in the case of the roller bearing 1 shown in FIG. 2 as described above, the pin type cage 7 is guided by each roller 6. That is, the pin type cage 7 is positioned in the radial direction and the rotational direction based on the positional relationship between the rollers 6 and the pins 12 inserted into the through holes 9 of the rollers 6. However, in the case of such a structure, for example, the pin type cage 7 is displaced in the radial direction along with a large load, vibration and impact applied during operation, and each pin 12 constituting the pin type cage 7 The force applied from the roller 6 becomes excessive, and there is a possibility that a large stress is applied to the connecting portion between each pin 12 and each annular plate 13a, 13b. Depending on the magnitude of the stress, for example, the welded portion provided between the other end portion of each pin 12 and the other connecting plate 13b is damaged (for example, the weld body is peeled off). )there is a possibility.

上述した特許文献１に記載された構造の場合には、上記ピン型保持器７を構成する各ピン１２の強度並びに耐摩耗性を確保すべく、これら各ピン１２の外周面のうちの上記各ころ６を外嵌保持する部分に、表面硬化処理を施している。但し、この様に各ピン１２に表面硬化処理を施すだけでは、これら各ピン１２の強度並びに耐摩耗性を確保できても、上述した様な各ピン１２と環状板１３ａ、１３ｂとの連結部に加わる応力の低減を図る事はできない。この為、運転時に加わる荷重、振動及び衝撃等の大きさによっては、上記各ピン１２と環状板１３ａ、１３ｂとの連結部に大きな応力が加わり、上述した様な溶接部が損傷する等の不都合を生じる可能性がある。   In the case of the structure described in Patent Document 1 described above, each of the outer peripheral surfaces of each of the pins 12 in order to ensure the strength and wear resistance of each of the pins 12 constituting the pin type cage 7. A surface hardening process is applied to a portion that holds the roller 6 by fitting. However, even if the surface of each pin 12 is simply hardened in this way, the connecting portion between each pin 12 and the annular plates 13a and 13b as described above can be ensured even if the strength and wear resistance of each pin 12 can be secured. It is not possible to reduce the stress applied to the surface. For this reason, depending on the magnitude of load, vibration, impact, etc. applied during operation, a large stress is applied to the connecting portion between each pin 12 and the annular plates 13a, 13b, and the above-described welded portion is damaged. May occur.

一方、特許文献２には、各ピンの端部とこのピンを内嵌支持するピン受け孔の内周面との間にブッシュを嵌め込んで、このブッシュにより、これら各ピンの端部とピン受け孔とのがたつきの防止を図る事で、これら各ピンの端部とピン受け孔との間の溶接部に加わる応力の低減を図る技術が記載されている。但し、この様な特許文献２に記載された構造の場合には、上記各ピン受け孔にそれぞれブッシュを内嵌する分、部品点数、組立工程数が増大し、製造コストが嵩む可能性がある。又、上記各ブッシュにより上記各ピンの端部とピン受け孔とのがたつきを防止する分、これら各ピンの端部とピン受け孔との連結部で、これら両部材同士の（微小な）変位を許容（吸収）できなくなる可能性がある。そして、この様に変位を許容（吸収）できなくなる分、上記各ピンの基端部（根元）に大きな応力が加わり易くなり、上述の様に溶接部に加わる応力の低減を図る事ができても、運転時に加わる荷重、振動及び衝撃等の大きさによっては、上記各ピンの基端部（根元）が損傷し易くなる可能性がある。   On the other hand, in Patent Document 2, a bush is fitted between an end portion of each pin and an inner peripheral surface of a pin receiving hole for internally fitting and supporting the pin. A technique for reducing stress applied to the welded portion between the end portion of each pin and the pin receiving hole by preventing rattling with the receiving hole is described. However, in the case of the structure described in Patent Document 2, the number of parts and the number of assembling steps are increased by the amount of bushing fitted into each pin receiving hole, and the manufacturing cost may increase. . In addition, since the bushes prevent rattling between the end portions of the pins and the pin receiving holes, the connecting portions between the end portions of the pins and the pin receiving holes (a minute amount) ) Displacement may not be allowed (absorbed). Since the displacement cannot be allowed (absorbed) in this way, a large stress is easily applied to the base end portion (root) of each pin, and the stress applied to the welded portion can be reduced as described above. However, depending on the magnitude of the load, vibration, impact, etc. applied during operation, the base end portion (root) of each pin may be easily damaged.

特開平１１−３２５０６３号公報JP 11-325063 A 特開平１０−２２０４６４号公報Japanese Patent Laid-Open No. 10-220464

本発明のころ軸受は、上述の様な事情に鑑みて、ピン型保持器を組み込んだ構造で、コストを高くする事なく、このピン型保持器の各ピンと各環状板との連結部に加わる応力の低減を図れる構造を実現すべく発明したものである。   The roller bearing according to the present invention has a structure in which a pin type cage is incorporated in view of the circumstances as described above, and is added to a connecting portion between each pin of the pin type cage and each annular plate without increasing the cost. It was invented to realize a structure capable of reducing stress.

本発明のころ軸受は、前述した従来のころ軸受と同様に、外輪と、内輪と、複数のころと、ピン型保持器とを備える。
このうちの外輪は、内周面に外輪軌道を有する。
又、上記内輪は、外周面に内輪軌道を有する。
又、上記各ころは、上記内輪軌道と外輪軌道との間に転動自在に設けられた、それぞれが軸方向に貫通する通孔を有する中空のものである。
又、上記ピン型保持器は、上記各ころの通孔にそれぞれ挿通された複数本のピンを、互いに（平行に且つ）同心に配置された１対の環状板同士の間に結合固定して成るものである。 The roller bearing of the present invention includes an outer ring, an inner ring, a plurality of rollers, and a pin type cage, as in the conventional roller bearing described above.
Of these, the outer ring has an outer ring raceway on the inner peripheral surface.
The inner ring has an inner ring raceway on the outer peripheral surface.
Each of the rollers is a hollow roller provided between the inner ring raceway and the outer ring raceway so as to be freely rollable and having a through hole penetrating in the axial direction.
Further, the pin type retainer is configured such that a plurality of pins respectively inserted through the through holes of the rollers are coupled and fixed between a pair of annular plates arranged in parallel (in parallel). It consists of.

特に、本発明のころ軸受に於いては、上記ピン型保持器の径方向に関する位置決めを、このピン型保持器を構成する上記各環状板の内外両周面のうちの一方の周面と、この一方の周面と径方向に対向（近接乃至は摺接）する一方の軌道輪の周面とにより行う。即ち、上記ピン型保持器の案内を、上記各環状板の一方の周面に対向する一方の軌道輪の周面により行う。
この為に、このピン型保持器並びに上記各ころを上記外輪及び内輪同士の間に組み付けると共に、これらピン型保持器の中心軸と外輪及び内輪の中心軸とを一致させた中立状態で、このピン型保持器を構成する上記各ピンの外周面と上記各ころの通孔の内周面との間隔を、上記各環状板の一方の周面と上記一方の軌道輪の周面との間隔よりも大きくする。より具体的には、上記各ピンの外周面と上記各ころの通孔の内周面との間の隙間のうちで、上記外輪及び内輪の径方向に関する寸法が最も小さくなる部分の間隔（径方向寸法）を、上記各環状板の一方の周面と上記一方の軌道輪の周面との間の隙間のうちで、上記外輪及び内輪の径方向に関する寸法が最も小さくなる部分の間隔よりも大きくする。 In particular, in the roller bearing of the present invention, positioning in the radial direction of the pin type cage, one circumferential surface of the inner and outer circumferential surfaces of each annular plate constituting the pin type cage, This is carried out by this one peripheral surface and the peripheral surface of one of the race rings facing (adjacent or sliding) in the radial direction. That is, the pin type cage is guided by the peripheral surface of one of the race rings facing the one peripheral surface of each annular plate.
For this purpose, the pin type cage and the rollers are assembled between the outer ring and the inner ring, and the center axis of the pin type cage is aligned with the center axis of the outer ring and the inner ring. The distance between the outer peripheral surface of each pin constituting the pin type cage and the inner peripheral surface of the through hole of each roller, and the distance between one peripheral surface of each annular plate and the peripheral surface of one of the bearing rings Larger than. More specifically, in the gap between the outer peripheral surface of each pin and the inner peripheral surface of the through hole of each roller, the interval (diameter of the portion where the dimension in the radial direction of the outer ring and the inner ring is the smallest. Direction dimension) of the gap between one circumferential surface of each of the annular plates and the circumferential surface of the one raceway, and the gap between the portions where the dimensions in the radial direction of the outer ring and the inner ring are the smallest. Enlarge.

又、上述の様な本発明のころ軸受を実施する場合に好ましくは、請求項２に記載した発明の様に、一方の軌道輪の周面の軸方向両端部にそれぞれ、他方の軌道輪に向け径方向に突出する状態で全周に亙り鍔部を設けると共に、これら両鍔部の周面と、ピン型保持器を構成する各環状板の一方の周面とを係合（近接対向乃至は摺接）させる。
又、請求項３に記載した発明の様に、ピン型保持器の径方向に関する位置決めを行う為の、各環状板の一方の周面（被案内面）と、この一方の周面と径方向に係合する一方の軌道輪の周面｛のうちの少なくともこの一方の周面と近接対向する部分（案内面）｝とのうちの少なくとも何れかの面（より好ましくは両面）に、摩擦低減の為の酸化皮膜｛例えば、四酸化三鉄皮膜（Ｆｅ3Ｏ4）｝を形成する。 In the case of carrying out the roller bearing of the present invention as described above, preferably, as in the invention described in claim 2, the two bearing rings are respectively provided at both ends in the axial direction of the peripheral surface of one of the bearing rings. The flanges are provided on the entire circumference in a state of projecting in the radial direction, and the peripheral surfaces of both the flanges are engaged with one peripheral surface of each annular plate constituting the pin type cage (proximity facing or Are in sliding contact).
Further, as in the third aspect of the invention, one circumferential surface (guided surface) of each annular plate for positioning in the radial direction of the pin type cage, and the one circumferential surface and the radial direction Friction reduction on at least one surface (more preferably both surfaces) of the peripheral surface {at least one of the peripheral surfaces (guide surface)} of the raceway engaging with An oxide film {for example, triiron tetroxide film (Fe 3 O 4 )} is formed.

上述の様に構成する本発明のころ軸受によれば、コストを高くする事なく、ピン型保持器の各ピンと各環状板との連結部に加わる応力の低減を図れる。
即ち、本発明の場合には、上記ピン型保持器の径方向に関する位置決め（案内）を、各環状板の一方の周面とこの一方の周面に係合（近接対向乃至は摺接）する一方の軌道輪の周面とにより行う為、このピン型保持器の各ピンの外周面と各ころの通孔の内周面との間隔を大きくできる。この為、運転時に加わる大きな荷重、振動及び衝撃等に伴い、例えば上記各ころの位置関係が不正規になる様な場合にも、これら各ころの変位を許容して、これら各ころから各ピンに加わる力が過大になる事を防止できる。そして、その分、これら各ピンと各環状板との連結部に加わる応力の低減を図れる。この結果、これら各ピンの基端部（根元）や溶接部が損傷し易くなる事を防止でき、ころ軸受全体としての耐久性を十分に確保できる。しかも、前述の特許文献２に記載された様なブッシュ等の他の部材を必要としない為、製造コストが高くなる事も防止できる。
又、請求項３に記載した発明の様に、ピン型保持器の被案内面と軌道輪の案内面とのうちの少なくとも何れかの面（より好ましくは両面）に、例えば四酸化三鉄皮膜（Ｆｅ3Ｏ4）等の酸化皮膜を形成すれば、これら両面同士の摺動に拘らず、摩擦抵抗及び摩耗の低減を図れる。 According to the roller bearing of the present invention configured as described above, the stress applied to the connecting portion between each pin of the pin type cage and each annular plate can be reduced without increasing the cost.
That is, in the case of the present invention, the positioning (guide) in the radial direction of the pin-type cage is engaged (proximately opposed or slidably contacted) with one peripheral surface of each annular plate and the one peripheral surface. Since this is performed by the peripheral surface of one of the race rings, the distance between the outer peripheral surface of each pin of the pin type cage and the inner peripheral surface of the through hole of each roller can be increased. For this reason, even when the positional relationship between the rollers becomes irregular due to a large load, vibration, impact, etc. applied during operation, the rollers are allowed to move and It is possible to prevent excessive force applied to the. Accordingly, the stress applied to the connecting portion between each pin and each annular plate can be reduced accordingly. As a result, it is possible to prevent the base end portion (base) and the welded portion of each pin from being easily damaged, and sufficiently ensure the durability of the roller bearing as a whole. And since other members, such as a bush as described in the above-mentioned patent document 2, are not required, it can also prevent that a manufacturing cost becomes high.
Further, as in the invention described in claim 3, for example, a triiron tetroxide film is formed on at least one surface (more preferably both surfaces) of the guided surface of the pin type cage and the guide surface of the bearing ring. If an oxide film such as (Fe 3 O 4 ) is formed, it is possible to reduce frictional resistance and wear regardless of sliding of both surfaces.

図１は、本発明の実施の形態の１例を示している。尚、本例の特徴は、コストを高くする事なく、ピン型保持器７ａの各ピン１２と各環状板１３ａ、１３ｂとの連結部に加わる応力の低減を図るべく、このピン型保持器７ａを案内する部分（ピン型保持器７ａの位置決めを図る部分）の構造を工夫した点にある。その他の部分の構造及び作用は、前述の図２に示した従来構造と同様であるから、同等部分に関する図示並びに説明は省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。   FIG. 1 shows an example of an embodiment of the present invention. The feature of this example is that this pin type cage 7a is intended to reduce the stress applied to the connecting portion between each pin 12 of the pin type cage 7a and each annular plate 13a, 13b without increasing the cost. The structure of the portion for guiding the pin (the portion for positioning the pin type cage 7a) is devised. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIG. 2, the illustration and description of the equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of this example.

本例のころ軸受１ａを構成するピン型保持器７ａも、前述した従来構造と同様に、各ころ６の通孔９にそれぞれ挿通される複数本のピン１２と、互いに平行に、且つ同心に配置され、これら各ピン１２の両端部を連結固定する１対の環状板１３ａ、１３ｂとから成る。又、上記各ピン１２の一端部（図１の左端部）に、テーパねじ部１４を設けると共に、上記両環状板１３ａ、１３ｂのうちの一方（図１の左方）の環状板１３ａに、複数のテーパねじ孔１５を、周方向に亙り等間隔に形成している。そして、上記各ピン１２の一端部に形成した上記テーパねじ部１４を、上記一方の環状板１３ａの各テーパねじ孔１５にそれぞれ螺合し、この一方の環状板１３ａと各ピン１２とを連結している。   The pin type cage 7a constituting the roller bearing 1a of the present example is also parallel to and concentric with the plurality of pins 12 respectively inserted into the through holes 9 of the rollers 6 as in the conventional structure described above. It consists of a pair of annular plates 13a, 13b which are arranged and which connect and fix both ends of each pin 12. Further, a taper screw portion 14 is provided at one end portion (left end portion in FIG. 1) of each pin 12, and one of the annular plates 13a and 13b (left side in FIG. 1) is provided on the annular plate 13a. A plurality of taper screw holes 15 are formed in the circumferential direction at equal intervals. The taper screw portion 14 formed at one end of each pin 12 is screwed into each taper screw hole 15 of the one annular plate 13a, and the one annular plate 13a and each pin 12 are connected. is doing.

又、上記１対の環状板１３ａ、１３ｂのうちの他方（図１の右方）の環状板１３ｂは、上記各ピン１２の他端部（図１の右端部）を内嵌支持する為の複数のピン受け孔１６を、周方向に亙り等間隔に形成している。そして、上記各ピン１２の他端部を、上記他方の環状板１３ｂの各ピン受け孔１６に内嵌支持した状態で、これら各ピン１２の他端部外周面に設けた段部１７ａと各ピン受け孔１６の内周面に設けた段部１７ｂとに掛け渡す状態で溶接を施して、上記各ピン１２と上記他方の環状板１３ｂとを、図示しない溶接体により連結している。   The other of the pair of annular plates 13a and 13b (the right side in FIG. 1) is an annular plate 13b for internally fitting and supporting the other end of each pin 12 (the right end in FIG. 1). A plurality of pin receiving holes 16 are formed at equal intervals in the circumferential direction. Then, in a state in which the other end portion of each pin 12 is fitted and supported in each pin receiving hole 16 of the other annular plate 13b, a step portion 17a provided on the outer peripheral surface of the other end portion of each pin 12 and each Each pin 12 and the other annular plate 13b are connected to each other by a welded body (not shown) by performing welding in a state of being stretched over a stepped portion 17b provided on the inner peripheral surface of the pin receiving hole 16.

又、本例の場合には、上述の様なピン型保持器７ａの径方向に関する位置決めを、このピン型保持器７ａを構成する上記各環状板１３ａ、１３ｂの内周面と、内輪５の軸方向両端部にそれぞれ設けた大径側、小径側各鍔部１０、１１の外周面との係合（近接対向乃至は摺接）により行う様にしている。即ち、本例の場合には、上記ピン型保持器７ａの案内（径方向に関する位置決め）を、上記各環状板１３ａ、１３ｂの内周面と係合する、上記内輪５の大径側、小径側各鍔部１０、１１の外周面により行う様にしている。この為に、本例の場合には、上記環状板１３ａの内径を上記大径側鍔部１０の外径よりも、上記環状板１３ｂの内径を上記小径側鍔部１１の外径よりも、それぞれ少しだけ大きくしている。又、上記ピン型保持器７ａ並びに各ころ６を外輪３の内周面と内輪５の外周面との間の所定の位置に組み付けると共に、これらピン型保持器７ａの中心軸と外輪３及び内輪５の中心軸とを一致させた中立状態（図１の状態）で、このピン型保持器７ａのピン１２の外周面ところ６の通孔９の内周面との（上記外輪３及び内輪５の径方向に関する）間隔Ｄを、互いに係合する上記各環状板１３ａ、１３ｂの内周面と上記大径側、小径側各鍔部１０、１１の外周面との（上記外輪３及び内輪５の径方向に関する）間隔ｄ1、ｄ2よりも大きく（Ｄ＞ｄ1、Ｄ＞ｄ2）している。又、本例の場合には、被案内面となる上記各環状板１３ａ、１３ｂの内周面と、案内面となる上記大径側、小径側各鍔部１０、１１の外周面とのうち少なくとも何れかの面（必要に応じて両面）に、酸化皮膜を形成し、互いに摺接するこれら両面同士の、摩擦抵抗（ころ軸受１ａの動トルク）、及び、係合部を構成する各面の摩耗の低減を図っている。 Further, in the case of this example, the positioning of the pin type cage 7a in the radial direction as described above is performed with respect to the inner peripheral surfaces of the annular plates 13a and 13b constituting the pin type cage 7a and the inner ring 5. This is performed by engagement (proximity facing or sliding contact) with the outer peripheral surfaces of the large-diameter side and small-diameter side flanges 10 and 11 provided at both ends in the axial direction. That is, in the case of this example, the guide (positioning in the radial direction) of the pin type retainer 7a is engaged with the inner peripheral surface of each of the annular plates 13a and 13b. It is made to carry out by the outer peripheral surface of each side collar part 10,11. Therefore, in the case of this example, the inner diameter of the annular plate 13a is larger than the outer diameter of the large-diameter side flange 10, and the inner diameter of the annular plate 13b is larger than the outer diameter of the small-diameter side flange 11. Each is slightly larger. The pin type cage 7a and each roller 6 are assembled at a predetermined position between the inner circumferential surface of the outer ring 3 and the outer circumferential surface of the inner ring 5, and the central axis of the pin type cage 7a, the outer ring 3 and the inner ring 5 in the neutral state (the state shown in FIG. 1) in which the central axis of the pin 5 is aligned with the outer peripheral surface of the pin 12 and the inner peripheral surface of the through-hole 9 of the pin 12 (the outer ring 3 and the inner ring 5). The distance D between the inner peripheral surface of each of the annular plates 13a and 13b and the outer peripheral surface of each of the large-diameter side and small-diameter side flanges 10 and 11 (with respect to the outer ring 3 and the inner ring 5). Are larger than the distances d 1 and d 2 (D> d 1 , D> d 2 ). In the case of this example, the inner peripheral surface of each of the annular plates 13a and 13b serving as a guided surface and the outer peripheral surface of each of the large-diameter side and small-diameter side flanges 10 and 11 serving as a guide surface. An oxide film is formed on at least one surface (both surfaces if necessary), and friction surfaces (dynamic torque of the roller bearing 1a) between these surfaces that are in sliding contact with each other, and each surface that constitutes the engaging portion The wear is reduced.

尚、上記酸化皮膜としては、例えば四酸化三鉄皮膜（Ｆｅ3Ｏ4）が好ましい。又、この皮膜形成時の皮膜厚さは、例えば０．３〜３μｍとする。この様な四酸化三鉄皮膜は、軸受材料として一般的に使用されるＳＵＪ２（高炭素クロム軸受鋼）に比べて摩擦係数が低いと共に、潤滑油を保持し易い多孔質層を構成する。又、四酸化三鉄皮膜の最表面の硬度は約３５０〜５００Ｈｖ程度であり、ＳＵＪ２製のころの軸方向端面（或いは鍔部の側面）の硬度（約６５０〜７７０Ｈｖ）に比べて低くなる。この為、四酸化三鉄皮膜は、所謂固体潤滑剤の軟質皮膜と同様の役割を果たし、摺接部での摩擦を低減し、摩擦熱の発生を抑える事ができる。従って、高速回転で運転する場合にも、摺接部での温度上昇を抑え、かじりや焼き付き等の損傷が発生する事を有効に防止できる。又、上記四酸化三鉄皮膜を形成する為には、所謂黒染処理の中でも一般的な、低温加熱（１３０〜１６０℃）の苛性ソーダ（ＮａＯＨ）水溶液中に浸漬して行なう方法を採用できる。この様な黒染処理は、表面粗さを向上させる為の仕上加工（潤滑油を保持する為の溝や凹部の加工を行なう場合も含む）を行う場合や、セラミック系皮膜を（例えばＰＶＤ法等により）形成する場合に比べて、低コストで実施できる。尚、上記黒染処理としては、上述の苛性ソーダ水溶液を用いる方法の他、従来から知られた、乾式酸化法、過熱水蒸気法、溶融硝酸塩法、酸性着色法、陽極酸化法、アルカリ着色法等の黒染処理を用いる事もできる。 As the oxide film, for example, a triiron tetroxide film (Fe 3 O 4 ) is preferable. Moreover, the film thickness at the time of this film formation shall be 0.3-3 micrometers, for example. Such a triiron tetroxide film has a lower friction coefficient than SUJ2 (high carbon chromium bearing steel) generally used as a bearing material, and constitutes a porous layer that easily retains lubricating oil. Further, the hardness of the outermost surface of the triiron tetroxide film is about 350 to 500 Hv, which is lower than the hardness (about 650 to 770 Hv) of the axial end surface (or side surface of the flange) of the SUJ2 roller. For this reason, the triiron tetroxide film plays the same role as the so-called soft film of the solid lubricant, can reduce the friction at the sliding contact portion, and can suppress the generation of frictional heat. Therefore, even when operating at high speed rotation, it is possible to suppress temperature rise at the sliding contact portion and effectively prevent damage such as galling or seizure. Moreover, in order to form the said triiron tetroxide film | membrane, the method of immersing in the caustic soda (NaOH) aqueous solution of a low temperature heating (130-160 degreeC) common among what is called a black dyeing process can be employ | adopted. Such blackening treatment can be used for finishing processing to improve the surface roughness (including when processing grooves and recesses for retaining lubricating oil), and for ceramic coating (for example, PVD method). Etc.) can be carried out at a lower cost compared to the case of forming. In addition, as the blackening treatment, in addition to the method using the above-mentioned aqueous sodium hydroxide solution, conventionally known methods such as dry oxidation, superheated steam, molten nitrate, acidic coloring, anodic oxidation, alkali coloring, etc. Black dyeing treatment can also be used.

上述の様に構成する本例の場合には、コストを高くする事なく、ピン型保持器７ａを構成する各ピン１２と各環状板１３ａ、１３ｂとの連結部に加わる応力の低減を図れる。
即ち、本例の場合には、上述の様に、上記ピン型保持器７ａの径方向に関する位置決め（案内）を、上記各環状板１３ａの内周面とこの内周面に近接対向する内輪５の外周面（より具体的には大径側、小径側各鍔部１０、１１の外周面）とにより行う。そして、この様に案内する為に、上記各ピン１２の外周面と各ころ６の通孔９の内周面との（外輪３及び内輪５の径方向に関する）間隔Ｄを大きくしている。この為、運転時に加わる大きな荷重、振動及び衝撃等に伴ない、例えば上記各ころ６の位置関係が不正規になる様な場合にも、これら各ころ６の変位を許容して、これら各ころ６から各ピン１２に加わる力が過大になる事を防止できる。そして、その分、これら各ピン１２と各環状板１３ａ、１３ｂとの連結部に加わる応力の低減を図れる。この結果、これら各ピン１２の基端部（根元）や溶接部が損傷し易くなると言った不都合を防止でき、ころ軸受１ａ全体としての耐久性を十分に確保できる。しかも、前述の特許文献２に記載された様なブッシュ等の他の部材を必要としない為、製造コストが高くなる事も防止できる。 In the case of this example configured as described above, it is possible to reduce the stress applied to the connecting portion between each pin 12 and each annular plate 13a, 13b constituting the pin type cage 7a without increasing the cost.
That is, in the case of the present example, as described above, the positioning (guide) in the radial direction of the pin type cage 7a is performed with respect to the inner peripheral surface of each annular plate 13a and the inner ring 5 that is closely opposed to the inner peripheral surface. The outer peripheral surface (more specifically, the outer peripheral surface of each of the large-diameter side and small-diameter side flanges 10 and 11). And in order to guide in this way, the space | interval D (with respect to the radial direction of the outer ring 3 and the inner ring 5) of the outer peripheral surface of each said pin 12 and the inner peripheral surface of the through-hole 9 of each roller 6 is enlarged. For this reason, even when the positional relationship between the rollers 6 becomes irregular due to a large load, vibration, impact, etc. applied during operation, the rollers 6 are allowed to be displaced, 6 can prevent the force applied to each pin 12 from becoming excessive. Accordingly, the stress applied to the connecting portion between each pin 12 and each annular plate 13a, 13b can be reduced accordingly. As a result, it is possible to prevent the inconvenience that the base end portion (root) and the welded portion of each pin 12 are easily damaged, and the durability of the roller bearing 1a as a whole can be sufficiently secured. And since other members, such as a bush as described in the above-mentioned patent document 2, are not required, it can also prevent that a manufacturing cost becomes high.

本発明は、図示の様な円すいころ軸受に限らず、円筒ころ軸受、自動調心ころ軸受等の他の型式のころ軸受で実施する事もできる。又、図示の様な単列のころ軸受の他、複列、更には、多列のころ軸受で実施する事もできる。又、図示した構造は、ピン型保持器の各環状板の内周面を被案内面とし、内輪の軸方向両端部に設けた鍔部の外周面を案内面としているが、内外を逆にする事もできる。即ち、図示は省略するが、ピン型保持器の各環状板の外周面を被案内面とし、外輪の内周面（外輪の軸方向両端部に鍔部を設けた構造であれば、これら両鍔部の内周面）を案内面とする事もできる。   The present invention is not limited to the tapered roller bearing as shown in the figure, but can be implemented by other types of roller bearings such as a cylindrical roller bearing and a self-aligning roller bearing. Further, in addition to the single row roller bearings as shown in the figure, it can also be implemented with double row or multi-row roller bearings. In the illustrated structure, the inner peripheral surface of each annular plate of the pin type cage is the guided surface, and the outer peripheral surfaces of the flanges provided at both axial ends of the inner ring are the guide surfaces. You can also do it. That is, although not shown in the drawings, the outer peripheral surface of each annular plate of the pin type cage is a guided surface, and the inner peripheral surface of the outer ring (if the structure is provided with flanges at both axial ends of the outer ring, both these The inner peripheral surface of the buttocks can be used as a guide surface.

本発明の実施の形態の１例を示す図２の上半部に相当する断面図。Sectional drawing equivalent to the upper half part of FIG. 2 which shows one example of embodiment of this invention. 従来構造の１例を示す半部断面図。The half part sectional view showing an example of conventional structure.

１、１ａ ころ軸受
２ 外輪軌道
３ 外輪
４ 内輪軌道
５ 内輪
６ ころ
７、７ａ ピン型保持器
８ 転動面
９ 通孔
１０ 大径側鍔部
１１ 小径側鍔部
１２ ピン
１３ａ、１３ｂ 環状板
１４ テーパねじ部
１５ テーパねじ孔
１６ ピン受け孔
１７、１７ａ 段部 DESCRIPTION OF SYMBOLS 1, 1a Roller bearing 2 Outer ring raceway 3 Outer ring 4 Inner ring raceway 5 Inner ring 6 Roller 7, 7a Pin type cage 8 Rolling surface 9 Through hole 10 Large diameter side flange 11 Small diameter side collar 12 Pin 13a, 13b Annular plate 14 Taper screw part 15 Taper screw hole 16 Pin receiving hole 17, 17a Step part

Claims (3)

内周面に外輪軌道を有する外輪と、外周面に内輪軌道を有する内輪と、これら内輪軌道と外輪軌道との間に転動自在に設けられた、それぞれが軸方向に貫通する通孔を有する中空の複数のころと、これら各ころの通孔にそれぞれ挿通された複数本のピンを、互いに同心に配置された１対の環状板同士の間に結合固定して成るピン型保持器とを備えた
ころ軸受に於いて、
上記ピン型保持器の径方向に関する位置決めを、このピン型保持器を構成する上記各環状板の内外両周面のうちの一方の周面と、この一方の周面と径方向に対向する一方の軌道輪の周面とにより行うべく、上記ピン型保持器並びに上記各ころを上記外輪及び内輪同士の間に組み付けると共に、これらピン型保持器の中心軸と外輪及び内輪の中心軸とを一致させた中立状態で、このピン型保持器を構成する上記各ピンの外周面と上記各ころの通孔の内周面との間隔を、上記各環状板の一方の周面と上記一方の軌道輪の周面との間隔よりも大きくした、
事を特徴とするころ軸受。 An outer ring having an outer ring raceway on the inner peripheral surface, an inner ring having an inner ring raceway on the outer peripheral surface, and a rolling hole provided between the inner ring raceway and the outer ring raceway, each having a through hole penetrating in the axial direction. A plurality of hollow rollers, and a pin-type cage formed by coupling and fixing a plurality of pins respectively inserted through the through holes of the rollers, between a pair of annular plates arranged concentrically with each other. In the roller bearing provided,
Positioning in the radial direction of the pin type cage is performed by positioning one circumferential surface of both the inner and outer circumferential surfaces of each annular plate constituting the pin type cage and one circumferential surface facing the one circumferential surface. The above-mentioned pin type cage and each roller are assembled between the outer ring and the inner ring, and the center axis of these pin type cage and the center axis of the outer ring and the inner ring coincide with each other so In the neutral state, the distance between the outer peripheral surface of each of the pins constituting the pin type cage and the inner peripheral surface of the through hole of each of the rollers is set so that the one peripheral surface of each of the annular plates and the one track Larger than the distance from the circumference of the ring,
Roller bearings characterized by things. 一方の軌道輪の周面の軸方向両端部にそれぞれ、他方の軌道輪に向け径方向に突出する状態で全周に亙り鍔部を設けると共に、これら両鍔部の周面と、ピン型保持器を構成する各環状板の一方の周面とを係合させた、
請求項１に記載したころ軸受。 At both ends in the axial direction of the peripheral surface of one track ring, a flange portion is provided on the entire circumference in a state of projecting in the radial direction toward the other track ring. Engaged with one peripheral surface of each annular plate constituting the vessel,
The roller bearing according to claim 1. ピン型保持器の径方向に関する位置決めを行う為の、各環状板の一方の周面と、この一方の周面と径方向に対向する一方の軌道輪の周面とのうちの少なくとも何れかの面に、酸化皮膜を形成した、
請求項１〜２のうちの何れか１項に記載したころ軸受。 At least one of one circumferential surface of each annular plate and the circumferential surface of one raceway ring that is radially opposed to the one circumferential surface for positioning in the radial direction of the pin type cage An oxide film was formed on the surface,
The roller bearing described in any one of Claims 1-2.
JP2009054365A 2009-03-09 2009-03-09 Roller bearing Withdrawn JP2010209955A (en)

Priority Applications (1)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104265771A (en) * 2014-09-23 2015-01-07 徐州重型机械有限公司 Bearing, pulley assembly, telescopic arm and crane
WO2016159137A1 (en) * 2015-04-03 2016-10-06 Ntn株式会社 Rolling device and rolling bearing
JP2016196958A (en) * 2015-04-03 2016-11-24 Ntn株式会社 Rolling device and rolling bearing

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104265771A (en) * 2014-09-23 2015-01-07 徐州重型机械有限公司 Bearing, pulley assembly, telescopic arm and crane
WO2016159137A1 (en) * 2015-04-03 2016-10-06 Ntn株式会社 Rolling device and rolling bearing
JP2016196958A (en) * 2015-04-03 2016-11-24 Ntn株式会社 Rolling device and rolling bearing

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